This is just one possible way of working out the loading on the clamp block. At the end, the point reaction loads can be used to come up with a distributed loading on the hole surface, which can then be used to calculate a final bending moment. Hope it gives you some ideas.
Edit - Looks like...
I recall some Structural Repair Manuals (SRM's) stating a size of blend (rectangular surface area and depth) and a minimum defined distance between blends. Any blending that falls within this size and spacing criteria is considered structurally acceptable, and only to report any blending that...
From a concessions / repairs background, we would receive reports identifying the locations along threaded joints where blending had been carried out to remove corrosion / damage, etc. These blending locations could be anywhere along the threads. I could see the potential for using a go/no-go...
As a suggestion, you can put a procedure in place where the MRO supplies you with a report identifying the region of the threads that have been blended to remove corrosion / impact damage etc, such as a circumferential length of each damaged thread. I'm sure this will also include an appropriate...
There are a number of ways you can model this clamp. It also depends on what software tools you want to use for the calculations.
If you wanted to do this by hand, I would suggest Mathcad. It also depends on how much simplification you want to apply.
This is just one suggested approach. The...
The amount of interference needed I think will be defined by what type of loading it's going to see. What are the operational loads? For this type of joint, you can calculate the radial interference pressure seen at the contacting surfaces. This and friction are the only things that will be...
The aspect I've noted may not be relevant / significant, but would you need to take into account that bolts in the round base plate placed on a circular line will have different radial distances to the rectangular column, and, as such, wouldn't the bolts closer to the rectangular corners pick up...
If you’re copying an existing design, do you have a copy of the stress calculations for it? Sounds like you’re doing a new set of stress calculations. Can you show a picture of your free body diagram (FBD)? I’m assuming there’s another clamp block on the underside. If there is, is there a gap...
If you could show some pictures of the cylinder [thin / thick walled (geometry), material, etc] and how it is being loaded and restrained [FBD(s), internal pressure and / or externally applied loading [point force(s) / moment(s), distributed load, circumstantially / local point restraints, etc]...
He may be thinking of thin wall cylinder theory, where loading is distributed circumferentially, axial load can be given as N/mm and circumferential BM as N.mm/mm. Is that what he’s after?
One thing that would be good, and that's if you can set up a menu system that allows the user to make selections on the page layout / format. I know Mathcad does have page margins and header / footer capabilities. In my case, the documentation I write are formal Engineering Justification...
There are a number of methods you can use to produce a beam column buckling template. One, as suggested above, is by successive approximations, another is by a strain energy method, where you assume the displaced shape by using a trigonometric series. I've created one where I've solved the 2nd...
Just as an update to what I've currently done to estimate a pressure over-closure spring stiffness value 'k', the info below is what I've come up with. There are a couple of aspects that I think has a big influence on the 'k' value. The 1st is the factor Pk. This is based on the assumed manner...
Knowing the loading, I would construct a FBD for each load case. This will enable you to determine the load paths. For instance, it looks like that, before any bolt sees a tension load, the load has to migrate through the plate and go towards the outer edges. Would the bolts see a compression...
Just as an indication, these are the current hand calc to FEA results (use of older FEA results).
The shear is seen to be more sensitive to the used k factor. At the end of the day though, all are affected by the k value.
The k I’m referring to is the pressure overclosure slope factor (compression spring stiffness) used in FE contact analysis. I’m looking for an approach that will give more confident values.
When considering failure of a high dW lug, I would agree, you would expect tension failure.
The purpose of my investigation is to try and predict the Pmax and to obtain the kt. I’m not trying to predict any failure mode, to do so would involve plasticity. A part of the approach was to first come up with the lug loading, just like a typical beam analysis. My investigation also involves...
The FE model is 1/4 of the lug, so you're seeing 1/2 the lug thickness. This is the most current FE model version (done today with a revised 'k'). The position of the peak may be off, but the bearing stress level is quite close to the hand calc. The bearing pressure distribution for this dW...
