1、Index of Technical and Symposium Papers Vol. 1 IO, Part 1 TITLES A Algorithm of Stereoscopic Particle Image Velocimetry for Full-Scale Room Airflow Studies, An, YIGANG SUN, YUANHUI ZHANG, LINGYING ZHAO, XINLEI WANG 75 Ammonia-Water Absorption Heat and Mass Transfer in Microchannel Absorbers with Vis
2、ual Con- firmation, J. MARK MEACHAM, SRINIVAS GARIMELLA 525 Analysis of the Impact of C02-Based Demand-Controlled Ventilation Strategies On Energy Consumption, Average Modified Stanton Number for Evaluating the Ice-Melting Characteristics of Ice Harvested from a Thermal Storage Tank, AKIYOSHI OHIRA,
3、 MICHIO YANADORI, YOSHITAKA SAKANO, MIYUKI MIKI 81 MONCEF KRARTI, MOHSIN AL-ALAWI . 274 Bin Method Energy Analysis for Ground-Coupled Heat Pumps, A, STEPHEN P. KAVANAUGH, STEVEN E. LAMBERT. . 535 C Calorimetric Analysis of the Solar and Thermal Performance of Windows with Interioir Louvered Blinds,
4、MICHAEL R. COLLINS, STEPHEN J. HARRISON . 474 Comparative Study of the Airside Performance of Winglet Vortex Generator and Wavy Fin-and-Tube Heat Exchangers, A, C.C. WANG, Y.J. CHANG, C.S. WEI, B.C. YANG 53 Comparative Study of Shell-Side Condensation on Inte- gral-Fin Tubes with R-II4 and R-236ea,
5、A, WADE W. HUEBSCH, M.B. PATE . 40 Comparison of Diffusion Characteristics of Aerosol Parti- cles in Different Ventilated Rooms by Numerical Method, BIN ZHAO, ZHAO ZHANG, XIANTING LI, DONGTAO HUANG . 88 Considerations in the Design and Application of Solid Oxide Fuel Cell Energy Systems in Residenti
6、al Mar- kets, ROBERT J. BRAUN, SANFORD A. KLEIN, DOUGLAS T. REINDL. . 14 Consumptive Water Use for U.S. Power Production, PAUL A. TORCELLINI, NICHOLAS LONG, RONALD D. JUDKOFF 96 Convective Evaporation on Plain Tube and Low-Fin Tube Banks Using R-123 and R-l34a, LIANG-HAN CHIEN, J.-S. WU . 101 Coolin
7、g of High Heat Density Rooms Today and in the Future, LENNART K. STAHL. 574 D Decision Support Software for Sustainable Building Refurbishment, C.A. BALARAS, E. DASCALAKI, S. KONTOY IAN N I DI S . 592 Development and Implementation of HVAC-KBCD: A Knowledge-Based Expert System for Conceptual Design
8、of HVAC it may also include a receiver, economizer, expansion turbine, and/or subcooler. In addition, aux- iliary components may be used, such as a lubricant cooler, lubri- cant separator, lubricant-return device, purge unit, lubricant pump, refrigerant transfer unit, refrigerant vents, and/or addit
9、ional con- trol valves. For information on absorption equipment, see Chapter 41 of the 2002 ASHRAE Handbook-Refrigeration. GENERAL CHARACTERISTICS PRINCIPLES OF OPERATION Liquid (usually water) enters the cooler, where it is chilled by liq- uid refrigerant evaporating at a lower temperature. The ref
10、rigerant vaporizes and is drawn into the compressor, which increases the pressure and temperature of the gas so that it may be condensed at the higher temperature in the condenser. The condenser cooling medium is warmed in the process. The condensed liquid refrigerant then flows back to the evaporat
11、or through an expansion device. Some of the liquid refrigerant changes to vapor (flashes) as pressure drops between the condenser and the evaporator. Flashing cools the liquid to the saturated temperature at evaporator pressure. It pro- duces no refigeration in the cooler. The following modification
12、s (sometimes combined for maximum effect) reduce flash gas and increase the net refrigeration per unit of power consumption. Subcooling. Condensed refrigerant may be subcooled below its saturated condensing temperature in either the subcooler sec- tion of a water-cooled condenser or a separate heat
13、exchanger. The preparation of this chapter is assigned to TC 8.1, Positive Displace- ment Compressors, and TC 8.2, Centrifugal Machines. Subcooling reduces flashing and increases the refrigeration effect in the chiller. Economizing. This process can occur either in a direct- expansion (DX), an expan
14、sion turbine, or a flash system. In a DX system, the main liquid refrigerant is usually cooled in the shell of a shell-and-tube heat exchanger, at condensing pressure, from the saturated condensing temperature to within several degrees of the intemediate saturated temperature. Before cooling, a smal
15、l portion of the liquid flashes and evaporates in the tube side of the heat exchanger to cool the main liquid flow. Although subcooled, the liq- uid is still at the condensing pressure. An expansion turbine extracts rotating energy as a portion of the refrigerant vaporizes. As in the DX system, the
16、remaining liquid is supplied to the cooler at intermediate pressure. In a flash system, the entire liquid flow is expanded to interme- diate pressure in a vessel that supplies liquid to the cooler at satu- rated intermediate pressure; however, the liquid is at intermediate pressure. Flash gas enters
17、 the compressor either at an intermediate stage of a multistage centrifugal compressor, at the intermediate stage of an integral two-stage reciprocating compressor, at an intermediate pressure port of a screw compressor, or at the inlet of a high- pressure stage on a multistage reciprocating or scre
18、w compressor. Liquid Injection. Condensed liquid is throttled to the interme- diate pressure and injected into the second-stage suction of the com- pressor to prevent excessively high discharge temperatures and, in the case of centrifugal machines, to reduce noise. For screw com- pressors, condensed
19、 liquid is injected into a port fixed at slightly below discharge pressure to provide lubricant cooling. COMMON LIQUID-CHILLING SYSTEMS Basic System The refrigeration cycle of a basic system is shown in Figure 1. Chilled water enters the cooler at 12“C, for example, and leaves at 7C. Condenser water
20、 leaves a cooling tower at 30C, enters the condenser, and returns to the cooling tower near 35C. Condensers may also be cooled by air or evaporation of water. This system, with a single compressor and one refiigerant circuit with a water-cooled condenser, is used extensively to chill water for air conditioning because it is relatively simple and compact. 38.1
