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IEA SHC Task 38 Solar Air Conditioning and Refrigeration Subtask C2-A, November 9, 2009 Figure 5. Comparison of simulated and measured generator outlet temperatures. Figure 5 shows that the steady-state agreement between measured and simulated values is reasonably well despite the fact that steady-state accuracy has been incorporated coarsely only. At simulation start, the simulated temperatures diverge slightly from the initial measured state towards a different steady-state. In general, the temperature difference between experiment and simulation is larger after the step which shows that there is a dependency of the model output on the hot water temperature. This can be related to temperaturedependent parameters which have been assumed constant for the simulation, such as evaporation and solution enthalpy, density and specific heat capacity. As steady-state accuracy is not the focus in this paper this deviation shall not be discussed further. Much more important is the fact that the dynamic agreement between measured and simulated output data is very good. Figure 5 shows that the fluctuations of simulated and measured hot water outlet temperature are well synchronized, although there is a slight delay of approximately 10 seconds of measured to simulated values. This has to be put into relation to the 600 seconds or 10 minutes that it takes to reach a steady state in the generator temperatures again. The delay between simulation and experiment can – at least to some extent - be explained with the assumptions of thermal mass for the individual vessels in Table 1 which have not been verified yet. Another reason for the disagreement is the fact that some time delays page 74
IEA SHC Task 38 Solar Air Conditioning and Refrigeration Subtask C2-A, November 9, 2009 existing in reality have not been incorporated into the model. These include the forced circulation of refrigerant in the evaporator by means of a second internal pump. Also, the condensed refrigerant flowing from condenser to evaporator has a time delay which has been neglected. There is no vapour storage in the vessels assumed. The transport delay c 1 has been assumed constant although it changes in proportion to the strong solution mass flow. The transport delay in the cooling water between absorber outlet and condenser inlet due to piping length has also been neglected as well as the change in solution storage on the tube bundles. These time delays have not been included in order to keep the model as simple as possible. The results in Figure 5 are shown here just in order to demonstrate the basic functionality of the model. A sensitivity analysis along with more experimental data is presented in the second part of this paper [7]. Conclusions In this paper a dynamic model for absorption chillers has been presented. It is based on internal energy balances as well as mass balances. Dynamic behaviour is implemented via eight thermal and two mass storage terms as well as by two delay times. The heat transfer has been divided into two parts: one which transfers heat from the external heat carrier to the exchanger material and the second from there on to the refrigerant or solution side, or vice versa. In this way the thermal mass of the vessel could be introduced easily. The agreement between experiment and simulation is very good with deviations of 10s for the generator. The total time to achieve a new steady-state after an input temperature step amounts to approximately 15 minutes. Compared to this, the present dynamic deviations are in the magnitude of approximately 1%. More information about the simulation results, comparison with experiments and sensitivity checks will be presented in the second part of this paper [7]. page 75
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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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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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Questionnaire for Owners of Small-S
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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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