US20120186787A1 - Heat pipe system having common vapor rail - Google Patents
Heat pipe system having common vapor rail Download PDFInfo
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- US20120186787A1 US20120186787A1 US13/247,707 US201113247707A US2012186787A1 US 20120186787 A1 US20120186787 A1 US 20120186787A1 US 201113247707 A US201113247707 A US 201113247707A US 2012186787 A1 US2012186787 A1 US 2012186787A1
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- Prior art keywords
- heat pipe
- conduits
- sections
- evaporator
- condenser
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/0266—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes with separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
- F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
- F24F12/002—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/0275—Arrangements for coupling heat-pipes together or with other structures, e.g. with base blocks; Heat pipe cores
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D15/06—Control arrangements therefor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F12/00—Use of energy recovery systems in air conditioning, ventilation or screening
- F24F12/001—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air
- F24F12/002—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid
- F24F12/003—Use of energy recovery systems in air conditioning, ventilation or screening with heat-exchange between supplied and exhausted air using an intermediate heat-transfer fluid using a heat pump
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
- F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
- F28D2015/0216—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes having particular orientation, e.g. slanted, or being orientation-independent
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0014—Recuperative heat exchangers the heat being recuperated from waste air or from vapors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2210/00—Heat exchange conduits
- F28F2210/10—Particular layout, e.g. for uniform temperature distribution
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- 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
- Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
- Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
- Y02B30/56—Heat recovery units
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Thermal Sciences (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Geometry (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
Abstract
A heat pipe has a plurality of conduits. Each conduit has an evaporator section extending laterally from a first open end of the conduit, a condenser section extending laterally from a second open end of the conduit, and a liquid return section connected to the evaporator section at a position away from the first open end and connected to the condenser section at a position away from the second open end. The liquid return section of at least one conduit is distinct from the liquid return section of another of the conduits. A common vapor manifold extends between the first and second open ends of each of said plurality of conduits so vapors produced in the evaporator sections can flow from the first open ends through the common vapor manifold to the second open ends without flowing through the conduits.
Description
- This application claims priority to U.S. provisional application No. 61/436,076 filed Jan. 25, 2011, the entire contents of which are hereby incorporated by reference.
- The present invention relates generally to passive heat transfer devices and more particularly to heat pipes, which are closed loop systems using the high heat of evaporation/condensation associated with a phase changing working fluid to efficiently transfer large amounts of heat and which require no or only small energy input.
- Heat pipes are closed loop heat exchangers that rely on a phase change of a working fluid to absorb heat by evaporation and release heat by condensation. A liquid working fluid (e.g., water, Freon, or the like) is vaporized in the evaporator portion of a heat pipe using heat absorbed from the environment. The vapor flows into the condenser portion of the heat pipe where it is condensed, releasing heat into the environment. Liquid condensed in the condenser is returned to the evaporator (e.g., by gravity, capillary action, pump, etc.) where it is evaporated again. In use the working fluid is continuously vaporized in the evaporator portion of the heat pipe and continuously condensed in the condenser portion of the heat pipe such that heat is absorbed from the environment by the evaporator, transferred to the condenser, and then released into the environment by the condenser. This process cools the environment surrounding the evaporator and heats the environment surrounding the condenser. Heat pipes can be extremely efficient at transferring large amounts of heat and can operate with only a limited difference between the temperatures of the evaporator and condenser portions of the system. Heat pipes also require no moving parts and typically require little or no maintenance.
- One practical application for heat pipes is in de-humidification systems that pre-cool air in the inlet stream of a cooling coil (e.g., in the HVAC system for a commercial or residential building) and re-heat the outlet air stream from the cooling coil. The heat pipe can be configured to extend from one side of the cooling coil to its opposite side so the evaporator portion is in the cooling coil inlet stream and the condenser portion is on the opposite side of the cooling coil in the cooling coil outlet stream. For example, heat pipes can wrap around the sides and/or over the top of the cooling coil so the evaporator portion of the heat pipe is in the inlet stream and the condenser portion of the heat pipe is in the outlet stream. Pre-cooling the air as it enters the cooling coil allows the cooling coil to cool the air to a significantly lower temperature without using much if any additional energy. The overly cooled output air stream from the cooling coil is then heated by the condenser portion of the heat pipe system to a comfortably cool temperature. Over cooling the air in this manner increases the amount of moisture condensed from the air stream as it flows through the cooling coil. This combination of heat pipe and cooling coil provides a low cost, low maintenance dehumidification system.
- Heat pipes can also be used to recover heat that would otherwise be lost in exhaust from an HVAC system during cold weather. For example, a heat pipe can be installed in the duct system of an HVAC system so the heat pipe extends into two adjoining ducts, one of which is being used to exhaust warmer stale air from the building and the other of which is used to convey cooler fresh air from outside the building to the HVAC system. Heat from the warm exhaust is captured by evaporation of the working fluid in the part of the heat pipe exposed to the exhaust and transferred to the cool inlet air by condensation of the working fluid in the part of the heat pipe exposed to the inlet stream. Thus, heat that would otherwise be lost to the outside of the building is used to pre-heat the cool inlet air, which means less energy is required by the heater of the HVAC system to heat the fresh air to a comfortable temperature. The heat pipes can be designed so when the cooling coil is operating in warm weather heat is transferred from the relatively warm inlet air to relatively cool stale exhaust air. Using the heat pipes to recapture heat from the warm exhaust in cold weather and recapture coolness from the cool exhaust in warm weather reduces the load on the heater and cooling coil and reduces energy required by the HVAC.
- Various improvements to the prior art heat pipes are been made and will be described in the detailed description below.
- One aspect of the invention is a heat pipe. The heat pipe includes a plurality of conduits. Each conduit has an evaporator section extending laterally from a first open end of the respective conduit, a condenser section extending laterally from a second open end of the respective conduit, and a liquid return section. The liquid return section for each conduit is connected to the evaporator section at a position away from the first open end and connected to the condenser section at a position away from the second open end so the evaporator and condenser section are in fluid communication with one another through the liquid return section for flow of liquid condensed in the condenser section to the evaporator section. The liquid return section of at least one conduit is distinct from the liquid return section of another of the conduits. The heat pipe has a common vapor manifold in fluid communication with and extending between the first and second open ends of each of said plurality of conduits so vapors produced in the evaporator sections can flow from the first open ends through the common vapor manifold to the second open ends without flowing through the conduits.
