US3880230A - Heat transfer system - Google Patents

Heat transfer system Download PDF

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Publication number
US3880230A
US3880230A US366193A US36619373A US3880230A US 3880230 A US3880230 A US 3880230A US 366193 A US366193 A US 366193A US 36619373 A US36619373 A US 36619373A US 3880230 A US3880230 A US 3880230A
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United States
Prior art keywords
heat
recited
transformer
working fluid
medium
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Expired - Lifetime
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US366193A
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English (en)
Inventor
Richard L Pessolano
Robin B Rhodes
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Isothermics Inc
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Isothermics Inc
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Priority to US366193A priority Critical patent/US3880230A/en
Priority to CA186,008A priority patent/CA982533A/en
Priority to JP49014622A priority patent/JPS5016154A/ja
Priority to FR7415331A priority patent/FR2231929B1/fr
Priority to DE2425745A priority patent/DE2425745C3/de
Priority to US05/478,982 priority patent/US3994336A/en
Application granted granted Critical
Publication of US3880230A publication Critical patent/US3880230A/en
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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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • F28D21/0005—Recuperative heat exchangers the heat being recuperated from exhaust gases for domestic or space-heating systems
    • F28D21/0008—Air heaters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H6/00—Combined water and air heaters
    • 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
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S505/00—Superconductor technology: apparatus, material, process
    • Y10S505/825—Apparatus per se, device per se, or process of making or operating same
    • Y10S505/90—Heat exchange
    • Y10S505/901—Heat pipe

