TECH_MATTERS_no6_tcm155-236231.pdf
Transcript of TECH_MATTERS_no6_tcm155-236231.pdf
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TechnicalMattersCase studies covering technical issues and their solutions
March 2012 Issue 6
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Technical Matters March 2012
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CASE STUDY 1
Water tank cracking
An investigation was initiated by therepeated cracking of water tanks in theaft body of an LNG carrier due to highlocal vibrations at the aft end.
To identify the source of vibrations andadvise the owner on possible remedial
actions, vibration sensors were placed at anumber of strategic locations. In addition,hull pressures were recorded near thepropeller, and borescope observations were
made. All recorded data was analysed withMATLAB, a technical computing language,using frequency domain representations.
The results showed that the tanks naturalfrequencies coincided with the third,fourth and fifth blade passing frequencies,
resulting in structural resonances withvelocities well above the 30 mm/s peakvalue (the maximum recommended at
those frequencies in Lloyds RegistersShip Vibration and Noise Guidance Notes).
Such higher order blade frequencies donot normally transmit sufficient energyto cause large excitations, so this was an
unusual case.
Borescope observations showed that
significant sheet cavitation was generated
each time a propeller blade passed the topdead centre position. The shed cavitation
interacted with the sheet cavitation on thefollowing blade, resulting in periodic burstsof high energy pressure excitation. This
behaviour indicated a strongly retarded flowinto the propeller plane.
Based on the advice of Lloyds RegistersTechnical Investigation Department (TID),the client installed vortex generators aheadof the propeller. These generators improved
the inflow into the propeller plane andreduced the cavitation significantly. Nofurther cracking of the water tanks has
occurred since then.
LESSON
Strongly retarded inflow in the
propeller plane can result in
dynamic cavitation and higher
order excitations that could
lead to resonances in aft end
structures.
Time histories of vibration and hull pressure
Velocity transducers on panel structure
Frequency analysis of vibration time histories showing principal modes
Vessel
LNG carrier (see front cover)
Issue
Excessive aft end vibration
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Technical Matters March 2012
CASE STUDY 2
Gas dispersion
Natural evaporation of organic chemicalcompounds during the loading ofcrude oil carriers leads to tank pressurebuild-up. When this exceeds the setsafety standard, gaseous compoundsare vented via a riser mast. Becauseinhalation of these compounds poses
a health risk, safety limits are set forpermitted concentration levels.
At the clients request, Lloyds RegistersTechnical Investigation Department (TID)provided a Computational Fluid Dynamics
(CFD) study on the dispersion of theseorganic compounds. This included threedifferent wind speeds, two wind headings
and two riser heights. In all cases theconcentration of hydrogen sulphide (H2S)and hydrocarbons (CxHy) were recorded.
These analyses clearly demonstrated thata threshold wind speed exists, belowwhich concentration levels onboard and in
the vessels direct surroundings exceededsafety limits. Concentrations were particularlyhigh at the aft deck due to re-circulation
behind the wheelhouse. The resultsfurther showed that riser height had littleinfluence on dispersion patterns. Of even
more significance was the velocity of riseremissions as greater velocities increasedispersion volumes.
Given the limited number of case studiesand the likelihood of exceeding safety
levels, further analyses were recommendedto provide a definite answer. For the timebeing, the client was advised not to vent
Hydrogen sulphide on aft deck
Hydrocarbon dispersion cloud
LESSON
CFD analyses can significantly contribute to defining operational
windows for the safe loading of crude oil tankers.
Vessel
Crude oil tanker
Issue
Safe operational loading windows
at low wind speeds. Two possible solutionssuggested to the client were to remove the
heavier hydrocarbons from the emissions orto pre-mix the riser emissions and increasethe outflow velocity.
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Technical Matters March 2012
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CASE STUDY 3
Stern tube bearing damage
When the stern tube bearing of a newcontainer ship was damaged duringsea trials, Lloyds Registers TechnicalInvestigation Department (TID) wasasked to investigate the possible causes.
The propeller was removed from the tail
shaft and radial run-out measurementswere taken along with clearances between
the shaft and stern tube bearings. The tailshaft was removed and a visual examinationcarried out on the stern tube bearings and
shaft. Bearing bore and tail shaft diametermeasurements were taken and alignment
checks carried out. Stern bush wall thicknessmeasurements were also taken, andon-board documentation was reviewed.
