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Manual - DeepSea Power & Light

1. Copies Number of copies i Pages ker i 1 ju Kl S Collate t Selection Ge All Cancel Windows NT and 98 Print Screen Printer Default Printer HP LaserJet AMW on MWDeep sea Tihp Amv que Print range Cancel DC an Setup C Selection s Pages Print quality Jeng dpi Copies Print to file Collate copies Windows 95 Print Screen The top selection specifies what printer you want to print to similar to if you had selected the Print Setup dialog box You can specify the number of copies that you want to generate and also specify Print to file more on that later Clicking on the OK button will start the generation of the printout It will vary in number of pages depending on the type of analysis that 1s being printed Another way to quickly print the results to the printer 1s to simply depress the Report button that appears on the Analysis form next to the Done button Pressing this button will force an immediate print of the analysis to your default printer Note Whenever you either print or copy the report all the values are recalculated and any error or warning messages will be repeated DeepSea Power amp Light 72 Rev 3 27 01 Under Pressure Version 4 0 User Manual In this case the information that was generated in the report appears on the following page Urider Pressure Wer 05 15 52 23 107 117 1998 TUBE C
2. Ks Ft sea Stress Ksi Stress Ksi Stress Ksi 1 0000 2248 8 0 0000 9 5899 4 0791 2 0000 4490 9 0 0000 19 180 8 1582 3 0000 6726 2 0 0000 28 770 12 237 3 6497 fail 8174 8 0 0000 39 000 14 587 4 0000 fail 16 316 5 0000 fail 20 396 6 0000 fail 24 475 7 0000 fail 15601 Um 67 129 128 554 8 0000 fail 32 633 LR DeepSea Power amp Light E 35 Rev 3 27 01 Under Pressure Version 4 0 User Manual Clicking on Graph gives the following im Flat Annular Endcap Graph Stress us Radial Location for 1 Ksi pressure Radial Tangential 1 Maximum Radial Stress 6346 psi Location 2 796 diameter 2 Maximum Tangential Stress 9590 psi Location 1 000 diameter hole diameter Finite Element Method graphical stress results FEA model element mesh pressure loading B C s from eann7mod bmp Radial stress contour eann7rad bmp Tangential stress contour eann7tan bmp 1 Maximum Radial Stress 6777 psi Location see stress contour 2 Maximum Tangential Stress 7694 psi Location 1 000 diameter DeepSea Power amp Light E 36 Rev 3 27 01 Under Pressure Ve 25 000 Free Diameter 2 000 IA KELL A AE eke E exe 41 000 Center Hole Diameter ANSYS 5 3 AUG 1 1997 11 48 07 NODAL SOLUTION STEP 1 SUB 1 TIME 1 SX AVG RSys 0 DMX 001218 SMN 6777 SMNB 22612 SMX 5777 gGMXB22612 r 5777 i SO 3 2765 cp mu WS
3. weight m Waler WI 4 7523 Fail value units p i Units Pressure Depth Stress Linear Deflection Angle Deflection Units fiba psi Ft sea psi Inches e radians Pressure Depth Max Meridional Max Hoop MaxEquiv Max Shear psi Ettel 1 Maximum Meridional Stress 2360 1 psi 2 Maximum Hoop Stress 2360 1 psi Finite Element Method graphical stress results FEA model element mesh pressure loading from espherelmod bmp Meridional stress contour espherelmer bmp Maximum Meridional Stress 2354 psi Discussion Test Aluminum fs 35000 psi Under Pressure based on the formulas given in Appendix C and the sphere finite element model provide nearly identical results for peak meridional stress in the spherical housing Appendix D defines the orientation of the meridional stresses in the walls of the spherical shell For this exercise a mesh of four quadrilateral elements across the spherical shell wall thickness was selected for the finite element model A uniform pressure of 1000 psi was applied along the outside radius The finite element stress contours indicates that the compressive meridional stress in the spherical shell varies from 1858 psi compressive stress at the sphere outer surface to a peak 2354 psi compressive stress at the sphere inner surface DeepSea Power amp Light E 7 Rev 3 27 01 Under Pressure Version 4 0 User Manual
4. ANSYS m3 AUG 1 1997 10 43 01 NODAL SOLUTION STEF 1 SUB 1 FLAT ANNULAR ENDCAP ANALYSIS 6 TAN TIME 1 eann6tan bmp _ AVG DME 004447 SMN 1l2013 SMNB 22675 LA LA LA tn DeepSea Power amp Light E 33 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 34 Rev 3 27 01 Under Pressure Version 4 0 User Manual Case 7 Plate Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Center Hole Diameter 1 00 Simply Supported Outer Edge Restraint Simply Supported Inner Center Hole Edge Restraint Plate cross section with applied pressure B C s eann7 bmp Under Pressure numerical stress results E Flat Annular Endcap Analysis External Pressure UI Fa Pressure Range 1000 20000 psi m M Graph Heport Done Theoretical Failure Material CH Radial moment failure at 5 5152 Ksi Dia 2 7959 inches Test Aluminum Go Tangential moment failure at 3 6497 Ksi Dia 1 0000 inches C Shear stress failure at 4 2901 Kai Dia 1 0000 inches C Seat failure at 10 694 Ka a Fail value units Table eval dia De finches 11 0000 Hetaie ksi E Units eld Strength 35000 psi Weight Ai wt 1 7181 Pressure Depth Stress Linear Detection Angle Deflection Water wk T 0817 ksi P sea ksi sl Inches sl Fradians sl Units fibs sl Pressure Deph De Radial e Tangential De Shear
5. Material Database Dialog Box Select Analysis Units Click on either the English or Metric Option Button depending on the user s preference Note you must switch to another analysis type or exit and reenter the Under Pressure program for this change to take effect Select Pressure Orientation Click on either the Internal or External Option Button Internal option should be used when the magnitude of the applied pressure is greatest on the interior walls of the enclosed pressure vessel External option should be used when the magnitude of the applied pressure is greatest on the exterior walls of the enclosed pressure vessel Examples of Internal Pressure Vessels Boilers Reactors Hyperbaric Chambers Compressors Gas Storage Scuba Tanks Steam Generators Pumps Piping Valves and other equipment used in energy systems chemical processing plants etc Examples of External Pressure Vessels DeepSea Power amp Light 7 Rev 3 27 01 Under Pressure Version 4 0 User Manual Submerged Housings Vacuum Chambers Hyperbaric Chambers High Altitude Chambers Select Analysis Options Click on the Force Thick Wall Equations check box if the user desires to force the use of thick wall equations for stress of analysis of tubes spheres and hemispheres in lieu of thin wall equations Thick wall equations can be used for all ratios of mean shell wall radius to shell wall thickness Thin wall equations are only recomme
6. Ultimate Strength Working Strength DeepSea Power amp Light 35 Rev 3 27 01 Under Pressure Version 4 0 User Manual Young s Modulus Density Poisson s Ratio The All Main Category allows the user to view all materials in all Main Categories at once The All Main Category defaults to material properties for the Metals Main Category SUB CATEGORIES The Sub Category parameter allows the user to further organize materials that fall into the same Main Category Under Pressure comes with the following Sub Categories Main Category Ceramics Sub Categories All Alumina Silicon Carbide Main Category Glass Sub Categories All Glass Main Category Metals Sub Categories All Aluminum Nickel Stainless Steel Steel Titanium Main Category Plastics Sub Categories All Composites Thermoplastics NAME The Name parameter designates the specific material alloy or composition MATERIAL DATABASE Under Pressure comes with the following materials database where the following abbreviations are used U S T Ultimate Strength tensile U S C Ultimate Strength compressive Y M Young s Modulus Den Density P R Poisson s Ratio Y S Yield Strength U S Ultimate Strength W S Working Strength DeepSea Power amp Light 36 Rev 3 27 01 Under Pressure Version 4 0 User Manual Main Category Ceramics Sub Cat Name U S T U S C Y M Den Ksi Ksi Mpsi b in Sapphire Silicon Silico
7. Click the Analysis Options Force Thick Wall Equations Check Box Select Analysis Type Tube by clicking on the scroll arrow and clicking on Tube The Under Pressure Application Window should appear as follows DeepSea Power amp Light 13 Rev 3 27 01 Under Pressure Version 4 0 User Manual i a Under Pressure Biel x EXAMPLE1 PRJ Project Parameters Project Description aluminum alloy cylindrical housing for 4500 psi external Pressure service Design Parameters Maternal ALUMINUM 6061 T 6 Choose Units Pressure Analysis Options Ce English Internal C Metric Ge External T Use Working Strength for Plastic Analys z Type Tube Enter Geometry EXAMPLE 1 APPLICATION WINDOW Click on Enter Geometry to open the Geometry Dialog Box Use the cursor and keyboard to enter 6 00 inches for Tube I D Estimate the appropriate Tube O D or Wall thickness and enter this corresponding value using the cursor and keyboard Use the cursor and keyboard to enter 24 00 inches for Tube length Click the Maintain I D constant Option button given that the 6 00 inch Tube I D is a fixed constraint for this particular example Click on Perform Analysis to generate analysis results Review the analysis results in the Analysis Dialog Box for this example a minimum safety factor of 2 0 was desired on buckling and stress for a design pressure of 4500 psi Therefore the Theoretical Failure portion of the Analysis Dialog Bo
8. Clicking on Cancel closes the Flat Circular Endcap Geometry Dialog Box without saving user inputs Clicking on Perform Analysis analyzes the Flat Circular Endcap geometry and opens the Flat Circular Endcap Analysis Dialog Box Flat Circular Endcap Formulas Formulas used for Flat Circular Endcap stress analysis are presented in APPENDIX C FORMULAS USED BY UNDER PRESSURE Flat Circular Endcap Formula Assumptions DeepSea Power amp Light 66 Rev 3 27 01 Under Pressure Version 4 0 User Manual Stress analysis formulas assume that the plate is flat and has a constant thickness The ratio of the Plate Free Diameter to the Plate Thickness is greater than or equal to 4 If this assumption is violated the results of the analysis may not be valid and the following warning will appear The maximum deflection of the plate does not exceed one half the plate thickness If this assumption is violated the results of the analysis may not be valid and the following warning will appear Maximum plate deflection exceeds half the thickness Analysis results may not be valid for all pressures in the table Flat Circular Endcap Analysis Results The following Flat Circular Endcap Analysis Dialog Box from Example 2 of this manual will be used to highlight the data and options available to the user after an analysis has been performed DeepSea Power amp Light 67 Rev 3 27 01 Under Pressure Version 4 0 User Manual ds U
9. Max Equiv Stress Maximum uniaxial stress that is equivalent to the three dimensional stress state that exists in the hemisphere wall for predicting failure of ductile materials by comparison to the uniaxial yield strength Max Shear Stress Maximum Shear Stress in hemisphere wall N A for external pressure Avg Seat Stress Average bearing Stress on flat annular area at hemisphere equator dID displacement of hemisphere Inner Diameter dOD displacement of hemisphere Outer Diameter An explanation of the orientation of the above stresses is provided in Appendix D PRESSURE VESSEL STRESSES Again the user has an option as to which units will be used to display the data in the results table Rows of data for an applied pressures at or greater than the calculated failure pressure are highlighted by the program to warn the user As discussed in Appendix C FORMULAS USED BY UNDER PRESSURE Maximum Equivalent Stress is used as a failure criteria for Metal Hemispherical Endcaps and is not applicable to hemispheres fabricated from other Main Category Materials Ceramics Glass and Plastics FLAT CIRCULAR ENDCAP ANALYSIS Flat Circular Endcap Edge Restraint Options The significance of Edge Restraint Options Simply Supported or Fixed for Flat Circular Plates 1s defined in APPENDIX B FLAT ENDCAP BOUNDARY CONDITIONS In practical application the edge restraint of a flat circular plate is not likely to be purely simply supported or purely fixed
10. Under Pressure Version 4 0 User Manual DeepSea Power amp Light B 4 Rev 3 27 01 Under Pressure Version 4 0 User Manual APPENDIX C FORMULAS USED BY UNDER PRESSURE All formulas are based on Roark s Formulas for Stress amp Strain Sixth Edition by Warren C Young McGraw Hill Inc 1989 TUBE Thin wall stress formulas Table 28 case Ic pg 519 Thick wall stress formulas Table 32 case la ld pgs 638 639 Thin wall buckling formulas Table 35 case 20 pg 690 SPHERE Thin wall stress formulas Table 28 case 3a pg 523 Thick wall stress formulas Table 32 case 2a 2b pg 640 Thin wall buckling formulas Table 35 case 22 pg 691 FLAT ANNULAR ENDCAP Stress Formulas Table 24 case la 11 2a l pgs 398 408 CONICAL ENDCAP Thin wall stress formulas Table 28 case 2a pg 520 Thin wall buckling formulas see Table 23 case 23 pg 691 for approximate formula for truncated cones with closed ends not part of Under Pressure HEMISPHERICAL ENDCAP Thin wall stress formulas Table 28 case 3a pg 523 Thick wall stress formulas Table 32 case 2a 2b pg 640 Thin wall buckling formulas Table 35 case 22 pg 691 FLAT CIRCULAR ENDCAP Stress Formulas Table 24 case 10a 10b pg 429 FAILURE CRITERIA Failure criteria formulas used are dependent on Material Main category Analysis Type pressure vessel geometry Material Main Category Analysis Type Criteria INE Coramics TUDU EE A 2 lass
11. az AVG RESYazu DMS 011315 SMH 2 523131 SMMBEB 6B8341 Shit 531851 gMXBE 69341 531481 I LP ud el ie Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 46 Rev 3 27 01 Under Pressure Version 4 0 User Manual Case 10 Plate Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Center Hole Diameter 1 00 Guided Outer Edge Restraint Fixed Inner Center Hole Edge Restraint Plate cross section with applied pressure B C s eann10 bmp Under Pressure numerical stress results E Flat Annular Endcap Analysis External Pressure Pressure Range 2000 psi psi Graph Report Done Theoretical Failure Material Geh Radial moment failure at 778 61 psi Dia 1 0000 inches Test Aluminum CH Tangential moment Failure at 2272 2 psi Dia 1 2448 inches O Shear stress failure at 1750 0 psi Dia 1 0000 inches CH Seat failure at 10694 psi Pub Table eval dia De inches 1 0000 G lale psi Units Yield Strength 35000 psi Weight Air wt 1 181 Pressure Depth Stress Linear Deflection Angle Deflection Water wt 1 0817 psi sl Ft sea sl psi sl Inches sl Degrees sl Units libs Pressure Depth De Radial De Tangential DeShear psi fie Stess psi Stress pi Stress psi 225 13 4495 2 1348 6 450 31 8990 4 2697 1 675 37 13486 4045 7 300 35 17981 5394 2 al 1125
12. 10221 133308 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 14 Rev 3 27 01 Under Pressure Version 4 0 User Manual Case 2 Plate Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Center Hole Diameter 1 00 Fixed Outer Edge Restraint Guided Inner Center Hole Edge Restraint Plate cross section with applied pressure B C s eann2 bmp Under Pressure numerical stress results E Flat Annular Endcap Analysis External Pressure Iof SI Pressure Range 1000 20000 psi o ro sl Graph Report Done Theoretical Failure Material Geh Radial moment failure at 3 0392 Ksi Dia 5 0000 inches Test Aluminum C Tangential moment failure at 6 5493 Ksi Dia 1 7347 inches CH Shear stress failure at 8 7500 Ksi Dia 5 0000 inches CH Seat failure at 10 694 Ka A Fail value units Table eval dia De inches 5 0000 Realt ksi D Units Pressure Depth Stress Linear Deflection Angle Deflecton Yield Strength 35000 psi Weight Ar wt 1 181 Water wt 1 0817 Units ibs ue E Int sea E JS Inches Fradians Pressure De e Radia De Tangential De Shear Stress Ksi Stress Ksi Stress Ksi 11 520 3 4560 2 0000 23 040 6 9120 4 0000 S 34_560 10 368 6 0000 3 0382 fa 6811 4 35 000 10 500 6 0764 4 0000 fail 8 0000 5 0000 fail 10 000 6 0000 Fail 12 000 7 0000
13. 752 965 se 752 9565 um 2259 3765 S231 6777 DeepSea Power amp Light FLAT ANNULAR ENDCAP ANALYSIS 7 DWG eann7 bmp FLAT ANNULAR ENDCAP ANALYSIS 7 MOD eann7mod bmp FLAT ANNULAR ENDCAP ANALYSIS 7 RAD eann7rad bmp FLAT ANNULAR ENDCAP ANALYSIS 7 TAN eann7tan bmp 6275 Thickness ANSYS 5 2 AUG 1 1537 11 46 24 ELEMENTS TYPE NUM Tl To FRE kel aw DIST 1 505 XF 1 047 YE 31235 ANSYS 5 3 AUG 1 1597 11 45 05 NODAL SOLUTION STE P 1 SUB 1 TIME 1 B AVG RSYs 0 DMX 001218 SMN 7694 SMNB 22612 SMX 7694 SMXB 22612 a 7594 5584 4275 e 2565 ee 854 911 854 911 Tag 2565 Ex 4275 i em 5384 7694 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 38 Rev 3 27 01 Under Pressure Version 4 0 User Manual Case 8 Plate Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Center Hole Diameter 1 00 Simply Supported Outer Edge Restraint Fixed Inner Center Hole Edge Restraint Plate cross section with applied pressure B C s eann8 bmp Under Pressure numerical stress results E Flat Annular Endcap Analysis External Pressure UI X Pressure Range f 000 20000 psi Ba T sl Theoretical Failure Geh Radial moment failure at 2 5133 Kei Dia 1 0000 inches CH Tangential moment failure at 8 0647 Ksi Dia 1 0876 inches O Shear stress
14. D D D D D D T Li The ratio of pressure vessel principal radius to wall thickness is lt 10 analysis results map nat be valid Calculation of average seat stress results for a conical endcap assume that the open end of the cone is supported with axial edge support see conical endcap figure of Appendix D Calculation of meridional and hoop membrane stress results for a conical endcap assume that the open end of the cone is supported with tangential edge support see support of conical endcap FEA model econelhoop mod in Appendix E Conical Endcap Analysis Results DeepSea Power amp Light 58 Rev 3 27 01 Under Pressure Version 4 0 User Manual The following Conical Endcap Analysis Dialog Box will be used to highlight the data and options available to the user after an analysis has been performed DeepSea Power amp Light 59 Rev 3 27 01 Under Pressure Version 4 0 E Conical Endcap Analysis External Pressure Pressure Range 1000 20000 psi E E Theoretical Failure C Thin all Buckling H A Geh Shell Failure at 7530 1 psi Thin wall eqs O Seat failure at 17143 psi CA Shear failure NA Units Pressure Depth psi P sea l Inches Degrees Depth Max Meridional MaxHoop Max Equiv Pressure Stress pa Ftisea Stess psi 630_1 Fail E000_0 Fail CONICAL ENDCAP ANALYSIS DIALOG BOX EXAMPLE 2248 8 4430 3 6726 2 0354 8 11177 13332 15601
15. 1 Maximum Radial Stress 12 672 psi Location 2 225 diameter 2 Maximum Tangential Stress 39 936 psi Location 1 000 diameter Finite Element Method graphical stress results FEA model element mesh pressure loading B C s from eannSmod bmp Radial stress contour eann5rad bmp Tangential stress contour eannStan bmp 1 Maximum Radial Stress 12 328 psi Location see stress contour 2 Maximum Tangential Stress 35 963 psi Location 1 000 diameter DeepSea Power amp Light E 28 Rev 3 27 01 Under Pressure Vers 25 000 Free Diameter 2 200 ULL UL T gem TOCA oi Uu Center Hole Diameter FLAT ANNULAR ENDCAP ANALYSIS 5 DWG eann5 bmp ANBYS 5 3 AUS 1 1537 11 36 11 ELEMENTS TYEE NUM FLAT ANNULAR ENDCAP ANALYSIS 5 MOD eann5mod bmp PRES ANSYS 5 3 Zu 1 AUG 1 1997 SANE 1 208 dum SE L on F _3125 NODAL SOLUTION STEP 1 SUB 1 n a m FLAT ANNULAR ENDCAP ANALYSIS 5 RAD RSYS 0 eann5rad bmp ANSYS 5 3 DMX 014097 AUG 1 1997 SMN 12328 11 38 38 SMNB 13663 NODAL SOLUTION SMX 12328 STEP 1 SMXB 13663 SUB 1 E 222e TIME 1 Em 7 SE AVG Em 5823 RSYS 0 E 0 DMX 014097 1370 FLAT ANNULAR ENDCAP ANALYSIS 5 TAN SMN 35963 pm 1370 eann5tan bmp GMNB 36142 om 6849 SMXB 36142 Em gt gt 88 wm 0 12328 ES 27371 Em 13273 11388 3996 rui 3996 11988 19979 Em 27271 35963 DeepSea Power amp Light E 29 Rev 3 27 01 Under Pressure Version 4 0 U
16. 1 1997 i 12 07 44 ELEMENTS TYPE NUM IT FLAT ANNULAR ENDCAP ANALYSIS 11 MOD BEES eann11mod bmp zv sl DIST 1 508 XE 1 047 0 ep 3125 AUG 1 1997 12 09 17 NODAL SOLUTION STEP 1 SUB TIME 1 FLAT ANNULAR ENDCAP ANALYSIS 11 RAD SX AVG eannllrad bmp e ANSYS 5 3 DMX 2 023817 3 SMN 12444 C EE SMNB 61741 Eam SMZ 12444 GE SMXB 61741 Se em 77 EE DS LAMG EH FLAT ANNULAR ENDCAP ANALYSIS 11 TAN pavs n EM eann11tan bmp DS 023817 mm ie SMN 8085T8 ak SMNB 87099 EB 513 SME 20678 EM SMXB B7089 EH 2444 om C ms 2743 mm 10821 EN Emm 559 e964 EN mm 3 mm 12221 52749 ROGTS DeepSea Power amp Light E 53 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 54 Rev 3 27 01 Under Pressure Version 4 0 User Manual Case 12 Plate Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Center Hole Diameter 1 00 Free Outer Edge Restraint Fixed Inner Center Hole Edge Restraint Plate cross section with applied pressure B C s eann12 bmp Under Pressure numerical stress results Flat Annular Endcap Analysis External Pressure Pressure Range 100 2000 psi sl DE sl Graph Report Done Theoretical Failure Material i D Radial moment failure at 594 23 psi Dia 1 0000 inches Test Aluminum Tangential moment Failure at 1610 1 psi Dia 1 4082 inches CA Shear stress failure at 1750 0 psi Dia 1 0000 i
17. 3 22476 6742 8 1350 1 26971 8091 3 1574 9 31466 9439 9 778 61 fail 1751 6 35000 10500 7786 1 00 00 Fail 1733 5 39962 10788 aun 0 DeepSea Power amp Light E 47 Rev 3 27 01 Under Pressure Version 4 0 User Manual Clicking on Graph gives the following im Flat Annular Endcap Graph Stress us Radial Location for 1 Ksi pressure 7 Radial Tangential Stress Kaj 1 Maximum Radial Stress 44 952 psi Location 1 000 diameter hole diameter 2 Maximum Tangential Stress 15 403 psi Location 1 245 diameter Finite Element Method graphical stress results FEA model element mesh pressure loading B C s from eannlO0mod bmp Radial stress contour eannlOrad bmp Tangential stress contour eann lOtan bmp 1 Maximum Radial Stress 40 655 psi Location 1 000 diameter 2 Maximum Tangential Stress 25 680 psi Location see stress contour DeepSea Power amp Light E 48 Rev 3 27 01 Under Pressure V 25 000 Free Diameter 2 000 ALIA A Me Ee M 1 00J Center Hole gaere FLAT ANNULAR ENDCAP ANALYSIS 10 DWG eann10 bmp 1 FLAT ANNULAR ENDCAP ANALYSIS 10 MOD eann10mod bmp ANSYS 5 3 AUG 1 1597 La Pose A8 NODAL SOLUTION STE P 1 SUB 1 TIME 1 FLAT ANNULAR ENDCAP ANALYSIS 10 RAD eann10rad bmp AVG FLAT ANNULAR ENDCAP ANALYSIS 10 TAN eann10tan bmp DeepSea Power amp Light 525 Thickness e ANSYS 5 35 AUG 1 19
18. Application Window then click on Quit or enter Ctrl Q from the keyboard or click on the x in the upper left corner of the main Under Pressure window DeepSea Power amp Light 1 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light 12 Rev 3 27 01 Under Pressure Version 4 0 User Manual EXAMPLES Example 1 Aluminum Tube Design Requirements Aluminum Alloy Cylindrical Electronics Housing for Undersea service 4500 psi maximum external service pressure Internal diameter of 6 00 Internal length of 24 00 Minimum safety factor of 2 0 on buckling and stress shell material failure Procedure Follow the steps outlined in GETTING STARTED to set up the Under Pressure Application Window for this example Use the cursor and keyboard to enter the Project Title Project Description and Project Designer in the Project Parameters portion of Application Window Click on CHOOSE to open the Material Database Dialog Box Select Main Category Metals by clicking on the scroll arrow and clicking on Metals Select Sub Category Aluminum by clicking on the scroll arrow and clicking on Aluminum Select Name 6061 T6 as a first option for this example by clicking on scroll arrow and clicking on 6061 T6 Note 6061 T6 has a yield strength of 35 000 psi Click on Done to return to the Application Window Click the Units English Option Button Click the Pressure External Option Button
19. Dialog Box is dependent upon the pressure vessel geometry that has been analyzed Further detail on the specific information contained in the Analysis Dialog box is addressed in the section DETAILS ON ANALYSIS TYPE PRINTING THE RESULTS OF A COMPLETED PROJECT ANALYSIS Click on File on the menu bar of the Application Window then click on Print or enter Alt F P from the keyboard See the section REPORTS for more details SAVING A PROJECT Click on File on the menu bar of the Application Window then click on Save As or enter Alt F A from the keyboard to open the Save As Dialog Box DeepSea Power amp Light 10 Rev 3 27 01 Under Pressure Version 4 0 User Manual File name Folders I Cancel annularl on i 2 platel_prj 5 spherel on tubel on Save file as type Drives Project _pry j ES c X ante Save As Dialog Box In the Save As Dialog Box use the keyboard and cursor to enter a file name prj and directory and click on OK OPENING AN EXISTING PROJECT Click on File on the menu bar of the Application Window then click on Open Design or enter Ctrl O from the keyboard to open the Open Dialog Box Folders c Yupi annularl on platel pri spherel pri tubel on List files of type Drives Project 7 prj Em c Open Dialog Box Click on the desired project file name prj in the Open Dialog Box Click on OK EXITING UNDER PRESSURE Click on File on the menu bar of the
