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Aerodynamic Performance of a Compact, High Work-Factor Centrifugal Compressor
at the Stage and Subcomponent LevelEdward P. Braunscheidel & Gerard E. Welch - NASA Glenn Research Center
Gary J. Skoch – Army Research LaboratoryGorazd Medic and Om P. Sharma – United Technologies Research Center
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50th AIAA/ASME/SAE/ASEE Joint Propulsion ConferenceJuly 28-30, 2014, Cleveland, OH
https://ntrs.nasa.gov/search.jsp?R=20140017398 2020-04-04T01:15:51+00:00Z
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Aerodynamic Performance of a Compact, High Work-FactorCentrifugal Compressor at the Stage and Subcomponent Level
• Background and Scope• Test Article and Facility Description• Key Instrumentation• Stage and Subcomponent Results• Performance Assessment vs. Pre-test CFD• Summary
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Background and Scope
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• NASA/UTRC High Efficiency Centrifugal Compressor (HECC) NRA cost-share contract– Develop HPC technologies for
advanced turboshaft engines for rotorcraft
– Challenging goal set for centrifugal compressors
– Maintain similitude between engine scale and rig scale hardware
– Design/Analysis, fab, assembly, test
Metric Intent (rig scale,2x engine scale) CFD*
Exit-corr. flow 2.1 < �c,ex < 3.1 lbm/s 2.98
Work factor 0.60 < �H0/U22 < 0.75 0.7905
�p,tt (poly) � 0.88 0.888
Diam. ratio Dmax / D2 � 1.45 1.45
Design SM 13% 12%
Mex 0.15 0.15
�ex 15� 14�
*Medic, G., et al., “High Efficiency Centrifugal Compressor for Rotorcraft Applications,” NASA/CR—2014-218114, Sept., 2014.
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HECC Stage OverviewDesign speed = 21,789 ft/s (Exit tip speed = 1615 ft/s)
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– Impeller: 15 blade/splitter pairs, spanwise varying backsweep, lean, elliptical leading and trailing edges
– Diffuser: 20 vane/splitter pairs, with splitters offset to maximize pressure recovery– EGVs: 60 cascade-style airfoils
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Small Engine Component Test Facility (CE-18)
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• 6000 hp / 60,000 rpm / 30:1 PR / Max 20� diameter • Inlet pressures 2-45 psia / Inlet air -20 ºF to ambient• Inlet flow 60 lbm/s / Exhaust to ambient or 26 in-hg
Air supply
Air Exhaust
Inlet Fine Control Valve
Plenum (Station 0, Inlet Reference)
Mass Flow Orifice
Test articleInlet Coarse Control Valve
Gearbox
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Tip Clearance System
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��/b of 0.5%, � 0.12 pt. impact on �tt
Impeller Translates Axially
Tip Clearance Variations @ Nc = 100%
• 4 rub probes at each station used for tip clearance calibration/alignment
• �/b = 2% (0.012�) design tip clearance, no step in flowpath at impeller/diffuser interface
0.0094
0.0111
0.0095
0.0118
0.00900.00960.0127
0.0092
Impeller�TEImpeller�LE
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Diffuser LE and “Rake” Instrumentation
• Vane Leading Edge (2.4)– Two vanes with 7 Kiel head p0 ports – Key measurements for impeller and
diffuser performance
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• Vane Trailing Edge (2.7)– 6 locations resolve one main-to-
main diffuser passage– Miniature Cobras at immersions
of 15-85%, calibrated for � and p0
Passage�APassage�B
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Surveys3-Port Cobra Probe
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• Vaneless Space (2.2) & Diffuser Exit (2.7)– Traversable spanwise, manually aligned to
flow– Calibrated to M=0.84 (Cal. Facility limit)
Station 2.2
Station 2.7
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EGV Exit/Stage Rating (Station 3)• 12 Rakes indexed to resolve one main-to-main diffuser pitch• Kiel head p0 and T0 ports on area centroids
• 3 adjacent EGVs have LE Kiel head p0 (25-75% span)
