US20120291772A1 - Solar heat receiver - Google Patents

Solar heat receiver Download PDF

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Publication number
US20120291772A1
US20120291772A1 US13/575,982 US201113575982A US2012291772A1 US 20120291772 A1 US20120291772 A1 US 20120291772A1 US 201113575982 A US201113575982 A US 201113575982A US 2012291772 A1 US2012291772 A1 US 2012291772A1
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United States
Prior art keywords
heat
receiving pipe
casing
receiving
opening
Prior art date
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Abandoned
Application number
US13/575,982
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English (en)
Inventor
Kenji Atarashiya
Shigenari Horie
Keiji Mizuta
Manabu Maeda
Kazuta KOBAYASHI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Assigned to MITSUBISHI HEAVY INDUSTRIES, LTD. reassignment MITSUBISHI HEAVY INDUSTRIES, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ATARASHIYA, KENJI, HORIE, SHIGENARI, KOBAYASHI, KAZUTA, MAEDA, MANABU, MIZUTA, KEIJI
Publication of US20120291772A1 publication Critical patent/US20120291772A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S20/00—Solar heat collectors specially adapted for particular uses or environments
    • F24S20/20—Solar heat collectors for receiving concentrated solar energy, e.g. receivers for solar power plants
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S10/00—Solar heat collectors using working fluids
    • F24S10/70—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits
    • F24S10/74—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits the tubular conduits are not fixed to heat absorbing plates and are not touching each other
    • F24S10/748—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits the tubular conduits are not fixed to heat absorbing plates and are not touching each other the conduits being otherwise bent, e.g. zig-zag
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S80/00—Details, accessories or component parts of solar heat collectors not provided for in groups F24S10/00-F24S70/00
    • F24S80/40—Casings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S60/00—Arrangements for storing heat collected by solar heat collectors
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/40—Solar thermal energy, e.g. solar towers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/40—Solar thermal energy, e.g. solar towers
    • Y02E10/44—Heat exchange systems

Definitions

  • the present invention relates to a solar heat receiver for increasing a temperature of a fluid medium that drives a turbine of a solar heat power generator.
  • the light condensation and the heat collection are performed by a combination of a light condenser using a mirror and a heat receiver.
  • a combination method of the light condenser and the heat receiver generally, there are two kinds of methods including a trough light condensation method and a tower light condensation method.
  • the trough light condensation method is a method in which solar light is reflected by a semi-cylindrical mirror (a trough), light and heat are collected in a pipe passing through a center of the cylinder, and the temperature of a thermal medium passing in the pipe is increased.
  • a trough semi-cylindrical mirror
  • the direction of the mirror is changed so as to track the solar light, but since the control of the mirror is one-axis control, it is difficult to expect a high temperature rise of the thermal medium.
  • the tower light condensation method is a method in which a light condensation heat receiver is arranged on a tower section (a support section) erected from the ground, a plurality of focusing reflected light control mirrors called a heliostat (a solar light condensation system) are arranged so as to surround the tower section, and the solar light reflected in the heliostat is guided to the light condensation heat receiver to perform light condensation and heat collection.
  • a power generator a tower light condenser
  • the temperature of a fluid is raised by causing the fluid to flow through a plurality of heat-receiving pipes arranged on an inner surface of a cylindrical insulating container, irradiating the surface of the heat-receiving pipe with sunlight, and inputting heat.
  • a difference in temperature is increased between a front surface of the heat-receiving pipe on which sunlight is directly incident and a back surface facing a wall side.
  • the mirrors are arranged to be axially symmetrical, a heat load near an entrance of the heat-receiving pipe is increased by the area effect of the mirrors when the light is condensed and the temperature is increased.
  • the temperature difference is generated between the front surface and the back surface of the heat-receiving pipe due to cycles of day and night, influence of clouds or a fluctuation in an irradiated amount of sunlight.
  • thermal fatigue is easily generated particularly in the heat-receiving pipe near the entrance having a high temperature and a large temperature difference, durability of the heat-receiving pipe is required, and there is thus room for improvement at this point.
  • the present invention has been achieved in view of the above circumstances, and it is an object of the present invention to provide a solar heat receiver that is able to improve a life strength of the heat-receiving pipe by reducing a temperature difference between front and back surfaces (a front portion and a back portion in an incident direction of sunlight) of the heat-receiving pipe.