- Other objects and features will in part be apparent and in part pointed out hereinafter.
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FIG. 1 is a perspective of one embodiment of a heat pipe; -
FIG. 2 is front elevation of the heat pipe; -
FIG. 3 is a right side elevation of the heat pipe with a portion of a conduit broken away to show a phase changing working fluid; -
FIG. 4 is a left side elevation of the heat pipe with a portion of a conduit broken away to show the phase changing working fluid; -
FIG. 5 is a top plan view of the heat pipe in combination with a cooling coil; -
FIG. 6 is perspective of one embodiment a heat pipe nested within another heat pipe; -
FIG. 7 is a perspective of a heat pipe having a common vapor manifold configured to wrap around the side of a cooling coil; -
FIG. 8 is a perspective of a heat pipe having evaporator sections and condenser sections configured to double back on themselves; -
FIG. 9 is a perspective of another embodiment of a heat pipe; -
FIG. 10 is a perspective of a system including a plurality of heat pipes; -
FIG. 11 is a perspective of the system illustrated inFIG. 10 in a frame with fins; -
FIG. 12 is a schematic illustrating the system ofFIGS. 10 and 11 installed in the duct system of an HVAC system; -
FIG. 13 is a perspective of another embodiment of a heat pipe; -
FIG. 14 is a top plan view of a set of heat pipes including the heat pipe illustrated inFIG. 13 ; -
FIG. 14A is a top plan view of another embodiment of set of heat pipes including the heat pipe illustrated inFIG. 13 ; and -
FIG. 15 is a schematic illustrating a system having the set of heat pipes inFIG. 14 installed in the duct system on an HVAC system. - Corresponding reference characters indicate corresponding parts throughout the drawings.
- Referring to
FIGS. 1-5 , one embodiment of a heat pipe, generally designated 101, includes a plurality ofconduits 103 containing a working fluid (e.g., water, Freon or another refrigerant), some of which exists as a vapor V and some of which exists as a liquid L, as illustrated inFIGS. 3 and 4 . Each of theconduits 103 includes anevaporator section 105 extending laterally from anopen end 107 of the conduit and acondenser section 109 extending laterally from anotheropen end 111 of the conduit. Each of the conduits also includes aliquid return section 113 for flow of liquid L condensed in thecondenser section 109 to theevaporator section 105. - As illustrated in the drawings, the
liquid return section 113 for eachconduit 103 is connected to theevaporator section 105 at a position away from theopen end 107 of the evaporator section. For example, theliquid return section 113 is suitably connected to theevaporator section 105 at an end of the evaporator section opposite theopen end 107. Theliquid return section 113 is also connected to thecondenser section 109 at a position away from theopen end 111 of the condenser section (e.g., at an end of the condenser section opposite theopen end 111 of the condenser section) so theevaporator section 105 and condenser section of eachconduit 103 are in fluid communication with one another through the respective liquid return section. Theliquid return section 113 of at least oneconduit 103 is distinct from the liquid return section of another of the conduits. As illustrated, for example, eachconduit 103 has its ownliquid return section 113, meaning the liquid return section for each conduit is distinct from the liquid return sections of all the other conduits. - The
evaporator sections 105,condenser sections 109, andliquid return sections 113 are each suitably substantially straight sections of therespective conduit 103, although this is not required to practice the invention. Thesections conduits 103 could also be formed by bending a single segment of pipe to produce thevarious sections evaporator sections 105 of theconduits 103 suitably have a horizontal orientation. At least a portion of thecondenser section 109 for eachconduit 103 is at an elevation higher than the elevation of theevaporator section 105 of therespective conduit 103. For example, as illustrated inFIG. 2 , theopen end 111 of thecondenser section 109 is suitably at an elevation above the elevation of theopen end 107 of theevaporator section 105 for each of theconduits 103. Thecondenser sections 109 are inclined downward from theiropen ends 111 so gravity assists flow of liquid L condensed in the condenser section toward theliquid return section 113. Theliquid return sections 113 can suitably have an orientation inclined downward from thecondenser sections 109 to theevaporator sections 105. In the illustrated embodiment, however, theliquid return sections 113 are substantially horizontal. Further, the degree of inclination in any of the various parts of theconduit 103 is suitably relatively slight (e.g., about 1 percent slope). Moreover, conduits that do not have any slope are within the broad scope of the invention. - Although the embodiment illustrated in the drawings has a configuration in which gravity drives or assists flow of condensed liquid L through the
heat pipe 101 to theevaporator sections 105, condensed liquid can be returned to the evaporator portion of a heat pipe without any gravity assistance and/or against gravity using various internal wicking features and/or pumps known to those skilled in the art without departing from the scope of the invention. - As illustrated in
FIGS. 1-5 , theconduits 103 are suitably generally U-shaped and have a substantially horizontal orientation. In particular, the difference in elevation between the highest part of the conduit 103 (e.g., atopenings 111 in the illustrated embodiment) and the lowest part of the conduit (e.g.,evaporator section 105 and/or at the openings 107) is suitably no more than about 10 percent of the overall length of the conduit, meaning the conduit has a substantially horizontal orientation. Theconduits 103 are arranged so they are spaced vertically from one another, as illustrated inFIG. 1 . For example, theconduits 103 are suitably stacked generally one on top of the other so they each have an identical U-shaped footprint when viewed from the top, as illustrated inFIG. 5 . Theconduits 103 may lie directly on top of one another so the top of one conduit is in contact with the bottom of another conduit within the broad scope of the invention. In the illustrated embodiment, however, theconduits 103 are retained in spaced relation from one another and fins extend vertically between the conduits. Referring toFIG. 1 , one set offins 121 is connected to theevaporator sections 105 of theconduits 103 to facilitate absorption of heat from the environment. Another set offins 123 is connected to thecondenser sections 109 of the conduit to facilitate release of heat to the environment. Thefins conduits 103 such that the conduits are embedded in the fins. The sets offins evaporator sections 105 andcondenser sections 109. Only some of thefins FIG. 1 to show the conduits better. Theliquid return sections 113 are substantially free of fins to limit heat transfer between the working fluid in the liquid return sections and the environment. - The
