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SteveMelton
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- SteveMelton
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after running some test frequency response models using various connectors for rivets: beam, spring, bonded faces... I found unacceptable variation in the response for the methods. I decided to find a way to use RBE3-CBUSH-RBE3. working the model…
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yes, a bonded connect may be OK for frequency analysis. not looking for any stresses.
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hey, the 1d beam bolded connection is neat. however, I have LOTS of rivets and was looking for a way to model them easily such as CBUSH (spring/damper) at rivet nodes, no holes. for this rudder, since I am only looking for frequency response, I ma…
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installed and now flying instrument approaches.
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https://www.rvplasticparts.com/
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this is a airplane control gust lock. it is part of a kit. a separate part captures the rudder. my youngest daughter makes gas money with printed parts. I throw them over the wall she sells them to experimental aircraft builders. Mecway was ke…
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load testing. perfect.
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addictive to watch. I need to get a life.
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agree, for plastic analysis always use true stress/strain
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I do not need nonlinear or large displacement. ANSYS doesn't do nonlinear for remote displacement or remote force either.
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some say, 1000 lb bolt preload + 1000 lb tension load = 2000 lb bolt load
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yes, what is the load on the bolt? 1000 lb
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I think that could be useful. Correct, load the bolts close to yield. My favorite question, preload a single rigid flange bolt to 1000 lb and apply a 1000 lb load to the flange. What is the load on the bolt?
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final plot with moment on flange. hoop stress. flange face has no friction in this case.
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new config. no load on the model, only prestress on the fasteners.
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yes, draw the bolt short .005 and apply contact from the bolt face to the flange. CCX will prestress the bolt by that amount. in this case I also applied .3 friction factor to the bolt contact.
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thx for the radial displacement. also, this 360 model makes it easy to add a moment to the flange. better than ANSYS. I like V10 beta. Faster graphics and right click position input for cut viewing. it's good.
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Stress_tt = hoop stress. I am still trying to determine the formula for radial and tangential displacement.
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spot on deflection, validated!
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3D non-linear CCX. Nine contact surfaces. Each part is separate, clamp, arm, pin, bar. the pin has a .002 inch gap on the diameter, others are no gap. start with a small load. if the deflection is too much it cannot converge.
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that's automesh of a STEP file with x2 mesh refine using paint at the arm to clamp contact. quick and easy. solves in less than 30 minutes. a couple of things going on here, one, the arm to clamp interface and two, the peeling of the clamp from t…
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my fault. I should have been clearer. 2D beam, I wasn't selecting the correct beam stress. works fine.
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same for me.
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I may be able to do that but give me some time.
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note: I was able to apply bolt pre-tension by using offset nodes and the contact feature. That was a nice.
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for this plastic analysis I neglected the bolt threads.
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thank you for your excellent program! this is very beneficial to the experimental aircraft association since these are widely used. www.eaa.org
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as printed
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yes, the material is truly anisotropic for strength. for frequency analysis, isotropic probably OK. 1000 mile round trip, the fairing look OK. speed gain with the fairing is about 3 kts.
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TAZ6 printer and ABS plastic. it's an experimental homebuilt airplane.