Definitions

  • the present heat transfer system comprises a heat source; a heat pipe; a thermal transformer in thermal contact with said heat pipe and proximately disposed to said heat source; and a first chamber containing a medium with defined heat transfer characteristics. said chamber thermally coupled to said heat pipe; whereby a uniform heat transfer from said heat source to said medium is obtained.
  • the heat pipe can be utilized to significantly increase the efficiency of heat transfer. thereby obtaining a resultant minimization of undesired heat dissipation.
  • the heat pipe can transmit thermal energy at rates that are several hundred times greater than that of the best solid conductors, i.e.. silver. copper and gold. Additionally, a much lower power to weight ratio is attained in the use of the heat pipe.
  • This device is simple. has no moving parts. is inexpensive to manufacture. has a long if not indefinite life. and can be operated over an extended range oftemperatures.
  • the device is more accurately described as a miniaturized, hermetically sealed evaporating and condensing system.
  • the primary object of the present invention is to define at least one significant commercial application for this promising device.
  • the heat pipe consists essentially of a sealed container. a capillary wick structure which is secured to the interior surface of the container, and a quantity of working fluid sufficient to saturate the wick structure.
  • the container is sealed while under a vacuum.
  • the container is sealed under a vacuum.
  • the working fluid is in equilibrium with its own vapor.
  • any application of heat to any external surface of the heat pipe will cause an instantaneous evaporation of the working fluid near the heated surface.
  • the latent heat of vaporization is absorbed by the vapor.
  • the latent heat of vaporization is essentially the ratio of (a) the heat absorbed during the change of phase from liquid to vapor to (b) the mass of the system undergoing the change of phase. More technically speaking. the heat of vaporization is defined as the difference between the enthalpies of the system before and after the change of phase from liquid to vapor at constant temperature.
  • the vapor generated as a result of any heat addition creates a pressure gradient within the heat pipe which forces the excess vapor to an area of the heat pipe having a lower pressure and temperature.
  • the lower temperature causes the condensation of some vapor. thereby causing the latent heat of vaporization to be absorbed by the condenser surfaces of the heat pipe.
  • the heat may be removed from the condenser surfaces by conduction. convection or radiation to the surrounding environment.
  • the condensate is retuned to the evaporator region (area of heat addition) by the capillary pumping forces within the circumferential interior wick structure. This return may occur either with or without the aid of gravity.
  • the high efficiency of the heat pipe derives from the fact that the quantity of heat absorbed in the vaporization of a fluid is enormous compared to that absorbed during an increase in temperature of a fluid. For example. the amount of heat absorbed by 1 pound of water while being heated from 164 to 165 F. is l Btu. However, if the same pound of water were first vaporized at 164 F. and then the vapor heated to 165F.. the amount of heat absorbed would be l,000 Btu. Hence the same mass of water offers l.000 times the heat transfer capability over the same temperature gradient. when latent heat transfer is utilized.
  • Heat pipes can be designed to handle virtually any heat load and can be designed to operate over any temperature range. from below 300"Fv to above 3.630F.. by proper selection of the working fluid.
  • Heat pipe fluids have ranged from cryogenics such as nitrogen and helium. to liquid metals such as potassium and silver.
  • cryogenics such as nitrogen and helium.
  • liquid metals such as potassium and silver.
  • One of the most common fluids is water which has a useful operating range from 40 to 450 F.
  • a standard line of copper-water heat pipes is now commercially available. These heat pipes range in diameter from 3/l6 inch to l inch. and in length from 6 inches to 72 inches. The range of axial power ratings is from 60 watts to 1400 watts.
  • the present invention can be viewed as one of the first of what is believed will be virtually innumerable applications of the heat pipe concept. More particularly, the present invention constitutes an attempt to (a) reduce heat losses, (b) increase heating efficiency in domestic heating systems. and (c) at the same time, to eliminate the duplication of system components such as now exists in gas, oil. or coal systems with separate hot water heaters. and separate air-conditioning systems.
  • the present invention in its application to domestic heating systems. comprises a heat transfer system having three basic sections: a primary heat transformer, a hot water chamber, and a hot air chamber. In addition to these three basic sections. there is an additional fundamental system component, that of a plurality of heat pipes which thermally connect said hot water chamber and said hot air chamber to said primary heat transformer.
  • chamber shall be hereafter applied to any distinct and separate region of the system into or through which pass a plurality of heat pipes, which thermally connect said region with another region of the system, and the primary purpose of said region is to permit heat to be transferred to or from said plurality of heat pipes. from or to some medium with defined heat transfer properties which may reside within or pass through said region.
  • the transformer can be powered by any type of heat source. From the transformer, heat enters the heat pipes which in turn direct the thermal energy toward both the water and air chambers.