20. Dialog Box to return to the Geometry Dialog Box to iterate on the required Plate thickness until the requirements of this example aluminum alloy 7075 T6 flat circular endcap are met For aluminum alloy 7075 T6 a plate thickness of 1 28 1s found to be adequate for this example as shown by setting up the Geometry Dialog Box below al Flat Circular Endcap Simply Supported Plate Free Diameter Plate Thickness b 0000 fi sl 1 2800 i Plate Outside Diameter 6 5400 in Update Done a EXAMPLE2 GEOMETRY DIALOGBOX The Analysis Dialog Box for the geometry shown above appears as follows DeepSea Power amp Light 20 Rev 3 27 01 Under Pressure Version 4 0 User Manual ds Under Pressure File Edit Materials Window Design Options Help B Flat Circular Endcap Analysis External Pressure Pressure Hange 1000 20000 psi sl ps sl Heport Done Material ALUMINUM 7075 T6 amp Theoretical Failure Radial Stress Failure at 9038 4 psi plate center CH Tangential Stress Failure at 9038 4 psi plate center CH Seat failure at 15658 psi Yield Strength b Ks Fail value units Table eval da De plate center for Max Rad al T able eval da De plate center for Max Tangential Weight Ar wr 4 8304 Pressure Depth Stress Linear Deflecton Angle Deflection Water wt 3 0969 m sea sl i h sl Ir di Unit Ir psi psi nches Radians nite lbs Pressure De Max
21. If in doubt about which edge restraint 1s most appropriate for a given Flat Circular Endcap design the use of the simply supported edge restraint results in higher stresses in the plate and consequently is a more conservative approach for the designer to use DeepSea Power amp Light 65 Rev 3 27 01 Under Pressure Version 4 0 User Manual Flat Circular Endcap Geometry By selecting Analysis Type Endcap Only in the Application Window selecting Endcap Configuration Flat Circular selecting appropriate Edge Restraint Options and clicking on Enter Geometry the program user can access the Flat Circular Endcap Geometry Dialog Box ef Flat Circular Endcap Simply Supported Plate Free E Plate Plate Outside Diameter Ip e Update Done Perform Analysis Cancel FLAT CIRCULAR ENDCAP GEOMETRY DIALOG BOX Flat Circular Endcap geometry is defined by the variables Plate Outside Diameter Plate Free Diameter and Plate Thickness APPENDIX A PRESSURE VESSEL GEOMETRIES shows a figure of a flat circular endcap and the variables used to define its geometry After using the cursor and keyboard to define the endcap geometry a three dimensional view of the resulting flat circular endcap geometry is generated using a dashed line to denote the Plate Free Diameter on the left hand side of the Flat Circular Endcap Geometry Dialog Box Clicking on Done saves the geometry and closes the Flat Circular Endcap Geometry Dialog Box
22. Re asa ogee eee se eee sees eee ease A 5 Metals Kri B 4 Plasties Tube u u u uuu u0 0000000000 ER SEE e C Ds Coram 53 Ee Eege A Os en A T Metals S EE D 8 Plastic S SDlefe u E DeepSea Power amp Light C 1 Rev 3 27 01 Under Pressure Version 4 0 User Manual 9 Ceramics Flat Annular cee cece cece eee F 10 Glass Flat Annular 0c cece ccc ccc cc F 11 Metals Flat Annular ern G 12 Plastics Flat Annular eere H I3 Ceramics Conlcal su coercet oerterr RE PRU EIE ER Eiei DES I 14 Glass Conical eee I 15 Me tals Conlcal 2 etre rtt Er ER REFERRE ER EE J 16 Plastics C OMICal EEN K 17 Ceramce Hemspbhercal eee e ees I 18 Golass Hemspbencal 00 cece ccc cece eeeeeeeeees I 19 Metals Hemopbhencal cece eee e cece cece eens L 20 Plastcs Hemspbencal ce eeeee cece eeeeeeees M 2 Ceramics Flat Crcular irre rira re r Erain F 22 Glass Flat Circular ccc cece cece ec ee cece ees F 23 Metals Flat Crcular cee cence cee cence N 2A Plastics Elat CIrculat oe btt een A O A Maximum hoop stress compared to Ultimate Strength tensile for internal pressure loading or compared to Ultimate Strength compressive for external pressure loading B Maximum equivalent membrane stress von Mises stress constant energy of distortion stress compared to Yield Strength see theory 4 pg 26 of Roark s C Maximum hoop stress c
23. STEP 1 mm 79 SUB 1 6529 Se m FLAT ANNULAR ENDCAP ANALYSIS 2 TAN EH sos SZ AVG eann2tan bmp mm 7 DMX 2 003337 Em SMN 7256 am 77 SMNB 13320 glz SMX 7256 E sea 10965 DeepSea Power amp Light E 17 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 18 Rev 3 27 01 Under Pressure Version 4 0 User Manual Case 3 Plate Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Center Hole Diameter 1 00 Fixed Outer Edge Restraint Simply Supported Inner Center Hole Edge Restraint Plate cross section with applied pressure B C s eann3 bmp Under Pressure numerical stress results Flat Annular Endcap Analysis External Pressure Pressure Range 1000 20000 psi Bi nm Graph Report Done Theoretical Failure Material CH Radial moment failure at 6 5012 Kale 5 0000 inches Test Aluminum CH Tangential moment failure at 7 5336 Ksi Dia 1 0000 inches Geh Shear stress failure at 6 3680 Kai Dia 1 0000 inches CH Seat failure at 10 694 Ka Fail value units Table eval dia De inches 1 0000 Relate ksi eld Strength 35000 psi Weight Uni Am wt 1 7181 nits Pressure Depth Stress Linear Deflecton Angle Deflection Water wt 1 0817 ks P zea ksi sl Inches radians Pressue Deph De Radial Units Ibs sl Ee fiel Stress Kai Stress Ksi
24. Stress Ka 1 0000 2 0000 3 0000 4 0000 5 0000 6 0000 6 3660 Fail 7 0000 fail 5 0000 fail DeepSea Power amp Light 2248 8 4430 3 6726 2 8354 8 11177 13332 0 0000 0 0000 0 0000 0 0000 0 0000 0 0000 4 b453 3 2918 13 938 18 584 23 229 2f 8 5 2 7481 3 4963 9 2444 10 333 13 741 16 483 15601 0 0000 32 521 19 237 14206 0 0000 23 585 17 500 17804 0 0000 of 16 21 385 q Rev 3 27 01 Under Pressure Version 4 0 User Manual Clicking on Graph gives the following im Flat Annular Endcap Graph Stress us Radial Location for 1 Ksi pressure Radial Tangential L A a Lab GL a IM DR CL 1 Maximum Radial Stress 5384 psi Location 5 000 diameter plate free diameter 2 Maximum Tangential Stress 4646 psi Location 1 000 diameter hole diameter Finite Element Method graphical stress results FEA model element mesh pressure loading B C s from eann3mod bmp Radial stress contour eann3rad bmp Tangential stress contour eann3tan bmp 1 Maximum Radial Stress 4644 psi Location 5 000 diameter 2 Maximum Tangential Stress 4809 psi Location 1 000 diameter DeepSea Power amp Light E 20 Rev 3 27 01 Under Pressure Version 4 0 eo Free Diameter 2 O00 S ore CE ATLAS gl OOU Center Hole Diameter FLAT ANNULAR ENDCAP ANALYSIS 3 DWG eann3 bmp FLAT ANNULAR ENDCAP ANALYSIS 3 MOD eann3mo
25. Tangential moment failure at 13 849 Ksi Dia 1 0816 inches CH Shear stress failure at 4 9913 Kai Dia 1 0000 inches CH Seat failure at 10 694 Ka an Fail value units Table eval dia De inches 1 0000 Hetzatr kai Unita Pressure Depth Stress Linear Deflection Angle Deflection Yield Strength 35000 pst VW eight Am wt 1 7181 Water wt 1 0817 Units libs sl ks sl Ft sea Ir sl Inches sl Radians sl Ki Ft sea jStress Ksi iess Ksi Stress Ksi 1 0000 2248 8 8 2797 2 4839 3 5061 2 0000 4490 9 16 559 4 9678 7 0122 3 0000 6726 2 24 839 7 4517 10 518 4 0000 8954 8 33 119 9 9356 14 024 4 2272 fail an 35 000 10 500 114 821 5 0000 fail 11177 41398 12419 117 581 6 0000 Fail 49 678 14 903 21 037 7 0000 fail 15601 ETE 24 543 8 0000 Fail 28 049 BE ee 2 DeepSea Power amp Light E 23 Rev 3 27 01 Under Pressure Version 4 0 User Manual Clicking on Graph gives the following i Flat Annular Endcap Graph x Stress us Radial Location for 1 Ksi pressure 7 Radial Tangential 1 Maximum Radial Stress 8280 psi Location 1 000 diameter hole diameter 2 Maximum Tangential Stress 2527 psi Location 1 0816 diameter Finite Element Method graphical stress results FEA model element mesh pressure loading B C s from eann4mod bmp Radial stress contour eann4rad bmp
26. Yield Strength b Ksl Weight Ar wt 5 5371 Pressure Depth Stress Linear Deflection Angle Deflection Water wt 3 9054 psi Ft sea psi Inches Radians D Units libs sl Pressure Depth De Radial De Tangential DeShear ps jFt sea Stress psi Stress psi Stress psi DI 2248 8 0 0000 10319 D 4490 9 0 0000 20638 6726 2 0 0000 30958 8954 8 0 0000 41277 11177 51596 13392 51315 15601 10 0000 72234 17804 0 0000 87553 0 0000 EXAMPLE 3 ANALYSIS DIALOG BOX This analysis indicates the following results Radial Stress Failure occurs at 17 402 psi safety factor 3 87 at a diameter of 2 43 inches Tangential Stress Failure occurs at 6008 psi safety factor 1 34 at a diameter of 1 00 inches at the hole diameter Weight in air 5 54 Ib Weight in water 3 51 Ib If you scroll to the right on the horizontal scroll bar you ll find additional columns with data analysis this 1s true for nearly all data analysis screens m Under Pressure De Angular Defl HD Radial HD Tangential HD Shear HD Vert Dell H D Angular Defl Badians Stress psi Stress psi ess psi Inches Rad ans 0 00067693 0 0000 10313 0 0000 0 0013612 0 00067693 0 001 3539 0 0000 20638 0 0000 D 0033225 0 0013533 0 0020308 0 0000 30358 0 0000 D0 0058837 0 0020308 0 0027077 0 0000 41277 0 0000 D 0078450 0 0027077 0 003384 0 0000 51596 0 0000 D0 0038062 0 0033847 D
27. ccceccccccccceesccceeeeeeeeeeceeceeeeseeseaseeaseeeenseeaeges 40 electing Pressure Vessel reegen 4 Viewing All Materials in the Database at Once esses 4 Editing the Properties of an Existing Material esses 42 Ald ns N W Malt hneln erscheinen 42 DeepSea Power amp Light 1 Rev 3 27 01 Under Pressure Version 4 0 User Manual Deleting an Fe ert E E EE 42 Closing the Material Database Dialog Box 43 Units Tor Material Se E 43 Details on Analysis Type Tube MAN EE 45 SEN 49 Flat Annular Endcap Analyse er er e 53 Conical Endcap Analysis EE 57 Hemispherical HEEN 62 Flat Circ lar Endcap WE 65 Analysis Results Warning Messages 69 Report Generation nee ee een 71 Appendices A Pressure RE E A I B Plate noeap Bounda y Con e N B 1 C Formulas Used by Under Pressure cccceccccsescccesecceeseceeneeeseseeeeneeeeseeaeeeeeenseeseneeas C 1 D Pressure Vessel SIC SES ee er US ENS uu EDS RU OUR D 1 E Pressure Vessel Stress Distribution 22 125220 op 20e BESAAT SES DEES EE E 1 DeepSea Power amp Light u Rev 3 27 01 Under Pressure Version 4 0 User Manual GENERAL INFORMATION UNDER PRESSURE DESIGN SOFTWARE Under Pressure is a user friendly software program running in a PC environment that uses theoretical elastic stress and strain formulas to calculate the stresses strains and deflections of simple pressure vessel geometries Under Pressure can provide quick and reliable re
28. cross section Max Equiv Stress Maximum uniaxial stress that is equivalent to the three dimensional stress state that exists in the sphere wall for predicting failure of ductile materials by comparison to the uniaxial yield strength Max Shear Stress Maximum Shear Stress in sphere wall N A for external pressure Avg Seat Stress Average Seat Stress N A for spheres dID displacement of sphere Inner Diameter dOD displacement of sphere Outer Diameter An explanation of the orientation of the above stresses is provided in Appendix D PRESSURE VESSEL STRESSES Again the user has an option as to which units will be used to display the data in the results table Rows of data for an applied pressures at or greater than the calculated failure pressure are highlighted by the program to warn the user As discussed in Appendix C FORMULAS USED BY UNDER PRESSURE Maximum Equivalent Stress is used as a failure criteria for Metal Spheres and is not applicable to spheres fabricated from other Main Category Materials Ceramics Glass and Plastics DeepSea Power amp Light 32 Rev 3 27 01 Under Pressure Version 4 0 User Manual FLAT ANNULAR ENDCAP ANALYSIS Flat Annular Endcap Edge Restraint Options The significance of Edge Restraint Options Outer Inner for Flat Annular Plates is defined in APPENDIX B FLAT ENDCAP BOUNDARY CONDITIONS If in doubt about which edge restraint is most appropriate for a given Flat Annular Endcap design the use
29. distribution on the outer upper half thickness of the plate is compressive due to its concave deflection during pressure loading The stress distribution on the inner lower half thickness of the plate is tensile due to its convex displacement during pressure loading The distribution of the compressive and tensile stresses in the plate are symmetric and the plate s neutral axis The peak radial stress occurs at the inner and outer flat surfaces of the plate at the plate free diameter DeepSea Power amp Light E 12 Rev 3 27 01 Under Pressure Version 4 0 95 000 Free Diameter 4 500 21 000 Center Hole Diameter FLAT ANNULAR ENDCAP ANALYSIS DWG eannl bmp on e mn Ae nn a AN aaaaaaaaaaaaaaaaaaaaMmMl AT et rale mrri aA I 4 HO HHH FLAT ANNULAR ENDCAP ANALYSIS MOD eannlmod bmp FLAT ANNULAR ENDCAP ANALYSIS RAD eannlrad bmp FLAT ANNULAR ENDCAP ANALYSIS TAN eannltan bmp ANZSYS 5 3 AUG 1 1997 10 43 01 HODAL SOLUTION STEP 1 ANG ae ae SMM 12013 SMNE 22675 gI 1z013 SMR R 2 2073 12017 9393 507d 4004 1335 1335 Joad 6614 3343 12013 DeepSea Power amp Light User Manual 425 Thickness ANSYS 5 3 AUG 1 193 10 45 26 ELEMENTS TYPE NUM d IDE zv j DIST 1 5093 HF 1 097 EE _3125 ANSYS 2 3 AUG l 1587 10 43 56 NODAL SOLUTTON SMME 17356 SMS 123235H SMZE 129356 1 3399 10421 1443 d466 1433 1485 4455 7443
30. fai 15601 80 640 24192 3000 8 0000 fail 16 000 LR DeepSea Power amp Light E 15 Rev 3 27 01 Under Pressure Version 4 0 User Manual Clicking on Graph gives the following m Flat Annular Endcap Graph Stress us Radial Location for 1 Ksi pressure Radial Tangential Stress bai 1 Maximum Radial Stress 11 520 psi Location 1 000 diameter hole diameter 2 Maximum Tangential Stress 5344 psi Location 1 735 diameter Finite Element Method graphical stress results FEA model element mesh pressure loading B C s from eann2mod bmp Radial stress contour eann2rad bmp Tangential stress contour eann2tan bmp 1 Maximum Radial Stress 10 965 psi Location 1 000 diameter 2 Maximum Tangential Stress 7256 psi Location see stress contour DeepSea Power amp Light E 16 Rev 3 27 01 Under Pressure Version 4 0 User Manual 85 000 Free Diameter 625 Thickness 81 000 Center Hole Diameter FLAT ANNULAR ENDCAP ANALYSIS 2 DWG eann2 bmp ANSYS 5 3 AUG 1 1997 f 10 49 05 ELEMENTS TYPE NUM FLAT ANNULAR ENDCAP ANALYSIS 2 MOD CE eann2mod bmp PRES TW OIST 1 504 ee EF 1 047 mu YF _3125 POM ON z BUFFER nd NODAL SOLUTION STEP 1 FLAT ANNULAR ENDCAP ANALYSIS 2 RAD SE eann2rad bmp ax inva ASYS D DS 003337 ANSYS 5 3 SMN 10965 AUG 1 1997 SMNB Z0TON 10 52 32 SHE 10865 NODAL SOLUTION SMZR 2 0700
31. failure at 3 5831 Ksi Dia 1 0000 inches O Seat failure at 10 694 Ksi Fail value units Table eval da De inches 1 0000 Helsale ksi D Material Weight Uni Ai wt 1 181 nitg Pressure Depth Stress Linear Deflection Angle Deflection Mater wi 1 0817 Unit E Ft sea S Ka sl r E Fradians sl SC De Tangential DeShear SE SS Ksi Stress Ksi Stress Ksi BE 1 0000 2248 8 13 32b 4 1778 4 8753 2 0000 4431 3 2 852 8 3999 9 7518 2 5133 fail 156391 35 000 10 500 112 255 3 0000 fail 14 628 4 0000 fail 19 504 5 0000 fail 24 380 6 0000 fal 13392 83555 L nner 29 255 7 0000 fai 5601 2 34 131 8 0000 fal 17804 111 41 338 422 39 007 EB DeepSea Power amp Light E 39 Graph Report T est Aluminum eld Strength 35000 psi lbs Sa Rev 3 27 01 Under Pressure Version 4 0 User Manual Clicking on Graph gives the following im Flat Annular Endcap Graph Stress us Radial Location for 1 Ksi pressure Radial Tangential 1 Maximum Radial Stress 13 926 psi Location 1 000 diameter hole diameter 2 Maximum Tangential Stress 4340 psi Location 1 082 diameter Finite Element Method graphical stress results FEA model element mesh pressure loading B C s from eann8mod bmp Radial stress contour eann8rad bmp Tangential stress contour eann8tan bmp 1 Ma
32. the user selected Distortion Pressure Range The following information is provided for an analysis as a function of the selected pressure range Depth equivalent water Depth of selected pressure De Radial Stress maximum Stress in plate cross section in direction normal to plate center line at noted evaluation Diameter De Tangential Stress maximum Stress in plate in direction normal to plate cross section at noted evaluation Diameter Avg Seat Stress Average bearing Stress on annular area of plate between plate outside diameter and plate free diameter CL Deflection Deflection of Center of plate in direction of plate centerline An explanation of the orientation of the above stresses is provided in Appendix D PRESSURE VESSEL STRESSES Again the user has an option as to which units will be used to display the data in the results table Rows of data for an applied pressures at or greater than the calculated failure pressure are highlighted by the program to warn the user As discussed in Appendix C FORMULAS USED BY UNDER PRESSURE the maximum radial and tangential membrane stresses occur on the flat surfaces of the flat circular plate with the concave side of the plate loaded in compression and convex side of the plate loaded in tension the radial and tangential membrane stresses are zero at the plate midthickness ANALYSIS RESULTS WARNING MESSAGES If Main Category Glass or Ceramic is selected for the design of a pressure vessel sub
33. thickness Sphere OI DeepSea Power amp Light A 2 Rev 3 27 01 Under Pressure Version 4 0 User Manual APPENDIX B FLAT ENDCAP BOUNDARY CONDITIONS DEFINITIONS Fixed Boundary condition at the circumferential edge of a plate that prevents radial rotations and transverse deflections but allows for radial displacements Free Boundary condition at the circumferential edge of a plate that allows for radial rotations and both transverse and radial displacements Guided Boundary condition at the circumferential edge of a plate that prevents radial rotations but allows for transverse and radial displacements Simply Supported Boundary condition at the circumferential edge of a plate that prevents transverse deflections but allows for radial rotations and displacements FIGURES The following figures show a symbolic representation of the various flat endcap boundary conditions adjacent to a pressure vessel assembly cross section for which the boundary condition might be applicable FLAT ANNULAR Fixed Guided DeepSea Power amp Light B 1 Rev 3 27 01 Under Pressure Version 4 0 User Manual Simply Supported Guided Simply Supported Simply Supported Simply Supported Fixed Free Fixed GASKET COMPLIANT RELATIVE TO PLATE FLAT CIRCULAR DeepSea Power amp Light B 2 Rev 3 27 01 Under Pressure Version 4 0 User Manual Simply Supported Fixed DeepSea Power amp Light B 3 Rev 3 27 01
34. through the centerline axis The finite element method involves subdividing the cross section of the tube into a mesh of finite elements For this exercise a mesh of four quadrilateral elements across the tube wall thickness by 40 elements along the tube length was selected A uniform pressure of 1000 psi was applied along the outside diameter and an axial pressure of 2042 psi was applied to one end of the tube and resisted at the opposite end by an axial constraint boundary condition The finite element stress contours indicates that the compressive axial stress in the tube wall is uniform throughout the wall thickness and 1s equal in magnitude to the applied axial pressure of 2042 psi The hoop stress contour indicates that the hoop stress varies from 3080 psi compressive stress at the tube outer diameter to a peak 4074 psi compressive stress at the tube inner diameter Color contours are used to graphically display stress distribution in the tube For this example the entire range of stress has been subdivided into nine bands of color ranging from red stresses from 3080 to 3191 psi to blue stresses from 3964 to 4074 psi For this case the peak hoop stress greatest in magnitude is represented by the blue contour along the tube inner diameter While Under Pressure only provides a numerical value for the maximum stress in the tube the finite element color contour provides the distribution of stress throughout the entire t
35. vessel geometry ADDING NEW MATERIALS TO THE DATABASE Note you can not create new main categories DeepSea Power amp Light 40 Rev 3 27 01 Under Pressure Version 4 0 User Manual In general Main Category Glass should be used to define glass like materials Main Category Ceramics should be used to define ceramic like materials or brittle fracture types of metal crystalline and sapphire Main Category Metals should be used to define metallic materials and Main Category Plastics should be used to define thermoplastics and thermosets This approach is valid as long as the failure criteria that is appropriate for the new material corresponds with the failure criteria that is used by Under Pressure to perform structural analysis for the selected Main Category brittle materials that are characterized by significant differences in the magnitudes of their compressive strength and tensile strength should be defined using Main Category Glass or Ceramics ductile materials that are characterized by yielding permanent deformation prior to ultimate failure should be defined using Main Category Metals materials that are characterized by strengths that are heavily dependent upon duration of applied load and service temperature should be defined using Main Category Plastics The reason for reinforcing the above discussion is that it is possible for example to have a metallic material that exhibits brittle behavior that may be bett
36. 00 I D The Analysis Dialog Box for the geometry shown above appears as follows As Under Pressure TE X File Edit Materials window Design Options Help B Tube Analysis External Pressure Pressure Range 100 2000 psi T NE Theoretical Failure Geh Thin wall Buckling at 266 60 psi by 3 nodes O Shell failure at 824 43 psi Thin wall eg s M aterial PLASTIC ACETAL Ultimate Strength CH Seat failure N A Da C Shear failure N A Working Strength Fail value units 3 ksi Weit Uni Ai wt 2 0782 nits Pressure Depth Stress Linear Deflection Angle Deflection Water wt 6 6980 ps sl Fe sea ps sl Inches Radians Ibs psi Ft sea s 100 00 225 19 1091 7 200 00 450 31 1091 7 2183 3 266 60 fail N A 300 00 Fail N A 400 00 fail 900 35 2183 3 _ 4366 7 INVA 500 00 fail 11253 27232 Hi INA 600 00 fai 13501 3250 6550 0 NR 700 00 fail N A 800 00 fail N A EE EXAMPLE 4 ANALYSIS DIALOG BOX 5 00 I D DeepSea Power amp Light 32 Rev 3 27 01 Under Pressure Version 4 0 User Manual This analysis indicates the following results Thin Wall Buckling occurs at 600 feet safety factor equals 3 0 Hoop stress in tube is below selected Working Strength 3000 psi at a maximum service depth of 200 feet sea water Weight in air 2 08 Ib Weight in water 6 66 Ib the tube generates in excess of 6 Ib of positive buoyancy when subm
37. 000 6 0000 HA 0 048328 0 041419 13000 2922 3 3 1227 0 2454 HA 0 050305 0 043113 14000 3146 5 3 3029 0 7259 HA 0 054175 0 046430 1 5000 3370 7 3 6031 7 2063 HA 0 058045 0 049746 1 5000 3584 9 3 9433 7 0807 HA 0 061914 0 053063 1 7000 3819 0 4 0836 8 1671 HA 0 065784 0 056379 1 000 4043 0 4 3238 5 0475 HA 0 069654 0 059695 19000 4267 0 4 5040 0 1279 HA 0 073523 0 063012 2 0000 4490 9 4 5042 H 5084 HA 0 077393 0 066328 affer bows iz failure DeepSea Power amp Light 73 00057650 0 007 6567 0 0096054 0 011530 0 013454 0 015373 0 017395 0 019417 0 031135 0 023000 0 02400 0 044933 0 020403 D 028525 0 030747 D 032668 D 034 590 D 036513 D 038435 Rev 3 27 01 Under Pressure Version 4 0 User Manual Note The default text font for different printers varies and so your actual results may appear somewhat different from that shown If instead of printing to paper you want to make a file copy of this information then you can select Print from the File menu and then choose the Print to file option When you select Ok a Save As dialog box opens as below Gave As Save in E Curent UP Version Software E cl E E File name Renatt tst Save as Hype Text WO sl Cancel The default file name is Report txt The information is saved in a tab delimited ASCII format so that it can be imported into applications su
