{"id":111,"date":"2018-01-30T21:38:54","date_gmt":"2018-01-31T02:38:54","guid":{"rendered":"https:\/\/pressbooks.bccampus.ca\/powr4406\/?post_type=chapter&#038;p=111"},"modified":"2018-10-15T14:47:33","modified_gmt":"2018-10-15T18:47:33","slug":"pressure-vessels","status":"publish","type":"chapter","link":"https:\/\/pressbooks.bccampus.ca\/powr4406\/chapter\/pressure-vessels\/","title":{"raw":"Pressure Vessels","rendered":"Pressure Vessels"},"content":{"raw":"<div class=\"bcc-box bcc-highlight\">\r\n<h3 itemprop=\"educationalUse\"><strong>Learning Objectives<\/strong><\/h3>\r\nAt the end of this chapter you should be able to\r\n<ul>\r\n \t<li>Identify thin wall or thick wall pressure vessels<\/li>\r\n \t<li>Discuss the difference between longitudinal and circumferential stress<\/li>\r\n \t<li>Demonstrate the derivation of the stress formulas in a thin wall pressure vessel<\/li>\r\n \t<li>Perform thin wall pressure vessel design calculations<\/li>\r\n<\/ul>\r\n<\/div>\r\n<div class=\"textbox shaded\" style=\"text-align: center\"><strong>Thin-walled and thick-walled pressure vessels<\/strong><\/div>\r\nThe distinction between thin vs. thick wall pressure vessels is determined by the ratio between the mean radius of the vessel and the thickness of the wall.\u00a0 If this ratio is greater than 10, the vessel is considered a thin wall pressure vessel.\u00a0 If the ratio is less than 10, the vessel is considered a thick wall pressure vessel.\r\n\r\n<img src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig1.jpg\" alt=\"\" class=\"alignnone wp-image-112\" width=\"429\" height=\"66\" \/>\r\n\r\nIn operation, in a thin wall pressure vessel, stresses developed in the (thin) wall can conservatively be assumed to be uniform.\u00a0 These are the stresses students are familiar calculating using ASME Section I PG-27 or Section VIII Div. I UG-27.\u00a0 In fact, most of the pressure vessels power engineers will work with are of a thin-wall type.\r\n\r\nIn contrast, a thick wall pressure vessel develops a greater (circumferential) stress on the inside surface of the vessel and it reduces towards the outside diameter.\u00a0 The design calculations for this type of vessels are only covered in the ASME Section VIII (Pressure Vessels) code, Mandatory Appendix 1 (Supplementary Design Formulas).\r\n<div class=\"textbox shaded\" style=\"text-align: center\"><strong>Development of stress formula in a pressure vessel<\/strong><\/div>\r\n<div class=\"textbox shaded\">Circumferential stresses (longitudinal joints)<\/div>\r\nThe circumferential stress (or hoop stress) acting on a longitudinal cross-section is derived in the textbook as:\r\n\r\n<img src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig2-1.jpg\" alt=\"\" class=\"alignnone wp-image-121\" width=\"237\" height=\"58\" \/>\r\n\r\nDesign problems most typically deal with finding the minimum required wall thickness, therefore the above formula is more useful expressed as:\r\n\r\n<img src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig3.jpg\" alt=\"\" class=\"alignnone wp-image-117\" width=\"248\" height=\"70\" \/>\r\n\r\nHoop stress formula from ASME Section VIII Div. 1 UG-27 is:\r\n\r\n<img src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig4.jpg\" alt=\"\" class=\"alignnone wp-image-118\" width=\"173\" height=\"65\" \/>\r\n\r\nEfficiency \"E\" is a factor that accounts for loss of material strength due to welds or ligaments.\u00a0 Also note that applying \"-0.6P\" to the denominator leads to a thicker shell compared to the theoretical formula, and therefore more conservative (or safer).\u00a0 Before using the formula check if the relation is applicable (thin wall).\r\n\r\nASME Section I (Power Boilers) calculates the shell thickness only based on circumferential stress, as follows:\r\n\r\n<img src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig5.jpg\" alt=\"\" class=\"alignnone wp-image-119\" width=\"249\" height=\"68\" \/>\r\n\r\nThe formulas are quite similar; in the above \"y\" is a temperature coefficient and C is an added allowance for corrosion or structural stability.\u00a0 Again, the code formula leads to a thicker shell than simply based on derivations.