Heat receiver for urban concentrated solar power

Abstract

An urban concentrated solar power for mounting on a roof top is provided. The urban concentrated solar power has a heat receiver has a non-circular duct that distinguishes an insulated area with an insulation layer on the outer surface of the non-circular duct and a non-insulated area. The non-circular duct contains a heat transferring fluid which can reach temperatures of at least 500 degrees Celsius. A parabolic trough with an aperture of below 2 meters concentrates sunlight onto the non-insulated area of the non-circular duct of the heat receiver. The heat receiver can be placed in a glass tube. Due to roof top mounting the electricity can be generated in proximity of the user and as a result decrease net congestion. The low-cost heat receiver design will make electricity generated by urban CSP competitive with electricity from fossil fuel plants and PV combined with lithium-ion battery storage.

Claims

1. An urban concentrated solar power for mounting on a roof top, comprising: (a) a heat receiver having a non-circular duct distinguishing an insulated area with an insulation layer on the outer surface of the non-circular duct and a non-insulated area, wherein the non-circular duct contains a heat transferring fluid, wherein the non-circular duct has an irradiated duct area versus a total duct area of 5% to 30%, wherein the total duct area is defined as a perimeter of the non-circular duct multiplied by a length of the non-circular duct; (b) a glass tube holding a vacuum, wherein the heat receiver is placed within the vacuum of the glass tube; (c) a vacuum pump in connection with the glass tube, wherein the vacuum pump draws or redraws the vacuum within the glass tube; (d) a coupling with an intermediate O-ring holding an end of the glass tube; (e) a heat shield near the intermediate O-ring and circumferentially positioned around the heat receiver and within the glass tube wherein the heat shield protects the intermediate O-ring from a temperature of at least 400 degrees Celsius; and (f) a parabolic trough to concentrate sunlight onto the non-insulated area of the non-circular duct of the heat receiver.

2. The urban concentrated solar power as set forth in claim 1, wherein the parabolic trough has an aperture of below 2 meters.

3. The urban concentrated solar power as set forth in claim 1, wherein the heat transferring fluid reaches temperatures of at least 500 degrees Celsius.

4. The urban concentrated solar power as set forth in claim 1, wherein the non-circular duct comprises a square shape wherein one flat side of the square shape is the non-insulated area.

5. The urban concentrated solar power as set forth in claim 1, wherein the non-circular duct comprises a square shape wherein one corner area of the square shape is the non-insulated area.

6. The urban concentrated solar power as set forth in claim 1, wherein the non-circular duct has a circular portion with a triangular shape as the non-insulated area.

7. The urban concentrated solar power as set forth in claim 1, wherein the non-circular duct has a circular portion or an oval portion with a flat side as the non-insulated area.

8. The urban concentrated solar power as set forth in claim 1, wherein the non-circular duct comprises a rectangular shape where one flat side of the rectangular shape is the non-insulated area.

9. The urban concentrated solar power as set forth in claim 1, wherein the non-circular duct has an inner hydraulic diameter of at least 15 mm.

10. The urban concentrated solar power as set forth in claim 1, wherein the heat shield protects the intermediate O-ring from a temperature of at least 500 degrees Celsius.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) FIG. 1 shows a cross section of a parabolic trough arrangement according to the current state of the art.

(2) FIGS. 2A-B show a heat receiver according to the current state of the art (option 1).

(3) FIGS. 3A-B show according to exemplary embodiments of the invention a heat receiver with a rectangular duct where one area around one corner is where the irradiation is concentrated (option 2).

(4) FIGS. 4A-C show according to exemplary embodiments of the invention a heat receiver with a circular duct with a triangle at the bottom where irradiation is concentrated (option 3).

(5) FIGS. 5A-C show according to exemplary embodiments of the invention a heat receiver with a rectangular duct where one flat area of the duct is where the irradiation is concentrated (option 4).

(6) FIG. 6 shows according to exemplary embodiments of the invention cross sections of a receiver arrangement.

(7) FIGS. 7A-C show according to exemplary embodiments of the invention different heat shield configurations.

(8) FIG. 8 shows the maximum concentration ratios of sunlight on a receiver of different receiver shapes. The principle is the same as a magnifying glass, the smaller the focal point, i.e. the higher the concentration ratio, the easier it is to make a fire, i.e.: obtain high molten salt temperatures.

DETAILED DESCRIPTION

(9) FIG. 1 shows a cross section of a parabolic trough arrangement according to the current state of the art. Sunlight 102 enters the aperture of the parabolic trough 101, which concentrates the sunlight at angle φ.sub.R, to the bottom of the duct 104 with internal hydraulic diameter D.sub.H, containing the heat transfer fluid (HTF). The insulation 103 on the top part of the tube prevents excessive heat losses. FIG. 2A shows option 1 which demonstrates according to the current state of the art a heat receiver where the outer diameter of the duct 104 is 1.4 cm and the hydraulic diameter (D.sub.H) 10 mm. At a reflector aperture of 1.35 m the concentration ratio is (1350 mm/0.5×π×14 mm=) 61. Another version of the state of the art is where the duct 105 is concentrically encapsulated in a glass cylinder 106 (FIG. 2B).

