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© Wärtsilä
RECEIVER PULSES AND TEMPERATURE DISTRIBUTION IMPACT ON PERFORMANCE OF A LARGE BORE GAS ENGINE
GT CONFERENCE 2016FRANKFURT, OCTOBER 17
1
Wärtsilä: G. Lo Iacono, G. CaputoPOWERTECH: E. Servetto
© Wärtsilä2
AGENDA
1. Introduction
2. GT-POWER Simulation Model Setup
3. Investigation on Engine Variants
4. Resonator Tuning and Optimization
5. Experimental Measurements
6. Conclusions
© Wärtsilä3
1. Introduction
2. GT-POWER Simulation Model Setup
3. Investigation on Engine Variants
4. Resonator Tuning and Optimization
5. Experimental Measurements
6. Conclusions
© Wärtsilä4
1. INTRODUCTION
Merchant OffshoreCruise
and FerryNavy
Special
Vessels
Product requirements for Marine engines:
W46DFCO2
NOxSOx
ParticulatesDual-Fuel engine
in gas mode
Diesel
engine
0
10
20
30
40
50
60
70
80
90
100
Emission
values [%]-30%
-85%
-99%
-95%
• Fuel flexibility (Gas, MDO, HFO)
• High output and low fuel consumption
• IMO and EPA compliance
• High power density
• Advanced engine control and diagnostics
• Compact design
© Wärtsilä5
1. INTRODUCTION
6L20DF 1.0 MW
8L20DF 1.4 MW
9L20DF 1.6 MW
8V31DF 4.4 MW
10V31DF 5.5 MW
12V31DF 6.6 MW
14V31DF 7.7 MW
16V31DF 8.8 MW
20V31DF 11.0 MW
6L34DF 3.0 MW
8L34DF 4.0 MW
9L34DF 4.5 MW
12V34DF 6.0 MW
16V34DF 8.0 MW
20V34DF 10.0 MW
6L50DF 5.9 MW
8L50DF 7.8 MW
9L50DF 8.8 MW
12V50DF 11.7 MW
16V50DF 15.6 MW
18V50DF 17.6 MW
6L46DF 6.9 MW
7L46DF 8.0 MW
8L46DF 9.2 MW
9L46DF 10.3 MW
12V46DF 13.7 MW
14V46DF 16.0 MW
16V46DF 18.3 MW
0 5 10 15 20 MW
34DF
50DF
46DF
31DF
20DF
• Charge air system performance in terms of receiver
pressure pulses and charge air temperature distribution
affect remarkably the power output of modern DF engine.
• Huge pressure pulses and large temperature gradient
inside the receiver lead to:
Deteriorated knock resistance in Gas mode reduced max
power output and lower engine brake efficiency
Turbocharger instability unexpected compressor surge
and/or overall lower engine performance
40
42
44
46
48
50
52
54
56
58
60
CA temp cyl 2 CA temp cyl 5 CA temp cyl 6 CA temp cyl 7 CA temp cyl 8 Temp Receivert3
Tem
pera
ture
[ C
]
8L46DF lab engine Receiver Temperature - Diesel mode
100% load No resonator
• Different pressure pulsations behavior for different cylinder
configuration.
© Wärtsilä6
1. Introduction
2. GT-POWER Simulation Model Setup
3. Investigation on Engine Variants
4. Resonator Tuning and Optimization
5. Experimental Measurements
6. Conclusions
© Wärtsilä
7
2. GT-POWER MODEL SETUP
• A detailed GT-POWER model representing the 8LW46DF engine was built
• Intake/Exhaust geometries were converted in GEM-3D
The SPEX pulse
converter was
modeled by means of
a FlowSplitGeneral.
