WO2013130350A1 - Collecteur solaire à flux direct - Google Patents

Collecteur solaire à flux direct Download PDF

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Publication number
WO2013130350A1
WO2013130350A1 PCT/US2013/027339 US2013027339W WO2013130350A1 WO 2013130350 A1 WO2013130350 A1 WO 2013130350A1 US 2013027339 W US2013027339 W US 2013027339W WO 2013130350 A1 WO2013130350 A1 WO 2013130350A1
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WO
WIPO (PCT)
Prior art keywords
solar
liquid
tube
fin
shaped channel
Prior art date
Application number
PCT/US2013/027339
Other languages
English (en)
Inventor
Yan Kunczynski
Original Assignee
Yan Kunczynski
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Yan Kunczynski filed Critical Yan Kunczynski
Publication of WO2013130350A1 publication Critical patent/WO2013130350A1/fr
Priority to PCT/US2013/065807 priority Critical patent/WO2014066194A1/fr
Priority to US14/467,179 priority patent/US20140360492A1/en

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Classifications

    • 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
    • F24S10/72—Solar heat collectors using working fluids the working fluids being conveyed through tubular absorbing conduits the tubular conduits being integrated in a block; the tubular conduits touching each other
    • 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
    • F24S10/40—Solar heat collectors using working fluids in absorbing elements surrounded by transparent enclosures, e.g. evacuated solar collectors
    • F24S10/45—Solar heat collectors using working fluids in absorbing elements surrounded by transparent enclosures, e.g. evacuated solar collectors the enclosure being cylindrical
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S40/00—Safety or protection arrangements of solar heat collectors; Preventing malfunction of solar heat collectors
    • F24S40/50—Preventing overheating or overpressure
    • F24S40/55—Arrangements for cooling, e.g. by using external heat dissipating means or internal cooling circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24S—SOLAR HEAT COLLECTORS; SOLAR HEAT SYSTEMS
    • F24S40/00—Safety or protection arrangements of solar heat collectors; Preventing malfunction of solar heat collectors
    • F24S40/70—Preventing freezing
    • 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
    • F24S60/30—Arrangements for storing heat collected by solar heat collectors storing heat in liquids
    • 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
    • F24S80/30—Arrangements for connecting the fluid circuits of solar collectors with each other or with other components, e.g. pipe connections; Fluid distributing means, e.g. headers
    • 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
    • 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
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P90/00—Enabling technologies with a potential contribution to greenhouse gas [GHG] emissions mitigation
    • Y02P90/50—Energy storage in industry with an added climate change mitigation effect

