Date of download: 11/7/2017 Copyright © ASME. All rights reserved. From: Experimental and Numerical Heat Transfer Analysis of an Air-Based Cavity-Receiver for Solar Trough Concentrators J. Sol. Energy Eng. 2012;134(2):021002-021002-8. doi:10.1115/1.4005447 Figure Legend: Convective heat transfer at surfaces 2 and 3, Q·convection,2, Q·convection,3, as functions of surface temperatures T2 and T3, for a downward-facing receiver aperture, obtained by CFD (+), by the empirical correlations (solid lines), and by applying Kuehn-Goldstein Nu-correlation [] for convective heat transfer between nested cylinders (dashed lines)

Date of download: 11/7/2017 Copyright © ASME. All rights reserved. From: Experimental and Numerical Heat Transfer Analysis of an Air-Based Cavity-Receiver for Solar Trough Concentrators J. Sol. Energy Eng. 2012;134(2):021002-021002-8. doi:10.1115/1.4005447 Figure Legend: Experimental test facility in Biasca, Switzerland

Date of download: 11/7/2017 Copyright © ASME. All rights reserved. From: Experimental and Numerical Heat Transfer Analysis of an Air-Based Cavity-Receiver for Solar Trough Concentrators J. Sol. Energy Eng. 2012;134(2):021002-021002-8. doi:10.1115/1.4005447 Figure Legend: Measured and simulated pressure drops in the HTF flow between receiver inlet and outlet as a function of the HTF mass flow rate

Date of download: 11/7/2017 Copyright © ASME. All rights reserved. From: Experimental and Numerical Heat Transfer Analysis of an Air-Based Cavity-Receiver for Solar Trough Concentrators J. Sol. Energy Eng. 2012;134(2):021002-021002-8. doi:10.1115/1.4005447 Figure Legend: Thermal heat losses from the receiver for 13 off-sun test runs

Date of download: 11/7/2017 Copyright © ASME. All rights reserved. From: Experimental and Numerical Heat Transfer Analysis of an Air-Based Cavity-Receiver for Solar Trough Concentrators J. Sol. Energy Eng. 2012;134(2):021002-021002-8. doi:10.1115/1.4005447 Figure Legend: Efficiency of the solar receiver prototype as a function of the HTF outlet temperature, for the spring equinox (a) and the summer solstice (b), at 8:00, 10:00, and 12:00 solar time; HTF mass flow rate is varied from 0.1 to 1 kg/s; HTF inlet temperature is 120 °C; for comparison, the efficiency of the Schott PTR70 (2008) receiver at solar noon is shown

Date of download: 11/7/2017 Copyright © ASME. All rights reserved. From: Experimental and Numerical Heat Transfer Analysis of an Air-Based Cavity-Receiver for Solar Trough Concentrators J. Sol. Energy Eng. 2012;134(2):021002-021002-8. doi:10.1115/1.4005447 Figure Legend: Pressure drop ΔpHTF across the solar receiver prototype and corresponding isentropic HTF pumping power requirement W·pump,s for the spring equinox (a) and the summer solstice (b) at solar noon, as functions of the HTF mass flow rate

Date of download: 11/7/2017 Copyright © ASME. All rights reserved. From: Experimental and Numerical Heat Transfer Analysis of an Air-Based Cavity-Receiver for Solar Trough Concentrators J. Sol. Energy Eng. 2012;134(2):021002-021002-8. doi:10.1115/1.4005447 Figure Legend: Energy breakdown of heat losses by the receiver (gray areas) and heat gain by the HTF (white area), and the associated HTF pumping power requirement (black curve), normalized by the solar power incident from the primary concentrator, Q·solar, as functions of the HTF outlet temperature THTF,out in the range 250–450 °C for the spring equinox (a) and the summer solstice (b) at solar noon; THTF,in=120 °C