  • the water tank serves three functions: first, as a source of domestic hot water; second, as a thermal capacitor; and third, as a burner control.
  • the burner will shut down when the water tank reaches a predetermined temperature. Since the hot water section is connected by heat pipes to the hot air section, the water tank will serve as an additional source of heat for the hot air section when the burner is off. This represents an efficiency in heat use that does not exist in prior art systems.
  • the burner will reignite.
  • the hot air flow is regulated by a room thermostat which controls a two-speed fan.
  • the fan has a low speed to supply a constant trickle of warm air, and a high speed to provide additional heat when required.
  • the fan controls are completely independent from the burner.
  • This mode of operation eliminates the type of large temperature variations that are common in present systems.
  • the water tank as a thermal capacitor, it is possible to reduce overall burner running time and to change the burning cycle from many short runs to fewer, longer runs per day. Fewer starts and stops reduce burner exhaust pollution as well as system maintenance costs, as compared to the higher frequency conventional burner cycles.
  • FIG. 1 is a cross-sectional schematic view of a heat pipe.
  • FIG. 2 is a systems view of one embodiment of the present invention.
  • FIG. 3 is a cross-sectional radial schematic view of the transformer.
  • FIG. 4 is a cutaway perspective view of a domestic heating system utilizing the principles of the present invention.
  • FIG. 5 is a schematic view of a residential climate control system embodying the present invention.
  • FIG. 1 a single heat pipe in schematic form.
  • the pipe in the illustrated embodiment, comprises a closed elongated cylindrical container 9 containing a working fluid ll and a capillary wick structure 12 which is cirumferentially secured to the interior surface of the pipe 10.
  • Region I3 is termed the evaporator end of the pipe. It is at this end that heat is added to the present system, thereby causing evaporation of the fluid ll or the formation of vapor ll and movement of said vapor axially to the right and toward a cooler area 14 of the pipe having a lower pressure.
  • Area 14 comprises the condenser end of the pipe.
  • the vapor 11' is condensed, thus releasing its latent heat.
  • the fluid ll is absorbed into the wick structure 12 and is returned, by capillary forces, to the evaporator end 13 where the above cycle can be repeated indefinitely.
  • Section 15 is variously termed as a transport and an adiabutic section. In essence, this terminology means that section 15 functions to effect an efficient transfer of the vaporized fluid from sections 13 to 14, and the condensed vapor from sections 14 to 13.
  • FIG. 2 presents a systems illustration of one embodiment of the present invention. Shown is a multichambered heat transfer system which utilizies heat pipes to thermally connect several separate chambers.
  • the number, size, shape, construction and relative orientation of the separate chambers may be varied in any manner whatsoever to accommodate virtually any type of heating or cooling problem.
  • the heat pipes, their number, shape, size, orientation, construction and internal working mechanisms can be varied wherever necessary to achieve a solution to a particular heating or cooling problem.
  • the present invention is similarly intended to be readily adaptable to use with any source of heat and with virtually any heating load.
  • the primary mode of heat transfer is through the evaporation and condensation of a working fluid in a thermal transformer 18, and in one or more of the heat pipes 20, 22, 24 and 25.
  • the transformer 18 functions to convert or transform the high and non-uniform heat fluxes typical on the exterior of said transformer, into lower and more uniform heat fluxes.
  • Said heat pipes serve as thermal connectors and as heat transfer mediums to the several chambers 26, 28, 30 and 32. Secondary heat transfer can be obtained by ancillary heat pipes 33 disposed within or between said chambers 26, 28, 30 and 32.
  • the working fluid utilized within the transformer 18 need not necessarily be the same as the working fluid utilized within said heat pipes in said chambers.
  • All containment materials, and other materials in the inventions construction may be varied in any manner and are limited only with regard to their chemical compatability with each other and with the different materials with which they may come into contact.
  • This constraint pertains to the working fluids employed in the invention and its component parts.
  • both the working fluids, and their respective containment materials have a common limitation in that the structural integrity of said containments must withstand the operating temperatures and resultant operating pressures of the respective fluids.
  • Heat may be transferred through and/or from the transformer 18, to one or more of several chambers 26 through 32. These several chambers are intended to be sealed from each other in a suitable manner with, under the worst design and external conditions, no mass transfer occurring from one chamber to any other chamber, except where a mass transfer is intended as a part of a heat transfer process.
  • An ultimate heat source 34 is intended to supply the primary heat in required amounts to the invention.
  • the heat source 34 is applied to the transformer 18. It is, however, to be emphasized that alternate arrangements could be equally suitable in any given application. For example, the system of FIG. 2 could, with minor adaptations, have the heat source 34 applied to one of the chambers 26 through 32.
