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In Section 3. Obviously in this case the manufacturer has already supplied the dynamic load, and I will use it for my calculations. However, for the sake of comparison, I wanted to also look at the other three methods. Machine unbalance provided by Manufacturer 3. I have to be doing something wrong. Perhaps a second set of eyes will find it. Does anybody see an error? I just need some peer review to see if these calcs make sense.
RE: ACI You have a foundation I get , lb. The speed is not very high. In the old days we tried to size foundations based on weight using rules of thumb, such as 3 times the machine weight or 10 times the rotating parts.
Is soil stiffness part of it? It took a surprising amount of time to realize what happened. Because the output looked perfectly reasonable Be sure you are using the right mass and that you are using mass not weight for this equation. Speaking of that, you say that you ignoring rocking. At least for the hand calcs. STAAD can be a big help there. And in many instances, rocking turns out to be critical. The tricky part is, the customer wants the vibration limited to 0.
I might have to check that out. WARose - equations and require the rotating mass mr to be in terms of lbm. Equation requires the rotating weight Wr to be in terms of lbf. The unit conversions in ACI seem to get very messy!
ACI-351.3R-04 Foundations for Dynamic Equipment (Reapproved 2011)
Tezuru Defense manufacturing is all about project manufacturing and project accounting. If the frequencies are well separated, no further evaluation is needed. Gas Machinery Research Council, Afi. Computer programs, such as DYNA, are very useful in this regard. ACI provides some guidance that can machinery require that sufficient clamping force be available be extrapolated
aci 351.3r 04 foundations for dynamic equipment shared files:
351.3R-04: Foundations for Dynamic Equipment (Reapproved 2011)