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2170, Page 4 - Test A represents the typical operating conditions of a heat pump system, i.e. condensation temperature equal to 60°C and evaporation temperature fixed at 20°C. The water conditions were 105 L/h for water flow rate and 40°C at the inlet of the evaporator and 115 L/h for water flow rate and 34.5°C at the condenser side. - Test B. The condensation temperature was around 52.5°C and the evaporation around 19°C; all the other parameters were kept equal to Test A, except the water temperature surrounding the condenser fixed at 30°C. - Test C. The condensing temperature was lowered to 50°C and the evaporation temperature at 10°C, just setting the water temperature at 32°C inlet to the condenser and 15°C inlet to the evaporator. 3. RESULTS AND DISCUSSION 3.1 Experimental results Firstly, tests with pure POE oil were carried on, according to the three operative conditions described above. 180 cm3 of POE oil were loaded into the compressor and the experimental obtained data were used as reference point for tests with nanofluids. The acquired data were used to calculate several parameters to evaluate the system performance, as: - Superheating (SH); - Subcooling (SC); - Heat transferred through the condenser in both refrigerant (Qcond) and water side (Qw_cond); - Heat transferred through the evaporator in both refrigerant (Qevap) and water side (Qw_evap) - Heating (COPH) and Cooling (COPC) coefficient of performance; - Compressor isentropic efficiency (is); - Compressor volumetric efficiency (vol). Obtained results are summarized in Table 1, Table 2 and Table 3, according to selected test conditions. First of all, the POE oil with TiO2 nanoparticles at a mass concentration of 0.1% was tested. Then, the nanolubricants with TiO2 nanoparticles at 0.05% and 0.5% in mass and with SWCNH at 0.1 wt% were considered. Therefore, mineral oil was also kept into account as base fluid. As widely known, R134a is not miscible with mineral oil (MO). As proposed in Wang et al. (2003), MO was studied, initially without nanoparticles and then with TiO2 nanoparticles at a mass concentration of 0.1%. For each nanolubricant and experimental condition, tests were repeated at least three times and were found to be repeatable in all cases, within the limits of the experimental errors. As standard procedure, after tests with each nanofluid, the system was carefully cleaned and the compressor was sectioned to visually observe any possible deposition of nanoparticles inside it. The presence of nanoparticles was evident on the surface of the rotor, as shown in Figure 3. Moreover, the nanolubricant was extracted and analysed by means of DLS technique. It was observed that for each nanofluid, the nanoparticles dimensions remained constant before and after the tests. 3.2 Results discussion Analysing the experimental results and the derived parameters, it seems that nanoparticles do not have any influence on system performances, in contrast with the literature reported above. In Tables 1, 2 and 3, the deviations between system parameters working with POE pure oil and with nanolubricants are also reported. They were calculated form Equation 1 deviation% datacalculated datareference 100 (1) data reference where “data” stands for the property indicated in the table. From these results, an appreciable performance increase was not found, if compared with the reference test carried out with pure POE oil; improvements were not obtained even when MO is used, pure or as base fluid mixed with TiO2 nanoparticles. 15th International Refrigeration and Air Conditioning Conference at Purdue, July 14-17, 2014PDF Image | Nanofluids Application as Nanolubricants in Heat Pumps Systems
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