\r\n<div class=\"textbox shaded\">Longitudinal stress (circumferential joints)<\/div>\r\nLongitudinal stress demonstrated and derived in the textbook is derived as:\r\n\r\n<img src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig6.jpg\" alt=\"\" class=\"alignnone wp-image-120\" width=\"344\" height=\"72\" \/>\r\n\r\nNote that longitudinal stresses are 50% of the hoop stresses and therefore they rarely govern the design.\u00a0\u00a0 This is the reason ASME Section I does not even require evaluating this stress.\r\n\r\nASME Section VIII Div. 1 requires estimating the vessel thickness based on both stresses, and choosing the largest of the two values.\u00a0 Formula is:\r\n\r\n<img src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig7.jpg\" alt=\"\" class=\"alignnone wp-image-122\" width=\"185\" height=\"62\" \/>\r\n<div class=\"textbox shaded\">Spherical pressure vessels<\/div>\r\nSpherical pressure vessel stress is calculated in the same way as the longitudinal stress.\u00a0 You may conclude that a spherical pressure vessel will require a thinner shell, theoretically one half, than a cylindrical pressure vessel operating at the same pressure and temperature, and therefore it would be a preferred shape.\u00a0 Reality is that while most of that is true, it is difficult to manufacture a spherical shell.\r\n<p style=\"text-align: left\">Follow the links for examples of pressure vessels:<\/p>\r\n\r\n<ul>\r\n \t<li><a href=\"https:\/\/en.wikipedia.org\/wiki\/Pressure_vessel#\/media\/File:Modified_Hanson_steelwatertank.jpg\" target=\"_blank\" rel=\"noopener\">A pressure vessel constructed of a horizontal steel cylinder.<\/a><\/li>\r\n \t<li><a href=\"https:\/\/en.wikipedia.org\/wiki\/Pressure_vessel#\/media\/File:Biogasholder_and_flare.JPG\" target=\"_blank\" rel=\"noopener\">Spherical gas container.<\/a><\/li>\r\n \t<li><a href=\"https:\/\/en.wikipedia.org\/wiki\/Pressure_vessel#\/media\/File:Methanier_aspher_LNGRIVERS.jpg\" target=\"_blank\" rel=\"noopener\">LNG carrier ship.<\/a><\/li>\r\n<\/ul>\r\n&nbsp;\r\n\r\n&nbsp;\r\n<div class=\"bcc-box bcc-info\">\r\n<h3 itemprop=\"educationalUse\"><strong>Assigned Problems<\/strong><\/h3>\r\n<ul>\r\n \t<li>The Pressure Vessel problems must be solved using the theoretical formulas developed in the textbook and NOT the ASME code formulas.<\/li>\r\n \t<li>Always check first if you are dealing with a thin-walled or a thick-walled pressure vessel.\r\n<ul>\r\n \t<li>Thick wall formulas will be provided if necessary.<\/li>\r\n<\/ul>\r\n<\/li>\r\n \t<li>Cylindrical vessels require both calculations (longitudinal and circumferential joints); you specify the final answer (minimum wall thickens or MAWP maximum allowable working pressure)<\/li>\r\n<\/ul>\r\n<\/div>\r\n<strong>Problem 1: <\/strong>Derive in detail the formulas for longitudinal and circumferential stresses acting on a cylindrical pressure vessel.\u00a0 Briefly discuss the results.\r\n\r\n<strong>Problem 2: <\/strong>A seamless pipe of 508 mm outside diameter is used as a header in a large power plant carrying steam at 2 MPa pressure.\u00a0 The standard lengths of pipe are butt-welded together to build a continuous pipe.\u00a0 The pipe material, SA-106 Grade C, has minimum Tensile Strength of 485 MPa and a safety factor of 3.5 based is specified.\u00a0 The allowable stress for the butt-welds is 110 MPa.\u00a0 Specify the minimum pipe wall thickness.\r\n\r\n<strong>Problem 3: <\/strong>A cylindrical tank 36\" diameter and 12 feet long, is used as a compressed air accumulator.\u00a0\u00a0 The tank is made of ASTM SA-36 rolled steel plate with a wall thickness of 3\/4\".\u00a0 Find the maximum allowable working pressure in the tank using a safety factor of 3.5 based on the Ultimate Strength.\r\n\r\n<strong>Problem 4: <\/strong>A large spherical storage tank for compressed nitrogen is 8.6 m diameter and is constructed using AISI 1040 cold rolled steel plate of 12 mm thickness.\u00a0 The maximum pressure in the tank is 0.66 MPa.\u00a0 If a design factor of 4 based on the Yield Strength is required, does the tank meet the specifications?