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Unsteady Flow in a Turbocharger CompressorSimulation vs. Experiment
Hans-Peter Dickmann, ABB Turbo Systems Ltd, Baden, Switzerland
Presented at the NUMECA German User Meeting, Lauf an der Pegnitz, Germany, October 21-22, 2014
Abstract
© ABB GroupNovember 14, 2014 | Slide 2
The here presented work can be regarded as a “prelude” of an extensive Fluid Structure Interaction (FSI) investigation
because it describes the computational fluid dynamics (CFD) part of a unidirectional FSI chain (consisting of fluid
mechanics and structural mechanics in series) only. The compressor is equipped with 5 circumferentially uneven
distributed struts upstream of the impeller. This configuration was chosen to excite a certain engine order of the impeller
main blades on purpose. As a means to evaluate the quality of the CFD data many steady and unsteady static pressure
measurements have been done along the casing contour above the rotating impeller. These measured data were
compared to time-averaged and unsteady results of the CFD simulations for 3 operating points (OPs). These 3 OPs
consist of 2 charged states with high and low inlet temperature and 1 atmospheric inlet state with high inlet temperature
for the high pressure component of a 2 stage turbocharger compressor. The agreement between measured and
simulated data is very good. Power generated by every single of 8 main blades during one revolution is compared for all
operating points with respect to size and shape. Videos per OP show the overall flow through the entire compressor,
state a non-reflecting inlet with respect to upstream traveling pressure waves generated by the impeller and document
the disturbed flow structure generated by the “excitation struts” in front of the impeller. The project team is still busy with
the 2nd part of the FSI chain (Forced Response Analyses). Improving the reliability of FSI simulations for compressor
blade vibrations will increase the comprehension of the FSI processes themselves (origins and impacts) and should
reduce the number of iterations on the path to a final compressor design.
Outline
1 Typical Applications of ABB Turbochargers
2 Compressor and Compressor Map
3 Flow Measurement Setup and CFD Simulation Setup
4 Results and Comparison «Simulation vs. Experiment»
5 Outlook
6 Conclusions
© ABB GroupNovember 14, 2014 | Slide 3
1 Typical Applications for ABB Turbochargers
© ABB GroupNovember 14, 2014 | Slide 4
2.1 Compressor and Compressor Map
© ABB GroupNovember 14, 2014 | Slide 5
Compressor Applicationq High pressure compressor of a 2 stage turbocharging system
q Run on 2 stage test facility with atmospheric and charged inlet conditions
Series Setupq Serial impeller with 8 pairs consisting of main blade and splitter blade
q Serial vaneless diffuser (à no influence of diffuser vanes)
q Serial volute
Non-Series Setup on Purposeq Axial inlet duct variant (to avoid secondary flows caused by radial inlet duct)
q 5 unevenly distributed struts in front of impeller for intentional excitation
q Inducer casing bleed system closed on purpose (to avoid its influence on flow)
2.2 Compressor and Compressor Map
© ABB GroupNovember 14, 2014 | Slide 6
Volume FlowT*=298K (Mass Flow)à
Tota
lPre
ssur
eR
atioà
ExperimentSimulation (time averaged)
charged, high T*IN
atmospheric, high T*IN
charged, low T*IN
LPC
HPC
Engine
LPT
HPTIdentical rpm,
but not
with respect to
T*IN=298K
© ABB GroupNovember 14, 2014 | Slide 7
Measured:
§ The usual thermodynamic data
§ Rotational speed
§ detailed pstatic (steady+unsteady)
§ Blade vibration (optically)
3.1 Experimental Setup and Simulation Setup
© ABB GroupNovember 14, 2014 | Slide 8
3.2 BCs & Interfaces / "Global Measurements "
Stator/Rotor-Interface:
«Inlet duct with struts ßà Impeller with diffuser»
Outlet BCs
Inlet BCs
Inlet pressure measurements
Outlet pressure measurements
Rotor-Stator-Interface
«Impeller+Diffuser ßà Volute»
«360° unsteady» simulation with 256 time steps per revolution
due to Nyquist criterion and later FFT analyses
© ABB GroupNovember 14, 2014 | Slide 9
3.3 "Local Measurements" along Impeller Casing Wall
(unsteady) Pressure
transducers (3)
LEMain Blade LESplitter Blade
Imp. Tip
(steady) Pressure
taps (11)+ extra taps in circumferential direction
Blade Vibration
optical sensors (2*8)
8 8
Charged - high T*IN
Pow
erN
orm
[-]
