I'd really like to work out a way to measure force on a link to compare to buckling. CHow can it be done by using the weight on the link and length and angle of the link?
From the calculations I've done, it backs up the statement that most of the failures are going to be from bending loads (landing on a rock in the middle of the link) than it will be from buckling.
For the buckling load, using that formula of Fa = T/(a+b), you should get Fa = 5500 ft*lbs/(10.5/12 ft) = around 6300 lbs. Divide by the cross sectional area of 1.178 in^2 should give you around 5300 psi. I wouldn't worry too closely about dealing with a ground force. The formula I posted is used for a "trapped tire" scenario. If the vehicle is accelerating, it can never be more than the maximum torque output the axle can withstand. And you are using the maximum rating of the axle anyways.
One thing to keep in mind is that with impact loading, it's true that the applied forces can far exceed the stress limit of the material, but it's only for a extremely short amount of time. In the words of Andy Dufresne, it's all about pressure and time. For instance, if you hit the link with a hammer, the stress at that point is going to be very high and you might "ding" the tube. You will not, however, buckle the entire tube. Take that same force and apply it for a longer period of time, and you'll probably get the truck to break orbit. If I was designing a four-link for my truck, I would probably design that lower link for a 5G impact both for the truck standing on end (buckling) and the link hitting a rock (bending). This means you should be able to withstand a sustained load of 5Gs without failure. As for factor of safety, I would run with an FOS of around 1.2-1.3. It's all really just a play on numbers. You can run a lower FOS (1.5) with a higher expected load rating (5G) or you can run a lower load rating (3G) with a higher factor of safety. There is no reason to design for 5Gs and then run a factor of safety of 8. Because all you're doing then is designing for 40Gs with a FOS of 1. (Factor of safety is the load that the tube CAN withstand divided by the load it WILL actually see)
People are right that it can get complicated when you try to analyze a dynamic situation from a static point of view, but it doesn't have to be. For starters, you could analyze it at ride height, full droop, and full compression. That oughtta get you good nominal values with boundary conditions at both suspension travel limits. It's all in the assumptions. I threw out a number of 5Gs. That number came from design work I've done on "on-road" suspensions. If you want to estimate, you'll need to pick and example or assume a situation.
With some of the buggies you see, I've seen them trying to climb a near vertical bluff that's maybe 20-30 ft high. Then they stall out and land back on the rear suspension with a near vertical vehicle. From that, you can use the good old F=ma. You know the weight of your truck (m), and you can estimate the acceleration by calculating the speed at impact (based on distance above the ground when it started freefall, and the time it took to reach a velocity of zero. Roughly one half of the rebound time of the tire should be a good estimate of the acceleration (deceleration) time. That will give you a loading scenario that you can apply to your truck. Are you going to see something that extreme? Probably not. But it's a start.
Okay, this post is probably long enough.....
-krug