\r\n\r\n<strong>Problem 5: <\/strong>Recommend one improvement to this chapter.","rendered":"<div class=\"bcc-box bcc-highlight\">\n<h3 itemprop=\"educationalUse\"><strong>Learning Objectives<\/strong><\/h3>\n<p>At the end of this chapter you should be able to<\/p>\n<ul>\n<li>Identify thin wall or thick wall pressure vessels<\/li>\n<li>Discuss the difference between longitudinal and circumferential stress<\/li>\n<li>Demonstrate the derivation of the stress formulas in a thin wall pressure vessel<\/li>\n<li>Perform thin wall pressure vessel design calculations<\/li>\n<\/ul>\n<\/div>\n<div class=\"textbox shaded\" style=\"text-align: center\"><strong>Thin-walled and thick-walled pressure vessels<\/strong><\/div>\n<p>The distinction between thin vs. thick wall pressure vessels is determined by the ratio between the mean radius of the vessel and the thickness of the wall.\u00a0 If this ratio is greater than 10, the vessel is considered a thin wall pressure vessel.\u00a0 If the ratio is less than 10, the vessel is considered a thick wall pressure vessel.<\/p>\n<p><img loading=\"lazy\" decoding=\"async\" src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig1.jpg\" alt=\"\" class=\"alignnone wp-image-112\" width=\"429\" height=\"66\" srcset=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig1.jpg 760w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig1-300x46.jpg 300w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig1-65x10.jpg 65w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig1-225x35.jpg 225w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig1-350x54.jpg 350w\" sizes=\"auto, (max-width: 429px) 100vw, 429px\" \/><\/p>\n<p>In operation, in a thin wall pressure vessel, stresses developed in the (thin) wall can conservatively be assumed to be uniform.\u00a0 These are the stresses students are familiar calculating using ASME Section I PG-27 or Section VIII Div. I UG-27.\u00a0 In fact, most of the pressure vessels power engineers will work with are of a thin-wall type.<\/p>\n<p>In contrast, a thick wall pressure vessel develops a greater (circumferential) stress on the inside surface of the vessel and it reduces towards the outside diameter.\u00a0 The design calculations for this type of vessels are only covered in the ASME Section VIII (Pressure Vessels) code, Mandatory Appendix 1 (Supplementary Design Formulas).<\/p>\n<div class=\"textbox shaded\" style=\"text-align: center\"><strong>Development of stress formula in a pressure vessel<\/strong><\/div>\n<div class=\"textbox shaded\">Circumferential stresses (longitudinal joints)<\/div>\n<p>The circumferential stress (or hoop stress) acting on a longitudinal cross-section is derived in the textbook as:<\/p>\n<p><img loading=\"lazy\" decoding=\"async\" src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig2-1.jpg\" alt=\"\" class=\"alignnone wp-image-121\" width=\"237\" height=\"58\" srcset=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig2-1.jpg 347w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig2-1-300x73.jpg 300w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig2-1-65x16.jpg 65w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig2-1-225x55.jpg 225w\" sizes=\"auto, (max-width: 237px) 100vw, 237px\" \/><\/p>\n<p>Design problems most typically deal with finding the minimum required wall thickness, therefore the above formula is more useful expressed as:<\/p>\n<p><img loading=\"lazy\" decoding=\"async\" src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig3.jpg\" alt=\"\" class=\"alignnone wp-image-117\" width=\"248\" height=\"70\" srcset=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig3.jpg 344w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig3-300x85.jpg 300w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig3-65x18.jpg 65w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig3-225x63.jpg 225w\" sizes=\"auto, (max-width: 248px) 100vw, 248px\" \/><\/p>\n<p>Hoop stress formula from ASME Section VIII Div. 1 UG-27 is:<\/p>\n<p><img loading=\"lazy\" decoding=\"async\" src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig4.jpg\" alt=\"\" class=\"alignnone wp-image-118\" width=\"173\" height=\"65\" srcset=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig4.jpg 319w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig4-300x113.jpg 300w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig4-65x24.jpg 65w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig4-225x85.jpg 225w\" sizes=\"auto, (max-width: 173px) 100vw, 173px\" \/><\/p>\n<p>Efficiency &#8220;E&#8221; is a factor that accounts for loss of material strength due to welds or ligaments.