  • a solar heat receiver includes a casing having an opening on which sunlight is incident, and a plurality of heat-receiving pipes which are arranged in the casing in a circumferential direction of the casing and through which a heat medium is circulated.
  • the heat-receiving pipes are configured so that portions having high heat flux on the opening side are extended to a radially outer position of the casing and expanded sections constituted by a plurality of heat-receiving pipes and having an expanded pitch circle diameter are formed.
  • the solar heat receiver according to the present invention is normally used in tower type solar heat power generation.
  • the solar heat receiver according to the present invention includes a casing having an opening on which sunlight is incident, and a plurality of heat-receiving pipes that are vertically arranged inside the casing and raise the temperature of the heat medium flowing therein by the irradiation of the sunlight.
  • the plurality of heat-receiving pipes are arranged so as to be spaced from each other and to extend in one direction. Centers of the heat-receiving pipes are arranged on the same circumference.
  • the plurality of heat-receiving pipes may be bent outward in a radial direction in a portion near the opening of the casing.
  • a circle passing through the centers of the plurality of heat-receiving pipes is configured so that a diameter in a region near the opening is expanded compared to a diameter in a region separated from the opening.
  • the pitch circle in the present invention is a circle which intersects center axes of the plurality of heat-receiving pipes through the centers of the heat-receiving pipes. That is, the plurality of heat-receiving pipes are arranged at a predetermined pitch (a space), and the centers thereof are arranged on the circumference of the pitch circle.
  • the present invention by expanding the diameter of the pitch circle in a portion of the heat-receiving pipe having high heat flux, surface areas of the heat-receiving pipe and a heat insulating material are increased in that portion, and thus it is possible to reduce a heat input quantity per unit area to the heat-receiving pipe. Moreover, the reduced amount of heat in the heat-receiving pipe enters from an interval between the heat-receiving pipes to the heat insulating material of the back side, and heat is further diffused to the surrounding.
  • sunlight which is incident on the opening of the casing and passes between the heat-receiving pipes, is incident on a wall surface of the casing separated from the opening of the casing behind the heat-receiving pipe.
  • the heat insulating material or a heat absorption material forming the inner wall surface of the casing is heated by sunlight passing between the heat-receiving pipes.
  • the heated heat insulating material or the heat absorption material radiates heat, and heats the portion of the back side of the heat-receiving pipe to which sunlight is not directly irradiated.
  • the interval between the heat-receiving pipes in the portion of the heat-receiving pipe having high heat flux near the opening of the casing is widened, and the number of the heat-receiving pipes arranged per unit area is reduced.
  • a distance between the heat-receiving pipe and the opening of the casing, in which a diameter of luminous flux of sunlight is minimized, is separated, and energy of sunlight directly irradiated per unit area of the surface of the heat-receiving pipe is reduced.
  • more sunlight than in the past passes between the heat-receiving pipes, and energy of sunlight directly irradiated to the heat-receiving pipe is reduced.
  • the heat flux of the heat-receiving pipes may be reduced compared to the related art in the region near the opening of the casing.
  • the heat flux of the heat-receiving pipe surface is reduced in a region in which the heat flux of the heat-receiving pipe is easily increased near the opening of the casing, and thus it is possible to reduce the temperature difference between the front surface (a surface of the center axis side of the casing) and the back surface (a surface of an inner surface side of the casing) of the heat-receiving pipe. That is, the temperature difference is reduced between a portion of the front side of the heat-receiving pipe to which sunlight incident from the opening of the casing is directly irradiated and a portion of the back side of the heat-receiving pipe to which sunlight incident from the opening of the casing is not directly irradiated. Accordingly, life strength of the heat-receiving pipe may be extended.
  • the diameter of the heat-receiving pipe in the expanded section may be greater than that of the heat-receiving pipe in a portion other than the expanded section. That is, in a region in which the diameter of the circle passing through the centers of the heat-receiving pipes is expanded, the diameters of each heat-receiving pipe may be expanded compared to the diameters of each heat-receiving pipe in other regions.
  • the surface area of the outer circumferential surface of the heat-receiving pipe is further expanded.