  • the chamber to which the heat source 34 is applied should contain, in addition to its enclosing walls, a working fluid (which may from time to time be frozen) and its vapor, as well as evaporation surfaces, condensation surfaces, a pressure release safety valve, and any temperature and/or pressure sensitive control devices that may be required in the solving ofa particular heating problem.
  • the primary purpose in the use of a transformer as opposed to the direct application of the heat source 34 to the evaporator ends of the heat pipes through 26, is to create a uniformity in the heat flux (noted by the four arrows in FIG. 2) from the heat source 34 to the chambers (26 through 32).
  • the transformer 18 also serves to reduce the possibility of a phenomenon which is known as heat pipe burnout. Heat pipe burnout occurs when the rate of evaporation in the evaporator section exceeds the rate of condensate return to the evaporator section, and the evaporator becomes dried out. In such a condition, a heat pipe cannot function.
  • FIG. 2 need comprise only a single heat pipe.
  • experimentation has shown that a more efficient operation can be obtained where a plurality of heat pipes are enclosed within the transformer 18.
  • FIG. 3 A representative configuration of such multiple heat pipes, enclosed with the transformer, is illustrated in FIG. 3.
  • a Y-shaped channel 36 (see FIG. 3) is termed a percolation channel.
  • a collector 37 serves to collect vapor bubbles which provide the means to pump working fluid via the percolation channel to the upper extremities of the wick structure. In doing so, the burnout heat flux of the transfomer evaporation surface is greatly increased because of this added condensate return mechanism.
  • An additional condensate return mechanism that of the gravity return of condensate from the condenser surface, is aided by the use of parallel radial fins 38 on the heat pipes. Said parallel radial fins, when spaced properly, aid the condensate return as a result of a miniscus which forms between adjacent fins, and on the lower surfaces, with respect to gravity. As droplets fall from said lower surfaces, surface tension forces resultant from said miniscus serve to draw condensate in the form of a falling film from the upper surfaces of said parallel fins. It is believed that this phenomenon can increase the heat transfer due to condensation on the underside of a horizontal surface by as much as five fold as compared to condensation without formation of said miniscus and its resultant surface tension forces. The primary reason for increased heat transfer is the reduc tion of the film thickness as a result of this falling film phenomenon.
  • FIG. 3 It has also been found that the design of FIG. 3 will operate at maximum efficiency where each pipe 10 is aligned in its own vertical plane. Such alignment provides each pipe with its own dripping path to the region 40. Hence, the fluid transport process within the transformer 18 is further assisted.
  • Heat may enter the transformer by means of conduction through one or more of its walls, and then through evaporator surface 42. See FIG. 3. Since the working fluid and its vapor are in a state of equilibrium at a reduced pressure, the addition of any heat to chamber 18 will cause a shift in the equilibrium state, favoring the evaporation of the working fluid. When this occurs, the latent heat of vaporization of the working fluid is transferred to the heat pipes by the condensation of vapor on said heat pipes exterior surfaces. The heat is then transferred axially away from the transformer by the internal dynamics of said heat pipes.
  • the heat deposited in regions 14' of said heat pipes 10 will conduct through the wall of said heat pipes 10 in regions 14' disposed within chambers 26, 28, 30 and 32, and then transfer from the exterior surfaces of the heat pipes 10 to the mediums contained within chambers 26, 28, 30 and 32, in a manner which is extremely efficient and uniform.
  • source 34 is inactive, and that one or more of the media contained within chambers 26, 28, 30 and 32 reside at a temperature which is different from the temperature at which one medium within one of the chambers resides at. said temperature gradient is sufficient to promote heat transfer from a medium residing at higher temperature to a medium residing at lower temperature.
  • Heat transfer to the media contained within chambers 26 to 32 of the system of FIG. 2 from the thermally connective heat pipes may be effected by any transfer means, that is. by conduction. convection, radiation. or the evaporation and condensation of a working fluid. or any combination of these.
  • the thermally connective heat pipes 10 may be variously smooth. rough. or finned in any manner so as to regulate the heat transfer to or from a heat pipe surface and from or to the medium in contact with said surface.
  • transfomer l8 and its associated plurality of heat pipes may serve as a means of thermally linking, and thereby thermally powering, any heating or cooling system.
  • the hereinafter described embodiment represents but one of a multiplicity of systems to which the present concept may be readily adapted.
  • one or more of the several chambers may be in the form of an air duct 26' designed so as to allow the passage of various quantities of air 44 or any other suitable gas, through the duct 26.
  • Said air 44 is in thermal contact with the exterior surface of the heat pipes 10 which extend into chamber 26'.
  • the intent of such a chamber is to raise or lower the temperature of the air 44 flowing through it.
  • the system will be equipped with air moving equipment. air flow controls, with temperature controls. and with any other control deemed necessary for the solution of a particular heat transfer problem.
  • One or more of the several chambers may contain a medium. with defined thermodynamic properties. which has the ability to store heat energy. either by virtue of increasing the temperature of said medium (sensible energy storage) or by virtue of changing the phase of said medium, either from solid to liquid, or from liquid to vapor (latent energy storage), or by virtue of a combination of these two (sensible and latent energy storage).