Definitions

  • This invention relates to the harnessing of solar energy, and more particularly to solar hot water heating.
  • a hot water solar collector which is generally a part of a system comprising a water supply and/or storage means, a circulation pump, and a heat-exchanger means.
  • Flat-plate solar collectors are popular in the sunny, year-around warm, climates in the United States. They are comprised of a heat- absorption panel in contact with circulating water and are typically housed under a transparent covering and over an insulating bed. The flat panels absorb solar energy in much the way photo-voltaic (PV) electric panels do. Heat transfer efficiency is a function of reflective, conductive, and convective heat losses, as well as the temperature differential between the absorption panel and the incident water.
  • PV photo-voltaic
  • Evacuated tube (EVT) collectors are common in China, where 60% of global solar collector capacity is installed and where over 70% of the EVT's are manufactured.
  • the most popular EVT type is a double-walled glass tube having an evacuated air space between the walls.
  • the inside tube is coated to enhance absorption and back- reflection of spectral infra-red (IR).
  • IR spectral infra-red
  • Heat absorbed by the tubes is transferred to a manifold, into which they are inserted, by circulation of a liquid through an internal viaduct (U-tube) or by phase change of a captive liquid in a capillary (heat pipe).
  • U-tube internal viaduct
  • heat pipe phase change of a captive liquid in a capillary
  • the tubular design accommodates different solar angles.
  • the use of a complete vacuum as an insulator makes them appropriate for cold climates and where extremely high temperatures are required or maintained. Maintenance is also simpler, in that individual tubes can be replaced, often while the system is in use.
  • the major disadvantage of the EVT collector is the cost in dollars per BTU.
  • the object of the present invention is to enable solar hot water heating at colder locations, not to mention improvement at all locations, by addressing the cost of the EVT collector.
  • the heat pipe EVT design requires a heat exchange in the manifold, whereas the U- tube design avoids this exchange and the energy losses attendant thereto, by directly heating the solar liquid.
  • the disadvantages of the currently-practiced U-tube technology present opportunities for improvement. Both freezing and overheating, also called “stagnation", become issues with the solar liquid present in the EVT.
  • glycol antifreeze is used for the solar liquid in a closed-loop circulation system. High pressure is required to prevent the glycol from boiling during periods of stagnation.
  • the glycol To heat water in a storage tank, or a swimming pool, the glycol must communicate through a heat exchanger, presenting another opportunity for thermal loss.
  • the high pressure requirement drives high installation costs.
  • the U-tubes are typically arranged in an array and integrated into a manifold configuration at a factory location.
  • the ungainly package produced typically 30-40 U-tubes joined by brazing, soldering or welding, is then shipped to the installation site. Shipping costs can be quite expensive considering the volume and dimension of the package.
  • Elimination of the high pressure requirement could mean less expense in materials, shipping, and assembly. Without a pressure requirement, seals and flexible tubing could be used to join components. Without a factory configuration, modular design could be implemented and customization thereby facilitated. Assembly work could be done on-location with unskilled labor. Pressure and relief tanks could be eliminated as necessary system components and the expense of pressure-rated pumps could be avoided. System maintenance could be achieved without bleeding and recharging lines, often with the loss of the glycol charge. Elimination of glycol alone would bring maintenance and material cost advantages.
  • Eliminating glycol would address the high pressure requirement but freezing and stagnation would remain as issues.
  • Gravity drain-back systems prevent freezing by evacuating the solar liquid channels, but under current art some liquid is always left fugitive in the channels, regardless of the orientation or tilt of the array. These "gravity blind-spots", or pathway low spots, can cause flash vaporization during stagnation causing damage to the EVT's.
  • the present invention presents a novel solution for drain-back which eliminates glycol as the solar liquid by substituting the system water and, in so doing, accesses additional cost advantages attendant to a low pressure system model. Freeze protection and stagnation control, under the novel concept, are provided by mechanically forcing air through the liquid channels, thereby assuring a complete evacuation of liquid.
  • the forced-air drain-back feature also allows the solar array to be mounted at any vertical angle, including that of horizontal, because pathway low spots can now be purged regardless of orientation.
  • the low- angle/horizontal mounting itself presents several benefits, including that of enhanced visual impact and reduced wind resistance from the low architectural profile and more efficient layout of farm arrays consisting of multiple panels. The latter benefit results from the fact that relatively high-angle profiles cast horizontal sun shadows which force increased spacing between neighboring panels.
