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E r 2 (Table 13). From the geometry of the device,we can estimate a total ,seal line 4 \ I I I - of 16" (4" sealline between rotors, two 3" lines between rotor edges and casing and two 3" lines between rotor ends and casing), giving an average tolerance of .010". This tolerance is large and could be easily improved. Improvements to efficiencies could be large, Table 14lists efficiencies if 3% of the leakage were reduccd for several runs. An improvement of this nature is not at all unlikely. Note that this table assumes, fordata runs 162 and 195, that the leakagehasthesame quality as the working fluid, something that isprob- ably not true. This can be checked roughly by assuming thc water spreads over the casing about an inch thick, leaving only 6" of sealline or b .06in2 of area for the steam to leak through. Then, from Crashof's re- lation, the leakage &to of steam atlo5psig would be A = .0165(.06)(1~0)'~~= ,10lb/s correspondingtoavolumetric * qf: flow rate of .38 ft3/s. Tiiis very rough estimate indicates that the majority of the leakage ~ h i c h occurs at low qunlities is steam, as it would seem intuitively. One further characteristic of tho efficiency curves is the fact that efficiency differences between LOMand high quality flows seem to decrease withrpm. Thisappearstobecausedbyenergylossesathighrpmsdueto theneedto accelerate the water to rotor tip velocity. Th9s velocity, at 8 Tiiis equation was solved for A* for all inlet pressures (75 -3.20 psia) at all average leakage rates to get a value of A* of ,1602,014in !PDF Image | Performance Characteristics of the Lysholm Engine
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