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Assembly Torque Values
4

Assembly Torque Values

Assembly Torque Values

(OP)
  I'm surprised I cant get the answer to this using Google... maybe I'm using the wrong search words.

I am installing 16 inch diameter steel pipe, to be used to pump water  against 1000 feet head,  so duty will be approx 450 psi at the pump outlet.  Pipe has been engineered as Class 300,  which I believe is rated at about 750psi,  so no issues there.

What is the required torque value for the assembly of the flanges??  We are in North America, so no references to European standards please.

RE: Assembly Torque Values

Your best bet would be to refer to ASME PCC-1.  However, it all depends on your gasket.

So, short answer - ask your gasket manufacturer.  What gasket are you using?

RE: Assembly Torque Values

I might be mis-remembering a conversation I had quite a while back, but I seem to recall that torques values for flange bolting is hard to come by because no one wants to stand behind the data.  

I have seem some tables, but I don't think any of them came from a recognized standard.  

I think there are so many variables such as cleanliness of the bolts, gasket type, etc. that the answer to how much torque you need is more complex than it initially seems.   

RE: Assembly Torque Values

Google "European Sealing Association Flange & Gasket Guidelines" and don't worry, they use imperial units too!  Look at Pages 16 and clause 6.6 on page 29.

Steve Jones
Materials & Corrosion Engineer
http://www.linkedin.com/pub/8/83b/b04
 

RE: Assembly Torque Values

If I were to complete this process assuming that it is a Group 1.1 RFWNK flange as per ASME B16.5 (which has a max rating of 1125 PSI) I would get a company or use a high torque machine to torque the (20)1-1/4" studs and nuts (presumably grade B7 studs and 2H nuts) and proceed to obtain a final value of 690 ft lbs. Not forgetting to follow the bolt tightening pattern.  If your company is QC driven then they might also have an exhibit to be filled out for these types of torqued joints.  To that end all you would have to do is ask your client what they want them torqued to.

Just how I would do it being only a JM in a Hydro position.

RE: Assembly Torque Values

(OP)
  Thanks Cuemaster, that was exactly the sort of response I was looking for. I dont have access to all the standards, nor am I am familiar with these documents... thats not the way we tend to work undereground.  Your assumptions are pretty accurate.

On a practical basis, I need to prepare some general installation guidelines for my own mining crews... highly skilled in rock excavation and working in dirty, dark, wet confined areas with extremely limited visibility, but who typically never install piping more sophisticated than 100psi victaulic.

I have done work in the oil and gas industry and understand in general terms how to train my workforce and I had found a reference in the Flexitallic gasket web site that suggested a minimum of 500 foot pounds, assuming 30,000 psi bolt stress or 750 foot pounds if the required stress is 45,000 psi.  This is close to your estimate.

Service duty will be regular mine water with some suspended solids.  Occassional leaks are not a safety hazard,  indeed they are to be expected in the environment we work in.

Given this extra info, is 500 ft lbs likely to be adequate or will we have to go to 700+??. Either way, its going to be a major exercise with the amount of pipe we have to install.

RE: Assembly Torque Values

"European Sealing Association Flange & Gasket Guidelines" are downloadable free.  If you have access to the web you have access to the document!

Steve Jones
Materials & Corrosion Engineer
http://www.linkedin.com/pub/8/83b/b04
 

RE: Assembly Torque Values

2

"I would get a company or use a high torque machine to torque the (20)1-1/4" studs and nuts" ... "If your company is QC driven then they might also have an exhibit to be filled out for these types of torqued joints" surprise surprise

C'mon now; with all due respect, it saddens me that highly-educated people continue to put their faith (and safety!) into something which clearly has dubious or limited, at best, relationship to bolt load.  

"Quality Assurance" and "torque" in reference to bolt load should not be put into the same sentence. There are so many variables which affect how much of the input torque actually results in bolt tension, yet many of us choose to remain oblivious to this reality. It's no wonder that in the mining industry, grinding mills throw bolts, autoclaves leak, crushers fall apart and on, and on... We all know that "Torque" is not and CANNOT be an indication of how "tight" a bolt is!

Tightening a bolt by applying "torque" (with a calibrated torque wrench even!) and then walking away, exepecting all to be fine, is almost negligent. Not only can this result in under-loaded bolts, it can also result in yielded bolts! Since "torque" often has such an insipient, unknown relationship to a bolt's load, one must always take the next obvious step: measurement and verification. The easiest way of doing this is by measuring the stretch of the loaded fastener. Any QA process which omits this crucial component will do much more harm than good as it'll only provide a dangerous false sense-of-security.

