Conceptual Design of a Semi-SubmersibleFloating Oil and Gas Production System for             Offshore Malaysia           ...
OCEN 407 Design Class                                   Team Malaysia                                                     ...
OCEN 407 Design Class               Team Malaysia                                             iiNomenclatureABS -         ...
OCEN 407 Design Class                              Team Malaysia                                                          ...
OCEN 407 Design Class                              Team Malaysia                                                          ...
OCEN 407 Design Class                 Team Malaysia                                                1Executive SummaryOverv...
OCEN 407 Design Class               Team Malaysia                                              25. Hydrodynamics of Motion...
OCEN 407 Design Class                 Team Malaysia                                                 3with the structure fl...
OCEN 407 Design Class                 Team Malaysia                                            4as to offset a permanent t...
OCEN 407 Design Class                Team Malaysia                                               5occurs in the pontoon, w...
OCEN 407 Design Class               Team Malaysia                                               6account for corrosion as ...
OCEN 407 Design Class                 Team Malaysia                                                7Regulatory ComplianceC...
OCEN 407 Design Class                Team Malaysia                                               8                        ...
OCEN 407 Design Class      Team Malaysia                      9                        Figure 2: General Iterative Process
OCEN 407 Design Class              Team Malaysia                                          10ObjectivesThe conceptual desig...
OCEN 407 Design Class               Team Malaysia                                              11           •   Cost      ...
OCEN 407 Design Class                    Team Malaysia                                         12                         ...
OCEN 407 Design Class               Team Malaysia                                           13                            ...
OCEN 407 Design Class                 Team Malaysia                                                  14accepted ranges. Al...
OCEN 407 Design Class                   Team Malaysia                                          15Appendix C: Environmental...
OCEN 407 Design Class               Team Malaysia                                            16to represent the topside. T...
OCEN 407 Design Class                   Team Malaysia                                         17                          ...
OCEN 407 Design Class                   Team Malaysia                                             18These forces were put ...
OCEN 407 Design Class                  Team Malaysia                                          19                  Figure 1...
OCEN 407 Design Class                Team Malaysia                                         20                    Figure 16...
OCEN 407 Design Class                Team Malaysia                                          21                            ...
OCEN 407 Design Class                Team Malaysia                                             22The weight of the pontoon...
OCEN 407 Design Class                Team Malaysia                                              23Two conditions were cons...
OCEN 407 Design Class                 Team Malaysia                                              24                       ...
OCEN 407 Design Class              Team Malaysia                                            25                            ...
OCEN 407 Design Class                Team Malaysia                                              26counteract any offsettin...
OCEN 407 Design Class                  Team Malaysia                                                  27                  ...
OCEN 407 Design Class                  Team Malaysia                                              28                      ...
OCEN 407 Design Class                Team Malaysia                                             29                         ...
OCEN 407 Design Class               Team Malaysia                                            30                           ...
OCEN 407 Design Class                  Team Malaysia                                         31Hydrodynamics of Motions an...
OCEN 407 Design Class                    Team Malaysia                                         32                      •• ...
OCEN 407 Design Class                  Team Malaysia                                            33             Fcr        ...
OCEN 407 Design Class               Team Malaysia                                              34the stranded wire. The wi...
OCEN 407 Design Class                Team Malaysia                                             35   •   Polyester Rope/Jac...
OCEN 407 Design Class               Team Malaysia                                             36                          ...
OCEN 407 Design Class             Team Malaysia                                          37                               ...
OCEN 407 Design Class                 Team Malaysia                                         38              Figure 35: Max...
OCEN 407 Design Class                 Team Malaysia                                               39                    Fi...
OCEN 407 Design Class                                                  Team Malaysia                                      ...
OCEN 407 Design Class                                                                              Team Malaysia          ...
OCEN 407 Design Class                   Team Malaysia                                                 42Strength and Struc...
OCEN 407 Design Class               Team Malaysia                                              43The deflections are small...
OCEN 407 Design Class                        Team Malaysia                                                      44        ...
OCEN 407 Design Class                                          Team Malaysia                                              ...
OCEN 407 Design Class               Team Malaysia                                            46condition is 2.63 intact an...
OCEN 407 Design Class                                         Team Malaysia                                               ...
OCEN 407 Design Class              Team Malaysia                                            48ConclusionAll of the followi...
OCEN 407 Design Class                Team Malaysia                                               49For the eight aforement...
OCEN 407 Design Class              Team Malaysia                                           50ReferencesAmerican Bureau of ...
OCEN 407 Design Class               Team Malaysia                                              51Appendix A: Hydrodynamics...
OCEN 407 Design Class   Team Malaysia   52
OCEN 407 Design Class   Team Malaysia   53
OCEN 407 Design Class   Team Malaysia   54
OCEN 407 Design Class                 Team Malaysia                                                55Appendix B: Ballastin...
OCEN 407 Design Class   Team Malaysia   56
OCEN 407 Design Class   Team Malaysia   57
OCEN 407 Design Class               Team Malaysia                                            58Appendix C: Environmental L...
OCEN 407 Design Class   Team Malaysia   59
OCEN 407 Design Class   Team Malaysia   60
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  1. 1. Conceptual Design of a Semi-SubmersibleFloating Oil and Gas Production System for Offshore Malaysia Team Members: Mr. HuiDong Bea Mr. Aaron Gregg Mr. Milton Hooks Mr. Brian Riordan Mr. Justin Russell Mr. Miles Williams
  2. 2. OCEN 407 Design Class Team Malaysia iTable of Contents________________________Nomenclature...................................................................................................................... iiList of Figures .................................................................................................................... iiiList of Tables ..................................................................................................................... ivExecutive Summary ............................................................................................................ 1 Overview......................................................................................................................... 1 Competencies.................................................................................................................. 1 General Arrangement and Overall Hull Design.......................................................... 2 Local and Global Loading .......................................................................................... 2 Weight, Buoyancy, and Stability ................................................................................ 3 Hydrodynamics of Motions and Loading ................................................................... 4 General Strength and Structural Design ..................................................................... 4 Mooring....................................................................................................................... 5 Cost ............................................................................................................................. 6 Regulatory Compliance .................................................................................................. 7Acknowledgements............................................................................................................. 7Introduction......................................................................................................................... 7Objectives ......................................................................................................................... 10Design Basis...................................................................................................................... 11Design Methodology......................................................................................................... 12 General Arrangement and Overall Hull Design............................................................ 12 Wind and Current Loading ........................................................................................... 14 Local and Global Loading ............................................................................................ 15 Weight, Buoyancy and Stability ................................................................................... 21 Hydrodynamics of Motions and Loading ..................................................................... 31 Strength and Structural Design - General ..................................................................... 32 Mooring......................................................................................................................... 33 Cost ............................................................................................................................... 35Results............................................................................................................................... 35 General Arrangement and Overall Hull Design............................................................ 35 Wind and Current Loading ........................................................................................... 35 Local and Global Loading ............................................................................................ 36 Weight, Buoyancy and Stability ................................................................................... 37 Hydrodynamics of Motions and Loading ..................................................................... 39 Strength and Structural Design - General ..................................................................... 42 Mooring......................................................................................................................... 43 Cost ............................................................................................................................... 47Conclusion ........................................................................................................................ 48References......................................................................................................................... 50Appendix A: Hydrodynamics of Motions and Loading ................................................... 51Appendix B: Ballasting..................................................................................................... 55Appendix C: Environmental Loads .................................................................................. 58Appendix D: StabCad ....................................................................................................... 61Appendix E: GMOOR .................................................................................................... 117