256 time steps = 1 revolution
Charged - low T*IN
Pow
erN
orm
[-]
256 time steps = 1 revolution
Atmospheric - high T*IN
Pow
erN
orm
[-]
256 time steps = 1 revolution
© ABB GroupNovember 14, 2014 | Slide 10
4.1 Main Blade Powers per Operating Point … in series
PowerNorm = single main blade power / average power of «Charged –low T*IN»
after 21 revs
after 21 revs
after 17 revs
atmospheric
charged
chargedP
ower
Nor
m[-]
256 time steps = 1 revolution
© ABB GroupNovember 14, 2014 | Slide 11
4.2 Main Blade Powers per OP … synchronized
PowerNorm = single main blade power / average power of «Charged –low T*IN»
Pow
erN
orm
[-]
after 17 revs
1 non-dimensional revolution
Charged - high T*IN
1 non-dimensional revolution
after 21 revs
Charged - low T*IN
1 non-dimensional revolution
after 21 revs
Atmospheric - high T*IN
43
51 2
T
© ABB GroupNovember 14, 2014 | Slide 12
4.3 Static Pressures along Impeller Casing Contour
Atmospheric - high T*IN
Rel. D = 0.2 – 7.0 %
Average Error = 1.9%
Charged - low T*IN
Rel. D = 0.5 – 7.6 %
Average Error = 5.0%
psN = static pressure / static pressure EXP-Tap 11
1 2 34
56
7
8
91011
Charged - high T*IN
Rel. D = 0.2 – 4.4 %
Average Error = 2.8%
© ABB GroupNovember 14, 2014 | Slide 13
4.4 Unsteady pstatic @ close to LEMain Blade
Experiment: average over 14 (15) revolutionsSimulation: just last revolutionDp = around time averaged value
Charged - high T*IN
Charged - low T*IN
Atmospheric - high T*IN
© ABB GroupNovember 14, 2014 | Slide 14
4.5 Unsteady pstatic @ close to LESplitter Blade
Experiment: average over 14 (15) revolutionsSimulation: just last revolutionDp = around time averaged value
Charged - high T*IN
Charged - low T*IN
Atmospheric - high T*IN
© ABB GroupNovember 14, 2014 | Slide 15
4.6 Unsteady pstatic @ close to ImpellerTip
Experiment: average over 14 (15) revolutionsSimulation: just last revolutionDp around time averaged value
Charged - high T*IN
Charged - low T*IN
Atmospheric - high T*IN
© ABB GroupNovember 14, 2014 | Slide 16
4.7 Unsteady Flow «Mach Number @ ½ Diffuser Width Cut»
Charged - low T*IN
Atmospheric - high T*IN Charged - high T*IN
© ABB GroupNovember 14, 2014 | Slide 17
4.8 Unsteady Flow «pstatic-fluctuations on 2 crossing planes»
Charged - low T*IN
Atmospheric - high T*IN
psNorm = Static Pressure / Inlet Total Pressure
Charged - high T*IN
© ABB GroupNovember 14, 2014 | Slide 18
4.9 Unsteady Flow «Streaklines @ 5 struts in front of impeller»
Charged - low T*IN
Atmospheric - high T*IN Charged - high T*IN
5 Outlook
© ABB GroupNovember 14, 2014 | Slide 19
q Comparison of computed Fluid Structure Interaction (FSI) data to experimental data:
Ø FFT (Fast Fourier Transformation) & forced response analysis of pstatic of main blade 1
Ø agreement of absolute maximum displacements Dsmax per OP? (a very ambitious goal)
Ø agreement of displacement ratios «Dsmax-OP / Dsmax-OP»? (would already be a great success)
q In case of good agreement only:
Ø rerun of operating points with the NLH module instead of «unsteady 360°»
Ø comparison of experimental vs. «unsteady 360°» vs. NLH (Nonlinear Harmonics Method)
q In case of good agreement only:
Ø increase the degree of complexity (+bypass, +diffuser vanes, +suction elbow)
Ø again comparison to unsteady pressure and blade vibration measurements
6 Conclusions
© ABB GroupNovember 14, 2014 | Slide 20
à Successful quality assessment of flow simulations prior to forced response analyses
q Static pressure rise along casing confirmed by experiment
q Unsteady pressure fluctuations confirmed by experiment
q No disturbance by reflections at compressor inlet
Acknowledgments
© ABB GroupNovember 14, 2014 | Slide 21
I appreciate the support of and a lot of fruitful interesting discussions on this project …
… and thank
q ABB Turbo Systems Ltd to publish this presentation,
q Raphael Brechbühler (student at ETH Zürich) for almost the entire preprocessing, many
runs, a lot of postprocessing and many valuable ideas concerning the project.
q … at the test facility for all those numerous and detailed measurements.
q … of the CFD Team and Compressor Design Team for all kinds of support.
q NUMECA Ingenieurbüro Altdorf for the support concerning NUMECA software.
q … of the application team for the installation of a very high number of probes.
q … of the Structural Mechanics Team for the FSI analyses preparation discussions.
My colleagues at ABB Turbo Systems Ltd …