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© by VKA – all rights reserved. Confidential – no passing on to third parties
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Institute for Combustion Engines
RWTH Aachen University
Prof. Dr.-Ing. Stefan Pischinger
1 Institute for Combustion Engines RWTH Aachen University 2 FEV GmbH, Aachen
Modeling of Axial Forces on
Turbocharger Rotors
Frankfurt, October 26th, 2015
Max Stadermann1, Johannes Scharf2
© by VKA – all rights reserved. Confidential – no passing on to third parties
Enhanced part load simulation accuracy
– Prediction of fuel consumption in driving cycles (GT-Drive)
– Set point for load step simulations
Design of TC thrust bearings
– One of the most frequent causes for TC failure
Definition of boundary conditions for TC bearing
simulations
Precise consideration of TC bearing losses for TC
efficiency calculation
Do we need thrust load modeling?
BM
EP
/ b
ar
0
4
8
12
16
20
Engine speed / 1/min
1000 2000 3000 4000
1.5 l TC DI WLTP
0.50
0.55
0.60
0.65
0.70
0.75
0.80
0.85
0.90
0.95
1.00
1.0 1.2 1.4 1.6 1.8 2.0 2.2 2.4 2.6 2.8 3.0 3.2 3.4
Tu
rbin
e E
ffic
ien
cy η
T/ -
.
Turbine Pressure Ratio p3t/p4 / - .
)hh(m
P)hqh(m
stis,4,tot3,T
Ftot1,Ctot2,Vadis,T,
Isentropic adiabatic efficiency
)hh(m
P)hh(m
stis,4,tot3,T
Ftot1,tot2,VisT,
Isentropic efficiency
)hh(m
)hh(m*
stis,4,tot3,T
tot1,tot2,VTCm,isT,
Net turbine efficiency
© by VKA – all rights reserved. Confidential – no passing on to third parties
Agenda
General Behavior of TC Friction Losses
Overview of TC Thrust Load Modeling
Impact of TC Friction Losses on Engine Modeling
– Full Load Operation at Rated Power Condition
– Transient Response during Load Steps at Low Engine Speeds
Conclusion
© by VKA – all rights reserved. Confidential – no passing on to third parties
Main Influential Parameters on TC Bearing Friction
Thrust Load Difficult to Predict during TC Operation
-60 -40 -20 0 20 40 60Axialkraft / N
Axial Load Fax / N
pOil = 4 bar (abs.)
TOil = 90 °C
nTC = 120 000 1/min
nTC = 80 000 1/min
nTC = 40 000 1/min
0
50
100
150
200
250
300
350
400
450
500
550
0 40000 80000 120000 160000
ATL Drehzahl / 1/min
pOil = 4 bar (abs.)
TOil = 90 °C
FAx = 0 N
TC Speed nTC / 1/min
TC
Be
arin
g F
riction
PF /
W
© by VKA – all rights reserved. Confidential – no passing on to third parties
TC Friction Test Bench
Independent Speed and Thrust Load Control
Electric Drive
Toil,out
MF
Toil,in, poil Thrust Load Actuator
Fax
© by VKA – all rights reserved. Confidential – no passing on to third parties
Agenda
General Behavior of TC Friction Losses
Overview of TC Thrust Load Modeling
Impact of TC Friction Losses on Engine Modeling
– Full Load Operation at Rated Power Condition
– Transient Response during Load Steps at Low Engine Speeds
Conclusion
© by VKA – all rights reserved. Confidential – no passing on to third parties
Overview of Thrust Load Modelling
Model Validation using Strain Gage and Pressure Sensors
C,1mF
CS,F
CWheel,F
TWheel,F
TS,F
T,4mF
Tp4,FCp1,
F
2p
1p
3p
4p
BFC,p
BFT,p
Model has been calibrated using TC test bench data and works for
different temperature and pressure boundary conditions
© by VKA – all rights reserved. Confidential – no passing on to third parties
Agenda
General Behavior of TC Friction Losses
Overview of TC Thrust Load Modeling
Impact of TC Friction Losses on Engine Modeling