38. 0040616 0 0000 61915 0 0000 0 011767 0 0040616 0 0040672 62000 0 0000 0 011784 0 004106 72 0 004 7385 IH EFF 0047385 0 0054155 0 015630 0 0054155 DeepSea Power amp Light 25 Rev 3 27 01 Under Pressure Version 4 0 User Manual FD Radial FD Tangential FD Shear FD Vert Dell FD Angular Defl 0 0000 2343 7 1013 5 0 0000 0 00032485 3999 7 0 0000 4533 5 2027 0 0 0000 0 0018437 313 3 0 0000 043 2 3040 5 0 0000 0 0027746 11879 0 0000 3393 0 4054 1 0 0000 0 0035334 15833 0 0000 11743 5067 6 0 0000 0 0045243 19798 6081 1 0 0000 0 0055431 237 58 6089 4 0 0000 0 005556 7 237 90 7034 6 0 0000 0 0064 740 27718 8108 1 0 0000 0 00739388 31677 EXAMPLE 3 ANALYSIS DIALOG BOX cont Clicking on Graph in the Analysis Dialog Box generates a plot of radial and tangential stresses in the plate for a 1 Ksi external pressure load as a function of the location along the plate diameter This plot confirms that the maximum membrane stress in the plate is in the tangential direction and occurs at the edge of the hole in the center of the plate Note that 50 points were used to generate these stress curves The number of points used in these curves corresponds to the number of Radial Increments that the user selects in the Geometry Dialog Box for Flat Annular Endcaps Further detail on the specific information contained in the Analysis Dialog box is addressed later in section DETAILS ON ANALY
39. 074 psi DeepSea Power amp Light E 3 Rev 3 27 01 Under Pressure Version 4 0 User Manual Discussion Under Pressure based on the formulas given in Appendix C and the finite element model provide nearly identical results for both axial and hoop stresses Appendix D defines the orientation of the axial and hoop stresses in the walls of the cylindrical tube Both of these methods are based on the assumption the tube is capped by some type of end cap which provides a uniform axial pressure to the ends of the tube that is derived from the external pressure applied to the end cap The axial pressure applied to the tube ends equals Total axial force on end cap annular area of tube end P n Tube O D x Tube O D Tube LD where P is the applied external pressure For the specific case above the axial pressure 1000 psi r 7 mm Vic in 5 in 2042 psi A two dimensional cross section of the tube 1s modeled with the finite element method rather than constructing a three dimensional model of the tube Since the geometry of the tube and the applied loads and boundary conditions are symmetric about the tube centerline the resulting stresses in the tube are also symmetric about the tube centerline All pressure vessel geometry s and applied pressures that are analyzed by Under Pressure are axis symmetric For this type of symmetry the stress distribution in the pressure vessel wall is the same for any cross section taken
40. 2648 4 5296 7 7945 1 10593 13242 15890 18539 pis Fail value units Linear Deflection Angle Deflection Material ALUMINUM 6061 T6 weight Ayr Wl User Manual Bie E Report Done eld Strength 35 Ksi 3 1352 Water wt 1 2955 Units Ibs wn Stress psi Stress psi 5296 7 10593 15890 21187 26484 31780 37077 4587 1 3174 2 13761 18348 22935 2 523 32110 16990 20207 40415 ETT 17804 21187 42374 36697 Clicking on the scroll arrow adjacent to the two boxes titled Distortion Pressure Range at the top of Conical Endcap Analysis Dialog Box allows the user to select the range of pressure in units of psi or Bar that will be used with the data in the results table below For example if psi is selected as the pressure units of choice one of the following pressure ranges can be selected for presenting the results DeepSea Power amp Light 60 Rev 3 27 01 Under Pressure Version 4 0 User Manual 0 1 2 psi 1 20 psi 10 200 psi 100 2000 psi 1000 20 000 psi 10 000 200 000 psi The Theoretical Failure portion indicates the pressure or depth at which the two modes of failure for a conical endcap analysis Shell Failure and Seat Failure occur Thin wall buckling failure is non applicable N A not because buckling of a conical shell won t occur but because an explicit buckling formula for conical shells does not ex
41. 42566 0 036480 0 021138 0 046436 0 039797 0 023060 0 048328 0 041419 0 024000 0 050305 0 043113 0 024982 0 054175 0 046430 0 026903 0 058045 0 049746 0 028825 0 061914 0 053063 0 030747 0 065784 0 056379 0 032668 0 069654 0 059695 0 034590 0 073523 0 063012 0 036512 0 077393 0 066328 0 038433 d Length Inches Notice how the last few columns appear mis aligned To correct this the information in the table can be selected and either reformatted so that the tabs are wider or it can be converted into a table In Microsoft Word converting it into a table 1s a matter of selecting the table contents noted by the dashed line above and then selecting Convert Text to Table This will yield a formatted table DeepSea Power amp Light 76 Rev 3 27 01 Under Pressure Version 4 0 User Manual APPENDIX A PRESSURE VESSEL GEOMETRIES HOUSINGS Tube Sphere Sphere D Wall thickness Sphere OD Tube LD Wall thickness Tube OD ENDCAP Flat Annular Conical Plate Outside Diameter i r Conical Outer Height Plate Free Diameter Center Hole Diameter Wall thickness Ve E F Plate thickness jim Inside Diameter Bose Outside Diameter eg DeepSea Power amp Light A Rev 3 27 01 Under Pressure Version 4 0 User Manual ENDCAP Continued Hemispherical Flat Circular Plate Outside Diameter Plate Free Diameter Plate thickness Sphere LD Wall
42. 45 0005308 0 002014 43 100 225 13 260 85 621 7 MIA 0 006163 0 0059 0 002057 4 10 247 71 286 34 633 37 MIA 0 006773 0 00605 0 002236 45 120 er 22 313 02 745 04 MiA DUU 7336 D 0066 0 002504 Aer 130 232 73 333 11 303 21 MIA 0 008012 00075 0 002713 B 140 315 25 365 19 370 35 MIA n se28 0 0077 0 002322 45 150 aarre 331 28 332 556 MIA 0 003245 0 009525 000313 49 160 360 27 417 36 334 73 MIA 0 003561 0 0058 0 003333 Eso 170 382 78 44345 1056 3 MiA 0 010477 000935 0 003545 oL DU 405 23 463 53 13 1 MA 0 011034 0 0033 0 003756 DE 130 427 3 435 62 11 2 Nie 0 0171 0 01045 0 003365 E53 200 450 31 B21 1243 4 MEA 0 012326 DUT 0 004174 54 after housing Failure Sheetz sheets f Jal gt Ready CE RRE I Ss DeepSea Power amp Light 75 Rev 3 27 01 Under Pressure Version 4 0 User Manual On the other hand pasting it into a word processor will have varying results Under Pressure Ver 4 05 16 41 26 07 17 1998 TUBE CONFIGURATION External Pressure Inner Diameter 3 4380 in Outer Diameter 4 5000 in Wall Thickness 0 53100 in Tube Length Weight in air 10 000 in 3 1516 lbs Weight in water 2 7393 Ibs Thin Wall Buckling at 2 4984 Ksi by 2 nodes Seat failure N A Shear failure N A Ultimate Strength 6 Ksi Working Strength 0 6 Ksi Elastic Modulus 0 35 Mpsi Density 0 0476 Ib cu in Poisson s Ratio 0 36 Comments Molded or Extruded Rigi
43. 5 T6 Yield Strength b Ksi Fail value units Ka LI ribs Pressure Depth Stress Linear Deflection Angle Deflection weight Air wt 23 157 Water wt 10 470 Units libs ksi sl Ft sea sl ksi sl Inches sl Radians sl Ft sea Stress Ksi Stress Ksi Stress Ksi 3 0401 Fail 10 000 Fail DeepSea Power amp Light 17 Rev 3 27 01 Under Pressure Version 4 0 User Manual This analysis indicates the following results Thin Wall Buckling occurs at 10 632 psi S F 2 36 Shell failure occurs at 9040 psi S F 2 0 Weight in air 23 16 Ib Weight in water 10 47 Ib The use of a higher strength aluminum alloy 7075 T6 for the cylindrical housing results in a design wall thickness equals 47 inches that generates 10 47 Ib of positive buoyancy when submerged as compared to a negative buoyancy of 8 15 Ib for the 6061 T6 design wall thickness equals 1 03 Again note that if you change back to 6061 T6 the thin wall buckling does not change appreciably whereas the shell failure does Further detail on the specific information contained in the Analysis Dialog box is addressed later in the section DETAILS ON ANALYSIS TYPE Example 2 Aluminum Flat Circular Endcap Design Requirements 7075 T6 Aluminum Alloy Flat Circular Endcap for Aluminum Cylindrical Housing design of Example 1 4500 psi maximum external service pressure Plate Free Diameter of 6 00 equ
44. 6000 0 fail 13392 173220 bi ROT 7000 0 fai pn 202090 60626 0 0000 8000 0 fail 0 0000 Kim DeepSea Power amp Light E 31 Rev 3 27 01 Under Pressure Version 4 0 User Manual Clicking on Graph gives the following w Flat Annular Endcap Graph x Stress us Radial Location for 1 Ksi pressure 30 25 20 15 Stress Ksi 7 Radial Tangential 1 Maximum Radial Stress 28 869 psi Location 1 000 diameter hole diameter 2 Maximum Tangential Stress 15 058 psi Location 2 143 diameter Finite Element Method graphical stress results FEA model element mesh pressure loading B C s from eann6mod bmp Radial stress contour eann6rad bmp Tangential stress contour eann6tan bmp 1 Maximum Radial Stress 24 257 psi Location 1 000 diameter 2 Maximum Tangential Stress 17 005 psi Location see stress contour DeepSea Power amp Light E32 Rev 3 27 01 Under Pressure Version 4 0 User Manual ANSYS 5 3 AUG l 1997 11 43 47 NODAL SOLUTI STEP I Sx DV DME 00951 gt SHH 24257 SMNE 4 gt 517 AME 24237 25 000 Free Diameter 2 000 NAAR AA Thickness 31 000 Center Hole Diameter FLAT ANNULAR ENDCAP ANALYSIS 6 DWG eann6 bmp ANSYS 5 3 AUG 1 1397 11 40 12 ELEMENTS TYPE HUM FLAT ANNULAR ENDCAP ANALYSIS 6 MOD eann6mod bmp rm a PRES aV 1 DIST 1 5 039 SE 1 047 UERBO mud on FLAT ANNULAR ENDCAP ANALYSIS 6 RAD E eann6rad bmp
45. 97 12 02 41 ELEMENTS TIPE NUM LU DIZST 1 5D59 TEE 1 047 CHE 24125 ANSYS 5 3 AUG 1 1997 12204559 NODAL SOLUTION STEP 1 SUB 1 TIME 1 AVG RSYS U DME 007346 SMN 25680 SMNB 62496 SME 25680 SMXB 62495 236080 185974 14267 85360 2893 2803 8560 14267 19974 23680 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 50 Rev 3 27 01 Under Pressure Version 4 0 Case 11 User Manual Plate Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Center Hole Diameter 1 00 Free Outer Edge Restraint Simply Supported Center Hole Edge Restraint Plate cross section with applied pressure B C s eannl 1 bmp Under Pressure numerical stress results E Flat Annular Endcap Analysis External Pressure _ nix Pressure Range 100 2000 psi D EE Graph Report Done Theoretical Failure Material CA Radial moment failure at 5454 8 psi Dia 1 5714 inches Test Aluminum Units Pressure Depth psi Fi sea nsi sl Inches Degrees Pressure Deph De Radial e Tangential psi Ft sea Stress psi Stress psi Stress psi 100 00 200 00 300 00 400 00 429 57 fail 500 00 fail 600 00 fail 700 00 fail 800 00 fail SS Tangential moment Failure at 429 57 psi Dia 1 0000 inches CH Shear stress failure at 1750 0 psi Dia 1 0000 inches CH Se
46. D inner diameter Tube O D outer diameter and Tube length Alternatively the variable Wall thickness can be used in conjunction with either Tube I D or Tube O D to define the tube geometry APPENDIX A PRESSURE VESSEL GEOMETRIES shows a figure of a tube and the variables used to define its geometry While analyzing a tube design the option buttons Maintain I D constant and Maintain O D constant can be used to constrain either the Tube I D or the Tube O D for successive iterations of a tube design Clicking on Pipe Tables allows the user to load standard pipe cross section geometries for analysis After using the cursor and keyboard or Pipe Tables to define a tube geometry a three dimensional view of the resulting tube geometry is generated on the left hand side of the Tube Geometry Dialog Box Clicking on Done saves the tube geometry and closes the Tube Geometry Dialog Box Clicking on Cancel closes the Tube Geometry Dialog Box without saving user input DeepSea Power amp Light 45 Rev 3 27 01 Under Pressure Version 4 0 User Manual Clicking on Perform Analysis analyzes the tube geometry and opens the Tube Analysis Dialog Box Tube Formulas Formulas used for Tube stress analysis are presented in APPENDIX C FORMULAS USED BY UNDER PRESSURE If the ratio of the tube mean radius tube wall thickness is greater than 10 the program uses thin wall formulas to calculate stresses If the ratio of the tube mean radius tube wa
47. DeepSea Power amp Light E 8 Rev 3 27 01 Under Pressure Version 4 0 User Manual OD 297 000 ID a5 900 1 000 WALL THICKNESS SPHERE ANALYSIS DWG espherel bmp ANSYS 5 3 AUG 1 199 ANSYS3 5 3 10 38 12 Aus 1 1997 NODAL SOLUTION 10 39 38 STEP 1 ELEMENTS SUE 1 TYPE NUM TIME 1 Uu d A AVG m RSYS 0 DME 826E 03 za L SMM 2354 DIST 23 85 SMNB 235 SE SME 1858 SGMEB 1857 2254 rege m 2244 SPHERE ANALYSIS MOD SPHERE ANALYSIS MER E 2182 espherelmod bmp espherelmer bmp i 3 2023 ges 1568 emm EIS 1858 DeepSea Power amp Light E 9 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 10 Rev 3 27 01 Under Pressure Version 4 0 User Manual FLAT ANNULAR ENDCAP ANALYSIS For the purposes of the flat annular endcap cases presented below the following assumptions are used e All flat annular endcap case results from Under Pressure are based on enabling Uniform Load and Line Load Options in the Flat Annular Endcap Geometry Dialog Box e All flat annular endcap case results from Under Pressure are based on using 50 radial increments for calculating radial and tangential stresses Case 1 Plate Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Center Hole Diameter 1 00 Fixed Outer Edge Restraint Free Inner Center Hole Edge Restraint NOTE The elastic formulas used in UP use only the free diameter The outside diamet
48. Edge Restraint Free Inner Center Hole Edge Restraint Plate cross section with applied pressure B C s eann5 bmp Under Pressure numerical stress results Flat Annular Endcap Analysis External Pressure _ joy x Graph Report Di Pressure Range Ja pong E psi e Material Test Aluminum Theoretical Failure CH Radial moment Failure at 2762 1 psi Dia 2 2245 inches Tangential moment failure at 876 40 psi Dia 1 0000 inches CH Shear stress failure at 8750 0 psi Dia 5 0000 inches CH Seat failure at 10694 psi Fal value units Table eval dia De inches 1 0000 Hetzalc psi D eld Strength 35000 psi Weight Uni Am wt 11 7181 nitg Pressure Depth Stress Linear Deflection Angle Deflection Water Mt 1 0817 Units ibs D E P sea a ps p x ET H mi rites E s psi Stress psi Stress psi HELLE Fail 90 oop E 0 0000 20000 fail 0 0000 30000 fail 0 0000 40000 Fail 0 0000 50000 fail 105140 00000 1996800 0 0000 60000 fail 0 0000 70000 fail 0 0000 80000 fail 0 0000 90000 fail 0 0000 al DeepSea Power amp Light E 27 Rev 3 27 01 Under Pressure Version 4 0 User Manual Clicking on Graph gives the following im Flat Annular Endcap Graph Stress us Radial Location for 1 Ksi pressure TTT TT N H HH KIT 20 Stress Ksi Radial Ta Tangential 10 10 15 20 25 30 35 40 45 50
49. Manual Clicking on Graph gives the following im Flat Annular Endcap Graph Stress vs Radial Location for 1 Ksi pressure Radial Tangential Stress Kaj 1 Maximum Radial Stress 14 744 psi Location 4 265 diameter 2 Maximum Tangential Stress 52 221 psi Location 1 000 diameter hole diameter Finite Element Method graphical stress results FEA model element mesh pressure loading B C s from eann9mod bmp Radial stress contour eann9rad bmp Tangential stress contour eann9tan bmp 1 Maximum Radial Stress 15 887 psi Location see stress contour 2 Maximum Tangential Stress 53 181 psi Location 1 000 diameter DeepSea Power amp Light E 44 Rev 3 27 01 Under Pressure Ve 5000 Free Diameter 2 500 LLL UL N i5 1 04 Center Hole Diameter FLAT ANNULAR ENDCAP ANALYSIS 9 DWG eann9 bmp FLAT ANNULAR ENDCAP ANALYSIS 9 MOD eann9mod bmp ANSYS 5 3 AUG 1 19597 12 00 28 NODAL SOLUTION STEP I SUB 1 TIME 1 SEA AG RSYs 0 DME 011819 SMN 15887 SMNB 61741 SMX 15887 FLAT ANNULAR ENDCAP ANALYSIS 9 RAD eann9rad bmp FLAT ANNULAR ENDCAP ANALYSIS 9 TAN eann9tan bmp LA J e Cn DeepSea Power amp Light E 45 525 Thickness AN SYS 5 3 AUG 1 1597 BETAS S25 ELEMENTS TYEE NUM U BE ERES zv l DIST 1 509 XF 1 047 EYF e eS ANSYS 5 3 AUG 1 1337 12 01 18 NODAL SOLUTION STEP I SUB TIME 1
50. Max Equiv Stress Maximum uniaxial stress that is equivalent to the three dimensional stress state that exists in the cone wall for predicting failure of ductile materials by comparison to the uniaxial yield strength Avg Seat Stress Average Stress on flat annular bearing area at cone open end dRadius radial displacement of cone open end dHeight change in cone height dMeridian rotation of cone meridian DeepSea Power amp Light 61 Rev 3 27 01 Under Pressure Version 4 0 User Manual An explanation of the orientation of the above stresses is provided in Appendix D PRESSURE VESSEL STRESSES Again the user has an option as to which units will be used to display the data in the results table Rows of data for an applied pressures at or greater than the calculated failure pressure are highlighted by the program to warn the user As discussed in Appendix C FORMULAS USED BY UNDER PRESSURE Maximum Equivalent Stress is used as a failure criteria for Metal Conical Endcaps and is not applicable to conical shells fabricated from other Main Category Materials Ceramics Glass and Plastics HEMISPHERICAL ENDCAP ANALYSIS Hemispherical Endcap Geometry By selecting Analysis Type Endcap Only in the Application Window selecting Endcap Configuration Hemispherical and clicking on Enter Geometry the program user can access the Hemispherical Endcap Geometry Dialog Box i a Under Pressure EI Hemispherical Endcap geomet
51. O CROSS SECTION SHOWN N AVG SEAT STRESS Meridianal stress Y2 Hoop stress User Manual Rev 3 27 01 Under Pressure Version 4 0 User Manual ENDCAP Flat Circular IA Ze TANGENTIAL STRESS PERPENDICULAR TO CROSS SECTION SHOWN AVG SEAT STRESS e Simply Supported Edge Restraint Maximum radial stress maximum tangential stress and occurs at the inner and outer surfaces of the plate at the plate center line e Fixed Edge Restraint Maximum radial stress occurs at the inner and outer surfaces of the plate at the plate free diameter Maximum Tangential Stress Occurs at the inner and outer surfaces of the plate at the plate center line Peak maximum stress Radial stress at the inner and outer surfaces of the plate at the plate free diameter DeepSea Power amp Light D 3 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light D 4 Rev 3 27 01 Under Pressure Version 4 0 User Manual APPENDIX E PRESSURE VESSEL STRESS DISTRIBUTION Once a pressure vessel design has been analyzed using Under Pressure stress results are displayed numerically in the Analysis Dialog Box Depending on the pressure vessel geometry that has been analyzed different significant stress components are displayed in table format in the Analysis Dialog Box In order to help the pressure vessel designer visualize the distribution of stress in a particular pressure vessel geometry and thereby better understand t
52. OMFIGURATION External Pressure imer Diameter 34320 im Chater Diameter 4 5000 in Wall Thickness 0 53100 im Tube Length 10 000 im Weight in ar 3 1516 be Weight i water 4 7393 Ibs Failure Mode Shel failure at 1 2489 Esi Thick wall eg s Thir Wall Duch ling at 2 4984 Esi by 2 rodes Seat failure Myth Shear faibure HA PLASTIC POLYVINYL CHLORIDE PC Properties Ultinate Strength 6 Esi Working Strength 0 6 Esi Elastic Modubx 0 35 Mier Density 0 0476 vc m Poisors Ratio 0 36 Comments Molded or Exruded Eigid Compressive Ultimate Strength 8 Exi Tube distortion values d Length Inches 0 0019217 00038433 Pressure Depth Max Ardal Max Hoop Max Equm dID d OD Esi Ft isea Stress Esi Stress Esi Stress Esi che Fiches O 10000 225 19 0 24021 0 48043 HA O 0038696 0 0033164 0 20000 450 31 0 48043 0 90084 MA Q n077393 0 0066328 0 30000 675 37 0 72063 1 4413 HA 0 011509 0 0099492 0 40000 900 35 0 96084 1 9217 HA 0 015479 0 013266 Da0000 1125 3 1 2010 2 4021 HA 0 019348 0 016582 0 60000 1350 1 1 4413 3 8825 HA 0 023218 0 019595 D70m000 1574 9 1 6815 3 3629 HA 0 027088 0 023215 0 000 1799 5 1 9217 3 433 HA 0 030957 0 026531 O 90000 2034 3 2 1619 4 3235 HA 0 034827 0 029848 10000 2248 5 3 4021 4 5043 HA 0 038696 0 033164 1 1000 2473 5 2 6423 5 2546 HA 0 042506 0 036480 1 2000 2697 6 2 0825 5 7650 HA 0465436 0 039797 12439 2807 5 3 0
53. Pressure Version 4 0 User Manual by clicking on choice Outer refers to the boundary condition that exists at the outside diameter outer edge of the plate Inner refers to the boundary condition that exists at the edge of the center through hole in the plate If Flat Circular Endcap Configuration is selected click on the user s choice of Edge Restraint Options by clicking on the scroll arrow and selecting the Appropriate Boundary Condition Simply Supported Fixed by clicking on choice ENTERING PRESSURE VESSEL GEOMETRY AND ANALYIZE RESULTS Click on Enter Geometry to open the Geometry Dialog Box for the selected shape Tube Sphere Flat Annular Endcap Conical Endcap Hemispherical Endcap or Flat Circular Endcap The title bar of this dialog box is based on the selected geometry and boundary conditions for example Flat Annular Endcap Simply Supported Free ef Flat Annular Endcap Simply Supported Free UT ES u mE Cap Uutade ire Center Hole Diameter lin gt ks ks v Enable Uniform Load Enable Line Load Update Done Loading Options Perform Analysis Cancel Radial Increments 50 Geometry Dialog Box shown for Flat Annular Endcap Use the cursor and keyboard to enter dimensions and units of pressure vessel shape in the Geometry Dialog Box Click on Perform Analysis to generate analysis results Analysis results are displayed in an Analysis Dialog Box The title bar of this dialog bo
54. Radial pi tel Stress psi Stress psi jStress psi psi Y Unita EXAMPLE 2 ANALYSIS DIALOG BOX This analysis indicates the following results Radial Stress Failure Tangential Stress failure occurs at 9038 psi S F 2 0 Seat failure occurs at 15 658 psi S F 3 48 Weight in air 4 89 Ib Weight in water 3 10 Ib Note that the average seat stress at the outer edges of the flat circular plate is equal to axial stress in the 7075 T6 tube of example 1 Further detail on the specific information contained in the Analysis Dialog box is addressed later in section DETAILS ON ANALYSIS TYPE Note When using certain materials it is often advisable to construct such endcaps from sawn plate rather than round bar to ensure fully tempered material at the maximally stressed plate center Example 3 Aluminum Flat Annular Endcap Design Requirements 7075 T6 Aluminum Alloy Flat Annular Endcap for Aluminum Cylindrical Housing design of Example 1 4500 psi maximum external service pressure Plate Free Diameter of 6 00 equal to Tube I D of Example 1 Plate Outside Diameter of 6 94 equal to Tube O D of Example 1 1 00 hole in the center of plate for an electrical connector DeepSea Power amp Light 21 Rev 3 27 01 Under Pressure Version 4 0 User Manual Minimum safety factor of 1 33 on membrane stresses tangential and radial stress in plate Procedure Follow the steps outlined in GETTING STARTED t
55. SIS TYPE The hole at the center of a flat annular endcap is a stress concentrator The presence of a hole regardless of size acts to increase the magnitude of stresses in the plate in the local vicinity of the hole A direct comparison of a flat circular plate and a flat annular plate reveals the magnitude of stress concentration around the hole simply supported edge restraint for flat circular plates should be compared to simply supported free edge restraint for flat annular endcaps or fixed edge restraint for flat circular plates should be compared to fixed free edge restraint for flat annular endcaps For a given material plate thickness plate free diameter and pressure loading the addition of a hole on the plate centerline acts to approximately double tangential stresses in the plate at the edge of the hole for cases where the hole diameter is small as compared to the plate free diameter The addition of the hole with free edge restraint acts to relieve the plates ability to carry radial stress at the hole radial stresses at the edge of the hole go to zero As a consequence the tangential stress must bear the portion of the load picked up as radial stress pre hole with the result that the tangential stress increases by a factor of approximately two at the edge of the hole This result can be seen in flat annular endcap graph below DeepSea Power amp Light 26 Rev 3 27 01 Under Pressure Version 4 0 User Manual im Flat Annular Endca
56. Tangential stress contour eann4tan bmp 1 Maximum Radial Stress 5575 psi Location 1 000 diameter 2 Maximum Tangential Stress 3040 psi Location see stress contour DeepSea Power amp Light E 24 Rev 3 27 01 Under Pressure Version 4 0 User Manual 25 000 Free Diameter 2 200 4 T 0 625 Thickness LZ LIN GI IO Center Hole Diameter FLAT ANNULAR ENDCAP ANALYSIS 4 DWG eannd bmp ANSYS 5 3 AUG 1 1397 LEKT d ELEMENTS TYFE NUM u a a D FLAT ANNULAR ENDCAP ANALYSIS 4 MOD eann4mod bmp Cp ay DIST 1 503 HF 1 047 ANSYS 5 3 ZER s cdlas AUG 1 1957 11 53 38 NODAL SOLUTION STEP 1 FLAT ANNULAR ENDCAP ANALYSIS RAD SUB eann4rad bmp EX AYG RSY3 0 ANSYS 5 3 DMX 582E 03 AUG 1 1997 SMN 5575 11 07 11 NODAL SOLUTION SME 5575 STEP 1 SMEP 1BZ61 SUB em TIME 1 Em 75 FLAT ANNULAR ENDCAP ANALYSIS TAN Sz AVG ZE eanndtan bm prre EH 1 p DME 682E 03 EH 5 451 SMN 2040 EH 515 451 SMNE 18851 EH 2 SMZ 3040 En 3087 GMER 18861 n duxi 3040 5575 EN 5 mm 1683 m 2012 EH 705 337 765 EH 1013 EB mE e EH ou DeepSea Power amp Light E 25 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 26 Rev 3 27 01 Under Pressure Version 4 0 User Manual Case 5 Plate Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Center Hole Diameter 1 00 Simply Supported Outer
