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IEA SHC Task 38 Solar Air Conditioning and Refrigeration Subtask A Report A-D3b, Date: December 2010 A few systems show values below 3 which means that the system probably consumes more electricity than a conventional compression chiller would. A general conclusion is that in most systems the electricity consumption of the external components of the cold production (pumps, fans) has not been optimized and is therefore too high. In the best system in Figure 3 (Garching) the pump in the generator loop has been exchanged against a more energy efficient one. In addition it is planned to replace the fan of the dry cooler in the near future which would increase the electrical COP even further. Another topic is the part load operation of the system. If a system is operated a lot in part load but the external pumps are still operated at full speed, this will lead to low electrical COPs. Optimized control strategies for this operation scenario are mandatory to ensure primary energy savings of the system. 3.4 Total electrical COP of the Solar Cooling System As a next step, the total electrical COP of the system can be calculated. This includes in addition to the electrical consumers mentioned before, the electricity consumption of the pumps in the solar circuit(s) and the electricity consumption of the auxiliary heater and the associated pumps if applicable. Total electrical COP, - 8 7 6 5 4 3 2 1 0 Jun Jul Aug Zaragoza 2008 Maclas Perpignan 2009 Graz 09/10 Sattledt 2007 Chambéry 09/10 Butzbach 2009 Garching 2009 Gleisdorf 2010 Freiburg 09/10 Figure 4: Total electrical COP of 10 solar cooling systems Figure 4 compares the total electrical COP of 10 systems only for the summer months. The value for the system in Gröbming is not shown because the system was also used for DHW preparation and space heating. Therefore, the value is significantly higher but not comparable. For the other 10 systems the trend is the same as described in the previous section. But the total electrical COPs of the systems are obviously somewhat lower than for the cold production itself, but the more critical factor seems to be the electricity consumption of the pumps in the chiller circuits and the heat rejection system. These are the components that need to be optimized in terms of component selection and control strategies. 3.5 Fractional Primary Energy Savings Now, let’s take a look at the probably most important monitoring result of a solar heating and cooling system: The primary energy saved by the system. For this purpose, the primary energy ratio was calculated for both the monitored solar heating and cooling system and for a conventional reference system delivering the same amount of heating, cooling and domestic hot water. The following assumptions were taken for the conventional reference system: Space heating is done by a fossil fuel boiler without storage tank. The primary energy ratio for space heating is calculated as follows: page 50
IEA SHC Task 38 Solar Air Conditioning and Refrigeration Subtask A Report A-D3b, Date: December 2010 PER with QSH 0.02Q 1 1 0.02 0.95 0.9 0.4 ref , space _ heating QSH SH boiler fossil boiler Mean annual efficiency of fossil fuel boiler: 0.95 elec 81.99 % fossil Primary energy factor for fossil fuel: 0.9 kWh final /kWh PE elec Annual electricity generation efficiency: 0.4 kWh el /kWh PE The electricity consumption of the fossil fuel boiler was assumed to be 2% of the generated heat of the boiler. All these assumption lead to a reference primary energy ratio for space heating of 81.99%. The numbers listed above are mean European values and have been chosen in order to compare different systems. Local values may be used in order to evaluate the saving in a specific location. Domestic hot water preparation is done using the same fossil fuel boiler than for space heating but assuming a storage tank containing 75% of the average daily hot water consumption in the monitored system. Average heat losses of such a tank were then added to the measured heat consumed for domestic hot water. Cooling is done by a conventional compression chiller. The primary energy ratio for cooling is calculated as follows: PER With Q 1 1 2.80.4 cold ref , cooling Qcold SPF ref elec 112 % SPF ref Reference seasonal performance factor: 2.8 This leads to a reference primary energy ratio for cooling of 112%. This reference primary energy consumption is then compared with the measured primary energy consumption of the system according to the equations below: f f sav, shc 1 sav, shc 1 Qboiler QRES fossilboiler RESRES Qboiler , ref E PER ref PER fossil boiler , ref el, ref Some monitored systems use fossil backup systems. In that case, the same primary energy factors and efficiencies as for the reference system were used. Also for the electricity consumption the same electricity conversion efficiency was used. For other backup systems (in the equation called renewable energy sources Q RES ), individual primary energy factors and efficiencies were used. The primary energy factor RES here is defined as the “non renewable primary energy factor”: a) Wood pellets (only Gröbming): RES =0.9, RES =10 kWh fuel /kWh PE b) District heating system city of Graz: RES =1, RES =0.96 kWh heat /kWh PE elec E Q el elec SPF Qcooling , ref SPF page 51 ref cooling , missed elec elec
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Endbericht Solare Kühlung und Klim
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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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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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Questionnaire for Owners of Small-S
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Grundprinzip Solare Wärme thermisc
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- Leistungsvergleich von verfügbar
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Subtask A: Pre-engineered systems f
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Subtask C: Modelling and fundamenta
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Liste der Systeme im Monitoring von
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Tekniker Centro Tecnológico Teknik
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