heat pipe 101 is suitably configured so theevaporator sections 105 are positioned on one side of aspace 131 for receiving a cooling coil 135 (FIG. 5 ) and the condenser sections are positioned on the opposite side of the space. InFIG. 5 , theheat pipe 101 is illustrated in combination with a cooling coil 135 (broadly a “cooling system”). The coolingcoil 135 is conventional except for theheat pipes 101 and need not be described or illustrated in detail. Those skilled in the art will recognize thecooling coil 135 is suitably part of a conventional air conditioning system (not shown). Theevaporator sections 105 of theheat pipe 101 collectively form an array of evaporator sections disposed in the path of air incoming to the evaporator of the cooling system for pre-cooling air before it arrives at the evaporator. Thecondenser sections 109 of theheat pipe 101 collectively form an array of condenser sections disposed in the air path downstream of the evaporator of the cooling system for re-heating overly cooled air to a temperature that is suitable for the occupants of a building cooled by the cooling system. - The
conduits 103 are suitably made of relatively long narrow tubing. For example, theconduits 103 are suitably made of tubing no larger than 1 inch tubing, more suitably no larger than ⅝ inche tubing, more suitably no larger than ½ inch tubing and can in some cases be made of tubing no larger than ⅜ inch tubing. As illustrated inFIG. 5 , theevaporator sections 105 andcondenser sections 109 are generally parallel to one another and spaced from one another by a distance D1 that is at least about 2 feet, more suitably at least about 4 feet, still more suitably in the range of about 4 to about 10 feet, and still more suitably in the range of about 6 to about 8 feet. The length L1 of theliquid return sections 113 of the conduits is suitably about equal to the distance D1. The evaporator andcondenser sections condenser sections - The overall length of the flow path through the
conduits 103 from thecondenser opening 111, through thecondenser section 109,liquid return section 113, andevaporator section 105 to theevaporator opening 107 is suitably in the range of about 50 inches to about 300 inches, more suitably in the range of about 60 to about 250 inches, more suitably in the range of about 100 to about 250 inches, more suitably in the range of about 125 to about 225 inches, and still more suitably in the range of about 150 to about 200 inches, with each of the foregoing lengths being suitable when the conduits are made from ½ inch tubing. Those skilled in the art will recognize the lengths described above for the conduits and the various parts thereof are fairly long flow paths for a heat pipe made of ½ inch tubing. Again, if larger tubing is used, the lengths can be increased even more without experiencing a significant loss in efficiency. For example, when the tubing is ⅝ inch diameter tubing, the overall length of the flow path through theconduits 103 from the condenser opening, through thecondenser section 109,liquid return section 113, andevaporator section 105 to theevaporator opening 107 is suitably in the range of about 100 inches to about 500 inches, more suitably in the range of about 200 inches to about 500 inches, and still more suitably in the range of about 200 inches to about 400 inches. As another example, when the tubing is ⅜ inch diameter tubing, the overall length of the flow path through the conduits is suitably in the range of about 12 inches to about 200 inches, more suitably in the range of about 12 inches to about 100 inches, and still more suitably in the range of about 12 inches to about 60 inches, and still more suitably in the range of about 24 inches to about 60 inches. As still another example, when the tubing is in the range of about 5/16 to 7 mm diameter tubing, the overall length of the flow path through the conduits is suitably in the range of about 12 inches to about 50 inches. It costs substantially more to make heat pipes using larger diameter tubing than it does with smaller diameter tubing, so it is desirable to use the smallest diameter tubing that does not result in an unacceptably inefficient heat pipe. But the improvements described herein can also improve the efficiency for heat pipes in which the dimensions for the lengths and diameters of the conduits vary from those listed above within the scope of the invention. - The
heat pipe 101 also has acommon vapor manifold 151 in fluid communication with the open ends 107, 111 of each of said plurality ofconduits 103 and extending between the open ends of the conduits so vapors V produced in theevaporator sections 105 can flow from the open ends 107 of theevaporator sections 105 through the common vapor manifold to open ends 111 of thecondenser sections 109 without flowing through the conduits. Because the vapor V can return to thecondenser sections 109 without flowing through the conduit, there is much less resistance to flow of liquid from the condenser sections to theevaporator sections 105 because counterflow of vapor and liquid L in theconduits 103 is greatly reduced or eliminated. The common vapor manifold can have many different configurations within the broad scope of the invention. As illustrated, thecommon vapor manifold 151 is an inverted U-shaped conduit having a generally uprightevaporator leg 153, a generallyupright condenser leg 155, and a generallyhorizontal vapor passage 157 connecting the legs to one another so they are in fluid communication with one another through the vapor passage. Theevaporator leg 153 and thecondenser leg 155 are suitably substantially straight (e.g., vertical) sections of tubing. Thevapor passage 157 is also a substantially straight section of tubing having the same diameter as thelegs vapor passage 157 can be connected to thelegs vapor manifold 151 using a 90 degree elbow connection or other suitably connecting means. Similarly, a single piece of tubing can be bent into an inverted U-shape to form thecommon vapor manifold 151 within the scope of the invention. - The tubing for the
common vapor manifold 151 suitably has a diameter that is larger than the diameter of theconduits 103, as in the illustrated embodiment. In one embodiment, theconduits 103 can be made from 0.5 inch or ⅜ inch copper tubing while thecommon vapor manifold 151 is made from larger diameter ⅝ inch or 0.5 inch copper tubing, respectively. However, the cross sectional flow area of thevapor manifold 151 can be much larger than described above or be the same or smaller than the cross sectional flow area aconduit 103 within the scope of the invention. It is also understood theconduits 103 andmanifold 151 are not required to have any particular cross sectional shape within the broad scope of the invention. - The open ends 107 of the