  • the length of the heat-receiving pipe may be shortened. Accordingly, it is possible to further reduce the temperature difference between the portion (the front surface) of the front side of the heat-receiving pipe to which sunlight is directly incident and the portion (the back surface) of the back side to which sunlight is not directly incident.
  • the volume of the heat medium in the heat-receiving pipe is increased.
  • the heat medium in the heat-receiving pipe is increased in heat capacity, the temperature is not easily increased, and the temperature of the heat-receiving pipe is not easily increased.
  • a heat transfer accelerator may be equipped inside the heat-receiving pipe in the expanded section. That is, in a region in which the diameter of the circle passing through the centers of the plurality of heat-receiving pipes is expanded, the heat transfer accelerator having a thermal conductivity higher than that of the heat-receiving pipe may be placed inside the heat-receiving pipe. Furthermore, thermal conductivity of the heat transfer accelerator may be higher than that of the heat medium.
  • the present invention it is possible to increase the heat transfer coefficient inside the heat-receiving pipe and more effectively transfer heat from the heat-receiving pipe to the heat medium.
  • the amount of heat transfer between the heat-receiving pipe and the heat medium may be increased, length dimensions of the heat-receiving pipes may be shortened, and thus the size of the heat receiver may be reduced.
  • the heat transfer accelerator may be equipped inside the heat-receiving pipe without increasing the pressure loss of the inside of the heat-receiving pipe compared to other regions.
  • the temperature difference between the front portion and the back portion of the heat-receiving pipe may be reduced, and thus the life strength of the heat-receiving pipe may be improved.
  • FIG. 1 is a diagram showing a tower type solar light condensation heat receiver according to a first embodiment of the present invention.
  • FIG. 2 is a plan view showing an arrangement of heliostats around a tower.
  • FIG. 3A is a transverse cross-sectional view showing a schematic configuration of the tower top.
  • FIG. 3B is a longitudinal cross-sectional view showing a schematic configuration of the tower top.
  • FIG. 4 is a perspective view showing a schematic configuration of a heat receiver.
  • FIG. 5 is a perspective view of a heat-receiving pipe shown in FIG. 4 .
  • FIG. 6 is a cross-sectional view taken along line A-A shown in FIG. 3B showing a configuration of an insulating material (a radiation shield plate)
  • FIG. 7 is a perspective view that is seen from an arrow B of FIG. 6 .
  • FIG. 8 is a longitudinal cross-sectional view showing a schematic configuration of the heat receiver.
  • FIG. 9 is a graph of solar heat incident intensity of the heat-receiving pipe shown in FIG. 8 .
  • FIG. 10 is a longitudinal cross-sectional view showing a schematic configuration of a heat-receiving pipe according to a second embodiment.
  • a tower type solar power plant shown in FIG. 1 includes a solar light heat receiver placed on a high tower, and mirrors called heliostats which are placed on the ground around the solar light heat receiver and are able to control reflected light.
  • the tower type solar power plant condenses sunlight on the solar light heat receiver on the tower through the heliostats to generate electricity.
  • a heliostat field 101 is provided on the ground G.
  • a plurality of heliostats 102 for reflecting sunlight are placed in the heliostat field 101 .
  • a tower type solar light condensation heat receiver 100 which receives sunlight guided by the heliostats 102 is provided in a central section of the heliostat field 101 .
  • the heliostats 102 are placed 360° around the entire circumference of the tower type solar light condensation heat receiver 100 .
  • the tower type solar light condensation heat receiver 100 is constituted by a tower 110 erected on the ground G, an accommodation chamber 120 over the tower 110 , and a heat receiver (a solar heat receiver) 10 provided in the accommodation chamber 120 .
  • a plurality of reinforcing members 111 are provided in the tower 110 .
  • the reinforcing members 111 are placed so as to intersect the tower 110 in a height direction (a length direction) and are provided at intervals (distances between the reinforcing members adjacent to each other) P in the height direction of the tower 110 .
  • the interval P is increased toward the top (a side provided with the heat receiver 10 ) of the tower 10 in a range to be included in an optical path through which reflected light of sunlight is incident on the heat receiver 10 by the heliostat 102 . Accordingly, sunlight reflected by the heliostat 102 is condensed in the heat receiver 10 on the tower 110 without being blocked by the reinforcing members 111 .