57. UNDER PRESSURE Version 4 0 USER MANUAL DeepSea Power amp Light Rev 3 27 01 Under Pressure Version 4 0 User Manual Table of Contents General Information Under Pressure Design Software I Deep Sed Power amd Belt een ee a l GUStOMEL DUD POLL ee E E E tee ias 2 Installation EE 3 OBE Re OU CCS E 3 Tinga ne Under E 3 Install te E AWW Eege 3 Eeer 4 Getting Started Starting the Under Pressure Application Wmdow eese 5 barn a NEW E secs ema EM E E E E PEEL IURE MENU 5 DEI PTO CCl Wald CES icc E entisu EUR EER 6 pettine Klee EE e 6 Entering Pressure Vessel Geometry and Analyzing Results 02220002ssnsereeeeeen 9 Reviewing Analysis Rosli S sieur b cepto ESAME ee er eng 10 Printing the Results of a Completed Project Analys 10 AV HTS Ai OCC lan dens sascasnraataerasatedatacanasinasateaniasasasanedect ona AA 020 db AS E Uode dau 10 Openins an Exis ng Project erh 11 Pune Under Pressure era 11 Examples Example 1 Aluminum Tube Desen 13 Example 2 Aluminum Flat Circular Endcap Desen 18 Example 3 Aluminum Flat Annular Endcap Design eere 21 Example 4 Plastic Tube Desi EE 21 Details on Materials E BIS GO NIE EET E TOT OT E 35 SE ETE TT 36 Lu 36 Me ERR 36 Dette OF Maternal Propetties araee nennen 38 Material Database Reference 39 Material Properties DisCUssI6n u u uunuune aa 39 Adding New Materials to the Database
58. USED BY UNDER PRESSURE DeepSea Power amp Light 49 Rev 3 27 01 Under Pressure Version 4 0 User Manual If the ratio of the sphere mean radius sphere wall thickness is greater than 10 the program uses thin wall formulas to calculate stresses If the ratio of the sphere mean radius sphere wall thickness is less than or equal to 10 the program uses thick wall formulas to calculate stresses Thick wall formulas can be used for all ratios of sphere mean radius tube wall thickness by the program user by clicking on the Force Thick Wall Equations check box in the Application Window If thin wall equations are used for an analysis the membrane stresses meridianal and hoop stress are assumed to be uniform constant magnitude throughout the shell wall thickness for either external or internal pressure loading If thin wall equations are used for an analysis the displacement of the Sphere I D and the Sphere O D are assumed to be equal during pressure loading If thick wall equations are used for an analysis the meridianal and hoop stresses vary throughout the shell wall thickness with the maximum magnitude of stress occurring at the Sphere I D for either external or internal pressure loading If thick wall equations are used for an analysis the displacement of the Sphere I D and the Sphere O D differ from one another during pressure loading Shear stresses in the sphere wall are calculated when thick wall equations are used a
59. Working Strength of plastic for this example Select Done in the Analysis Dialog Box to return to Geometry Dialog Box to iterate on required Wall thickness or alternatively Tube O D until requirements of this example Acetal cylindrical housing are met For an Acetal tube with a Tube I D of 4 00 inches a wall thickness of 226 is found to be adequate for the structural design requirements stress buckling of this example as shown by setting up the Geometry Dialog Box below lt Under Pressure I XI File Edit Materials Window Design Options Tube LII Wall thickness 4 0000 KR 0 22600 KR Tube O D Tube length 4 4520 KS 10 000 KR Ce Maintain LD constant C Maintain O D constant Update Done EXAMPLE 4 GEOMETRY DIALOG BOX 4 00 I D The Analysis Dialog Box for the geometry shown above appears as follows DeepSea Power amp Light 30 Rev 3 27 01 Under Pressure Version 4 0 User Manual Under Pressure Eile Edit Materials Window Design Options Help E Tube Analysis External Pressure Fressure Hange 2000 psi D De e Theoretical Failure 9 Thin all Buckling at 267 89 psi by 2 nodes O Shell failure at 867 36 psi Thick wall eg s Matena PLASTIC ACETAL Ultimate Strength C Seat failure N A EIS C Shear failure NA working Strength Fail value units aka Weight psi Uni Ar wt 11 5782 ris Pressure Depth Stress Linear Deflection A
60. Yer 40y c 15 05 54 7123138 TUBE CONFIGURATION Internal Pressure 4 TES Inner Diameter 3 8260 in 2g Outer Diameter 4 5000 in E Wall Thickness 0 33700 in 3 Tube Length 10 000 in 10 weight in air 2 0373 Ibs Hl Weight in water 3 7930 Ibs mp B Failure Mlode Shell Failure at 96 509 psi Thick wall eq s 457 Thin Wall Buckling Mis iB Seat failure Mi Shear Failure Mi E 48 PLASTIC POLYVINYL CHLORIDE FYC Properties 20 Ultimate Strength 5 Esi t Working Strength 0 6 Ksi Taa Elastic Modulus 0 35 Mpsi 52 Density 0 0476 Ibrcu in 24 Poisson s Ratio 0 36 pe Comments ies Molded or Extruded Rigid SCH Compressive Ultimate Strength Ksi ER 3 Tube distortion values ot Pressure Depth Mag Arial Mas Hoop Ma Equiv d IDI doo d Length 32 psi Ft ses Stress psi Stress psi Stress psi Inches Inches Inches 33 Lu ec Dae 26 055 621r MIA HUDD 0 00055 0 000203 34 20 45 044 air 124 34 MIA 0 001233 0 0011 0000r SE 30 Brad 75 256 156 51 M 0001845 0 00165 0 000EZE 3 40 30 038 4 34 248 60 MIA 0002465 00022 0 000835 oF 5 112 6 130 43 310 85 PLA 0 003082 0 00275 0 001043 38 BO 135 12 156 51 373 02 MIA 0003698 0 0033 0 001252 EXER HU 157 64 182 6 435 13 MIA D t 000385 0 001461 40 GU 150 16 209 68 437 35 MIA 0 004931 0 0044 OOD E 30 202 67 23477 553 53 MIA 0 005547 0 00495 0 001873 2 96 503 217 33 251 75 BOO MiA 0 0053
61. ailure occur The mode of failure that occurs at the lowest least in magnitude pressure is highlighted with the aid of an option button Since failure by buckling requires at least some compressive loading this failure mode will be non applicable N A for an internal pressure analysis of a sphere design Clicking on the scroll arrow adjacent to the Fail value units box allows the user to select the units for at which failure will be presented Ksi DeepSea Power amp Light 51 Rev 3 27 01 Under Pressure Version 4 0 User Manual Kbar psi Bar Ft sea Ft fresh m sea m fresh The upper right hand portion of the Sphere Analysis Dialog Box provides weights in air and water Air Wt and Water Wt with the option of expressing these values in either Ib or kg The weight in water when completely submerged assumes that that the internal volume of the sphere is empty The bottom portion of the Sphere Analysis Dialog Box provides a results table of applicable stresses and deflections for a sphere analysis that are displayed as a function of the user selected Distortion Pressure Range The following information is provided for a sphere analysis as a function of the selected pressure range Depth equivalent water Depth of selected pressure Max Meridional Stress Maximum Stress in sphere wall in direction of sphere cross section meridian Max Hoop Stress Maximum Stress in sphere wall in direction normal to sphere
62. al or internal pressure loading If thick wall equations are used for an analysis the displacement of the Hemisphere I D and the Hemisphere O D differ from one another during pressure loading Shear stresses in the Hemisphere wall are calculated when thick wall equations are used and the load case 1s for internal pressure loading Formulas used for Hemisphere buckling analysis are presented in APPENDIX C FORMULAS USED BY UNDER PRESSURE Hemispherical Endcaps buckle by dimpling of the shell wall and therefore the number of nodes generated for a tube buckling analysis are not presented Hemispherical Endcap Formula Assumptions Buckling Analysis If the ratio of the hemisphere mean radius hemisphere wall thickness 1s less than or equal to 10 the results of the buckling analysis may not be valid Hemispherical Endcap Analysis Results The following Hemispherical Endcap Analysis Dialog Box will be used to highlight the data and options available to the user after an analysis has been performed DeepSea Power amp Light 63 Rev 3 27 01 Under Pressure Version 4 0 User Manual des Under Pressure iol Ele Edt Materials Window Design Options Help Hemispherical Endcap Analysis External Pressure bx ajl Pressure Range 1000 20000 psi sl DE sl Report Done Theoretical Failure Material Thin wall Buckling at 64240 psi ALUMINUM 6061 16 Shell failure at 7701 9 psi Thick wall eq s CH Seat failure at 8203 1
63. al to Tube I D of Example 1 Plate Outside Diameter of 6 94 equal to Tube O D of Example 1 Minimum safety factor of 2 0 on stress Procedure Follow the steps outlined in GETTING STARTED to set up the Under Pressure Application Window for this example Use the cursor and keyboard to enter the Project Title Project Description and Project Designer in the Project Parameters portion of Application Window optional Click on CHOOSE to open the Material Database Dialog Box Select Main Category Metals by clicking on the scroll arrow and clicking on Metals Select Sub Category Aluminum by clicking on the scroll arrow and clicking on Aluminum Select Name 7075 T6 as a first option for this example by clicking on the scroll arrow and clicking on 7075 T6 Click on Done to return to the Application Window Click the Units English Option Button Click the Pressure External Option Button Select Analysis Type Endcap Only by clicking on the scroll arrow and clicking on Endcap Only DeepSea Power amp Light 18 Rev 3 27 01 Under Pressure Version 4 0 User Manual Select Endcap Configuration Flat Circular by clicking on the scroll arrow and clicking on Flat Circular Select Edge Restraint Options Simply Supported by clicking on the scroll arrow and clicking on Simply Supported For this example we will assume that the interface between the cylindrical tube of example 1 and the flat circular endcap of this
64. appendix is to aid the pressure vessel designer in visualizing stress distributions in common pressure vessel geometries as a supplement to Under Pressure In some of the cases presented in this appendix there is significant difference between the magnitude of stresses calculated by Under Pressure and the finite element method The accuracy of the finite element method s results is depended upon the methods used to model the pressure vessel geometry applied loads and boundary conditions Factors such as the number of elements used mesh density type of elements employed and techniques used to represent applied loads and boundary conditions will effect the accuracy of the model DeepSea Power amp Light E 1 Rev 3 27 01 Under Pressure Version 4 0 User Manual For the purposes of this appendix the following parameters shall be fixed e Pressure Vessel Material is a Metal approx 6061 T6 Aluminum with Young s Modulus 10 Mpsi Poisson s Ratio 3 density 1 Ib cu in yield strength 35 000 psi Me Material Database Fes all Main Category Metals i sl Update Search Sub Category Aluminum sl Name vt Yield Strength 35000 psi sl Add Mpsi ts Delete Ib cu in sl Done Cancel Edit Controls Edit Record Youngs Modulus Density Poisson s Ratio Comments Test materials for user manual examples similar to 60601 T6 AL e Under Pressure stress results for Tube and Sphere Analysis are b
65. ased on Thick Wall Equations e FEA Stress results presented are based on an applied external pressure of 1000 psi DeepSea Power amp Light E 2 Rev 3 27 01 Under Pressure Version 4 0 User Manual TUBE ANALYSIS Tube length 10 00 Tube I D 5 00 Wall thickness 1 00 Tube O D 7 00 Tube cross section with applied pressure and B C s etubel bmp Under Pressure numerical stress results E Tube Analysis External Pressure Pressure Hange 1000 20000 psi m TE Report Done Material Test Aluminum Theoretical F ailure CO Thin wall Buckling at 165700 psi by 2 nodes Geh Shell failure at 3837 4 psi Thick wall eq s O Seat failure N A CH Shear failure M A Held Strength 35000 psi Fall value units weight ps Aj wt 18 850 Units Pressure Depth Stress Linear Deflection Angle Deflection Water wt 4 5343 ps Fi sea ps Inches zl Degrees Unita fibs Pressure Depth MaxAxial MaxHoop Max Equiv psi Ftiseal n ED 9897 4 fail 21955 20207 40415 EET 1 Maximum Axial Stress 2041 7 psi 2 Maximum Hoop Stress 4083 3 psi Finite Element Method graphical stress results FEA model element mesh pressure loading B C s from etubelmod bmp Axial stress contour etubelax al bmp Hoop stress contour etubelhoop bmp 1 Maximum Axial Stress 2042 psi 2 Maximum Hoop Stress 4
66. at failure at 10694 psi Table eval da De inches 1 0000 Healt psi Fail value units Ww eight Stress Linear Deflection Angle Deflector 225 19 0 0000 450 31 0 0000 675 37 0 0000 24443 3000 0 900 35 0 0000 32591 4000 0 36686 Wunn 35000 42957 5000 0 6000 0 7000 0 8000 0 8147 7 16295 1000 0 2000 0 Yield Strength 35000 psi Air wt 1 181 water wt 1 0817 Units Ibs DeShear k DeepSea Power amp Light Rev 3 27 01 Under Pressure Version 4 0 User Manual Clicking on Graph gives the following im Flat Annular Endcap Graph Stress us Radial Location for 1 Ksi pressure Radial Tangential Stress Ka 1 Maximum Radial Stress 6405 psi Location 1 571 diameter 2 Maximum Tangential Stress 81 477 psi Location 1 000 diameter hole diameter Finite Element Method graphical stress results FEA model element mesh pressure loading B C s from eannl Imod bmp Radial stress contour eannl 1l rad bmp Tangential stress contour eann Itan bmp 1 Maximum Radial Stress 12 444 psi Location see stress contour 2 Maximum Tangential Stress 80 678 psi Location 1 000 diameter DeepSea Power amp Light E52 Rev 3 27 01 Under Pressure 25 000 Free Diameter 2 000 Qoo Quoc GI D Center Hole Diameter FLAT ANNULAR ENDCAP ANALYSIS 11 DWG eann11 bmp ANSYS 5 3 AUG
67. ation Window Note the Yield Strength of 7075 T6 62 000 psi Click Perform Analysis and note that the thin wall buckling is nearly identical but that the fail pressure 1s much greater Buckling is directly a function of material stiffness not strength Now select Enter Geometry to iterate on Wall thickness or alternatively Tube O D for this new alloy DeepSea Power amp Light 16 Rev 3 27 01 Under Pressure Version 4 0 User Manual For aluminum alloy 7075 T6 a wall thickness of 47 is found to be adequate for this example as shown by setting up the Geometry Dialog Box below Further detail on the specific information contained in the Analysis Dialog box is addressed later in this manual File Edit Materials window Design Options L Tube Fa Tube I I Mall thickness 6 0000 KR 0 47000 Gs Tube OD Tube length 6 9400 sl 24 000 Gs Ce Maintain LD constant C Maintain D D constant Update Done Perform Analysis Pipe Tables L ancel EXAMPLE 1 GEOMETRY DIALOG BOX 7075 T6 The Analysis Dialog Box for the geometry shown above appears as follows ds Under Pressure File Edit Materials Window Design Options Help E Tube Analysis External Pressure Pressure Range 1000 20000 psi sl Fr sl Theoretical Failure CH Thin wall Buckling at 10 632 Ksi by 2 nodes GH Shell Failure at 9 0401 Ksi Thick wall eq s CH Seat failure N A CH Shear failure H A ALUMINUM 707
68. cation 1 000 diameter 2 Maximum Tangential Stress 34 960 psi Location see stress contour DeepSea Power amp Light E 56 Rev 3 27 01 Under Pressure Version 4 0 User Manual ANSYS 5 3 AUG 1 18397 lec tle NODAL SOLUTION STE P 1 SUB 1 TIME 1 RSYS DME 01338 SMN S3866 SMNB 38054 SMX S3866 tn LO en tn DeepSea Power amp Light 85 000 Free Diameter 625 Thickness I N X O AS 81 000 Center Hole Diameter FLAT ANNULAR ENDCAP ANALYSIS 12 DWG eann12 bmp ANSYS 5 3 AB 1 15597 LI k 12 11 46 Bs FS IIIA X 4g id Lid ELEMENTS TrPE NUM FLAT ANNULAR ENDCAP ANALYSIS 12 MOD ER eann12mod bmp nv sl nIST 1 5093 YXE 1 047 ANP ee 3123 FLAT ANNULAR ENDCAP ANALYSIS 12 RAD SX AVG eann12rad bmp 5 ANSYS 5 3 AUG 1 199397 12 14 10 NODAL SOLUTION STEP I JVE 1 FLAT ANNULAR ENDCAP ANALYSIS 12 TAN Ties 8E CANG eann12tan bmp REYS I L CA xp if E 57 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 58 Rev 3 27 01 Under Pressure Version 4 0 User Manual CONICAL ENDCAP ANALYSIS Base Inside Diameter 5 00 Conical Outer Height 2 641 Wall thickness 10 Conical endcap cross section with applied pressure B C s econel bmp Under Pressure numerical stress results Conical Endcap Analysis External Pressure Pressure Range 1000 20000 psi psi e Repo
69. ch as spreadsheats or tables easily Because there are different title lengths 1n the different column titles the information may appear to overlap or be mixed up if brought up in a word processor that 1s not formatting the information as a table In order to solve this problem the tab stops need to be spaced wider 1f 1n a word processor or the information can be placed imported into a table or spreadsheet Copy to clipboard When the analysis screen is active not only can you print the results but also the results can be copied to the clipboard for insertion into another program s Under Pressure File Edt Materials Window Design Options Help S Tube LD 3 Copy Analisis ta Clipboard Ctrl H Tube HT ee Selecting the Copy Analysis to Clipboard option will copy the entire analysis contents of the printed report into the clipboard to allow it to be pasted into another application DeepSea Power amp Light 74 Rev 3 27 01 Under Pressure Version 4 0 User Manual An obvious place to paste this information is into a spreadsheet or word processor Since the information is tab delimited pasting it into a spreadsheet will cause the information to all fall into its own cell Microsoft Excel Book File Edit wiew Insert Format Tools Data Window Help x DacE Aem pe o o a g Arial i0 si B Z U Se e TTE EHE Al vi Under Pressure Ver 4 0x A 4 8 DSS SSS SS EE E K Under Pressure
70. conical endcap For this exercise a mesh of two quadrilateral elements across the conical shell thickness was selected for the finite element model The finite element stress contour indicates that the peak hoop stress occurs at the base of the endcap HEMISPHERICAL ENDCAP ANALYSIS Discussion See discussion of the sphere analysis above Under Pressure used the same formulas to perform stress analysis for spheres and hemispherical endcaps DeepSea Power amp Light E 60 Rev 3 27 01 Under Pressure Version 4 0 25 000 Bass ID ab 293 Base OD 100 Thlekness CONICAL ENDCAP ANALYSIS DWG econel bmp ANSTS 5 3 AUG 1 1997 Lettre ELEMENTS TYPE NUM PREG zV 1 DIST 1 453 Zb 1 285 d 351 ZE sel 3 CONICAL ENDCAP ANALYSIS MOD econelmod bmp DeepSea Power amp Light E 61 2 541 Outer Height 45 000 CONICAL ENDCAP ANALYSIS HOOP econelhoop bmp User Manual ANSYS 5 3 AUS 1 133 1z 15 34 WODAL SOLUTION TIME 1 S Z5 LAW Di EBYS3 2 U Dix 0097866 JMN 2 342435 SMNB 35555 dix 15 2549 MXRA 2 56 963 34d243 30456 25669 272842 15045 15306 11521 1733 1245 155 254 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 62 Rev 3 27 01 Under Pressure Version 4 0 User Manual FLAT CIRCULAR ENDCAP ANALYSIS Case 1 Plate Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Sim
71. d Compressive Ultimate Strength 8 Ksi Tube distortion values Pressure 0 10000 0 20000 0 30000 0 40000 0 50000 0 60000 0 70000 0 80000 0 90000 1 0000 1 1000 1 2000 1 2489 1 3000 1 4000 1 5000 1 6000 1 7000 1 8000 1 9000 2 0000 Depth Ft sea 225 19 450 31 675 37 900 35 1125 3 1350 1 1574 9 1799 6 2024 3 2248 8 2473 3 2697 8 2807 5 2922 2 3146 5 3370 7 3594 9 3819 0 4043 0 4267 0 4490 9 Max Axial Max Hoop Max Equivd ID Stress Ksi Stress Ksi Stress Ksi Inches 0 24021 0 48042 0 72063 0 96084 1 2010 1 4413 1 6815 1 9217 2 1619 2 4021 2 6423 2 8825 3 0000 3 1227 3 3629 3 6031 3 8433 4 0836 4 3238 4 5640 4 8042 after housing failure PLASTIC POLYVINYL CHLORIDE PVC Properties 0 48042 0 96084 4413 1 9217 2 4021 2 8825 3 3629 3 8433 4 3238 4 8042 5 2846 5 7650 6 0000 6 2454 6 7259 7 2063 7 6867 8 1671 8 6475 9 1279 Failure Mode Shell failure at 1 2489 Ksi Thick wall eq s N A N A N A N A N A N A N A N A N A N A N A N A N A N A N A N A N A N A N A N A d OD Inches 0 0038696 0 0033164 0 0019217 0 0077393 0 0066328 0 0038433 0 011609 0 0099492 0 0057650 0 015479 0 013266 0 0076867 0 019348 0 016582 0 0096084 0 023218 0 019898 0 011530 0 027088 0 023215 0 013452 0 030957 0 026531 0 015373 0 034827 0 029848 0 017295 0 038696 0 033164 0 019217 0 0
72. d Inner Center Hole Edge Restraint Plate cross section with applied pressure B C s eann9 bmp Under Pressure numerical stress results E Flat Annular Endcap Analysis External Pressure IOJ x Pressure Range 1000 20000 psi Theoretical Failure Radial moment failure at 2 3739 Ksi Dia 4 2653 inches Tangential moment failure at 0 67023 Ki Dia 1 0000 inches O Shear stress failure at 1 7500 Ksi Dia 1 0000 inches CH Seat failure at 10 694 Ka T able eval dia De inches 11 0000 Helale ksi Unita Pressure Pressure 1 0000 fail 2 0000 fail 3 0000 Fail 4 0000 fail 3 0000 Fail 6 0000 Fail 7 0000 Fail 8 0000 fail 3 0000 fail HE Depth Stress Depth Stress 2748 8 0 0000 44903 0 0000 6726 2 0 0000 89548 00000 T1177 0 0000 133322 0 0000 15601 00000 417 77 80 000 17804 0 0000 20000 0 0000 Linear Deflection Angle Deflection Inches E De Radial La Fail value units Material weight Units De Tangential Stress La 52 221 10 000 104 44 20 000 156 66 30 000 _208 88 40 000 261 10 50 000 313 32 60 000 365 99 70 000 469 99 40 000 Graph Report Test Aluminum Yield Strength 35000 psi Air wt 1 181 Water wt 1 087 lbs Stress Ka DeepSea Power amp Light Rev 3 27 01 Under Pressure Version 4 0 User
73. d applies a line load to the circular edge of the center hole that is equivalent to the pressure load that exists on any insert mounted in the hole Line load x circumference of hole pressure load x cross sectional area of hole By selecting Enable DeepSea Power amp Light 53 Rev 3 27 01 Under Pressure Version 4 0 User Manual Uniform Load a uniformly distributed pressure is applied to the flat annular surface of the plate from the center hole diameter to the cap outside diameter By selecting Enable Line Load a uniform circular line load is applied to the flat annular surface of the plate at a diameter equal to the hole diameter A typical analysis of a flat annular endcap for pressure loading should be performed with BOTH the Enable Uniform Load and Enable Line Load check boxes active at the same time Under Pressure allows further options for applying loads to flat annular endcaps by clicking on Loading Options Selecting Loading Options allows the user to increase the inner diameter of the annular area to which uniform pressure loading is applied and or allows the user to increase the diameter at which a uniform circular line load is applied These loading diameters can be adjusted by clicking on Loading Options clicking the Custom Option Button and using the cursor and keyboard to input values for Uniform Loading I D Line Load Application Diameter and Line Loading O D If the Loading Options is not used the inner diameter of th
74. d bmp ANSYS 5 3 AUG 1l 1997 Lco 3 NODAL SOLUTION STEP 1 pe ND FLAT ANNULAR ENDCAP ANALYSIS 3 RAD Sx AVG eann3rad bmp ROYS DME o MN SMB bord kd ee oh B 3612 EM gt FLAT ANNULAR ENDCAP ANALYSIS 3 TAN 1548 eann3tan bmp E ae 5 Lou EIU SE 1548 2580 Lee 3612 4644 DeepSea Power amp Light E 21 User Manual 625 Thickness ANSYS 5 3 AUG 1 139 Eee e E ELEMENTS TYPE NUM u GE PRES ayo l DIST 1 508 FXF zl D i EYE ucl ANSYS 5 3 AUG 1 1997 11 00 32 NODAL SOLUTION STEP 1 SUB 1 TIME 1 SZ AVG RSYS 0 DMX 771E 03 SMN 4809 SMNB 16307 SMX 4809 SMXB 16307 Em 3809 3741 3 2672 BE 1603 Bei 534 365 534 365 ex 1603 ES 2672 em i 4809 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 22 Rev 3 27 01 Under Pressure Version 4 0 User Manual Case 4 Plate Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Center Hole Diameter 1 00 Fixed Outer Edge Restraint Fixed Inner Center Hole Edge Restraint Plate cross section with applied pressure B C s eann4 bmp Under Pressure numerical stress results Flat Annular Endcap Analysis External Pressure fe x Pressure Hange 1000 20000 psi PME Graph Report Done Theoretical Failure Material Geh Radial moment Failure at 4 2272 Kai Dia 1 0000 inches Test Aluminum CH
75. d time creep behavior and should therefore be considered by the pressure vessel designer DeepSea Power amp Light 70 Rev 3 27 01 Under Pressure Version 4 0 User Manual REPORT GENERATION Part of the process of evaluation of a design is the comparison of the results that are achieved using different design parameters materials shapes etc Under Pressure supports saving the files for easy retrieval but it is often more convenient to have a printed copy of the information Furthermore it is often useful to have the ability to transfer the generated results of the analysis into another program for additional analysis to include in a report or to send a copy of the results electronically via e mail Under Pressure supports the following types of report generation 1 Printed report on paper overheads etc This generates a printed report of the analysis to your current printer as set up in the print dialog box 2 Print report to file This is used to make a file copy of the analysis report This file can then be opened with a word processor or other program to format the contents 3 Copy Analysis to Clipboard This is useful to quickly copy the entire report from the analysis window into other programs In particular this is useful for placing the report in e mails or to put it in a spreadsheet such as Microsoft Excel This chapter will cover how these reports are generated and how the information can be formatted or
