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IEA SHC Task 38 Solar Air Conditioning and Refrigeration Subtask C2-A, November 9, 2009 75 Collectors outlet temperature 60 Tank bottom temperature 59 70 58 57 Temperature [ C] 65 60 Temperature [ C] 56 55 54 53 55 52 calculated measured 50 12 13 14 15 16 17 18 65 64 63 Time [hours] Tank top temperature 51 calculated measured 50 12 13 14 15 16 17 18 60 59 58 Time [hours] Regeneration temperature 62 57 Temperature [ C] 61 60 59 58 Temperature [ C] 56 55 54 53 57 52 56 calculated measured 55 12 13 14 15 16 17 18 Time [hours] 51 calculated measured 50 12 13 14 15 16 17 18 Time [hours] Figure 15: Comparison of the predicted temperature with the measured one for the collectors outlet, storage top, storage bottom, and regeneration air Figure 16 compares the measured outlet conditions of the desiccant wheel to those predicted by the model. The profiles of the temperature and humidity ratio are very well predicted by the model during the whole day. For the measured temperature we noticed some peaks et we can count 7 peaks per hour and for each peak in the temperature corresponds a minimum in the outlet humidity of the wheel. Or the angular speed of the wheel is 7 rounds per hour this mean for each revolution of the wheel corresponds a peak. The reason behind this behaviour is a probable anomaly in the desiccant wheel with a sector having more desiccant and yields more dehumidification this mean an increase in the outlet temperature of the wheel. It is evident that the desiccant does not take into account this anomaly. page 44
IEA SHC Task 38 Solar Air Conditioning and Refrigeration Subtask C2-A, November 9, 2009 50 45 Desiccant wheel outlet conditions 0.015 0.014 0.013 Temperature [ C] 40 35 30 0.012 0.011 0.01 0.009 0.008 T 2 calculated 25 T 2 measured 0.007 w 2 calculated 0.006 20 w 2 measured 0.005 12 13 14 15 16 17 18 Time [hours] Humidity ratio [kg.kg -1 ] Figure 16: Comparison of the outlet temperature and outlet humidity ratio of the desiccant wheel for the considered day For the supply temperature, figure 17 shows that the maximum committed error is below 0.5 °C and appears during the increase of the humidific ation rate. Temperature [ C] 25 24 23 22 21 20 19 18 17 16 15 14 13 12 11 10 Supply temperature 12 13 14 15 16 17 18 Time [hours] calculated measured Figure 17: Comparison of the predicted and measured supply temperature of the installation (position 4 on the figure 1) for the considered day All these results proofs that the model of the installation can predict accurately the supply conditions of the solar desiccant installation. In the next section a transient model of the desiccant wheel is presented. page 45
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IEA Solar Heating and Cooling Progr
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IEA Solar Heating and Cooling Progr
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Endbericht Solare Kühlung und Klim
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Task 38 Solar Air-Conditioning and
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IEA SHC Task 38 Solar Air Condition
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3.1 Adsorption Systems Table 1: Ads
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4 Heat Rejection There is a number
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M M IEA SHC Task 38 Solar Air Condi
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M M M IEA SHC Task 38 Solar Air Con
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IEA SHC Task 38 Monitoring Procedur
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Table of tables Table 1 List of ele
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Pompe évaporateur + compteur C3 Dr
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80 70 Temperature (°C) 60 50 40 3
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Power (kW) 20 19 18 17 16 15 14 13
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Power (kW) 20 19 18 17 16 15 14 13
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Country Name/ Company City Applicat
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79 Spain Private House Olivares-Sev
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Questionnaire for Owners of Small-S
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Fragebogen an Besitzer solare Kühl
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Cuestionario para propietarios de i
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Questions to Package Solution Provi
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9. Maintenance o What type of maint
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Grundprinzip Solare Wärme thermisc
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Hintergrund Operating Agent: Hans-M
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- Leistungsvergleich von verfügbar
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Subtask A: Pre-engineered systems f
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Abb. 3: Das Bürogebäude in St. Sc
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Beispiele realisierter großer Syst
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a) b) c) Abb. 9: Installation eines
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Subtask C: Modelling and fundamenta
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Liste der Systeme im Monitoring von
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Liste der Systeme im Monitoring von
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Marletta, L., Evola, G. and Sicurel
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Ellehauge & Kildemoes Vestergade 48
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Tekniker Centro Tecnológico Teknik
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IEA Solar Heating and Cooling Programm - NachhaltigWirtschaften.at

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