Are you unintentionally adding deadlegs to your piping designs? 

We all have hopes and dreams but your "future expansion” may actually be a major hazard due to the susceptibility of corrosion in these areas. Please be careful with piping headers and branched connections that are intentionally blinded off after construction to prepare for a future expansion. Many times the expansion plan never materializes and the associated deadleg is never properly accounted for in the site’s integrity program. 

What’s wrong with deadlegs? They get hardly any flow and experience higher corrosion rates than the rest of the piping system.

Ever plot CML thickness and notice your piping or equipment growing over time? 

This “reverse corrosion” phenomenon sweeping inspection departments can defile your data and give false impressions of real metal loss and corrosion rates. 

How common are growth readings for CMLs? VERY. In fact, during Jeff Goldstein, P.E.’s latest webinar “Rethinking Piping Inspection Locations” he discussed a site with 12,000 of 40,000 CML readings showing growth over the last CML reading. That is 30% of readings showing a growth rate instead of an expected metal loss/corrosion rate. What you decide to do with these growth readings will have a big impact on maintenance and inspection plans moving forward. 

Maybe there was an undocumented piping or equipment replacement. 

Maybe the measuring device was not properly calibrated when the operator took CML readings. 

Maybe the CML readings were entered into software or spreadsheets incorrectly. 

Maybe the CML readings were taken in the wrong location.

Please spend some time trying to understand what is causing growth readings and act accordingly.

Like to use ASME B16.9 Elbows as main pressure containing components? Please remember to treat them as seamless pipe and to calculate the required thickness by outer diameter. This means using Appendix 1-1 instead of UG-27 for internal pressure in Division 1.

I see off-the-shelf ASME standard flanges and pipe fittings often used as main pressure containing components in pressure vessels and heat exchangers. I’ve noticed the biggest variance in approach when I investigate ASME B16.9 Elbow calculations. Some design engineers believe that ASME B16.9 Elbows do not require any calculations at all. Others calculate ASME B16.9 elbows using UG-27. Very few use Appendix 1-1. 

Notice that Appendix 1-1 may require extra thickness compared to UG-27. Please refer to UG-44 for more information regarding the calculation of standard flanges and pipe fittings.

Let’s talk about my favorite product form “Welded and Seamless Pipe”. 

Is it Welded? Is it Seamless? Is it Both? Wait, that’s impossible…

Well then what is a “Welded and Seamless Pipe”? I have no idea. What I do know is that there is a big difference between how welded pipe and seamless pipe are handled when it comes to ASME Code calculations. You need to know exactly which version of the material you have before performing calculations or there is a good chance you will be making a big mistake. 

Let’s take a look at SA-312 TP316L, which includes the seamless and welded pipe product form in the same specification. 

Seamless: No need for a longitudinal weld joint efficiency factor in the allowable stress. Double-check to make sure the allowable stress reflects this. 

Welded Pipe Made without Filler: The longitudinal weld joint efficiency factor needs to be included in the allowable. Notice the allowable is (15,300 x 0.85 = 13,005). There is no need to count this twice and multiply by 0.85 again in the joint efficiency value.

Welded Pipe Made with Filler: The joint efficiency factor was not included in the allowable so it needs to be taken into consideration in the joint efficiency value itself. Keep in mind that the joint efficiency value may be lower than 0.85 depending on the radiography performed.

Do you need to multiply welded pipe material allowables by 0.85? 

I get a lot of questions regarding the allowable stresses for various material product forms. The one I’ve been asked about a lot recently is whether or not the allowable stress for welded pipe needs to be multiplied by 0.85.

The answer is, probably not, but it depends. You really need to take a look at the material notes for your welded pipe material in ASME Section II, Part D. This will reveal whether or not the lookup allowable in ASME Section II, Part D has already been multiplied by 0.85. Let’s take a look at a couple of the notes in Table 1A:

G24: This note indicates that the 0.85 has already been applied to the allowable stress. You do not need to multiply the allowable stress by 0.85 again. In this example the allowable stress lookup of 14,600 psi can be used directly in circumferential stress equations. 

W12: This note indicates that the 0.85 has not been applied to the allowable stress. You need to multiply the allowable stress by 0.85 if the welded pipe was created without using filler metal. In this example the lookup of 21,400 psi was multiplied by 0.85 to achieve the 18,190 psi allowable used in the circumferential stress equations. 

The ASME Section II, Part D material notes are not just informational, they can directly affect the allowables you used in stress equations.