76. dow and clicking on Enter Geometry the program user can access the Sphere Geometry Dialog Box Under Pressure I XI Sphere LD Hal Thickness 11 in T KR 11 Sphere OD In T Ce Maintain LO constant C Maintain O D constant Update Done Perform Analysis Cancel SPHERE GEOMETRY DIALOG BOX Sphere geometry is defined by the variables Sphere I D inner diameter and Sphere O D outer diameter Alternatively the variable Wall thickness can be used in conjunction with either Sphere I D or Sphere O D to define the sphere geometry APPENDIX A PRESSURE VESSEL GEOMETRIES shows a figure of a sphere and the variables used to define its geometry While analyzing a sphere design the option buttons Maintain I D constant and Maintain O D constant can be used to constrain either the Sphere I D or the Sphere O D for successive iterations of a sphere design After using the cursor and keyboard to define a sphere geometry a three dimensional view of the resulting sphere geometry is generated on the left hand side of the Sphere Geometry Dialog Box Clicking on Done saves the sphere geometry and closes the Sphere Geometry Dialog Box Clicking on Cancel closes the Sphere Geometry Dialog Box without saving user input Clicking on Perform Analysis analyzes the Sphere geometry and opens the Sphere Analysis Dialog Box Sphere Formulas Formulas used for Sphere stress analysis are presented in APPENDIX C FORMULAS
77. e Analysis Options Ge English C Internal v Force Thick Wall Equations C Metric Ce External v Use Working Strength for Plastic Analysis Type Tube Enter Geometry EXAMPLE 4 APPLICATION WINDOW Click on Enter Geometry to open the Geometry Dialog Box Use the cursor and keyboard to enter 4 00 inches for Tube I D Estimate appropriate Tube O D or Wall thickness and enter the corresponding value using the cursor and keyboard Use the cursor and keyboard to enter 10 00 inches for Tube length Click on Perform Analysis to generate analysis results Review the analysis results in Analysis Dialog Box for this example a minimum safety factor of 3 0 was desired on buckling at a depth of 200 feet seawater Therefore the Theoretical Failure portion of the Analysis Dialog Box titled Tube Analysis External Pressure for this example should indicate than Thin Wall Buckling occurs at a depth greater than or equal to 600 feet Safety Factor equals Failure Depth Maximum Service Depth 600 200 3 A safety factor of 3 was arbitrarily selected for this example In actual practice the safety factor that is selected will depend on specific requirements of the pressure vessel and the confidence of the pressure vessel designer DeepSea Power amp Light 29 Rev 3 27 01 Under Pressure Version 4 0 User Manual The Analysis Dialog Box should also indicate that the maximum hoop stress at a depth of 200 feet does not exceed 3000 psi selected
78. e Diameter O D and Conical Outer Height Alternatively the variable Wall thickness can be used in conjunction with either LD or O D to define the conical endcap geometry APPENDIX A PRESSURE VESSEL GEOMETRIES shows a figure of a Conical Endcap and the variables used to define its geometry While analyzing a Conical Endcap design the option buttons Maintain I D constant and Maintain O D constant can be used to constrain either the I D or the O D for successive iterations of a Conical endcap design analysis After using the cursor and keyboard to define the endcap geometry a three dimensional view of the resulting conical shell geometry is generated on the left hand side of the Conical Endcap Geometry Dialog Box Clicking on Done saves the geometry and closes the Conical Endcap Geometry Dialog Box Clicking on Cancel closes the Conical Endcap Geometry Dialog Box without saving user input Clicking on Perform Analysis analyzes the Conical Endcap geometry and opens the Conical Endcap Analysis Dialog Box Conical Endcap Formulas Formulas used for Conical Endcap stress analysis are presented in APPENDIX C FORMULAS USED BY UNDER PRESSURE Conical Endcap Formula Assumptions If the ratio of the cone open end mean radius principal radius cone wall thickness is less than or equal to 10 the results of the stress analysis may not be valid If this assumption is violated the following warning will appear Under Pressure Be
79. e hel becas Stress psi Stress psi Material ALUMINUM 075 TE eld Strength b Ksi weight 1000 0 2000 0 3000 0 4000 0 5000 0 6000 0 6008 2 Fail 2248 a 4490 9 6726 2 8954 8 11177 13392 13411 0000 0 0000 0 0000 0 0000 0 0000 0 0000 0 0000 20638 30958 41277 51536 61915 62000 0 0000 0 0000 0 0000 0 0000 0 0000 0 0000 0 0000 7000 0 Fail 000 0 fail EI 15601 0 0000 72234 0 0000 17804 0 0000 82553 0 0000 FLAT ANNULAR ENDCAP ANALYSIS DIALOG BOX EXAMPLE Clicking on the scroll arrow adjacent to the two boxes titled Distortion Pressure Range at the top of Flat Annular Endcap Analysis Dialog Box allows the user to select the range of pressure in units of psi or Bar that will be used with the data in the results table below For example if psi is selected as the pressure units of choice one of the following pressure ranges can be selected for presenting the results 0 1 2 psi 1 20 psi 10 200 psi DeepSea Power amp Light 55 Rev 3 27 01 Under Pressure Version 4 0 User Manual 100 2000 psi 1000 20 000 psi 10 000 200 000 psi The Theoretical Failure portion indicates the pressure or depth and radial location at which the four modes of failure for a Flat Annular Endcap analys s Radial moment fail Stress Failure Tangential moment fail Stress Failure Shear Stress Failure and Seat Fail Pressure occur T
80. e uniform load and the application diameter of the line load default to the plate s center hole diameter Using a Uniform Loading I D Line Load Application Diameter and Line Loading O D larger than the hole diameter may be appropriate for endcap designs where some type of circular cover or connector is installed over the center hole that seals a circular area on the flat plate that is larger in diameter than the center hole diameter For this situation the Uniform Loading I D Line Load Application Diameter and Line Loading O D could be adjusted to equal the diameter of the endcap flat surface that 1s sealed from pressure by the cover or connector Clicking on Done saves the geometry and closes the Flat Annular Endcap Geometry Dialog Box Clicking on Cancel closes the Flat Annular Endcap Geometry Dialog Box without saving user input Clicking on Perform Analysis analyzes the Flat Annular Endcap geometry and opens the Flat Annular Endcap Analysis Dialog Box Flat Annular Endcap Formulas Formulas used for Annular Circular Endcap stress analysis are presented in APPENDIX C FORMULAS USED BY UNDER PRESSURE Flat Annular Endcap Formula Assumptions Stress analysis formulas assume that the plate is flat and has a constant thickness The ratio of the Plate Free Diameter to the Plate Thickness is greater than or equal to 4 If this assumption is violated the results of the analysis may not be valid and the following warning will appea
81. eport Done Material ALUMINUM 6061 T Theoretical Failure C Thin wall Buckling at 81 941 Esi by 2 nodes Shell failure at 3 0093 Kei Thick wall eq s O Seat Failure N A C Shear failure N A Yield Strength 35 Ksi Fail value units Weight e Units Pressure Depth Stress Linear Deflection Angle Deflection Water wt 18 1 464 Ka Le Ft sea P Ka w Inches Ke F adians y Writs lbs mr Pressure Depth Max xial MaxHoop Nato 6726 2 8354 8 11177 13332 15601 17804 2DODO b 7288 8 9718 11 215 13 458 15 701 17 944 20 186 13 458 17 944 22 429 26 915 31 401 35 887 40 373 20020 20 207 40 415 27190 22 429 44 859 38 849 EXAMPLE 1 ANALYSIS DIALOG BOX 6061 T6 This analysis indicates the following results Thin Wall Buckling occurs at 81 941 psi S F 18 2 Shell failure occurs at 9009 psi S F 2 0 Weight in air 53 5 Ib Weight in water 8 15 Ib Note This assumes the ends are capped with weightless end closures Endcap weights must be added to all actual housing weights In this example the designer might consider a slight safety factor reduction to allow the use of stock 8 OD material Return to the Under Pressure Application Window Select Choose and select aluminum alloy 7075 T6 from the material database Select Done to return to the Applic
82. er defined using Main Category Glass or Ceramics for the purposes of performing structural analysis within Under Pressure SELECTING A PRESSURE VESSEL MATERIAL Click on CHOOSE in the Application Window to open the Material Database Dialog Box alternatively the Material Database Dialog Box can be accessed by clicking on Materials in the Application Window and clicking on View Material or by entering Altt M V from the keyboard Click on appropriate Main Category of desired material by clicking on the scroll arrow and clicking on choice Click on appropriate Sub Category of desired material by clicking on the scroll arrow and clicking on choice Click on Name of desired material by clicking on the scroll arrow and clicking on choice Click on Done VIEWING ALL MATERIALS IN THE DATABASE AT ONCE Click on CHOOSE in the Application Window to open the Material Database Dialog Box Click on All for Main Category Click on All for Sub Category Click on the scroll arrow adjacent to the Name box to scroll through all materials listed in alphabetic order in the database DeepSea Power amp Light 41 Rev 3 27 01 Under Pressure Version 4 0 User Manual EDITING THE PROPERTIES OF AN EXISTING MATERIAL Click on CHOOSE in the Application Window to open the Material Database Dialog Box Click on appropriate Main Category of the material to be edited Click on appropriate Sub Category of the material to be edited Click on Name
83. er is used for weight and seat stress calculations only As the plate diameter is increased relative to the free diameter the results should be more conservative Plate cross section with applied pressure B C s eannl bmp Under Pressure numerical stress results E Flat Annular Endcap Analysis External Pressure IOI x Pressure Range 1000 20000 psi E Bi TM Graph Report Done Theoretical Failure Material CH Radial moment failure at 2 7461 Ksi Dia 5 0000 inches Test Aluminum Tangential moment Failure at 2 6153 Kai Dia 1 0000 inches O Shear stress failure at 8 7500 Kai Dia 5 0000 inches CH Seat failure at 10 694 Ka Di Fail value units Table eval dia De inches 1 0000 HetzalE ksi Units Pressure Depth Stress Linear Deflection Angle Deflection Yield Strength 35000 psi eight Ar wt 1 181 Water wt 1 0817 Units libs Kai Ft sea sl Kai Inches sl Radians sl Pressure Depth De Radial Ksi_ fie jStress Ksi Stress Ksi Stress Ksi 1 0000 2248 8 0 0000 13 383 0 0000 2 0000 4490 9 0 0000 Zb 755 0 0000 2 6153 fail 58670 00005000 00000 3 0000 Fail 0 0000 4 0000 fail 89548 0000 D nn 0 0000 5 0000 fail 0 0000 6 0000 fail 0 0000 7 0000 fai 15601 on 93 680 0 0000 8 0000 Fail 17804 0 0000 107 06 0 0000 L1 EE DeepSea Power amp Light E 11 Rev 3 27 01 Under Pr
84. erged Further detail on the specific information contained in the Analysis Dialog box is addressed later in section DETAILS ON ANALYSIS TYPE DeepSea Power amp Light 33 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light 34 Rev 3 27 01 Under Pressure Version 4 0 User Manual DETAILS ON MATERIALS MAIN CATEGORIES Clicking on CHOOSE in the Under Pressure Application Window allows the user to select the pressure vessel material Under Pressure comes with a database of commonly used pressure vessel materials but also allows the user to edit the material s data base for their own specific needs Materials are defined by the following parameters Main Category Sub Category Name Main Categories are pre defined and cannot be edited by the program user Five Main Categories exist for the material s database All Ceramics Glass Metals Plastics Main Categories are pre set by the program because they define the material properties needed by the program to perform an analys s The material properties needed for each of the Main Categories are as follows Ceramics Ultimate Strength tensile Ultimate Strength compressive Young s Modulus Density Poisson s Ratio Ultimate Strength tensile Ultimate Strength compressive Young s Modulus Density Poisson s Ratio Metals Yield Strength Young s Modulus Density Poisson s Ratio Plastics
85. ersion 4 0 User Manual designed to perform in harsh marine environments from wet dry applications to full ocean depth deployments Under Pressure software is one of the important tools used in designing our standard products DeepSea Power amp Light is headquartered in over 62 000 square feet of high tech manufacturing space Included in the plant are environmental and pressure testing facilities complete machine shop with CNC lathes and mills CAD and 3D drafting stations electronics workshops mold making and ultrasonic welding stations and assembly and repair facilities Our staff includes mechanical electrical and software engineers machinists and sales and service personnel Equipment manufactured by DeepSea has been used by various titanic expeditions including lighting for the IMAX film Titanica National Geographic Society Woods Hole Oceanographic Institute Monterey Bay Aquarium Research Institute NASA Lockheed Oceaneering Technologies and on dozens of deep diving submersibles including Alvin Mirs I amp II Sea Cliff Turtle Nautille Shinkai 6500 and Kaiko an 11 000m ROV that has explored the Mariana trench CUSTOMER SUPPORT Customer support is available during normal business hours at 858 576 1261 For emergencies after hours or on the weekend customer support can be reached by using the emergency paging service Just follow the instructions in the after hours recording Faxes can be sent to 858 576 0219 Emai
86. essure Version 4 0 User Manual Clicking on Graph gives the following im Flat Annular Endcap Graph Stress us Radial Location for 1 Ksi pressure 7 Radial Tangential Stress Kai 1 Maximum Radial Stress 12 746 psi Location 5 000 diameter plate free diameter 2 Maximum Tangential Stress 13 383 psi Location 1 000 diameter hole diameter Finite Element Method graphical stress results FEA model element mesh pressure loading B C s from eannl mod bmp Radial stress contour eannlrad bmp Tangential stress contour eann1tan bmp 1 Maximum Radial Stress 12 013 psi Location 5 000 diameter 2 Maximum Tangential Stress 13 398 psi Location 1 000 diameter Discussion Under Pressure based on the formulas given in Appendix C and the flat annular endcap finite element model provide similar results for peak radial and tangential stresses as well as radial and tangential stress distribution in the endcap Appendix D defines the orientation of the radial and tangential stresses in the endcap For this exercise a mesh of four quadrilateral elements across the endcap thickness was selected for the finite element model The finite element stress contours indicates that the peak tangential stress in the endcap occurs at the inner and outer flat surfaces of the plate at the hole diameter The stress contours indicate that the mid thickness of the plate has zero stress neutral axis The stress
87. example is such that the outer edges of the endcap can rotate during pressure loading simply supported boundary condition If the pressure housing design was such that the edges of the endcap cannot rotate during pressure loading a Fixed Edge Restraint Option clamped boundary condition would be appropriate for example a welded on endcap or bored solid bar The Under Pressure Application Window should appear as follows File Edi Materials Window Design Options EXAMPLE 2 PRU Project Parameters Project Title Example 2 Project Description aluminum alloy 7 75 TB flat circular endcap for 4500 pst external pressure service Project Designer Design Parameters Maternal ALUMINUM 7075 T 5 Choose Units Pressure Analysis Options Ce English C Internal Force Thick all Equations C Metric Ce External Use Working Strength for Plastic Analysis Type Endcap Only Endcap Configuration Flat Circular Enter Geometry Edge Restraint Options Simply Supported EXAMPLE 2 APPLICATION WINDOW Click on Enter Geometry to open the Geometry Dialog Box Use the cursor and keyboard to enter 6 94 inches for Plate Outside Diameter Use the cursor and keyboard to enter 6 00 inches for Plate Free Diameter Note The free diameter is the unsupported diameter The formulas used by Under Pressure can not account for material DeepSea Power amp Light 19 Rev 3 27 01 Under Pressure Version 4 0 User Manual outside the f
88. he mode of failure that occurs at the lowest least in magnitude pressure is highlighted with the aid of an option button Clicking on the scroll arrow adjacent to the Fail value units box allows the user to select the units for at which failure will be presented Ks Kbar psi Bar Ft sea Ft fresh m sea m fresh The bottom of the Theoretical Failure portion of the Flat Annular Endcap Analys s Dialog Box provides the radial location of the Plate 1 e the diameter of evaluation De for which the maximum radial and tangential stresses are presented in the results table The user can change the radial location used in the results table using the box adjacent to Table eval dia De and clicking on ReCalc The upper right hand portion of the Flat Annular Endcap Analysis Dialog Box provides weights in air and water Air Wt and Water Wt with the option of expressing these values in either Ibs or kg The bottom portion of the Flat Annular Endcap Analysis Dialog Box provides a results table of applicable stresses and deflections for an analysis that are displayed as a function of the user selected Distortion Pressure Range The following information is provided for an analysis as a function of the selected pressure range Depth equivalent water Depth of selected pressure De Radial Stress maximum Stress in plate cross section in direction normal to plate center line at user selected evaluation Diameter De Tangen
89. he significance of the numerical stress results generated by a Under Pressure analysis this appendix compares numerical stress results generated by Under Pressure with graphically displayed stress distribution results generated by a computer aided structural analysis using the finite element method Surface pressures on an enclosed vessel are resisted by internal forces that develop in the walls of the pressure vessel The orientation and distribution of internal forces known as stresses that develop within the material of the pressure vessel wall are a function of the vessel geometry material and type of loading Typically the material of the pressure vessel wall resists the stresses that develop without failure until some critical stress level is achieved The critical stress level that causes failure is generally related to the strength of the material Under Pressure provides the designer with the magnitude of the peak stresses as a function of the pressure loading and also provides the critical pressure at which failure of the vessel material is initiated Generally the peak stresses displayed in the Analysis Dialog Box of Under Pressure are localized to a specific region of the pressure vessel wall This appendix aids in visualizing the location of the peak stresses provided by Under Pressure as well as understanding the complete distribution of stresses that develop for pressure vessel geometry s analyzed by the program The intent of this
90. ic plastic composition of interest Plastic data sheets will typically recommend working strengths for a material as a function of service conditions Service conditions are normally defined in terms of maximum design temperature and duration of load Analysis of plastic composite materials e g fiberglass tubes using Under Pressure should be approached with caution The properties of many composite material are directional such that large variations in strength and modulus exist depend on the orientation with respect to fibers cloth etc Analysis of this material directionality along with unique composite failure modes such as delamination are beyond the scope of Under Pressure The Young s Modulus also known as Elastic Modulus and Poisson s Ratio of a material are known as the material s elastic constants The elastic constants are used in the evaluation of stresses and deflections of a pressure vessel geometry Under Pressure also uses the elastic constants to predict the pressure at which thin wall buckling will occur for pressure vessel shell geometries such as tubes spheres and hemispheres Thin wall buckling of tubes spheres and hemispheres is dependent on the material s elastic constants and geometry i e the material and geometric stifiness and is independent of the material s strength The density of a material is used by Under Pressure to calculate the in air weight and water weight weight when submerged of a pressure
91. ical stress results FEA model element mesh pressure loading B C s from ecirc2mod bmp Radial stress contour ecirc2rad bmp Tangential stress contour ecric2tan bmp 1 Maximum Radial Stress 11 612 psi Location plate free diameter 2 Maximum Tangential Stress 8192 psi Location plate center DeepSea Power amp Light E 67 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 68 Rev 3 27 01 Under Pressure Version 4 0 User Manual 85 000 Free Diameter z a0 25 Thickness MMMM ch FLAT CIRCULAR ENDCAP ANALYSIS 2 DWG ecirc2 bmp ANSYS 5 3 AUG 1 1857 12 38 12 ELEMENTS TYFE NUM FLAT CIRCULAR ENDCAP ANALYSIS2 MOD PRES ecirc2 bmp DV DIST21 375 ANSYS 5 3 Sp 1 35 AUG 1 1997 TF 3125 12 39 20 NODAL SOLUTION STEP 1 SUB 1 m ch FLAT CIRCULAR ENDCAP ANALYSIS 2 RAD Gen ecirc2 bmp DMX 0023678 SMM 11612 SGMNR 2 16898 LAO Ls J EE 12 40 09 R HODAL SOLUTION mj 11012 STEL 1 gea 6451 JUR 1 E 5 FLAT CIRCULAR ENDCAP ANALYSIS 2 TAN AD NUM eem mde DG 003678 Ge SMH 192 SE SMNB 14013 Pi ee SMS R192 SMEB 14018 Em 7 63 72 4551 341 mm 210 278 510 278 um 2131 mm 3551 5372 BlSUZ DeepSea Power amp Light E 69 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 70 Rev 3 27 01
92. ight Inc DSP amp L assumes no liability under any circumstances beyond replacement of the distribution media and accompanying documentation No warranty or affirmation of fact express or implied is made or authorized by DSP amp L In no event shall DSP amp L be liable for any loss of profit or any other damage including but not limited to special incidental consequential or other damages It is assumed that persons who use the UNDER PRESSURE design tool are already experienced in pressure housing design and are aware of the applicability and limitations of the formulas used It is the responsibility of the individual designer to incorporate a reasonable factor of safety into a pressure housing design where appropriate as there are no safety allowances provided for within the program OSP amp L assumes no responsibility for the accuracy of the formulas utilized in UNDER PRESSURE In case of any doubt regarding the accuracy of a particular formula please consult the references provided Under Pressure Liability Disclaimer Box STARTING A NEW PROJECT Click on File on the menu bar of the Under Pressure Application Window then click on New Design or enter Ctrl N from the keyboard DeepSea Power amp Light 5 Rev 3 27 01 Under Pressure Version 4 0 User Manual i a Under Pressure File Edit Materials Window Design Options Not saved Project Parameters T EN Design Parameters HM aterial Choose Units Pre
93. ight 42 Rev 3 27 01 Under Pressure Version 4 0 User Manual Delete Material S Delete the maternal ALUMINA CERAMIC S4 7 Delete Material List Box Click on OK CLOSING THE MATERIAL DATABASE DIALOG BOX To close the Material Database Dialog Box without completing any operations select CANCEL or press the Escape key from the keyboard UNITS FOR MATERIAL PROPERTIES Materials in the database provided with Under Pressure are defined using English Units When editing or adding materials to the database Under Pressure allows the user to use the following units Strengths Young s Modulus Ks psi Mps Kbar MPa GPa Mbar Density Ib in Tbft kg m e or cm e kg cm DeepSea Power amp Light 43 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light 44 Rev 3 27 01 Under Pressure Version 4 0 User Manual DETAILS ON ANALYSIS TYPE TUBE ANALYSIS Tube Geometry By selecting Analysis Type Tube in the Application Window and clicking on Enter Geometry the program user can access the Tube Geometry Dialog Box i a Under Pressure EI XI File Edit Materials Window Design Options AG 2 Tube I D Wall thickness el E ube O D Tube length KS rE r Ce Maintain LD constant C Maintain O D constant Update Done Perform Analysis Fipe Tables Cancel TUBE GEOMETRY DIALOG BOX Tube geometry is defined by the variables Tube I
