Gas Bearings for Oil-Free Turbomachinery 29th Turbomachinery Consortium Meeting Dynamic Response of...
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Transcript of Gas Bearings for Oil-Free Turbomachinery 29th Turbomachinery Consortium Meeting Dynamic Response of...
Gas Bearings for Oil-Free Turbomachinery29th Turbomachinery Consortium Meeting
Dynamic Response of a Rotor-Air Bearing System due to Base
Induced Periodic Motions
TRC-B&C-1-09
2009 TRC Project
GAS BEARINGS FOR OIL-FREE TURBOMACHINERY
Yaying NiuYaying NiuResearch Assistant
Luis San AndrésLuis San AndrésMast-Childs ProfessorPrincipal Investigator
Start date: Oct 1st, 2008
Gas Bearings for Oil-Free TurbomachineryMicro Turbomachinery (< 0.5 MW)
• Compact and fewer parts• Portable and easily sized• High energy density• Lower pollutant emissions• Low operation cost
Advantages
http://www.hsturbo.de/en/produkte/turboverdichter.html
Turbo Compressor100 krpm, 10 kW
Micro Turbo500 krpm, 0.1~0.5 kW
http://www.hsturbo.de/en/produkte/micro-turbo.html
Oil-free turbocharger120 krpm, 110 kW
http://www.miti.cc/new_products.html
Gas Bearings for Oil-Free TurbomachineryGas Bearings for MTM
• Small friction and power losses• Less heat generation • Simple configuration • High rotating speed (DN value>4M)• Operate at extreme temperatures
Advantages
Gas Foil Bearing Flexure Pivot Bearing
Metal Mesh Foil Bearing
AIAA-2004-5720-984 GT 2004-53621
Issues• Small damping• Low load carrying capacity• Prone to instability
GT 2009-59315
Gas Bearings for Oil-Free Turbomachinery
Rotor motion amplitude increases largely. Subsynchronous amplitudes larger than synchronous. Excitation of system natural frequency. NOT a rotordynamic instability!
Gas Bearings for MTM
Ps=2.36 bar (ab)
GT 2009-59199
2008: Intermittent base shock load excitationsDrop induced shocks ~30 g. Full recovery within ~ 0.1
sec. Load cell
Pressurized air supply
Eddy current sensors
Alignment Bolt
Hitting rod
Test table
Load cell
Rubber pad
Accelerometer (A1)
Accelerometer (A2)
Plunger
Solenoid
RotorGas bearing
Hinged fixture
cmcm Plastic pad
Gas Bearings for Oil-Free Turbomachinery
• Set up an electromagnetic shaker under the base of test rig to deliver periodic load excitations
• Measure the rig acceleration and rotordynamic responses due to shaker induced excitations
• Model the rotor-air bearing system subject to base motions and compare the predictions to test results
2008-2009 Objectives
Evaluate the reliability of rotor-air bearing systems to withstanding base load excitations
Gas Bearings for Oil-Free Turbomachinery2009 Gas bearing test rig
Oscilloscope
Functiongenerator
Power amplifier
Test rig
Electromagnetic shakerTest table
Alignment bolts Rubber O-ringsEddy current
sensors
Trust pin
Imbalance plane
Infrared tachometer
Load cells
Test bearings Motor
Accelerometer
Support springs
Electromagnetic shaker
Test rig base
Air supply
Rotor
cm
The rod merely pushes on the base plate!
Rubber pad
Hingedfixture
Rotor
Bearing
y
x
Rotationdirection
10°
Coilspring (9 kN/m)
28 cm
Gas Bearings for Oil-Free Turbomachinery
Clearances ~42 m, Preload ~40%. Web rotational stiffness = 62 Nm/rad.Test rig tilts by 10°. NOT Load-on-Pad (LOP) !
Flexure Pivot Hybrid Bearings: Improved stability, no pivot wear.
Test rotor and gas bearings
45°
43° 72°
6.02.