evaporator sections 105 open into theevaporator leg 153 of themanifold 151. The open ends 111 of thecondenser sections 109 open into thecondenser leg 155 of themanifold 151. In the illustrated embodiment, theevaporator leg 153 of thecommon vapor manifold 151 extends to a position that is higher in elevation than the highest of the open ends 107 of theevaporator sections 105. For example, the manifold 151 suitably extends a distance H1 (FIG. 3 ) above the highest of the open ends 107 of theevaporator sections 105. Likewise, thecondenser leg 155 leg of thecommon vapor manifold 151 extends to a position that is higher in elevation than the highest of the open ends 111 of thecondenser sections 109. Thevapor passage 157 connects to theevaporator leg 153 at an elevation above the highest of the open ends 107 of theevaporator sections 105 and connects to thecondenser leg 155 at an elevation above the highest of the open ends 111 of thecondenser sections 109. Thevapor passage 157 of the illustrated embodiment is also at an elevation that is higher than the highest of the generallyhorizontal conduits 103. An opening 137 (FIG. 1 ) for receiving the coolingcoil 135 as it slides relative to theheat pipe 101 into thespace 131 is formed between thelegs vapor passage 157 of the vapor manifold. Like theliquid return sections 113 of theconduits 103, thecommon vapor manifold 151 is suitably substantially free of fins to limit heat transfer between theheat pipe 101 and the environment except at the evaporator andcondenser sections - When the cooling
coil 135 is on, air flows into the cooling coil and is cooled. Meanwhile, theevaporator sections 105 of theheat pipe 101 are exposed to the relatively warm air flowing into the coolingcoil 135, represented inFIG. 5 by arrows A. Heat from the warm inlet air is absorbed by thefins 121 andevaporator sections 105. This process cools the air before it reaches the coolingcoil 135. The absorbed heat causes liquid phase working fluid L to evaporate in theevaporator sections 105. Vapors V produced in theevaporator sections 105 flow into theevaporator leg 153 of thevapor manifold 151 through theopenings 107, up to thevapor passage 157, across the vapor passage to thecondenser leg 155, down into thecondenser leg 155, and then into thecondenser sections 109 through theopenings 111. Because the air was pre-cooled by theevaporator sections 105 before reaching thecooling coil 135, the cooling coil can cool the air down to a temperature significantly below the temperature to which it would be cooled if there were no heat pipe present, but with little or no additional energy consumption. Because the air is cooled by the coolingcoil 135 to this lower temperature, significantly more water vapor is condensed and removed from the air flowing through the cooling coil. - As this is occurring, the
condenser sections 109 are exposed to the cold outlet air stream from the coolingcoil 135, represented by arrows B inFIG. 5 . As the cold air outlet stream flows through thefins 123, it absorbs heat released from thecondenser sections 109 of theheat pipe 101 through condensation of the working fluid in the condenser sections. The interaction of the cold air from the coolingcoil 135 and thecondenser sections 109 warms the air to a comfortable temperature and produces condensation of the working fluid in the condenser sections of theheat pipe 101. The liquid L condensed in the condenser sections flows from thecondenser sections 109 to theevaporator sections 105 through the respectiveliquid transfer sections 113. The air warmed by thecondenser sections 109 has lower relative humidity than it would without theheat pipe 101. Moreover, the heat pipe dehumidifies the air with little or no additional energy consumption. - Because the
common vapor manifold 151 allows vapors evaporated in the evaporator sections to flow to the condenser sections through the vapor manifold, there is less resistance to flow of liquid L through theconduits 103 to theevaporator sections 105 and there is less resistance to flow of vapor V to thecondenser sections 109 because of the relative absence of counter flowing vapor and liquid in any section of theheat pipe 101. This increases the speed at which vapor V and liquid L flows through theheat pipe 101 and thereby allows theheat pipe 101 to perform efficiently even when the overall length of theconduits 103 is relatively long and the inner diameter of the conduits is relatively small (e.g., as described above). Moreover, theheat pipe 101 can perform efficiently with a relatively low charge of working fluid. For example, the charge of working fluid can suitably be in the range of about 15 percent to about 60 percent, more suitably in the range of about 15 percent to about 45 percent, more suitably in the range of about 15 percent to about 30 percent, and still more suitably in the range of about 20 percent to about 30 percent. In other examples, the interior surface of the tubing has grooves (which those skilled in the art will recognize aids flow of liquid through the tubing by capillary action) and the charge of working fluid can suitably be in the range of about 20 percent to about 50 percent, more suitably in the range of about 20 percent to about 45 percent, more suitably in the range of about 25 percent to about 40 percent, and still more suitably in the range of about 25 to 35 percent. Grooved tubing typically works better with a slightly larger charge of working fluid compared to tubing that is smooth on the inside. As further examples, the charge of working fluid is suitably less than about 40 percent, still more suitably less than about 35 percent, and still more suitably no more than about 30 percent. As those skilled in the art know, the amount of charge is the weight of working fluid (liquid+vapor) in the system expressed as a percentage of the weight of liquid phase working fluid that would completely fill the interior volume of the heat pipe. It is understood that larger charges than those specified above may be used within the broad scope of the invention. Accordingly, the performance of theheat pipe 101 can be equivalent to conventional heat pipe having significantly more expensive larger diameter tubing for the conduits and requiring a higher volume of working fluid. It is understood the improvements described herein can also improve efficiency of the heat pipes with the charge of working fluid varies from the amounts described above without departing from the scope of the invention. - As illustrated in
FIG. 1 , thesystem 101 can include avalve 161 installed in thecommon vapor manifold 151 for selectively reducing flow of vapor through the common vapor manifold. Thevalve 161 is suitably moveable (e.g., manually or via an electronic control system, not shown) between first and second operating positions such that there is relatively less resistance to flow of vapor through thecommon vapor manifold 151 in the first position (e.g., a fully open position) and relatively more resistance to flow of vapor through the common vapor manifold in the second position (e.g., a fully closed position). Thus, the valve provides the ability to adjust the efficiency of the system from a higher heat transfer efficiency for better dehumidification to a lower heat transfer efficiency. It may be desirable to operate in a lower heat transfer efficiency mode when the air flowing into the system is already relatively dry and less dehumidification is desired. Thevalve 161 is optional. Although the valve illustrated inFIG. 1 is a manually operated ball valve, it is understood it will often be desirable to use an electronically controlled valve so the valve can be operated from a remote position (e.g., by a processor). If desired thevalve 161 can be positionable at one or more additional operating positions intermediate the first and second positions (e.g., an infinite number of positions between a fully closed position and a fully open position) to provide greater control over the amount of fluid flowing through thecommon vapor manifold 151. -
