I need to calculate the torque on the 20inch diameter wheels to rotate the 30,000lb 120inch diameter cylinder past the 90deg position where the center of gravity is 12.5inches from the rotational center.
Wheels are linked mechanically and driven by single motor.
Coefficient of friction between...
Correct, as stated above I already asked. They couldn't explain it. Just when the ratio D/d was over 2 to "double the force".
I have one idea that it could be due to the part geometry. The concentration of mass at the far end could need to be treated as a separate part with it's own cg and not...
Yes, the CG height is lower on the strange shaped part. Which made me believe a smaller force is required to hold it in place since the inertia and mass are the same as the cylinder.
But I was told the reaction force would actually increase, even though the CG is closer to the mounting end of...
D is distance from top of part to center of gravity.
d is distance from bottom of part to center of gravity.
The bolts themselves are not relevant to the question and can be ignored, I only mentioned them as a description of how the real part is attached to the tilting table.
The force...
Thanks for the help so far. I have already done the bolted joint calcs and have that worked out.
The question is about identical moment of inertia values but mass distribution changing.
Does the reaction force change based on D/d ratio from center of mass as shown in my first message?
Or does...
The cylinder has a flange on the base that is bolted to a tilting table. Imagine the cylinder axis being perpendicular to the floor and then tilted by the base until the axis is parallel with the ground.
Assume the bolts are equally spaced with one at the 12 oclock position.
I am looking for...
I have a cylinder rotating about its base.
When I decelerate to a stop is there a point where the ratio between the mass at the outer fibers and the center of gravity make a difference in calculating the reaction force?
The cylinder base is bolted down with four bolts and I am calculating the...
Since these are custom 4140 gears I ended up having them put on a shaper and the keyways cut parallel to the bores.
Made steel spacer-shims to bring the vertical clearance to 0.002in and standard keystock.
I referenced an old Koike power drive design manual where it talked about toque of snug...
Does the sharp corner on the step-key shear plane reduce shear capacity?
Also I would have to cut a larger keyway in the gear and I don't want to do that.
Going up to the next size key does not leave enough material between the keyway corners and the gear hub diameter and I would be afraid of it cracking.
I have two gears that have been keyed incorrectly.
The widths on gears and shafts are correct.
The depth of the keyway in the shafts are correct.
One gear has been broached too tall by 0.02" and tapered 0.006".
The other gear has been broached at an angle and leaves a keyway height of 0.502 on...
There is a high probability of impact loading so I am attempting to keep a shallow angle to avoid excessive bolt loading. I realize there is no way you would know since I forgot to include that in my original post.
This application requires a specific type of titanium to avoid contaminating the part that touches the wheels.
I will contact ringfeder and see if we can work out a way to use their design and still meet the material requirements.
I'm designing a wheel that can be moved along a machined tube.
I have chosen an 8deg taper between my split collar and clamp plates but that was just a guess.
Are there any guidelines on split friction clamps that might reduce the number of design iterations I have to build and test...
