introduction to basic vibration analysis - · pdf fileintroduction to basic vibration analysis...
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![Page 1: Introduction to Basic Vibration Analysis - · PDF fileIntroduction to Basic Vibration Analysis By: Jack D. Peters Connection Technology Center, Inc. 7939 Rae Boulevard. Victor, New](https://reader030.vdocument.in/reader030/viewer/2022021419/5aa786057f8b9ac5648c389b/html5/thumbnails/1.jpg)
Introduction to Basic Vibration
AnalysisBy: Jack D. Peters
Connection Technology Center, Inc7939 Rae Boulevard
Victor, New York 14564
www.ctconline.com
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Jack D. Peters - CTC 2
Eastman Kodak1976 –
2004
Senior Engineer for Vibration Monitoring of Photographic Film and Paper Manufacturing Machines world wide.
24/7 Permanent Monitoring using dynamic signal analyzers and proprietary statistical process control software generating quality alerts and alarms.
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Jack D. Peters - CTC 3
Vibration Institute
Category IV AnalystISO 18436-2InstructorPast Chairman CNY
www.cnyvi.com
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Jack D. Peters - CTC 4
Connection Technology Center
2004 –
Present
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Jack D. Peters - CTC 6
Data Collection
0.2G
rms
0
Magnitude
kHz2.53 Hz
Auto Pwr Spec 1
Portable
Route Based Permanent
Continuous On-line
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Jack D. Peters - CTC 7
Portable Data Collectors
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Jack D. Peters - CTC 8
Portable Data Collectors
Route BasedFrequency SpectrumTime WaveformOrbitsBalancingAlignment
Data AnalysisHistoryTrendingDownload to PCAlarms“Smart” algorithms
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Jack D. Peters - CTC 9
On-Line Systems (permanent)
Rack mounted systems with large numbers of channels.
24/7
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Jack D. Peters - CTC 10
Dynamic Signal Analyzers “Test & Measurement”
Large PC driven solutions with multiple channels and windows based software.
Smaller portable units with 2 – 4 channel inputs and firmware operating systems.
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Jack D. Peters - CTC 11
Tape Recorders “Insurance Policy”
Multi-channel digital audio tape recorders.
For the Measurement that can’t get away !
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Jack D. Peters - CTC 12
What’s This ?0.0002
inchPeak
0
Magnitude
Hz100 0 Hz
1
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Jack D. Peters - CTC 13
FFT, Frequency Spectrum, Power Spectrum
0.0002inch
Peak
0
Magnitude
Hz100 0 Hz
1
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Jack D. Peters - CTC 14
Scaling X & Y
0.0002inch
Peak
0
Magnitude
Hz100 0 Hz
1
X
Y
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Jack D. Peters - CTC 15
Scaling X & Y
0.0002inch
Peak
0
Magnitude
Hz100 0 Hz
1
FREQUENCY
A
M
P
L
I
T
U
D
E
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Jack D. Peters - CTC 16
Scaling X & Y
0.0002inch
Peak
0
Magnitude
Hz100 0 Hz
1
What is it
H o w
B a d
i s
i t
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Jack D. Peters - CTC 17
What’s That ?0.0004
inch
-0.0004
Real
s7.996094 0 s
1
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Jack D. Peters - CTC 18
Time Waveform0.0004
inch
-0.0004
Real
s7.996094 0 s
1
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Jack D. Peters - CTC 19
Scaling X & Y
X
Y
0.0004inch
-0.0004
Real
s7.996094 0 s
1
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Jack D. Peters - CTC 20
Scaling X & Y
TIME
A
M
P
L
I
T
U
D
E
0.0004inch
-0.0004
Real
s7.996094 0 s
1
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Jack D. Peters - CTC 21
0.0004inch
-0.0004
Real
s7.996094 0 s
1
Scaling X & Y
What is it
H o w
B a d
i s
i t
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Jack D. Peters - CTC 22
The X Scale
What is it ?
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Jack D. Peters - CTC 23
Single Frequency1V
rms
0
Magnitude
Hz100 0 Hz
Pwr Spec 1
1V
-1
Real
ms62.469480 s
Time 1
X:55 Hz Y:706.8129 mV
dX:18.18848 ms dY:2.449082 mVX:27.00806 ms Y:3.579427 mV
55 Hz
8.82 ms
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Jack D. Peters - CTC 24
Frequency & Time
fHz
= 1/tSec
tSec
= 1/fHz
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Jack D. Peters - CTC 25
Frequency & Time
If: F = 1/T and T = 1/F
Then: FT = 1
FT = 1
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Jack D. Peters - CTC 26
Concept !FT = 1
If: F increases
Then: t decreases
If: T increases
Then: f decreases
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Jack D. Peters - CTC 27
Single Frequency1V
rms
0
Magnitude
Hz100 0 Hz
Pwr Spec 1
1V
-1
Real
ms62.469480 s
Time 1
X:55 Hz Y:706.8129 mV
dX:18.18848 ms dY:2.449082 mVX:27.00806 ms Y:3.579427 mV
55 Hz
8.82 ms
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Jack D. Peters - CTC 28
Multiple Frequencies1
Hz100 0 Hz
Pwr Spec 1
1 Hz100 0 Hz
Pwr Spec 1
1 Hz100 0 Hz
Pwr Spec 1
1 Hz100 0 Hz
Pwr Spec 1
X:55 Hz Y:706.8129 mV
X:78 Hz Y:706.9236 mV
X:21 Hz Y:706.7825 mV
X:42 Hz Y:706.9266 mV
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Jack D. Peters - CTC 29
Multiple Time Waveforms
1V
ms62.469480 s
Time 78 1
1V
ms62.469480 s
Time 21 1
1V
ms62.469480 s
Time 42 1
1V
ms62.469480 s
Time 55 1
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Jack D. Peters - CTC 30
Real Life Time Waveform
4V
-4
Real
ms62.469480 s
TIME 1
55 + 78 + 21 + 42 = Trouble !