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po x3
To�x2
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Stage and Subcomponent Results
• Compressor Maps• Design point performance - comparison of measured vs. predicted• Representative subcomponent measurements at Nc = 100%
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Stage Pressure Ratio vs. Inlet Corrected Mass Flow Rate
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1.5
2.0
2.5
3.0
3.5
4.0
4.5
5.0
5.5
4 5 6 7 8 9 10 11 12 13
Total�Pressure�Ra
tio,�p
0,3.0/p 0
,0
Inlet�Corrected�Mass�Flow�Rate,�lbm/s
Stall�Boundary
3.0�lbm/s�op�line
Design Point
105%
100%
95%
90%85%
75%70%
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0.6
0.65
0.7
0.75
0.8
0.85
0.9
0.95
4.0 5.0 6.0 7.0 8.0 9.0 10.0 11.0 12.0 13.0
Efficiency,�%�
Inlet�Corrected�Mass�Flow�Rate,��lbm/s
Design Intent
Adiabatic
Polytropic
105%100%95%90%85%75%70%
Efficiency vs. Inlet Corrected Mass Flow Rate
12
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Metric Design�GoalRig�Scale�
Design�Intent�p0,0=14.7�psia
Rig�Scale��Design�Intent�
p0,0=11�psia
Measuredp0,0=11�psia
Uncertainty�(95%�Confidence)
Pressure�ratio,�������������������p0,3/p0,0 4.85 4.80 4.68�± 0.0074
Inlet�flow�rate,��������������c,in ,�lbm/s 11.2 11.1 10.85�± 0.1
Exit flow�rate,���������������c,ex ,�lbm/s 2.1�<��c,ex <�3.1 2.98 2.98 2.98
Adiabatic�efficiency�, �tt ,���% 0.862 0.8495 0.822�± 0.011
Polytropic efficiency, �p,tt ,�% > 0.88 0.888 0.879 0.855
Adiabatic,�total�pressure�to�static�pressure,�������������������������������ts , %
0.852 0.8396 0.805
Exit�Mach�number,������������Mex 0.15 0.15 0.15 0.18
Exit�flow�angle,������������������ex ,�deg 15o 14o 14o 34.3o
Stability�Margin,����������������SM,���% 13 12 12 7.5
Work factor 0.60�<��H0/U22 <�0.75 0.7905 0.793 0.81
Diameter�ratio Dmax/D2 < 1.45 1.45 1.45 1.45
Measured vs. Predicted Performance(Nc = 100%, �c,ex = 3.0 lbm/s, design tip clearance)
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Impeller Exit (2.2) and Diffuser Vane LE (2.4)(Nc = 100%, �c,ex = 3.0 lbm/s)
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0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.9
1
50 60 70 80 90 100
Fractio
n�of�sp
an�from
�hub
Swirl�angle��2.2,�deg.
100% Nc
Probe�at�2.2
Pre�test�CFD
• Measured swirl angle in relatively good agreement
• Vane to vane agreement very good• Vane LE and CFD in good agreement• Probe p0 (at 2.2) lower than vane LE, probe does not
adequately resolve the pressure flow field • Probe (2.2 vaneless space) data only used qualitatively
ur
u�
�u
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0.9
1
3 3.5 4 4.5 5 5.5 6
Fractio
n�of�sp
an�from
�hub
Local�p0,2.2(z)/p0,0
100% Nc
Probe�at�2.2
Vane�LE�
Pre�test�CFD
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Diffuser Exit Probe Survey Data (2.7)(Nc = 100%, �c,ex = 3.0 lbm/s)
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�
B
p0,2.7/p0,0
Flow�Angle,�Deg.
SS���PSsplitter
SS��PSmain
PSmain
SS���PSsplitter
SS���PSmain
%�Span�Hub�to�Tip
%�Pitch,�Main�to�Main
%�Span�Hub�to�Tip
A
TE�Mean�Camber�AngleMain�=�51�degSplitter�=�52�deg
0%
100% 200%
100%
0%
ur
u�
�u
AB
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Diffuser Exit Survey Results vs. Operating Condition (Nc = 100%, Choke, Design, Near-Stall)
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• Flow redistributes as stage is throttled• High swirl angles at SS main vane could indicate
separated flow
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Pressure Contours at Stations 2.7, 2.8, 3.0(Nc = 100%, �c,ex = 3.0 lbm/s)
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po,x/po,0
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Diffuser Vanes Loading Diagrams-Shroud Static Pressures (Nc=100, near design point CFD)
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2.5
3
3.5
4
4.5
5
Normalize
d�static�pressure,�p/p
0,0
1.5
2
2.5
3
3.5
4
4.5
5
8.5 9 9.5 10 10.5 11 11.5
Normalize
d�static�pressure,�p/p
0,0
Radius,�in.