Ciao,

HevïGuy
www.heviitech.com

RE: Assembly Torque Values

Heviiguy,
Your last response about bolt measurement is very interesting. It is seldom regarded in large rotating, high temp., high impact type of equipment such as ore milling. Bottom line; it saves lives and equipment.
I was curious to know a source for this information regarding bolt stretch. It is not commonly used and I would like to apply this method myself, with your advice on where to find such a table, graph, etc... I would greatly appreciate it. I work on mills, crushers, etc... myself and I see this type of thing all the time.
Thank you.

RE: Assembly Torque Values

(OP)
Heaviguy, I suspect your suggestions are 100% accurate when it comes to crushers and grinding mills.. especially the bigger units that are becoming relevant in the mining industry but I'm just a simple production guy putting in some dewatering lines.

I'm still working on getting my procedures together,  but ultimately I will instruct my crews to bolt to a certain torque value... and yes, I will insist on the use of never sieze etc... and I will leave the QA/QC stuff to other persons.  All Im doing is pumping large quantities of water. Worst case scenario, a few leaks have to have the gaskets replaced... and I personally wont be doing any measurements on bolt stretch or anything like that.

I will follow this thread with interst tho,  in case I have to install a crusher at some point in the future.  Thanks for your response.   

RE: Assembly Torque Values

Hello Ork1,

Fastener stretch depends on a number of known variables (unlike the enigmatic "K" factor in the torque equation). In its basic form, it's really quite simple:

δ = FiLo/EbAst

where δ = is the elongation
Fi = the required bolt load
Lo = the original effective length
Eb = Youngs Modulous
Ast = Effective cross sectional area

"Ah..," you're probably saying, "... but I don't know what the required bolt load is. All I have is this ambiguous 'torque' spec...". Fair enough. In that case, what one has to do if one can't perform a full joint analysis, is to simply work backwards from the Torque Equation to get a value of Fi :

T = K Dn Fi
Fi = (K Dn)/T

Unfortunately, this is fraught with an enormous problem: one has to guess at the Friction Factor (K) which the designer's voo-doo beads had told him to use. Doing this compounds an already-ineffectual process! All is not lost, though: On non-gasketed joints such as mill flanges or crusher sections, one can assign a value of Fi based on a percentage of proof strength. This has to be done with the assumption that the equipment designer, when performing his flange stress calculation, designed the system with sufficient stiffness.

Interestingly, we have quite a bit of experience with SAG and Ball Mill OEMs who are now desigining their structural fasteners to be preloaded up to 90% of yield!! What's even more interesting (and refereshing ) is that most of them also include bolt elongation values in a column beside the torque specs. They often won't honor future warranty claims if the elongations of all fasteners haven't been measured and recorded. Insurance underwriters have also begun to insist on this for other critical plant equipment.

It seems that people are finally realizing the that the Torque Emperor has been strutting around in the buff... wink

 

Ciao,

HevïGuy
www.heviitech.com

RE: Assembly Torque Values

Miningman,

(I think that you must have posted as I was composing my reply to Ork1). Indeed, you make a very valid point. Some applications simply do not need this degree of control and Quality Assurance. It's all based on risk. One has to ask: What's the economic or human cost of joint-integrity failure on a particular joint? Heck, plant air lines, process water lines, dewatering lines and the like might as well just be beat'n'bashed together with an impact gun (which many of them are!) since the effect of a leak would be relatively minor.

There are a number of different bolting methods ranging from simply having Bubba swing a hammer against a slugging wrench, to using an overhead crane, to tightening by using impact wrenches, torque wrenches, or bolt tensioners, to torque-and-turn, to heat-tightening, to yield tightening and so on. Most of them (although some being quite unsafe and certainly not advocated!) are prefectly suitable for certain applications. The trick is assigning the most appropriate method and level of QA control to each particular application.  

Ciao,

HevïGuy
www.heviitech.com

RE: Assembly Torque Values

Question - is it possible (feasable) to measure stud stretch?  

RE: Assembly Torque Values


Indeed it is, John. We always use this method when faced by critical or problematic joints. Although it takes quite bit of experience to properly operate the equipment, it's accomplished utilizing specialized ultrasonics. The technology is based on "time-of-flight". In colloquial terms, the process is akin to sonar.

