api 5l x65 allowable stress

api 5l x65 allowable stress

api 5l x65 allowable stress

 Thickness:1-120mm
 Width:1500-3600mm
 Length:as custom's request
 Technique:Cold rolled or hot rolled
 Surface treatment:Bare/Shot Blasted and Spray Paint or as required.
 Standard:ASTM,EN,GB,JIS,DIN

Allowable stress for API 5L materials in ASME VIII ...

eng-tips› …› Boiler and Pressure Vessel engineering ForumOct 26, 2006· RE: Allowable stress for API 5L materials in ASME VIII calculations. stanweld (Materials) 18 Oct 06 09:23 MTR is the Materials Test Report defining the actual tensile properties obtained from coupons taken from the heat of material per the API 5L Specification.gbratis; Is this pipe for new construction of a pressure vessel or to repair/alter an existing pressure vessel??Suggest you get a MTR for this stick of pipe. API 5L covers about 10~15 different types,some may be OK,some not. Sometimes this pipe is dual marked such as API 5L/SA-106B ASME or API 5L/SA-53EB ASME,it could be a type F,or not marked for ASME at all. The Grade and Type of a stick of API pipe may be ASME acceptable and maybe not. You must always be very careful. Read the "Forward" of any Code section for guidence. Cross reference the material specs. in Sec II A. Do your homework----if in doubt do not use it.I guess I'm a bit confused: Quote (gbratis): ...I've used an API 5L X 65 pipe to lower the calculated thickness of the vessel. followed by Quote (gbratis): The crucial thing is to obtain the allowable stress value for this material.There is no ASME II part D material index for this pipe so I'll have to estimate one. seems to be contradictory. How can you already have lowered the calculated thickness of the vessel if you haven't yet figured out the allowable tensile stress? I presume you are at least talking about a vessel whose design temperature is ambient and that the "or 2/3 yield" part of the allowable stress basis doesn't apply and that compressive stresses do not govern. Further, you have no intention to code stamp this vessel - you are only using ASME VIII as a guideline. If so, then using the specified minimum UTS divided by 3.5 is not an unreasonable approach to developing a tensile design stress. I'd stay away from using MTR values for a couple of reasons: Your calc's may be used later by someone else who presumes that the MTR value for your vessel is equal to or lower than the MTR UTS for their vessel. Second, how do you deal with it when the time comes to repair the vessel and the original material isn't available. The savings for going with MTR values instead of specified minimum values can't be that great. jt2jte: Good point!It is not advisable to use material that not listed in section II of ASME BPV Code. If you insist to do that, approach it with extreme caution. Review UG-10(a) that seems to be the most applicable to your case and ensure you can use the material on the vessel at all. If it can be used it needs to be recertified. All this was written under assumption that you are building an ASME VIII vessel for a regulated jurisdiction. If there is a local variance approved for API material, just go for it. Putting Human Factor Back in Engineering1Thanks everybody, Jte to clarify things up I'm adding some remarks on your original post : I presume you are at least talking about a vessel whose design temperature is ambient (No) and that the "or 2/3 yield" part of the allowable stress basis doesn't apply (We are not performing test at known condition so as to compare information with similar materials) and that compressive stresses do not govern ( I cant understand the meaning of the term "compressive stresses"). Further, you have no intention to code stamp this vessel (No) - you are only using ASME VIII as a guideline (Correct). If so, then using the specified minimum UTS divided by 3.5 is not an unreasonable approach to developing a tensile (no tensile-max allowable) design stress. I'd stay away from using MTR (Sorry I dont know what MTR stands for) values for a couple of reasons: Your calc's may be used later by someone else who presumes that the MTR value for your vessel is equal to or lower than the MTR UTS for their vessel. Second, how do you deal with it when the time comes to repair the vessel and the original material isn't available (It is a circumstance, unlikely to happen). The savings for going with MTR values instead of specified minimum values can't be that great. As for Very Picky I believe that the ASME VIII vessel is not intended for o regulated juristiction.Even though I dont seem to understand the term "local variance" I believe that I can proceed with my estimation. If local variance has to do with the third party inspector sanction of my approch then I assume that everything is ok. I'm I right?MTR is the Materials Test Report defining the actual tensile properties obtained from coupons taken from the heat of material per the API 5L Specification. In terms of using ASME VIII, Div. 1 as a guide for design, the appropriate tensile strength to use is the Specified Minimum Tensile Strength per API 5LX-65, not the value shown on the MTR.1Quote: I presume you are at least talking about a vessel whose design temperature is ambient (No) If your design temperature is not ambient - which is the temperature at which either the MTR (see above post by Stan) is obtained or the SMUTS (specified minimum ultimate tensile stress) or SMYS (… yield stress) is specified - then how do you plan to develop allowable stresses which correspond to your design temperature? Quote: and that the "or 2/3 yield" part of the allowable stress basis doesn't apply (We are not performing test at known condition so as to compare information with similar materials) Ummm… see above comments… You better be confident here. Allowable stresses of commonly used ASME SA carbon steels are governed by the "or 2/3 yield" criteria at temperatures as low as 600 deg F. Quote: and that compressive stresses do not govern ( I cant understand the meaning of the term "compressive stresses"). I really hope this is a language / translation issue and not an engineering knowledge issue. By compressive stress I mean a stress which tends to force the material together. If a tensile (pulling apart) stress has a positive sign then a compressive stress is negative. Quote: Further, you have no intention to code stamp this vessel (No) - you are only using ASME VIII as a guideline (Correct). Good. Quote: If so, then using the specified minimum UTS divided by 3.5 is not an unreasonable approach to developing a tensile (no tensile-max allowable) design stress. If you don't recognise that there are several "max allowable" stresses in any ASME VIII vessel then I'd question your ability to safely design one. See second quote above for one example. Quote: I'd stay away from using MTR (Sorry I dont know what MTR stands for) See Stan's explaination in the above post. Quote: Second, how do you deal with it when the time comes to repair the vessel and the original material isn't available (It is a circumstance, unlikely to happen). By original material, I mean the exact twin of the material from which the vessel was fabricated - same mill run / heat. Unless this vessel will be thrown out when it wears out it will need some repair someday. That repair may use another API 5L pipe or weld build up which has lower MTR values thus invalidating your design if you based your design on your current MTR values instead of specified minimum values. Only by then the paperwork will be lost and nobody will know that the repair does not meet the original design. (I'm such a pessimist! Can't claim to be "born in the trenches" but I've been in 'em.) Quote: As for Very Picky I believe that the ASME VIII vessel is not intended for o regulated juristiction.Even though I dont seem to understand the term "local variance" I believe that I can proceed with my estimation. If local variance has to do with the third party inspector sanction of my approch then I assume that everything is ok. I'm I right? What Mr. (or Ms.?) Picky is referring to is that you need to check with the local authorities to see what they require for pressure vessel design and construction. In the USA some states require that vessels be built to ASME VIII or another "equivalent" code (to allow for foreign code use) while some states have no requirements and leave it to the individual owner/user/designer/fabricator to decide how to design and build a vessel. Basically, Mr. Picky is pointing out that you'd better check your approach with the folks who can put you out of business or in jail before you proceed. jtvery hard topic, i would lower 25% of that of the a106/a53 Smls or a53E pipe as as the api pipe form of construction, why: api pipe locks an NDE test and that makes it unfit for ASME Construction. it can not be used in ASME Construction and be careful of asking around: The National Bd or the Jurisdiction can recall your vessel... it is that serious... genb1gbratis variance is a deviation from a code granted by local authority as a blanket or for a specific purpose. It can be issued for any code requirement: insppection, test, design, material etc. In regions regulated by jurisdictions those jurisdictions specify design, fabrication and testing codes-criteria and also, specify any deviations from them - hence "variance". Putting Human Factor Back in EngineeringB31.3 Allowable Stress Design Basis ConfirmationFeb 28, 2008Allowable Stress for Pipe Spec API 5L Gr. X42Apr 11, 2007See more results

