Originally Posted By: DeepFriar
Originally Posted By: Gokhan
However, this patent claims that PVCI for synthetic oil (at least for GTL) is better than for conventional oil, therefore PVC for synthetic oil eventually exceeding PVC for conventional oil at some high temperature (130 C or above). Esters, PAOs, Group IIIs, etc. have a lower 100 C PVC than Group II but they may actually have a higher 130+ C PVC. Therefore, I'm not worried about the PVC for synthetic base stocks anymore, including esters. Synthetic oils in addition tend to have better VIs, helping even more for high-temperature oil-film strength along with PVC.
Thanks for that, it helps me understand it better. Does this also mean that the HTHSv metric is a wobbly one at best for the poor layman given that PVC most closely resembles the real world in terms of actual working viscosity?
The answer lies in the fundamental curve of lubrication -- Stribeck curve:
There are three regions in lubrication, and elastohydrodynamic lubrication (EHL) overlaps with two of them and covers a large portion of the lubrication curve. Therefore, EHL, where PVC (oil-film strength) plays an important role, is important for all engine components, including journal bearings.
The curve basically says that if you can keep the viscosity
high, and/or the speed (V) high, and/or the pressure (P) low, you will be in the hydrodynamic lubrication (HL) region, in which there is a thick oil film seperating the moving parts. HL region is the same terrifying phenomenon of hydroplaning of a car, where the car completely loses tire-to-road contact and starts flying on the water, which is caused by driving too fast on water -- hence the usefulness of the Stribeck curve.
So, keep your viscosity (HTHSV) high, load (pressure) low, and RPM high, and you will be fine. However, this is not always practical. For example, there will be cases where you will experience high loads and/or low RPMs, and your bearings will enter the EHL region. Then, PVC (oil-film strength) becomes important.
Also, in the valvetrain and parts of the cylinders and rings, the pressures will always be high because of the inherent geometry, as you don't have the luxury of a large smooth matching surface as in the journal bearings. Therefore, valvetrain and parts of cylinders and rings always run in the boundary lubrication and mixed lubrication regions because the pressures are always high between sliding components due to their smaller surface area.
In summary:
(1) Keep you HTHSV high enough so that you spend as much time in the HL region (rightmost part in the curve) as possible, where there is no metal-to-metal contact at all (like no tire-to-road contact during hydroplaning). The only downside to this is that as you can see in the curve friction increases slowly as you move further right into the curve. This is not due to metal contact but because of the internal friction of the oil. There is no engine wear caused by that by you lose fuel economy if you make HTHSV too large and you are needlessly too far right into the curve.
(2) EHL regime and therefore PVC (oil-film strength) is always crucial in any part of the engine, including journal bearings, while being a lot more crucial in the valvetrain and parts of cylinders and rings, where you are always in the BL and ML regions. (Note that in the BL region, AW/EP/FM additives are crucial.) Therefore, always choose an oil known to exhibit low wear due to its higher-quality base stocks. You don't necessarily need a synthetic oil. Nevertheless, the Chevron patent claims that with a synthetic (at least with a GTL), you have a higher high-temperature (130+ C) PVC (higher oil-film strength, thicker EHL oil film) and are better off in the EHL regime.
I hope this covers it all!