(10) FIG. 3A shows option 2, where the rectangular duct 107 pertains an embodiment of the invention, has an insulation 108 and focuses the solar irradiation on the heat receiver. However, in option 2 the duct has a larger hydraulic diameter (DO to lower the pressure drop of the HTF flow through the rectangular duct. The angles of this rectangular duct can have round corners and although the rectangular is a drawn as a square it does not have to be a square as long as the irradiated (non-insulated) bottom is a triangle. The entire heat receiver can also be placed in a glass tube 110 (FIG. 3B) The insulation 108 can also have an additional outer layer, like aluminum foil, to minimize radiation.

(11) FIG. 4A shows option 3. The duct 113 is circular (or oval), but has a triangle at the bottom where the irradiation is concentrated on. At the non-irradiated part an insulation 114 is placed and both the duct 113 and the insulation 114 can be placed in a concentric glass tube 115. Another version of this option is duct 117, 117B where the triangle is flattened at the bottom (FIG. 4B or FIG. 4C). The insulation 114 can also have an additional outer layer, like aluminum foil, to minimize radiation.

(12) FIG. 5A shows option 4 and is another version of the invention. The rectangular duct 119 has a flat bottom where the irradiation is concentrated on. At the non-irradiated part an insulation 120 can be added, like fiber paper (FIG. 5B) to minimize radiation from the insulated surface. This insulating layer 120 can also be covered with an additional layer, like aluminum foil, to minimize radiation. A third alternative of option 4 is heat shield 121 covering the rectangular duct to minimize radiation (FIG. 5C). All alternatives of option 4 can be concentrically encapsulated in a glass cylinder 118.

(13) The consequences in terms of power and temperature between option 1, option 2, option 3 and option 4 are shown in the TABLE 1 for a concentrated solar power plant with a trough of 1.35 meters aperture width, 8000 meters length, molten salt mass flow of 2.5 kg/s, ambient wind velocity of 3.6 m/s and a direct normal irradiance of 950 W/m.sup.2 to generate 1000 kW of electricity. Embodiments of the invention enable the generation of high temperatures of 500 degrees Celsius HTF or higher with parabolic troughs at small scale below 2 meters aperture to be placed at roof tops. Option 2 and 4 have a maximum HTF temperature of 772 degrees Celsius at the lowest pressure drop. Hence, the overall CSP system efficiency of these options will be the highest.

(14) The power loss due to the pressure drop is calculated by equation 1:
P.sub.loss,pressure drop=ΔpV′  Equation 1

(15) Where Δp is the pressure drop given by the Darcy-Weissbach equation and V′ is the volume flow. Radiation is the dominant heat flux from the duct to the inner diameter of the glass at an annular pressure of 1 mbar in the glass cylinder.

(16) TABLE-US-00001 TABLE 1 Power losses for five different type of heat receivers and their related options at maximum concentration ratios (FIG. 8), reflectors of 1.35 m aperture to generate 1000 kW, emissivity of absorptive painting of 0.50 (@T = 550 degrees Celsius) on irradiated part and polished aluminum of 0.15 (@T = 550 degrees Celsius) on insulated part of the duct. State of the art: Invention: Invention: Invention: Option 1 Option 2 Option 3 Option 4 FIG. 2B 2A 3B 4A 5A Maximum Solar  69  83 108 108 108 concentration factor C.sub.max Hydraulic inner  2  9  31  31  31 diameter D.sub.H (wall thickness of 2 mm) [mm] Irradiated duct area/  100%   39%    9%    9%    9% total duct area T.sub.HTF, max [° C.] 896 794 772 675 772 P.sub.loss, pressure drop [kW] 9070000   9529   19  31  19 P.sub.loss/P.sub.generated [%] 907000%    953%    2%    3%    2%

(17) For a CSP plant with parabolic troughs of around 1.35 meters aperture width—and other apertures below 2.0 meter—it is essential that the losses due to the pumping of the HTF through the heat receiver are kept to a minimum and in the range of 0-5% of the generated power. Only options 2, 3 and 4 are capable of generating high temperatures HTF at small aperture troughs at a positive overall CSP plant efficiency. The pressure drop of option 1 can be decreased to 3% of generated power by increasing the hydraulic inner diameter also to 31 mm. However, this will decrease T.sub.HTF,max to 499 degrees Celsius. It will require an infinite time to heat the molten salt to 499 degrees Celsius and it is impossible to reach the required 550 degrees Celsius.