The failure of the stern tube bearingcould have been caused by any one of,
or combination of, several modes of failure.It was necessary to examine each one inturn and, where justified, discount possiblemodes, to arrive at the most probable
cause of failure.
Potential causes were considered and
some discounted. The slope of the sterntube bearing bush housing was satisfactoryand it was probable that the slope of
the original stern tube bearing had been
satisfactory before failure. The originalclearances between the bearing and tail
shaft were within the manufacturersrecommended limits. A small gapexisted between adjacent bearing bush
sections but in this case had not significantlyaffected the bearing load carrying capacity.
Measurements by TID on other vesselshave demonstrated that manoeuvring athigh speed imposes additional loads on
the stern tube after bearing. The additionalloads are particularly severe during turnsto starboard when high pressures and
consequent thin oil films are generated atthe aft edge at the five o clock positionlooking forwards.
The vessel was in the light ballast conditionduring the sea trials. This was only just
sufficient to immerse the propeller andwould have generated an adverse bendingmoment with the centre of thrust belowthe shaft centre line. Records also indicated
that the vessel was undergoing high speed
manoeuvring immediately before the sterntube bearing damage occurred.
This excessive manoeuvring in thelight ballast condition was therefore
considered to be the most probable causeof the damage.
Damage to stern tube aft bearing Damage to propeller tail shaft
Washways
Damaged
areas
Grooving
Black band
LESSONThere should be adequate propeller immersion at all
times and excessive manoeuvres at high speed using
large rudder angles should be avoided.
Vessel
Container ship
Issue
Damage sustained during sea trials
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Technical Matters March 2012
CASE STUDY 4
Propeller optimisation
Design limitations and powerrequirements often force propellerdesigners to accept certain levelsof cavitation. Striking the balancebetween acceptable cavitationand the risk of damage is a delicatematter however.
This is reflected in the significant number
of propeller-induced vibrations cases that
Lloyds Registers Technical InvestigationDepartment (TID) receives each year.
One possible solution is to install finsor vortex generators (VGs) to influencethe flow towards the propeller.
By introducing a fin or VG on a strategiclocation, the inflow in the propeller planecan be improved significantly. In general,the more uniform the propeller inflow
becomes the lower vibration levels arelikely to be.
Aided by Computational FluidDynamics (CFD), the design and locationof fins and VGs can be optimised.
In this particular case, a strong tube
vortex was identified at the end of thewing propellers bossing. At full speed
ahead, the tube vortex interacted with
Before flow improvement After flow improvement
Vessel
Motor yacht
Issue
Improving propeller inflow
LESSON
With the aid of CFD analysis it
is possible to test and optimise
flow improvement devices priorto installation.
the tip vortex, leading to violent
cavitation shedding.
By placing four shaped fins on the shaft
casing, the tube vortexs strength waslargely diminished and its path altered.Instead of going through the tip region,
it now passed through the root sectionof the propeller. As a result of themodification the propeller inflow
improved considerably.
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CASE STUDY 5
Environmental impactof wave making
Lloyds Registers Technical InvestigationDepartment (TID) was asked to makea Computational Fluid Dynamics (CFD)parametric study of the wave-makingcharacteristics of a shallow waterarticulated tug/barge (ATB) assembly.
The studys key objective was to estimatethe maximum height of the wavesgenerated by the ATB while operating in a
shallow, 5 metre deep, river and assess itsenvironmental impact.
Using CFD techniques, the project wassplit into two stages. The first (main)
investigation involved 12 parametricruns covering the operation of the ATB
assembly under two loading conditions(load and ballast draughts) and sixspeeds (1, 2, 3, 4, 5 and 6 knots) at zerotrim condition.
The output of each parametric run was thenused to predict values for the maximumwave height at distances of up to 200
metres from the sailing line of the ATB.
A validation study was carried out to
corroborate the CFD predictions. Thestudy modelled the flow around the ATB
at load draught at 10 knots. This studyallowed qualitative comparison withphotographs of a similar ATB travelling atthe same speed, thus increasing confidencein the results of the main investigation.