  • the arrangement structure of reinforcing members 111 may be, for example, a truss structure in terms of ensuring rigidity.
  • the accommodation chamber 120 of the top of the tower 110 has a circular plane shape.
  • the accommodation chamber 120 has two accommodation chambers including an upper accommodation chamber 121 and a lower accommodation chamber 122 .
  • An opening 122 c for capturing sunlight is provided on a bottom of the lower accommodation chamber 122 .
  • the plane shape of the opening 122 c is a circular shape.
  • a diameter of the opening 122 c is determined depending on a spot diameter of sunlight.
  • the diameter of the opening 122 c of the present embodiment is greater than or equal to the spot diameter of sunlight.
  • the spot diameter is a diameter of a position at which the diameter of luminous flux of sunlight, which is reflected by the heliostats 102 of the heliostat field 101 and is incident on the opening 122 c , is the smallest.
  • the heat receiver 10 includes a cylindrical casing 11 and a heat-receiving pipe 20 .
  • the shape of the casing 11 is not limited to the cylindrical shape and may be a conical shape, a polygonal column shape, a spherical shape, an oval shape, or a combined shape of two or more of these.
  • the heat receiver 10 is provided in the lower accommodation chamber 122 . Specifically, the heat receiver 10 is fixed to an upper wall 122 a of the lower accommodation chamber 122 via a lifting tool 12 , and is suspended from the upper wall 122 a in the lower accommodation chamber 122 .
  • the heat receiver 10 is placed having a space between the inner walls in the position separated from the inner wall of the lower accommodation chamber 122 so as not to come into contact with the inner wall of the lower accommodation chamber 122 .
  • a plurality of lifting tools 12 are provided in the circumferential direction of the upper wall 122 a having a circular plane shape.
  • the lifting tools have flexibility. Furthermore, the lifting tools 12 pass through the casing 11 .
  • an opening 11 b for capturing sunlight is provided on the lower surface side (the bottom) of the casing 11 .
  • the opening 11 b is formed to have a circular plane shape.
  • the diameter of the opening 11 b is determined depending on the spot diameter of sunlight.
  • the diameter of the opening 11 b of the present embodiment is greater than or equal to the spot diameter of sunlight.
  • the diameter of the opening 11 b of the casing 11 of the present embodiment is smaller than or equal to the diameter of the opening 122 c of the accommodation chamber 120 .
  • the casing 11 is drawn in a cylindrical shape of the same diameter in an axial direction.
  • the casing 11 of the present embodiment has an expanded section 11 c in which a diameter of a lower portion thereof is expanded so as to widen outward in the radial direction. That is, the diameter of a lower part of the casing 11 near the opening 11 b is expanded compared to the diameter of an upper part of the casing 11 separated from the opening 11 b .
  • a heat-receiving pipe main body 23 extending in an axial direction (a vertical direction) of the casing 11 along an inner wall surface of the expanded section 11 c is placed inside the expanded section 11 c.
  • a gas turbine 30 which is operated using fluid (the heat medium) heated by the heat receiver 10 as a working fluid, and a generator 33 which extracts actuating energy of the gas turbine 30 as electric power are placed inside the upper accommodation chamber 121 .
  • the gas turbine 30 has a compressor 31 which sucks and compresses fluid (for example, atmosphere) serving as the heat medium to generate a compressed fluid, and a turbine 32 which is operated using the fluid compressed by the compressor 31 and heated by the heat receiver 10 as the working fluid. Moreover, kinetic energy generated by the rotation of the turbine 32 is converted into electric energy by the generator 33 and is extracted as electric power.
  • Devices such as a temperature sensor which detects heat received by the heat receiver 10 , an auxiliary drive device which starts the gas turbine 30 , a regenerative heat exchanger which performs the heat exchange between the working fluid and the exhaust of the turbine 32 before the working fluid is heated by the heat receiver 10 , an auxiliary combustor which performs auxiliary combustion of the working fluid and causes the working fluid to flow in the turbine 32 , and a vibration damper which cancels the vibration of the generator 33 may be placed inside the upper accommodation chamber 121 as necessary. In this manner, an installation area of the device may be reduced by integrally placing the devices over the tower 110 .