Pressure�side���pre�test�CFDSuction�side���pre�test�CFDPressure�side���dataSuction�side���data
AB
SS Main
PS Main
PS Splitter
SS Splitter
• Overall pressure rise lower than predicted• Negative loading on splitter indicates
operating at large negative incidence vs. lightly loaded design intent
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60
65
70
75
80
85
90
95
10 10.5 11 11.5 12 12.5
Impe
ller�a
nd�stage�efficiency,�%
Inlet�corrected�flow,�lbm/s
Impeller�(Sta.�0�to�2.4)Stage�(Sta.�0�to�3)Impeller���pre�test�CFDStage���pre�test�CFD
Stage and Impeller Adiabatic Efficiency
19
100% Nc
Impeller CFD
Stage CFD
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Diffusion System Static Pressure Rise
20
�0.1
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
10 10.5 11 11.5 12
Static�pressure�rise�coefficient
Inlet�corrected�flow,�lbm/s
Diffuser90�deg.�bend�+�EGVDiffuser�+�90�deg.�bend�+�EGV
100% Nc
Design�intent�(�c,ex =�3�lbm/s)
Stall
Choke
• Static pressure rise increases from choke to stall (Diffuser and Diffuser+Bend+EGV)
• Static pressure rise across 90� bend and EGV is relatively constant
� � inininexp ppppc � ,0/
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Diffuser Loss Bucket
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0
5
10
15
20
25
30
35
10 10.5 11 11.5 12 12.5
�p 0/p
0of�diffuser,�%
Inlet�corrected�flow,�lbm/s
Design�intent�(�c,ex =�3�lbm/s)
100% Nc
Expt.stall�boundary
Data
CFD
Test results show a minimum loss at a lower flow rate than design intent
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Diffuser Corrected Flow Characteristic
22
2
2.2
2.4
2.6
2.8
3
3.2
2 2.5 3 3.5 4
Impe
ller�e
xit�corrected
�flow
,�lb m
/s
Stage�exit�corrected,�lbm/s
NASA�HECC�12�mil���coarse�grid���mixing�planeNASA�HECC�12�mil���fine�grid���mixing�planeHECC�test�data
Design�intent�100% Nc
Diffuser processes flow as per design intent @ �c,ex=3.0 lbm/s
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Impeller Corrected Flow Characteristic
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2
2.2
2.4
2.6
2.8
3
3.2
10 10.5 11 11.5 12 12.5
Impe
ller�e
xit�corrected
�flow
,�lb m
/s
Stage�(impeller)�inlet�corrected�flow,�lbm/s
Data CFD
Design�intent�(�c,ex =�3�lbm/s)
100% Nc
• Impeller is operating at a lower �c,in at the design intent impeller exit correct flow rate
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Summary
• Aerodynamic performance of an advanced, compact, high work-factor centrifugal compressor stage was presented
• Stage performance and stability were lower than design intent– Adiabatic Efficiency by 2.75 pts., mass flow by 2.25%, and
Stability Margin by 4.5 pts. • Differences in predicted and measured impeller efficiency,
impeller flow characteristics, and diffuser loss buckets were observed.
• Root-cause-analysis of the performance shortfall was initiated within the NRA contract. Analyses continue with intent to guide future design efforts.
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Comprehensive data sets and geometry to be made publically available
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Acknowledgements
Drs. Joo JongwookLarry HardinDuane McCormickWilliam CousinsBrian HolleyPaul Van SlootenElizabeth LurieAamir Shabbir
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Dr. Michael HathawayMark StevensJonathon MitchelJozsef PuskasAdam ReddingDavid HayduRichard Senyitko
Design Review Team