In practice, a signal is sent down the length of a fastener where it's reflected off of the bottom. The time which the signal requires to return to the transmission point is converted into a length. Obviously, one has to have recorded the initial, relaxed length of the fastener in order for the loaded length value to be useful. Variables such as bolt material temperature and stress play a big part in the equation. This is why typical ultrasonic thickness guages aren't at all suitable for this purpose.

As one can see, one of the the beauties of this process is that it can be used on applications with blind holes. Another is that it's effective for a wide range of fastener lengths. It does become a bit of a challenge sometimes but, we've "shot" fasteners from as short as under 2" to as long as 25 feet.

 

Ciao,

HevïGuy
www.heviitech.com

RE: Assembly Torque Values

I agree with {b]Heviguy's[/b], informative posts, but will have to diverge on the topic of tightening flanges by torque values on a routine basis. On our site we tighten thousands of fasteners daily by torque value or in most cases by wrench value. The sizes range from 1/2" - 1" H11 SHCS  TO 2 1/4" B7 studs and everything in between. Leaks are extremely rare. All our wrenches are set and checked against a Skidmore-Wilhelm tester, we have 3, weekly. A secret to getting a flange such as yours tight is to get as near the calculated torque value as practically possible and keep the flange faces parallel as there is some freedom in the gasket seating stress required form normal piping systems. Normal meaning piping without tremendous extraneous loads.

Measuring bolt stretch by micrometer was the norm when I entered the petrochemical field in the 1950's and is still used today, though sparingly. Our chemical group had technician whose job was ensure the integrity of any and all flanges using the best practice. You will find the bolt holes on some of our older exchangers are still numbered.
The normal procedure was to applied 1/3 the torque value,  measure, then apply full torque in 2 steps, final measure with adjustments. As torquing  normally understates the preload it was very easy to ratchet up to the required stretch

Here is the Sure Bolt site that has a ultrasonic measurement system that works extremely well.

http://www.surebolt.com/Flange-Design.htm

HeviiGuy,

Here is a interesting paper from Superbolt concerning fasteners. I noted in a previous post that this was eluded to by Mr. Biach, Biach tensioners,  several years before this article.

http://www.superbolt.com/articles/virgin_bolt.html

RE: Assembly Torque Values

Hello Uncle Syd,

Thanks for the comments and links (I'm quite familiar with them winky smile ) I'm also very familiar with the Surebolt equipment. It's certainly good but, we don't use these particular devices in projects where were involved. In our opinion they're much too cumbersome to use in light of the new generation of equipment which has superseded this.  

Ciao,

HevïGuy
www.heviitech.com

RE: Assembly Torque Values

This is pretty simple - we all know that torque only measures the turning force on the nut, not the actual bolt load. Hydraulic tensioners are also pretty unreliable once you let the oil presure down. Final loads from either torque or tensioner are +/- quite a wide scatter.

Check out these guys - http://www.rotabolt.co.uk/ They convert the bolts with what is effectively a mechanical strain-gauge pin down the centre and set the cap to lock-up at whatever the desired axial load is. Much quicker to install than using ultrasound, so the cost of the bolt conversion pays back in reduced downtime and installation costs. Also, you get some condition-monitoring in-service as if the bolt loses load, you just twiddle the cap. They are used a lot in offshore cranes as well I believe.

RE: Assembly Torque Values


Wait a minute: "Hydraulic tensioners are also pretty unreliable once you let the oil presure down". With all due respect, gasketguru, I don't think that you fully understand bolt tensioners... sad

Bolt tensioners impart an axial load to a fastener by directly stretching the fastener rather than relying on the "inclined plane" action of a nut traveling along a bolt's thread as it's turned.  Friction doesn't enter into the process at all as it does with torquing. Granted, there is some thread relaxation involved but, this is well known and controlled by the proper pressurization process. There is nothing "unreliable" about bolt tensioners at all.

Not wishing to offend or to be improper by posting a blatant commercial link, if anybody would like further information, I could provide them with a link to a non-commercial, generic explanation of bolt tensioning.

It's great when one has a number of options to choose from. In our business we have to be impartial to every option as we need to choose what's best for our client's specific problem.

