willie59
Administrator
And I would be curious as to what is causing aerated oil in the first place, that's not normal.
Hi TC
Thanks for responding. Tank is massive for the application (450 ish L). Machine is using standard 32 grade hydraulic oil. 2 Rexroth piston pumps (pressure compensated). as soon as Hi rpm is selected the compensators move the swash plates one way which brings system pressure up to 200 bar. Idle pressure is approx. 20 bar. (adjusted on the pumps).
Tank has a baffle plate in the centre with the suction lines on the opposite diagonal to the return line. We have had the access plate off the top of the tank and sometimes at full flow you can see small bubbles coming back into the tank. However it's on the opposite diagonal to the suction ports! One tank for the machine, 2 main pumps and one small electric pump in case of main engine failure (main pumps PTO driven, back to back)
Can't see any froth in the tank, just what I'd call small bubbles in the oil (like what you'd see in flat lager or cider).
Regards
Phil
What an excellent discussion to discover. One question I have, and I qualify this by saying that I haven't done the sums, but, in the circumstance where we assume the piston seals are cactus and we're assuming that the load is being supported by the difference in displacement between the above piston space, with rod, and the below piston space, without rod; surely there's potential for fairly severe amplification of pressure? It seems to me to be a form of leverage and I can imagine that in many circumstances this could be enough to open a pressure relief valve and allow the load to drop.
The point I'm making is that whilst theory says that dodgy piston seals can't allow the load to drop (without squirting oil out the rod seals!), surely they can cause excessive pressure in other areas which will result in the same thing?
Nutwood, you are exactly right, when a cylinder changes from a piston type cylinder to a displacement type cylinder due to the piston seals leaking pressures can increase by orders of magnitude. If a cylinder has a 4" piston, the area of the piston is roughly 12 square inches. A 12,000 pound load would create a 1,000 psi pressure on the piston side of the cylinder. If the same cylinder has a 2" rod, then the displacement area of the rod is roughly 3 square inches, if the piston seals are bad then the same 12,000 pound load would induce about 4,000 psi on BOTH cylinder ports, piston and rod end. If there are no relief valves opening to tank, then damage can occur to the cylinder tube, rod packing, hoses, steel lines, or even the control valve. Note that a crossport relief block won't help at all because the pressures are equal on both lines due to the piston seal leakage.
Sorry, just felt like preachin' for a minute I guess, lol
Nutwood, you are exactly right, when a cylinder changes from a piston type cylinder to a displacement type cylinder due to the piston seals leaking pressures can increase by orders of magnitude.
I'd suggest that this potential pressure amplification is a really good reason not to leave a load on a hydraulic cylinder that's not been designed for continuous load holding.
When I tried to explain some of this stuff the other day, the guy politely told me 'all you need to do is remove and re-install the cylinder the other direction and that will show you it doesnt matter'....
No need to comment, stuck this in here for the pure amusement.
Thanks to all who post high quality info on HEF, I love the theory of mechanics.........TIO