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Federal Technology Alert power generated by the MTG plus the ABSC cooling capacity, and the energy input consisted of the natural gas input plus the total electric power consumed by the HRU, AC, CT, and pumps. Tests were performed for chilled water flow rates of 0.07 and 0.13 m3/min (19 and 34 gpm). The variation in the chilled water flow rate had practically no effect (only a 0.5 to 0.8% average increase) on the overall IES efficiency. Therefore, the efficiency versus ambient temperature for only one flow rate is presented in Fig. 19. In spite of a decrease in MTG efficiency (20–18%) with ambient temperature, the two IES configuration overall efficiencies increased with ambient temperature. The MTG + HRU configuration showed an efficiency range of 53 to 55% over the ambient temperatures experienced during the test while the MTG + HRU + ABSC configuration yielded an efficiency range of 37 to 42%. Addition of the ABSC to the MTG + HRU configuration resulted in a decrease in IES efficiency ranging from 16 to 13%, indicating, as expected, that using the waste heat to generate hot water for end use is more efficient than generating hot water for use to drive a single-effect absorption ABSC unit with a nominal COP of 0.7. 5.4 ABSORPTION CHILLER AND DIRECT-FIRED DESICCANT DEHUMIDIFICATION6 In the previous IES configuration (MTG + HRU + AC) the temperature of the exhaust gas leaving the HRU and discharging to the environment is in many cases sufficient for use in regenerating the desiccant in a DFDD. Addition of a DFDD to this configura tion will increase the utilization of the MTG waste heat and the efficiency of the IES. A series of tests were performed to compare a MTG + HRU + ABSC + DFDD configuration with the previously tested configurations. The LC and LCOP of the DFDD increase with an increase in process air dew-point or humidity ratio. Therefore, the series of tests were performed at the two DFDD process inlet dry-/wet-bulb temperature conditions of 29.4/24.3oC (85/75.8oF) and 35.0/23.9oC (95/75oF). The corresponding dew- point conditions were 22.4oC (72.4oF) and 19.2oC (66.5oF), respectively. At both inlet process air conditions, MTG power output, hot water, cooling water, and chilled water flow rates were held approximately constant at the measured conditions listed in Table 7. Also listed in Table 7 are the major performance parameters (i.e., HRU heat capacity, ABSC cooling capacity, and DFDD latent capacity) measured at the two process air conditions. As seen in Table 7, the LC of the DFDD for the 22.4oC dew-point condition was much higher than that for the 19.2oC dew-point inlet air. Fig. 19. Effect of ambient temperature on the efficiency of IES configurations. (Source: “Laboratory R&D on Integrated Energy Systems (IES),” Proceedings of the 2003 International Congress of Refrigeration, ICR2003, Washington, DC, August 2003.) The MTG exhaust flow rate, ranging from 11.33 to 4.16 m3/min (400 to 500 scfm), passed through the HRU and entered the regeneration inlet plenum of the DFDD. In the regenerative inlet plenum, in order to achieve a required regenerative stream air flow of 25.5 m3/min (~900 scfm), the MTG exhaust flow was mixed with outside air. The DFDD’s air flow rates, measured during the tests, were found to be within the range of 92.60 to 94.58 m3/min (3,270 to 3,340 scfm) with a face velocity of 318.4–325.3 m/min (1,044.7–1,067.1 ft/min) for the process side and 25.63–25.77 m3/min (905–910 scfm) with a face velocity of 88.1–88.6 m/min (289.1–290.7 ft/min) for the regeneration side. The overall IES efficiency with the addition of the DFDD calculated as the ratio of the energy output and the energy input was determined for the two process-air inlet conditions. The energy output consisted of net electric power generated, the ABSC cooling capacity, and the DFDD latent capacity; the energy input included the natural gas input and the total electric power con sumed by the HRU, AC, DFDD, CT, and pumps. The efficiencies of the MTG, MTG + HRU, and MTG + 20–– FEDERAL ENERGY MANAGEMENT PROGRAM .PDF Image | Summary of Results from Testing a 30-kW-Microturbine and Combined Heat and Power (CHP) System
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