Comparison between the computedwave patterns, in particular the bow
wave, at 10 knots load draught andthe photograph of a similar ATB at
the same speed indicated a goodqualitative match. The actual maximumpeak-to-trough wave height at a distanceof 25 metres from the sailing line of the
ATB is around 0.3 metres and this wasobserved for the 6 knot load case usingCFD techniques.
It was also predicted that the rateof wave height decay is generallylarger near the ship and decreases
with distance. The CFD techniques alsoconfirmed that wave height, as expected,
decreases with decreasing ship speed.Wave heights at ballast draughtwere predicted to be roughly two-thirdsof those at the same speed at
load draught.
Articulated tug barge travelling at 10 knots with surrounding wave pattern
CFD prediction of wave pattern at 10 knots which
allows a qualitative comparison
Vessel
Articulated tug barge
Issue
Waves generated in shallow waters
LESSON
Computational Fluid Dynamics
provides a viable alternative
to extensive model testing for
predicting wave heights at
varying distances from the
sailing line.
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Technical Matters March 2012
CASE STUDY 6
Stabiliser fin failure
After six years of active service, oneof a pair of retractable stabilising finsattached to the side of a passenger/ro ro ship was to be found missing.
During examination of the remaining partof the stabiliser stock at the Lloyds Register
Materials and NDE Laboratory it wasfound that a fatigue crack, caused by cyclicunidirectional bending, had formed froma single initiation point at a tear drop
artefact. This artefact was due to a lackof fusion between successive weld beadswithin the intermediate weld between
the parent material and the stainlesssteel cladding.
The purpose of the ferrous intermediate
weld was not clear, although it mayhave been used to reduce the carboncontent of the material to which the
austenitic stainless steel cladding wasto be laid down. However the interfacebetween the carbon steel parent metal
and austenitic stainless steel claddingwould normally be facilitated usinga higher alloy weld material for the
first weld layer onto the carbon steel,
followed by laying down the austeniticstainless steel cladding layer.
The material properties and dimensionsof the parent material and the stainless steelcladding were within design specification.
The distinct bands of slow and fast crackpropagation indicated considerable
variation in service loading due tothe variable sea conditions. The crackpropagation extended almost the entire
diameter of the shaft before the shaftfailed due to overload. This indicated thatthe fin stock shaft had a high margin
against failure for the operationalbending stresses experienced.
It was recommended that the reason
for the intermediate weld should beidentified. Recommendations were
also made that the stabiliser stocksshould be examined both visually andby non-destructive examination (NDE)techniques for the presence of cracks.
Replacement stabiliser stocks should beexamined visually and ultrasonically forcracks after two years in service.
Fracture surface on section of stabiliser stock
Section through initiation point at tear
drop artefact
Fracture initiation zone showing beach marks
indicative of fatigue fracture
LESSON
Poor manufacturing practices can often lead to early failure during
service life. Understanding material properties and the mechanisms of
failure can lead to more robust solutions.
Vessel
Passenger/ro ro ship
Issue
Material failure
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CASE STUDY 7
Auxiliary enginecrankshaft problems
After the failure and subsequentoverhaul of an auxiliary diesel engineon a passenger/ro ro ship, a crankshaftbalance weight was dischargedthrough the side of the engine soonafter the ship went back into service.
Lloyds Registers Technical Investigation
Department (TID) was asked to investigatethe cause of the damage and to ascertainwhether the failure was linked to arecent overhaul carried out by the engine
manufacturers personnel.
The engine was examined along with
operational documentation. The causeof the damage was fatigue fracture
of the balance weight which, alongwith the securing studs, was submittedto Lloyds Register Materials and NDELaboratory for further metallurgical
examination.
The fatigue crack had propagated from
a fillet radius in the balance weight.Subsequent rupture caused the impactdamage and shutdown of the engine.
The crack initiation site was within a heat-affected zone associated with the flame-
cutting procedure used in the originalbalance weight manufacturing process.The failure mechanism had previously been
identified by the manufacturers some13 years previously. Finite element analysisdetermined the magnitude of the stress
at the fatigue fracture initiation point.Based on this value, fracture mechanicscalculations indicated a crack depth up to
2 mm might exist before propagation torupture is l ikely.
The fatigue crack had propagated in twophases. The first was during the period ofoperation after the engine was built. The
second, more recent, propagation followedfrom a sudden stoppage of the enginecaused by a dropped valve and coolingwater ingress into a cylinder.