FIG. 6 illustrates another embodiment of a heat pipe system, generally designated 101′. Thissystem 101′ includesmultiple heat pipes 101 nested together so they work in tandem. InFIG. 6 , there are twoheat pipes 101 in thesystem 101′ and each of the two heat pipes is exactly the same as theheat pipe 101 inFIG. 1 except one of the heat pipes is slightly smaller than the other so it can nest inside the other. It is understood there could be more than two heat pipes nested together without departing from the scope of the invention. Thesystem 101′ operates in a manner that is substantially the same as thesystem 101 inFIG. 1 , except thesystem 101′ has a greater capacity to transfer heat because of themultiple heat pipes 101 working in tandem. -
FIG. 7 illustrates another embodiment of a heat pipe system, generally designated 101″. This heat pipe is substantially identical to theheat pipe 101 illustrated inFIG. 1 , except as noted. Theheat pipe 101″ has acommon vapor rail 151″ having avapor passage 157″ configured to extend from the top of theevaporator leg 153 to the top of thecondenser leg 155 along a path that matches the U-shaped contour of theconduits 103. Accordingly, a portion of thecommon vapor manifold 151″ is on the same side of theheat pipe 101″ as at least one (e.g., all) of theliquid return sections 113 of theconduits 103. As illustrated inFIG. 7 , thevapor passage 157″ extends from the top of theevaporator leg 153 along and above theevaporator section 105,liquid return section 113, andcondenser section 109 of the uppermost conduit. Thevapor passage 157″ is configured so it wraps around the same side of the coolingcoil 135 as the conduits. This allows theheat pipe 157″ to be installed around the coolingcoil 135 without requiring thevapor rail 151″, and in particular thevapor passage 157″ thereof, to be passed over the top of the cooling coil. This can be desirable, for example, when the coolingcoil 135 is already installed and obstructions would prevent or make it difficult to move thevapor passage 157 for the embodiment illustrated inFIG. 1 over the top of the cooling coil to wrap theconduits 103 around the sides of the cooling coil during installation of the heat pipe. Theheat pipe 101″ illustrated inFIG. 7 can also be nested with one or more similar heat pipes in a manner analogous to the nesting illustrated inFIG. 6 . - Another embodiment of a heat pipe, generally designated 101″′, is illustrated in
FIG. 8 . Thisheat pipe 101″′ is substantially identical to theheat pipe 101 illustrated inFIG. 1 except as noted. Theconduits 103″′ of thisheat pipe 101″′ have evaporatorsections 105″′ andcondenser sections 109″′ that double back on themselves so the open ends 107″′, 111′ are at the same end of the system as theliquid return sections 113 of the conduits. The overall shape of theconduits 103″′ is that of a horizontal U, with the doubled back evaporator andcondenser sections 105″′, 109″′ forming the sides of the U and theliquid return sections 113″′ forming the bottom of the U. The overall length of theconduits 103″′ is suitably the same as the lengths of theconduits 103 described above. However, doubling back of theevaporator sections 105″′ andcondenser sections 109 requires the working fluid to flow double the length of the cooling coil to flow through the condenser section and through the evaporator section. Accordingly, theheat pipe 101″′ inFIG. 8 is particularly suitable for small and medium sized cooling coils. Thecommon vapor manifold 151″′ is substantially similar to thevapor manifold 151 described above, but it is at the same end of theheat pipe 101″′ as theliquid return sections 113 of theconduits 103″′. Accordingly, similar to the embodiment illustrated inFIG. 7 , there is no need to pass thecommon vapor rail 151″′ over the top of the coolingcoil 135 during installation. - The
evaporator sections 105″′ andcondenser sections 109″′ are suitably horizontal (e.g., perfectly horizontal or substantially free of any incline), as illustrated. Eachevaporator section 105″′ is suitably doubled back in such a way that theend 107″′ of the evaporator section is spaced inward from the end of theliquid return section 113 connected to the evaporator section. Eachcondenser section 109″′ is suitably doubled back in such a way that theend 111″′ is spaced outward from the end of the liquid return section that is connected to the condenser section. Accordingly, when theheat pipe 101″′ is installed for use withcooling coil 135, eachevaporator section 105″′ includes afirst portion 105 a″′ adjacent theopening 107″′ and asecond portion 105 b″′ remote from theopening 107″′ and upstream of the first portion in the cooling coil intake stream. Likewise, eachcondenser section 109″′ includes afirst portion 109 a″′ adjacent theopening 111″′ and asecond portion 109 b″′ remote from theopening 111″′ that is upstream of the first portion in the flow out of the cooling coil. Theevaporator leg 153″′ of thecommon vapor manifold 151″′ is positioned inside theportions 105 b″″ of theevaporator sections 105″′ that are remote from the open ends 107″′. Thecondenser leg 155″′ of thecommon vapor manifold 151″′ is positioned outside theportions 109 b″′ of thecondenser sections 109″′ that are remote from the open ends 111″′. When theheat pipe 101″′ is in use, this arrangement causes temperature gradients to form in theconduits 103″′ that pump the working fluid through theheat pipe 101″′. In particular,evaporator portion 105 b″′ will be warmer thanportion 105 a″′ andcondenser portion 109 a″′ will be warmer thanportion 109 b″′. The thermal gradients pump working liquid L from the warmer portion toward the cooler portion. - Another embodiment of a heat pipe, generally designated 201, is illustrated in
FIG. 9 . Except as noted, thisheat pipe 201 is substantially identical in construction to theheat pipe 101 described above. The heat pipe includes acommon vapor manifold 251 that is analogous to the manifold 151 describe above. However, theconduits 203 of thisheat pipe 201 are substantially straight all the way from oneend 107 to the other 111 instead of U-shaped. Consequently, theends conduits 203 are spaced much farther from one another and thevapor manifold 251 has a muchlonger vapor passage 257 than is the case for theheat pipe 101. Theentire vapor manifold 251, including theevaporator leg 253,condenser leg 255, andvapor passage 257, and theconduits 203 are oriented on a common plane. In this embodiment, theevaporator sections 205 are in-line with thecondenser sections 209. Theheat pipe 201 includes a first set offins 221 on theevaporator sections 205 and a second set offins 223 on thecondenser sections 209. Only some of thefins FIG. 6 . Theliquid return section 213 is a short segment of theconduit 203 that is substantially free of fins positioned between the evaporator andcondenser sections conduits 203 andvapor passage 257 are substantially horizontal in orientation. It is noted however theconduits 203 could be inclined slightly downward from the condenser sections to the evaporator sections to provide gravity assistance for liquid flow from the condenser sections toward the evaporator sections within the scope of the invention. - One embodiment of