  3. 3. OCEN 407 Design Class Team Malaysia iiNomenclatureABS - American Bureau of ShippingAPI - American Petroleum InstituteArea ratio - Ratio of the area between the righting moment curve, downflooding angle, and heeling moment curve added to the area under the heeling moment curve, righting moment curve, downflooding angle, and inclination angle compared to the sum of the area under the heeling moment curve, righting moment curve, downflooding angle, and inclination angle and the area between the heeling moment curve and righting moment curveDown flooding angle - Static angle from the intersection of the vessels centerline and the waterline in calm water to the first opening that cannot be closed watertight and through which downflooding can occurDamaged condition - Condition in which ballast tanks are flooded to represent a damaged situationHeave - Vertical motion in waterHeeling arm - The horizontal distance between the buoyant force and the center of gravity to move the vessel away from the upright positionHeight coefficient - Characteristic of a structure in wind based on its heightIntact condition - Condition in which the semi-submersible is unharmedMARPOL - Marine Pollution ConventionPitch - Rotation around the transverse (x) axisRighting arm - The horizontal distance between the buoyant force and the center of gravity to bring the vessel to an upright positionRoll - Rotation around the longitudinal (y) axisSCR - Steel Catenary RisersSemi-taut mooring system - Mooring system in which the mooring lines are pulled in tension, but leaving some slackShape coefficient - Characteristic of a structure in wind based on its shapeSOLAS - Safety of Life at SeaTaut-leg mooring system - Mooring system in which the mooring lines are pulled in tension, having no slackUSCG - United States Coast GuardYaw - Rotation about the vertical (z) axis
  4. 4. OCEN 407 Design Class Team Malaysia iiiList of FiguresFigure 1: Final Team Organization..................................................................................... 8Figure 2: General Iterative Process..................................................................................... 9Figure 3: Proposed Project Location................................................................................. 11Figure 4: Original Basic Hull Design ............................................................................... 13Figure 5: Modified Basic Hull Design.............................................................................. 13Figure 6: Wind Height Divisions...................................................................................... 14Figure 7: Semi-submersible Current Drag Coefficients ................................................... 15Figure 8: ETABS Structural Model .................................................................................. 16Figure 9: ETABS Model with Waterline .......................................................................... 16Figure 10: Static Wave Model with Crest across Diagonal.............................................. 17Figure 11: Static Wave Model with Trough across Diagonal........................................... 17Figure 12: Pressures in Positive X, Y, and Z Directions without Wave........................... 18Figure 13: Pressures in Negative X, Y, and Z Directions without Wave ......................... 18Figure 14: Pressures in Positive X, Y, and Z Directions with Static Wave...................... 19Figure 15: Pressures in Negative X, Y, and Z Directions with Static Wave .................... 19Figure 16: Weight Distribution of Semi-Submersible Components................................. 20Figure 17: Buoyancy Force............................................................................................... 20Figure 18: Springs Attached at Nodes .............................................................................. 21Figure 19: Column Diagram ............................................................................................. 21Figure 20: Pontoon Diagram............................................................................................. 22Figure 21: Node Diagram ................................................................................................. 22Figure 22: Riser Placement and Ballasting Tank Diagram............................................... 24Figure 23: Balancing Spreadsheet .................................................................................... 25Figure 24: Auto Ballasting Example................................................................................. 26Figure 25: Horizontally Centered Topside CG Float-on/Float-off Scenario .................... 27Figure 26: Excessive topside CG offset for Float-on/Float-off ........................................ 28Figure 27: Intact Stability Objective Diagram.................................................................. 29Figure 28: Damaged Stability Objective Diagram............................................................ 30Figure 29: Final Hull Dimensions..................................................................................... 35Figure 30: Deflections and Displacements ....................................................................... 36Figure 31: Reaction Forces ............................................................................................... 37Figure 33: Shear Diagram................................................................................................. 42Figure 34: Bending Moment Diagram.............................................................................. 42Figure 35: 12 Leg Spread.................................................................................................. 43Figure 36: 16 Leg Spread.................................................................................................. 44Figure 37: Mooring Analysis Results ............................................................................... 44Figure 38: Mooring Material and Equipment Costs ......................................................... 45Figure 39: Chosen Mooring Design.................................................................................. 46
  5. 5. OCEN 407 Design Class Team Malaysia ivList of Tables_____ ____________Table 1: Metocean Data .................................................................................................... 12Table 2: Total Environmental Loads ................................................................................ 36Table 3: Deflections, Moments, and Stresses of Structure ............................................... 42
  6. 6. OCEN 407 Design Class Team Malaysia 1Executive SummaryOverviewWith the relatively low cost of energy and the rapid advancement of technology in the lastcentury, humankind has become highly dependent upon large quantities of inexpensive fuel foreverything from transportation of goods and people to the harvesting of crops for food to beingable see at night. As the population increases exponentially and demands for inexpensive energysolutions continue to rise, the readily available reservoirs of energy rich fossil fuels have rapidlydeclined. In order to meet these demands, fossil fuel exploration and production is forced intomore and more inhospitable conditions such as the extreme deep sea. The expenses associatedwith fixed production platforms at this depth are no longer within a feasible range making afloating production platform design a far more economical choice. One of the floatingproduction platform designs in use today and pursued by this conceptual design team is the semi-submersible production platform. This conceptual design team was given the weights anddimensions of the platform topsides required for production and drilling, and a location in theSouth China Sea at a water depth of 5,500 ft. A highly iterative process of altering the keydimensions of a four-column ring pontoon was conducted in order to meet applicable regulationsand client requests while minimizing costs and satisfying the chosen competencies. The designteam was divided into subgroups that would tackle different components of design based onindividual talent, desire and schedule availability and given a 3 month deadline.CompetenciesThe following 8 competencies were chosen to analyze and address in the conceptual design:1. General Arrangement and Overall Hull Design2. Wind and Current Loading3. Local and Global Loading4. Weight, Buoyancy and Stability
  7. 7. OCEN 407 Design Class Team Malaysia 25. Hydrodynamics of Motions and Loading6. General Strength and Structural Design7. Mooring8. CostGeneral Arrangement and Overall Hull Design(Methodology pg. 12, Results pg.35)The final hull design was a square ring pontoon with outer lengths of 270 ft., a height of 40 ft.and a width of 55 ft. The ring pontoon is topped with four square columns with a length of 50 ft.to a side and height of 80 ft. A square topside deck is supported by the four columns with thecorners of the topside deck placed at the geographical centers of column tops.Wind and Current Loading(Methodology pg. 14, Results pg.35)The provided metocean data for the Malaysia site includes the wave height, period, wind speedand current speed for both the operational and survival design condition. The operational andsurvival design storms are 10 year and 100 year storm conditions respectively for the designlocation. Shape and height coefficients taken from ABS were applied to the constant topsideshapes, the final exposed column shapes (with zero shielding) and the final component elevationsonce the final freeboard was calculated. Wind, current and mean wave drift were appliedconcurrently in the bow, beam and quartering directions resulting in maximum environmentalloads for operational and survival conditions to be 473.3 kips and 603.1 kips from the quarteringdirection.Local and Global Loading(Methodology pg. 15, Results pg.36)An analysis of the semi-submersible structure was performed using a three-dimensional analysisprogram for building systems, ETABS, to determine the deflections, moments, and stressesacting on the topside, columns, and pontoon of the hull. Two types of analyses were viewed: one
  8. 8. OCEN 407 Design Class Team Malaysia 3with the structure floating at a constant draft and the other with a static wave with the crest of thewave acting on two of the columns opposite from each other. This wave, modeled as per ABScode 3-3-A2/3.7, produced maximum moments, stresses, and deflections. Then, the weights ofthe hull, topside, ballast tanks filled with water, and nodes were added, along with the buoyancyacting on the bottom of the pontoon. Springs were added to the joint of the columns and pontoonto represent the mooring lines. Wind, wave, and current forces were not modeled for thestructural analysis, thus reaction forces for the springs in the x and y directions are zero when theanalysis was run. In addition the weights of all of the components are of equal and oppositeforce to the buoyancy resulting in zero net global displacement in the z direction.Weight, Buoyancy, and Stability(Methodology pg. 21, Results pg.37)Weight approximations of 9, 12 and 14 lbs/ft3 were used for columns, pontoons and nodesrespectively. An additional 48-62.5% was added for marine systems, brackets, paint, and designallowances. The hull buoyancy was simply the weight of the water displaced by the pontoons,nodes and the part of the columns that were submerged either during float-on, float-off,operational or survival conditions. Physical centers used for small angle stability and input intoStabCad for large angle stability were: KG = 70 ft., KB = 29.9 ft., BM = 63.4 ft., KM = 93.2 ft.,GM = 23.1 ft., with a draft of 85 ft. and a freeboard of 35 ft. All down flooding angles and arearatios for intact stability were in excess of the ABS recommended values. Two consecutivetanks were flooded all the way around semi-submersible to analyze the damaged stabilityresponse. The distance between down flooding angle and the first righting arm/ heeling armintercept is greater than the recommended 7 degree minimum in the worst case damaged casescenario. Six tanks in each pontoon are floodable to reach operational and survival drafts as well