The rotabolts have been around for a long time. In some cases they're adequate  However, there are two significant issues with them:

One can't tell if the bolt is over-tightened.
More seriously, they don't provide a definitive indication of bolt load as actual measurement would.

One must place one's faith in the initial set-up of the "rota" by the manufacturer. Earlier this year, we were in central Asia,  working with a client who had similar "indicating bolts" on a key piece of critical equipment. Although many locked close to the desired load, quite a few showed a discrepancy of up to 15% - with a couple even beyond 20%. In fact, some even indicated load when the nuts had been removed. This would have been fine on a less-critical application (where we've sometimes recommended them) but not on this particular one where forced shutdowns due to bolt problems had routinely resulted in hundreds of thousands of dollars per hour in lost revenue.

Remember: "The trick is assigning the most appropriate method and level of QA control to each particular application."

Ciao,

HevïGuy
www.heviitech.com

RE: Assembly Torque Values

I'm not sure what problems you had with "indicating bolts" from whichever supplier, though as you say it may depend on how you set them up initially, but installed measurement is the key to success.
How did you measure your 20% inaccuracy? Did you calibrate the bolts out of the installation initially and measure extension over a given clamp length? (Even modulus can vary slightly between material batches.) With tensioners, I had a problem a while back where the calculated tensioner over-pressure was around 25% but it took more than 100% overload to achieve the final bolt extension and applied load.
These overload values are based upon around 2-4 thou' (typically) of relaxation per inch, depending on the tensioner size, but I've never seen any research papers to prove it - I would still say that they are indeed highly unreliable in terms of accuracy, but pretty good in terms of applying plently of load in one go fairly evenly around the joint.

RE: Assembly Torque Values


The "accuracy" of these fasteners was verified by actually measuring stretch - best way to do it short of attaching strain gauges onto the bolts winky smile

I dare say that if you had to apply "100% oveload" to acheive a certain residual load, there must have been a significant problem with your method. We have some very detailed generic instructions in the safe and effective operation of bolt tensioners which should help. I'd be happy to have someone send a copy to you, if you would like. I'm sure that this will go a long way in ensuring that you obtain results typical of this technology in the future.

gasketguru: I'm quite confident that qualified individuals who have had any experience at all with bolt tensioners would find your incorrect phrase "highly unreliable in terms of accuracy" smacking of a nefarious and blatant ulterior motive sad

Ciao,

HevïGuy
www.heviitech.com

RE: Assembly Torque Values

purpleface
gasketguru, do you hear this: "mrrppph mrphhmrmm"? It's the sound of my foot in my mouth. I am very sorry for my rude insinuation. I had looked at other posts of yours, expecting to see references of the particular bolts which you had mentioned. None were to be found. Only, astute, non-commercial advice. Please accept my sincere apologies.

After seeing so many obvious commercial placements in these forums, one becomes too cynical sad

With all seriousness now: Perhaps the fact that you experienced such atypical results were indeed due to some unfamiliarity with the process. A few things to keep in mind:
 
Unless all bolts on a flange are being tightened simultaneously (aka: "100% Tensioning"), different hydraulic pressures are required for successive placements of the tensioners. For example, when enough tensioners are used so that 50% of the bolts can be loaded at once (ie "50% Tensioning"), an "A" and a "B" pressure need to be calculated and applied. The former is higher than the latter to account for load transfer. It's a relatively easy calculation.
 
When less than 50% tensioning is performed, the calculations tend to get a bit more complex.
 
In any event, a very common problem experienced by people new to the technology is not energizing the tools up to three times at the same pressure. This must be done to ensure that the joint has properly "settled". If this isn't done, yes indeed, one may get unexpected results.

Don't give up on tensioning. As you say, it's a very fast method and, if done properly, it's also a very accurate method. One more thing - it acheives even gasket crush since the bolts are tightened simultaneously .

Ciao,

HevïGuy
www.heviitech.com

RE: Assembly Torque Values

gasketguru,
How were you seating the nut after appying tension to the stud?

RE: Assembly Torque Values

Trust me - after 25 years of doing this, I have a lot of experience with both torque and tensioners, and as you say the best way to ensure correct load is by measuring the extension, either by by micrometer, ultrasound or indicating bolts (it is just that those I mentioned have helped me over the years). The point is to stretch the bolt to the required amount over the desired clamping length(using a tensioner here really helps!), measure the loaded fastener length, and then try to replicate this length in the final settled installed condition. Within the accuracy of measurement method used, you then get pretty much the load you want.