system 271 including a plurality of theheat pipes 201 is illustrated inFIGS. 10 and 11 . Thesystem 271 is suitable for transporting heat between two different and parallel ducts in a ventilation system and includes a frame 273 (FIG. 11 ) and a plurality of theheat pipes 201 supported by the frame. Theheat pipes 201 are arranged relative to one another so anarray 275 ofevaporator sections 205 is formed on one side of the system and anarray 281 ofcondenser sections 209 is formed on the other side of the system. As illustrated inFIG. 10 , for example, theheat pipes 201 are arranged so theconduits 203 of the plurality of heat pipes are parallel to one another. Further, theevaporator sections 205 of theheat pipes 201 are in side-by-side relation to one another in theevaporator array 275 and thecondenser sections 209 are also in side-by-side relation to one another in thecondenser array 281. Thefins 221 in the evaporator array 275 (FIG. 11 ) are spaced from thefins 223 in thecondenser array 209 by agap 225 aligned with theliquid return sections 213 of theconduits 203. Thefins adjacent heat pipes 201, as illustrated inFIG. 11 . - The
system 271 can be installed in theduct system 291 of an HVAC (not shown) as illustrated schematically inFIG. 12 . The side having theevaporator array 275 is installed in aninlet duct 293 conveying exterior air toward the HVAC. The side having thecondenser array 281 is installed in anadjacent duct 295. Air in theducts system 271 transfers heat from relatively warm air being taken into the HVAC system from outside the building through one of theducts 293 to relatively cooler stale air from inside the building that is being exhausted to outside the building by the HVAC system through theother duct 295. This saves energy by pre-cooling the intake air before it reaches the cooling coil using the already cooled stale air being exhausted by the HVAC. - In winter, the
system 271 can be operated in heat recovery mode by reversing the direction of heat transfer through theheat pipes 201. For example, the stale air from inside is now being vented to the exterior through theduct 295 is now relatively warmer while colder fresh air from the exterior of the building is conveyed to the HVAC through theadjacent duct 293. Because of the reversal of the direction of the temperature gradient between the sides of thesystem 271, what was theevaporator array 275 in the summer now functions as a condenser array and what was thecondenser array 281 in the summer now functions as an evaporator array. The warm exhaust air flowing through theexhaust duct 295 evaporates the working fluid in theevaporator array 281 while the colder air in theinlet duct 293 condenses the working fluid in thecondenser array 275. The heat captured from the warmer exhaust air by evaporation of the working fluid is transferred to the other side of theheat pipe system 271 where it pre-heats the colder inlet air before it arrives at the HVAC. Consequently, significantly less energy is required to heat the colder incoming air than would be required without theheat pipe system 271. - Significantly, no tilting mechanism is required to reverse flow of the liquid phase working fluid through the
heat pipe system 271. This is contrary to some prior art heat pipe based heat recovery modules in which a complicated tilting system and more costly flexible ducts are needed to adjust the inclination of the conduits and use gravity to overcome resistance to flow of the liquid phase working fluid associated with counterflowing vapors in the conduits. Instead, whenever thecondenser array 275 is in a relatively warmer environment and theevaporator array 281 is in a relatively cooler environment, the flow of the working fluid through thesystem 271 automatically reverses and the condenser sections function as evaporator sections while the evaporator sections functions as condenser sections. This is because thecommon vapor manifold 251 sufficiently reduces resistance to flow of liquid phase working fluid in theconduits 203 that natural liquid pumping forces produced by the thermal gradient are sufficient to produce flow of liquid between thecondenser array 275 and evaporator array without requiring any gravitationally induced flow in the conduits. Accordingly, theconduits 203 can remain in the same horizontal orientation for operation in summer and winter. - Another embodiment of a heat pipe, generally designated 301, is illustrated in
FIG. 13 . The heat pipe includes first and second sets ofconduits conduit 303 in the first andsecond sets conduits 103 of theheat pipe 101 inFIG. 1 . Theconduits 303 are suitably all substantially straight, although this is not required to practice the invention. Theconduits 303 of thefirst set 303 a are in generally side-by-side relation with the conduits of thesecond set 303 b and are spaced laterally from the conduits of the second set by agap 305. Theheat pipe 301 includes twovapor manifolds 311′, 311″ each of which includes a pair oflegs vapor passage 321 extending between and in fluid communication with the legs. The legs and vapor passages of the first manifold are designated with a single prime (′) after the reference number while the legs and vapor passage of the second manifold are designated with a double prime (″) after the reference number. - The
first leg 315′ of thefirst manifold 311′ is at one end of theconduits 303 of thefirst set 303 a while thesecond leg 317′ of the first manifold is at the opposite end of the conduits of thesecond set 303 b. Thevapor passage 321′ extends across thegap 305 and between thelegs 315′, 317′. Thevapor passage 321′ is in fluid communication with thelegs 315′, 317′ and allows vapor to flow through the manifold 311′ between the end of theconduits 303 of thefirst set 303 a and the ends of the conduits of thesecond set 303 b on the opposite side of theheat pipe 301 without flowing through any of the conduits of the first or second sets. Thesecond vapor manifold 311″ is substantially identical to the first 311′ except that itslegs 315″, 317″ are connected to the ends of theconduits 303 opposite the ends to which thelegs 315′, 317′ of thefirst manifold 311′ are connected. Thevapor passages 321′, 321″ of themanifolds 311′, 311″ are suitably substantially straight and criss-cross one another as they extend over the top of thegap 305. - The
heat pipe 301 is suitable for use in a heat transfer system used to transfer heat between two different ducts of a ventilation system. Although theheat pipe 301 can be the only heat pipe in the ventilation system within the scope of the invention, it is possible to combine theheat pipe 301 with various other heat pipes to create a set of heat pipes that work together in the ventilation system. For example,FIG. 14 is a top plan view of a set of heat pipes that can be supported by theframe 273 of the heat transfer system illustrated inFIG. 11 instead of the sixheat pipes 201 in that embodiment. There are four heat pipes inFIG. 14 . Thefirst heat pipe 301 is the heat pipe illustrated inFIG. 13 . Thesecond heat pipe 401 is substantially similar to theheat pipe 301 illustrated inFIG. 13 except that it is dimensioned to nest with thefirst heat pipe 301. As illustrated inFIG. 14 , the conduits of thesecond heat pipe 401 are positioned in thegap 305 between the first andsecond sets first heat pipe 301. The third andfourth heat pipes 201 inFIG. 14 are each substantially identical to theheat pipe 201 illustrated inFIG. 9 and described above. The conduits for the third and fourth heat pipes are each positioned in the gap between the conduits of the first and second set for thesecond heat pipe 401. It is understood that another heat pipe similar to theheat pipe 301 could be nested within thesecond heat pipe 401 instead of or in addition to the third andfourth heat pipes 201 inFIG. 14 . - As illustrated schematically in