  • Said chamber can be termed a thermal battery, or a thermal capacitor.
  • Such a chamber may be in the form of a water tank 30'. as is illustrated in FIG. 4.
  • the intent of the tank 30' (in addition to its obvious use as a tank for supplying hot water for domestic use) is to absorb and store thermal energy, from the transformer I8, that is not immediately being utilized by the domestic hot water and hot air system. Energy absorbed by the tank 30'. is available for immediate use. either as instantaneous domestic hot water, or by virtue of the thermally connective heat pipes, as instantaneous hot air for domestic heat. regardless of whether the ultimate heat source is functioning or not.
  • One or more of the several chambers may comprise a geometric configuration similar to interchangeable with. or in place of the generator of an absorption refrigeration system of suitable size to be powered by the energy which could be provided by said chamber. It is not intended that an absorption refrigeration system is a part of this invention; however, it is intended that an appropriately sized absorption refrigeration system can be powered by a suitably designed chamber of said invention.
  • Such a suitably designed chamber 28 or 32 of said invention when serving to power such an appropriately sized absorption system can be considered to provide a means for removing heat energy from a second chamber. which may be an integral part of the invention, by virtue of the direct application of the absorption refrigeration system evaporating coil to that chamber. Said chamber could provide means for cooling air. water or any other medium used within the present system.
  • the residential heating system shown in FIGS. 4 and 5 includes a stack 46 for venting products of combustion from the heat source 34'. Also shown is a chimney 48.
  • the stack 46 receives the products combustion through the circumferential channel 50 (shown in FIG. 3).
  • Hot water for household use is. as above noted, supplied from the tank 30' (shown in FIG. 4).
  • An air exchange system and duct network for conditioning residential air comprises the duct for supplying air and an air return 52.
  • the air is circulated, by a fan 54, past a portion of the hot air chamber 26.
  • the heated air is thereby supplied through air supply 56 and to the individual room heat vents 58.
  • a typical operation cycle would be as follows: The water in tank 30' will be initially heated to 200F. A blower 54 will run at a low speed, sufficient to transfer an amount of heat from the transformer I8 through the air supply duct 56 and into the individual room vents 58, thereby compensating for heat losses through the domestic structure. With the heat source 34' off, heat is supplied to the air supply 44 via heat pipe 10 from 30' of the system. That is. the hot air chamber 26' will draw upon the thermal energy stored within the hot water chamber 30. This illustrates, in one form, the above-described thermal battery properties of the chamber 30.
  • an aquastat 62 When the temperature within the chamber 30' is reduced to l40 F.. an aquastat 62 will reactivate heat source 34'. Said heat source will supply heat through the transformer 18' for both the air and water supplied to the present domestic system. (The source 34' will operate until the water in tank 30' reaches 200 F, at which point the aquastat 62 will turn off the heat source.) In order to compensate for what is often a variable demand for heat within the rooms. a room thermostat 64 is provided which will control the speed of the fan 54, thereby regulating the rate at which heat is drawn from the chamber 26 for delivery to the rooms.
  • a tempering valve 66 may be employed to provide domestic hot water at one specified temperature, perhaps F.
  • Such a valve contains a thermal sensor which regulates the mixing ratio of hot water and cold water input to obtain a constant temperature output.
  • a heat transfer system comprising:
  • thermo transformer thermally linked to both said heat pipes and said heat source.
  • said transformer comprising:
  • said transformer further comprises: a wick structure affixed to the interior surface of said transformer and in contact with said evaporating surfaces.
  • a second chamber containing a second medium with defined thermodynamic properties said second medium thermally connected to said first chamber by said ancillary heat pipe.
  • said heat pipe comprises a plurality of heat pipes, each of said heat pipes being disposed in a vertical plane that does not intersect the vertical plane of any other of said heat pipes.
  • said heat source comprises: an exothermic chemical heat source.
  • a heat transfer system comprising:
  • thermal transformer thermally linked to both said heat pipe and said heat source, said thermal transformer comprising:
  • a first chamber containing a first medium with defined heat transfer characteristics and residing at a first temperature, said first chamber thermally coupled to said first end of said heat pipe;
  • a second chamber containing a second medium with defined heat transfer characteristics and residing at a second temperature, said second chamber chamber thermally coupled to said second end of said heat pipe,
  • the system as recited in claim 17 is which said transformer further comprises: a wick structure affixed to the interior surface of said transformer and in contact with said evaporating surfaces.
  • heat source comprises an electric heating element disposed externally proximate said transformer.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Central Heating Systems (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US366193A 1973-06-01 1973-06-01 Heat transfer system Expired - Lifetime US3880230A (en)

