Page 1 Analysis of the Thermal Losses in the Innovative Technology, the Compact Fresnel Linear Reflector with the trapezoidal absorbers. Capstone Research Course (E 194) Name: Fang-Ming Lin Department of Engineering Science Major: Energy Engineering Course supervisor: Van Carey Department of Mechanical Engineering Abstract Concentrated Solar Power System (CSP) is the most proven technology for the solar energy technology. The compact Fresnel Linear Reflector takes the concept of trough design and enhance the efficiency and reduce the cost with a set of rows, flattening the parabolic reflectors into flat mirrors. With this change, the mirrors are able to avoid the thermal oil used in traditional receiver technology, the concentrated sun light is then used directly to heat water, produce the superheated steam and improve the thermal efficiency. Since the efficiency for the solar power system is extremely important, it would be analyzed through the heat loss happens at the light absorber, with the adjusting cavity angles cavity depth and the insulation thickness, heat loss would be analyzed for obtaining the most efficient configuration for the technology of CSP.
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Absorber Technology for Concentrated Solar Power System
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Page 1
Analysis of the Thermal Losses in the Innovative
Technology, the Compact Fresnel Linear Reflector with the
trapezoidal absorbers.
Capstone Research Course (E 194)
Name: Fang-Ming Lin
Department of Engineering Science
Major: Energy Engineering
Course supervisor: Van Carey
Department of Mechanical Engineering
Abstract
Concentrated Solar Power System (CSP) is the most proven technology for the solar energy
technology. The compact Fresnel Linear Reflector takes the concept of trough design and
enhance the efficiency and reduce the cost with a set of rows, flattening the parabolic
reflectors into flat mirrors. With this change, the mirrors are able to avoid the thermal oil used
in traditional receiver technology, the concentrated sun light is then used directly to heat
water, produce the superheated steam and improve the thermal efficiency. Since the efficiency
for the solar power system is extremely important, it would be analyzed through the heat loss
happens at the light absorber, with the adjusting cavity angles cavity depth and the insulation
thickness, heat loss would be analyzed for obtaining the most efficient configuration for the
technology of CSP.
Page 2
1. INTRODUCTION
1.1 The Compact Fresnel Linear Reflector
Concentrated solar power (CSP) is one of the most important candidate for providing the
majority of the energy source because of its cost-effective electricity technologies and its
potential for further technology improvements. The Compact Fresnel Linear Reflector is the
innovative design which is suitable for the large-scale solar thermal energy collection but also
efficiently uses the available power plant area, further reducing the cost with the low-cost
materials([3] Edkins et al). In traditional Fresnel Linear Reflector, there is only one absorber,
reflectors concentrate the sun light all to the only one linear system. For this design, it contains
many optical losses, especially the shading loss, with its geometric configuration that produces
the limits. With the Compact Fresnel Linear Reflector, its design system contains at least two
absorbers, which absorbs reflected sun light from a series of mirror that are put into different
configuration, the mirrors placed on the outside of the two absorbers maintain the same
configuration as the traditional Fresnel Linear Reflector, but for the mirrors sit between two
absorbers, each mirror faces to the opposite direction as to the adjacent one so that it reduces
the shading loss and enhance the optical efficiency ([10] Pye, John D et al).
1.2 Direct Steam Generation
For most of the innovative design of the Compact Fresnel Linear Reflector, it uses the
technology of direct steam generation to do the heat conversion. The basic idea of the Direct
Steam Generation is heating the water directly and generating steam from it without going
through from various energy mechanisms and transitions. Unlike the most common chosen
heat transfer fluids (HTF), the synthetic thermal oil or the molten salt; the direct steam
generation uses water as the heat transfer fluid and directly generates the steam with a more
simplified model by eliminating the complex heat exchanger component. With the usage of the
synthetic thermal oil or the molten salt, the maximum temperature the system can reach is
around 400 Celsius. With the application of direct steam generation, it is able to exceed the
limited temperature and reaches up to 550 Celsius ([1] Alguacil, M. et al). With this, the direct
steam generation enhances the efficiency by increasing the steam temperature, and avoids the
environmental risk that the traditional HTF can have.
2. DATA COLLECTION
2.1 Heat Transfer and Heat Loss on the Receiver
For the solar power collectors, each collector contains a concentrator and a receiver.
Two main types of concentrators are the nonimaging concentrator or the focusing
concentrator, and the two main types of receivers are the refracting lens type or the reflecting
mirror type. Therefore the performance for each solar collector is determined by two
parameter, the concentration and the acceptance angle ([14] Vieira, 2005).
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In order to analyze the heat transfer and heat loss, the design of the receiver is really
important, different factors will result in different effects on each design. The choice of the type
of receiver the concentrated power system was made of would determine the analysis for the
heat loss. There are two types of receiver designs, which later receiver designs deviate from
them but still sustain those fundamental concepts from the formers. These two types are the
Heat Loss from Linear, Omnidirectional Receiver and the Heat Loss from Cavity Receiver.