  9. 9. OCEN 407 Design Class Team Malaysia 4as to offset a permanent topside center of gravity that is as far from the geographical center ofgravity as (47, 47) (ft).Hydrodynamics of Motions and Loading(Methodology pg. 31, Results pg.39)Using closed-form equations, the heave and pitch/roll period were determined to be 21.8 25.5seconds respectively. Heave and pitch/roll response was found using response amplitudeoperators found from a hull of similar dimensions for the degree headings of 0, 22.5, 45, 67.5and 90. The maximum heave response was found to be from the 22.5 degree heading and was+/-8.9 ft and +/-12.6 ft for the operating 10 year and survival 100 year storm conditionsrespectively. The maximum pitch/roll response was found to be from the 0 degree heading andwas +/-2.5 degrees and +/-4.3 degrees for the operating 10 year and the survival 100 year stormconditions respectively.General Strength and Structural Design(Methodology pg. 32, Results pg.42)As stated before, the structural analysis was performed using the program called ETABS. Thestick figure and loadings as previously mentioned were used. The stresses, for both wave cases,that were created from the pressures, weights, and buoyancy were compared to guidelines fromABS 3-2-3.3 through 3-2-3.11. The stresses for the topside and pontoon were the same while thestresses in the columns were slightly less.The structural analysis was run and the maximum values for the deflections, moments, andstresses for the topside, columns, and pontoon came from the moment diagrams in the staticwave case. The maximum deflection of the hull occurs in the topside, which is 1.17 in., whilethe columns contain the maximum moment at 13.8x106 kip-ft. The maximum stress, 29.92 ksi,
  10. 10. OCEN 407 Design Class Team Malaysia 5occurs in the pontoon, which is less than the calculated value, 29.94 ksi, as per ABSrecommendations.Mooring(Methodology: pg. 33, Results: pg.43)The mooring design for the semi-submersible was created with the aid of the software programGMOOR. Environmental and mooring line component data was manually entered into GMOORwhich constructed a model of the system. Twelve and sixteen leg mooring system designs weretested with chain, polyester, and spiral wire components in both taut-leg and semi-taut legmooring system designs. The mooring lines at both the fairleads and anchors are composed ofchain to account for an increase of stresses at the fairleads and to fit chain jacks, as well as toaccommodate the situation where the mooring lines may lay on the ocean floor, not to getsediment into the polyester or wire components. Wire as the middle component performed wellin both taut and semi-taut designs, providing the required in-water weight for the semi-tautsystem for restoring force but added a significantly larger downward force on the hull. Thepolyester middle component could also be adapted to work well in both taut and semi-taut legmooring systems. While this provided the required stretch for the restoring force in the taut-legconfiguration, it lacked the in-water weight to provide an adequate restoring force in the semi-taut design. A dynamic analysis of the mooring system was conducted with concurrentenvironmental forces applied in the direction of each mooring line to find the worst case intactand damaged conditions. The results of these analyses were checked against API 2SKrecommended mooring guidelines. It was determined that the polyester line was ideal for a taut-leg system, and the wire line was ideal for a semi-taut system. An increase of 0.02-0.04mm tothe diameter of all the steel components of the mooring line per design year is recommended to
  11. 11. OCEN 407 Design Class Team Malaysia 6account for corrosion as per API 2SK Stationkeeping Manual. The final design was dictated bymeeting all mooring objectives and pertinent regulations stipulated in API 2SK as well asminimizing cost. The finalized system was a twelve leg taut system with 200 ft. of 2.75 in. K4Studless chain at the anchor, 7,350 ft. of 3.94 in. polyester rope as the middle component and300 ft. of 3.0 in. K4 Studless chain at the fairlead. The anchors chosen for this design are 11.36tons Stevmanta vertically loaded drag embedment anchors built by Vryhof. The Stevmanta waschosen because it performs ideally for taut leg systems and it is much more cost effective thanusing suction piles. SEPLAs (Suction Embedded Plate Anchors) were also considered for theanchors, but were not included in the final design due to unknown installation costs, which areexpected to be significantly higher than Stevmanta placement.Cost(Methodology: pg. 35, Results: pg.47)The total hull cost was approximated by steel weight at $12,000 per short ton of steel. Threeweight estimates were used for cost approximation purposes: 12 lbs/ft3 for pontoons, 9 lbs/ft3 forcolumns and 14 lbs/ft3 for nodes. The final semi-submersible design resulted in a steel weight of21,902 (kips) or 10,951 (tons) resulting in a net hull cost of $184 Million (USD). UsingStevmanta drag embedment anchors projected to be $51,000 (USD) apiece; total anchor cost is$612,000 (USD). With a 12-leg taut mooring system design as previously mentioned, line andassociated equipment costs are estimated to be $192 Million (USD). Total hull and mooringcapital would then cost $7.8 Million (USD).
  12. 12. OCEN 407 Design Class Team Malaysia 7Regulatory ComplianceConsiderations were made towards American Bureau of Shipping (ABS), American PetroleumInstitute (API), International Convention for the Safety of Life at Sea (SOLAS), United StatesCoast Guard (USCG) and the Marine Pollution Convention (MARPOL) in all applicable areas ofchosen conceptual design competencies.AcknowledgementsIt should be noted that a significant amount of help in understanding the problems andapproaches to solving offshore issues was provided by engineering mentors currently working inthe offshore industry. This list of engineers included: Rod King of Lloyds Register, Peter Nobleof ConocoPhillips, Philip Poll of Houston Offshore Engineering and Kent Longridge ofInterMoor.IntroductionThe conceptual design team decided to analyze the aforementioned competencies from thestandpoint of a four-column ring pontoon semi-submersible platform. Regard was made to giventopside dimensions and weight, required risers and their respective tensions, water depth andMetocean data associated with the reservoir location. Engineers of varied backgrounds assistedin the design process by giving guest presentations during classroom meetings, answering someof the questions presented by the different design teams and helping with approximationmethods.The teams first meeting resulted in the election of Brian Riordan as the team captain who thenbroke the rest of the members into two-man teams to tackle what was thought at the time themost crucial and most likely governing factors to the design: ABS/API regulatory complianceresearch, StabCad familiarization, ETABS (structural analysis program) familiarization, andautomation of generating StabCad input points from prototype spreadsheet. After two weeks ofmeetings with only small accomplishments in some StabCad familiarization and a Matlabprogram to quickly develop a StabCad model based on dimension changes a strategicrestructuring was required to re-identify and prioritize the order in which analysis would takeplace. The two-man teams also lead to a lack of accountability in analysis so everyone wasgiven a “point man” or lead status for different aspects of design with a partner assigned to workon the project at the same time to offer aid. Regularly scheduled team meetings reviewedprogress from each lead to keep everyone on track. This structuring seemed to work for a fewweeks before it became apparent that each lead had developed his own semi-submersible thatmet his immediate goals, whether it was large angle stability, hydrodynamic properties orstructural strength constraints, but did not meet all of them. The final restructuring kept the pointman positions previously assigned but had them report immediately to the Team Captain anychanges they made or problems they encountered and almost all inter-team communication wasthen facilitated through the team captain in the following organizational structure seen in Figure1: Final Team Organization.
  13. 13. OCEN 407 Design Class Team Malaysia 8 Figure 1: Final Team OrganizationTeam members worked jointly with each other to help solve certain issues within their specificassignments and tried to keep designs dynamic so changes in an interdependent competencywere easily updated in their design during the iterative process.All other responsibilities were absorbed by the team captain and cost was determined jointly bythe Mooring lead and the Team Captain- combining costs of anchors and mooring with thestructural steel costs of the hull. Once spreadsheets and programs such as GMOOR, StabCadand ETABS were understood, a spreadsheet would take the input changes to any dimensionalchanges, provide hydrodynamic responses, freeboards, drafts and ballasting requirements. If allof these past inspection, a batch file would run a Matlab program converting the X,Y,Z pointsgenerated in the spreadsheet to a StabCad compatible input file for large angle stability analysis,and other dimensions and area moments of inertia were also given to ETABS for structuralanalysis. The topside dimensions (with the exception of a horizontal center of gravity) remainedconstant, so a change in draft and exposed areas of columns were all that were needed torecalculated concurrent environmental forces. The maximum concurrent forces were then usedin GMOOR to determine mooring line sizes.To aid in iteration cycle speed, the acceptable column width range was determined by ahydrodynamic analysis, and a minimum area moment of inertia used in ETABS while amaximum projected area used for environmental forces. With a freeboard set to a constant, alldimension iterations were then compared to the maximum bending and shear stresses for theweakest structural design and with the largest environmental loads. If the tested dimensions pasthydrodynamic inspection and a quick comparison to worst case scenarios for structural andenvironmental conditions, then it would definitely pass an in-depth analysis and was worthpursuing. The general iteration process can be seen in Figure 2: General Iterative Process.
  14. 14. OCEN 407 Design Class Team Malaysia 9 Figure 2: General Iterative Process
  15. 15. OCEN 407 Design Class Team Malaysia 10ObjectivesThe conceptual design is to satisfy the following criterion: • Drafts & Freeboard o A maximum float-on float-off draft of 29.52 ft. determined by Dockwise boat capacity. o A minimum operational freeboard (air gap) of 35 ft. based on metocean data. • Hydrodynamic responses o A minimum natural heave and pitch/roll period of 20 seconds based on client requests for optimum operation of topside separation tanks and risers. o A maximum of +/-16 ft heave response based recommendations from HOE o A maximum 4◦ pitch/roll for 10 year storm conditions and a maximum 10◦ pitch/roll for 100 year storm conditions based on HOE recommendations. • Large Angle Intact Stability o Righting Arm should be greater than 2 times the heeling arm at the down flooding angle. o Area ratio for a non-ship shaped floating structure should be greater than 1.3. • Large Angle Damaged Stability o There should be a distance greater than 7 degrees between the first intercept of the righting and heeling arm and the down flooding angle. • Structural Stress Allowances o Maximum topside stress of 29.94 ksi o Maximum column stress of 27.8 ksi o Maximum pontoon stress of 29.94 ksi • Mooring o Dynamic intact mooring analysis factor of safety should be greater than 1.67 as per API codes. o Dynamic damaged mooring analysis factor of safety should be greater than 1.25 as per API codes. o Pretension stress for semi-taut and taut-leg mooring systems should not exceed 20% of the breaking strength. o Platform offset for intact mooring system during operations should not exceed 5% of the water depth. o Platform offset for intact mooring system during survival mode should not exceed 7% of the water depth. o Platform offset for damaged mooring system should not exceed 7% of the water depth. o Platform must be able to move 150 feet off center in any direction for drilling purposes.