  • the concept addresses the fin, which is commonly attached to standard tubing and projects arcuate "wings" there from which serve to absorb radiant heat passing through the EVT walls.
  • the fin and the water channel are combined in a single extrusion, which is then bent into a "U" shape.
  • the construction eliminates the insulating air gap that results from separate components, and the curvature of the extrusion, by closely following the wall contour, adds additional thermal efficiency by permitting large area surface contact with the wall.
  • the cross-sectional area of the water channel is enlarged by elongating its shape. The enlargement, measuring almost twice that of the standard tube, permits a larger volume of throughput resulting in lower pressure. With pressure sufficiently optimized by eliminating the glycol and making the channel enlargement, inexpensive and easy-to-install flexible tubing may be used in the interconnecting links of the U- tubes.
  • Still another novel concept derives from manipulation of series and parallel connections channeling the water through the U-tubes.
  • U-tubes connected in series provide higher output temperatures, but too many tubes connected in this manner produce lower heat-transfer efficiency because successive heating causes reduction of the temperature differential, the thermal driving force.
  • U-tubes connected in parallel have a constant temperature differential but require a longer circulation and pump operation time to achieve the same heating result.
  • An unexpected result of the parallel configuration is that the necessarily larger supply channels tend to cause a cavitation effect in the relatively smaller tube channels; that is, air pockets get trapped that produce an insulating layer and result ultimately in lowered thermal efficiency.
  • the inventive concept is to use an optimal combination of both configurations to give an improved result in terms of operating cost per BTU.
  • a solar collector comprising a manifold having an input port, an output port and a plurality of orifices; a corresponding plurality of solar tubes connected to the manifold through the orifices, the plurality of solar tubes assembled in a planar array and positioned for exposure to solar radiation; at least one liquid channel from the input port to the output port, said liquid channel having at least one continuous flow path there through; a means for transferring heat absorbed from solar radiation in each solar tube to a solar liquid flowing through the at least one continuous flow path; a means for forcibly evacuating the at least one liquid channel to prevent damage by freezing or boiling; and a means for circulating the solar liquid through the means for transferring heat.
  • heat from solar radiation is transported for work purposes through the solar liquid by the means for transferring heat and by the means for circulating and the solar liquid is drained substantially completely from the at least one liquid channel by the means for forcibly evacuating.
  • the means for transferring heat comprises a fin inserted into each solar tube and extending the length of the tube.
  • the fin has an integrated U- shaped channel extending from an input end to an output end.
  • the input end of a first U-shaped channel in a first solar tube of the planar array forms a fluid connection to the input port while the output end of the first U-shaped channel of the first solar tube forms a fluid connection in preferred configuration to the input end of a last U-shaped channel in a last solar tube.
  • the output end of the last U-shaped channel in the last solar tube then forms a fluid connection to the output port.
  • at least one liquid channel is formed for a continuous flow path through each solar tube, the flow of solar liquid therein receiving heat by conduction from the fin.
  • the preferred configuration is a serial linkage joining ten solar tubes and a parallel linkage joining four serial linkages.
  • FIG. 1 is a perspective view of a mounted solar collector of the present invention
  • FIG. 2 is a truncated elevation view of an EVT
  • FIG. 3 is a section view of the EVT taken along the lines 3-3 of Fig. 2;
  • FIG. 4 is a partial perspective view of two serially connected U-tubes
  • FIG. 5 is a detail view of detail 5_in Fig. 4;
  • FIG. 6 is a detail view of detail 6 in Fig. 4;
  • FIG. 7 is a partial perspective view of a 20-tube array showing series and parallel path connections
  • FIG. 8 is a partial plan view of a 20-tube array showing a modular connection to tubes
  • FIG. 9 is a side view of a 10-tube module with an eleventh tube in phantom line;
  • FIG. 10 is a truncated section view taken along lines 10-10 of Fig. 9 showing solar liquid paths;
  • FIG. 11 is a partial exploded perspective view of three serially-linked tubes
  • FIG. 12 is a truncated perspective view of an extruded fin
  • FIG. 13 is a truncated elevation view of a U-tube
  • FIG. 14 is a section view taken along the lines 14-14 of Fig. 13 showing a cross- section of the water channel;
  • FIG. 15 is a perspective view of the manifold
  • FIG. 16 is an exploded perspective view of the manifold and insulation
  • FIG. 17 is a diagram of a solar collector system of the present invention.
  • FIG. 18 is a perspective view of an innovative blow-back valve of the present
  • FIG. 19 is a plan view of the blow-back valve
  • FIG. 20 is a section view of the blow-back valve taken alone lines 20-20 of Fig. 19;