The problem comes when simply replying on the recommended overload pressures from the tensioner manufacturers, as these are based upon an assumed loss per inch of bolt. The case I described was a high temp HX which had been a problem leaker for many years, and has now worked fine for the last two. With 60 bolts of around 2" diameter then the pattern was the usual A/B pattern you describe.

I do not know of any tensioner overload calcs that account for gasket/flange rigidity (like the ASME J factor). Integrating something like this into the overload calc might help, along with research into the loss per number of interfaces in the fastener (i.e. bolt vs. studbolt, and with or without washers, hard vs. soft gaskets etc.) as each piece creates some of the load-transfer relaxation in the joint. Maybe a good research project for someone like PVRC or ISO TC74 etc.?

RE: Assembly Torque Values


I really don't want to flog this dearly-departed horse any longer but, I'd still like to add a couple of farthings:  winky smile

There are two reasons for applying a higher hydraulic pressure to tensioners than what at first blush may seem necessary:

Although the constituent components of a joint certainly do have a great deal of impact, the calculated bolt load is a non-variable. And, since the area of a hydraulic tensioner is also fixed, the hydraulic pressure required to apply the bolt load is fixed. The reason for over pressure in this case is to address the issue of thread relaxation and consequent load loss. This is usually a very small amount.

The other reason for a modified pressure is to account for load transfer. Load Transfer could indeed result in huge variations if not accounted for. Certainly, if a small number of tensioners is being used (relative to the total number of bolts on the flange) one can apply a single pressure to the inter-linked tensioners by following a convoluted "pattern", much like torquing. However, since one of the most benefical traits of bolt tensioning is speed due to the ability to simultaneously tighten every bolt, a method was derived to compensate for this load transfer. Hence, the A/B pressures for 50% tensioning. Alas, this quickly becomes a potentially-complicated A/B/C/D/E... process whenever even fewer tensioners are used. One can see that if relying on a tensioner manufacturer's suggested operating pressures, the results may not turn out as expected if all prior assumptions are not valid.

Your points about the other compelling factors in the joint "system" are well taken and appreciated. However, my gut feel is that this atypical experience was due more to procedure rather than an inherent deficiency of this well-proven technology.

Suggestion:
An easy way to verify or modify the tensioner pressure ratios (again: not necessary at all with 100% tensioning)is to measure the resultant stretch (or twiddle the indicators) after the intial pass per set of tensioners. Then, if necessary, simply increase or decease the hydraulic pressure so that  consistent loads are acheived. As long as everything remains constant (ie process, flange condition, gasket etc), these new tensioning pressures would be the ones to use for future assembly. One very important thing to watch out for is the capacity of the flanges. You'll need to verify that any additional load wouldn't result in flange rotation!

Ciao,

HevïGuy
www.heviitech.com

RE: Assembly Torque Values

Late to the party, but here goes. The torque range is dependent on the minimum sealing stress and maximum load of the gasket. The following data assumes using a non-asbestos compressed gasket material, specifically Thermoseal (Klinger) C-4433 X 1/8" Thick Ring Gasket. Grade B7A Bolts. Flat face flanges. (450 psi X 16" pipe for hysdrostatic end thrust calculations.)

Minimum Seating Stress @ 450 PSI Internal = 5511 PSI Flange Load
Maximum Allowable (Gasket) Stress = 13808 PSI Flange Load

Torque values assume mineral oil lubricated bolts seating against hardened washers. Three tightening passes in a star pattern to achieve a (theoretically) even load. Also want to shoot for a reasonable bolt stress to achieve a "tensioned" flange unit, capable of compensating for creep relaxation and possible unloading of the flanges from external forces.

@5511 PSI the torque value is 374 ft. lbs. bolt stress is 18% (Min sealing stress)

@13808 PSI the torque value is 905 ft. lbs. bolt stress is 46% (Max allowable stress on gasket.)

A reasonable range of bolt stress is 30-35% which equates to a range of 590 to 688 ft, lbs applied torque. This correlates to an effective gasket stress range of 9132 and 10654 psi gasket load.

The caveat here, of course, as stated in arguments above is the accuracy of applying bolt tension via torque to achieve the gasket stress. The values given here are strictly for gasket sealing purposes.

Values provided by the Klinger Expert gasket software program.

"Tighten it until you hear the bolt snap, then back off half a turn."