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Jack D. Peters - CTC 31
FFT Capabilities4V
-4
Real
ms62.469480 s
TIME 1
1V
rms Hz100 0 Hz
FREQUENCY 1X:78 Hz Y:706.9236 mVX:55 Hz Y:706.8129 mVX:42 Hz Y:706.9266 mVX:21 Hz Y:706.7825 mV
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Jack D. Peters - CTC 32
The Most Copied Slide in the History of Vibration Analysis !
Am
plitu
de
InputTime Frequency
Time Waveform Spectrum
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Jack D. Peters - CTC 33
Lines or Bins
0.0002inch
Peak
0
Magnitude
Hz100 0 Hz
1The FFT always has a defined number of lines or Bins.
100, 200, 400, 800, 1600, and 3200 lines are common choices.
This spectrum has 800 lines, or the X scale is broken down into 800 bins.
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Jack D. Peters - CTC 34
LRFThe Lowest Resolvable Frequency is determined by:
Frequency Span / Number of Analyzer Lines
The frequency span is calculated as the ending frequency minus the starting frequency.
The number of analyzer lines depends on the analyzer and how the operator has set it up.
Example: 0 - 400 Hz using 800 lines
Answer = (400 - 0) / 800 = 0.5 Hz / Line
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Jack D. Peters - CTC 35
Bandwidth
The Bandwidth can be defined by:
(Frequency Span / Analyzer Lines) Window Function
Uniform Window Function = 1.0
Hanning Window Function = 1.5
Flat Top Window Function = 3.8
Example: 0 - 400 Hz using 800 Lines & Hanning Window
Answer = (400 / 800) 1.5 = 0.75 Hz / Line
Note: More discussion later on window functions for the analyzer !
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Jack D. Peters - CTC 36
Resolution
The frequency resolution is defined in the following manner:
2 (Frequency Span / Analyzer Lines) Window Function
or
Resolution = 2 (Bandwidth)
Example: 0 - 400 Hz using 800 Lines & Hanning Window
Answer = 2 (400 / 800) 1.5 = 1.5 Hz / Line
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Jack D. Peters - CTC 37
Using Resolution
The student wishes to measure two frequency disturbances that are very close together.
Frequency #1 = 29.5 Hz.
Frequency #2 = 30 Hz.
The instructor suggests a hanning window and 800 lines.
What frequency span is required to accurately measure these two frequency disturbances ?
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Jack D. Peters - CTC 38
Using Resolution
Resolution = 30 - 29.5 = 0.5 Hz / Line
Resolution = 2 (Bandwidth)
BW = (Frequency Span / Analyzer Lines) Window Function
Resolution = 2 (Frequency Span / 800) 1.5
0.5 = 2 (Frequency Span / 800) 1.5
0.5 = 3 (Frequency Span) / 800
400 = 3 (Frequency Span)
133 Hz = Frequency Span
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Jack D. Peters - CTC 39
Data Sampling Time
Data sampling time is the amount of time required to take one record or sample of data. It is dependent on the frequency span and the number of analyzer lines being used.
TSample = Nlines / Fspan
Using 400 lines with a 800 Hz frequency span will require:
400 / 800 = 0.5 seconds
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Jack D. Peters - CTC 40
Average & OverlapAverage - OnOverlap Percent - 50%Overlap is the amount of old data that is used
TR#1 TR#2 TR#3FFT#1 FFT#2 FFT#3
TR#1
TR#2
TR#3FFT#1
FFT#2
FFT#3
0% Overlap
50% Overlap
How long will it take for 10 averages at 75% overlap using a 800 line analyzer and a 200 Hz frequency span?
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Jack D. Peters - CTC 41
75% Overlap ?10 Averages75% Overlap800 Lines200 Hz
Average #1 = 800 / 200
Average #1 = 4 seconds
Average #2 - #10 = (4 x 0.25)
Average #2 - #10 = 1 second each
Total time = 4 + (1 x 9)
Total time = 13 seconds
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Jack D. Peters - CTC 42
Filter WindowsWindow filters are applied to the time waveform data to simulate data that starts and stops at zero.They will cause errors in the time waveform and frequency spectrum.We still like window filters !
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Jack D. Peters - CTC 43
Window Comparisons
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Jack D. Peters - CTC 44
Filter WindowsHanning (Frequency)Flat Top (Amplitude)Uniform (No Window)Force Exponential
Force/Expo Set-up(Frequency Response)
Hanning 16% Amplitude Error
Flat Top 1% Amplitude Error
Window functions courtesy of Agilent “The Fundamentals of Signal Analysis”
Application Note AN 243
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Jack D. Peters - CTC 45
Filter WindowsUse the Hanning Window for normal vibration monitoring (Frequency)Use the Flat Top Window for calibration and accuracy (Amplitude)Use the Uniform Window for bump testing and resonance checks (No Window)
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Jack D. Peters - CTC 46
The Y Scale
How bad is it ?
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Jack D. Peters - CTC 47
Amplitude
Acceleration = g’s rms. or peak
Velocity = inch/s rms. or peak
Displacement = mils peak to peakNote: 1 mil = 0.001 inches
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Jack D. Peters - CTC 48
Pk-Pk (Peak - Peak)
1V
-1
Real
ms62.469480 s
Time 1
2V
Pk-Pk
0
Magnitude
Hz100 0 Hz
Pwr Spec 1
dX:9.094238 ms dY:1.994871 VX:22.43042 ms Y:-993.8563 mV
X:55 Hz Y:1.999169 V
The Peak - Peak value is expressed from the peak to peak amplitude.
The peak to peak value is measured in the time waveform.
Peak -
Peak. = 2 V
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Jack D. Peters - CTC 49
Pk (Peak)
1V
-1
Real
ms62.469480 s
Time 1
1V
Peak
0
Magnitude
Hz100 0 Hz
Pwr Spec 1
dX:4.516602 ms dY:997.4356 mVX:27.00806 ms Y:3.579427 mV
X:55 Hz Y:999.5843 mV
The time wave has not changed. The Peak value is expressed from zero to the largest positive or negative peak amplitude.
