Many users have spiral wound gaskets on class 150 flanges, though they are sometimes thought of as being too "hard" for lightweight flanges with limited bolting (remember that originally spirals had a "y" factor of 4500 psi which was later increased to 10,000 psi). Note that many manufcturers...
The Hg is of course the forces at the gasket reaction, and the App. Y says it is the gasket load due to seating plus the load due to the self sealing of the gasket - thus, whether you are taking the gasket load as being the traditional factor derived value (i.e. the 2b x Pi x G x m x P etc.) or...
I'm not sure I understand the housing here - 2mm deep x 30 wide - are you coming metal-metal on the outside or something, or is this a regular gasket with variable compression in a spigot-recess etc.?(It does not sound like an O-ring for instance....) As you say, if the diameter and pressure...
Surely if it is a pressure energised rubber O-ring then for traditional Taylor-Forge / ASME VIII calcs., then m and y are both zero (previous table - 2.5.1), so from the various parts of the load calcs, then what you are left with is the hydrostatic force as pi/4 x G^2 x p which is the pressure...
That makes sense, as of course the hydrostatic force as seal diameter x 300 psi then equates to just under 25 ksi bolt stress - a typical value for B7 etc. - the space is slightly tight as a 1.1/8" usually has 1.5" from hub to PCD and 1.125 from PCD to O/D so 2.5/8" compared to 2.1/2", to allow...
It is something I definitely wouldn't do.... (Though I know some fitters do it to try and hold them in place etc. and some misguidedly think it makes them seat easier.)
Originally RTJ's were used at modest temperatures in oilfield service, but have also been used at high temperatures. There have...
I would say the intent of the designer was for an O-ring, not a 1" tall x 0.3" wide ring - note that rubber is incompressible, so your proposal has around 40% more rubber than groove, so what happens to the over-spill?... I'd say the design is for an 88.3/4" x 7/16" section O-ring (hence around...
You must be talking about materials that can flow quite a lot - e.g. uniaxial PTFE, or perhaps displace such as rubber, as mostly at "normal" bolt loads and stresses a CNAF or graphite gasket would not spread into the bore. Note that the I/D of most cut joints is the same as the pipe O/D (N.B. =...
I agree with LittleInch here, as I think I've seen this in a BASF standard for lens ring type joints (WN18-010) as well as in an old Czech standard - ref. number was 13-9732, and the sizes are not the same as the old DIN2696 for lens rings, where PN320 was a little different.
This sounds like a regular 12"-150 flange, presumably flat faced (not with a 15" raised face), so you have full contact. Note that rubber does not compress it only displaces, so if you over-load it then it squeezes out of the side of the flange. I don't get your area calculation - 12" x 19", or...
This is an old obsolete size - 22"-600 would have 24 x 1.3/4" bolts, and flanges are 3.3/4" thick plus 1/4" r.f. height. Thus, assuming say 1/8" for a compressed spiral-wound gasket for example (another non-standard size item these days, not likely to be ex-stock), then you get 8.1/8" clamp...
Just to clarify, there are essentially ASME flanges and metric (DIN) flanges, where the ratings of ASME are in psi (150, 300, 600 etc.) and that rating is at elevated temperature (traditionally 300 is 300 psi at 800 or 850 deg.F depending on whether it is carbon or carbon-moly steel etc.) The...
There are already jet powered drag race trucks - wind them up, hold on the brakes then let 'em go - sub 6 second 1/4 mile... - search the internet and you'll find videos of such things - just don't stand behind them at the track...
(There was a project some years ago to power a tram using a...
SnTMan - perhaps I was getting a little cynical after a long day yesterday, but in the last 30 years I've fixed so many leaking joints where they have been under-designed, used the cheapest gasket possible, which has been fitted badly where the user has been overly optimistic about things like...
PN20 is not an original DIN flange - they go PN 2.5, 6, 10, 16, 25, 40, 63 bar rating etc., whereas PN20 is a metricated ASME 150 from the ISO 7005 standard, which was never a good idea in my view. The ASME flanges are converted to PN numbers e.g 20 for 150, 50 for 300 and 110 for 600 to avoid...
Selecting the gasket is traditionally the starting point for a custom flange design given the vessel diameter and operating conditions. Sadly the m and y factors are a weakness and are not a good indicator of actual gasket behaviour and performance. They are little more than an “engineering...
The 3"-150 (and 8-150) is one of the the worst case flanges in terms of bolt load vs. gasket area - thankfully the max system pressure is only low. However the traditional ASME VIII / Taylor-Forge calculation will under-cook the loads for you. A limit analysis calculation such as EN1591 tends to...
You are right - the stack of gaskets is basically a crude compensator, to take up build tolerances and thermal movement - usually at least 6-10 gaskets. (We used to do these many years ago for companies such as Mather & Platt, back when the gaskets were still asbestos!...) Whilst you might get...
No - spiral wound gaskets are not particularly pressure energised e.g. like a hydraulic cylinder chevron set etc. - they can seal external pressure and vacuum as well as internal pressure. The V profile allows them to be wound and be stable of course as well as fold upon compression. As they...
Some people touted disc springs as a universal panacea for a while, but they often add more complication than do any good. The springs used on bolted joints tend to be quite thick with a low dish height, and if tightened flat have rather a high internal stress. You also need to get ones in a...