EXHAUST SIDEINTAKE SIDE
© Wärtsilä8
2. GT-POWER MODEL SETUP
• The GT-POWER model was calibrated and extensively validated in both
constant and variable speed conditions on several experimental datasets
© Wärtsilä9
2. GT-POWER MODEL SETUP
• The GT-POWER model was calibrated and extensively validated in both
constant and variable speed conditions on several experimental datasets
Temperature
along receiver
Gradient as a
function of Load
© Wärtsilä10
1. Introduction
2. GT-POWER Simulation Model Setup
3. Investigation on Engine Variants
4. Resonator Tuning and Optimization
5. Experimental Measurements
6. Conclusions
© Wärtsilä11
3. INVESTIGATION ON ENGINE VARIANTS
• The other engine variants of the 46DF family were built, scaling the
validated 8L into the 6L, 7L, 9L, 12V, 14V and 16V configurations
© Wärtsilä12
3. INVESTIGATION ON ENGINE VARIANTS
• The natural frequencies of the whole intake system were investigated via
linear analysis for the 8L, 9L, 12V and 16V engines.
~630rpm
8L ~575rpm
9L
~520rpm
16V ~620rpm
12V
© Wärtsilä13
1. Introduction
2. GT-POWER Simulation Model Setup
3. Investigation on Engine Variants
4. Resonator Tuning and Optimization
5. Experimental Measurements
6. Conclusions
© Wärtsilä
14
4. RESONATOR TUNING AND OPTIMIZATION
• In order to reduce the pressure fluctuations and
the consequent temperature gradient, an
internal Lambda/4 resonator was proposed
Air Receiver
Internal
Lambda/4
• Resonator Length = 6600mm
• Receiver Length (8L) = 7700mm
• Too tight a fit!
Solution: U-Shaped Resonator
Open End
Closed End
Dividing Wall
Closed End
f=1/4*v/L 1st harmonic order resonator frequency
F=3/2*RPM/60 receiver pulsation frequency
L=10*v/RPM Length resonator
© Wärtsilä
15
4. RESONATOR TUNING AND OPTIMIZATION
• Coupled CONVERGE Lite + GT simulations were run, to assess the impact of
the 180° bend at the end of the U-Shaped Lambda/4 on its effectiveness.
High velocity
region around lip
180° bend does
not affect resonator
frequency or
effectiveness
© Wärtsilä
16
4. RESONATOR TUNING AND OPTIMIZATION
• Standalone 1D simulations were carried out as well, to prove that GT is
capable of correctly reproducing the effects of the U-shaped Lambda/4
Temperature
along receiver
Gradient at
100%
© Wärtsilä
17
4. RESONATOR TUNING AND OPTIMIZATION
• GT-POWER results were used
to determine the optimal
location along the receiver
where to place the Lambda/4
• On the 8L configuration, the
amplitude of the 1.5° order was
found to be maximum close to
cylinder 8
• The resonator was therefore
placed there to maximize its
effectiveness
C8C7C6C5C4C3C2C1
165
170
175
180
185
190
0 0.1 0.2 0.3 0.4 0.5 0.6 0.7 0.8 0.9 1
Am
plit
ud
e [d
B]
Normalized Distance [-]
L/4
© Wärtsilä18
2. GT-POWER MODEL SETUP
• A trade-off length for the U-shaped Lambda/4 was defined and then tested
on all the “critical” cylinder configurations (8L, 9L, 12V and 16V)
© Wärtsilä19
1. Introduction
2. GT-POWER Simulation Model Setup
3. Investigation on Engine Variants
4. Resonator Tuning and Optimization
5. Experimental Measurements
6. Conclusions
© Wärtsilä20
5. EXPERIMENTAL MEASUREMENTS
Peak to
peak [bar]Cyl 2 Cyl 4 Cyl 8
No
resonator0,38 0,31 0,82
Resonator
U type0,24 0,28 0,49
• Pressure pulses are reduced along all
the receiver. Huge improvement -40%
on the last cylinder.
• Knocking resistance in Gas mode is
improved. Lower Lambda is possible
to set reducing the fuel consumption.
Pressure pulses damping and higher
volumetric efficiency explains the
improvement.