94. ing pressure ranges can be selected for presenting the results 0 1 2 psi 1 20 psi 10 200 psi 100 2000 psi 1000 20 000 psi 10 000 200 000 psi The Theoretical Failure portion indicates the pressure or depth and radial location at which the three modes of failure for a Flat Circular Endcap analysis Radial Stress Failure Tangential Stress Failure and Seat Failure occur The mode of failure that occurs at the lowest least in magnitude pressure is highlighted with the aid of an option button Clicking on the scroll arrow adjacent to the Fail value units box allows the user to select the units at which failure will be presented DeepSea Power amp Light 68 Rev 3 27 01 Under Pressure Version 4 0 User Manual Ks Kbar psi Bar Ft sea Ft fresh m sea m fresh The bottom of the Theoretical Failure portion of the Flat Circular Endcap Analys s Dialog Box provides the radial location of the Plate 1 e the diameter of evaluation De for which the maximum radial and tangential stresses are presented in the results table The upper right hand portion of the Flat Circular Endcap Analysis Dialog Box provides weights in air and water Air Wt and Water Wt with the option of expressing these values in either Ibs or kg The bottom portion of the Flat Circular Endcap Analysis Dialog Box provides a results table of applicable stresses and deflections for an analysis that are displayed as a function of
95. ist in the APPENDIX C formula reference An approximate buckling formula for truncated conical shells with closed ends based on the formulas used for cylindrical shells tubes is referenced in APPENDIX C but is not programmed into Under Pressure The mode of failure that occurs at the lowest least in magnitude pressure is highlighted with the aid of an option button Clicking on the scroll arrow adjacent to the Fail value units box allows the user to select the units for at which failure will be presented Ks Kbar psi Bar Ft sea Ft fresh m sea m fresh The upper right hand portion of the Conical Endcap Analysis Dialog Box provides weights in air and water Air Wt and Water Wt with the option of expressing these values in either Ibs or kg The weight in water when completely submerged assumes that that the internal volume of the conical endcap is empty The bottom portion of the Conical Endcap Analysis Dialog Box provides a results table of applicable stresses and deflections for an analysis that are displayed as a function of the user selected Distortion Pressure Range The following information is provided for an analysis as a function of the selected pressure range Depth equivalent water Depth of selected pressure Max Meridional Stress Maximum Stress in cone wall in direction of cone cross section meridian Max Hoop Stress Maximum Stress in cone wall in direction normal to cone cross section
96. jected to internal pressure the following warning will appear with the Analysis results Dialog Box Under Pressure Pu D D D D D JL The effects of tensile loading on alass ceramic materiale should be considered wien evaluating these results DeepSea Power amp Light 69 Rev 3 27 01 Under Pressure Version 4 0 User Manual Explanation Brittle materials such as Glass or Ceramics are generally intended for use in compression only subjecting these materials to internal pressure results in tensile loads If Main Category Glass or Ceramic is selected for the design of flat circular or flat annular endcaps the following warning will appear with the Analysis results Dialog Box Ci The effects of tensile loading on glass ceramic materials should be considered when evaluating these results Explanation Brittle materials such as Glass or Ceramics are generally intended for use in compression only the convex side of pressure and or line loaded flat endcaps will be subjected to tensile stresses If Main Category Plastic is selected for the design of a pressure vessel the following warning will appear with the Analysis results Dialog Box Ci The effects of time duration of load and service temperature on plastic materials should be considered when evaluating these results Explanation Stress and buckling analysis of plastic pressure vessel components can have a significant dependence on service temperature an
97. l can be sent to mail to UPWIN deepsea com or via our web site at http www deepsea com We encourage you to send us suggestions for future releases of the Under Pressure program to the above email address Also please send us any material information you would like to see included in the standard material database in future release of the program DeepSea Power amp Light 2 Rev 3 27 01 Under Pressure Version 4 0 User Manual INSTALLATION COMPUTER REQUIREMENTS e 486 66 or better processor e Minimum 16MB RAM e VGA Graphics e 20MB hard disk space e CD ROM drive e Parallel port for software key Dongle or hardware lock SOFTWARE REQUIREMENTS e Windows 95 or later or Windows NT 4 0 or later INSTALLING UNDER PRESSURE With power to you system turned off plug the included software key into the printer port with the side that reads COMPUTER connected to the printer port If you also have a printer you can connect the printer cable to the other end of the key This key must be installed in order for the software to run Turn on power to your computer and then once Windows is loaded insert the CD install disk The installation program should automatically start If not double click on the Setup program Follow the on screen instructions that guide you through the installation Once this installation is completed a new group and items in the Start menu will be added After this installation you will be re
98. late Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Fixed Edge Restraint Plate cross section with applied pressure and B C s ecirc2 bmp Under Pressure numerical stress results Flat Circular Endcap Analysis External Pressure Miel XI Pressure Hange 1000 20000 psi E m M Report Done Theoretical Failure Material Radial Stress Failure at 2916 7 psi free dia 5 0000 inches Test Aluminum CH Tangential Stress Failure at 4487 2 psi plate center O Seat failure at 10694 psi Yield Strength 35000 psi Table eval dia De plate free diameter for Max Radial FA value units Table eval da De plate center for Max Tangential Units Pressure Depth Stress Linear Deflection Angle Deflection Weight Ar wt 11 7671 Water wt 1 1126 Units libs sl ps es psi sl P sea sl psi sl Inches sl radians sl Pressure Deph De Max Radial De Ma fon Weg Seat Stress psi Stress psi Stress psi 1000 0 2248 8 12000 7800 H 272 2000 0 4490 9 24000 15600 6545 5 2916 7 fai 6540 2 mmm Domp 9545 5 3000 0 fail 9818 2 4000 0 fail 13031 5000 0 fail 16364 6000 0 fail 19636 7000 0 fai Dem 84000 54600 22909 8000 0 fail 26182 E 1 Maximum Radial Stress 12 000 psi Location plate free diameter 2 Maximum Tangential Stress 7800 psi Location plate center Finite Element Method graph
99. le Uniform Load the program will apply uniform external pressure to the flat external surface of the annular plate By checking Enable Line Load the program will apply an appropriate line load to the circumference of the hole at the center of the plate This line load is equivalent to the pressure load that exists on the flat external surface of the connector This line load simulates the load on the edge of the hole in the plate that is generated by the pressure loading on the item installed into the hole in the plate in this example the electrical connector Click on Perform Analysis to generate analysis results DeepSea Power amp Light 23 Rev 3 27 01 Under Pressure Version 4 0 User Manual Review the analysis results in the Analysis Dialog Box for this example a minimum safety factor of 1 33 was desired on membrane stress radial and tangential stress for a design pressure of 4500 psi Therefore the Theoretical Failure portion of the Analysis Dialog Box titled Flat Annular Endcap Analysis External Pressure for this example should indicate that Radial Stress Failure and Tangential Stress Failure occur at a pressure greater than or equal to 6000 psi Safety Factor equals Failure Pressure Maximum Service Pressure 6000 4500 1 33 The use of different safety factors in the tube and flat circular endcap of examples 1 and 2 safety factor 2 00 than in this example is done arbitrarily and not intended to imply that less safety fact
100. lectrical connector are such that the edges of the hole are essentially unconstrained e free edge restraint by the presence of the connector during pressure loading The Under Pressure Application Window should appear as follows DeepSea Power amp Light 22 Rev 3 27 01 Under Pressure Version 4 0 User Manual i a Under Pressure Wie XI Eie Edit Materials Window Design Options EXAMPLE 3 PRJ Sl EZ Project Parameters Project Tithe Project Description aluminum alloy 7075 76 flat annular endcap for 4500 psi external pressure service Project Designer Design Parameters Material ALUMINUM 7075 T 6 Choose Units f English C Metric Analysis Type Endcap Only Endcap Configuration Flat Annular Enter Geometry Edge Hestraint Options Duter Inner Simply Supported Free M A BN EXAMPLE 3 APPLICATION WINDOW Pressure C Internal Ce External Analysis Options Force Thick Wall Equations Use working Strength for Plastic Click on Enter Geometry to open the Geometry Dialog Box Use the cursor and keyboard to enter 1 00 inches for Center Hole Diameter Use the cursor and keyboard to enter 6 94 inches for Cap Outside Diameter Use the cursor and keyboard to enter 6 00 inches for Free Diameter Estimate Thickness and enter the corresponding value using the cursor and keyboard Click on Enable Uniform Load and Enable Line Load Check Boxes By checking Enab
101. ll thickness is less than or equal to 10 the program uses thick wall formulas to calculate stresses Thick wall formulas can be used for all ratios of tube mean radius tube wall thickness by the program user by clicking on the Force Thick Wall Equations check box in the Application Window If thin wall equations are used for an analysis the membrane stresses axial and hoop stress are assumed to be uniform constant magnitude throughout the shell wall thickness for either external or internal pressure loading If thin wall equations are used for an analysis the displacement of the Tube I D and the Tube O D are assumed to be equal during pressure loading If thick wall equations are used for an analysis the axial stress 1s constant throughout the shell wall thickness for either external or internal pressure loading If thick wall equations are used for an analysis the hoop stress varies throughout the shell wall thickness with the maximum magnitude of stress occurring at the Tube I D for either external or internal pressure loading If thick wall equations are used for an analysis the displacement of the Tube I D and the Tube O D differ from one another during pressure loading Formulas used for Tube buckling analysis are presented in APPENDIX C FORMULAS USED BY UNDER PRESSURE Number of nodes for a Tube buckling analysis refers to the number of circumferential lobes that develop around the tube in its buckled configura
102. m Analysis analyzes the Hemispherical Endcap geometry and opens the Hemispherical Endcap Analysis Dialog Box Hemispherical Endcap Formulas Formulas used for Hemispherical Endcap stress analysis are presented in APPENDIX C FORMULAS USED BY UNDER PRESSURE These formulas are the same as those used for a Sphere stress analysis as discussed previously If the ratio of the hemisphere mean radius hemisphere wall thickness is greater than 10 the program uses thin wall formulas to calculate stresses If the ratio of the hemisphere mean radius hemisphere wall thickness is less than or equal to 10 the program uses thick wall formulas to calculate stresses Thick wall formulas can be used for all ratios of hemisphere mean radius tube wall thickness by the program user by clicking on the Force Thick Wall Equations check box in the Application Window If thin wall equations are used for an analysis the membrane stresses meridianal and hoop stress are assumed to be uniform constant magnitude throughout the shell wall thickness for either external or internal pressure loading If thin wall equations are used for an analysis the displacement of the Hemisphere I D and the Hemisphere O D are assumed to be equal during pressure loading If thick wall equations are used for an analysis the meridianal and hoop stresses vary throughout the shell wall thickness with the maximum magnitude of stress occurring at the Hemisphere I D for either extern
103. m stress allowed in material during service as defined by pressure vessel designer Young s Modulus for all Main Categories Average ratio of stress to strain for stress below the proportional limit measurement of material stiffness Density for all Main Categories Mass or weight per unit volume of material Poisson s Ratio for all Main Categories Absolute value of the ratio of lateral strain over axial strain MATERIAL DATABASE REFERENCES Glass See Comments in Material Database Dialog Box for specific vendor technical data sheet references Ceramics See Comments in Material Database Dialog Box for specific vendor technical data sheet references Metals MIL HDBK 5 Metallic Materials and Elements for Aerospace Vehicle Structures Department of Defense United States of America Washington D C Engineering Data For Aluminum Structures the Aluminum Association Incorporated 900 19th St N W Washington D C 20006 Metals Handbook American Society for Metals Metals Park Ohio Plastics Plastics Edition 8 Thermoplastics and Thermosets D A T A Inc A Cordura Company 9889 Willow Creek Road P O Box 26875 San Diego CA 92126 MATERIAL PROPERTIES DISCUSSION The strength properties of a material are used by Under Pressure to predict the pressure depth at which material failure will occur Bearing stresses average seat stresses and membrane stresses axial hoop and meridional stres
104. n 44 5 362 57 ll 19 Carbide Carbide Main Category Glass Sub Cat Name Y M Den Mpsi Ib in a e E ps a La Main Category Metals 5052 H34 5082 H32 2 111 07 33 Aluminum 5456 H111 26 e ak Steel HI 150 304 303 DeepSea Power amp Light 37 Rev 3 27 01 Under Pressure Version 4 0 User Manual Steel 304L 316L see 316 Steel H1075 M mm n m RS IT H900 Steel Carbon Low Alloy Sub Cat Name Y S Y M Den Ksi Mpsi Ib in Titanium Ti 5AI 110 15 5 162 31 2 5Sn Ti 6AL4V Main Category Plastics MIEIEEIEI Ksi Ksi Mpsi Ib in site Epoxy SIT GG plastic E al P PIP plastic mec PP plastic mar em plastic Bonate Em os mmu plastic prop a pp plastic DEFINITION OF MATERIAL PROPERTIES Ultimate Strength tensile for Main Categories Glass Ceramics Maximum uniaxial tensile stress material can withstand without failure Ultimate Strength compressive for Main Categories Glass Ceramics Maximum uniaxial compressive stress material can withstand without failure Yield Strength for Main Category Metals Uniaxial stress at which yield permanent deformation of the material is initiated DeepSea Power amp Light 38 Rev 3 27 01 Under Pressure Version 4 0 User Manual Ultimate Strength for Main Category Plastics Maximum uniaxial stress material can withstand without failure Working Strength for Main Category Plastics Maximu
105. nches O Seat failure at 10694 psi Fal value unite Table eval dia De inches 11 0000 Beale psi sl Yield Strength 35000 psi Weight Uni Ar wt 1 7181 nits Pressure Depth Stress Linear Deflection Angle Deflection Water wit 1 0817 psi P sea sl ns sl Inches Degrees Pressure Depth De Radial psi Ftisea Stress psi Stress psi Stress psi E 100 00 225 13 9889 9 1767 0 1000 0 200 00 450 31 11780 3934 0 2000 0 Units fibs 300 00 675 37 17670 5300 9 3000 0 400 00 900 35 23560 7067 9 4000 0 500 00 1125 3 29450 8834 9 5000 0 594 23 fail 1337 2 35000 10500 59423 600 00 Fail 1350 1 35340 10602 6000 0 700 00 Fail 1574 9 41230 12369 7000 0 800 00 fail 1799 6 47119 14136 s0000 EES DeepSea Power amp Light E 55 Rev 3 27 01 Under Pressure Version 4 0 User Manual Clicking on Graph gives the following im Flat Annular Endcap Graph Stress vs Radial Location for 1 Ksi pressure 7 Radial Tangential Stress Kaj 1 Maximum Radial Stress 58 889 psi Location 1 000 diameter hole diameter 2 Maximum Tangential Stress 21 738 psi Location 1 408 diameter Finite Element Method graphical stress results FEA model element mesh pressure loading B C s from eann12mod bmp Radial stress contour eannl2rad bmp Tangential stress contour eann12tan bmp 1 Maximum Radial Stress 53 886 psi Lo
106. nd the load case is for internal pressure loading Formulas used for Sphere buckling analysis are presented in APPENDIX C FORMULAS USED BY UNDER PRESSURE Spheres buckle by dimpling of the shell wall and therefore the number of nodes generated for a tube buckling analysis are not presented Sphere Formula Assumptions Buckling Analysis If the ratio of the sphere mean radius sphere wall thickness is less than or equal to 10 the results of the buckling analysis may not be valid Buckling of spheres is dependent on the sphere material s elastic constants and geometry and is independent of the sphere material s strength As discussed in Example 1 of this manual variations in thickness and flat spots can impact buckling resistance of spherical shells Sphere Analysis Results The following Sphere Analysis Dialog Box will be used to highlight the data and options available to the user after a sphere analysis has been performed DeepSea Power amp Light 50 Rev 3 27 01 Under Pressure Version 4 0 User Manual E Under Pressure File Edit Materials Window Design Options Help E Sphere Analysis External Pressure Be g e Pressure Range 1000 20000 psi Ka TM Report Done Material Theoretical Failure Thin Wall Buckling at 40039 psi ALUMINUM BUbT TE Shell Failure at 6323 3 psi Thick wall amp q s CH Seat failure N A CH Shear failure N A Yield Strength 35 Kast Fail value
107. nd variations in thickness such as flat spots on spheres and hemispherical endcaps can impact buckling resistance Stress concentrations include any deviations from the idealized pressure vessel geometry analyzed by Under Pressure such as O ring grooves through holes blind holes screw threads notches shoulders and generally any variations or discontinuities in wall thickness or curvature of the pressure vessel geometry Select Done in the Analysis Dialog Box to return to the Geometry Dialog Box to iterate on required Wall thickness or alternatively Tube O D until the requirements of this example aluminum alloy cylindrical housing are met For aluminum alloy 6061 T6 a wall thickness of 1 03 1s found to be adequate for this example as shown by setting up the Geometry Dialog Box below i a Under Pressure D I XI File Edi Materials window Design Options Tube I D Wall thickness 6 0000 KR 1 0300 KR Tube 0 0 Tube length 3 8 0600 KR 24 000 KR v Maintain L D constant C Maintain O D constant Update Perform Analysis Pipe Tables Cancel a EXAMPLE 1 GEOMETRY DIALOG BOX 6061 T6 The Analys s Dialog Box for the geometry shown above appears as follows DeepSea Power amp Light 15 Rev 3 27 01 Under Pressure Version 4 0 User Manual ds Under Pressure File Edit Materials Window Design Options Help E Tube Analysis External Pressure TEE XI E Pressure Range 1000 20000 psi ME R
108. nded for ratios of mean shell wall radius to shell wall thickness gt 10 This check box has no relevance to the analysis of conical flat circular or flat annular endcaps Click on the Working Strength for Plastic check box if the user desires to evaluate calculated stresses for plastic pressure vessel geometry s using the Working Strength of the selected plastic in lieu of the Ultimate Strength of the selected plastic This check box has no relevance to pressure vessel materials other than plastics such as metals ceramics and glass Select Analysis Type Pressure Vessel Geometry Click on the scroll arrow and select the user s choice of Tube Sphere Endcap Only by clicking on choice If Endcap Only Analysis Type is selected Click on the user s choice of Endcap Configuration by clicking on the scroll arrow and selecting Flat Annular Conical Hemispherical Flat Circular by clicking on choice If Flat Annular Endcap Configuration is selected click on the user s choice of Edge Restraint Options Outer Inner by clicking on the scroll arrow and selecting the Appropriate Boundary Condition Fixed Free Fixed Guided Fixed Simply Supported Fixed Fixed Simply Supported Free Simply Supported Guided Simply Supported Simply Supported Simply Supported Fixed Guided Simply Supported Guided Fixed Free Simply Supported Free Fixed DeepSea Power amp Light 8 Rev 3 27 01 Under
109. nder Pressure E Flat Circular Endcap Analysis External Pressure Pressure Range 1000 20000 psi D Theoretical Failure Geh Radial Stress Failure at 3114 2 psi plate center CH Tangential Stress Failure at 3114 2 psi plate center CH Seat failure at 9285 7 psi ALUMINUM 6061 TE Yield Strength 35 Esi Table eval dia De plate center for Max Aadial Fail value units Table eval dia De plate center for Max Tangential DS Units Pressure Depth Stress Linear Deflection Angle Deflection Water wt 2 3450 psi Ft sea psi Inches Radians El Units fibs Pressure Depth jDeMaxHadial DeMaxTan Weg Seat ns Pea mesem Steep Sane pe 1000 0 2248 8 11233 11233 3769 2 2000 0 4490 9 22478 22478 7538 5 3000 0 6726 2 33716 33716 11308 3114 2 fail 11738 4000 0 fail 8954 8 44955 44955 15077 5000 0 Fail 56194 56194 18846 6000 0 fail 22615 7000 0 fai 15601 967 78671 26385 8000 0 fail 30154 Fl gt fi rly FLAT CIRCULAR ENDCAP ANALYSIS DIALOG BOX EXAMPLE weight Ai wt 3 7715 Clicking on the scroll arrow adjacent to the two boxes titled Distortion Pressure Range at the top of Flat Circular Endcap Analysis Dialog Box allows the user to select the range of pressure in units of psi or Bar that will be used with the data in the results table below For example if psi is selected as the pressure units of choice one of the follow
110. ngle Deflection Water wt 4 1877 bud S m Inches sl Radians Units bs m Pressure Depth Max Axial MaxEque EE a eO Td 100 00 22519 518 81 1037 6 N A 200 00 450 31 1037 6 2075 3 N A 267 89 fail 603 10 1389 8 2779 7 N A 300 00 fail 675 37 1556 4 3112 9 TES 400 00 fail 1900 35 1 2075 3 EILEEN 500 00 fail N A 600 00 fail 13501 31129 6225 E 700 00 fail N A 800 00 fail 17936 4505 8301 0 N A Fell EXAMPLE 4 ANALYSIS DIALOG BOX 4 00 I D This Analysis Dialog Box indicates that the requirements for stress and buckling have been met but that the Acetal tube only generates 4 19 Ib of positive buoyancy Since reducing the Wall Thickness further to generate more buoyancy will result in a housing that does not meet a buckling safety factor of 3 0 the Tube I D must be increased and the required Wall Thickness rechecked By increasing the Acetal Tube I D to 5 0 inches and iterating on Wall Thickness until all requirements have been met a Wall Thickness of 24 inches is found to be adequate for this example as shown by setting up the Geometry Dialog Box below DeepSea Power amp Light 31 Rev 3 27 01 Under Pressure Version 4 0 User Manual Tube LU Mall thickness 5 0000 0 24000 KR Tube O D Tube lenath 5 4600 10 000 KR Ce Maintain LD constant C Maintain Q D constant Update Done Pipe Tables Cancel i EXAMPLE 4 GEOMETRY DIALOG BOX 5
111. o set up the Under Pressure Application Window for this example Use the cursor and keyboard to enter the Project Title Project Description and Project Designer in the Project Parameters portion of Application Window Click on CHOOSE to open the Material Database Dialog Box Select Main Category Metals by clicking on the scroll arrow and clicking on Metals Select Sub Category Aluminum by clicking on the scroll arrow and clicking on Aluminum Select Name 7075 T6 as a first option for this example by clicking on the scroll arrow and clicking on 7075 T6 Click on Done to return to the Application Window Click the Units English Option Button Click the Pressure External Option Button Select Analysis Type Endcap Only by clicking on the scroll arrow and clicking on Endcap Only Select Endcap Configuration Flat Annular by clicking on the scroll arrow and clicking on Flat Annular Select Edge Restraint Options Outer Inner Simply Supported Free by clicking on the scroll arrow and clicking on Simply Supported For this example we will assume that the outer interface between the cylindrical tube of example and the flat annular endcap of this example is such that the outer edges of the endcap can rotate during pressure loading simply supported boundary condition For this example we will also assume that the compliance clearances between the center hole in the aluminum annular endcap and the radial surfaces of the e