– Full Load Operation at Rated Power Condition
– Transient Response during Load Steps at Low Engine Speeds
Conclusion
© by VKA – all rights reserved. Confidential – no passing on to third parties
Impact of Friction Losses on Engine Modelling
Calculation of Thrust Load Based on 3-Cylinder GT-Power Model
Look-up table based on friction test bench results
20000
40000
60000
80000
100000
120000
140000
160000
180000
200000
220000
240000
260000
-60 -50 -40 -30 -20 -10 0 10 20 30 40 50 60
100100
100
300300
300
600600
600
2525
25
5050
50
150150
150
200200
200
400400 400
500500 500
700700 700
803748831
Thrust Load Fax / N
TC
Sp
ee
d n
TC / 1
/min
PF / W
p3 = f(° CA)
p2 = f(° CA)
Thrust Load Model
Fax = f(° CA)
Input for thrust
load model
p1 = f(° CA) p4 = f(° CA)
nTC = f(° CA)
TC Geometry Data Loss Coefficients
© by VKA – all rights reserved. Confidential – no passing on to third parties
-60
-40
-20
0
20
40
60
80
100
120
0 60 120 180 240 300 360 420 480 540 600 660 720
Th
rust L
oa
din
g F
ax
/ N
Crank Angle / ° CA
Thrust Loading During an Engine Cycle (neng = 5500 1/min WOT)
Maximum amplitude reaches ΔFax,max = 42 N
Thrust Load
Compressor
Turbine
Turbine+Compressor
© by VKA – all rights reserved. Confidential – no passing on to third parties
-60
-40
-20
0
20
40
60
80
100
120
0 60 120 180 240 300 360 420 480 540 600 660 720
Th
rust L
oa
din
g F
ax
/ N
Crank Angle / ° CA
Thrust Loading During an Engine Cycle (neng = 5500 1/min WOT)
Maximum amplitude reaches ΔFax,max = 42 N
Thrust Load
Compressor
Turbine
Turbine+Compressor
© by VKA – all rights reserved. Confidential – no passing on to third parties
-60
-40
-20
0
20
40
60
80
100
120
0 60 120 180 240 300 360 420 480 540 600 660 720
Th
rust L
oa
din
g F
ax
/ N
Crank Angle / ° CA
Thrust Loading During an Engine Cycle (neng = 5500 1/min WOT)
Maximum amplitude reaches ΔFax,max = 42 N
Thrust Load
Compressor
Turbine
Turbine+Compressor
ΔFax,max = 42 N Sign change before and after
each blow down phase
© by VKA – all rights reserved. Confidential – no passing on to third parties
Contribution of Friction Losses to Overall Compressor Power
Friction needs to be Considered in Part Load
Engine Speed
En
gin
e L
oa
d
0
20
40
60
80
100
Turbine Power BearingFriction
BearingFriction (Fax)
No
rmalized
Po
wer
/ %
5 %
0
20
40
60
80
100
Turbine Power BearingFriction
BearingFriction (Fax)
No
rma
lize
dP
ow
er
/ %
66 %
© by VKA – all rights reserved. Confidential – no passing on to third parties
Load Step 1500 rpm 2bar to WOT
Consideration of Thrust Load Leads to Slower Load Step
Normalized Time To Torque (TTT) Comment
14
. Both load steps start at the
same part load point
The WG has been closed before
and during the load step
Difference in response time only
caused by different friction
losses of the turbocharger
Load
t
0.8
0.9
1
1.1
1.2
1 2
no
rma
lize
d T
TT
PF = f(nTC) PF = f(nTC,Fax)
∼10 %
TTT
90 %
Increase TTT by 10 %
© by VKA – all rights reserved. Confidential – no passing on to third parties
Conclusion
© by VKA – all rights reserved. Confidential – no passing on to third parties
Motivation
Detailed Sub-Models enable Precise Modelling of Turbochargers
Extended turbine maps
0.00
0.10
0.20
0.30
0.40
0.50
0.60
0.70
0.80
1.0 1.2 1.4 1.6 1.8 2.0 2.2 2.4 2.6 2.8 3.0 3.2 3.4 3.6 3.8 4.0 4.2 4.4 4.6
Tu
rbin
e E
ffic
ien
cy e
ta_
T /
-.