 

RE: Assembly Torque Values

(OP)
Mkessell, late maybe, but a very timely and usefull contribution. My planning for this is progresing rapidly, and I know I am looking in the 600 -1000 foot lb range. I also now understand that the optimum torque is dependent on both the allowable stresses in the gasket as well as in the studs,  as well as some sound engineering judgement. You clearly have the background to make a reccomendation and I would be gratefull if you could repeat your analysis using Class 300, ASME B16.5 Spiral Wound Gaskets / flanges,  grade B7 studs.  Pressure will be closer to 500psi. I do not have enough background in this area to apply the appropriate engineering judgement.

The Garlock website seems to suggest a preffered torque of 1000 foot lbs but unless I have misunderstood some of the previous posts, I find it significant that this is a "preffered" rating as opposed to "recommended".

Am I mis-reading something, or does good engineering judgement suggest a slightly lower value.??  I would hate to have my crews user a higher than necessary value and have leaks develop, say because the studs were over stretched.  

RE: Assembly Torque Values

The program I was using is strictly for Klinger materials and their sealing properties. Spiralwounds are a different animal in terms of the necessity of compressing the winding to affect a seal, using the outer guide ring as a "stop." Theoretically the stop prevents over-tightening however on b16.5 150# class flanges the Y value exceeds the point where flange rotation becomes a potential. Probably not valid with 300# flanges.

Flexitallic offers a pretty good technical manual which should get you in the ballpark. Check it out and I believe you will be able to calculate the necessary torque values for your application. I will attach the file.

Finally, the Garlock recommendation is also material dependent and their suggested torque range for a similar material is 401 ft. lbs. min and 912 as "preferred." I can't comment on why they would use the term preferred, other than again, ballparking a bolt stress range. It's instructive to recognize that both Garlock and Klinger's interest and expertise lie with the affectation of the seal rather than the science that effects the bolted joint.


RE: Assembly Torque Values

Sorry, it appears as of the file did not upload, here's the URL: http://www.flexitallic.com/pdf/designcriteria.pdf

RE: Assembly Torque Values


C'mon folks: Although you're getting torque values from the "experts" you've got to take this with a huge grain of salt: "torque" does not and cannot be considered as a metric of applied load!. It's "preload that you must be concerned with. The most practical way to verify preload is to measure the resultant stretch of the applicable fasteners.

Ciao,

HevïGuy
www.heviitech.com

RE: Assembly Torque Values

Hevi: You're absolutely correct, and your reasoning is why 85% of gasket failures occur. I know the corresponding error rates of hand tools vs. calibrated torque wrenches, vs. hydraulic tensioners. I'm aware of the fact that surface rust is rarely cleaned from nuts and bolts in the field. Nine times out of ten USED bolts nuts and washers are re-used, with little due regard for condition. Loosen the bolts, spread the flanges, remove the old gasket and replace with a new one.  Next to expansion joints, the bolted flange is the weakest link in any piping system because sophisticated engineering rarely translates into field practices.

Other than M&Y values, which is at best sorely misunderstood and outdated, the second most popular question coming from the field regarding gasket installation is exactly what was asked right here. The results are legitimate, come from published known physical properties of gaskets and fasteners and represent good science. In that regard the opinion is indeed, "expert."   

Your argument can't be against attainment of these recommendations, because utilizing any method even as primitive as a hand wrench might attain the necessary goal of creating a uniform leak tight seal, with appropriate load applied.  Therefore your argument must be for "verification" by way of the accuracy in the measurement of bolt strain.

I agree 100% that your argument embodies best practices, however is in reality a "control" issue in terms of installation. Given the variables likely to be encountered in the field, the issues of both verification and control are well outside the purview of the materials manufacturer. Ultimately these practices must be adopted by the end user or installer.

 

RE: Assembly Torque Values

I agreed with the previous post in that the only way to go is measure the elongation but in reality you have to look at torque values are going to be used.

Here are some torque tables eluded to in previous posts. It gives the complete range of values to seat a gasket from the min. to max.
As I've mentioned before look at the values for the 3" & 8" flange on the lower Class flanges.

One thing not mentioned in most literature is the requirement that you have enough flange to do the job. Our piping codes don't allow the use SW gaskets with store bought Class 150 flanges. Having said that we do allow SW gaskets on some home built flanges if they are of the many small vs the normal few large studs and calculate out.
 

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