Receiver Pressure Cyl 2 – 100% load
Receiver Pressure Cyl 4 – 100% load
Receiver Pressure Cyl 8 – 100% load
- U-type Resonator
- No resonator
© Wärtsilä21
5. EXPERIMENTAL MEASUREMENTS
• Wider temperature gradient distribution inside the receiver with the U-type resonator than no
resonator case. Result is not in line with GT-power simulation.
• The different behavior is probably due to an uneven wall temperature distribution along the charge air
receiver, which was not modeled in GT.
CA temp cyl 2 CA temp cyl 5 CA temp cyl 6 CA temp cyl 7 CA temp cyl 8
Exp. 100% load no resonator 45.8 47.3 48.0 49.1 51.1
Sim. GT 100% load no resonator 46.3 48.0 48.7 49.5 51.0
40.0
42.0
44.0
46.0
48.0
50.0
52.0
54.0
56.0
58.0
60.0
Tem
pe
ratu
re [
°C]
8L46DF lab engine - NO Resonator Diesel mode
Exp. 100% load no resonator
Sim. GT 100% load no resonator
CA temp cyl 2 CA temp cyl 5 CA temp cyl 6 CA temp cyl 7 CA temp cyl 8
Exp. 100% load U-type 41.8 43.1 44.3 45.3 49.5
Sim. GT 100% load U-type 46.2 47.3 47.7 48.3 50.0
40.0
42.0
44.0
46.0
48.0
50.0
52.0
54.0
56.0
58.0
60.0
Tem
pe
ratu
re [
°C]
8L46DF lab engine - U-type Resonator test Diesel mode
Exp. 100% load U-type
Sim. GT 100% load U-type
© Wärtsilä22
5. EXPERIMENTAL MEASUREMENTS
Engine settings No resonator vs U-type
p3 Press In Receiver bar_g -0,10
t3 Temp In Receiver °C 45
Main Engine performance
Engine Efficiency pts % +0,3
Lamda TOT Total Air Ratio - 2,05
NOx Specific At 5% O2 Dry % +35,0
THC Marine Specific As CH4 % -14,0
t5 Temp b Turbine °C -3,0
Firing Pressure max max bar -20
Heat Release 5% Mean °CA -1,1
Heat Release 50% Mean °CA -1,2
Combustion Duration Mean °CA -1,3
IMEP COV Mean pts % -0,45
The installation of the resonator allows:
• +0.3 pts % brake efficiency @ same
knocking margin thanks to the chance to
set a lower receiver pressure setting.
• CoV < 1.5%.
• Faster Combustion duration.
• Lower pmax max -20bar.
© Wärtsilä23
1. Introduction
2. GT-POWER Simulation Model Setup
3. Investigation on Engine Variants
4. Resonator Tuning and Optimization
5. Experimental Measurements
6. Conclusions
© Wärtsilä24
6. CONCLUSIONS
• GT power well supported in predicting pressure pulses inside the charge air receiver and in
designing the resonator to dump them. Good correlation between experimental data and simulated
one is found on 8L cylinder configuration lab engine.
• Cylinder configurations that needs a resonator and the most critical frequencies have been identified.
• Experimental Temperature distribution along the charge air receiver does not match with the
simulated wider distribution in the real case is found. Difference is most probably due to the
complex design of the charge air receiver, so the wall heat exchange was not well reproduced with
the simplified model used.
• A comparison among overall performance of the U-type resonator with other resonator designs
(external, long internal…) is planned as next step of the study, focusing on the influence of volumetric
efficiency and charge air distribution on knock resistance and engine brake efficiency.
© Wärtsilä25
6. CONCLUSIONS
21.3.2016 Authors: G. Lo Iacono; E. Servetto; G. Caputo
© Wärtsilä26
6. CONCLUSIONS
© Wärtsilä
RECEIVER PULSES AND TEMPERATURE DISTRIBUTION IMPACT ON PERFORMANCE OF A LARGE BORE GAS ENGINE
GT CONFERENCE 2016FRANKFURT, OCTOBER 17
27
Wärtsilä: G. Lo Iacono, G. CaputoPOWERTECH: E. Servetto