  • An opening 121 b for capturing fluid (atmosphere) to be supplied to the compressor 31 is provided on the side surface of the upper accommodation chamber 121 .
  • the opening 121 b is used to discharge the exhaust from the turbine 32 to the outside as necessary.
  • the heat-receiving pipe 20 has a lower header pipe 21 , an upper header pipe 22 , and a heat-receiving pipe main body 23 .
  • the lower header pipe 21 has a ring shape and is placed below the casing 11 . Specifically, the lower header pipe 21 is exposed to the outside of the casing 11 and is placed near the lower wall 122 b in the lower accommodation chamber 122 .
  • a plurality of heat-receiving pipe main bodies 23 are provided inside the casing 11 in a vertical direction between the upper header pipe 22 and the lower header pipe 21 .
  • the heat-receiving pipe main bodies 23 are connected to the upper header pipe 22 at one end thereof and are connected to the lower header pipe 21 at the other end thereof.
  • the heat receiving pipe main bodies 23 raise the temperature of the working fluid (heat medium) flowing therein from the lower header pipe 21 by the irradiation of sunlight.
  • the heated working fluid is discharged from the heat-receiving pipe main body 23 to the upper header pipe 22 .
  • the heat-receiving pipe main bodies 23 are placed at predetermined intervals (gaps) in the circumferential direction of the upper header pipe 22 (the lower header pipe 21 ) (see FIGS.
  • the end portion of the heat receiving pipe main body 23 connected to the lower header pipe 21 is exposed to the outside of the casing 11 .
  • Most of the part of the heat-receiving pipe main bodies 23 is formed in a shape (a straight line shape) that extends straight in the axial direction (a longitudinal direction) of the casing 11 . Bending stress due to self weight is not applied to the portion of the heat-receiving pipe main bodies 23 formed in a straight line.
  • the working fluid in the heat-receiving pipe main body 23 flows from the lower header pipe 21 toward the upper header pipe 23 in one direction.
  • the lower header pipe 21 is an annular pipe which is inflected in a ring shape or a polygonal shape when viewed from plane, and is disposed below the casing 11 . Specifically, the lower header pipe 21 is exposed to the outside of the casing 11 and is placed near the lower wall 122 b in the lower accommodation chamber 122 . With the configuration mentioned above, the heat-receiving pipe 20 is configured so that the upper header pipe 22 is fixed to the upper wall 122 a in the lower accommodation chamber 122 via the lifting tool 12 , all of which are suspended from the upper wall 122 a.
  • An L-shaped inlet pipe 13 is connected to the lower header pipe 21 .
  • a connection pipe 14 is connected between the inlet pipe 13 and the compressor 31 .
  • the connection pipe 14 is exposed to the outside of the casing 11 and is placed along the inner wall of the lower accommodation chamber 122 .
  • the compressed fluid generated by the compressor 31 is supplied to the lower header pipe 21 via the connection pipe 14 and the inlet pipe 13 .
  • the compressed fluid (the heat medium) supplied to the lower header pipe 21 flows in the plurality of heat-receiving pipe main bodies 23 and the upper header pipe 22 , and is heated by the heat-receiving pipe main body 23 and the upper header pipe 22 heated by thermal energy of sunlight that is incident from the opening 11 b.
  • an insulating material (a heat absorption material, a heat storage material or a radiation shield plate) 15 absorbing the solar heat is provided on the inner wall surface of the casing 11 .
  • the insulating material 15 is increased in temperature by absorbing the heat, and radiates the heat to the back surface (the portion of the back side on which sunlight is not directly incident) of the heat-receiving pipe main body 23 .
  • the portion of the back side of the heat-receiving pipe 20 is heated by the thermal radiation of the insulating material 15 and the portion of the front side of the heat-receiving pipe 20 is heated by sunlight, and thus, the entire heat-receiving pipe 20 in the circumferential direction is heated.
  • the insulating material 15 sends radiation heat generated from the heat-receiving pipe main body 23 back to the portion (the back surface) of the back side of the heat-receiving pipe main body 23 , and stably heats the heat-receiving pipe main body 23 . Furthermore, the insulating material 15 reduces an amount of heat going outward from the heat-receiving pipe main body 23 and the upper header pipe 22 .
  • An outlet pipe 25 is connected to the upper header pipe 22 via a plurality of connecting pipes 24 .