Priority Applications (6)

Application Number Priority Date Filing Date Title
US366193A US3880230A (en) 1973-06-01 1973-06-01 Heat transfer system
CA186,008A CA982533A (en) 1973-06-01 1973-11-16 Heat transfer system
JP49014622A JPS5016154A (enrdf_load_stackoverflow) 1973-06-01 1974-02-06
FR7415331A FR2231929B1 (enrdf_load_stackoverflow) 1973-06-01 1974-05-03
DE2425745A DE2425745C3 (de) 1973-06-01 1974-05-28 Einrichtung zur Wärmeübertragung
US05/478,982 US3994336A (en) 1973-06-01 1974-06-13 Transformer for heat pipes

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US366193A US3880230A (en) 1973-06-01 1973-06-01 Heat transfer system

Related Child Applications (1)

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US05/478,982 Continuation-In-Part US3994336A (en) 1973-06-01 1974-06-13 Transformer for heat pipes

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US3880230A true US3880230A (en) 1975-04-29

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US (1) US3880230A (enrdf_load_stackoverflow)
JP (1) JPS5016154A (enrdf_load_stackoverflow)
CA (1) CA982533A (enrdf_load_stackoverflow)
DE (1) DE2425745C3 (enrdf_load_stackoverflow)
FR (1) FR2231929B1 (enrdf_load_stackoverflow)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4037786A (en) * 1975-08-15 1977-07-26 International Telephone And Telegraph Corporation Energy recovery and storage system
US4582121A (en) * 1977-06-09 1986-04-15 Casey Charles B Apparatus for and method of heat transfer
US20050109057A1 (en) * 2003-11-25 2005-05-26 Twinbird Corporation Thermosiphon
US20050126761A1 (en) * 2003-12-10 2005-06-16 Je-Young Chang Heat pipe including enhanced nucleate boiling surface
US6990816B1 (en) * 2004-12-22 2006-01-31 Advanced Cooling Technologies, Inc. Hybrid capillary cooling apparatus
US20070240851A1 (en) * 2006-04-14 2007-10-18 Foxconn Technology Co., Ltd. Heat pipe
RU2313733C1 (ru) * 2006-03-10 2007-12-27 Сергей Дмитриевич Дмитриев Устройство для вентиляции помещения
US9404392B2 (en) 2012-12-21 2016-08-02 Elwha Llc Heat engine system
US9752832B2 (en) 2012-12-21 2017-09-05 Elwha Llc Heat pipe

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5051687A (enrdf_load_stackoverflow) * 1973-09-07 1975-05-08
JPS51136052A (en) * 1975-05-19 1976-11-25 Matsushita Electric Ind Co Ltd Heat pipe type thermal organ
JPS53132088A (en) * 1977-04-22 1978-11-17 Du Pont Coagulated powdered resin of tetrafluoroethylene copolymer
DE2942126C2 (de) * 1979-10-18 1982-10-14 L. & C. Steinmüller GmbH, 5270 Gummersbach Wärmeleitelemente für regenerativen Wärmeaustausch
US4474230A (en) * 1982-08-31 1984-10-02 Foster Wheeler Energy Corporation Fluidized bed reactor system
JP2507905B2 (ja) * 1991-08-30 1996-06-19 工業技術院長 安定化超電導線

