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...inverse of this, but this is how it is defined here) By conservation of energy, the effect of the spring at the wheel can be characterized by F_s*dz_s = F_w*dz_w Therefore, F_w/F_s = dz_s/dz_w = MR Combining equations from above: F_w = MR*F_s, (from here down I take some derivatives, if...

...would be encouraging if it we independantly arrived at the same result? The only thing that looks appreciably different to me is that you have a 2*T factor instead of a T/2 factor, which may come out in the wash. One of the finer points might be chassis flex, which would probably mean that...

Well, most people wouldn't classify me as old just yet, so in my case, it's just another senile engineer.

...cancellation that you speak of, I get a somewhat different expression than you: K_R/L = ratio of RF to LF wheel rate = N/D N = %FRS + %RRS*(t_f/2)*(h_cg/L)*(eta/R_L) D = %RRS*(t_f/2)*(h_cg/L)*(eta/R_L) - %FRS %FRS = your "Z" value %RRS = fraction of total roll stiffnes @ the rear t_f...

Also, if you would like a break out radius/cutter radius at the ending, you can sweep a triangle along a path... I do this probably once every 3 months or so, and it actually comes out looking nice and you can even dimension the runout radius.

quest4k, Did you try a section, it should be able to pick up an arc then?

kcj, Your suggestion is exactly what we had worked up and pursued for a couple of days, but then realized that packaging to the master cylinder would then also be and issue. We've decided to manufacutre our own master cylinder to eliminate packaging uncertainties. Thank you for your suggestions.

Have been searching the internet all day for something that I was sure would exist: an electronically actuated master cylinder. For my system, I have a slave (output) cylinder that is mounted remotely in a very tight space, so no room for using direct electrical actuation on the output...

We currently use an MSI laminated piezo film strip sandwiched between a cover plate and the vehicle to detect contact between a given surface of the vehicle and anything else in its surroundings (MSI P/N 1-1002405-0). We have a new project that requires a smaller sensor. Basically, the...

Greg, The part # would be greatly appreciated.

Norm, I see what you are saying about the 3DOF requirement, but the way that I have analyzed a trailing link in the past is to say... OK we have two points with a fixed distance in between them, one is grounded (chassis pivot) so what do we have to specify to determine where the other point...

Norm, No street use, strictly a race vehicle. Also, not looking for something that is "less harsh" or anything like that. I just mainly want to eliminate friction surfaces from the suspension system by eliminating sliding pivots. A similar idea to what open wheel cars (F1, Indy, etc.)...

Does anybody know of current designs that utilize a/multiple flexure joints as a substitute for a spherical type joint? I have been considering ways to accomplish this for the purposes of a racing suspension, where it is generally required that a trailing link joint be very stiff along the axis...

This is not the only reason, but if you try to fillet unknit faces SW informs you: "Cannont knit laminar faces". But if you knit them, it understands how to create the fillet. I'm not very experienced w/ surfacing, but I would imagine that there are other examples of similar operations in SW...

Is there a way to determine which feature the temporary axis I am selecting belongs to (it seems length of the axis is a rough indicator, but not good enough sometimes)? I am concerned w/ selecting specific temporary axes b/c in a part w/ concentric features, I would like to associate as much...

Help --> About SolidWorks --> License Agreement --> Article 1.A (near bottom of paragraph) " If the Software is permanently installed on the hard disk or other storage device of a computer (other than a network server) and one person uses that computer more than 80% of the time it is in use...

Background: I have recently installed COSMOSWorks and am trying to follow through some tutorials, but I am especially interested in the buckling tutorial. However, when I get to the point of running the analysis (after, meshing, mat'l definitions, etc.) I get a pop up w/ the following text...

I did the search before I posted and I found that you could not put a different EXPLICIT tolerance on each dimension, but the tolerance I am talking about is implicit based on our drawing standards. 3 decimals = +/- .005 2 decimals = +/- .01 Oh well, I guess that's not possible either.

Is there a way to get an independant # of decimals on the diam. & depth of a hole in a callout (differing decimals = different tolerance on diameter vs. depth)?

I am trying to define the shape of standard aero/streamline drawn tube. There is a MIL spec that gives some inspection dimensions and major and minor lengths of the tubing, however, it does not seem as though I have enough info to fully define the shape for modeling (stress analysis not CFD)...