The peak value is measured in the time waveform.
Peak. = 1 V
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Jack D. Peters - CTC 50
RMS (Root Mean Square)
1V
rms
0
Magnitude
Hz100 0 Hz
Pwr Spec 1
1V
-1
Real
ms62.469480 s
Time 1
X:55 Hz Y:706.8129 mV
dX:2.288818 ms dY:709.1976 mVX:27.00806 ms Y:3.579427 mV
The time wave has not changed.
The rms. value is expressed from zero to 70.7% of the peak amplitude for a single frequency.
The rms. value is calculated for the spectrum.
rms. = 707 mV
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Jack D. Peters - CTC 51
Suffix Comparison
2V
rms
0
Magnitude
Hz100 0 Hz
Pwr Spec 1
2V
Peak
0
Magnitude
Hz100 0 Hz
Pwr Spec 1
2V
Pk-Pk
0
Magnitude
Hz100 0 Hz
Pwr Spec 1
1V
-1
Real
ms62.469480 s
Time 1
1V
-1
Real
ms62.469480 s
Time 1
1V
-1
Real
ms62.469480 s
Time 1
X:55 Hz Y:706.8129 mV
X:55 Hz Y:999.5843 mV
X:55 Hz Y:1.999169 V
dX:2.288818 ms dY:709.1976 mX:27.00806 ms Y:3.579427 mV
dX:4.516602 ms dY:997.4356 mX:27.00806 ms Y:3.579427 mV
dX:9.094238 ms dY:1.994871 VX:22.43042 ms Y:-993.8563 mV
RMS
Peak
Peak - Peak
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Jack D. Peters - CTC 52
Changing Suffixes
Many times it is necessary to change between suffixes.
Pk-Pk / 2 = Peak
Peak x 0.707 = RMS (Peak / 1.414 = RMS)
RMS / 0.707 = Peak (RMS x 1.414 = Peak)
Peak x 2 = Pk-Pk
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Jack D. Peters - CTC 53
Converting the Unit Suffix
Peak - Peak
RMS
÷ 2
x 0.707
x 2
÷ 0.707
PeakPeak
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Jack D. Peters - CTC 54
Engineering Units (EU)
Engineering units are used to give meaning to the amplitude of the measurement.
Instead of the default “volts”, it is possible to incorporate a unit proportional to volts that will have greater meaning to the user.
Examples: 100 mV / g 20 mV / Pa
1 V / in/s 200 mV / mil
50 mV / psi 10 mV / fpm
33 mV / % 10 mV / V
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Jack D. Peters - CTC 55
EU’s the Hard Way
Sometimes we forget to use EU’s, or just don’t understand how to set up the analyzer. The measurement is in volts!
There is no immediate need to panic if ????
You know what the EU is for the sensor you are using.
Example: An accelerometer outputs 100 mV / g and there is a 10 mV peak in the frequency spectrum.
What is the amplitude in g’s ?
Answer = 10 mV / 100 mV = 0.1 g
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Jack D. Peters - CTC 56
The Big Three EU’s
Acceleration
Velocity
Displacement
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Jack D. Peters - CTC 57
Converting the Big 3
In many cases we are confronted with Acceleration, Velocity, or Displacement, but are not happy with it.
Maybe we have taken the measurement in acceleration, but the model calls for displacement.
Maybe we have taken the data in displacement, but the manufacturer quoted the equipment specifications in velocity.
How do we change between these EU’s ?
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Jack D. Peters - CTC 58
Changing UnitsVelocity = 2π
f D
Acceleration = 2π
f V or (2π
f)2
D
f = frequency, cycles/sec or HzD = displacement, inches (mm)V = velocity, in./sec. (mm/sec)A = acceleration, in/sec2
(mm/sec2)
(divide by 386.1 in/sec2/g to obtain acceleration in g’s)(divide by 9807 mm/sec2/g to obtain acceleration in g’s)
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Jack D. Peters - CTC 59
386.1 What ?
1g = 32.2 feet/second2
32.2 feet 12 inchessecond2 X foot
386.1 inches/second2
g
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Jack D. Peters - CTC 60
Doing the Math Units0.5g x 386.1 inches
second2
g
2π x 25 cyclessecond
0.5g x 386.1 inches x 1 secondg second2 2π x 25 cycles
0.5 x 386.1 inches2π x 25 cycles second
cycle
1.23 inches/second
There is a 0.5 g vibration at 25 Hz.
What is the velocity ?
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Jack D. Peters - CTC 61
Radians, Degrees, or Time
00
900
1800
2700
3600
π 2
π
3π 2
2π
3600
= 2π
Radians
3600
/ 2π
Radians
57.3250
/ Radian0
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Jack D. Peters - CTC 62
Radians, Degrees, or Time
00
900
1800
2700
3600
π 2
π
3π 2
2π0
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Jack D. Peters - CTC 63
Radians, Degrees, or Time
00
900
1800
2700
3600
π 2
π
3π 2
2πPeriod (seconds/cycle)
0
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Jack D. Peters - CTC 64
Changing Units: Acceleration to Velocity
A f V= 2π
A V2πf
=
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Jack D. Peters - CTC 65
Changing Units: Velocity to Displacement
V f D= 2π
V D2πf
=
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Jack D. Peters - CTC 66
Converting the Unit Measure
Acceleration (g’s)
Velocity (inch/s)
Displacement (inch)
x 386.1
÷ 2(Pi)f
÷ 2(Pi)fx 2(Pi)f
x 2(Pi)f
÷ 386.1
Velocity (inch/s)
Acceleration (inch/s2)
Acceleration (inch/s2)
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Jack D. Peters - CTC 67
Converting the SI Unit Measure
Acceleration (g’s)
Velocity (mm/s)
Displacement (mm)
x 9807
÷ 2(Pi)f
÷ 2(Pi)fx 2(Pi)f
x 2(Pi)f
÷ 9807
Velocity (mm/s)
Acceleration (mm/s2)
Acceleration (mm/s2)
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Jack D. Peters - CTC 68
Acceleration - Velocity
Example: Find the equivalent peak velocity for a 25 Hz vibration at 7 mg RMS ?