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2237054A (en) * 1937-11-13 1941-04-01 Donald G Jensen Heating equipment
US2581347A (en) * 1943-07-09 1952-01-08 Electrolux Ab Absorption refrigeration apparatus and heating arrangement therefor
US3152774A (en) * 1963-06-11 1964-10-13 Wyatt Theodore Satellite temperature stabilization system
US3180405A (en) * 1959-03-11 1965-04-27 Itt Condensers
US3517730A (en) * 1967-03-15 1970-06-30 Us Navy Controllable heat pipe
US3621906A (en) * 1969-09-02 1971-11-23 Gen Motors Corp Control system for heat pipes
US3702533A (en) * 1969-12-24 1972-11-14 Philips Corp Hot-gas machine comprising a heat transfer device
US3746079A (en) * 1972-01-21 1973-07-17 Black Sivalls & Bryson Inc Method of vaporizing a liquid stream

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2237054A (en) * 1937-11-13 1941-04-01 Donald G Jensen Heating equipment
US2581347A (en) * 1943-07-09 1952-01-08 Electrolux Ab Absorption refrigeration apparatus and heating arrangement therefor
US3180405A (en) * 1959-03-11 1965-04-27 Itt Condensers
US3152774A (en) * 1963-06-11 1964-10-13 Wyatt Theodore Satellite temperature stabilization system
US3517730A (en) * 1967-03-15 1970-06-30 Us Navy Controllable heat pipe
US3621906A (en) * 1969-09-02 1971-11-23 Gen Motors Corp Control system for heat pipes
US3702533A (en) * 1969-12-24 1972-11-14 Philips Corp Hot-gas machine comprising a heat transfer device
US3746079A (en) * 1972-01-21 1973-07-17 Black Sivalls & Bryson Inc Method of vaporizing a liquid stream

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4037786A (en) * 1975-08-15 1977-07-26 International Telephone And Telegraph Corporation Energy recovery and storage system
US4582121A (en) * 1977-06-09 1986-04-15 Casey Charles B Apparatus for and method of heat transfer
US20050109057A1 (en) * 2003-11-25 2005-05-26 Twinbird Corporation Thermosiphon
EP1536191A3 (en) * 2003-11-25 2006-09-27 Twinbird Corporation Thermosiphon
US7234319B2 (en) 2003-11-25 2007-06-26 Twinbird Corporation Thermosiphon
US20050126761A1 (en) * 2003-12-10 2005-06-16 Je-Young Chang Heat pipe including enhanced nucleate boiling surface
US6990816B1 (en) * 2004-12-22 2006-01-31 Advanced Cooling Technologies, Inc. Hybrid capillary cooling apparatus
RU2313733C1 (ru) * 2006-03-10 2007-12-27 Сергей Дмитриевич Дмитриев Устройство для вентиляции помещения
US20070240851A1 (en) * 2006-04-14 2007-10-18 Foxconn Technology Co., Ltd. Heat pipe
US9404392B2 (en) 2012-12-21 2016-08-02 Elwha Llc Heat engine system
US9752832B2 (en) 2012-12-21 2017-09-05 Elwha Llc Heat pipe
US10358945B2 (en) 2012-12-21 2019-07-23 Elwha Llc Heat engine system

Also Published As

Publication number Publication date
JPS5016154A (enrdf_load_stackoverflow) 1975-02-20
CA982533A (en) 1976-01-27
FR2231929B1 (enrdf_load_stackoverflow) 1976-12-17
DE2425745B2 (de) 1978-09-28
DE2425745A1 (de) 1974-12-19
DE2425745C3 (de) 1979-05-23
FR2231929A1 (enrdf_load_stackoverflow) 1974-12-27

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