case study - seal oil piping 2012
TRANSCRIPT
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Seal Oil Piping Vibration on an Oil Free
Screw Compressor in an FPSO
Application
RayD.Kelm,P.E.(*presenter)KelmEngineering
DeanJefferyGEOil&GasWilliamEganGEOil&Gas
AbstractAdryscrewcompressorskidwasfabricatedforoffshoreservicethatincludedoilbufferedmechanicalsealsonthecompressor. Duringshoptesting,excessivesealoilpipingvibrationwasobservedthatresultedinpipecomponentfailures.Theoilsystemwasdesignedtoincludeacommonlubeandsealoilsystemwithapumpdesignpressureof590psi. Thereweresixoilcontrolvalvesonthesystem,includingalubeoilpressurecontrolvalve,oneflowcontrolvalveontheinletendofthecompressor,anotherflowcontrolvalveonthedischargeend,twodifferentialpressurecontrollerstomaintaindifferentialpressureonthesealsforeachendofthecompressor,aswellasabackpressurecontrolvalvefortheoilsystem.Vibrationandpressurepulsationmeasurementsindicatedthattheresponsewasatthepocketpassfrequencyof206Hz. Thesourcewasdeterminedtobeatthecompressor. Arrangementofthecontrolvalvesandcontrolsensinglineswerelikelycontributorstotheseverityoftheresponse.Modificationtothesealoilsystemincludedadditionofseveralvolumesatstrategiclocationstochangetheacousticalcharacteristicsoftheoilsystemtoreducetheshakingforcesinthepipesystem. Thesechangesalongwithpipesupportmodificationsandchangestothecontrolvalvesensinglinesweresuccessfulatreducingthepipepulsationsandvibrationresponsetoacceptablelevels.
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SealOilPipingVibrationonanOil
FreeScrewCompressorinan
Ray
D.
Kelm,
P.E.KelmEngineering
DeanJeffery
WilliamEgan
as
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E ui mentDescri tion
acombined
lube
and
seal
oil
system.
o or r venw gear ncreaser.
Oil
buffered
mechanical
seals.Verycompacts i require orFPSOapp ication
includingtheentiremachinetrainaswellasthe
.Skidispointsupportedon3AVMs(antivibration
.
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Com ressor
Details
2950HP4poleinductionmotor(50Hzpower)
2.13:1gearincreaser
3175RPM
Input
Speed
to
Compressor
211.7HzPocketPassFrequency
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GeneralSkidLayout
Compressor
r ver
Baseplate
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SealOilSupplySystem
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Vibration
Test
Results Generalpipingvibrationamplitudeswerein
the
0.2
1.0
in/sec
peak
range. Somelocationsonvalves(handles,instrument
connections,drains,etc.)wereashighas10
in/secpk.
Vibrationwasallat206Hz(1Xpocketpass
Theentireskidhadelevatedvibrationat206.
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InitialSolutionPath
Investigateforpipingsystemmechanical naturalfrequencies.
Numerous
resonances
near
pocket
pass
frequency
identified.
usingelastomericclamps.
Replaced
anumber
of
U
bolt
clamps
with
lined
clamshell
typetoimproverigidityandpossiblyadddamping.
theaddedcompliancewould reducethe forcedresponse.
Someim rovementbutacce tablelimitswerenotmet.
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AdditionalTestResults
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TestforAcousticalResonance
Pressurepulsationsensor
installednearoneflow
controlvalvesuggested
thatan
acoustical
resonanceexistednear1X
poc etpass requency
whenpipeimpactedwith
softmallet.
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AcousticalAnalysis
Acoustical analysis of the seal oil supply and return piping was doneusing a pulsation source at the connections to the compressor withvariable input frequency. An acoustical resonance was suspected in the
compressor for the seal supply piping.
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SealDescription
Thesealsusewereanoilbuffered mechanical
.
assemblyatapproximately30 PSIabove
reference as ressure usin back ressure
controlvalves.
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PossibleCauses
Controlvalvesamplifyingpulsationsdue
inthe
system
possibly
cross
talking.
Initialpulsationreadingsindicated
pulsationswerehigherbetweenthetwo
.
feedingbackintothesealoilsupply
.
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FinalSolution
Installedacousticalisolationvolumesinthe
acousticalresonance.
Similar volumes
added to both
return piping
near the
compressor.
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AcousticalVolumes
The size of the volumeswas selected based on theconce t that addin
compliance would shift thenatural frequency as well asprovide some low pass filtereffect.
selected was 0.1 at 206 Hz based on standard acousticallow pass filter theory (Kinsler, et. al.)
S12
2
121
1
+
kLSS
T
L
1
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PredictedResultswithVolumes
The predicted results were shown to almost eliminatepulsations upstream of the volumes as well as
connections at the compressor.
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FinalTestSummaryLocation Original Hoses Volume Prediction Final Test
LP Supply downstream
of FCV
75 psi pk-pk 40 psi pk-pk 1.0 psi pk-pk 1.2 psi pk-pk
LP Return upstream ofBPV
5 psi pk-pk 0.02 psi pk-pk
HP Supply downstream 51 psi pk-pk 24 psi pk-pk 1.3 psi pk-pk 4.6 psi pk-pk
of FCV
HP Return upstream of
BPV
32 psi pk-pk 0.9 psi pk-pk
Seal Oil Header 13 psi pk-pk 11 psi pk-pk 0.5 psi pk-pk 1.5 psi pk-pk
LP upstream of FCV 90 psi pk-pk
HP upstream of FCV 66 psi pk-pk
Pressure pulsation levels were significantly reduced
along with corresponding vibration response.
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LessonsLearned
Acousticalresponseofsealoilpipingcanproducehighpressurepulsationsandvibrationwithinsealoilsupply
sys emg ven er g con ons.
Previoussystemsofsimilardesigndidnothavethisproblem.
producedpulsingflowattheseals.
Thepresence
of
multiple
control
valves
may
have
contributedtotheseverityoncetheresponsestarted.
Inletsideflowcontrolvalves.
.
Acousticalresonancegreatlyamplifiedthepulsations.
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LessonsLearned,cont.
Correctingtheacousticalforcedresponsebyaddingvolumeswasmuchmoreeffectivethanstiffeningthe
p pean or e un ngmec an ca na ura requenc es.
Althoughmechanicalresonanceswereidentifiedonthe,
significantlyreducepipevibration.
Manyof
the
measured
natural
frequencies
were
not
easy
to
calculate
,
makingthemverydifficulttopredict.
Variationofvalvebrands(differenthandwheeldesigns,etc.)changed.
Theforcedresponsefromthepressurepulsationsproducedexcessivevibrationevenwhenresonanceswerecorrected.
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LessonsLearned,cont.
Pulsationlevelswerereducedbyacousticalmodification(addedvolumes)toreducetheforced
response
energy.Thepipesystemresponsedroppeddramaticallyoncethe
pu sat onenergywasre uce nt ep p ng.
Futuredesignsshouldconsiderreviewofthepossible.
Additionofpulsationdampinghardware(compliantvolumesand/ororifices similartoconce tsusedforreci rocatin
pumpsshould
be
considered
to
reduce
the
potential
for
resonantresponse.