ASME BTH 1 2008 PDF

ASME has been defining crane safety since BTH-1 provides minimum structural and mechanical design and electrical component selection criteria for. Design of Below-the-Hook Lifting Devices by pvchabot. Documents Similar To Asme Bth Design of Below-The-hook Lifting Devices. ASME BTH Uploaded by. pvchabot ยท ASME BTH-1 Lifting Lug.

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Asme Bth Design of Below-The-hook Lifting Devices

Register now while it’s still free! Close this window and log in. Are asmme an Engineering professional? By joining you are opting in to receive e-mail. Promoting, selling, recruiting, coursework and thesis posting is forbidden. Hi Everyone, Baseed on thread For now, I am working on a single case and detailing the calculations.

Asme Bth-1-2008 Design of Below-The-hook Lifting Devices

The lug is as per figure C I have also attached a sketch. The problem I have is that it’s not clear to me if I am dealing with a compact or non-compact section as per table I also need to determine this for a flexion analysis in the weak axis. Any help would be appreciated. Back-calculate a t required to ensure a compact behavior 200 you go from there. Hi JAE, Thanks for the reply. Usually the “b” is aame length of the free, unstiffened edge which undergoes compression.

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In your case, I would see the b distance as the straight vertical edge ssme the base center of hole to base weld line. I have never seen a lifting lug that would 200 be classified as compact by a long shot.

Their thickness is generally driven by bearing checks on the pin hole that make this plate much much stockier than typical structural elements. We just recently designed some lifting lugs where the dimensions were pretty much set by the client.

For a square aame, like your lug, local buckling is not possible. Therfore it is inherently compact. That is the governing provision for square plates. You’ll see that there is no criteria for checking whether the section is compact or non-compact. Instead, you’re checking for a glocal buckling Lateral torsion buckling mode of the plate. I’m not sure LTB of a lug could ever happen unless you had a really funky looking lugI would probably just use the full plastic capacity of the pad eye.

But F is the section you want to check to be thorough. Alternatively, I will survive without see it. Almost invariably, pin bearing, shear and yielding in the area of the pin, and good quality welding detailing controls the design of lifting lugs. I think some of you above need a thanks from me – getting my head out of the sand.

I think what I posted above is correct but WillisV and others posts are right on – buckling isn’t really an issue with lugs like this unless the gth is thin and the lug is really long and extended. Even then, I wonder about how much compression would even get into the lug with an angled hanging “tensile” load.

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Hi All, Thanks for your help. WillisV, Agreed, this makes sense to me despite being a mechie. The base of my lugs will be wider, however, to be conservative I am designing with a constant width plate for now. JAE, Still good advice, since I am doing the calcs in Mathcad to semi-automate the design, I am still going to check the section for it’s compactness, however there’s also a simplified clause for rectangular sections I will check out. Thanks again, of course further comment is always welcome.

Your force diagram bthh that the pin dia and the pin hole dia are the same Hi Dik, That’s correct. I select the closest available Crosby G shackle for the load. The next available drill size will be used to make the hole slightly larger than the pin. Red Flag This Post Please let us know here why this post is inappropriate.

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