  • FIG. 21 is a diagram of a solar collector system including the blow-back valve and a compressed air circuit.
  • Fig 1 shows the major components of a solar collector 1.
  • a solar tube planar array 12 is connected to a manifold 20 through orifices 29.
  • the manifold 20 has an input port 22 and an output port 23 defining there through and there between at least one liquid channel 4 receiving circulation of a solar liquid 3 (not shown) through at least one continuous flow path 9 (see also Fig. 10).
  • the solar collector 1 may be supported by frame members 2 received in frame slots 100 located in the middle and both ends of the solar collector 1 (see also Fig's 6 and 15).
  • a means forcibly evacuating 50 proactively expels all solar liquid 3 from the at least one liquid channel 4 to protect the apparatus from the effects of freezing or boiling.
  • the solar tube planar array 12 is comprised of a plurality of solar tubes 7.
  • the planar array 12 may be arrayed bi-laterally, as shown throughout the figures, or may be configured with all tubes oriented in one direction to accommodate space constraints at the installation site.
  • the number of solar tubes 7 in the planar array may be limited by roof-top layout or, otherwise, by the design pressure drop across the circulatory pathway. In the preferred embodiment, it is desirable to maintain a low operating pressure for cost advantage reasons. In a particular preferred embodiment, it is the objective to maintain the operating pressure at 10 psi or less. Accordingly, an optimal array would be comprised of not more than 40 tubes.
  • the solar tube 7 is designed to receive solar radiation through a glass envelope and retain the energy as heat in the interior.
  • the solar tube 7 is a double-walled EVT 8, as shown in Fig's 2-6.
  • the inner tube 102 has several coating layers to enhance performance, namely an anti-reflection layer, an absorbance-enhancing layer and an IR reflection layer.
  • the EVT 8 has an open end 104 and a closed end 109. When the solar tube 7 is connected to the manifold 20 through one of the orifices 29, the open end 104 shoulders against a ledge 105 in the interior (Fig. 15).
  • the closed end 109 is cradled in end cup 17, which is supported in the mounted configuration of solar collector 1 by end cup support 18.
  • End cup support 18 has an adjustment screw 107, which serves to bias the open end 104 against the ledge 105.
  • the at least one liquid channel 4 is comprised of a means for transferring heat 30, as shown in Fig's 11-14.
  • said means comprises a fin 31.
  • Fin 31 has an integrated U-shaped channel 32, which forms a part of the at least one continuous flow path 9.
  • the integration of the U-shaped channel 32 in the uni-bodied fin 31 eliminates any thermal losses resulting from air gaps necessarily in place between separate components.
  • Fin 31 is inserted into the EVT 8 to the extent of the draw therein.
  • Fin 31 has arcuate wing members 108 flanking the U-shaped channel 32 to form a contact surface with the inner tube 102 through which heat is conducted to the solar liquid 3 flowing through the U-shaped channel 32.
  • the arms of the "U” of the U-shaped channel 32 may be biased outwardly by a resilient member 44 (not shown) to make contact with the wall of the tube and thereby eliminate another potential air gap.
  • Fin 31 is fabricated as an extrusion 36 comprised of aluminum.
  • Arcuate wing members 108 may be trimmed away (Fig. 12) to form nipples 39 of U- shaped channel 32 at either end thereof.
  • Two such nipples 39 may be joined in a U- configuration by a U-shaped connector 200 (not shown).
  • the U-shaped connector 200 may be, for example, a section of flexible tubing braced open by an inserted coil spring.
  • the U-configuration is achieved by bending a single extrusion with slotted wings into the U-shaped channel 32.
  • the U-shaped channel 32 maintains its throat by means of gussets 35 therein.
  • two nipples 39 protrude from the open end 104 of the solar tube 7 to form an input end 33 and an output end 34 of U-shaped channel 32, as shown in Fig's 9 andlO.
  • the output end 34 in one solar tube 7 may be connected to the input end 33 in another solar tube to form a serial linkage 41.
  • the input end 33 in one solar tube may also be connected to the input end in another solar tube to form a parallel linkage 42.
  • the input end 33 of a first U-shaped channel 37 in a first solar tube 5 of the planar array 12 is connected to the input port 22 of the manifold 20 and the output end 34 of a last U-shaped channel 38 in a last solar tube 6 is connected to the output port 23.
  • the input port 22 is connected to the output 23 in a preferred configuration 40 comprised of a preferred number of solar tubes 7 in the serial linkage 41 and a preferred number of serial linkages 41 in a parallel linkages 42 to form the at least one liquid channel 4 through which the solar liquid 3 may flow through each solar tube 7 in the at least one continuous flow path 9.
  • One objective in the optimization of thermal efficiency is to avoid non-turbulent flow in the at least one continuous flow path 9. This is achieved by using serial linkage 41, wherein the cross-sectional area of the at least one liquid channel 4 can more closely approximate that of the cross-sectional area of the U-shaped channel 32.