112. of the edge restraint option that results in the highest stresses in the plate would be the conservative approach for the designer to use Flat Annular Endcap Geometry By selecting Analysis Type Endcap Only in the Application Window selecting Endcap Configuration Flat Annular selecting appropriate Edge Restraint Options and clicking on Enter Geometry the program user can access the Flat Annular Endcap Geometry Dialog Box ef Flat Annular Endcap Simply Supported Free UT EM u Cap Outside Es Center Hole Es be Enable Uniform Load Enable Line Load Update Done Loading Options Perform Analysis Cancel Radial Increments ail FLAT ANNULAR ENDCAP GEOMETRY DIALOG BOX Flat Annular Endcap geometry is defined by the variables Center Hole Diameter Cap Outside Diameter Free Diameter and Thickness APPENDIX A PRESSURE VESSEL GEOMETRIES shows a figure of a flat annular endcap and the variables used to define its geometry After using the cursor and keyboard to define the endcap geometry a three dimensional view of the resulting flat annular endcap geometry is generated using an additional line to denote the Plate Free Diameter on the left hand side of the Flat Annular Endcap Geometry Dialog Box Clicking on Enable Uniform Load applies a uniform pressure to the appropriate flat surface external surface for external pressure internal surface for internal pressure of the annular plate Clicking on Enable Line Loa
113. of the material to be edited Click on Edit Record Click on the item to be edited material property value material property units comments and edit item as desired Click on Done NOTE The Under Pressure material database resides in the files DESMAT LDB and DESMAT MDB Any edits performed by the user modify these two files It 1s recommended that the original material database be backed up prior to editing the material database An update or reinstallation of Under Pressure will overwrite these files If you have added material to the database back up these files before reinstalling Under Pressure ADDING A NEW MATERIAL Click on CHOOSE in the Application Window to open the Material Database Dialog Box Click on ADD Click on appropriate Main Category of the material to be added Click on appropriate Sub Category of the material to be added or use the cursor and keyboard to enter a new user defined Sub Category Use the cursor and keyboard to fill in Name of new material material properties material property units and comments Click on DONE DELETING AN EXISTING MATERIAL Click on CHOOSE in the Application Window to open the Material Database Dialog Box Click on appropriate Main Category of the material to be deleted Click on appropriate Sub Category of the material to be deleted Click on Name of the material to be deleted Click on Delete to open the Delete Material List Box DeepSea Power amp L
114. om ecircl mod bmp Radial stress contour ecirclrad bmp Tangential stress contour ecircl1tan bmp 1 Maximum Radial Stress 19 904 psi Location plate center 2 Maximum Tangential Stress 19 871 psi Location plate center DeepSea Power amp Light E 63 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 64 Rev 3 27 01 Under Pressure Version 4 0 User Manual 65 000 Free Diameter 2 500 625 Thickness KT FLAT CIRCULAR ENDCAP ANALYSIS 1 DWG ecircl bmp ANSYS 5 3 AUG 1 1997 dE LEIT jEDEMENTS TYPE NUM J FLAT CIRCULAR ENDCAP ANALYSIS 1 MOD Gage ecirclmod bmp a ET DIST 1 375 SE 31 25 ANSYS 5 3 YF 3125 AUG 1 1937 12 35 07 HODAL SOLUTION STEP 1 e FLAT CIRCULAR ENDCAP ANALYSIS 1 RAD SE AV ecirclmod bmp RSYs 0 DME 01186 SMH 13304 SMNB 15218 ANSYS 5 3 SME 13304 AUG 1 1997 GMEXB 19318 dee vc en E NODAL SOLUTION EB iii iech EH Goze SUB 1 EH FLAT CIRCULAR ENDCAP ANALYSIS 1 TAN e Se _3212 ecircltan bmp 85 AVG EM 2215 RSYS 0 D eeng DMX 01186 um 11058 SMN 19871 154351 SMNB 13885 19904 SMX 19871 SMXB 19885 19871 15455 EN 11033 Emm 5524 EN 2 Em 2208 mm 0024 gm 11033 Em 15455 19871 DeepSea Power amp Light E 65 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 66 Rev 3 27 01 Under Pressure Version 4 0 User Manual Case 2 P
115. om the keyboard Conversions FtSea 0 444 Sqr 0 444 4 0 3 1000 PsiVal 2 0 3 1000 Case Ft sea Conversion 1 Case Ft fresh Conversion 1 0 984 Case m sea Conversion 0 3048 Case m fresh Conversion 0 3048 0 984 DeepSea Power amp Light C 3 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light C 4 Rev 3 27 01 Under Pressure Version 4 0 User Manual APPENDIX D PRESSURE VESSEL STRESSES STRESSES Tube Sphere HOOP STRESS PERPENDICULAR TO CROSS SECTION SHOWN HOOP STRESS PERPENDICULAR TO CROSS SECTION SHOWN e Meridianal stress Hoop stress for both thin and thick equations and for both external and internal pressure loading e Axial stress Hoop stress for thin wall equations for both external and internal pressure loading e Axial stress l Hoop stress at Tube I D for thick wall equations for external pressure loading STRESSES Continued DeepSea Power amp Light D 1 Rev 3 27 01 Under Pressure Version 4 0 ENDCAP Flat Annular Conical TANGENTIAL STRESS PERPENDICULAR TO CROSS SECTION SHOWN AVG SEAT STRESS HOOP STRESS PERPENDICULAR TO CROSS SECTION SHOWN E AVG SEAT STRESS e Meridianal stress Hoop stress for both thin and thick wall equations and for both external and internal pressure loading STRESSES Continued DeepSea Power amp Light D 2 HOOP STRES PERPENDICULAR T
116. ompared to Ultimate Strength or Working Strength whichever 1s active D Maximum equivalent membrane stress von Mises stress constant energy of distortion stress compared to Yield Strength see theory 4 pg 26 of Roark s Maximum shear stress compared to V of Yield Strength when internal pressure and thick walled formulas are used see theory 2 pg 26 of Roark s E Maximum hoop stress compared to Ultimate Strength or Working Strength whichever is active Maximum shear stress compared to 12 of Ultimate Strength or 2 of Working Strength whichever is active F Maximum membrane stresses radial and tangential compared to Ultimate Strength tensile for both external and internal pressure loading Average seat stress compared to Ultimate Strength compressive for external pressure loading G Maximum membrane stresses radial and tangential and average seat stress compared to Yield Strength see theory 1 pg 26 of Roark s Maximum shear stress compared to 1 2 of Yield Strength see theory 3 pg 26 of Roark s H Maximum membrane stresses radial and tangential and average seat stress compared to Ultimate Strength or Working Strength whichever is active Maximum shear stress compared to of Ultimate Strength or 2 of Working Strength whichever is active DeepSea Power amp Light C 2 Rev 3 27 01 Under Pressure Version 4 0 User Manual I Maximum hoop stress and average seat stress compared to Ultimate S
117. on Pressure Range The following information is provided for a tube analysis as a function of the selected pressure range Depth equivalent water Depth of selected pressure Max Axial Stress Maximum Stress in tube wall in direction of tube centerline axis Max Hoop Stress Maximum Stress in tube wall in direction normal to tube cross section Max Equiv Stress Maximum uniaxial stress that is equivalent to the three dimensional stress state that exists in the tube wall for predicting failure of ductile materials by comparison to the uniaxial yield strength dID displacement of tube Inner Diameter dOD displacement of tube Outer Diameter dLength Change in tube length An explanation of the orientation of the above stresses is provided in Appendix D PRESSURE VESSEL STRESSES Again the user has an option as to which units will be used to display the data in the results table Rows of data for an applied pressures at or greater than the calculated failure pressure are highlighted by the program as a warning to the user As discussed in Appendix C FORMULAS USED BY UNDER PRESSURE Maximum Equivalent Stress is used as a failure criteria for Metal Tubes and is not applicable to tubes fabricated from other Main Category Materials Ceramics Glass and Plastics SPHERE ANALYSIS Sphere Geometry DeepSea Power amp Light 48 Rev 3 27 01 Under Pressure Version 4 0 User Manual By selecting Analysis Type Sphere in the Application Win
118. or is actually required for flat annular endcap Select Done in the Analysis Dialog Box to return to the Geometry Dialog Box to iterate on required thickness until the design requirements of the aluminum alloy 7075 T6 flat annular endcap are met For aluminum alloy 7075 T6 a thickness of 1 48 is found to be adequate for this example as shown by setting up the Geometry Dialog Box below ef Flat Annular Endcap Simply Supported Free Free Diameter Thickness 6 0000 in d 1 4800 in d Cap Uutade Diameter Center Hole Diameter 6 5400 in d 1 0000 in d Enable Uniform Load Enable Line Load Update Done Loading Options Perform Analysis Cancel Radial Increments 50 EXAMPLE 3 GEOMETRY DIALOG BOX The Analysis Dialog Box for the geometry shown above appears as follows DeepSea Power amp Light 24 Rev 3 27 01 Under Pressure Version 4 0 User Manual K Under Pressure mm pd File Edit Materials Window Design Options Help E Flat Annular Endcap Analysis External Pressure Il SX Graph Report Pressure Range 1000 20000 psi JB B TM Theoretical Failure Radial moment failure at 17402 psi Dia 2 4286 inches Tangential moment failure at 6008 2 psi Dia 1 0000 inches CA Shear stress failure at 30587 psi Dia 6 0000 inches C Seat failure at 15558 psi os lucite Table eval dia De inches 1 0000 Helale ns D Unita Material ALUMINUM 7075 TE
119. p Graph Stress us Radial Location for 1 Ksi pressure 12 10 4 S ZS B wa Radial 4 Tangential 1 0 1 5 20 25 30 35 40 45 50 55 6 0 Diameter inches EXAMPLE 3 FLAT ANNULAR ENDCAP GRAPH Example 4 Plastic Tube Design Requirements Acetal Plastic Delrin Cylindrical Camera Housing for Undersea service 200 ft sea water external pressure Minimum internal diameter of 4 00 Internal Length of 10 00 Minimum safety factor of 3 0 on buckling Maximum Membrane Stress in Plastic of 3000 psi at design depth 200 ft sea water Cylindrical housing to generate 6 Ib of positive buoyancy when submerged Procedure Follow the steps outlined in GETTING STARTED and previous examples to set up the Under Pressure Application Window for this example Click on CHOOSE to open the Material Database Dialog Box Select Main Category Plastics by clicking on the scroll arrow and clicking on Plastics Select Sub Category Thermoplastics by clicking on the scroll arrow and clicking on Thermoplastics DeepSea Power amp Light 27 Rev 3 27 01 Under Pressure Version 4 0 User Manual Select Name PLASTIC ACETAL as a first option for this example by clicking on the scroll arrow and clicking on PLASTIC ACETAL Click on Edit Record Use the cursor and keyboard to change Working Strength to 3 Ksi Click on Done The Material Database Dialog Box should appear as follows i 2 Under Pressure File Edi
120. ply Supported Edge Restraint Plate cross section with applied pressure B C s ecircl bmp Under Pressure numerical stress results B Flat Circular Endcap Analysis External Pressure fe x Pressure Range 1000 20000 psi E Report Done Material Theoretical Failure Geh Radial Stress Failure at 1767 7 psi plate center Test Aluminum CH Tangential Stress Failure at 1767 7 psi plate center CH Seat failure at 10694 psi Yield Strength 35000 psi Fail value unita Table eval da De plate center for Mas Radial Table eval da De plate center for Max Tangential Units Weight Ar wi 1 7671 Pressure Depth Stress Linear Deflection Angle Deflection Water wt 1 1126 psi sl Ft sea sl psi sl Inches sl Radians sl Units lbs z Pressure Depth De Mar Radial De MaxTan vgSeat pa Ft sea Stress psi Stress psi Stress psi 1000 0 2248 8 19800 19800 3272 f 1767 7 Fail 3970 6 35000 35000 5785 1 2000 0 fail 4430 3 33600 39600 6545 9 30010 0 Fail 6726 2 59400 59400 9818 2 psi Ux 4000 0 fail 13091 5000 0 fail 16364 6000 0 fail 19636 7000 0 fall pn 138600 138600 22309 8000 0 fail 26182 1 Maximum Radial Stress 19 800 psi Location plate center 2 Maximum Tangential Stress 19 800 psi Location plate center Finite Element Method graphical stress results FEA model element mesh pressure loading B C s fr
121. psi CH Shear failure N A eld Strength 35 Ki Fail value units Weight Uni Ar wt 0 54193 rite Pressure Depth Stress Linear Deflection Angle Detlection Water wt U 0 78521 ps sl Ft sea psi Inches sl Radians Units libs ee Pressure Deng Max Meridional ps Ft sea Stress psi Stress psi 2248 8 4544 4 4544 4 4544 4 4430 3 3088 8 3088 8 1088 8 p i Y 6726 2 13633 13633 13633 8954 8 18178 18178 18178 11177 22722 22722 22722 13392 27266 27266 27266 15601 31811 31811 31811 7701 8 fai EET 35000 35000 35000 8000 0 fail 17804 36355 36355 36355 HEMISPHERICAL ENDCAP ANALYSIS DIALOG BOX EXAMPLE Clicking on the scroll arrow adjacent to the two boxes titled Distortion Pressure Range at the top of Hemispherical Endcap Analysis Dialog Box allows the user to select the range of pressure in units of psi or Bar that will be used with the data in the results table below For example if psi is selected as the pressure units of choice one of the following pressure ranges can be selected for presenting the results 0 1 2 psi 1 20 psi 10 200 psi 100 2000 psi 1000 20 000 psi 10 000 200 000 psi The Theoretical Failure portion indicates the pressure or depth at which the four modes of failure for a hemispherical endcap analysis Thin Wall Buckling Shell Failure Seat Failure and Shear Failure occur The mode of failure that occurs at the lo
122. quired to install the drivers for the software key Follow the on screen directions to install Carefully review the readme file during or after installation INSTALLING THE HARDWARE LOCK Under Pressure is copy protected using a hardware device called a hardware lock or dongle The hardware lock only permits one copy of Under Pressure to run at a time Attempting to run Under Pressure on more than one computer at a time or attempting to defeat the intention of the hardware lock is a violation of the owner s copyright and is punishable by criminal and civil penalties Attach the hardware lock supplied with the program on the parallel printer port at the rear of the computer If you do not have a printer place the hardware lock in the port by itself If you have a printer disconnect the printer cable then attach the hardware lock to the port then attach the printer cable to the hardware lock Your printer and all other computer operations will be unaffected by the presence of the hardware lock DeepSea Power amp Light 3 Rev 3 27 01 Under Pressure Version 4 0 User Manual POLICY ON THE HARDWARE LOCK Under Pressure is multiple use protected by a device called a hardware lock The hardware lock must be attached to the computer on which Under Pressure is running The hardware lock prevents more than one copy of Under Pressure from running at one time The registered user of the Under Pressure software is allowed to install the Under Press
123. r Under Pressure E e M1 The ratio of plate free diameter to plate thickness is 4 analysis results may not be valid DeepSea Power amp Light 54 Rev 3 27 01 Under Pressure Version 4 0 User Manual The maximum deflection of the plate does not exceed one half the plate thickness If this assumption is violated the results of the analysis may not be valid and the following warning will appear Under Pressure Ea G Maximum plate deflection exceeds half the thickness Analysis results may not be valid for all pressures in the table Flat Annular Endcap Analvsis Results The following Flat Annular Endcap Analysis Dialog Box from Example 3 of this manual will be used to highlight the data and options available to the user after an analysis has been performed des Under Pressure File Edi Materials Window Design Options Help Flat Annular Endcap Analysis External Pressure Pressure Range 1000 20000 psi sl E IIT Graph Report Done Theoretical Failure CH Radial moment failure at 17402 psi Dia 2 4286 inches Ch Tangential moment failure at 6008 2 psi Dia 1 0000 inches CH Shear stress failure at 30587 psi Dia 6 0000 inches CH Seat failure at 15558 psi SCH Table eval da De inches 11 0000 Reale e wl E nits Pressure Depth Stress Linear Deflection Angle Deflection Waler Wl E sl Fe sea psi sl Inches sl radians sl Units Ibs Y o B Radial De Tange
124. r As discussed in Appendix C FORMULAS USED BY UNDER PRESSURE the maximum radial and tangential membrane stresses occur on the flat surfaces of the flat annular plate with the concave side of the plate loaded in compression and convex side of the plate loaded in tension the radial and tangential membrane stresses are zero at the plate midthickness Selecting GRAPH generates a plot of the radial and tangential stresses in the plate for a 1 Ksi external pressure load as a function of the location along the plate diameter These graphs aid the user in visualizing the state of stress in the Flat Annular Endcap CONICAL ENDCAP ANALYSIS Conical Endcap Geometry By selecting Analysis Type Endcap Only in the Application Window selecting Endcap Configuration Conical and clicking on Enter Geometry the program user can access the Conical Endcap Geometry Dialog Box fae Edit MMaternals Window Ele Edit Materials Window Design Opts eee Options L MConicalEndcap 0 s sSSSS gt MConicalEndcap 0 s sSSSS gt Base Inside Diameter Wall Thicknes m Base Outside Diameter Conical Duker Height KR f Maintain L D constant Maintain O D constant Update Done E Perform Analysis Cancel SE 77 ICAL ENDCAP GEOMETRY DIALOG BOX DeepSea Power amp Light 57 Rev 3 27 01 Under Pressure Version 4 0 User Manual Conical Endcap geometry is defined by the variables Conical Inside Diameter I D Conical Outsid
125. ree diameter except when calculating seat stress The strengthening effect of this additional material 1s not considered in these calculations Estimate Plate thickness and enter the corresponding value using the cursor and keyboard Click on Perform Analysis to generate analysis results Review the analysis results in the Analysis Dialog Box For this example a minimum safety factor of 2 0 was desired on stress for a design pressure of 4500 psi Therefore the Theoretical Failure portion of the Analysis Dialog Box titled Flat Circular Endcap Analysis External Pressure for this example should indicate that Radial Stress Failure Tangential Stress Failure and Seat Failure occur at a pressure greater than or equal to 9000 psi Safety Factor equals Failure Pressure Maximum Service Pressure or 9000 4500 z 2 Under Pressure provides a calculation of the maximum shear stress in flat circular endcaps The maximum shear stress occurs at the plate free diameter and is equal to Pxd 4xt where P applied pressure d plate free diameter and t plate thickness Shear stresses are insignificant as compared to radial and tangential stresses for flat circular plates unless the ratio of the plate thickness to plate free diameter t d approaches 3 8 for a fixed edge restraint or 5 8 for a simply supported edge restraint these ratios assume a Poissons s Ratio of 3 and a shear strength equal to 2 of the uniaxial strength Select Done in the Analysis
126. rt Done Material Test Aluminum Theoretical Failure C Thin all Buckling H A Geh Shell failure at 1111 7 psi Thin wall eqs C Seat failure at 3548 1 psi CH Shear failure NA Yield Strength 35000 psi Fail value units Weight Air wt 0 29370 Pressure Depth Stress Linear Deflection Angle Deflection Water wt D 42105 psi Ft sea sl Sg Inches sl radians Units Ir sl Pressure Deph Max Meridional MaxHoop Ma toute ps jJFt sea Stress psi Stress psi Stress psi 1000 0 2248 8 18178 36355 31484 D 1111 7 fai 24995 20207 405 00 2000 0 fail 62969 3000 0 fail 94453 4000 0 fail 8954 8 L n 14 125940 5000 0 fail 11177 30888 IE 1157420 6000 0 fail ES EE LE E ECO ET 1188910 7000 0 fai 15601 12720 25440 220390 8000 0 fail 251870 RE 1 Maximum Hoop Stress 36 355 psi psi SZ Units Finite Element Method graphical stress results FEA model element mesh pressure loading from econlmod bmp Hoop stress contour econelhoop bmp 1 Maximum Hoop Stress 34 243 psi DeepSea Power amp Light E 59 Rev 3 27 01 Under Pressure Version 4 0 User Manual Discussion Under Pressure based on the formulas given in Appendix C and the conical endcap finite element model provide similar results for peak hoop stress Appendix D defines the orientation of the hoop stresses in the
127. ry is defined by the variables Hemispherical Inside Diameter I D and Hemispherical Outside Diameter O D Alternatively the variable Wall thickness can be used in conjunction with either I D or O D to define the hemispherical endcap geometry APPENDIX A PRESSURE VESSEL GEOMETRIES shows a figure of a hemispherical endcap and the variables used to define its geometry File Edt Matera Window Design Options Not saved nk oe i r Hemispherical Endcap E Hemispherical Inside Diameter Wall Thickness Se Se Hemispherical Outside Diameter KS Ge Maintain ID constant Maintain O D constant Update Done Perform Analysis Cancel HEMISPHERICAL ENDCAP GEOMETRY DIALOG BOX While analyzing a hemispherical endcap design the option buttons Maintain I D constant and Maintain O D constant can be used to constrain either the I D or the O D for successive iterations of a hemispherical endcap design After using the cursor and keyboard to define the endcap geometry a three dimensional view of the resulting hemispherical shell geometry is generated on the left hand side of the Hemispherical Endcap Geometry Dialog Box DeepSea Power amp Light 62 Rev 3 27 01 Under Pressure Version 4 0 User Manual Clicking on Done saves the geometry and closes the Hemispherical Endcap Geometry Dialog Box Clicking on CANCEL closes the Hemispherical Endcap Geometry Dialog Box without saving user input Clicking on Perfor
128. s are defined by a value of stress yield strength at which permanent deformation of the material is initiated The commencement of permanent deformation yielding of a ductile material is generally considered to be the point at which material failure occurs for the purposes of performing structural analysis The magnitude of uniaxial stress that initiates yield of ductile materials is essentially the same for either a compressive or tensile load Main Category Materials such as Plastics are typically characterized by material strengths that are heavily dependent upon service temperatures and duration of applied load creep behavior For this reason it is often convenient to define these materials in terms of an Ultimate Strength and a Working Strength when performing structural analysis of plastic materials The Ultimate Strength of a plastic is the stress required to fail a material for a short term load applied at room temperatures The Working Strength of a plastic 1s the maximum allowable stress selected by the designer to account for the effects of creep behavior or any other factors that could effect the structural performance of the plastic In general the material database provided by Under Pressure uses a working strength equal to 1 10 of the ultimate strength The working strengths given in Under Pressure may be conservative for some applications It is recommended that the program user consult supplier s technical data sheets for the specif
129. sent In the following sample design we want to generate a printout of the properties of a tube type pressure vessel made from 4 schedule 80 PVC 10 in length 38260 p E 0 3270 fin E The ID pm x 1m fi E d D rdacisnl D corstant OO Marten D D coen Lind ate P Tube Analesiz Exleenel Poezii Precu Haus bh ate sl Then etical Faima Dhan Wad Behia s 0 8 5 B2 Esby 2 nodes O Selja at DEN SF Es Thick s eda 3 a Friuie KH OS O Shear liue Fl ied sd eal PLASTIC FOLTANTL CHLORIDE PVC Uleies Strength E Ezi Miot ke Srerg ke Le Es Weit D F L PL Prete Depth flyer Linger Deflection nga Defector aa Wi I n loas E AE D SS EI DES di Uni bs DeepSea Power amp Light 71 Rev 3 27 01 Under Pressure Version 4 0 User Manual A printed report can be generated only when the Analysis window is active When it is active the Print Setup and Print menu options under the file menu become available In order to print you can select Print from the File menu It will pull up the print dialog box similar to that seen below Note that the printer information will depend on your printer Printer Name Froperties Status Beach Type HF LaserJet ZA 4My PostScript where SSDEEP TREESHP AMV QUE DEEPSEE Comment Print to file Print range