Regular inspections as part of the vesselsplanned maintenance routine failed to
identify any crack. In this regard, theinspection procedures suggested by themanufacturers were considered inadequate.
Following the rupture of the balance weightand subsequent repair of the engine, all theoriginal balance weights were replaced with
those of the new design.
Damaged balance weight after discharge through side of engine
Vessel
Passenger/ro ro ship
Issue
Balance weight failure
LESSON
Poor manufacturing processes
can often lead to early failure.
When such problems are
identified it is essential that
adequate remedial guidance is
provided and appropriatein-service inspections carried out.
Balance weight fracture surface
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Technical Matters March 2012
CASE STUDY 8
Diesel pump failure
After a diesel engine failed in serviceat a water pumping station, aninvestigation was carried out by LloydsRegisters Technical InvestigationDepartment (TID) to pinpoint the cause.
The diesel engine was the prime mover for
a pump, which pumped floodwater fromthe local drainage system. The engine hadbeen rebuilt two years previously followingtotal immersion in floodwater, and when the
failure occurred only 42 running hours hadbeen accumulated since the rebuild.
The diesel pump had been running for95 minutes when there was a bang, theengine hall filled with smoke and the engine
stopped. None of the engine alarm/tripswere activated at the time of the failure. Avisual examination was made of the engine
components, the records were reviewed and
pumping station personnel interviewed.
The engine was fitted with a turbocharger,with the rotor supported by two oil lubricatedball bearings. The evidence pointed to failure
of the turbocharger turbine end bearing.This would have started a chain of eventsleading to high exhaust gas temperatures,reduced scavenge air flow and higher cylinder
temperatures causing a crank case explosion.
The failed turbocharger bearing, which
had been fitted at the time of rebuild, had
been stationary for prolonged periods. Otherrunning diesel engines could have caused
vibration at the contact points betweenthe stationary bearing rolling elementsand raceway causing impression damage
consistent with false Brinellingand eventual bearing failure.
No routine checks were carried out before
the engine started or while it was running.
End bearing showing evidence of ball race collapse
and overheating
Severe overheating of turbocharger casing and covers
Subject
Pumping station
Issue
Failure in service
This was inappropriate for the age of the
plant and the adequacy of the remotemonitoring systems. While not the primary
cause of the failure, a second watch-keeperand a high exhaust gas temperature alarm/trip may have averted the failure.
Recommendations were maderegarding repairs to the diesel engine,watch-keeping procedures and the level
of remote monitoring.
LESSON
Prolonged periods of diesel
engine idleness should be
avoided. Routine checks
should be carried out prior to
starting and while it is running.
Appropriate levels of remote
monitoring should be provided
that are consistent with the
levels of watchkeeping.
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CASE STUDY 9
Propulsion thruster damage
A tug had been experiencingcontamination of the propulsionthruster units. Oil samples were foundto contain high concentrations ofwater and wear products.
The propellers were subsequently removed
and dismantled. A large amount of afine paste as well as ice was found inthe hubs and in the propeller shaft seals.Lloyds Registers Technical Investigation
Department (TID) was asked to investigateand advise.
Each thruster unit was examined alongwith the associated static oil and lubricatingoil systems.
The damage process was likely to haveinvolved a number of contributory factors
relating to the original installation andcommissioning. It is probable that airwas trapped in the hub and this would
have caused poor lubrication of theblade operating mechanism. This mayhave contributed to the initial damage
which then led to water ingress andaccelerated wear.
The height of the oil tank reservoirs andvarious flow restrictions resulted in thetotal head of the static oil system at each
propeller hub being less than the designspecification. Contraction of the air andfluid in the hub after operations, along
with flow restrictions in the propeller shaftseal body, is thought to have produced alow pressure head in the hub resulting inan ingress of water.
Recommendations included repositioningthe static oil system gravity tanks to a
height appropriate for the thruster unitdesign pressure head range. This includedreplacing the interconnecting pipework
Typical galling damage of crank pin ring blade foot axial bearing surface
with pipes of larger diameter and rerouting
with a continuous fall of at least 5 thusreducing the risk of air traps being formed.
Recommendations were also made regardingventing procedures to ensure air did notbecome trapped when filling the static oilsystem. These recommendations included
filling the static oil system up from the hub tothe gravity tank and reconciling the amountof oil added with the volume of the system.