  • the plurality of connecting pipes 24 are configured so that one ends thereof are connected to the upper header pipe 22 , and the other ends thereof are connected to the outlet pipe 25 .
  • the connecting pipes 24 are placed in an X shape when viewed from the plane.
  • the outlet pipe 25 is bent in the upper accommodation chamber 121 , and is formed in an L shape when viewed from the plane shown in FIG. 3B .
  • the end portion of the outlet pipe 25 opposite to the side connected to the plurality of connection pipes 24 is connected to the turbine 32 .
  • the compressed fluid which flows through the inside of the heat-receiving pipe main body 23 and the upper header pipe 22 and is heated, is supplied to the turbine 32 as the high-temperature high-pressure working fluid via the connecting pipe 24 and the outlet pipe 25 .
  • the heat-receiving pipe main body 23 included in the heat-receiving pipe 20 of the heat receiver 10 is configured so that the portion having high heat flux at the opening 11 b side in the length direction extends to a position of the outside of the casing 11 in the radial direction, and an expanded section 20 c is formed where a diameter D of the pitch circle formed of the plurality of heat-receiving pipe main bodies 23 is expanded. That is, the diameter D of the pitch circle of the expanded section 20 c is greater than a diameter d of a pitch circle in a section 20 d other than the expanded section 20 c .
  • the pitch circle is a circle that intersects a central axis of each heat-receiving pipe main body 23 through the centers of the plurality of heat-receiving pipe main bodies 23 . That is, the plurality of heat-receiving pipe main bodies 23 are arranged at predetermined pitches (gaps) in the circumferential direction of the casing 11 , and the centers thereof are placed along the circumference of the pitch circle.
  • the plurality of heat-receiving pipe main bodies 23 are placed so as to be separated from each other in the circumferential direction of the casing 11 and to extend in the vertical direction.
  • the centers of the heat-receiving pipe main bodies 23 are placed along the same circumference.
  • the plurality of heat-receiving pipe main bodies 23 are bent outward in the radial direction of the casing 11 in the portion closer to the opening 11 b than the central section of the casing 11 in the vertical direction. Accordingly, the expanded section 20 c is provided in the heat-receiving pipe main body 23 in a region near the opening 11 b of the casing 11 .
  • the circle passing through the centers of the plurality of heat-receiving pipe main bodies 23 is configured so that the diameter D in the region near the opening 11 b is expanded compared to the diameter d in the region separated from the opening 11 b.
  • heat-receiving pipe main body 23 corresponds to the heat-receiving pipe of the present invention.
  • FIG. 8 the insulating material 15 shown in FIGS. 4 , 6 and 7 is omitted.
  • the expanded sections 20 c of the heat-receiving pipe main bodies 23 are placed along the inner surface of the expanded section 11 c of the casing 11 mentioned above at predetermined intervals and form a substantially trapezoidal shape when viewed from the side, and the lower ends thereof are projected outward from the casing 11 .
  • FIG. 9 is a graph showing an effect of the expanded section 20 c of the heat-receiving pipe main body 23 included in the heat-receiving pipe 20 , a vertical axis thereof indicates the length (a distance from the opening 11 b ) X of the heat-receiving pipe main body 23 , and a horizontal axis thereof indicates a heat input quantity (solar heat incident intensity) to the heat-receiving pipe main body 23 .
  • a dotted line is a result of a case in which the expanded section 20 c is not provided in the heat-receiving pipe main body 23
  • a solid line is a result of a case in which the expanded section 20 c is provided. As shown in FIG.
  • the diameter D of the pitch circle is expanded in the portion having high heat flux (the high temperature section K) of the heat-receiving pipe main bodies 23 included in the heat-receiving pipe 20 . Accordingly, the surface area of the outer circumferential surface of the heat-receiving pipe 20 in that portion is expanded. In other words, the interval between the heat-receiving pipe main bodies 23 in the high temperature section K of the heat-receiving pipe main bodies 23 near the opening 11 b of the casing 11 is widened, and the number of the heat-receiving pipe main bodies 23 to which sunlight is irradiated per unit area in the region is reduced.