\u00a0 Also note that applying &#8220;-0.6P&#8221; to the denominator leads to a thicker shell compared to the theoretical formula, and therefore more conservative (or safer).\u00a0 Before using the formula check if the relation is applicable (thin wall).<\/p>\n<p>ASME Section I (Power Boilers) calculates the shell thickness only based on circumferential stress, as follows:<\/p>\n<p><img loading=\"lazy\" decoding=\"async\" src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig5.jpg\" alt=\"\" class=\"alignnone wp-image-119\" width=\"249\" height=\"68\" srcset=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig5.jpg 460w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig5-300x82.jpg 300w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig5-65x18.jpg 65w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig5-225x62.jpg 225w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig5-350x96.jpg 350w\" sizes=\"auto, (max-width: 249px) 100vw, 249px\" \/><\/p>\n<p>The formulas are quite similar; in the above &#8220;y&#8221; is a temperature coefficient and C is an added allowance for corrosion or structural stability.\u00a0 Again, the code formula leads to a thicker shell than simply based on derivations.<\/p>\n<div class=\"textbox shaded\">Longitudinal stress (circumferential joints)<\/div>\n<p>Longitudinal stress demonstrated and derived in the textbook is derived as:<\/p>\n<p><img loading=\"lazy\" decoding=\"async\" src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig6.jpg\" alt=\"\" class=\"alignnone wp-image-120\" width=\"344\" height=\"72\" srcset=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig6.jpg 568w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig6-300x63.jpg 300w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig6-65x14.jpg 65w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig6-225x47.jpg 225w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig6-350x73.jpg 350w\" sizes=\"auto, (max-width: 344px) 100vw, 344px\" \/><\/p>\n<p>Note that longitudinal stresses are 50% of the hoop stresses and therefore they rarely govern the design.\u00a0\u00a0 This is the reason ASME Section I does not even require evaluating this stress.<\/p>\n<p>ASME Section VIII Div. 1 requires estimating the vessel thickness based on both stresses, and choosing the largest of the two values.\u00a0 Formula is:<\/p>\n<p><img loading=\"lazy\" decoding=\"async\" src=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig7.jpg\" alt=\"\" class=\"alignnone wp-image-122\" width=\"185\" height=\"62\" srcset=\"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig7.jpg 338w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig7-300x100.jpg 300w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig7-65x22.jpg 65w, https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-content\/uploads\/sites\/290\/2018\/01\/Ch4Fig7-225x75.jpg 225w\" sizes=\"auto, (max-width: 185px) 100vw, 185px\" \/><\/p>\n<div class=\"textbox shaded\">Spherical pressure vessels<\/div>\n<p>Spherical pressure vessel stress is calculated in the same way as the longitudinal stress.\u00a0 You may conclude that a spherical pressure vessel will require a thinner shell, theoretically one half, than a cylindrical pressure vessel operating at the same pressure and temperature, and therefore it would be a preferred shape.\u00a0 Reality is that while most of that is true, it is difficult to manufacture a spherical shell.<\/p>\n<p style=\"text-align: left\">Follow the links for examples of pressure vessels:<\/p>\n<ul>\n<li><a href=\"https:\/\/en.wikipedia.org\/wiki\/Pressure_vessel#\/media\/File:Modified_Hanson_steelwatertank.jpg\" target=\"_blank\" rel=\"noopener\">A pressure vessel constructed of a horizontal steel cylinder.<\/a><\/li>\n<li><a href=\"https:\/\/en.wikipedia.org\/wiki\/Pressure_vessel#\/media\/File:Biogasholder_and_flare.JPG\" target=\"_blank\" rel=\"noopener\">Spherical gas container.