  16. 16. OCEN 407 Design Class Team Malaysia 11 • Cost o Cost should be minimized while meeting all other objectives.Design BasisThe design site is in 5,500 ft. water depth in the South China Sea off the coast of Malaysia.Singapore has fabrication capacity for both platform topsides and semi-submersible hull only585 miles from the proposed platform location making Singapore the ideal construction site asseen Figure 3. Figure 3: Proposed Project LocationEven though the relatively short distance makes a wet-towing option economical, the ring-pontoon design considered is not as hydrodynamic as a two-pontoon hull, so designing the hullfor the dry-tow option left greater transportation versatility in the event that a wet tow was tooexpensive. A maximum draft for the dry-tow option is 29.52 ft.The metocean data for the proposed design site was given as follows in Table 1.
  17. 17. OCEN 407 Design Class Team Malaysia 12 Table 1: Metocean Data Location Malaysia Max Design Condition Operating Extreme Environmental 10 Year 100 Year Component Wind: Wind Spectrum API RP 2A API RP 2A Speed, Vw (1 hour31.1 knots 36.9 knots mean at 10 m) Sea Waves: Wave Spectrum JONSWAP3 JONSWAP3 Significant Wave 16.1 ft. 20.7 ft. Height, Hs Maximum Wave 30.8 ft. 39.4 ft. Height, Hmax Peak Period, Tp 12.7 sec. 13.1 sec. Peakedness 1.7 1.9 Parameter, γ Surface Speed, Vc 2.3 knots 2.5 knotsThe environment is fairly benign with insignificant swells and a 100 year significant wave heightof about 21 ft. Assuming linear wave theory applies, ABS suggests adding 5 ft. to the 100 yearsignificant wave height to determine a minimum freeboard or air gap, putting the minimum airgap at 26 ft.Riser fatigue and topside separation tank effectiveness are a function of natural heave andpitch/roll period. As such, natural heave and pitch/roll period were designed to be higher than 20seconds as per client requests.HOE recommends heave response to be within +/- 16 ft. for both 10 year and 100 year stormconditions. In addition, ABS stipulates an acceptable 10 year storm pitch/roll to be a maximumof 4 degrees and a 100 year storm pitch/roll to be a maximum of 10 degrees.For large angle intact stability analysis, ABS recommends that the righting arm should be at leasttwice the heeling arm at the down flooding angle. Since the semi-submersible is not consideredship-shape, the required minimum area ratio is 1.3. In a damaged stability condition, ABSrecommends a minimum distance between the first intercept of the righting and heeling arm tobe at least 7 degrees from the down flooding angle.Design MethodologyGeneral Arrangement and Overall Hull DesignThe original general hull design was as basic as could be: a square ring pontoon supporting foursquare columns with outer column edges flush with the given topside dimensions of 220 ft. by220 ft. as seen in Figure 4.
  18. 18. OCEN 407 Design Class Team Malaysia 13 Figure 4: Original Basic Hull DesignAfter calculating small angle stability and response periods, it was difficult to find a set ofdimensions that met the objectives adequately so the pontoon lengths were increased, spreadingthe distance between the columns so that the topside deck corners were set on the geographicalcenters of the tops of each column as seen in Figure 5. Figure 5: Modified Basic Hull DesignAcceptable small angle stability and physical center data seemed within reason and responseperiods, freeboard and float-on and float-off drafts were also easily obtainable within their
  19. 19. OCEN 407 Design Class Team Malaysia 14accepted ranges. All following iterations were made with the general basic hull design as seen inFigure 5.Wind and Current LoadingAn Excel spreadsheet was created to calculate all of the wind forces acting on the platform. Theexcel spreadsheet can be seen in Appendix 1. To compute the wind force the platform above thewaterline had to first be broken up into 50 foot increments as seen in Figure 6. Figure 6: Wind Height DivisionsThe area of each of the different components in between each 50 foot increment was thencomputed. For all the components in between 50 foot increments a height coefficient wasassigned. These coefficients were found from the ABS MODU manual. Also based on the typeof structure each component was (i.e. truss, flat hull, cylinder etc.) assigned a shape coefficientfound in the ABS MODU manual. The forces were computed for every 45 degrees around theplatform. It was determined that the greatest load would come when the wind impacted the rig onits northeast corner. The following equation was used to determine the wind forces: F = C S C H CW SV 2Where CS is a coefficient which comes from the shape of the structure in consideration, CH is thecoefficient of height which is based off the height of the structure above the mean water line. Todetermine the height coefficients the semi was broken up into 50 foot increments. The areas ofthese increments were then computed which is the value S. Both the coefficient of shape andheight come from recommended figures provided by ABS. The CW coefficient is a standardcoefficient that accounts for several constant factors. V is the average wind speed for a one hourtime interval.The current forces were calculated using the same spreadsheet listed in
  20. 20. OCEN 407 Design Class Team Malaysia 15Appendix C: Environmental Loads. Because the geometry of the hull is symmetrical there wasno need to compute the load for more than one side and one corner. Since there is more exposedsurface area when the current is flowing toward the semi at a 45 degree angle the force acting onthe corner of the hull will be greatest at the corners under this condition. The current force wascomputed using the equation below which is similar to that of the wind force equation mentionedabove. Unlike the wind force however the projected area of the submerged area did not have tobroken down into smaller areas, however a shape coefficient was computed based on the radiusthe corners of the columns and pontoons. F = C S SV 2In equation 8 all of the variables have the exact same meaning as those for equation 4 but thecoefficient of shape was calculated from API 2SK Figure C-2 which is shown below in Figure 7. Figure 7: Semi-submersible Current Drag Coefficients(ABS MODU)The mean wave drift force was calculated using the force coefficients given in the GMOORexample file. The wave period must be matched to the value given in the file. Then the force isthe coefficient times the wave amplitude squared.Local and Global LoadingThe program that is used for structural analysis of the semi-submersible is ETABS. This is athree-dimensional analysis program for building systems. The model that is inputted intoETABS is a stick figure version of the hull design. The length of the pontoons and topside comefrom the distance from center to center of the columns, which is 220 feet. The height of themodel is the distance from the center of the pontoon, entire length of the column, to half of thetopside height, which is 118 feet. Equivalent cross-sectional areas for the beams, pontoon, andcolumns were determined by moments of inertia. A rigid plate was placed on top of the columns
  21. 21. OCEN 407 Design Class Team Malaysia 16to represent the topside. This model, shown in Figure 8 was input into ETABS with forcesapplied. Figure 8: ETABS Structural ModelTwo different types of analyses were performed on the structure. One analysis has the structuresubmerged in a constant draft of 67.74 ft., shown in Figure 9. Figure 9: ETABS Model with WaterlineThe other analysis contains a static wave that causes the maximum deflection and moments. Tofind the maximum deflection of the topside and pontoons, the maximum moment needs to bedetermined. ABS code 3-3-A2/3.7 states that “A diagonal wave (30-60 degrees) from the bowwith a length of about one and half times the diagonal distance between pontoon ends will inducethe maximum design longitudinal shear force between the pontoons. In this load case, thelongitudinal forces on the two pontoons and columns are maximized and acting in the oppositedirections. Thus, the horizontal bracings will be subject to the maximum bending moment.” Thediagonal wave was modeled at 45 degrees from the bow, with a wavelength of 466.7 ft, and thecrest of the wave was placed across the diagonal of the semi-submersible, shown in Figure 10.
  22. 22. OCEN 407 Design Class Team Malaysia 17 Figure 10: Static Wave Model with Crest across DiagonalThe same wave was entered with the trough across the diagonal of the structure; this can be seeninFigure 11. The two cases involving the static wave gave similar results. From this pointforward, only the case with the crest across the diagonal will be discussed. Figure 11: Static Wave Model with Trough across DiagonalThe main forces on the hull are from hydrostatic pressures, which are more dominating thanwind, wave, and current forces. The total pressure is determined by the static and dynamicpressure equations: Ptotal = Pstatic + Pdynamic Pstatic = ρ gz Where: ρ = 1.99 slugs/ft3 g = 32.2 ft/sec2 z = water depth Pdynamic = ρ gAe kz Where: A = amplitude of wave k = wave number = 2π/L
  23. 23. OCEN 407 Design Class Team Malaysia 18These forces were put into ETABS as two different load combinations, for display reasons,shown in Figure 12, Figure 13, Figure 14, and Figure 15. The two former figures display thestructure in water, without static wave acting on it, while the two latter figures contain the staticwave with 100 year storm significant wave height and a wavelength 1.5 times the hull diagonallength as specified by ABS. Figure 12: Pressures in Positive X, Y, and Z Directions without Wave Figure 13: Pressures in Negative X, Y, and Z Directions without Wave
  24. 24. OCEN 407 Design Class Team Malaysia 19 Figure 14: Pressures in Positive X, Y, and Z Directions with Static Wave Figure 15: Pressures in Negative X, Y, and Z Directions with Static WaveAll of the weights of the semi-submersible were then added to the model. These weights includethe topside, columns, pontoon, nodes, risers, and the mooring lines. The weight of the topside is40,256 kips and was uniformly distributed across the rigid plate on top of the model. The weightof the columns and pontoons, 4,753 kips and 54,756 kips, respectively, were also inputted asuniformly distributed loads. The weights of the nodes, 4,159 kips each, were added to thebottom of the columns. The eight risers, weighing an average of 444 kips each, are located onopposite sides of the pontoon with four on each side. Located at the top of the columns are thetwelve mooring lines, weighting 68 kips each. This weight distribution can be seen in Figure 16.