0
33.2
62
.485
A
A
Rotation directionSection A-A
Load cells
Φ0.5 feed hole
Air supply
Flexure web
Pad
Y
X10°
Static Load
Eddy current sensor probe
Left bearing Right bearing
Vertical Vertical
Horizontal Horizontal
• 0.825 kg in weight• 190 mm in length• Location of sensors and bearings noted
Rotor
Gas bearing
Gas Bearings for Oil-Free TurbomachineryShaker delivered accelerations
-2
-1
0
1
2
3
0 0.1 0.2 0.3 0.4 0.5
Time [sec]
Acc
eler
atio
n [
g]
Acceleration
0.17 sec (6 Hz)
Excitation frequency: 6 Hz
0
0.05
0.1
0.15
0.2
0.25
0.3
0 200 400 600 800 1000
Frequency [Hz]
Acc
eler
atio
n [g
]
Acceleration
6 Hz
12 Hz
18 Hz624 Hz
51 Hz
Excited frequencies
Excitation frequency: 6 Hz
Rubber pad
Hingedfixture
Rotor
Bearing
y
x
Rotationdirection
10°
Coilspring (9 kN/m)
28 cm
Due to electric motor
Shaker transfers impacts to the rig base! Super harmonic frequencies are excited.
0
0.05
0.1
0.15
0.2
0.25
0.3
0 20 40 60 80 100
Frequency [Hz]
Acc
eler
atio
n [
g]
Acceleration
6 Hz12 Hz 18 Hz
51 Hz
Excited frequencies
Excitation frequency: 6 Hz
24 Hz
Rotor speed:
34 krpm (567 Hz)
Gas Bearings for Oil-Free TurbomachineryRotor speed coast down tests
0
5
10
15
20
25
0 5 10 15 20 25 30 35 40
Speed [krpm]
Am
pli
tud
e (p
k-p
k) [
μm
]
LV_2.36bar (ab)
LV_3.72bar (ab)
LV_5.08bar (ab)
192Hz (11.5krpm) @ 2.36bar
217Hz (13krpm) @ 3.72bar
250Hz (15krpm) @ 5.08bar
Frequency [Hz]
Am
plit
ud
e [m
m]
35krpm
2krpm
1X
2X
0.05
0.045
0.04
0.035
0.03
0.025
0.02
0.015
0.01
0.005
0
0 100 200 300 400 500 600 700 800 900 1000 1100 1200 1300 1400
30krpm
Left bearing
Rotor
Right bearing
LH RH
LV RV
Ps = 2.36 bar (ab)
Subsynchronous whirlingstarts beyond 30 krpm,fixed at system naturalfrequency 193 Hz
No base excitation
Slow roll compensatedSynchronous response
Rotor coasts down
from 35 krpm
No added imbalance
Pressure 2.36bar 3.72bar 5.08barNatural Freq 192Hz 217Hz 250Hz
Gas Bearings for Oil-Free TurbomachineryRotor speed coast down tests
2X
1X
Natural freq-193Hz
24Hz (2X12Hz-Excitation freq)
35krpm
2krpm
Frequency [Hz]
0 100 200 300 400 500 600 700 800 900 1000 1100 1200 1300 1400
Am
pli
tud
e [m
m]
0.05
0.045
0.04
0.035
0.03
0.025
0.02
0.015
0.01
0.005
0
0
5
10
15
20
0 100 200 300 400 500 600
Frequency [Hz]
Am
pli
tud
e [μ
m]
Amplitude_LV
Synchronous response
Natural frequency
212 Hz
Left bearing
Rotor
Right bearing
LH RH
LV RV
0
0.05
0.1
0.15
0.2
0.25
0.3
0 20 40 60 80 100
Frequency [Hz]
Acc
eler
atio
n [
g]
Acceleration
12 Hz 24 Hz 36 Hz
51 HzExcited frequencies
Excitation frequency: 12 Hz
48 Hz
Ps = 2.36 bar (ab)
Subsynchronous response:1) 24 Hz (Harmonic of 12 Hz)2) Natural frequency 193 Hz
Shaker input frequency: 12Hz
Synchronous Dominant! Excitation of system natural frequency does NOT mean instability!
Gas Bearings for Oil-Free Turbomachinery
Rotor response amplitude at the system naturalfrequency decreases, as the feed pressure increases.