  • Another objective in the optimization of thermal efficiency is to maintain at least some temperature differential across the path through serial linkage 41. This requires limiting the number of solar tubes 7 in any one serial linkage 41 and connecting multiple serial linkages 41 in the parallel linkage 42.
  • the breadth of the parallel linkage 42 is determined by the optimal pressure drop across the at least one continuous flow path 9, which in turn defines the operating pressure of the system.
  • the cross-sectional area of the U-shaped channel 32 is approximately 72 sq. mm.
  • the preferred embodiment specifies ten solar tubes 7 to a serial linkage 41 and four serial linkages 41 to a parallel linkage 42, optimally defining the planar array 12 as an array of 40 tubes (the first 10 tubes only are shown in Fig. 10). It has been discovered that the best optimization of thermal efficiency, as measured by cost per BTU, occurs by balancing the non-turbulent flow consideration, having the consequence of avoiding insulating air pockets in the channel, with the pressure consideration, having the consequence of protecting temperature differential. The pressure consideration also affects other efficiencies of construction.
  • Fig's 7 and 8 show a network of the flexible tubing 10 in both serial and parallel configurations.
  • flexible tubing 10 is comprised of high temperature (rated at 250° C) silicone rubber.
  • the flexible tubing 10 forms a seal with the nipples 39 when compressed thereon by a band, clip, or other form of compression known in the art.
  • a modular unit of planar array 12 is comprised of 20 solar tubes 7.
  • two or more modular units may be combined by extending parallel linkage 42 through linkage sections 13 of flexible tubing 10.
  • the modularity of the design facilitates customized installation and delivers cost benefits associated with on-site assembly.
  • the manifold 20 is comprised of manifold housing assembly 21 and insulation core 25, as shown in Fig's 15 and 16.
  • the manifold housing assembly 21 is comprised of a housing base 26 and a housing top 27.
  • the housing top 27 is connected to the housing base 26 through a manifold seal 24 to form an enclosure.
  • Each manifold seal 24 comprises a plurality of orifices 29 to receive the solar tubes 7 of the planar array 12.
  • the insulation core 25 has a center bore 28 in which the at least one liquid channel 4 is situated, said insulation core insulating the liquid channel 4 from heat loss.
  • the housing base 26 and the housing top 27 are fabricated from aluminum by extrusion.
  • the manifold seal 24 is fabricated in a molding of ethylene propylene diene monomer (EPDM) material.
  • the insulation core 25 is fabricated from mineral wool panels.
  • a gravity drain back system requires sloping paths which remain unobstructed to allow draining.
  • a planar-configured serpentine path such as that herein recited, it is virtually impossible, regardless of orientation, to not have some structure in obstruction along the at least one continuous flow path 9.
  • the solar liquid trapped in these "gravity blind-spots" vaporizes with damaging effect during stagnation heating.
  • the means for forcibly evacuating 50 improves upon the conventional gravity drain- back system by essentially flushing all parts of the at least one continuous flow path 9 with a mechanically-assisted forced-air system 56, as shown in Fig. 17.
  • the mechanically-assisted forced-air system 56 comprises a blower 51 and a fresh air source 53.
  • a solenoid valve 52 (normally open)_is required to isolate the air flow path 43 from the at least one continuous flow path 9.
  • a first diversion valve 54 and a second diversion valve 55 are placed at locations flanking the vent 57 where the air is in-ported.
  • the blower 51, the gate solenoid valve 52, the first diversion valve 54 and the second diversion valve 55 are controlled by a temperature control system 45.
  • the solenoid valve 52 is opened and the diversion valves are alternately closed.
  • a supply path 59 including the at least one continuous flow path 9, is purged of solar liquid 3.
  • a return path 58 is purged.
  • the solar collector 1 further comprises a means for circulating 60 the solar liquid 3 through the means for transferring heat 30.
  • the means for circulating 60 comprises a low-pressure pump 61, a solar liquid loop 74 and a holding tank 65, as shown in Fig. 17.
  • the holding tank 65 serves as a reservoir for the solar liquid 3, which may be supplied to the reservoir from another source or may circulate in a closed loop therein.
  • the solar liquid loop 74 communicates with the holding tank 65 and includes the supply path 59 and the return path 58.
  • the low- pressure pump 61 is also controlled by the temperature control mechanism 45.
  • the temperature control mechanism 45 is further comprised of a first temperature sensor 46 located in the holding tank 65 and a second temperature sensor 47 located in proximity to the output port 23.
  • the low-pressure pump 61 is activated with the solenoid valve 52 normally closed and the first diversion valve 54 and the second diversion valve 55 both normally open.
  • the preferred temperature setting at the second temperature sensor 47 is below 100° C, and the preferred temperature setting at the first temperature sensor 46 is below that at the second temperature sensor 47.
  • the mechanically-assisted forced air system 56 comprises a source of compressed air 81 and a means for automatically introducing low-pressure air 80 into the at least one continuous flow path 9.
