Search results for query: *

Thanks anyways

Thanks. Worked perfectly. I have another question. I tried the same procedure to run a C code I wrote but it doesn't seem to work. There must be another way for different types of code.

Hello. I am new to Octave for windows. I would like to know how to run an m-file I write in the notepad++ gui. Are there any tutorials available? Thanks,

Hello, I was wondering if anyone has used D-space for control simulations before? If so, could you recommend documentation or provide hints/tips on its use. Thanks, coppola

Actually I did a bit of reading. I figured out my assumptions do not apply here. Sorry for the inconvenience. These help the situation: A*(2*pi*f)^2=max accel. Power=Re(F*v(w)), where v is the Fourier spectrum of the exciter velocity cheers,

Greg- Ok I will not contradict you here. Maybe I misunderstood the question. If so, maybe you can enlighten me. I don't know any specs about the shaker in mind, I assumed that the maximum energy it needed to produce is to lift that MASS (in the face of gravity) in a particular time of 1/100s...

You need at least the distance the shaker moves the mass. For example, a simplified calculation results in an answer of 40.77kg in mass for a 0.5cm lift distance at 100Hz with 400Watts. If you turn up the freq you lower the amount you can lift. (this all assumes that you are lifting a couch)...

Start with the equation btrueblood gave you. It will start you off on the right foot. cheers,

:). thats great, the elderly. Interesting readings on the hydrino.

btw, the left block is aluminum and the right is titanium. They are within air initially at a higher temperature. Just a comparison. You can see how differently the temperature distribution propagates on the left compared to the right.....

Good comments above. I solved it as a CC (convection-conduction) problem in comsol. This could also be done by hand, but it takes 5min if you only need it for simulation/illustration purposes. I attached an animation for you. cheers...

Assuming your 552 lb is lbf. Simply, E=integral(F*ds)=F*s =552(lb)*16(in)=8832(lb-in) P=energy per unit time=E/t =8832/6=1472 (lb-in/s) = 122.67 (lb-ft/s) 1hp=550 (lb-ft/s) thus, required power assuming no losses=0.2230 hp cheers,

Understandable. Have you determined what mode of stress defines your system design?

Well, I don't know your exact case. However, in the vast majority of cases what you said is right and it would be customary to design the pin based on shear stress. What kind of system is it? cheers,

Why are you modeling the pins as simply supported or even fixed-fixed? Are you performing some kind of deflection analysis? Otherwise I would suspect that the pins you need for a pulley/sheave should be designed based on the shearing separation planes and von Mises stresses. cheers,

In my opinion rough estimates are not the way to go. Nowadays, we are a little more advanced then that (hint hint).

Ah yea. Thanks for the link. I did a bit of reading, it seems that we can define this as the amount of mass that participates with one particular eigenmode. In other words whether the mode is local or global. In most cases I think we would be more interested with the global modes and...

What do you mean by % mass participation? Shouldn't the entire mass be included?

Not sure I understand what you are asking

Just a thought. Maybe you are better off using finite elements as mentioned by others. The Comsol Multiphysics version I use actually has an example of a cylinder/tube with a hole in it. They then apply a stress/fatigue analysis, fairly interesting. You may want to look into something similar...