130. ser Manual DeepSea Power amp Light E 30 Rev 3 27 01 Under Pressure Version 4 0 User Manual Case 6 Plate Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Center Hole Diameter 1 00 Simply Supported Outer Edge Restraint Guided Inner Center Hole Edge Restraint Plate cross section with applied pressure B C s eann6 bmp Under Pressure numerical stress results E Flat Annular Endcap Analysis External Pressure Pressure Range 1000 20000 ps eg Theoretical Failure Radial moment failure at 1212 4 psi Dia 1 0000 inches CH Tangential moment Failure at 2324 3 psi Dia 2 1428 inches O Shear stress failure at 8750 0 psi Dia 5 0000 inches CH Seat failure at 10694 psi Table eval Unita Pressure Pressure pa Ft sea IStress psi Stress psi ___ Stress psi 1000 0 Graph Report Material Test Aluminum Yield Strength S5000 psi Fail value units dia De inches Rekalt ps Depth Stress Linear Deflecton Angle Deflection P sea ps Inches E Degrees Depth De Radial De Tangential Wi eight Ar wt 1 7181 Water wt 1 0817 Units lbs 2248 8 26069 4660 9 0 0000 1212 4 fail 2725 5 35000 10500 0 0000 2000 0 Fail 4490 9 57739 17322 0 0000 3000 0 Fail 6726 2 86608 25982 0 0000 4000 0 fail 8954 8 1540 3643 10 0000 5000 0 fail 177 14450 43304 0 0000
131. ses in shells and tangential and radial stresses in plates are compared to uniaxial strengths of the material to predict failure Shear stresses are compared to shear strengths of the material to predict failure Uniaxial strengths Yield Strength for Metals Ultimate Tensile and Compressive Strengths for Ceramics and Glass and Ultimate and Working Strengths for Plastics are provided by the program material database or added by the user to predict material failure due to bearing and membrane stresses Under Pressure predicts material failure due to shear stresses based on the criteria that the shear strength of the material is equal to 1 2 of its uniaxial strength This failure criteria for shear is known as the Maximum Shear Stress Theory The type of uniaxial DeepSea Power amp Light 39 Rev 3 27 01 Under Pressure Version 4 0 User Manual material strength used by Under Pressure to perform a pressure vessel analysis depends on the behavior of the material Main Category materials such as Ceramics and Glass are characterized by large differences in the magnitudes of the material s tensile strength and compressive strength Consequently in evaluating stresses in Ceramic Glass and similar brittle materials it is essential to compare tensile stresses to tensile strengths and to compare compressive stresses to compressive strengths Main Category Materials such as Metals are typically characterized as ductile materials Ductile material
132. ssure Analysis Options Ce English C Internal Force Thick Wall Equations C Metric Ge External Use Working Strength for Plastic Analysis Type Tube Enter Geometry Under Pressure Application Window SETTING PROJECT PARAMETERS Use the cursor and keyboard to enter user defined Project Parameters Project Title Project Description Project Designer SETTING DESIGN PARAMETERS Select pressure vessel Material Click on CHOOSE in the Under Pressure Application Window to open the Material Database Dialog Box alternatively the Material Database Dialog Box can be accessed by clicking on Materials on the menu bar in the Application Window and clicking on View Material or by entering Alt M V from the keyboard Click on the appropriate Main Category of the desired material by clicking on the scroll arrow and clicking on choice Click on the appropriate Sub Category of the desired material by clicking on the scroll arrow and clicking on choice Click on the Name of the desired material by clicking on the scroll arrow and clicking on choice DeepSea Power amp Light 6 Rev 3 27 01 Under Pressure Version 4 0 User Manual Click on Done i a Under Pressure Matenal Database Main Catesory DS Sub Category Update Search i Edit Controls Hame Edit Record Yield Strength A H Young s Modulus hipsi Delete WI Density Ib cu in H _ Poisson s Ratio Cancel Comments
133. sults for pressure vessel geometries that closely approximate the formulas Under Pressure can also help approximate more complex designs prior to the much more time consuming application of the finite element method of stress analysis Under Pressure contains a database of commonly used pressure vessel materials that can be easily edited and supplemented for the user s specific needs Under Pressure evaluates structural capabilities deflections and weights of common pressure vessel geometries such as cylindrical tubes spheres as well as hemispherical conical flat circular and flat annular end closures This program was developed primarily for the oceanographic instrument designer but it lends itself to all types of pressure vessel calculations Under Pressure assumes that the designer understands the application of these formulas to his or her specific vessel design problem The designer must manually iterate on wall thickness to achieve the safety factor and material sizing appropriate to the particular problem Under Pressure is NOT an automated pressure vessel design program Under Pressure will NOT calculate exact stresses for real world geometry The elastic formulas apply only to idealized pressure vessel configurations and the designer must interpret and apply these results as appropriate See Appendix E for comparisons to Finite Element Method FEA analysis Under Pressure cannot evaluate the impact of tolerances out of round condi
134. sure ranges can be selected for presenting the results 0 1 2 psi 1 20 psi 10 200 psi 1000 20 000 psi 10 000 200 000 psi DeepSea Power amp Light 47 Rev 3 27 01 Under Pressure Version 4 0 User Manual The Theoretical Failure portion indicates the pressure or depth at which the two modes of failure for a tube analysis Thin Wall Buckling and Shell Failure occur The mode of failure that occurs at the lowest least in magnitude pressure is highlighted with the aid of an option button Since failure by buckling requires at least some compressive loading this failure mode will be non applicable N A for an internal pressure analysis of a tube design Clicking on the scroll arrow adjacent to the Fail value units box allows the user to select the units that are used for presenting the Theoretical failure values Ks Kbar psi Bar Ft sea Ft fresh m sea m fresh The upper right hand portion of the Tube Analysis Dialog Box provides weights in air and water Air Wt and Water Wt with the option of expressing these values in either Ib or kg The weight in water when completely submerged assumes that the internal volume of the cylinder is empty e the cylinder is sealed at both ends with some type of endcap The bottom portion of the Tube Analysis Dialog Box provides a results table of applicable stresses and deflections for a tube analysis that are displayed as a function of the user selected Distorti
135. t Materials Window Design Options Matenal Database Mam Category 5 Update Search Sub Category Thermoplastics bd Edit Controls Name PL ASTIC ACETAL Edit Record Ultimate Strength Ezi Add Working Strength Ksi Delete Young s Modulus Hpi m Done Density Ib cu in Cancel Poisson s Ratio Comments Injection Molded or Extruded Unfilled Compressive Ultimate Strength 5 2 Ks Known Commercially as Celcon Delrin etc EXAMPLE 4 MATERIAL DATABASE DIALOG BOX Note In this instance the designer has elected to use a less conservative working strength of 3ksi versus that given in the provided database Click on Done to return to the Application Window Click the Units English Option Button Click the Pressure External Option Button Click the Analysis Options Force Thick Wall Equations Check Box Click the Analysis Options Use Working Strength for Plastic Check Box Select Analysis Type Tube by clicking on the scroll arrow and clicking on Tube The Under Pressure Application Window should appear as follows DeepSea Power amp Light 28 Rev 3 27 01 Under Pressure Version 4 0 User Manual Under Pressure Oxy Fil Edit Materials Window Design Options EXAMPLE 4 PHJ Project Parameters Project Title Example 4 Project Description acetal plastic cylindrical housing for 200 feet sea water service Project Designer RPJ Design Parameters H aterial PLASTIC ACETAL Choose Units Pressur
136. tial Stress maximum Stress in plate in direction normal to plate cross section at user selected evaluation Diameter De Shear Stress Shear Stress in plate at user selected evaluation Diameter De Vert Defl Deflection of plate in direction of plate centerline at user selected evaluation Diameter De Angular Angular rotation of plate cross section at user selected evaluation Diameter HD Radial Stress maximum Hole Diameter Radial Stress HD Tangential Stress maximum Hole Diameter Tangential Stress HD Shear Stress Hole Diameter Shear Stress HD Vert Defl Hole Diameter Vertical Deflection HD Angular Hole Diameter Angular rotation FD Radial Stress maximum Free Diameter Radial Stress DeepSea Power amp Light 56 Rev 3 27 01 Under Pressure Version 4 0 User Manual FD Tangential Stress maximum Free Diameter Tangential Stress FD Shear Stress Free Diameter Shear Stress FD Vert Defl Free Diameter Vertical Deflection FD Angular Free Diameter Angular rotation Avg Seat Stress Average bearing Stress on annular area of plate between plate outside diameter and plate free diameter An explanation of the orientation of the above stresses is provided in Appendix D PRESSURE VESSEL STRESSES Again the user has an option as to which units will be used to display the data in the results table Rows of data for an applied pressures at or greater than the calculated failure pressure are highlighted by the program to warn the use
137. tion Tube Formula Assumptions Stress Analysis Stress analysis results for a tube analysis assume that the ends of the tube are capped closed by endcaps The membrane axial and hoop stress results that are presented for a tube analysis are only valid for locations in the tube away from the tube endcap interface An analysis of the stresses in the tube at the tube endcap interface is beyond the scope of Under Pressure Buckling Analysis Buckling analysis results presented for a tube analysis assume that the ends of the tube are capped closed by endcaps and that the endcaps hold the ends of the tube circular The DeepSea Power amp Light 46 Rev 3 27 01 Under Pressure Version 4 0 User Manual validity of this assumption is dependent upon the type of endcap used and the amount of support it provides the ends of the tube For example this assumption would be better approximated by a relatively rigid thick flat circular endcap than by a relatively compliant thin walled hemispherical endcap Buckling of tubes is dependent on the tube material s elastic constants and geometry and is independent of the tube material s strength As discussed in Example 1 of this manual out of roundness of tubes can impact buckling resistance If the ratio of the tube mean radius tube wall thickness is less than or equal to 10 the results of the buckling analysis may not be valid Tube Analysis Results The following Tube Analysis Dialog Box from E
138. tions material variations tempering variations surface damage in brittle materials under tension O ring sealing grooves stress concentrations off center holes in round end caps etc A sophisticated application of the finite element method 1s required to model such situations Most importantly Under Pressure is no substitute for good engineering practices No pressure vessel design should ever be considered complete until a qualified engineer has checked the calculations performed by the software and verified the appropriateness of their application to the specific problem and confirmed that the results are reasonable This is particularly important when a design is to be fabricated and human safety and or significant costs are involved It is the engineer s responsibility to check the results of Under Pressure not the other way around It is our hope that Under Pressure will aid pressure housing designers in efficiently creating more reliable higher quality designs DEEPSEA POWER AND LIGHT DeepSea Power and Light was founded in 1983 with the goal of providing high quality innovative products to the oceanographic community Initially manufacturing deep water power systems the company s expertise has grown along with its product line to include underwater video and lighting systems as well as video pipe inspection systems All of DeepSea s standard products are rigorously DeepSea Power amp Light Rev 3 27 01 Under Pressure V
139. trength tensile for internal pressure loading or compared to Ultimate Strength compressive for external pressure loading J Maximum equivalent membrane stress von Mises stress constant energy of distortion stress and average seat stress compared to Yield Strength see theory 4 pg 26 of Roark s K Maximum hoop stress and average seat stress compared to Ultimate Strength or Working Strength whichever is active L Maximum equivalent membrane stress von Mises stress constant energy of distortion stress compared to Yield Strength see theory 4 pg 26 of Roark s Average seat stress compared to Yield Strength Maximum shear stress compared to 2 of Yield Strength when internal pressure and thick walled formulas are used see theory 2 pg 26 of Roark s M Maximum hoop stress and average seat stress compared to Ultimate Strength or Working Strength whichever is active Maximum shear stress compared to 2 of Ultimate Strength or 2 of Working Strength whichever is active N Maximum membrane stresses radial and tangential and average seat stress compared to Yield Strength see theory 1 pg 26 of Roark s O Maximum membrane stresses radial and tangential and average seat stress compared to Ultimate Strength or Working Strength whichever is active NOTE Formula references can be accessed by clicking on Window on the menu bar of the Application Window and clicking on References or by entering Altt W R fr
140. ube DeepSea Power amp Light E 4 Rev 3 27 01 Under Pressure Version 4 0 ENDCAP LOAD APPLIED 10 000 LENGTH RALLY EE 1 000 WALL THICKNESS TUBE ANALYSIS DWG etubel bmp ANSYS 5 3 AUG 1 1997 10 36 17 NODAL SOLUTION STR P 1 SUB 1 TIME 1 Si AVG RSYS 0 DMX 001192 SMN 4074 SMNB 4075 SMX 3080 SMXB 3080 4074 3964 wm 3854 wm C C TUBE ANALYSIS HOOP mm 7777 etubelhoop bmp 3412 Ems 3301 ES 3121 3080 DeepSea Power amp Light E 5 User Manual ANSYS 5 3 AUG 1 1597 10733231 ELEMENTS TYPE NUM U PRES A zv zl DIST 5 5 XF 3 YF 3 E TUBE ANALYSIS MOD etubelmod bmp ANSYS 5 3 AUG 1 1997 10235218 NODAL SOLUTION STEP 1 SUB 1 TIME 1 SY AVG RSYS 0 DMX 001192 SMN 2042 SMNB 2043 SMX 2042 SMXB 2041 2042 EH 5042 TUBE ANALYSIS AXIAL etubelaxial bmp Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 6 Rev 3 27 01 Under Pressure Version 4 0 SPHERE ANALYSIS Sphere I D 5 00 Wall thickness 1 00 Sphere cross section with applied pressure espherel bmp Under Pressure numerical stress results E Sphere Analysis External Pressure User Manual Pressure Range 1000 20000 psi sl Bee sl Done Theoretical Failure Material C Thin Wall Buckling at 405560 psi Shell failure at 14830 psi Thick wall ege C Seat failure N A CH Shear failure N A
141. units Weight Ai wt 11 7382 Water wt 0 68605 Units lbs T pi Units Pressure Depth Stress Linear Deflection Angle Deflection psi sl Fe seal psi sl Inches Radians Pressure Depth Max Meridional Max Hoop Max Equiv psi Ftiseal Stress psi Stress pg Stress psi 1000 0 2000 0 3000 0 4000 0 5000 0 6000 0 2248 8 4490 9 6726 2 8954 8 11177 13392 5535 1 11070 16605 22140 27675 33210 35000 5535 1 11070 16605 22140 21679 33210 35000 5935 1 11070 16605 22140 27575 33210 35000 6323 3 fail 14107 000 0 Fail 17804 44280 44280 44280 20 n V n n V V V n V 7000 0 Fail 15601 38745 38745 38745 SPHERE ANALYSIS DIALOG BOX EXAMPLE Clicking on the scroll arrow adjacent to the two boxes titled Distortion Pressure Range at the top of Sphere Analysis Dialog Box allows the user to select the range of pressure in units of psi or Bar that will be used with the data in the results table below For example if psi is selected as the pressure units of choice one of the following pressure ranges can be selected for presenting the results 0 1 2 psi 1 20 psi 10 200 psi 1000 20 000 psi 0 000 200 000 psi The Theoretical Failure portion indicates the pressure or depth at which the three modes of failure for a sphere analysis Thin Wall Buckling Shell Failure and Shear F
142. ure software on more than one computer as long as there is no possibility that more than one copy of Under Pressure will be running at one time For example the user is allowed to install the Under Pressure software on a computer at work and another computer at home as long as the two installations of Under Pressure are never used at the same time The hardware lock must be physically moved from one computer to another so that only one copy of Under Pressure can be run at one time The hardware lock supplied with the Under Pressure software is worth the full purchase price of the software If the hardware lock is lost or stolen it will not be replaced without payment of the full purchase price Insure the hardware lock as you would any other business or personal asset of comparable value DeepSea Power amp Light 4 Rev 3 27 01 Under Pressure Version 4 0 User Manual GETTING STARTED NOTE Most of the information in this manual is also available by clicking Help on the menu bar of the Under Pressure Application Window or by pressing the F1 key on the keyboard STARTING THE UNDER PRESSURE APPLICATION WINDOW From Windows Start menu choose the Under Pressure program by clicking on it Select OK if you accept the conditions of the Liability Disclaimer Box by single clicking on it to open the Under Pressure Application Window i a Under Pressure EI sl Bier EE Materiae IET GET Deeian Untere Liability Disclaimer DeepSea Power amp L
143. west least in magnitude pressure is highlighted with the aid of an option button Since failure by buckling requires at least some compressive loading this failure mode will be non applicable N A for an internal pressure analysis of a sphere design Clicking on the scroll arrow adjacent to the Fail value units box allows the user to select the units at which failure will be presented Ksi Kbar DeepSea Power amp Light 64 Rev 3 27 01 Under Pressure Version 4 0 User Manual psi Bar Ft sea Ft fresh m sea m fresh The upper right hand portion of the Hemispherical Endcap Analysis Dialog Box provides weights in air and water Air Wt and Water Wt with the option of expressing these values in either lbs or kg The weight in water when completely submerged assumes that that the internal volume of the hemispherical endcap is empty The bottom portion of the Hemispherical Endcap Analysis Dialog Box provides a results table of applicable stresses and deflections for an analysis that are displayed as a function of the user selected Distortion Pressure Range The following information is provided for an analysis as a function of the selected pressure range Depth equivalent water Depth of selected pressure Max Meridional Stress Maximum Stress in hemisphere wall in direction of hemisphere cross section meridian Max Hoop Stress Maximum Stress in hemisphere wall in direction normal to hemisphere cross section
144. x titled Tube Analysis External Pressure for this example should indicate that Thin Wall Buckling and Shell Failure occur at a pressure greater than or equal to 9000 psi Safety Factor equals Failure Pressure Maximum Service Pressure or 9000 4500 2 A DeepSea Power amp Light 14 Rev 3 27 01 Under Pressure Version 4 0 User Manual safety factor of two was arbitrarily selected for this example In actual practice the safety factor that is selected will depend on the specific requirements of the pressure vessel and the confidence of the pressure vessel designer In addition to specific requirements that may exist safety factors should be used by the pressure vessel designer to account for any number of variables that could affect the structural performance of a pressure housing design Variables that could affect the pressure housing performance could include dimensional tolerances imperfections corrosion allowances material properties creep behavior duration of load temperature effects cyclic loading fatigue dynamic loading stress concentrations residual stresses etc Variations in the pressure vessel geometry allowed by dimensional tolerances on the pressure boundary components can significantly effect structural performance In particular buckling of shells subjected to external pressure is sensitive to any geometric imperfections that may exist Out of roundness ID OD or concentric and or wall thickness variations of tubes a
145. x is based on selected geometry and loading for example Sphere Analysis External Pressure DeepSea Power amp Light 9 Rev 3 27 01 Under Pressure Version 4 0 User Manual CIE Pressure File Edit Materials window Design Options Help ES Sphere Analysis External Pressure Pressure Range 1000 20000 psi k Ti Report Done Theoretical Failure Material O Thin wall Buckling at 2 2030 Kai ALUMINUM B061 T6 Geh Shell failure at 1 7284 Kai Thin wall eq s Yield Strength O Seat failure H A 35 Kal Shear failure N A Fail value units ksi D Weight Air wi Units Pressure Depth Stress Linear Deflection Angle Detection Water wt 16 940 IS D Ft sea Ir i D Inches D Fiadians x Units im sl Pressure Depth Max Meridional_ MaxHoop Max Equiv Stress Ksi i Sess Kai Ka 1 0000 2248 8 20 250 20 250 20 250 1 7284 Fail eo e e 35 000 2 0000 fail 40 500 3 0000 Fail 60 750 4 0000 fal 8954 81 000 81 5 0000 fail aos 6 0000 Fail Hzis TE 7 0000 fail 14 75 8 0000 fail SITE ESDT Analysis Dialog Box shown for Sphere Analysis REVIEWING ANALYSIS RESULTS The Analysis Dialog Box displays calculated results for the user defined design material geometry boundary conditions type of pressure loading external or internal etc Various scroll arrows allow the user to change the units used to display the analysis results The structure of the Analysis
146. xample 1 of this manual will be used to highlight the data and options available to the user after a tube analysis has been performed des Under Pressure zr Eile Edit Materials window Design Options Help E Tube Analysis External Pressure psi Report Done Pressure Range Material ALUMINUM 7075 TE Theoretical Failure Q Thin wall Buckling at 10632 psi by 2 nodes Geh Shell failure at 9040 1 psi Thick wall eq s CH Seat failure HAS C Shear failure H A eld Strength b Ks Fail value units pl sl Units Pressure Depth Stress Linear Deflection Angle Deflection water wt 10 470 psi sl Ft sea sl psi sl Inches Radians sl Units libs Pressure Depth Max Axial Ma Hoop MaxEquv psi sit sea Stress psi Stress psi Stress psi f 6726 2 11879 23758 8354 8 15833 31677 11177 19798 39597 13392 23758 47516 15601 27718 59435 Weight Airw 23 157 17804 31677 63354 20000 35637 71274 20088 39796 F 1591 62000 22130 393597 73133 58583 TUBE ANALYSIS DIALOG BOX EXAMPLE Clicking on the scroll arrow adjacent to the two boxes titled Distortion Pressure Range at the top of Tube Analysis Dialog Box allows the user to select the range of pressure in units of psi or Bar that will be used with the data in the results table below For example if psi is selected as the pressure units of choice one of the following pres
147. ximum Radial Stress 8442 psi Location 1 000 diameter 2 Maximum Tangential Stress 4745 psi Location see stress contour DeepSea Power amp Light E 40 Rev 3 27 01 Under Pressure Vers AN YT 1A 1 P5000 Free Diameter 2 500 575 Thickness I Ya LL LIC 21 000 Center Hole Diameter FLAT ANNULAR ENDCAP ANALYSIS 8 DWG eann8 bmp TOF REO HSDOCEORO TOEST ANSYS 5 3 AUG 1 15397 LESI BA ELEMENTS TYPE NUM FLAT ANNULAR ENDCAP ANALYSIS 8 MOD u eann8mod bmp PRES zy 1 OLST Leoa ANSYS 5 3 Asp 1 047 A Dr we YF 3125 NODAL SOLUTION STEE 1 SUB 1 TIME 1 FLAT ANNULAR ENDCAP ANALYSIS 8 RAD SE AVG eann8rad bmp GECKEN AMSYS 5 3 DS 001027 AUG 1 1997 MN DA 11 57 10 SHNE 25539 HODAL SOLUTION SMS 3d442 STEP 1 GMER ZA519 SUB mm R342 TIME 1 E 6566 a AVS zz 4690 BRSYS 0 2814 FLAT ANNULAR ENDCAP ANALYSIS 8 TAN DME 001027 m 937 999 eann8tan bmp SHH 4745 327 9099 H SMNB 25533 Tm 2614 GMS 24745 465 GMEB Z55 595 6556 47 5 294 3551 1582 527 25 1582 2616 2591 4745 DeepSea Power amp Light E 41 Rev 3 27 01 Under Pressure Version 4 0 User Manual DeepSea Power amp Light E 42 Rev 3 27 01 Under Pressure Version 4 0 Case 9 User Manual Plate Outside Diameter 6 00 Plate Free Diameter 5 00 Plate thickness 625 Center Hole Diameter 1 00 Guided Outer Edge Restraint Simply Supporte

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Manual - DeepSea Power & Light