  25. 25. OCEN 407 Design Class Team Malaysia 20 Figure 16: Weight Distribution of Semi-Submersible ComponentsThe buoyancy force counteracts the weights of the entire semi-submersible and is equal to135,028 kips as seen in Figure 17. Figure 17: Buoyancy ForceSprings were placed at the nodes between the columns and the pontoons to represent the mooringlines, shown in Figure 18.
  26. 26. OCEN 407 Design Class Team Malaysia 21 Figure 18: Springs Attached at NodesThe spring stiffness is determined by: k = F/x Where: F = average force of mooring line (from GMOOR) at fairlead = 116.8 kips x = maximum displacement of semi-submersible = 550 ft. (from watch circle defined by ABS as 10% of the water depth)Weight, Buoyancy and StabilityWeight approximations were given for each of the main shapes used in the basic hull designwere 9, 12 and 14 lbs/ft3 for columns, pontoon and nodes respectively. The weight of thecolumns seen in Figure 20 is modeled as a point mass for stability at the geometrical center ofthe column. The buoyancy is modeled as a point force at the geometric center of the submergedportion of the column with a magnitude equal to the weight of displaced water. Figure 19: Column Diagram
  27. 27. OCEN 407 Design Class Team Malaysia 22The weight of the pontoon seen in Figure 20 is modeled as a point mass in the center of eachpontoon- there being four individual pontoons in the ring. The buoyancy is modeled as a pointbuoyancy in the geometrical center of the submerged portion of each of the pontoons in the ring.The force applied at the buoyancy point is equal to the weight of displaced water. Foroperational and survival conditions, the pontoon is completely submerged. Only in a float-on orfloat-off scenario is the pontoon possibly only partially submerged. Figure 20: Pontoon DiagramThe nodes were modeled as the densest part of the hull and are the portion of the hull where thecolumns intersect the ring pontoon as seen in Figure 21. Figure 21: Node DiagramLike the columns and pontoon, the nodes weight is modeled as a point mass located at thegeometric center of the node and the buoyancy is modeled as point buoyancy located at thecenter of the submerged portion of the node. Like the pontoon, under both operational andsurvival conditions the nodes are completely submerged and are only partially submerged in afloat-on or float-off scenario. The magnitude of force applied at the buoyancy point is equal tothe weight of the displaced volume of water.
  28. 28. OCEN 407 Design Class Team Malaysia 23Two conditions were considered in regard to given topside horizontal center of gravity: a givenCG of (0,0) (with the origin at the top, middle of the deck), or an offset CG. The ideal scenariowould be a topside with a given centered horizontal center of gravity. Conditions may arise infabrication resulting in a slight or even drastic movement of the CG from the topside center thatwould have to be permanently offset in ballasting tanks. This offset may require a significantamount of ballasting to offset, and thus put the float-on/float-off draft over the maximum draftallowed. If production deadlines are not met, a scenario might occur where most of the topsideis moved out with the hull to the project location and another topside component is derived at alater time. In this scenario, ballasting would be used to temporarily offset the asymmetricalweight of topside during float-on/float-off operations and until the missing topside component isdelivered. These scenarios were kept in mind during the ballasting tank design.Eight steel catenary risers (SCR) were required for production, all at different tensions. It wasinitially thought that ballasting tanks would have to be used to counteract the offset CG, but itwas also thought possible to hang the SCRs as evenly as possible off opposite sides of the hull tominimize CG shift. These risers were placed in the spreadsheet shown in the diagram in Figure22.
  29. 29. OCEN 407 Design Class Team Malaysia 24 Figure 22: Riser Placement and Ballasting Tank DiagramMooring weight and/or tension at fairleads had to be added as well to find the final verticalcenter of gravity, draft and freeboard. The mooring tensions (found in a later part of the report)are also shown at the corners of the diagram in Figure 22: Riser Placement and Ballasting TankDiagram.Resultant center of gravity was calculated from transverse, lateral and vertical moments as seenin Figure 23.
  30. 30. OCEN 407 Design Class Team Malaysia 25 Figure 23: Balancing SpreadsheetTo satisfy damaged stability criteria recommended in ABS, 6 equally sized tanks were placed ineach of the four pontoons. Tank ballasting levels were determined by an automated Macroimbedded in a spreadsheet that would first balance the hull by filling some of the tanks to
  31. 31. OCEN 407 Design Class Team Malaysia 26counteract any offsetting topside CG, then filling them all to reach a 35 ft. freeboard, thenconsolidating the ballasting water into as few tanks as a simple algorithm could handle. Ademonstration of an auto-ballasting spreadsheet system can be seen in Figure 24. Figure 24: Auto Ballasting ExampleA float-on/float-off scenario for a (0,0) topside CG analysis simply involved removing riser andmooring tension and emptying tanks. If the small angle stability was acceptable (GM greaterthan 10 ft.) and the draft was less than the maximum allowed by Dockwise equipment (29.52 ft.)then float-on/float-off would remain a viable option. An example of this scenario can be seen inFigure 25.
  32. 32. OCEN 407 Design Class Team Malaysia 27 Figure 25: Horizontally Centered Topside CG Float-on/Float-off ScenarioAs is evident in Figure 25, the gravity to metacentric height is in excess of the target 10 ft. andthe draft is less than the maximum 29.52 ft. leaving a dry-tow an option for this design.An offset topside CG for a float-on/float-off scenario was also considered and also seemed morecritical than for an operational situation. The only method the hull has to counteract an offsettopside CG is with ballasting. Any increase in ballasting weight, however, would increase thealready relatively deep draft for float-on/float-off and could quickly remove dry-towing fromtransportation options. An example of this scenario is seen in Figure 26.
  33. 33. OCEN 407 Design Class Team Malaysia 28 Figure 26: Excessive topside CG offset for Float-on/Float-offThe draft in Figure 26: Excessive topside CG offset for Float-on/Float-off is highlighted redsignifying an error that was triggered by excessive draft for the float-on/float-off condition.For quick analysis the gravity to metacentric height (GM) was used to determine right away ifthe proposed design dimensions would result in a stable hull or not. This stability analysis wasonly valid for small angles of list, so StabCad was used for the large angle stability analysis. Anintact stability analysis was run first resulting in a graph similar to the example shown in Figure27.
  34. 34. OCEN 407 Design Class Team Malaysia 29 Figure 27: Intact Stability Objective DiagramFor an intact analysis, two basic requirements were to be met: one, that the area ratio is greater ⎛ Area[ A + B] ⎞than 1.3 ⎜ ≥ 1.3 ⎟ and two, that the righting arm moment is at least 2 times greater ⎝ Area[C + B ] ⎠than the heeling arm moment at the down flooding inclination angle for 100 knot winds.A damaged case analysis stipulated that the worst-case scenario of any two consecutive floodedtanks anywhere in the hull had to result in a minimum 7 degree distance between the firstintercept between the righting arm and heeling arm and the down flooding angle as seen inFigure 28 in 50 knot winds.
  35. 35. OCEN 407 Design Class Team Malaysia 30 Figure 28: Damaged Stability Objective DiagramOnce dimensions passed small angle stability, freeboard and hydrodynamics tests a spreadsheetrecorded the X, Y and Z positions of each key point used for a StabCad model. A batch file thenran a Matlab program that took the Excel spreadsheet X, Y, and Z points and saved them as a .txtfile in a StabCad friendly format. The text file was saved as a new StabCad file which was thenrun to check large angle stability for intact and damaged cases. A simple example of thisStabCad model can be seen in Figure 29. Down flooding points were placed at the tops of thecolumns, and panels were defined according to where solid planes were in the model. Hullvolumes were defined differently than the topside volumes and shape coefficients were appliedto each of the topside components. Figure 29: StabCad Model
  36. 36. OCEN 407 Design Class Team Malaysia 31Hydrodynamics of Motions and LoadingOne of the early objective conformity tests was in hydrodynamics, having both heave andpitch/roll natural periods greater than 20 seconds. A virtual added mass approximation of 100%the hull weight was used to determine heave period. Two formulas were used to perform thesetests: 2m THeave = 2Π ρgAwp Where: m = mass ρ = density g = gravity Awp = Water plane area I TRoll = 2Π Awp gGM Where: I = Second Moment of Inertia with respect to water plane GM = distance from the center of gravity to metacenterIn addition to heave and pitch/roll periods, heave and pitch responses, were to be determined;conforming to ABS recommendations. A simplified dynamic free-body diagram can be seen inFigure 30. F(t) m k c Figure 30: Simplified example of heave motionRAO (Response Amplitude Operator) data was found using a hull of similar dimensions inGMOOR. RAO is defined as response amplitude of the structure per unit wave height or waveamplitude. Figure 30 shows a simplified example of heave motion, the governing equation usedfor calculation can be seen in the following equation.