= (g x 386.1) / (2 Pi x F)
= (0.007 x 386.1) / (6.28 x 25)
= 0.017 inches / second RMS
Answer = 0.017 x 1.414 = 0.024 inches / second Pk
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Jack D. Peters - CTC 69
Velocity - Displacement
Example: Find the equivalent pk-pk displacement for a 25 Hz vibration at 0.024 in/s Pk ?
= Velocity / (2 Pi x F)
= 0.024 / (6.28 x 25)
= 0.000153 inches Pk
Answer = 0.000153 x 2 = 0.000306 inches Pk-Pk
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Jack D. Peters - CTC 70
Acceleration -
Displacement
Example: Find the equivalent Pk-Pk displacement for a 52 Hz vibration at 15 mg RMS ?= (g x 386.1) / (2 Pi x F)2
= (0.015 x 386.1) / (6.28 x 52)2
= 0.000054 inches RMS
Answer = (0.000054 x 1.414) 2 = 0.000154 inches Pk-Pk
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Jack D. Peters - CTC 72
Sensors
Displacement
Frequency
Spee
d
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Jack D. Peters - CTC 74
AccelerometersIEPE
Electronics insideIndustrial
Charge ModeCharge AmplifierTest & Measurement
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Jack D. Peters - CTC 75
Industrial Requirements and Applications
RequirementsFunctionalityDurabilityAffordability
ApplicationsTrendingAlarmingDiagnostics
RememberOne sensor does not fit all applicationsFit, Form & Function
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Jack D. Peters - CTC 76
Accelerometer AdvantagesMeasures casing vibrationMeasures absolute motionCan integrate to Velocity outputEasy to mountLarge range of frequency responseAvailable in many configurations
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Jack D. Peters - CTC 77
Accelerometer DisadvantagesDoes not measure shaft vibrationSensitive to mounting techniques and surface conditionsDifficult to perform calibration checkDouble integration to displacement often causes low frequency noiseOne accelerometer does not fit all applications
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Jack D. Peters - CTC 78
Mass & Charge
Mass
Ceramic/Quartz
Post
Relative movement between post & mass creates shear in ceramic producing charge.
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Jack D. Peters - CTC 79
Accelerometer ParametersPerformance Suited for Application
Sensitivity (mV/g)Frequency ResponseDynamic Range
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Jack D. Peters - CTC 80
Typical Frequency Response
Frequency
Am
plitu
de
+/- 3dB
+/- 10%
Transmission RegionThe usable frequency range of the accelrometer
based on acceptable amplitude limits
AmplificationRegion
The natural frequency is excited causing gain around resonance
IsolationRegion
Phase between sensor & machine is shifted by 180
degrees and signal rolls off to zero
+/- 5%
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Jack D. Peters - CTC 81
Mounting the Accelerometer
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Jack D. Peters - CTC 82
Realistic MountingStud
Bees Wax
Adhesive
Magnet
Hand Held
100 1,000 10,000Frequency, Hz
In the real world, mounting might not be as good as the manufacturer had in the lab !
What about paint, rust, grease, oil, etc?
Vibration Institute, Basic Machinery Vibrations & Machinery Vibration Analysis
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Jack D. Peters - CTC 83
Sensitivity, Range & Application
Sensitivity Range Output Application
10 mV/g10 mV/g +/+/--
500 g500 g +/+/--
5 VAC5 VAC
50 mV/g +/-
100 g +/-
5 VAC
100 mV/g +/-
50 g +/-
5 VAC
500 mV/g +/-
10 g +/-
5 VAC
A 10 mV/g accelerometer will have a dynamic range of +/-
500 g’s, and a dynamic output of +/-
5 volts AC.
They are typically used for machinery that is generating high amplitude vibrations. With the large dynamic range, they are much less likely to become saturated as a result of the high amplitude vibrations.
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Jack D. Peters - CTC 84
Sensitivity, Range & Application
Sensitivity Range Output Application
10 mV/g10 mV/g +/+/--
500 g500 g +/+/--
5 VAC5 VAC
50 mV/g +/-
100 g +/-
5 VAC
100 mV/g +/-
50 g +/-
5 VAC
500 mV/g +/-
10 g +/-
5 VAC
A 50 mV/g accelerometer will have a dynamic range of +/-
100 g’s, and a dynamic output of +/-
5 volts AC.
They are typically used for general purpose machinery measurements, and are sometimes offered as standard sensors for data collectors.
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Jack D. Peters - CTC 85
Sensitivity, Range & Application
Sensitivity Range Output Application
10 mV/g10 mV/g +/+/--
500 g500 g +/+/--
5 VAC5 VAC
50 mV/g +/-
100 g +/-
5 VAC
100 mV/g +/-
50 g +/-
5 VAC
500 mV/g +/-
10 g +/-
5 VAC
A 100 mV/g accelerometer will have a dynamic range of +/-
50 g’s, and a dynamic output of +/-
5 volts AC.
Approximately 90% of all vibration analysis and data collection is accomplished with a 100 mV/g accelerometer.
Some sensors are also available with a +/-
80g dynamic range for measuring larger signal amplitudes.
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Jack D. Peters - CTC 86
Sensitivity, Range & Application
Sensitivity Range Output Application
10 mV/g10 mV/g +/+/--
500 g500 g +/+/--
5 VAC5 VAC
50 mV/g +/-
100 g +/-
5 VAC
100 mV/g +/-
50 g +/-
5 VAC
500 mV/g +/-
10 g +/-
5 VAC
A 500 mV/g accelerometer will have a dynamic range of +/-
10 g’s, and a dynamic output of +/-
5 volts AC.