FIG. 15 , aheat transfer system 571 including theframe 273 described above supports the fourheat pipes FIG. 14 so the conduits extend from a position within thefirst duct 293 to a position within thesecond duct 295 different from the first duct in a manner similar to what is illustrated inFIG. 12 . However, in contrast to the embodiment illustrated inFIG. 12 , the airflow A, B in theducts FIG. 15 can provide significant advantages when there is parallel flow. When theheat transfer system 571 is used in parallel flow situations as illustrated inFIG. 15 , the heat pipes operate more efficiency because vapors are exchanged between the first and second sets ofconduits 303 forheat pipe 301 andheat pipe 401. - Without exchange of working fluid between the upstream and downstream heat pipes in a parallel flow situation, as illustrated in
FIG. 15 , the evaporator and condenser sections of the heat pipe on the upstream side would be exposed to a relatively large temperature difference. Each heat pipe farther downstream would be exposed to a smaller temperature difference because the of heat already transferred between the two air streams by the one or more heat pipes farther upstream before the air arrives at the downstream heat pipe. Further, the heat pipes on the downstream end of the system may operate inefficiently because of the smaller temperature difference. - On the other hand, in the
heat pipes system 571 illustrated inFIGS. 14 and 15 vapor flows through the manifolds 351 from the warmer end of the system in eachduct heat pipes -
FIG. 14A is a top plan view of another set of heat pipes that can be supported by theframe 273 of the heat transfer system illustrated inFIG. 8 instead of the sixheat pipes 201 in that embodiment. There are three heat pipes inFIG. 14A . Thefirst heat pipe 301 is the heat pipe illustrated inFIG. 13 . The second andthird heat pipes heat pipe 301 illustrated inFIG. 13 except thesecond heat pipe 401 is dimensioned to nest with thefirst heat pipe 301 and thethird heat pipe 501 is dimensioned to nest within the second heat pipe. The heat pipes illustrated inFIG. 14A operate in a similar manner to those illustrated inFIG. 14 except the vapor manifolds of thethird heat pipe 501 also allow vapor exchange to occur which can further augment efficiency of a heat transfer system using theheat pipes - It is also noted that any of the vapor manifolds described for any of the embodiments described herein can optionally include a valve similar to the
valve 161 illustratedFIG. 1 and described above to reduce the capacity of the heat pipes. Again, the valves can be electronically actuated valves (e.g., solenoid valves) to facilitate control of the valve by a processor, although the valve inFIG. 1 is illustrated as a manually operated ball valve. - When introducing elements of the ring binder mechanisms herein, the articles “a”, “an”, “the” and “said” are intended to mean that there are one or more of the elements. The terms “comprising”, “including” and “having” and variations thereof are intended to be inclusive and mean that there may be additional elements other than the listed elements. Moreover, the use of “forward” and “rearward” and variations of these terms, or the use of other directional and orientation terms, is made for convenience, but does not require any particular orientation of the components.
- As various changes could be made in the above without departing from the scope of the invention, it is intended that all matter contained in the above description and shown in the accompanying drawings shall be interpreted as illustrative and not in a limiting sense.
Claims (26)
1. A heat pipe comprising:
a plurality of conduits, each conduit including an evaporator section extending laterally from a first open end of the respective conduit, a condenser section extending laterally from a second open end of the respective conduit, and a liquid return section, the liquid return section for each conduit being connected to the evaporator section at a position away from the first open end and connected to the condenser section at a position away from the second open end so the evaporator and condenser section are in fluid communication with one another through the liquid return section for flow of liquid condensed in the condenser section to the evaporator section, the liquid return section of at least one conduit being distinct from the liquid return section of another of the conduits; and
a common vapor manifold in fluid communication with and extending between the first and second open ends of each of said plurality of conduits so vapors produced in the evaporator sections can flow from the first open ends through the common vapor manifold to the second open ends without flowing through the conduits.
2. A heat pipe as set forth in claim 1 wherein the vapor manifold comprises first and second legs, the first open ends of said plurality of conduits opening into the first leg and the second open ends of said plurality of conduits opening into the second leg, the manifold further comprising a vapor passage connecting the first and second legs to one another for flow of vapors evaporated in the evaporator sections to the condenser sections through the common vapor manifold.
3. A heat pipe as set forth in claim 3 wherein said plurality of conduits are arranged so they are spaced apart vertically from one another, the first leg of the common vapor manifold extends to a position that is higher in elevation than the highest of the first open ends, and the second leg of the common vapor manifold extends to a position that is higher in elevation than the highest of the second open ends.
4. A heat pipe as set forth in claim 3 wherein the vapor passage connects to the first leg of the common vapor manifold at an elevation above the highest of the first open ends and the vapor passage connects to the second leg at an elevation above the highest of the second open ends.
5. A heat pipe as set forth in claim 1 wherein said plurality of conduits are arranged so they are spaced apart vertically from one another and the common vapor manifold has an inverted U-Shape.
6. A heat pipe as set forth in claim 1 wherein the evaporator sections have a horizontal orientation.
7. A heat pipe as set forth in claim 1 wherein the condenser sections are inclined downward from the second open ends.
8. A heat pipe as set forth in claim 1 wherein said plurality of conduits are made of tubing no larger in diameter than ½ inch tubing.
9. A heat pipe as set forth in claim 8 wherein the length of each of said plurality of conduits is in the range of about 100 to about 250 inches.