  • the source of compressed air 81 is compressed air tank 82 releasing air through solenoid valve 52'.
  • the compressed air tank 82 is charged by compressor 83.
  • the compressor 83 is activated by the temperature control system 45' to charge the compressed air tank 82 to a pressure of 125 psi, for example, when circulation is called for.
  • the temperature control system 45' opens solenoid valve 52' to release air into the air flow path 43'.
  • the second temperature sensor 47' is located in the first solar tube 5.
  • the temperature control system 45' responds to preferred temperature settings, as discussed above, but also responds to a power shutdown, planned or otherwise, by reverting to a default mode.
  • the default mode automatically opens solenoid valve 52' to permit air flow there through and provides, thereby, a fail-safe system immune to power failure.
  • the temperature control mechanism 45' will not permit a restart of the low- pressure pump 61 when stagnation conditions are present; that is, when the second temperature sensor 47' indicates a temperature of 100° C or above.
  • the means for automatically introducing low-pressure air 80 is comprised of a regulator 84 situated in the air flow path 43' downstream of the solenoid valve 52' and a blow-back valve 90 situated in the at least one continuous flow path 9 by intersection with the supply path 59 of the solar liquid loop 74.
  • the regulator 84 steps the pressure down to a low-pressure in the downstream part of air flow path 43'.
  • the pressure in the downstream part may be as low as 3 psi, for example.
  • the blow-back valve 90 is comprised of an outer valve body 91 and an inner valve body 92 inserted through a bore in the outer valve body 91, a valve chamber 98 defined there between.
  • the inner valve body 92 is comprised of a water inlet side 94 and an air inlet side 95 sealingly separated by a divider wall 93. Both the water inlet side 94 and the air inlet side 95 have slits 96 cut therein.
  • Slits 96 will open when pressure is directed outwardly from the inner valve body but, because of cylindrical construction, will be compressed closed when pressure is directed inwardly.
  • the arrangement of components defines three pressure zones: Pi in valve chamber 98, P 2 in the water inlet side 94, and P 3 in the air inlet side 95.
  • P 2 > Pi water will flow in the at least one continuous flow path 9.
  • P 3 > Pi air will flow in the at least one continuous flow path 9.
  • Drainback in the upstream part of the flow path is facilitated by aspiration holes 97 in the water inlet side 94.
  • the outer valve body 91 is a molded thermoplastic elastomer (TPE), preferably of a silicone composition.
  • the inner valve body 92 is fabricated from silicone tubing, preferably of an 18 mm OD by 3 mm wall configuration.
  • the divider wall 93 is an inserted cork plug held in place by a clamp 99 (not shown).
  • Shanks of aluminum tubing 75 interconnect receiving apertures in the outer valve body 91 and the inner valve body 92 with the solar liquid loop 74 and the air flow path 43', the connections sealed by other clamps 99 (not shown).
  • the holding tank 65 is a hot water storage vessel 71.
  • Hot water storage vessel 71 is a member of a solar hot water system 70, which is also includes solar collector 1.
  • the solar liquid 3 of the solar hot water system 70 is water 73 stored in water storage vessel 71.
  • the water 73 is a de-mineralized, or soft, water.
  • the means for circulating 60 further comprises a circulation of water 73 from a hot zone 62 of the water storage vessel 71 to a cold zone 63.
  • the water storage vessel 71 is preferably large enough in volume for a stratification to occur by the colder, denser water gravitating downward.
  • the solar liquid loop 74 fluidly connects the cold zone 63 to the input port 22 and the hot zone 62 to the output port 23.
  • Hot water storage vessel 71 also may comprise load 72.
  • the load 72 effectively removes heat from the storage part of the system.
  • the load 72 may be a submerged heat exchanger, whereby chlorinated pool water may be heated without contaminating the solar liquid 3.
  • the load 72 may be a source of cold, soft, water drawn into cold zone 63 and hot tap water drawn out of hot zone 62 on demand.
  • a method of configuring a solar collector to achieve operating efficiency, as measured by cost per BTU comprises the steps as follows: a) providing the solar collector 1, wherein the means for transferring heat 30 is a fin 31 inserted into each solar tube 7 and extending the length thereof, said fin having an integrated U-shaped channel 32 extending from an input end 33 to an output end 34; the input end 33 of a first integrated U-shaped channel 37 in a first solar tube 5 of the planar arrayl2 forming a fluid connection to the input port 22; the output end 23 of the first U-shaped channel 37 in the first solar tube 5 forming a fluid connection in a preferred configuration 40 to the input end 33 of a last U-shaped channel 38 in a last solar tube 6; and the output end 34 of the last U-shaped channel 38 in the last solar tube 6 forming a fluid connection to the output port 23;
  • serial linkage count may be greater than ten to provide higher temperatures; or the parallel linkage count may be greater than 4 to provide an increased solar fraction in colder climates.
  • phraseology and terminology employed herein are for the purpose of the description and should not be regarded as limiting.