  37. 37. OCEN 407 Design Class Team Malaysia 32 •• • m X + c X + kX = F ( t ) = Re { F0 eiwt } Where: m = Equivalent Virtual Mass of System (Real mass +Added mass) c = Equivalent Viscous Damping Coefficient of System k = Equivalent Stiffness of System F(t) =External Force (i.e. Regular Wave Force)RAO values in conjunction with JONSWAP data were used to develop maximum heave andpitch/roll responses for different headings using the following equations. RMS = ∆ω iΣ ( RAO 2 i S (ω ) ) RS = ∆ω i RAO 2 i S (ω ) Where: ω is in rad/s and S(ω) is the metocean data calculated using JONSWAP The limits recommended by ABS are defined as +/-16 feet for all heave maximum responses,+/-4 degrees for pitch/roll maximum response using 10 year storm data, and +/-10 degrees forpitch/roll maximum response using 100 year storm data.Strength and Structural Design - GeneralAs previously stated, the program called ETABS was used to perform the structural analysis.The model length of the pontoons and topside is 220 feet, while the height of the model is 118feet. Equivalent cross-sectional areas for the beams, pontoon, and columns were determined bymoments of inertia. The thickness of the columns and pontoon is 1 inch, and modeled as 1.25 in.to account for scantling, ribs, and stiffeners. A rigid plate was placed on top of the columns torepresent the topside. A stick figure was modeled to represent the semi-submersible, with theprevious stated pressure, weight, and buoyancy loadings. The stresses that are created fromthese forces are compared to the ABS code 3-2-3.3 through 3-2-3.11. The values of the stress forthe topside and pontoon from ABS come from the following equations. Fy F= F .S . Where: Fy = yield strength of steel F.S. = factor of safety = 1.67For the columns, the equation for the stress is:
  38. 38. OCEN 407 Design Class Team Malaysia 33 Fcr F= F .S . ⎛ Fy 2 ⎞ ⎛ Kl ⎞ 2 Fcr = Fy − ⎜ 2 ⎟ ⎜ ⎟ ⎜ 4π E ⎟ ⎝ r ⎠ ⎝ ⎠ Where: Fcr = critical stress of steel E = Modulus of Elasticity K = effective length factor r = radius of gyrationBy using 50 ksi, common for many types of steels, for the yield strength of the steel used, thestresses for the topside and pontoon are both 29.94 ksi. For the columns, the stress is calculatedto be 27.8 ksi.MooringThe purpose of a mooring system is to limit the semi-submersibles movement so that theplatform remains in place over the equipment on the sea floor. The mooring system does allowfor some movement of the platform so that the amount of tension in the mooring lines is reducedwhich allows for smaller diameter mooring lines thus reducing material costs. Also if themooring system is to tight then if the platform suffers an impact from a large wave such as arouge wave it can cause a very sudden and dramatic acceleration of the platform that can throwworkers to the floor and damage equipment. However, there is a limit to how much the platformcan offset because in most cases with steel catenary risers an offset greater than 5 percent of thewater depths will cause increased fatigue on the risers or break them. Traditionally mooring lineshave consisted of a chain fairlead and ground chain and a wire rope in between the two.However, for this design analysis it was decided to investigate the use a polyester rope as well atsteel stranded wire. The reason for this is that polyester is much lighter than wire and sodecreases the weight on the platform and has a much hire modulus of elasticity which allows formore restoring force.It was decided that a twelve leg taut and semi-taut mooring system should be analyzed alongwith a sixteen leg taut and semi-taut. A catenary mooring system was not analyzed because at5500 foot water depths such systems become very heavy and much more difficult to install. Dueto the limited amount of time available for this design a preliminary analysis was performed thattested the viability of using polyester rope and stranded wire for taut and semi-taut systems. Theactual material properties used for the polyester rope were those provided by InterMoor and forthe stranded wire the material properties of steel jacketed spiral stranded wire were used, theseproperties were also provided by InterMoor.After preliminary tests, by comparing the polyester rope and stranded wire designs with similarbreak strengths, it was found that for a taut mooring configuration, the polyester outperformed
  39. 39. OCEN 407 Design Class Team Malaysia 34the stranded wire. The wire in fact did not pass API design guidelines because the minimumfactor of safety for the stranded wire configuration was only 1.1. The API guidelines used forcomparison are listed later in this section. The reason that the wire had much lower factors ofsafety is because the wire is less elastic than the polyester, initiating fatigue sooner. Tocompensate for this, the wire diameter and length were increased until they passed theguidelines. As a result, the wire mooring configuration was 4.5 times heavier than the polyestersystem. Although wire is less expensive per pound than polyester, the cost of materials for thetwo designs is still similar. However, when a larger diameter is used for the line, it is moredifficult to install. When testing the semi-taut design, it was discovered that the polyesterallowed the offset of the platform to be greater than the API guidelines. There are two reasonsfor this occurrence: elasticity of the polyester and that it is almost neutrally buoyant in water.However, the semi-taut configuration needs the weight in the mooring lines to help pull theplatform back to its proper position. Due to these features of the polyester line, it was decidedthat further analysis for taut legs would only be performed with polyester rope and chainconfigurations. For semi-taut configurations only stranded wire and chain configurations wouldbe considered.In order to test the four designs, a software program called GMOOR was used. GMOOR is asoftware package that allows the user to input the water depth, environmental force coefficients,which are computed from the environmental loads computed earlier in the report. The locationof the semi-submersible’s fairleads is also entered into the GMOOR input file along with RAOdata. A separate input file is created for the actual mooring lines to be used. This file containsthe physical characteristics of the different mooring lines used, such as weight, design breakstrength, and stretch properties. This file also includes the length and diameter of each elementin the mooring line, the depth of the anchor, and the lateral distance from the fairlead to theanchor. Once these files are created, GMOOR combines them and constructs a diagram of whatthe design will look like and analyzes the tensions acting on the mooring lines and the anchor.GMOOR then allows the user to enter environmental forces and the angle at which they act onthe platform. GMOOR assumes that anchors can never fail, allowing the user to break lines inorder to check the damaged performance of the mooring system. Four designs were fully testedand optimized using GMOOR. The testing included running a batch file that dynamicallyanalyzed the environmental forces as being collinear and tested them at 22.5 degree intervalsaround the platform. At each of these intervals, GMOOR would test the mooring system with alllines intact and then break each line sequentially and then reset it and test the next line. Byanalyzing the mooring system this way, it was possible to determine not only the response whenthe 1st, 2nd or 3rd most loaded line is broken, but the response when any line is broken.Therefore, GMOOR was able to find the worse case scenario. The optimization was performedby shortening the line lengths and decreasing the diameters to minimize material costs whilemaking sure not to sacrifice the safety of the system. The mooring designs were tested againstguidelines created by the American Petroleum Institute (API) and the American Bureau ofShipping (ABS) which are: • Maximum Offset for Intact Operational Condition 5% of Water Depth • Maximum Offset for Damaged/Survival Condition 7% of Water Depth • Minimum Factor of Safety for Intact Condition 1.67 for Dynamically Analysis • Minimum Factor of Safety for Damaged Condition 1.25 for Dynamically Analysis
  40. 40. OCEN 407 Design Class Team Malaysia 35 • Polyester Rope/Jacketed Spiral must not touch seafloorIdeally, this mooring analysis would include analyzing the various environmental loads comingfrom the actual average directions and other various angles to the platform rather than examiningthem only as collinear. Such situations can cause unexpected responses. However, this wasbeyond the scope of the design because the actual current, wind and wave directions wereunknown since there are no obtainable historical records.CostThe total cost of this design is approximately $7.2 million, which includes materials andequipment but not installation costs.ResultsGeneral Arrangement and Overall Hull DesignFinal dimensions are seen in Figure 31. These dimensions were larger than originally expected,being governed by down flooding angle rather than the expected freeboard. Figure 31: Final Hull DimensionsWind and Current LoadingAfter completing the excel spreadsheet to calculate the wind, current and wave loads the excelspreadsheet added up the sum of all the forces to calculate the total environmental load acting onthe platform. Table 2 shows the result of these calculations, for both operational and survivalconditions.
  41. 41. OCEN 407 Design Class Team Malaysia 36 Table 2: Total Environmental Loads Operational Conditions (kips) North South West East 381.6 370.0 354.4 349.7 NE NW SE SW 470.2 473.3 462.5 465.6 Survival Conditions (kips) North South West East 488.6 472.4 450.5 443.8 NE NW SE SW 598.6 603.1 587.8 592.2Local and Global LoadingETABS was run with pressures, weights, buoyancy, and spring forces on the model. Figure 32displays an exaggerated model of the deflections and displacements of the topside, pontoons, andcolumns. Figure 32: Deflections and DisplacementsSince the wind, wave, and current forces were not modeled for the structural analysis, thereaction forces for the springs in the X and Y directions are zero, and the weights of all of thecomponents are cancelled out from buoyancy to have no reaction in the Z direction, as shown inFigure 33.