<\/a><\/li>\n<li><a href=\"https:\/\/en.wikipedia.org\/wiki\/Pressure_vessel#\/media\/File:Methanier_aspher_LNGRIVERS.jpg\" target=\"_blank\" rel=\"noopener\">LNG carrier ship.<\/a><\/li>\n<\/ul>\n<p>&nbsp;<\/p>\n<p>&nbsp;<\/p>\n<div class=\"bcc-box bcc-info\">\n<h3 itemprop=\"educationalUse\"><strong>Assigned Problems<\/strong><\/h3>\n<ul>\n<li>The Pressure Vessel problems must be solved using the theoretical formulas developed in the textbook and NOT the ASME code formulas.<\/li>\n<li>Always check first if you are dealing with a thin-walled or a thick-walled pressure vessel.\n<ul>\n<li>Thick wall formulas will be provided if necessary.<\/li>\n<\/ul>\n<\/li>\n<li>Cylindrical vessels require both calculations (longitudinal and circumferential joints); you specify the final answer (minimum wall thickens or MAWP maximum allowable working pressure)<\/li>\n<\/ul>\n<\/div>\n<p><strong>Problem 1: <\/strong>Derive in detail the formulas for longitudinal and circumferential stresses acting on a cylindrical pressure vessel.\u00a0 Briefly discuss the results.<\/p>\n<p><strong>Problem 2: <\/strong>A seamless pipe of 508 mm outside diameter is used as a header in a large power plant carrying steam at 2 MPa pressure.\u00a0 The standard lengths of pipe are butt-welded together to build a continuous pipe.\u00a0 The pipe material, SA-106 Grade C, has minimum Tensile Strength of 485 MPa and a safety factor of 3.5 based is specified.\u00a0 The allowable stress for the butt-welds is 110 MPa.\u00a0 Specify the minimum pipe wall thickness.<\/p>\n<p><strong>Problem 3: <\/strong>A cylindrical tank 36&#8243; diameter and 12 feet long, is used as a compressed air accumulator.\u00a0\u00a0 The tank is made of ASTM SA-36 rolled steel plate with a wall thickness of 3\/4&#8243;.\u00a0 Find the maximum allowable working pressure in the tank using a safety factor of 3.5 based on the Ultimate Strength.<\/p>\n<p><strong>Problem 4: <\/strong>A large spherical storage tank for compressed nitrogen is 8.6 m diameter and is constructed using AISI 1040 cold rolled steel plate of 12 mm thickness.\u00a0 The maximum pressure in the tank is 0.66 MPa.\u00a0 If a design factor of 4 based on the Yield Strength is required, does the tank meet the specifications?<\/p>\n<p><strong>Problem 5: <\/strong>Recommend one improvement to this chapter.<\/p>\n","protected":false},"author":239,"menu_order":4,"template":"","meta":{"pb_show_title":"on","pb_short_title":"Vessels","pb_subtitle":"Vessels","pb_authors":[],"pb_section_license":""},"chapter-type":[],"contributor":[57],"license":[],"class_list":["post-111","chapter","type-chapter","status-publish","hentry","contributor-alex-podut"],"part":3,"_links":{"self":[{"href":"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-json\/pressbooks\/v2\/chapters\/111","targetHints":{"allow":["GET"]}}],"collection":[{"href":"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-json\/pressbooks\/v2\/chapters"}],"about":[{"href":"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-json\/wp\/v2\/types\/chapter"}],"author":[{"embeddable":true,"href":"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-json\/wp\/v2\/users\/239"}],"version-history":[{"count":25,"href":"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-json\/pressbooks\/v2\/chapters\/111\/revisions"}],"predecessor-version":[{"id":638,"href":"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-json\/pressbooks\/v2\/chapters\/111\/revisions\/638"}],"part":[{"href":"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-json\/pressbooks\/v2\/parts\/3"}],"metadata":[{"href":"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-json\/pressbooks\/v2\/chapters\/111\/metadata\/"}],"wp:attachment":[{"href":"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-json\/wp\/v2\/media?parent=111"}],"wp:term":[{"taxonomy":"chapter-type","embeddable":true,"href":"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-json\/pressbooks\/v2\/chapter-type?post=111"},{"taxonomy":"contributor","embeddable":true,"href":"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-json\/wp\/v2\/contributor?post=111"},{"taxonomy":"license","embeddable":true,"href":"https:\/\/pressbooks.bccampus.ca\/powr4406\/wp-json\/wp\/v2\/license?post=111"}],"curies":[{"name":"wp","href":"https:\/\/api.w.org\/{rel}","templated":true}]}}