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By Authority Of - Public.Resource.Org

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ERW Standard and Line Pipe Grades - Continental Steel ...

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X65/X80/X100. The data contained in this publication is for informational purposes only and may be revised at any time without prior notice. The data is believed to be accurate and reliable, but Canadoil makes no representation or warranty ... API 5L, ISO 3183:2007. Plate-Forged.

Pipeline design consideration and standards - petrowiki.org

For colder-service conditions, A-106 and API 5L Grade B can operate to –50°F, if the maximum operating pressure is less than 25% of the maximum allowable design pressure, and if the combined longitudinal stress because of pressure, dead weight, and displacement strain is less than 6,000 psi.[PDF]

High Yield Steel - Canadoil

X65/X80/X100. The data contained in this publication is for informational purposes only and may be revised at any time without prior notice. The data is believed to be accurate and reliable, but Canadoil makes no representation or warranty ... API 5L, ISO 3183:2007. Plate-Forged.

Pipeline design consideration and standards - petrowiki.org

For colder-service conditions, A-106 and API 5L Grade B can operate to –50°F, if the maximum operating pressure is less than 25% of the maximum allowable design pressure, and if the combined longitudinal stress because of pressure, dead weight, and displacement strain is less than 6,000 psi.[PDF]

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Pressure Rating Tables for Carbon Steel Pipe Notes to the tables of allowable working pressures. Notes ... or API 5L. A weld join efficiency factor (typically 85%) must be allowed for standard ERW ... Maximum Allowable Stress (MPa) Size Nominal[PDF]

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DEFORMATION AND FRACTURE PROPERTIES OF STEEL …

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API 5L X60 Welded Steel Line Pipe Stock and Fresh (ERW, …

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