This high output sensor is typically used for low speed equipment, low frequency measurements, and low amplitude analysis.
The high output provides a much better signal to noise ratio for low amplitude signals.
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Jack D. Peters - CTC 87
Mounting Location
Load Zone
Axial
Radial
Vertical
Horizontal
Vibration Institute, Basic Machinery Vibrations & Machinery Vibration Analysis
Axial
Horizontal
Vertical
Axial
Horizontal
Vertical
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Jack D. Peters - CTC 88
Mounting Location
Load Zone
Axial
Radial
Vertical
Horizontal
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Jack D. Peters - CTC 89
Accelerometer AlarmsMachine Condition
rms peak
Acceptance of new or repaired equipment < 0.08 < 0.16Unrestricted operation (normal) < 0.12 < 0.24Surveillance 0.12 - 0.28 0.24 - 0.7Unsuitable for Operation > 0.28 > 0.7
Velocity Limit
Note #1: The rms velocity (in/sec) is the band power or band energy calculated in the frequency spectrum.
Note #2: The peak velocity (in/sec) is the largest positive or negative peak measured in the time waveform.
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Jack D. Peters - CTC 91
Velocity SensorsSelf Generating – no power supply requiredMagnet inside coil generates velocity proportional to vibrationSpring mass system10 Hz. to 1000 Hz.Phase changeDirectional mountingLarge & Heavy500 mV/inch/sec
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Jack D. Peters - CTC 92
PiezoVelocity SensorsRemember everything that you just learned about an accelerometerThe output of the accelerometer has been integrated to velocity100 mV/inch/sec
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Jack D. Peters - CTC 94
Proximity Probes, Cables, & Drivers
Overview
Technical Background
Technical Specifications
Applications
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Jack D. Peters - CTC 95
5 Meter & 9 Meter Systems
Typical lengths: 0.5 and 1.0 meters
Proximity Probe
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Jack D. Peters - CTC 96
5 Meter & 9 Meter Systems
Probe Length + Extension Cable Length
must equal 5 or 9 meters in system length
Extension Cable
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Jack D. Peters - CTC 97
5 Meter & 9 Meter Systems
Electronics tuned for 5 or 9 meter systems
Driver
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Jack D. Peters - CTC 98
Application
Measure Displacement Vibration in plain bearing applications
Non Contact sensing of the shaft
Ideal for measuring:Shaft vibrationShaft centerline positionShaft axial position (Thrust Bearing)Rod dropSpeed (key phaser)
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Jack D. Peters - CTC 99
Common Applications
CompressorsSteam Turbines PumpsFansBlowersGeneratorsGear Boxes
Plain Bearings Journal BearingsFluid Film BearingsBabbitt BearingsSleeve BearingsTilting Pad BearingsRecip’s (cross head)
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Jack D. Peters - CTC 100
Displacement Probes - Advantages
Non-contactMeasure relative shaft vibrationMeasure shaft centerline position (DC gap)Measure axial position (Thrust)Flat frequency response dc – 10KHzSimple calibrationSuitable for harsh environments
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Jack D. Peters - CTC 101
Displacement Probes - Disadvantages
Probe can move (vibrate)Doesn’t work on all metalsPlated shafts may give false measurementMeasurement is affected by scratches & tool marks in shaftAvailable system lengths (probe, cable & driver) 5 meter or 9 meter are standardMust have relief at sensing tip from surrounding metal (counter bore)
Plated shaft is round, but core material is not..
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Jack D. Peters - CTC 102
Technical Background
Driver
Target
Cable
Probe
• The tip of the probe emits a radio frequency signal into the surrounding area as a magnetic field
• As a conductive target intercepts the magnetic field, eddy currents are generated on the surface of the target, and power is drained from the radio frequency signal
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Jack D. Peters - CTC 103
Technical Background
Driver
Target
Cable
Probe
• Power varies with target movement in the radio frequency field creating a variation in the output voltage of the driver
-
A small DC voltage indicates that the target is close to the probe tip
-
A large DC voltage indicates that the target is far away from the probe tip
-
The variation of DC voltage is the AC dynamic signal indicating the vibration (displacement)
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Jack D. Peters - CTC 104
Driver
Typical non-contact displacement sensor for measuring shaft vibration on a sleeve or journal bearing.
Eddy Currents
Shaft
Journal/Sleeve
Cable
ProbeSensitivity 200 mV/mil
(8 V/mm)
Dynamic Range 10 – 90 mils(.25 – 2.3 mm)
Frequency Response DC – 10 kHz
Sensitivity, Range, Response
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Jack D. Peters - CTC 105
LinearityGap Gap Outputmils mm VDC10 0.25 -2.0120 0.51 -3.9730 0.76 -5.9040 1.02 -7.8850 1.27 -9.8760 1.52 -11.8070 1.78 -13.8080 2.03 -15.6990 2.29 -17.66100 2.54 -19.58
200 mV/mil x 50 mils =
-10.00 VDC
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Jack D. Peters - CTC 106
Materials & Output Values
Typical200 mv/mil (8 V/mm)
Depends on probe, cable (length), and driver.Target material varies output.
Calibration ExamplesCopper 380 mV/milAluminum 370 mV/milBrass 330 mV/milTungsten Carbide 290 mV/milStainless Steel 250 mV/milSteel 4140, 4340 200 mV/mil
Based on typical output sensitivity of 200 mV/mil. (8 V/mm)
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Jack D. Peters - CTC 107
It’s a Harsh World Out There!