  • the distance between the heat-receiving pipe main bodies 23 and the opening 11 b of the casing 11 in which the diameter of luminous flux of sunlight is minimal, is separated, and energy of directly irradiated sunlight per unit area of the surface of the heat-receiving pipe main bodies 23 is reduced. Accordingly, in the region near the opening 11 b , more sunlight than in the related art passes between the heat-receiving pipe main bodies 23 , and it is possible to reduce the heat input quantity per unit area to the heat-receiving pipe main bodies 23 (see FIG. 9 ). Moreover, the reduced amount of heat in the heat-receiving pipe 20 including the heat-receiving pipe main bodies 23 enters the insulating material 15 (see FIGS. 6 and 7 ) provided behind (the back side of) the heat-receiving pipe main bodies 23 through the gap between the heat-receiving pipe main bodies 23 , and the heat is further diffused to the surroundings thereof.
  • the heat flux of the surface of the heat-receiving pipe main bodies 23 is reduced, it is possible to reduce the temperature difference between the portion (the front surface) 20 a (the surface facing the central axis of the casing 11 ) of the front side of the heat-receiving pipe main bodies 23 and the portion (the back surface) 20 b (the surface facing the inner surface of the casing 11 ) of the back side thereof, and thus the life strength of the heat-receiving pipe 20 may be extended.
  • the fluctuation of a gas temperature of the heat-receiving pipe outlet is suppressed, the set gas temperature of the outlet side may be stabilized, and thus the operation of the turbine may be stabilized.
  • a heat receiver (a solar heat receiver) 10 A is configured so that a pipe diameter of an expanded section 20 e in the heat-receiving pipe main bodies 23 included in the heat-receiving pipe 20 is greater than that of a portion other than the expanded section 20 e . That is, in a region in which the diameter of the circle passing through the center of each heat-receiving pipe main body 23 is expanded, the diameter of each heat-receiving pipe main body 23 is expanded compared to the diameter of each heat-receiving pipe main body 23 in other regions.
  • the surface area of the outer circumferential surface of the heat-receiving pipe 20 is further increased, and thus the heat input quantity per unit area may be further reduced. Furthermore, by enlarging the diameter of the heat-receiving pipe main bodies 23 , the volume of the compressed fluid in the heat-receiving pipe main bodies 23 is increased. Accordingly, the compressed fluid in the heat-receiving pipe main bodies 23 is increased in heat capacity, the temperature does not rise easily, and the temperature of the heat-receiving pipe main bodies 23 does not rise easily either. Thus, it is possible to further reduce the temperature difference between the portion (the front surface) of the front side of the heat-receiving pipe main bodies 23 and the portion (the back surface) of the back side thereof to the incident direction of sunlight.
  • the expanded section 20 e of the heat-receiving pipe main bodies 23 may be equipped with a heat transfer accelerator 20 h . That is, the heat transfer accelerator 20 h having thermal conductivity higher than that of the heat-receiving pipe main bodies 23 may be placed inside the heat-receiving pipe main bodies 23 in the region in which the diameter D of the circle passing through the centers of the plurality of heat-receiving pipe main bodies 23 is expanded. Furthermore, the thermal conductivity of the heat transfer accelerator 20 h may be higher than that of the compressed fluid flowing in the heat-receiving pipe main bodies 23 .
  • the heat transfer accelerator 20 h may be equipped inside the heat-receiving pipe main bodies 23 without increasing the pressure loss.
  • the heat transfer coefficient inside of the heat-receiving pipe main bodies 23 may be increased. Accordingly, since an amount of heat exchange between the heat-receiving pipe main bodies 23 and the compressed fluid may be increased, the length dimension of the heat-receiving pipe main bodies 23 may be shortened, and thus the heat receiver 10 A may be downsized.
  • the pipe diameter of the heat-receiving pipe main bodies 23 is 1.3 times that of the expanded section 20 e
  • the expanded section 20 e is equipped with the heat transfer accelerator 20 h , and it is therefore possible to expand the amount of heat exchange by about 1.6 to 2.4 times compared to an original pipe diameter.
  • the shape of the expanded section 20 c of the heat-receiving pipe 20 is substantially a trapezoidal shape when viewed from the side, the shape is not limited thereto.
  • a tapered shape which gradually spreads radially outward from the casing 11 toward the bottom or in an umbrella shape may be adopted.