Turbine Pressure Ratio p3t/p4 / - .isentr
oper
adia
bate
rT
urb
inenw
irkun
gsgra
d η
is,a
d,T
Turbinendruckverhältnis p3t/p4
ηT
πT
Turbocharger Heat Flux Model
CoolantOil
Environment
Turbine housingCompressor housing Centre housing
Shaft
Compressor
wheelTurbine
wheel
TC
mcp mcp mcp
mcp mcpmcp
Extended compressor map
mcorC
.1.00
1.40
1.80
2.20
2.60
3.00
3.40
3.80
4.20
0.00 0.02 0.04 0.06 0.08 0.10 0.12 0.14
Co
mp
ress
or
Pre
ssu
re R
atio
p 2
t/p1t
/ -
.
Corr. Compressor Mass Flow Rate m_dot_cor_C / kg/s .
πC
Bearing friction losses
Fax
© by VKA – all rights reserved. Confidential – no passing on to third parties
Main Influential Parameters on Bearing Friction
Thrust Load Difficult to Predict during TC Operation
-60 -40 -20 0 20 40 60Axialkraft / N
Axial Load Fax / N
pOil = 4 bar (abs.)
TOil = 90 °C
nTC = 120 000 1/min
nTC = 80 000 1/min
nTC = 40 000 1/min
40 60 80 100 120Öltemperatur / °C
Oil Inlet Temperature Toil / °C
pOil = 4 bar (abs.)
FAx = 0 N
nTC = 120 000 1/min
nTC = 80 000 1/min
nTC = 40 000 1/min
0
50
100
150
200
250
300
350
400
450
500
550
0 40000 80000 120000 160000
ATL Drehzahl / 1/min
pOil = 4 bar (abs.)
TOil = 90 °C
FAx = 0 N
TC Speed nTC / 1/min
TC
Be
ari
ng
Fri
ctio
n P
F/
W
© by VKA – all rights reserved. Confidential – no passing on to third parties
Overview of Axial Force Modelling
Model Validation using Strain Gage and Pressure Sensors
C,1mF
CS,F
CWheel,F
TWheel,F
TS,F
T,4mF
Tp4,FCp1,
F
2p
1p
3p
4p
BFC,p
BFT,p
Model has been calibrated using TC test bench data and works for
different temperature and pressure boundary conditions
© by VKA – all rights reserved. Confidential – no passing on to third parties
Contribution of Friction Losses to Overall Compressor Power
Friction needs to be Considered in Part Load
Engine speed
En
gin
e lo
ad
0
20
40
60
80
100
Turbine Power BearingFriction
BearingFriction (Fax)
Po
wer
/ %
0
20
40
60
80
100
Turbine Power BearingFriction
BearingFriction (Fax)
Po
wer
/ %
© by VKA – all rights reserved. Confidential – no passing on to third parties
Enhanced part load simulation accuracy
– Prediction of fuel consumption in driving cycles (GT-Drive)
– Set point for load step simulations
Design of TC thrust bearings
– One of the most frequent causes for TC failure
Definition of boundary conditions for TC bearing
simulations
Precise consideration of TC bearing losses for TC
efficiency calculation
Do we need thrust load modeling?
BM
EP
/ b
ar
0
4
8
12
16
20
Engine speed / 1/min
1000 2000 3000 4000
1.5 l TC DI WLTP
0.50
0.55
0.60
0.65
0.70
0.75
0.80
0.85
0.90
0.95
1.00
1.0 1.2 1.4 1.6 1.8 2.0 2.2 2.4 2.6 2.8 3.0 3.2 3.4
Tu
rbin
e E
ffic
ien
cy η
T/ -
.
Turbine Pressure Ratio p3t/p4 / - .
)hh(m
P)hqh(m
stis,4,tot3,T
Ftot1,Ctot2,Vadis,T,
Isentropic adiabatic efficiency
)hh(m
P)hh(m
stis,4,tot3,T
Ftot1,tot2,VisT,
Isentropic efficiency
)hh(m
)hh(m*
stis,4,tot3,T
tot1,tot2,VTCm,isT,
Net turbine efficiency
© by VKA – all rights reserved. Confidential – no passing on to third parties
Special thanks to AiF and FVV !
Thank you for your Attention !