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Jack D. Peters - CTC 108
Driver to Driven
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Jack D. Peters - CTC 109
API Standard 670 (Typical Information)
American Petroleum Institute
4th
Edition, December 01, 2000
www.techstreet.com
$168.00 USD/Copy
Industry Standard for Proximity Probes
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Jack D. Peters - CTC 110
Vertical (Y) Horizontal (X)
Probe orientation based on facing Driver to Driven
Gap
Shaft
Journal/Sleeve
Technical Background
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Jack D. Peters - CTC 111
DC Gap with Dynamic AC
DC Gap
A negative voltage level proportional to the gap spacing
Dynamic AC
Varying DC voltage simulates dynamic AC voltage for vibration output
30 mV/(200 mV/mil) = 0.15 mil’s p-p
-9.75V
-10.25
Real
ms79.960920 s
Time Record 1
≈
-10.00
VDC
Gap
30 mV p-p VAC
Dynamic
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Jack D. Peters - CTC 112
Looking at Orbits with a Scope
Vertical for Amplitude
Y
Horizontal for Time Base
X
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Jack D. Peters - CTC 113
The Orbit Display
Y
X
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Jack D. Peters - CTC 114
Rolling the Scope
Machine Vertical
Machine Horizontal
YX
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Jack D. Peters - CTC 115
Modern Instrumentation & Orbits
Modern instrumentation can compensate for the location of the X and Y probes providing a true machine vertical and horizontal measurement.
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Jack D. Peters - CTC 116
Proximity Probe AlarmsMachine Condition
< 3,600 RPM < 10,000 RPM
Normal 0.3 0.2Surveillance 0.3 - 0.5 0.2 - 0.4Planned Shutdown 0.5 0.4Unsuitable for Operation 0.7 0.6
Allowable R/C
Note #1: R is the relative displacement of the shaft measured by either probe in mils peak-peak.
Note #2: C is the diametrical clearance (difference between shaft OD and journal ID) measured in mils.
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Jack D. Peters - CTC 117
Vertical (Y) Horizontal (X)
Absolute Shaft Displacement
Velocity1.
Measure the vertical shaft displacement.
2.
Measure the vertical casing velocity.
3.
Include phase
Vertical Measures
D = 2.85 milsp-p @1650
V = 0.24 IPSpk
@ 2110
3600 RPM
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Jack D. Peters - CTC 118
Graphical Addition
Vertical Measures
D = 2.85 milsp-p @1650
V = 0.24 IPSp
@ 2110
Velocity leads displacement by 900
2110
- 900
= 1210
Dp-p
= 2[0.24/(2πf)]
Dp-p
= 2[0.24/(6.28x60)]
D = 1.27 milsp-p
@ 1210
900
001800
2700
1.27 milsp-p
@ 1210
2.85 milsp-p
@ 1650
3.86 milsp-p
@ 1520
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Jack D. Peters - CTC 119
Mathematical Addition
D = 2.85 milsp-p @1650
D = 1.27 milsp-p
@ 1210
y = 2.85 milsp-p
x sin 1650
y = 0.74 milsp-p
y = 1.27 milsp-p
x sin 1210
y = 1.09 mils p-p
y = 0.74 + 1.09 = 1.83 milsp-p
x = 2.85 milsp-p
x cos 1650
x = -2.75 milsp-p
x = 1.27 milsp-p
x cos 1210
x = -0.65 milsp-p
x = -
2.75 + -
0.65 = -
3.40 milsp-p
900
001800
1.83 milsp-p
-3.4 milsp-p
3.86 milsp-p
@ 1520
D = y2
+ x2
D = 1.832
+ (-3.40)2
D = 3.86 milsp-p
900
+ acos
1.83/3.86
900
+ 620
= 1520
2700
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Jack D. Peters - CTC 120
Shaft Centerline
On Centers
Bore Dia.
Shaft Dia.
Zero RPM
CCW Rotation
CW Rotation
Diametrical Clearance
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Jack D. Peters - CTC 121
Shaft Centerline @ Zero RPM
Diametrical Clearance = 8 mils
Dia. Clr. / 2 = Radial Clr. = 4 mils
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Jack D. Peters - CTC 122
Plotting Shaft Position Change
At Running Speed
CCW Rotation
Y = -1 mil
X = +2 mils
Shaft Change = 2.24 mils @ 71.60
0 Y -450 X +450
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Jack D. Peters - CTC 123
Attitude Angle & Eccentricity Ratio
Shaft Attitude Angle
320
Typical 200
to 500
Eccentricity Ratio =
3.85 mils/ 4.0 mils = .96
Typical >.7 < 1.0
0 = On Centers
1 = Contact
Rad Clr 4 mils
Y -450 X +450
320
3.85
mils
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Jack D. Peters - CTC 124
Axial Shaft Position (Thrust)
Shaft Two axial oriented probes are used for redundancy to monitor the axial movement of the shaft or thrust collar.
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Jack D. Peters - CTC 126
Natural FrequencyA result of the Mass (m) and Stiffness (k) of the machine designResonance occurs when a natural frequency is excited by a forceCritical speed occurs when the machine speed matches the natural frequency and creates resonance
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Jack D. Peters - CTC 127
Natural Frequency
0.3G
rms
0
Real
Hz150 50.00001 Hz
Auto Pwr Spec 1 HZ1.63
2G
-2
Real
s8 0 s
Time Record 1 TIME1.63
X:109.125 Hz Y:214.7374 mG
dX:554.6875 ms dY:-729.2974 mGX:164.0625 ms Y:1.379613 G
Time Waveform
Frequency Spectrum
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Jack D. Peters - CTC 128
fn
= [1/(2π)] k/m
INCREASE the stiffness ( k )
INCREASE the frequency (f)
INCREASE the mass ( m )
DECREASE the frequency ( f )
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Jack D. Peters - CTC 129
Natural Frequency fN
= [1/(2 π)] √
k/m
10 lbs. 30 lbs.
50 lbs.
95 lbs.
Pull Strength
Frequency Response ≈
2000 Hz.
k/m
≈
k/m ≈
k/m
≈
k/m
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Jack D. Peters - CTC 130
Bump Testing Set-up
UNIFORM WINDOWTake your time – Bump aroundDo not over range or clip the input signal800 – 1600 lines of resolutionTry some different frequency spansOnly 1 bump for each time recordAbout 4 averages (depends on noise)
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Jack D. Peters - CTC 131
Why the Uniform Window ?