Fixed speed, increasing pressures
0
0.01
0.02
0.03
0.04
0.05
0.06
0.07
0 100 200 300 400 500 600 700
Frequency [Hz]
Am
pli
tud
e [
mm
]
LV_2.36barLV_3.72barLV_5.08bar
Natural frequency
70~90Hz
Excitation frequency: 12Hz; Speed: 34krpm
Synchronousfrequency 567Hz(34 krpm)
Excitedfrequency and harmonics
2.36 bar
3.72 bar
5.08 bar
Left bearing
Rotor
Right bearing
LH RH
LV RV
PressureincreasesPressureincreases
Shaker input frequency: 12HzRotor speed: 34 krpm (567 Hz)
193Hz193Hz
215Hz215Hz
243Hz243Hz
12Hz, 24Hz, 36hz, etc12Hz, 24Hz, 36hz, etc
NOT due to base motion!NOT due to base motion!
Offset by0.01 mm
Gas Bearings for Oil-Free TurbomachineryFixed pressure, increasing speeds
0
0.01
0.02
0.03
0.04
0.05
0.06
0.07
0 100 200 300 400 500 600 700
Frequency [Hz]
Am
pli
tud
e [m
m]
LV_26krpm
LV_30krpm
LV_34krpm
567Hz (34krpm)
500Hz (30krpm)
433Hz (26krpm)
Excitation frequency: 12Hz; Feed pressure: 2.36bar (ab)
Natural frequency
70~90Hz
Excited frequencyand harmonics
26 krpm
30 krpm
34 krpm
Left bearing
Rotor
Right bearing
LH RH
LV RV
Rotor response amplitude at the system naturalfrequency increases, as the rotor speed increases.
SpeedincreasesSpeedincreases
Shaker input frequency: 12HzFeed pressure: 2.36 bar (ab)
180Hz180Hz
180Hz180Hz
193Hz193Hz
12Hz, 24Hz, 36hz, etc12Hz, 24Hz, 36hz, etc
Gas Bearings for Oil-Free TurbomachineryFixed speed and pressure, increasing input frequency
0
0.01
0.02
0.03
0.04
0.05
0.06
0.07
0 100 200 300 400 500 600 700
Frequency [Hz]
Am
pli
tud
e [m
m]
LV_W/O LV_5HzLV_6Hz LV_9HzLV_12Hz
Synchronousfrequency 567Hz(34 krpm)
Excited frequencyand harmonics
Feed pressure: 2.36bar (ab); Speed: 34krpm
Natural frequency
70~90 HzNo excitation
5Hz
6Hz
9Hz
12Hz
Left bearing
Rotor
Right bearing
LH RH
LV RV
Rotor response amplitude at the system naturalfrequency increases, as the input frequency increases.
FrequencyincreasesFrequencyincreases
Rotor speed: 34 krpm (567Hz)Feed pressure: 2.36 bar (ab)
193Hz193Hz
NOT due to base motion!NOT due to base motion!
Same excitation magnitude for 6, 9, and 12 Hz
Gas Bearings for Oil-Free Turbomachinery
Prediction uses synchronous speed bearing force coefficients. In actuality, gas bearing force coefficients are frequency dependent!
XLTRC2 prediction
Shaft1232015105
Shaft11
Left bearing support Right bearing support
Test rig base
LH
LV
RH
RV
Base motion
Rotor speed 26 krpm 30 krpm 34 krpm
Conical 202 Hz 212 Hz 222 Hz
Cylindrical 185 Hz 193 Hz 201 Hz
Rotor speed 26 krpm 30 krpm 34 krpm
Cylindrical 180 Hz 180 Hz 193 Hz
Natural freq=13,338cpm (222Hz)Damping ratio=0.044Rotor speed=34 krpm
Conical mode
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0 50 100 150 200 250 300
Frequency [Hz]
Acc
eler
atio
n [
m/s
2]
Input acceleration
201 Hz
60 Hz
48 Hz
36 Hz
24 Hz
12 Hz
222 Hz
XLTRC2
Measured
Left bearing
Rotor
Right bearing
LH RH
LV RV
FE rotor model
Conical
Cylindrical
System Natural Freq
Input accelerationin XLTRC2, simulateactual acceleration.