  • the pipe diameter dimension of the expanded section 20 e of the heat-receiving pipe main bodies 23 having the large diameter in the second embodiment may be arbitrarily set, and may be determined depending on the conditions such as the presence or the absence of the heat transfer accelerator as mentioned above.
  • a solar light heat receiver includes a casing having an opening on which sunlight is incident, and a plurality of heat-receiving pipes that are vertically arranged inside the casing and raise the temperature of a heat medium flowing therein by the irradiation of the sunlight.
  • the plurality of heat-receiving pipes are arranged so as to be spaced from each other and to extend in one direction. Centers of the respective heat-receiving pipes are arranged on the same circumference.
  • the plurality of heat-receiving pipes are bent outward in the radial direction in a portion near the opening of the casing.
  • a circle passing through the centers of the plurality of heat-receiving pipes is configured so that a diameter in a region near the opening is expanded compared to a diameter in a region separated from the opening.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Photovoltaic Devices (AREA)
US13/575,982 2010-02-05 2011-01-28 Solar heat receiver Abandoned US20120291772A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2010-024395 2010-02-05
JP2010024395A JP2011163593A (ja) 2010-02-05 2010-02-05 太陽熱受熱器
PCT/JP2011/051790 WO2011096339A1 (ja) 2010-02-05 2011-01-28 太陽熱受熱器

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EP (1) EP2532984A1 (ja)
JP (1) JP2011163593A (ja)
AU (1) AU2011211877A1 (ja)
WO (1) WO2011096339A1 (ja)
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US20120012102A1 (en) * 2009-04-16 2012-01-19 Mitaka Kohki Co., Ltd. Solar power concentrating system
US20140305124A1 (en) * 2011-11-25 2014-10-16 Mitsubishi Heavy Industries, Ltd. Solar heat receiver and solar heat power generation device
US8936020B1 (en) * 2014-03-12 2015-01-20 Fricaeco America Sapi De C.V. Solar fluids preheating system with low thermal losses
US9534811B2 (en) 2014-12-31 2017-01-03 Fricaeco America, SAPI de C.V. Solar fluid preheating system having a thermosiphonic aperture and concentrating and accelerating convective nanolenses
US9557078B2 (en) 2011-02-11 2017-01-31 Fricaeco America Sapi De C.V. Solar heater for liquids
US10260014B2 (en) 2014-05-13 2019-04-16 Niigata University Concentrated solar heat receiver, reactor, and heater
US20210164694A1 (en) * 2019-11-29 2021-06-03 Guangdong Polytechnic Normal University Concentrated solar power generation system

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JP2013130372A (ja) * 2011-12-22 2013-07-04 Mitsubishi Heavy Ind Ltd 太陽熱受熱器、その組立方法、および太陽熱受熱器を備えた太陽熱発電システム

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120012102A1 (en) * 2009-04-16 2012-01-19 Mitaka Kohki Co., Ltd. Solar power concentrating system
US9557078B2 (en) 2011-02-11 2017-01-31 Fricaeco America Sapi De C.V. Solar heater for liquids
US20140305124A1 (en) * 2011-11-25 2014-10-16 Mitsubishi Heavy Industries, Ltd. Solar heat receiver and solar heat power generation device
US10060418B2 (en) * 2011-11-25 2018-08-28 Mitsubishi Heavy Industries, Ltd. Solar heat receiver and solar heat power generation device
US8936020B1 (en) * 2014-03-12 2015-01-20 Fricaeco America Sapi De C.V. Solar fluids preheating system with low thermal losses
US10260014B2 (en) 2014-05-13 2019-04-16 Niigata University Concentrated solar heat receiver, reactor, and heater
US9534811B2 (en) 2014-12-31 2017-01-03 Fricaeco America, SAPI de C.V. Solar fluid preheating system having a thermosiphonic aperture and concentrating and accelerating convective nanolenses
US20210164694A1 (en) * 2019-11-29 2021-06-03 Guangdong Polytechnic Normal University Concentrated solar power generation system
US11815291B2 (en) * 2019-11-29 2023-11-14 Guangdong Polytechnic Normal University Concentrated solar power generation system

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EP2532984A1 (en) 2012-12-12
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AU2011211877A1 (en) 2012-08-23
JP2011163593A (ja) 2011-08-25

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