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  • Photovoltaic Devices (AREA)

Abstract

L'invention porte sur un collecteur solaire à flux direct et sur un système d'eau chaude solaire, dans lesquels des liaisons à haute pression sont éliminées de façon à diminuer les coûts d'installation tandis qu'une protection contre le gel et la stagnation est assurée par un système d'évacuation à air forcé purgeant un liquide solaire à partir de points bas du trajet et d'impasses de gravité dans des installations orientées horizontalement. Une nouvelle configuration d'ailettes et un nouveau concept modulaire apportent des efficacités de fabrication, d'expédition et d'assemblage tout en produisant une souplesse de personnalisation de la configuration de collecteur.
PCT/US2013/027339 2012-02-27 2013-02-22 Collecteur solaire à flux direct WO2013130350A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/US2013/065807 WO2014066194A1 (fr) 2012-10-22 2013-10-20 Collecteur solaire à écoulement direct
US14/467,179 US20140360492A1 (en) 2012-02-27 2014-08-25 Direct flow solar collector

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
US201261603541P 2012-02-27 2012-02-27
US61/603,541 2012-02-27
US201261660446P 2012-06-15 2012-06-15
US61/660,446 2012-06-15
US201261716727P 2012-10-22 2012-10-22
US61/716,727 2012-10-22

Related Child Applications (1)

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PCT/US2013/065807 Continuation-In-Part WO2014066194A1 (fr) 2012-02-27 2013-10-20 Collecteur solaire à écoulement direct

Publications (1)

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WO2013130350A1 true WO2013130350A1 (fr) 2013-09-06

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PCT/US2013/027339 WO2013130350A1 (fr) 2012-02-27 2013-02-22 Collecteur solaire à flux direct

