Originally Posted By: ZeeOSix
Also, explain this graph from the more timely paper that shows wear essentially is constant if the viscosity is above 2.2 cP.
And along side that here's another SAE paper abstract that pretty much supports the same conclusion.
Easily explained with some of the basics that they would have taught you at secrete agent school. Remember back to the Stribeck curve.
You have cherry picked articles that are focused on the boundary/mixed end, where minimum oil film thickness has been obtained, and asperite contact is commencing.
As you well know, in that range, life is generated by surface chemical and (and dry film in some cases) interactions, not by hydrodynamics.
So if you pick an area that's boundary/mixed lubrication, then it's no surprise whatsoever that viscosity doesn't play a part.
The small end bush (LOL, conrod bearing) doesn't rotate, it has a relatively small arc of movement, is not hydrodynamic, and therefore is additive dependent not viscosity dependent. Camshaft same, it's boundary.
Piston rings (as I tried to explain in the Rat thread to no avail) have multiple components...at points they are stopped, and at others full hydrodynamic.
There you go...explained.
Other areas of the engine are hydrodynamic, like bearings and piston skirts...viscosity keeps them apart, and they are relatively soft.
Per my link to the boundary/mixed discussion, and seminars that Solarent has brought up, they are changing bearing materials, mechanical designs, and the additive packs needed to increase the boundary/mixed contact in these regions too, and get the next 0.5% fuel economy out of them.
Re Stribeck curve and engine components
Note per below the actions of friction modifiers and AW additives on the region in the left (where viscosity is no longer a significant part of the mix)..."Wear controlled by AW and EP additives"