Hypothetical Hollow Steel Sphere: collapse from outside pressure

AI Thread Summary
A hypothetical hollow steel sphere with a thickness of 1 mm and a diameter of 1 meter will collapse under external atmospheric pressure if enough gas is removed from the inside. The collapse is expected to occur through buckling rather than compressive failure of the material. The Zoelly-Van Der Neut formula, dating back to 1915, provides a theoretical limit for the buckling failure of spheres, although real-world failures often occur at lower loads due to defects. Alternative formulas, such as those derived from Timoshenko's work, suggest different critical pressures based on the radius-to-thickness ratio. Understanding these principles is crucial for accurate design and analysis of spherical structures under pressure.
thedan16
Messages
4
Reaction score
0
Hello physics forums,

Say you had a hollow steel sphere of thickness 1 mm and diameter of 1 meter (from outside to outside)?

Inside the sphere is gas at 1 atm pressure. Outside is 1 atm of pressure. How much gas would I have to remove from the inside until the sphere collapsed from outside atmospheric pressure?

I'd have to use bulk modulus correct?
 
Engineering news on Phys.org
This http://www.engr.uconn.edu/~cassenti/AnsysTutorial/Modules_APDL/Module%205%20Buckling%20Sphere.pdf

gives a formula $$P = \frac{2Et^2}{r^2\sqrt{3(1-\mu^2)}}$$

But since it doesn't give any information about to how it was derived and what assumptions were made, I have no reason to believe it's correct. This is one of those problems which is very easy to describe, but very hard to solve.

The only thing one can say confidently is that it will collapse by buckling, not by compressive failure of the material.
 
Yes, I'm curious to how this formula was derived! What about a cylinder or a cube?
 
That is the the Zoelly-Van Der Neut formula for buckling of spherical shells and goes as far back as 1915. It is the theoretical limit to the buckling failure of a sphere, whereas from experimental data most actual spheres will fail with loads 1/3 to 1/4 of that value, due to say manufacturing and assembly defects giving a sphere different from that of a perfectly smooth one.

If your library has the book by Timoshenko, Theory of Elastic Stability, you will find a derivation using linear methods.
Nonlinear methods of solution for this problem are difficult to solve.

Research pays off and here are some pdf's of interest:
http://traktoria.org/files/pressure_hull/spherical/buckling_of_spherical_shells.pdf
http://www.dtic.mil/dtic/tr/fulltext/u2/610809.pdf

The first link gives a different formula that is said to agree more with experimental results,
Pcr = 0.37E/ m^2

where m is the radius/thickness ratio.

The first formula in the same format becomes Pcr = 1.21 E / m^2, using a Poission ration of 0.3.

I suppose for your sphere, you will have to make some design choices on the differences fom an ideal shere
 
Last edited by a moderator:
Hi all, I have a question. So from the derivation of the Isentropic process relationship PV^gamma = constant, there is a step dW = PdV, which can only be said for quasi-equilibrium (or reversible) processes. As such I believe PV^gamma = constant (and the family of equations) should not be applicable to just adiabatic processes? Ie, it should be applicable only for adiabatic + reversible = isentropic processes? However, I've seen couple of online notes/books, and...
I have an engine that uses a dry sump oiling system. The oil collection pan has three AN fittings to use for scavenging. Two of the fittings are approximately on the same level, the third is about 1/2 to 3/4 inch higher than the other two. The system ran for years with no problem using a three stage pump (one pressure and two scavenge stages). The two scavenge stages were connected at times to any two of the three AN fittings on the tank. Recently I tried an upgrade to a four stage pump...
Back
Top