(18) In a serial connection of 8000 m of heat receivers a minimal internal hydraulic diameter of around 30 mm is required to ensure the power to overcome the pressure drop is at ˜2% of generated power. At a parallel connection of 10 serial connections of 800 m heat receivers, the minimal internal hydraulic diameter is 8 mm to maximize the pressure drop at 2%. So, option 1 would enable a high temperature HTF at an acceptable pressure drop at a parallel arrangement of heat receivers. However, the second moment of inertia of option 1 at 8 mm internal hydraulic diameter is around 4 times smaller as options 2, 3 and 4. As a consequence the metal duct will deform and the sunlight concentrated from the parabolic trough 101 of FIG. 1 will (partially) miss the duct. To ensure a rigid duct and a low pressure drop, the internal hydraulic diameter should be 15 mm or more.

(19) Options described in FIGS. 3A, 3B and 4A have an irradiated point at a significant higher temperature as the upper insulated part of the duct. Due to this temperature inhomogeneity it could be challenging to minimize deformation of the duct. However, this effect could be minimized through an optimized heat transfer, by a high conductance duct material, thin duct, a turbulent molten salt flow, or a combination thereof.

(20) FIG. 6 shows a cross section of a receiver arrangement (options 2 and 4), where 610 indicates the steel receiver duct including the conversion at the end from a rectangular duct to a circular pipe. 620 is the glass circular pipe, 630 indicates the gasket to minimize heat losses and ensure vacuum sealing, 640 is the coupling to fixate the receiver to a ground structure or the reflector, 650 is a rubber O-ring between the glass 620 and coupling 640. At the end coupling 660, the O-ring 650 has another function, namely vacuum sealing. End coupling 660 is mounted through bolts 670 on the duct 610 end and can move in longitudinal direction, along the glass pipe 620, to capture thermal expansion of the duct. As a result, internal convection can be minimized without glass-metal welding. It is noted that glass-metal weldings are expensive solutions for heat receivers.

(21) To minimize heat losses through convection a vacuum is created in the glass annulus. In the art, a glass-metal welding ensures a vacuum throughout the lifetime of the receiver. It also incorporates a bellow that captures different thermal expansion of the glass and metal. Inventor suggests an active vacuum that ensures a vacuum from sunrise to sunset. At least one vacuum connection is mounted on the end coupling 660 for the connection to a vacuum pump. In FIG. 6 two connections are shown: one for a vacuum pump and the other one for a pressure gauge. Before the start of each day the vacuum pump draws the vacuum in the glass annulus.

(22) To protect the O-rings 650 from the duct 610 high temperatures (550 degrees Celsius), one or multiple heat shields can be added in different shapes. In FIGS. 7A-C, three options of a heat shield configuration are shown through a cross section of end coupling 660. Through these heat shields a cooling of 400 degrees Celsius can be achieved over 2 cm distance to prevent the melting of the rubber O-ring 650.

(23) FIGS. 7A-C shows three embodiments of a heat shield. In option 1, one circular heat shield 720 is added to reduce radiation, and in option 2 another circular heat shield 730 is added. Option 3 is another shape of the heat shield and as an example a ribbed heat shield 710 is illustrated.

(24) FIG. 8 shows three different duct shapes, irradiated on four methods and further shows the maximum concentration ratio at given angles φ.sub.R. The first example is a fully irradiated 830 cylinder 810, which has a maximum concentration ratio of 69 at an angle of attack φ.sub.R (FIG. 1) of 90 degrees and a maximum heat flux of 69 kW/m.sup.2. The second example is a partially irradiated 840 cylinder 810, which has a maximum concentration ratio of 83 at an angle of attack of 70 degrees and a maximum heat flux of 83 kW/m.sup.2. An example of this derivation is given in Equation 2:

(25) $\begin{array}{cc}{C}_g=\frac{\sin \left({\phi }_R\right)\cos \left(\frac{{\phi }_R}{2}\right)}{2\sin \left({\theta }_S\right)}& \mathrm{Equation}2\end{array}$

(26) Where θ.sub.s is half the angular size of the sun at 0.26 degrees. Deriving C.sub.g to φ.sub.R will provide the maximal concentration ratio C.sub.g=83 at angle of attack φ.sub.R of 70 degrees through Equation 3:

(27) $\begin{array}{cc}\frac{{\mathrm{dC}}_g}{d{\phi }_R}=\frac{d}{d{\phi }_R}\left(\frac{\sin \left({\phi }_R\right)\cos \left(\frac{{\phi }_R}{2}\right)}{2\sin \left({\theta }_S\right)}\right)=0& \mathrm{Equation}3\end{array}$

(28) The third example is a square duct 820, which is irradiated on the bottom 850 and has a maximum solar concentration ratio of 108 at an angle of attack of 45 degrees and a maximum heat flux of 108 kW/m.sup.2. The fourth example is a square duct 820 which is irradiated at one corner 860 and has a maximum solar concentration ratio of 108 at an angle of attack at 90 degrees and a maximum heat flux of 108 kW/m.sup.2.