Furthermore, sizing the receiver will also alter different heat loss for the receiver, finding the
optimal receiver size is crucial to the design of the receiver. ([13] Stine, William B. et al). The
fundamental calculation is conducted by including the heat loss through convection and the
ℎ𝑔 2.6 W/m2 ∙ 𝐾 Convection coefficient outside of the cavity
window (glass side)
ℎ𝑤 0.5 W/m2 ∙ 𝐾 External heat loss coefficient outside of cavity
side walls
L 60 m Length of the absorber
W 160 mm Width of the receiver
T 20 mm The thickness of the wall
𝑘𝑖 0.04 W/m ∙ 𝐾 Insulation thermal conductivity
Varied Parameter
Definition
D 50,100,150 (mm) Depth of the absorber
ℎ𝑤 kair
𝐷/2 Convection coefficient inside of the cavity
t 0, 20, 50 mm The thickness of the insulation
𝜃 30,45,60 (°) Inclination of the wall
𝑇𝑎 100,200,300,400 (℃) Temperature enclosed in the absorber
𝑇𝑔 270,280,290,300,310 (K) Temperature at the outside surface of the
absorber
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4.2 Heat Loss calculated data for seven different combinations
Heat Loss with D=0.05m, θ=45⁰, t=0.02m
270 280 290 300 310
373 1655.399 1514.63 1372.945 1230.337 1086.801
473 3203.453 3062.641 2920.872 2778.145 2634.462
573 4841.027 4699.569 4557.13 4413.717 4269.337
673 6556.416 6413.532 6269.673 6124.85 5979.076 Heat Loss with D=0.1m, θ=45⁰, t=0.02m
270 280 290 300 310
373 1351.658 1235.93 1119.734 1003.067 885.9264
473 2580.439 2464.632 2348.34 2231.565 2114.309
573 3853.429 3737.244 3620.567 3503.404 3385.757
673 5164.483 5047.544 4930.12 4812.219 4693.844 Heat Loss with D=0.15m, θ=45⁰, t=0.02m
270 280 290 300 310
373 1224.433 1118.656 1012.555 906.1277 799.3736
473 2331.65 2225.807 2119.629 2013.118 1906.275
573 3469.148 3363.032 3256.577 3149.787 3042.665
673 4632.588 4525.937 4418.953 4311.641 4204.004 Heat Loss with D=0.1m, θ=30⁰, t=0.02m
270 280 290 300 310
373 1789.983 1632.542 1474.455 1315.717 1156.325
473 3462.927 3305.417 3147.235 2988.382 2828.859
573 5197.915 5039.911 4881.222 4721.854 4561.811
673 6986.456 6827.421 6667.709 6507.328 6346.286 Heat Loss with D=0.1m, θ=60⁰, t=0.02m
270 280 290 300 310
373 1105.324 1013.056 920.4156 827.4016 734.0129
473 2084.903 1992.555 1899.825 1806.713 1713.221
573 3099.189 3006.536 2913.497 2820.074 2726.27
673 4143.413 4050.168 3956.541 3862.538 3768.163 Heat Loss with D=0.1m, θ=45⁰, t=0.0m
270 280 290 300 310
373 1938.686 1796.096 1652.748 1508.653 1363.826
473 3483.757 3340.231 3196.002 3051.08 2905.479
573 5079.264 4934.585 4789.248 4643.268 4496.654
673 6715.535 6569.45 6422.756 6275.464 6127.587 Heat Loss with D=0.1m, θ=45⁰, t=0.05m
270 280 290 300 310
373 1212.22 1103.185 993.7068 883.7812 773.4053
473 2370.017 2260.98 2151.478 2041.51 1931.077
573 3571.551 3462.204 3352.379 3242.08 3131.311
673 4810.958 4700.912 4590.391 4479.402 4367.95
Page 15
References
[1] Alguacil, M., C. Prieto, A. Rodriguez, and J. Lohr. "Direct Steam Generation in Parabolic
through Collectors." (2013): n. pag. ScienceDirect. Web. 24 Sept. 2014. [2] AutoCAD. Sausalito, CA: Autodesk, 2013. Computer software.
[3] Edkins, Max, Harald Winkler, and Andrew Marquard. "Large-Scale Rollout of Concentrating
Solar Power in South Africa." Climate Strategies, Sept. 2009. Web. 1 Oct. 2014. [4] Hydro Solar Solutions. "Solar Design Manual." (n.d.): n. pag. Web. 3 Dec. 2014. [5] Incropera, Frank P. Principles of Heat and Mass Transfer. Hoboken, NJ: Wiley, 2013. Print.
[6] Jance M.J., Morrison G.L and Behnia M. (2000) “Natural Convection and Radiation within
an Enclosed Inverted Absorber Cavity”, Proceedings of ANZSES Annual Conference – From
Fossils to Photons, Brisbane, pp563-569. [7] Lai, Yanhua, Tao Wu, Shuping Che, Zhen Dong, and Mingxin Lyu. "Thermal Performance
Prediction of a Trapezoidal Cavity Absorber for a Linear Fresnel Reflector." Advances in
Mechanical Engineering 2013 (2013): 1-7. Web. 28 Nov. 2014. [8] Lievre, Peter Le. Multi-tube Solar Collector Structure. Areva Solar Pty Limited, assignee.
Patent PCT/AU2005/000208. 17 Feb. 2005. Print. [9] Microsoft Excel. Redmond, WA: Microsoft Corp., 2013. Computer software. [10] Pye, John D., Graham L. Morrison, and Masud Behnia. "Transient Modeling of Cavity
Receiver Heat Transfer for the Compact Linear Fresnel Reflector." (2003): n. pag. Web. 2
Oct. 2014. [11] Pye, John D., Graham L. Morrison, Masud Behnia, and David R. Mills. "Modelling of
Cavity Receiver Heat Transfer for the Compact Linear Fresnel Reflector." (2003): n. pag.