It's a superficial look at traditional iterative bearing design using proprietary software...rather than a half dozen iterations for every design point, and produces some very useful trends...the charts are applicable to the 2" bearing that they state, but the trends are worth paying attention to.
e.g.
Chart 6 gives two quite useful rules of thumb...
* that doubling rotational speed for a given design uses twice the oil (as I've stated before, bearings move their own oil. Oil pressure is there to provide oil for the bearing to use, not to push oil into/through the bearing)
* doubling the bearing clearance basically doubles the flow that the bearing utilises also.
Chart 7 shows the temperature rise for different clearances/speeds. This is demonstrative of the "work" that the engine has to do spinning the journal inside the bearing and shearing the oil...the average working temperature, and thus the bearing oil temperature is typically approximated by supply temperature plus half the rise...the part of the curve to the left needs to be read in conjunction with chart 6, as the smaller radial clearances result in smaller amounts of lubricant flow through the bearings, which means that the energy expended shearing the oil is on a smaller volume per unit time and provides greater heating...except for the extreme, and artificial left side, it would probably have only a minor impact on bulk oil temperatures, but in the oil being flung from the bearing, into an environment of hot blowby gasses could be significant in varnish production, not to mention the operational viscosity in the bearing.
Charts 4 and 5 demonstrate that if the bearing clearances are too large, the load is shared less equally around the loaded side of the bearing, and at lower speeds (2,000 RPM is not low, it's cruising speed, not off idle/stalled it letting the clutch out)...bearings too loose, and the journal is more like a high heeled shoe (poor analogy, but it works I think), and can cause material damage to the shell...spinning it faster reduces the effect.
THEN read charts 1 and 2, and you can see how the "high heel" effect, exaccerbated at low speeds, reduces the minimum oil film thickness.
(for interest, note also that 40 micro-inches is about a micron...compare that to available oil filter ratings/efficiencies)
Take the above charts into account, and you can see why revving engines with little high load/low speed requirement go loose.
Reverse it and see why the like of Honda are going tighter on clearances for street engines with lower viscosity oils.
Look at them all together, and you can recognise the futility in determining minimum oil film thickness from a pressure gauge on a supply line.