Typical galling damage of blade foot axial bearing surface in hub
Vessel
Tug
Issue
Contamination and damage
LESSON
Care needs to be taken in the
design and installation of podded
propulsors and their associatedstatic oil systems. In particular,
the installed pipework must not
lead to air locks and gravity tanks
should be located at sufficinet
height to maintain adequate
system pressure at all times.
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CASE STUDY 10
Overhead crane failure
After an incident in which the trolleyof a power station overhead cranefell from an L-shaped traversing beamduring an overhaul, a team fromLloyds Registers Technical InvestigationDepartment (TID) was asked to makean on-site investigation.
The TID team discovered that duringthe incident the cranes winch
motor windings had been removed,and during the operation the trolleybecame unbalanced and fell from the
traversing beam.
Team members examined the trolley
and the traversing beam, interviewedthe power stations personnel and tookdown and reviewed statements from
Trolley on traversing beam before removal of winch
motor windingsTrolley tilting and sliding on the traversing beam after
removal of winch motor windings
Subject
Power station
Issue
Failure during overhaul
witnesses. Markings on the trolley andtraversing beam also showed where thetrolley wheels had slid over the beams
lower plate before the trolley tipped andfell from the beam.
TID created a template the same widthas the traversing beams lower flange,placing on it the trolley wheels in the same
position as the trolley had been. The teamdiscovered that by tilting the board, thussimulating the trolleys instability, it waspossible for the trolley to tip over and fall
from the beam.
It was also found that while the lateral
clearance between the trolley wheels
and traversing beams lower flange weresatisfactory when the trolley was resting
normally on the lower flange with itswheels intact, when it was tilted, the lateralclearance became excessive and allowedthe trolley to fall off.
The TID team recommended that the trolley
be modified to reduce the lateral clearancesbetween it and the traversing beamslower flange, and to restrict the angular
movement of the trolley.
It was found that there were shortcomings
in the management system, with nowritten procedures produced by acompetent person. The team advised
that, in future, detailed procedures including provision for adequatelysupporting the balance weight side ofthe trolley prior to removal of the motor
windings be produced before suchwork started.
LESSON
Written procedures should
be in place prior to overhaul.
These should include provision
for adequately supporting the
balance weight side of the
trolley prior to removal of the
motor windings.
Template tilted to simulate the trolley tilting and then
sliding over the traversing beam lower plate
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March 2012
Technical Matters March 2012
Technical MattersEditor:Christopher Browne,
Marine CommunicationsDepartmentT +44 (0)20 7423 2305E [email protected]
Designer: Pipeline DesignT +44 (0)1480 462589E [email protected]
Technical Mattersis produced
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Communications Department
and designed by Pipeline Design.
Care is taken to ensure thatthe information in Technical
Mattersis accurate and up to
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accepts no responsibility for
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such information.
Technical Investigation TeamWe are a large group of highly experienced specialists and support staff. If you have anytechnical queries or issues that need a rapid response, please contact one of the following:
Donald Cameron Manager020 7423 1758 or
[email protected] joined Lloyds Registerin 1989 and has been withTID for most of that time.He is responsible for overallmanagement, recruitment,budgeting, tendering, servicedelivery, and monitoring andassessing performance.
Peter Filcek Technical Manager020 7423 1765 or
[email protected] LR in 1977 and hasbeen with TID since 1979. Peteroversees the technical quality ofTID services and training, and isresponsible for the allocation ofproject managers and projectteams. He represents TID in thediscipline of marine failures.
John Maguire Structural Engineering
Section Manager020 7423 1770 [email protected] joining LR in 1989 andthe TID team in 1994, Johnhas overseen a wide rangeof investigations, particularlythose relating to structuralengineering (marine andnon-marine), includingstructural dynamics, fatigueand fracture.
Peter Davies MachinerySection Manager020 7423 1761 [email protected], who joined LR in 1995 andhas been with TID since then, isresponsible for a wide range ofinvestigations, particularly thoserelating to machinery, propulsionand shafting systems.
Dejan Radosavljevic FluidDynamics Section Manager020 7423 1774 or
[email protected], who has been with LR andTID since 1994, is responsible fora wide range of investigations,particularly those relating to fluiddynamics (marine and non-marine), including computationalfluid dynamics (CFD).
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