  42. 42. OCEN 407 Design Class Team Malaysia 37 Figure 33: Reaction ForcesWeight, Buoyancy and StabilityFinalized dimensions resulted in the float-on/float-off (labeled as tow out/ loading) draft,operating draft and optional survival draft seen in Figure 34. Figure 34: Final DraftsAuto-ballasting could handle a permanent CG offset of 47 ft in both lateral and transversedirections for operational and survival conditions as seen in Figure 35.
  43. 43. OCEN 407 Design Class Team Malaysia 38 Figure 35: Maximum Permanent Offset for Operational and Survival ConditionsDue to draft constraints, and offset topside CG is likely more crucial for float-on/float-offconditions. A maximum acceptable topside CG shift of 10 ft in both lateral and transversedirections is seen in Figure 36.
  44. 44. OCEN 407 Design Class Team Malaysia 39 Figure 36: Maximum Permanent Offset for Float-on/Float-off Condition Hydrodynamics of Motions and Loading Using previously mentioned equations in a spreadsheet that can be seen in Appendix A: Hydrodynamics of Motions and Loading, for a hull running on the light side of weight approximations- response periods were 21.8 and 25.3 seconds for heave and pitch/roll respectively. Since the auto-ballasting Macro run in the ballasting spreadsheet kept the freeboard at 35 ft., the area of the water plane was the same for a hull on the heavy side of weight approximation as one running on the light side. Therefore, a hull running on the heavy side of the weight approximation had response periods of 21.8 and 25.5 seconds for heave and pitch/roll respectively. Both heavy and light cases were above the minimum 20 second natural period objectives. Table 3 shows maximum responses for heave and pitch/roll for each heading angle used. The maximum heave response occurs at a 22.5 degree heading and the maximum response for pitch/roll occurs at a 0 degree heading as can also be seen in bold type in Table 3. Table 3: Maximum Responses Heave Maximum Response (ft) Pitch/Roll Maximum Response (°)RAO Heading 0° 22.5° 45° 67.5° 90° 0° 22.5° 45° 67.5° 90°10 Year Storm 7.26 8.91 8.46 8.24 8.24 2.49 2.23 1.55 1.58 0.69100 Year Storm 10.61 12.57 11.78 11.25 11.15 4.26 3.86 2.76 2.22 0.86
  45. 45. OCEN 407 Design Class Team Malaysia 40Figure 37 through Figure 40 show the RAO, JONSWAP and resultant response plots for each ofthe maximum cases. 10 Year, 22.5 Degree, Spectral Analysis (Heave) 1.200 1.000 [RAO,JONSWAP]/peak, Response 0.800 RAO 0.600 JONSWAP Response 0.400 0.200 0.000 0 0.5 1 1.5 -0.200 w (rad/s) Figure 37: 10 year, 22.5° heading heave spectral analysis 100 Year, 22.5 Degree, Spectral Analysis (Heave) 1.200 [RAO,JONSWAP]/peak, Response 1.000 0.800 RAO 0.600 JONSWAP Response 0.400 0.200 0.000 0 0.5 1 1.5 -0.200 w (rad/s) Figure 38: 100 year, 22.5° heading heave spectral analysis
  46. 46. OCEN 407 Design Class Team Malaysia 41 10 Year, 0 Degree, Spectral Analysis (Pitch) [RAO,JONSWAP]/peak, Response 1.200 1.000 0.800 RAO 0.600 JONSWAP 0.400 Response 0.200 0.000 0 0.5 1 1.5 -0.200 w (rad/s) Figure 39: 10 year, 0° heading pitch/roll spectral analysis 100 Year, 0 Degree, Spectral Analysis (Pitch) 1.200 [RAO,JONSWAP]/peak, Response 1.000 0.800 RAO 0.600 JONSWAP Response 0.400 0.200 0.000 0 0.5 1 1.5 -0.200 w (rad/s) Figure 40: 100 year, 0° heading pitch/roll spectral analysisThe final max responses compared to the recommended maximum values can be seen in Table 4and are well within the maximum values recommended by ABS. Table 4: Actual Hull Response and Recommended Values Actual Max Recommended Max Heave 10 Year Conditions +/- 8.91 ft +/- 16 ft Heave 100 Year Conditions +/- 12.57 ft +/- 16 ft Pitch/Roll 10 Year Conditions +/- 2.49 ft +/- 4 ft Pitch/Roll 100 Year Conditions +/- 4.26 ft +/- 10 ft
  47. 47. OCEN 407 Design Class Team Malaysia 42Strength and Structural Design - GeneralThe shear and moment diagrams due to the applied forces are shown in Figure 41 and Figure 42,respectively. Figure 41: Shear Diagram Figure 42: Bending Moment DiagramFrom the shear and moment diagrams and tables, the deflections, moments, and stresses of thetopside beams, pontoons, and columns for both cases are shown in Table 5. Table 5: Deflections, Moments, and Stresses of Structure Calculated Stresses from ABS Deflections Moments Stresses Guidelines 4.37x106 kip-ft Constant Topside 1.16 in. (downward) 29.51 ksi 29.94 ksi Draft 6 Columns 0.04 in. (outward) 13.6x10 kip-ft 23.6 ksi 27.8 ksi 6 Pontoon 0.76 in. (upward) 5.30x10 kip-ft 29.76 ksi 29.94 ksi 6 Topside 1.17 in. (downward) 4.62x10 kip-ft 29.88 ksi 29.94 ksi Wave Static Columns 0.05 in. (outward) 13.8x106 kip-ft 23.7 ksi 27.8 ksi Pontoon 0.81 in. (upward) 5.59x106 kip-ft 29.92 ksi 29.94 ksi
  48. 48. OCEN 407 Design Class Team Malaysia 43The deflections are small enough to not cause any damage, and should not cause any motiondiscomfort. The stresses caused by the forces acting on the hull fall within the ABS code. Thethickness of 1 inch chosen for the hull is a good value to give small deflections and to keep thestresses within ABS recommendations, but could possibly be reduced to help with reducingmoments and stresses, along with cost efficiency. Also, the stresses are very close to therecommended values, which could cause buckling in the beams.MooringWhen all required data is entered into GMOOR it can generate a plan view or a 3D view of theinputted mooring system. Figure 43 shows the plan view for the twelve leg taut and semi-tautconfigurations, the lines are positioned to 30 degrees from horizontal with 15 degrees betweeneach line. Figure 43: 12 Leg SpreadFigure 44 shows the plan view for the sixteen leg taut and semi-taut configurations, the lines arepositioned to 30 degrees from horizontal with 15 degrees between each line
  49. 49. OCEN 407 Design Class Team Malaysia 44 Figure 44: 16 Leg SpreadFigure 45 shows the results of the tests ran in GMOOR for each mooring configuration. Thefigure compares the minimum factor of safety for intact and damaged conditions under survivalstorm conditions with the API guidelines. It also compares the offset of the platform as percentof water depth for operational, survival and damaged survival conditions to the recommendedguidelines. 7.00 7% Max Offset 6.00 5% Max Offset 5.00 12 Leg Taut 4.00 1.67 Min Damaged FOS 1.25 Min Damaged FOS 12 Leg Semi -Taut 3.00 16 Leg Taut 16 Leg Semi -Taut 2.00 1.00 0.00 Min FOS Intact Min FOS Max Offset Max Offset Max Offset Damaged Operational (% Survival (% WD) Damaged (% WD) WD) Figure 45: Mooring Analysis Results
  50. 50. OCEN 407 Design Class Team Malaysia 45For each of the designs the cost was computed using the different line costs as $3.20 per poundfor polyester mooring line, the jacketed spiral costs $2.07 per pound and the chain costs $1.40per pound. The cost of equipment (chain jacks, fairleads etc.) was $450,000 per line. Figure 46reflects the cost of each mooring configuration for line material costs and equipment costs,however it does not represent the installation costs. Mooring Line Costs $14,000,000.00 $12,000,000.00 Total Cost in US Dollars $10,000,000.00 $8,000,000.00 $6,000,000.00 $4,000,000.00 $2,000,000.00 $0.00 12 Leg Taut 12 Leg Semi-Taut 16 Leg Taut 16 Leg Semi-Taut Design Type Figure 46: Mooring Material and Equipment CostsAfter careful comparison of the different mooring designs it was decided that the twelve leg tautmooring system would be the best option. This conclusion was developed based on the fact thatthe twelve leg taut design while not having the best factor of safeties, it does have values wellabove the recommended minimum. Also the twelve leg taut design does have a good offsetdistance it is loose enough to not cause the response to be to rigid while it is tight enough that itdoesn’t get too close to recommended max offset. The price of the mooring design also makesthis the most cost effective choice. Figure 28 is a 3D drawing of the mooring system created byGMOOR. The 12 leg taut system consists of 200 feet of 2.75 inch diameter K4 Studless chain forthe anchor, 7350 feet of 3.94 inch Marlowpoly polyester rope, and 300 feet of 3.0 inch K4Studless chain for the fairlead. The extra diameter of the chain at the fairlead is to compensatefor the extra fatigue generated at the fairlead. The diameters of these chains reflect the addeddiameter for corrosion allowance as specified by API 2SK guidelines which is a range of 0.2 to0.4 millimeters per service year. It was decided to be a little conservative in the corrosionallowance so a value of 0.3 millimeter per service year was chosen resulting in an increased of0.25 inches in diameter for the 20 design life in this project. The tests were performed withoutthe additional corrosion allowance as suggested by API 2SK. The 300 feet of chain at thefairlead allows for the platform to offset in any direction up to 150 feet drilling purposes, at themaximum of 150 feet it was found that the minimum factor of safety in the 10 year storm