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Jack D. Peters - CTC 132
Bump It ! Two Responses !
2G
-2
Real
s1 0 s
Time Record 1 TIME4.63
0.015G
rms
0
Real
Hz100 0 Hz
Auto Pwr Spec 1 HZ4.63
dX:76.17188 ms dY:-1.36474 GX:23.4375 ms Y:1.63297 G
X:70.75 Hz Y:8.475402 mGX:65.5 Hz Y:12.23725 mGX:58.75 Hz Y:8.550765 mG
Time Waveform
Frequency Spectrum
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Jack D. Peters - CTC 133
Mental Health Check !
2G
-2
Real
s1 0 s
Time Record 1 TIME4.63
0.015G
rms
0
Real
Hz100 0 Hz
Auto Pwr Spec 1 HZ4.63
dX:76.17188 ms dY:-1.36474 GX:23.4375 ms Y:1.63297 G
X:70.75 Hz Y:8.475402 mGX:65.5 Hz Y:12.23725 mGX:58.75 Hz Y:8.550765 mG
Time Waveform
Frequency Spectrum
76.17 msec/5 = 15.23 msec
F = 1/0.01523 sec = 65.64 Hz
65.5 Hz
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Jack D. Peters - CTC 134
Using the Time Waveform
Log decrement = (1/n)[LN(A0
/An
)] = (1/5)[LN(1.633/0.268)] = 0.36
Damping ratio = Log dec/2Pi = 0.36/2Pi = 0.36/6.28 = 0.057
Amplification factor = 1/(2*Damping) = 1/(2*0.057) = 8.68
2G
-2
Real
s1 0 s
Time Record 1 TIME4.63X:99.60938 ms Y:268.2297 mGX:23.4375 ms Y:1.63297 G Time Waveform
A0
= 1.633 GAn
= 0.268 Gn = 5 cyclesLN = natural log
F = 1/0.01523 sec = 65.64 Hz
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Jack D. Peters - CTC 135
Using the Spectrum
0.015G
rms
0
Real
Hz100 0 Hz
Auto Pwr Spec 1 HZ4.63X:70.75 Hz Y:8.475402 mGX:65.5 Hz Y:12.23725 mGX:58.75 Hz Y:8.550765 mG Frequency Spectrum
F = 65.5 Hzf2
= 70.75 Hzf1
= 58.75 Hz
-3dB
Find the –3dB points = AF
* .707 = 12.24 mG
* .707 = 8.65 mG
Find the frequencies at the –3dB points (f1 and f2
)
Amplification factor = F/ (f2 - f1
) = 65.5/(70.75 –
58.75) = 5.46
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Jack D. Peters - CTC 136
Bump Testing SummaryTake your timeChoose your weaponBump aroundUniform WindowLook at the time waveformLook at the frequency spectrum
Do a mental health checkCalculate the amplification factorChange the massChange the stiffnessAdd dampingBump around
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Jack D. Peters - CTC 137
1x (Running Speed)
Mass Unbalance 1XCritical Speed 1XMisalignment 1x, 2x, 3xLooseness 1X, 2X, 3X, 4X, 5X, ….NxRunout 1X
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Jack D. Peters - CTC 138
1x Mass Unbalance
1.5inch
-1.5
Real
s15.99609 0 s
TIME 1
0.7inchrms
0
Magnitude
Hz100 0 Hz
FREQ 1X:60 Hz Y:88.18431 minchX:30 Hz Y:584.5464 minch
1x
2x
fT
= 1 ?
1600 Lines
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Jack D. Peters - CTC 139
1.5inch
-1.5
Real
ms249.9390 s
TIME 1
0.7inchrms
0
Magnitude
kHz6.40 Hz
FREQ 1
1x Mass UnbalanceFt = 1 ?
1600 Lines
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Jack D. Peters - CTC 140
1x Mass Unbalance
1x
2x
1.5inch
-1.5
Real
ms249.9390 s
TIME 1
0.7inchrms
0
Magnitude
Hz100 0 Hz
FREQ 1X:60 Hz Y:88.18431 minchX:30 Hz Y:584.5464 minch
FT ≠
1 !
But it makes a nice set of plots to analyze !
Primarily 1x
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Jack D. Peters - CTC 141
1x, 2x, 3x
Misalignment
1x
2x
1x2x
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Jack D. Peters - CTC 142
1x, 2x, 3x
Misalignment
1x
Angular
Misalignment
2x
Offset
Misalignment
Look for a 1800
phase shift across the coupling in axial vibration measurements. Be careful with the way
you mount the accelerometer. Don’t create the 1800 phase shift by flipping the accelerometer around.
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Jack D. Peters - CTC 143
Rolling Element BearingsRolling element bearings will not generate frequencies that are even multiples of running speed. They are non-synchronous.They often generate low amplitudesThey have stages of failure starting with high frequency stress waves deteriorating to low frequency components.When the vibration gets better – shut the machine off immediately!
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Jack D. Peters - CTC 144
Rolling Element Bearing Frequencies “Inner Race Rotates”
Inner race and shaft rotate.
Outer race is held or fixed.
FTF = (Hz/2)[1-(B/P)cosCA]
BPFO = (N/2)Hz[1-(B/P)cosCA]
BPFI = (N/2)Hz[1+(B/P)cosCA]
BSF = (PHz/2B){1-[(B/P)cosCA]2}
Where:
Hz. = rotor speed in cps
N = number of rolling elements
B = ball diameter
P = pitch diameter
CA = contact angle
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Jack D. Peters - CTC 145
Rolling Element Bearing Frequencies “Outer Race Rotates”
Inner race and shaft fixed.
Outer race rotates.