Shaker input frequency: 12HzFeed pressure: 2.36 bar (ab)
XLTiltPadHGB™
Gas Bearings for Oil-Free TurbomachineryXLTRC2 prediction
Left bearing
Rotor
Right bearing
LH RH
LV RV Shaker input frequency: 12HzFeed pressure: 2.36 bar (ab)Rotor speed: 34 krpm (567 Hz)
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0 50 100 150 200 250 300
Frequency [Hz]
Acc
eler
atio
n [
m/s
2]
Input acceleration
201 Hz
60 Hz
48 Hz
36 Hz
24 Hz
12 Hz
222 Hz
Input accelerationonly on VERTICAL direction
XLTRC2 predicts absolute rotor motions! Measured rotor response is relative to bearing housing.
Predicted natural frequencycomponent
Prediction frequency step:1.25 Hz.
0.01
0.1
1
10
100
1000
10 100 1000
Frequency [Hz]
Am
plit
ud
e [μ
m]
LV_34krpm_measurement_relative
LV_34krpm_XLTRC2 prediction_absolute
12Hz
24Hz
36Hz
48Hz
60Hz
201 & 222Hz
567Hz193Hz70~90Hz
Measured N.F. component
Gas Bearings for Oil-Free TurbomachineryRigid rotor model prediction
imb b bΜU GU CU KU = W F CU KU&& & & &
Rotor speed 26 krpm 30 krpm 34 krpm
Conical 191 Hz 200 Hz 208 Hz
Cylindrical 184 Hz 192 Hz 200 Hz
XLTRC2
Conical 202 Hz 212 Hz 222 Hz
Cylindrical 185 Hz 193 Hz 201 Hz
Measured
Cylindrical 180 Hz 180 Hz 193 Hz
Rigid rotor model
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0 50 100 150 200 250 300
Frequency [Hz]
Acc
eler
atio
n [
m/s
2]
Input acceleration
200 Hz
60 Hz
48 Hz
36 Hz
24 Hz
12 Hz
209 Hz
Left bearing
Rotor
Right bearing
LH RH
LV RV
System response equals to the superposition of unique single frequency responses.
System Natural Frequency:
Input acceleration in rigid rotor model, VERTICAL direction only!
Equations of Motion:Equations of Motion:
12 i i
Z K Μ G C F
Shaker input frequency: 12HzFeed pressure: 2.36 bar (ab)
Steady-State!
Absolute rotor response
r bZ Z U Relative rotor response
Rotor 1st bending mode: 1,917 Hz (115 krpm)
Gas Bearings for Oil-Free Turbomachinery
Rigid rotor model predicts relative rotor motions! The test rotor-bearing system shows good isolation.
Rigid rotor model prediction
Left bearing
Rotor
Right bearing
LH RH
LV RV Shaker input frequency: 12HzFeed pressure: 2.36 bar (ab)Rotor speed: 34 krpm (567 Hz)
Relative rotor motion
Predicted natural frequencycomponent
Above the natural frequency,the system is isolated!Above the natural frequency,the system is isolated!
0.01
0.1
1
10
100
1000
10 100 1000
Frequency [Hz]
Am
plit
ud
e [μ
m]
LV_34krpm_code prediction_relative
LV_34krpm_measurement_relative
12Hz
24Hz36Hz
48Hz
60Hz
200 & 208Hz
567Hz193Hz70~90Hz
Measured N.F. component
0
0.1
0.2
0.3
0.4
0.5
0.6
0.7
0.8
0 50 100 150 200 250 300
Frequency [Hz]
Acc
eler
atio
n [
m/s
2]
Input acceleration
200 Hz
60 Hz
48 Hz
36 Hz
24 Hz
12 Hz
209 Hz
Gas Bearings for Oil-Free Turbomachinery
• The recorded rotor response contains the main input frequency (5-12 Hz) and its super harmonics, and the rotor-bearing system natural frequency.
• The motion amplitudes at the natural frequency are smaller than the components synchronous with rotor speed.
• The rotor motion amplitude at the system natural frequency increases as the gas bearing feed pressure (5.08~2.36bar) decreases, as the rotor speed (26~34krpm) increases, and as the shaker input frequency (5~12 Hz) increases.
• Predicted rotor motion responses obtained from XLTRC2® and an analytical rigid rotor model show good correlation with the measurements. The system shows reliable isolation.
Conclusions
Reliability of rotor-air bearing system to withstanding base load excitations demonstrated