  51. 51. OCEN 407 Design Class Team Malaysia 46condition is 2.63 intact and 1.94 damaged which meets API guidelines. The total cost of thisdesign is approximately $7.2 million, which includes materials and equipment but notinstallation costs. Figure 47 shows the 3D rendering created by GMOOR of the chosen 12 legtaut leg mooring system. Figure 47: Chosen 12-leg Taut Mooring DesignFigure 48 shows the final 12 leg taut mooring system design, the final component diametersincluding corrosion allowances and component locations. Figure 48: Final Mooring Design
  52. 52. OCEN 407 Design Class Team Malaysia 47After designing the mooring configuration the type and size of anchor needed to be determined.The two options available for a taut leg mooring system are suction piles and vertically loadeddrag embedment anchors. For the vertically loaded drag embedment anchor the VryhofStevmanta anchor was chosen because the information for sizing was available. Using theVryhof Anchor Manual and the tension at the anchor found from GMOOR for the chosenmooring design the necessary size of the Stevmanta anchor was found to be 11.36 tons. Fordesigning the suction pile InterMoor volunteered to size the anchor base on the tension loadcomputed in GMOOR. The result was a suction pile 56 feet long with an outside diameter of 6feet and a wall thickness of 1.65 in. and a top thickness of 5.5 in. The weight of this anchor is75.5 tons. Because installation and manufacturing costs for both anchors was not available thedecision of which anchor to be used had to be based off the material costs. The steel cost of oneStevmanta anchor is approximately $51,000 (USD) and the steel cost of one suction pile isapproximately $340,000 (USD). Based on the drastic difference in price the undeniably mostcost effective solution was the Stevmanta vertically loaded drag embedment anchor. The steelcost for 12 of these anchors was only $612,000 (USD) approximately.CostThe final mooring line cost with associated equipment for the chosen 12-leg taut system can beseen in Figure 49. Mooring Line Costs $14,000,000.00 $12,000,000.00 Total Cost in US Dollars $10,000,000.00 $8,000,000.00 $6,000,000.00 $4,000,000.00 $2,000,000.00 $0.00 12 Leg Taut 12 Leg Semi-Taut 16 Leg Taut 16 Leg Semi-Taut Design Type Figure 49: Mooring Cost SummaryThe Stevmanta anchors chosen were priced at $51,000 (USD) a piece, running a total capital costof $612,000 (USD). Final hull dimensions with approximate densities and $12,000 per ton, costapproximately $184,000,000 (USD) capital. The total capital cost was approximately$192,000,000 (USD).
  53. 53. OCEN 407 Design Class Team Malaysia 48ConclusionAll of the following objectives of the chosen competencies have been met in excess of minimumrecommendations stipulated by pertinent regulatory agencies. • Drafts & Freeboard o A maximum float-on float-off draft of 29.52 ft. determined by Dockwise boat capacity. o A minimum operational freeboard (air gap) of 35 ft. based on metocean data. • Hydrodynamic responses o A minimum natural heave and pitch/roll period of 20 seconds based on client requests for optimum operation of topside separation tanks and risers. o A maximum of +/-16 ft heave response based on ABS recommendations. o A maximum 4◦ pitch/roll for 10 year storm conditions and a maximum 10◦ pitch/roll for 100 year storm conditions based on ABS recommendations. • Large Angle Intact Stability o Righting Arm should be greater than 2 X the heeling arm at the down flooding angle. o Area ratio for a non-ship shaped floating structure should be greater than 1.3. • Large Angle Damaged Stability o There should be a distance greater than 7 degrees between the first intercept of the righting and heeling arm and the down flooding angle. • Structural Stress Allowances o Maximum topside stress of 29.94 ksi o Maximum column stress of 27.8 ksi o Maximum pontoon stress of 29.94 ksi • Mooring o Dynamic intact mooring analysis factor of safety should be greater than 1.67 as per API codes. o Dynamic damaged mooring analysis factor of safety should be greater than 1.25 as per API codes. o Pretension stress for semi-taut and taut-leg mooring systems should not exceed 20% of the breaking strength. o Platform offset for intact mooring system during operations should not exceed 5% of the water depth. o Platform offset for intact mooring system during survival mode should not exceed 7% of the water depth. o Platform offset for damaged mooring system should not exceed 7% of the water depth. o Platform must be able to move 150 feet off center in any direction for drilling purposes. • Cost o Cost should be minimized while meeting all other objectives.
  54. 54. OCEN 407 Design Class Team Malaysia 49For the eight aforementioned competencies: 1. General Arrangement and Overall Hull Design 2. Wind and Current Loading 3. Local and Global Loading 4. Weight, Buoyancy and Stability 5. Hydrodynamics of Motions and Loading 6. General Strength and Structural Design 7. Mooring 8. CostThe general hull design had columns heights larger than would be expected. The governingobjective forcing the columns higher was the location of the modeled down flooding pointsinstead of the expected minimum freeboard. Further StabCad analysis is suggested to confirmthis. If indeed the down flooding angle is the governing factor, the down flooding points shouldbe moved up to the topside deck or above to reduce column height. A reduction of columnheight in either case will allow a reduction in required pontoon and node sizes further,significantly decreasing capital cost.Sloshing analysis at the natural heave and pitch/roll periods for the tank size should becompleted to see how sloshing could effect hull motions before partially filled tanks are acceptedfor long-term ballasting and trimming design. If sloshing proves to be an issue, tanks should befilled as full as possible, or fitted with floating-top tanks.A significant variable in cost for anchors is in installation. Installation costs could easily swingthe chosen anchor design from Stevmanta to SEPLAs. There is also a discrepancy betweenindustry review and product recommendations as to whether drag embedment anchors such asStevmantas are ideal for a taut-leg mooring system or not. Some suggest that they are ill-fitteddue to a lack of precision placement and the SEPLAs would be a better choice. Because of theirsuction embedment, however, SEPLAs are expected to run a higher installation cost.Clarification as to the precision placement capabilities of Stevmanta anchors and the associatedinstallation costs for the three different types of anchors analyzed (Suction Piles, Stevmanta andSEPLAs) need to be completed before placement.
  55. 55. OCEN 407 Design Class Team Malaysia 50ReferencesAmerican Bureau of Shipping (ABS) Guide for Building and Classing Facilities on OffshoreInstallations, Houston, TX. 2000American Bureau of Shipping. Guide for Building and Classing Floating ProductionInstallations, Houston, TX. 2004American Bureau of Shipping. Rules for Building and Classing Mobile Offshore Drilling Units,Houston, TX. 2004American Bureau of Shipping. Rules for Building and Classing Steel Vessels, Houston, TX.2005.American Petroleum Institute (API). Interim Guidance for Gulf of Mexico MODU DesignPractice- 2006 Hurricane Season (API RP95F), Washington D.C. 2006American Petroleum Institute (API). Recommended Practice for Design and Analysis of StationKeeping Systems for Floating Structures, First Edition. Washington D.C., June 1995. (API 2SK)AutoDesk, Inc. AutoCAD Software, 2004Computers and Structures, Inc., ETABS, Nonlinear Version 9.0.5, 2005Global Maritime Consultancy, Ltd. Gmoor32, Version 9.406c, 2001Gunter and Associates, Inc. StabCAD User’s Manual, 1999.
  56. 56. OCEN 407 Design Class Team Malaysia 51Appendix A: Hydrodynamics of Motions and LoadingThe following spreadsheet was used to take given data, hull dimension changes and estimateddensities and weights to process some of the required hydrodynamic properties of the semi-submersible. Design criterion being monitored per design iteration can be seen at the top of thespreadsheet below.
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  60. 60. OCEN 407 Design Class Team Malaysia 55Appendix B: BallastingThe following spreadsheets give examples of design processes in which varied centers of topsidegravity location are tested versus freeboard, hydrodynamic responses, small angle stability,maximum float-on draft and hull ability to counter-ballast offset center of gravity. The topsidecenter of gravity can be seen in the white cells on the left and a partially filled ballasting tank issignified by the blue cells in the plan view of the tank arrangement diagram. Percentage that anindividual tank is filled is labeled on that individual tank and riser and mooring tensions are zeroin a float-on, float-off scenario. Also included in this appendix is the table used to calculatemoment arms used in ballasting.
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  63. 63. OCEN 407 Design Class Team Malaysia 58Appendix C: Environmental LoadsThe following spreadsheets were used in conjunction with shape and height coefficients as perregulation to calculate concurrent wind, current and mean wave drift environmental loads on thesemi-submersible.
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