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US (1) US20140360492A1 (fr)
WO (1) WO2013130350A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107525291A (zh) * 2017-09-01 2017-12-29 宁波明禾新能源科技有限公司 一种太阳能热水器的连接器
CN112113354A (zh) * 2018-08-05 2020-12-22 青岛佰腾科技有限公司 一种集热器衡压管管径优化设计方法
CN115673513A (zh) * 2022-11-03 2023-02-03 浙江百立盛新能源科技有限公司 一种太阳能聚热导热器制造装置

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT508749A1 (de) * 2009-07-29 2011-03-15 Vkr Holding As Solaranlage mit mindestens zwei solarkollektoren unterschiedlicher exposition
US10094595B1 (en) * 2012-05-10 2018-10-09 Lockheed Martin Corporation Solar heat collector
US9879883B2 (en) 2012-07-07 2018-01-30 Mark Mueller High temperature direct solar thermal conversion
US20170045266A1 (en) * 2015-08-14 2017-02-16 Great American Duck Races, Inc. Dba Great American Merchandise And Events Curved solar heater
CN112728777B (zh) * 2020-12-14 2022-10-21 雨昕阳光(北京)能源科技有限公司 一种具有蓄能功能的太阳能热水器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0119046A2 (fr) * 1983-03-04 1984-09-19 The Mid Glamorgan County Council Collecteur d'énergie solaire
KR20030033800A (ko) * 2001-10-25 2003-05-01 정한식 진공 유리관 태양열 집열장치
KR200422676Y1 (ko) * 2006-04-28 2006-07-31 배덕수 태양열 온수난방기의 집열기 동파방지 구조
KR100956063B1 (ko) * 2008-04-22 2010-05-07 경희대학교 산학협력단 태양열을 이용한 온수시스템
US8100172B2 (en) * 2006-05-26 2012-01-24 Tai-Her Yang Installation adapted with temperature equalization system

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4167178A (en) * 1977-06-27 1979-09-11 Solar Energy Systems, Inc. Stationary type solar energy collector apparatus
AU538279B2 (en) * 1978-06-13 1984-08-09 Sharp K.K. Solar energy collector assembly
GR82075B (fr) * 1983-05-18 1984-12-13 Kaptan Aps
DK160218C (da) * 1987-04-06 1991-07-15 Soeby As Henry Solfangerabsorptionskoeleanlaeg
US5666818A (en) * 1995-12-26 1997-09-16 Instituto Tecnologico And De Estudios Superiores Solar driven ammonia-absorption cooling machine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0119046A2 (fr) * 1983-03-04 1984-09-19 The Mid Glamorgan County Council Collecteur d'énergie solaire
KR20030033800A (ko) * 2001-10-25 2003-05-01 정한식 진공 유리관 태양열 집열장치
KR200422676Y1 (ko) * 2006-04-28 2006-07-31 배덕수 태양열 온수난방기의 집열기 동파방지 구조
US8100172B2 (en) * 2006-05-26 2012-01-24 Tai-Her Yang Installation adapted with temperature equalization system
KR100956063B1 (ko) * 2008-04-22 2010-05-07 경희대학교 산학협력단 태양열을 이용한 온수시스템

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107525291A (zh) * 2017-09-01 2017-12-29 宁波明禾新能源科技有限公司 一种太阳能热水器的连接器
CN112113354A (zh) * 2018-08-05 2020-12-22 青岛佰腾科技有限公司 一种集热器衡压管管径优化设计方法
CN112113353A (zh) * 2018-08-05 2020-12-22 青岛佰腾科技有限公司 一种集热器衡压管间距优化设计方法
CN112113353B (zh) * 2018-08-05 2022-05-17 青岛佰腾科技有限公司 一种集热器衡压管间距优化设计方法
CN112113354B (zh) * 2018-08-05 2022-07-29 青岛佰腾科技有限公司 一种集热器衡压管管径优化设计方法
CN115673513A (zh) * 2022-11-03 2023-02-03 浙江百立盛新能源科技有限公司 一种太阳能聚热导热器制造装置

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