FTF = (Hz/2)[1+(B/P)cosCA]
BPFO = (N/2)Hz[1+(B/P)cosCA]
BPFI = (N/2)Hz[1-(B/P)cosCA]
BSF = (PHz/2B){1-[(B/P)cosCA]2}
Where:
Hz. = rotor speed in cps
N = number of rolling elements
B = ball diameter
P = pitch diameter
CA = contact angle
No Rotation
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Jack D. Peters - CTC 146
Approximate Rolling Element Bearing Frequencies
“Approximate Calculations when Inner Race Rotates”
Ball Pass Frequency Outer RaceBPFO = .41 x number of rolling elements x speed
Ball Pass Frequency Inner RaceBPFI = .59 x number of rolling elements x speed
Ball Spin FrequencyBSF = .22 x number of rolling elements x speed
Fundamental Train Frequency (Cage Frequency)FTF = .41 x speed
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Jack D. Peters - CTC 147
Rolling Element Bearings (BPFI)9 - CENTER ROLL
532E044D -MIH MOTOR INBOARD HORIZONTALRoute Spectrum 21-Feb-04 08:37:46
OVERALL= 5.20 V-AN PK = 2.13 LOAD = 100.0 RPM = 1174. (19.57 Hz)
0 300 600 900 12000
0.3
0.6
0.9
1.2
Frequency in Hz
PK V
eloc
ity in
mm
/Sec
Freq: Ordr: Spec: Dfrq:
589.03 30.10 .289 94.91
SKF 63267.66 FTF43.01 BSF61.31 BPFO95.26 BPFI
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Jack D. Peters - CTC 148
Rolling Element Bearings (BPFI)
9 - CENTER ROLL532E044D -MIH MOTOR INBOARD HORIZONTAL
Route Waveform 21-Feb-04 08:37:46
RMS = 3.52 LOAD = 100.0 RPM = 1506. (25.09 Hz)
PK(+) = 17.23 PK(-) = 17.94 CRESTF= 5.10
0 50 100 150 200-20
-15
-10
-5
0
5
10
15
20
Time in mSecs
Acc
eler
atio
n in
G-s
CF ALARM
CF ALARM
PK ALARM
PK ALARM Angel Fish
Impacts create Resonance of
Inner Ring
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Jack D. Peters - CTC 149
Rolling Element Bearings
ft = 1 ?
t is very small
F is very high
F max
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Jack D. Peters - CTC 150
Rolling Element Bearings
ft = 1 ?
t is longer
f is lower
F max
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Jack D. Peters - CTC 151
Rolling Element Bearings
ft = 1 ?
T is really long
f is really low
F max
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Jack D. Peters - CTC 152
Rolling Element Bearings ?
As the frequency gets lower bad things are happening !
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Jack D. Peters - CTC 153
Rolling Element Bearings ?
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Jack D. Peters - CTC 154
Rolling Element Bearings ?
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Jack D. Peters - CTC 155
Gear MeshNumber of Teeth x Speed of the Shaft it is mounted on.Sidebands around gear mesh will be spaced at the shaft speed the gear is mounted on.Typically the vibration will be in the axial direction
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Jack D. Peters - CTC 156
Gear Mesh & Shaft Speeds
1776 RPM
(29.6 Hz)25T
46T
29T
149T
16.09 Hz (965.2 RPM)
3.13 Hz (187.9 RPM)
Shaft Speeds
Inter Speed = 29.6(25/46) = 16.09 Hz16.09 x 60 = 965.2 CPMOutput Speed = 16.09(29/149) = 3.13 Hz3.13 x 60 = 187.9 CPM
Gear Mesh
GMH = 29.6 x 25 = 740 Hz740 x 60 = 44,400 CPMGML = 16.09 x 29 = 466.6 Hz466.6 x 60 =27,996 CPM
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Jack D. Peters - CTC 157
0.1psi
rms
0
Magnitude
Hz40 20 Hz
1X:33.05971 Hz Y:25.62417 mpsiX:31.82788 Hz Y:89.65971 mpsiX:30.59605 Hz Y:31.80463 mpsi
Gear Mesh with Sidebands of Shaft Speed
Gear Mesh = 31.828 Hz
Sideband spacing = 1.232 Hz1.232 Hz x 60 = 73.9 CPM73.9 RPM = Shaft Speed
Zoom Window
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Jack D. Peters - CTC 158
FansBlade Pass
Number of Blades x Speed of the Shaft the rotor is mounted on.Look at the damper and duct work for flow and restrictions.Blade clearance, discharge angle, wear & tear
Unbalance, misalignment, bearings
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Jack D. Peters - CTC 159
Pumps
Vane PassNumber of Vanes x Speed of the Shaft the rotor is mounted on.Look at the input and output pressuresVane clearance, discharge angle, wear & tear
RecirculationRandom noise in FFT & Time WaveformAxial shuttling, High back pressure, Low flow rateFluid being forced back into pump
CavitationRandom noise in the FFT & Time WaveformAudible noise, Low back pressure, High flow rateAir entrained in fluid
Unbalance, misalignment, bearings
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Jack D. Peters - CTC 160
Motors (synchronous)
Synchronous Speed(2 x Line Frequency)/number of poles
Stator2 x Line Frequency and Multiples
RotorSidebands Around Running Speed = Slip Frequency x Number of Poles with Multiples
Unbalance, Misalignment, Bearings
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Jack D. Peters - CTC 161
BibliographyEisenmann, Robert Sr. & Eisenmann, Robert Jr., Machinery Malfunction Diagnosis and Correction, ISBN 0-13-240946-1Eshleman, Ronald L., Basic Machinery Vibrations, ISBN 0-9669500-0-3Vibration Institute, Basic Machinery Vibrations & Machinery Vibration AnalysisLaRocque, Thomas, Vibration Analysis Design, Selection, Mounting, and Installation, Application Note, Connection Technology CenterAgilent Technologies, The Fundamentals of Signal Analysis, Application note 243Agilent Technologies, Effective Machinery Measurements using Dynamic Signal Analyzers, Application note 243-1
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Jack D. Peters - CTC 162
Thank You !
You can find technical papers onthis and other subjects atwww.ctconline.com
in the “Technical Resources”
section