Download Vespa Tecnica by Roberto Leardi, Luigi Frisinghelli, Giorgio Notari PDF

By Roberto Leardi, Luigi Frisinghelli, Giorgio Notari

Tutti i modelli Vespa prodotti dal 1977 al 2002: foto, particolari tecnici e costruttivi, caratteristiche tecniche, disegni tratti dal manuali originali, colori, esplosi dei motori, posizioni motore e numero telaio

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One is the current high efficiency chiller shown in Table 7. For the purpose of this discussion this chiller is labeled chiller A. The other two include a high efficiency chiller and a lower efficiency chiller, both available and popular in 1995. These chillers are labeled as chillers B and C respectively. Data from these older chillers is presented below. 91 Table 9. Liu's High Efficiency Chiller (B) Tevap,out Tcond,in Load 1000 900 800 700 600 500 400 300 200 1000 900 800 700 600 500 400 300 1000 900 800 700 600 500 400 300 85 85 85 85 85 85 85 85 85 75 75 75 75 75 75 75 75 65 65 65 65 65 65 65 65 44 44 44 44 44 44 44 44 44 44 44 44 44 44 44 44 44 44 44 44 44 44 44 44 44 GPMcond GPMevap KW 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 3000 2400 Tevap Tcond 612 555 503 453 406 362 318 273 220 536 483 436 395 356 319 281 243 478 437 396 361 328 296 260 223 Table 10.

Comparisons were made data at 71%, 45% and 25% load conditions. Similar chiller efficiencies were attained by either varying flow rate or inlet temperature. In fact the variable and constant flow results agreed to within 1% of one another. Redden’s work concluded that varying evaporator water flow rate has little effect on chiller performance. C om pressor pow er [kW ] 600 500 1000 ton load 660 ton load 330 ton load o 44 setpoint o 75 condenerw aterinlet 400 300 200 100 1000 1500 2000 2500 3000 3500 E vap o rato r w ater flo w rate [g p m ] Figure 32.

It is expected that there is augmentation on the tubes inner surfaces which increases heat transfer between the chilled water and tube wall. This augmentation affects evaporator pressure drop. In order to model the evaporator pressure drop, an effective length and roughness were determined. In actuality, the evaporator is much shorter and rougher than this effective length and roughness indicate. Also, much of the evaporator pressure drop results from tube bends and header losses. 53 However, since the actual geometry is not available, effective values were used.

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