10. A heat pipe as set forth in claim 1 wherein the length of each of said plurality of conduits is in the range of about 100 to about 250 inches.
11. A heat pipe as set forth in claim 1 wherein the second end of each of said plurality of conduits is at an elevation that is higher than an elevation of the first end of the respective conduit.
12. A heat pipe as set forth in claim 1 wherein the conduits are U-Shaped and the evaporator sections have a horizontal orientation.
13. A heat pipe as set forth in claim 1 wherein the conduits are substantially straight.
14. A heat pipe system comprising a frame and a plurality of heat pipes as set forth in claim 13 supported by the frame, the heat pipes being arranged relative to one another so the evaporator sections of the heat pipe conduits are positioned to form an array of evaporator sections on a first side of the frame and the condenser sections of the heat pipe conduits are positioned to form an array of condenser sections on a second side of the frame opposite the first side of the frame.
15. A heat pipe system as set forth in claim 14 further comprising a plurality of fins in thermal communication with the heat pipe conduits, the fins including a first set of fins in the array of evaporator sections and a second set of fins in the array of condenser sections, the first and second sets of fins being spaced from one another.
16. A heat pipe system as set forth in claim 14 installed in a duct system of an HVAC system, wherein the array of evaporator sections is in a first duct of the duct system and the array of condenser sections is in a second duct of the duct system, one of the first and second ducts leading to an inlet of the HVAC system and the other of the first and second ducts extending from an outlet of the HVAC system.
17. A heat pipe as set forth in claim 1 further comprising fins connected to the conduits in the evaporator section to facilitate heat transfer and fins connected to the conduit in the condenser section to facilitate heat transfer, the liquid return section and common vapor manifold being free of fins.
18. A heat pipe as set forth in claim 1 further comprising a working fluid contained in the conduits and common vapor manifold.
19. A heat pipe as set forth in claim 19 wherein the heat pipe contains no more than a 35% charge of the working fluid.
20. A heat pipe as set forth in claim 1 in combination with a cooling coil, the evaporator sections of the conduits being disposed in the path of air flowing into the cooling coil and the condenser sections of the conduits being disposed in the path of air downstream of the cooling coil.
21. A heat pipe as set forth in claim 1 in combination with another substantially identical heat pipe nested within the heat pipe.
22. A heat pipe as set forth in claim 1 wherein the common vapor manifold has a U-shaped configuration and at least a portion of the common vapor manifold is on the same side of the heat pipe as at least one of the liquid return sections of the conduits.
23. A heat pipe as set forth in claim 1 wherein the evaporator sections and condenser sections are configured so they are doubled back on themselves.
24. A heat pipe as set forth in claim 23 wherein the common vapor manifold has an inverted U-shape and is on the same side of the heat pipe as the liquid return sections of the conduits.
25. A heat pipe as set forth in claim 23 wherein the conduits have a horizontal U-shaped configuration and the common vapor manifold has an evaporator leg adjacent and connected to the evaporator sections, a condenser leg adjacent and connected to the condenser sections, and a vapor passage extending between the evaporator leg and condenser leg, the evaporator leg being positioned inside a portion of the evaporator sections of the conduits and the condenser leg being positioned outside a portion of the condenser sections.
26. A heat pipe as set forth in claim 1 further comprising a valve moveable between first and second operating positions, the valve producing relatively less resistance to flow of vapor through the common vapor manifold in the first position and relatively more resistance to flow of vapor through the common vapor manifold in the second position.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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US13/247,707 US20120186787A1 (en) | 2011-01-25 | 2011-09-28 | Heat pipe system having common vapor rail |
PCT/US2012/022218 WO2012103009A2 (en) | 2011-01-25 | 2012-01-23 | Heat pipe system having common vapor rail |
SG2013050463A SG191774A1 (en) | 2011-01-25 | 2012-01-23 | Heat pipe system having common vapor rail |
Applications Claiming Priority (2)
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US201161436076P | 2011-01-25 | 2011-01-25 | |
US13/247,707 US20120186787A1 (en) | 2011-01-25 | 2011-09-28 | Heat pipe system having common vapor rail |
Publications (1)
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US20120186787A1 true US20120186787A1 (en) | 2012-07-26 |
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US13/247,714 Abandoned US20120186785A1 (en) | 2011-01-25 | 2011-09-28 | Heat pipe system having common vapor rail for use in a ventilation system |
US13/247,707 Abandoned US20120186787A1 (en) | 2011-01-25 | 2011-09-28 | Heat pipe system having common vapor rail |
Family Applications Before (1)
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US13/247,714 Abandoned US20120186785A1 (en) | 2011-01-25 | 2011-09-28 | Heat pipe system having common vapor rail for use in a ventilation system |
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US10281220B1 (en) * | 2016-08-19 | 2019-05-07 | ZT Group Int'l, Inc. | Heat sink with vapor chamber |
US20190316803A1 (en) * | 2018-04-13 | 2019-10-17 | Mitek Holdings, Inc. | Heat exchanger |
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US11859850B2 (en) | 2018-04-13 | 2024-01-02 | Heat-Pipe Technology, Inc. | Heat exchanger |
US11598550B2 (en) * | 2018-06-05 | 2023-03-07 | Brunel University London | Heat pipe thermal transfer loop with pumped return conduit |
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US11892239B2 (en) * | 2020-05-12 | 2024-02-06 | Shinko Electric Industries Co., Ltd. | Loop-type heat pipe including an evaporator, first and second condensers, a liquid pipe connecting the evaporator to the first and second condensers, and first and second vapor pipes connecting the evaporator to the first and second condensers |
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Also Published As
Publication number | Publication date |
---|---|
US20120186785A1 (en) | 2012-07-26 |
WO2012103009A2 (en) | 2012-08-02 |
WO2012103009A3 (en) | 2012-11-22 |
SG191774A1 (en) | 2013-08-30 |
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Legal Events
Date | Code | Title | Description |
---|---|---|---|
AS | Assignment |
Owner name: HEAT-PIPE TECHNOLOGY, INC., FLORIDA Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:DINH, KHANH;DINH, THANG;REEL/FRAME:029386/0587 Effective date: 20120228 |
|
STCB | Information on status: application discontinuation |
Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION |