|Publication number||US3229759 A|
|Publication date||Jan 18, 1966|
|Filing date||Dec 2, 1963|
|Priority date||Dec 2, 1963|
|Also published as||DE1264461B|
|Publication number||US 3229759 A, US 3229759A, US-A-3229759, US3229759 A, US3229759A|
|Inventors||George M Grover|
|Original Assignee||George M Grover|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (7), Referenced by (93), Classifications (17)|
|External Links: USPTO, USPTO Assignment, Espacenet|
Jan. 18, 1966 G. M. GROVER I 3,229,759
EVAPORATION-CONDENSATION HEAT TRANSFER DEVICE Filed Dec. 2, 1963 2 Sheets-Sheet 1 eoo WATTS,
500 A L C 4 w w 900 [L] D: F. 600 I LL] 0. 2 500 LL] HEATED UNHEATED 300 I I I 1 l 0 1o so so so so INVENTOR DISTANCE (CM) George M. Grover Jan. 18, 1966 G. M. GROVER 3,229,759
EVAFORATION-CONDENSATION HEAT TRANSFER DEVICE Filed Dec. 2, 1963 2 Sheets-Sheet 2 Fig. 3
INVENTOR. George M. Grover BY .4../m A
United States Patent 3,229,759 EVAPORATION-CONDENSATIGN HEAT TRANSFER DEVltCE George M. Grover, Los Alamos, N. Mex., assignor to the United States of America as represented by the United States Atomic Energy Commission Filed Dec. 2, 1963, Ser. No. 327,559 3 Claims. (Cl. 165-105) This invention relates to structures of very high thermal conductance and, more particularly, to devices for the transfer of a large amount of heat with a small temperature drop, thereby being equivalent to a material having a thermal conductivity exceeding that of any known metal by a very large factor. The invention described herein was made in the course of, or under, a contract with the US. Atomic Energy Commission.
It is a desirable objective in substantially all heat transfer. applications to transfer a maximum amount of heat with a minimum temperature drop. For example, if
heatis to be transferred by radiation, it is desirable that the temperature at this place be as high as possible since therate of emission of radiant energy from the surface of abody is a function of the temperature to the fourth ,power.
The evaporation of a liquid, transport of the vapor through a duct, and subsequent condensation is a wellknown method for the transfer of a large amount of heat with a small temperature drop. In order to work continuously, the condensate must be returned to the evaporator. Ordinarily this is done by gravity or with a pump.
The present invention is a device in which this funcrtion is accomplished by a wick of suitable capillary structure. Devices of this general class will hereinafter be referred to as heat pipes, although it should be kept in mind that the shape of the device is not a matter for concern. Within certain limitations on the manner of use, a heat pipe may be regarded as a synergistic engineering structure which is equivalent to a material having a thermal conductivity greatly exceeding that of any known metal.
Accordingly, the invention is a heat transfer device comprising a container, said container enclosing a condensable vapor and capillary means within the container capable of causing the transport of the condensed vapor from a cooler area of the container to a hotter area. The transport of the vapor through the container uses, as the driving force, the difference in vapor pressures in the high temperature zone and cold temperature zone. The liquid which condenses in the cold zone is returned to the evaporation zone by capillary action. The forces to move fluids by capillary action are, of course, derived by the system attempting to arrive at a minimum free energy configuration,
It is an object of this invention to provide heat transfer devices having thermal conductivities exceeding that of any known metal by a very large factor.
It is a further object of this invention to transfer a relatively large quantity of heat with an exceedingly low temperature gradient.
It is another object of this invention to provide heat transfer devices which will accomplish the above 0bjectives under gravity-free conditions.
The above-mentioned and other features and objectives of this invention will become more apparent by reference to the following description taken in conjunction with the accompanying drawings in which:
FIGURE 1 is a schematic diagram of the principle of operation of a heat pipe.
FIGURE 2 represents the temperature profiles of a heat pipe representing the steady state temperatures measured at a number of input power levels.
FIGURE 3 is a cross section of an embodiment of the invention wherein the capillary material covers the entire inner surface of the container except for a portion of the condensing region.
The principle of operation of a heat pipe is shown schematically in FIGURE 1. The wick is saturated with a Wetting liquid. In the steady state, the liquid temperature in the evaporator is slightly higher than in the condenser region. The resulting difference in vapor pressure, P P O, drives the vapor from evaporator region 1 to condenser region 2. The depletion of liquid by evaporation causes the vapor-liquid interface in the evaporator to retreat into the wick surface where the typical meniscus has a radius of curvature, r equal to, or greater than, the largest capillary pore radius. The capillary represented in the drawing as a wire mesh is shown at 3. The pressure in the adjacent liquid will then be P (27 cos 0) /r where 7 is the surface tension and 0 the contact angle. In the condenser the typical meniscus assumes a radius, r which cannot exceed some relatively large radius determined by the geometry of the pipe. The pressure in the condenser liquid is then, P (2'y cos 0)/r The pressure drop available to drive the liquid through the wick from the condenser to the evaporator against the viscous retarding force is where p is the liquid density, g the acceleration of gravity, and k and h the heights of the liquid surfaces above a "reference level. This pressure drop may be made positive by choosing the capillary pore size sufficiently small. The above equation can be solved for r since the term 1/11 is so small as to be negligible. The pore radius of the capillary material should then be selected to be smaller than 1' Care should be taken to not make the pore radius too much smaller than r since for very small pores the increased viscous drag would interfere with the capillary return. It should be particularly noted that the possible case, g=0 (existent in gravity-free conditions such as space applications), is not excluded. Heat pipes will work under gravity-free conditions and even, to some extent, in opposition to gravity.
Water was used as working fluid in an initial qualitative experiment. A porous Alundum tube, 1' OD, I.D., and 12" long was inserted into a close-fittingPyrex tube. Enough water was added to saturate this wick and provide a small excess. The pressure in the tube was reduced by pumping at room temperature until the resulting boiling swept out all but water vapor from the central gas space. The tube was then sealed off. An evacuated blank of identical structure containing no water was also prepared. The heat pipe and the blank were arranged vertically side by side. Within a few minutes of the beginning of heating of the top few inches of the two tubes with an infrared lamp, the bottom of the heat pipe became and remained uncomfortably hot to the touch, while the bottom of the blank continued to stay nearly at room temperature.
In order to explore the qualitative potentialities further, a liquid sodium heat pipe was made for operation at about 1100 K. The containing tube was made of 347 stainless steel, GD, /8" I.D., and 12" long, with welded end-caps. The wick was made of -mesh 304 stainless steel screen with 0.005" diameter wires. This was formed in a spiral of five layers and fitted closely against the inner wall of the tube, leaving an ID. of /2". The pipe was loaded with 15 grams of solid sodium, evacuated to about 10* mm. Hg and sealed. When the top third of the pipe is heated by induction, the remarkably efficient heat transfer caused the heat pipe to be luminous almost to the cold end of the pipe. The 111- minous zone in the heat pipe terminates before reaching the bottom due to the relatively low thermal conductivity of the liquid sodium sump.
A second sodium heat pipe was made similar in all respects to the first except that the length was increased to 36". The sodium charge was increased to 40 grams. This heat pipe was placed in a vacuum chamber and about at one end was heated by electron bombardment from a concentric spiral filament. The data of FIGURE 2 were obtained after the pipe had been vacuum-baked at 1070 K. for two days. The vacuum baking, when using sodium as a coolant, is rather important owing to the fact that hydrogen is an impurity in sodium metal. Hydrogen is liberated in the reversible reaction NaH Na+%H AH3 -14 kcal.
The hydrogen is swept to the unheated end of the pipe by the refluxing sodium vapor. Consequently, in the hydrogen region the heat flux is accomplished by ordinary thermal conduction, mainly by the container wall and the saturated wick. This results in a rapidly decreasing temperature profile along the heat pipe. Under the vacuum baking conditions, hydrogen diffuses fairly readily through stainless steel. However, even after baking for two days, there appears to be about 5 X mole of hydrogen present at 100 watts, when the average temperature is near 500 K., increasing to 10 mole at 600 watts, when the average temperature is about 850 K. This is roughly consistent with the heat of reaction cited. Residual hydrogen occupies a volume determined jointly by the pressure of the sodium vapor in the refluxing section, and some average temperature in the non-refluxing section.
In FIGURE 2, which is a plot of the steady state temperatures measured at a number of input power levels versus the distances along the heat pipe, the region of rapidly decreasing temperature is caused by the presence of hydrogen gas. The temperature plateaus extending out from the heat region are of principal interest. This is the refluxing region. The method of measurement (five chromel-alumel thermocouples welded at intervals along the 36 pipe) was not precise enough to detect the minute temperature gradients but they do not exceed 0.05 K./ cm. In the refluxing region the heat pipe is behaving in a manner equivalent to a solid bar of material having a thermal conductivity in excess of 10 cal./sec.-cm.- K. A calculation, based on a detailed dynamic model of the heat pipe which will not be elaborated here, indicates that the actual temperature gradients are at least an order of magnitude less than this upper limit.
Attempts to deliver more than 30 watts/cm. through the surface of the heated section of the pipe resulted in the appearance of local overheated areas due either to deformation or drying of the wick. This phenomenon is probably a significant limitation on the operation of heat pipes.
Obviously, when using a coolant which does not have as an impurity a gas which is non-condensable at the temperatures of interest, the non-reflux region of rapidly decreasing temperatures will not be present. The use of sodium as a coolant may also be disadvantageous in that the corrosive sodium may, after extensive operation, dissolve the container at the place of condensation and deposit the container metal at the place of evaporation. Lithium coolant in a niobium-1% zirconium alloy would be advantageous at temperatures of about 1100 C. Lithium possesses another advantage in that its heat of vaporization is approximately 5000 caL/gram as compared to about 1000 cal/gram for sodium and about 500 cal./ gram for water. An experiment was carried out using lithium in niobium-1% zirconium alloy without a capillary path. The bottom portion of the pipe was immersed in a heat source. After proper operation for a short time the heat transfer rate went down very sharply. This was found to be due to the accumulation of lithium at the top of the pipe. The addition of a screen mesh along the inner walls of the pipe to provide a capillary flow return path allowed proper operation of this heat pipe. Tantalum and silver do not form alloys and this combination of materials would be useful at temperatures of about 2000 C. A heat pipe of tantalum with a tantalum screen and with silver as the working fluid has been operated for short times at 1700" C. The lifetime at this operating temperature has not been established. It should be noted that a range of temperatures for each coolant is possible by operating at various pressures inside the container. A range of temperatures would accordingly give a range of vapor pressures and heat transfer rates. The theoretical upper limit of temperature is the critical temperature of the circulating fluid since at that temperature the surface tension goes to zero. I
It should also be noted that the shape of the device is a matter of discretion. Hollow plates, rods, etc., are equally adaptable to the present inventive concept. Furthermore, there is no requirement that the pipe be heated at one end and condense at the other. For example, the pipe may be heated somewhere along its length and condense at both ends. Capillary material should be present at the point at which the heat transfer pipe is to be heated. However, it is not necessary that the capillary material cover the entire condensing region, only that the capillary material extend into the condenser region. This con struction is shown in FIGURE 3 wherein 1 represents the evaporator region and the condenser region is shown at 2. The material comprising the capillary path is a matter of complete discretion. For example, glass frit, wire mesh, tubes, etc., may be utilized; the only requirement being that the pore size be sufficiently small to produce capillary action. Since capillary action is utilized to return the liquid from condenser to evaporator regions, the heat pipe will work under gravity-free conditions and even, to some extent, against the force of gravity.
Since many changes can be made in the construction of a heat pipe (some of which are mentioned above) and many apparent widely diflerent embodiments of this invention could be made without departing from the scope thereof, it is intended that all matter contained in the above description or shown in the accompanying drawings shall be interpreted as illustrative and not in a limiting sense. The invention should therefore, be limited only by the following appended claims.
What is claimed is:
1. A heat transfer device comprising a container having condenser and evaporator regions composed of niobiuml% zirconium alloy, said container enclosing a condensable vapor consisting of lithium, capillary means, said capillary means covering the entire inner surface of the container except for a portion of the condensing region, the quantity of condensable vapor present being just suflicient to saturate the capillary means when condensed and provide a small excess, said capillary means capable of causing the transport of the condensed vapor from the cooler area of the container to the hotter area.
2. A heat transfer device comprising a container having condenser and evaporator regions composed of niobium- 1% zirconium alloy, the exterior portion of said container being smooth and said container enclosing a condensable vapor consisting of lithium, capillary means, said capillary means covering the entire inner surface of the container except for a portion of the condensing region, the quantity of condensable vapor present being just sufficient to saturate the capillary means when condensed and provides a small excess, said capillary means capable of causing the transport of the condensed vapor from the cooler area of the container to the hotter area.
3. A heat transfer device comprising a container having condenser and evaporator regions composed of niobium- 1% zirconium alloy, the exterior portion of said container being smooth, said container enclosing a condensable vapor consisting of lithium, capillary means, said capillary means covering the entire inner surface of the container except for a portion of the condensing region, the quantity of condensable vapor present being just suflicient to saturate the capillary means when condensed and provide a small excess, the pore radius of the capillary material being slightly smaller than r r being defined by making the expression 'Y( '2) 2 1)-P 2 1) slightly positive, Where p is the liquid density, g the acceleration of gravity, b and 12 the heights of liquid surfaces in the evaporator and condenser regions above a reference level, 7 is the surface tension, 0 the contact angle, P and P are the vapor pressures in the evaporator and condenser regions, and r the radius of curvature of region.
References Cited by the Examiner UNITED STATES PATENTS Gaugler 6256 X Kuenhold 261-104 Gaugler 26 1--1 04 X Cornelison et al. 165105 X Chandler 261-404 X Hebeler 165-134 Wyatt 2441 ROBERT A. OLEARY, Primary Examiner.
CHARLES SUKALO, Examiner.
a meniscus in the capillary located at the evaporator 15 N'R'WHSONAsslSmm Exammer'
|Cited Patent||Filing date||Publication date||Applicant||Title|
|US2350348 *||Dec 21, 1942||Jun 6, 1944||Gen Motors Corp||Heat transfer device|
|US2394698 *||Aug 7, 1942||Feb 12, 1946||Monmouth Products Company||Evaporator|
|US2517654 *||May 17, 1946||Aug 8, 1950||Gen Motors Corp||Refrigerating apparatus|
|US2958021 *||Apr 23, 1958||Oct 25, 1960||Texas Instruments Inc||Cooling arrangement for transistor|
|US3043573 *||Feb 16, 1956||Jul 10, 1962||Edward F Chandler||Thermo-transpiration portable air conditioner unit|
|US3089318 *||Jan 10, 1961||May 14, 1963||Boeing Co||Hypersonic cooling system|
|US3152774 *||Jun 11, 1963||Oct 13, 1964||Wyatt Theodore||Satellite temperature stabilization system|
|Citing Patent||Filing date||Publication date||Applicant||Title|
|US3302042 *||Oct 23, 1965||Jan 31, 1967||George M Grover||Nuclear reactor with thermionic converter|
|US3305005 *||Dec 3, 1965||Feb 21, 1967||Busse Claus A||Capillary insert for heat tubes and process for manufacturing such inserts|
|US3378449 *||Jul 27, 1967||Apr 16, 1968||Atomic Energy Commission Usa||Nuclear reactor adapted for use in space|
|US3378454 *||Aug 22, 1966||Apr 16, 1968||Euratom||Nuclear fuel arrangement|
|US3399717 *||Dec 27, 1966||Sep 3, 1968||Trw Inc||Thermal switch|
|US3402761 *||Feb 17, 1967||Sep 24, 1968||Navy Usa||Controllable heat pipe apparatus|
|US3403075 *||Aug 11, 1966||Sep 24, 1968||Euratom||Nuclear reactor|
|US3405299 *||Jan 27, 1967||Oct 8, 1968||Rca Corp||Vaporizable medium type heat exchanger for electron tubes|
|US3414050 *||Apr 11, 1967||Dec 3, 1968||Navy Usa||Heat pipe control apparatus|
|US3414475 *||May 13, 1966||Dec 3, 1968||Euratom||Heat pipes|
|US3426220 *||Feb 16, 1966||Feb 4, 1969||Rca Corp||Heat-sensitive seal for thermionic converters|
|US3435889 *||Apr 25, 1966||Apr 1, 1969||Martin Marietta Corp||Heat pipes for non-wetting fluids|
|US3441752 *||Oct 23, 1965||Apr 29, 1969||Atomic Energy Commission||Thermionic converter device|
|US3450195 *||Mar 16, 1967||Jun 17, 1969||Gen Electric||Multiple circuit heat transfer device|
|US3457436 *||Nov 7, 1966||Jul 22, 1969||Teledyne Inc||Heat pipes with unique radiator configuration in combination with thermoionic converters|
|US3464889 *||Nov 1, 1967||Sep 2, 1969||Atomic Energy Commission||Heat actuated control rod utilizing a cadmium-potassium mixture|
|US3465813 *||Jul 26, 1967||Sep 9, 1969||Trw Inc||Method of and means for increasing the heat transfer capability of a heat pipe|
|US3468300 *||Nov 13, 1968||Sep 23, 1969||Acf Ind Inc||Heat transfer means for a railway tank car|
|US3490718 *||Feb 1, 1967||Jan 20, 1970||Nasa||Capillary radiator|
|US3502138 *||Aug 14, 1967||Mar 24, 1970||Trw Inc||Means for regulating thermal energy transfer through a heat pipe|
|US3503438 *||Oct 25, 1968||Mar 31, 1970||Acf Ind Inc||Hydrogen release for a heat pipe|
|US3509386 *||Sep 6, 1967||Apr 28, 1970||Nasa||Heat pipe thermionic diode power system|
|US3516487 *||Feb 21, 1968||Jun 23, 1970||Gen Electric||Heat pipe with control|
|US3517730 *||Mar 15, 1967||Jun 30, 1970||Us Navy||Controllable heat pipe|
|US3524772 *||Dec 3, 1964||Aug 18, 1970||Nuclear Materials & Equipment||Generator of electrical energy|
|US3525670 *||Dec 17, 1968||Aug 25, 1970||Atomic Energy Commission||Two-phase fluid control system|
|US3541487 *||Nov 18, 1968||Nov 17, 1970||Westinghouse Electric Corp||Electrical winding having heat exchangers between layers of the winding for cooling the windings|
|US3561525 *||Jul 2, 1969||Feb 9, 1971||Energy Conversion Systemes Inc||Heat pipe condensate return|
|US3563309 *||Sep 16, 1968||Feb 16, 1971||Hughes Aircraft Co||Heat pipe having improved dielectric strength|
|US3568762 *||May 23, 1967||Mar 9, 1971||Rca Corp||Heat pipe|
|US3585842 *||May 12, 1969||Jun 22, 1971||Phillips Petroleum Co||Method and apparatus for temperature control|
|US3595304 *||Sep 15, 1967||Jul 27, 1971||Monsanto Co||Organic fluids for heat pipes|
|US3603382 *||Nov 3, 1969||Sep 7, 1971||Nasa||Radial heat flux transformer|
|US3603767 *||Sep 3, 1969||Sep 7, 1971||Dynatherm Corp||Isothermal cooking or heating device|
|US3604503 *||Aug 2, 1968||Sep 14, 1971||Energy Conversion Systems Inc||Heat pipes|
|US3613773 *||Dec 7, 1964||Oct 19, 1971||Rca Corp||Constant temperature output heat pipe|
|US3613774 *||Oct 8, 1969||Oct 19, 1971||Sanders Associates Inc||Unilateral heat transfer apparatus|
|US3621906 *||Sep 2, 1969||Nov 23, 1971||Gen Motors Corp||Control system for heat pipes|
|US3651240 *||Jan 31, 1969||Mar 21, 1972||Trw Inc||Heat transfer device|
|US3651861 *||Jan 15, 1970||Mar 28, 1972||Goetzewerke||Mold and method|
|US3662137 *||Jan 21, 1970||May 9, 1972||Westinghouse Electric Corp||Switchgear having heat pipes incorporated in the disconnecting structures and power conductors|
|US3670495 *||Jul 15, 1970||Jun 20, 1972||Gen Motors Corp||Closed cycle vapor engine|
|US3672443 *||Jan 28, 1969||Jun 27, 1972||Teledyne Inc||Thermal control and power flattening for radioisotopic thermodynamic power system|
|US3677329 *||Nov 16, 1970||Jul 18, 1972||Trw Inc||Annular heat pipe|
|US3688838 *||Aug 24, 1970||Sep 5, 1972||Bbc Brown Boveri & Cie||Heat tube|
|US3699343 *||Aug 19, 1969||Oct 17, 1972||Sanders Associates Inc||Condensation heated black body radiation source|
|US3712053 *||Apr 27, 1970||Jan 23, 1973||S Kofink||Thermal-mechanical energy transducer device|
|US3763838 *||Dec 23, 1971||Oct 9, 1973||Shell Oil Co||Carburetor having a heat pipe for vaporizing fuel|
|US3786861 *||Apr 12, 1971||Jan 22, 1974||Battelle Memorial Institute||Heat pipes|
|US3788388 *||Feb 19, 1971||Jan 29, 1974||Q Dot Corp||Heat exchange system|
|US3788389 *||Aug 25, 1971||Jan 29, 1974||Mc Donnell Douglas Corp||Permafrost structural support with heat pipe stabilization|
|US3834457 *||Jan 17, 1973||Sep 10, 1974||Bendix Corp||Laminated heat pipe and method of manufacture|
|US3853112 *||Feb 16, 1973||Dec 10, 1974||Thermo Electron Corp||Vapor transfer food preparation and heating apparatus|
|US3854524 *||Sep 7, 1972||Dec 17, 1974||Atomic Energy Commission||Thermal switch-heat pipe|
|US3889096 *||Feb 22, 1973||Jun 10, 1975||Philips Corp||Electric soldering iron delivering heat by change of state of a liquid heat transporting medium|
|US3921710 *||Aug 22, 1973||Nov 25, 1975||Tokico Ltd||Heat pipe and manufacturing method thereof|
|US4005297 *||Oct 18, 1972||Jan 25, 1977||Westinghouse Electric Corporation||Vacuum-type circuit interrupters having heat-dissipating devices associated with the contact structures thereof|
|US4108239 *||Mar 22, 1976||Aug 22, 1978||Siemens Aktiengesellschaft||Heat pipe|
|US4273100 *||Feb 16, 1979||Jun 16, 1981||W. R. Grace & Co.||Passive solar heating and cooling panels|
|US4282926 *||Feb 22, 1979||Aug 11, 1981||James Howden And Company Australia Pty. Limited||Cooling of fluid streams|
|US4294659 *||Jan 16, 1978||Oct 13, 1981||United Kingdom Atomic Energy Authority||Apparatus for use in a liquid alkali metal environment|
|US4320246 *||Jul 19, 1979||Mar 16, 1982||Russell George F||Uniform surface temperature heat pipe and method of using the same|
|US4413475 *||May 14, 1982||Nov 8, 1983||Moscrip William M||Thermodynamic working fluids for Stirling-cycle, reciprocating thermal machines|
|US4452298 *||Mar 23, 1982||Jun 5, 1984||Mannesmann Aktiengesellschaft||Method and apparatus for cooling continuously cast metal strands|
|US4478784 *||Jun 10, 1982||Oct 23, 1984||The United States Of America As Represented By The United States Department Of Energy||Passive heat transfer means for nuclear reactors|
|US4485670 *||Feb 13, 1981||Dec 4, 1984||The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration||Heat pipe cooled probe|
|US4526533 *||Sep 29, 1982||Jul 2, 1985||A. Monforts Gmbh & Co.||Cylinder for guiding a web of textile material|
|US4560533 *||Aug 30, 1984||Dec 24, 1985||The United States Of America As Represented By The United States Department Of Energy||Fast reactor power plant design having heat pipe heat exchanger|
|US4582121 *||Sep 16, 1980||Apr 15, 1986||Casey Charles B||Apparatus for and method of heat transfer|
|US4681995 *||Apr 4, 1986||Jul 21, 1987||Ahern Brian S||Heat pipe ring stacked assembly|
|US4697205 *||Mar 13, 1986||Sep 29, 1987||Thermacore, Inc.||Heat pipe|
|US4854378 *||Oct 27, 1986||Aug 8, 1989||Zappia Joseph M||Heat transfer and fluid heating device|
|US5002122 *||Sep 25, 1984||Mar 26, 1991||Thermacore, Inc.||Tunnel artery wick for high power density surfaces|
|US5947111 *||Apr 30, 1998||Sep 7, 1999||Hudson Products Corporation||Apparatus for the controlled heating of process fluids|
|US7168480 *||Apr 29, 2004||Jan 30, 2007||Los Alamos National Security, Llc||Off-axis cooling of rotating devices using a crank-shaped heat pipe|
|US7306654||Jan 30, 2004||Dec 11, 2007||Ronald King||Method and apparatus for recovering water from atmospheric air|
|US7828046||Jul 20, 2005||Nov 9, 2010||Xiao Huang||Hybrid wicking materials for use in high performance heat pipes|
|US7957708||Mar 2, 2005||Jun 7, 2011||Rosemount Inc.||Process device with improved power generation|
|US8145180||Sep 27, 2005||Mar 27, 2012||Rosemount Inc.||Power generation for process devices|
|US8188359||Sep 28, 2006||May 29, 2012||Rosemount Inc.||Thermoelectric generator assembly for field process devices|
|US8538560||May 21, 2004||Sep 17, 2013||Rosemount Inc.||Wireless power and communication unit for process field devices|
|US8626087||Aug 27, 2010||Jan 7, 2014||Rosemount Inc.||Wire harness for field devices used in a hazardous locations|
|US8694060||Jun 16, 2009||Apr 8, 2014||Rosemount Inc.||Form factor and electromagnetic interference protection for process device wireless adapters|
|US8787848||Jun 17, 2009||Jul 22, 2014||Rosemount Inc.||RF adapter for field device with low voltage intrinsic safety clamping|
|US8827498 *||Sep 30, 2008||Sep 9, 2014||Osram Sylvania Inc.||LED light source having glass heat pipe with fiberglass wick|
|US8847571||Jun 17, 2009||Sep 30, 2014||Rosemount Inc.||RF adapter for field device with variable voltage drop|
|US8929948||Jun 16, 2009||Jan 6, 2015||Rosemount Inc.||Wireless communication adapter for field devices|
|US9103498||Jul 23, 2007||Aug 11, 2015||Shell Oil Company||Method and apparatus for vaporizing a liquid stream|
|US20050208908 *||Mar 2, 2005||Sep 22, 2005||Rosemount Inc.||Process device with improved power generation|
|US20050241807 *||Apr 29, 2004||Nov 3, 2005||Jankowski Todd A||Off-axis cooling of rotating devices using a crank-shaped heat pipe|
|DE2602211A1 *||Jan 22, 1976||Aug 5, 1976||Philips Nv||Waermeaustauscher|
|DE102013014988A1||Sep 7, 2013||Mar 26, 2015||Messer Austria Gmbh||Brenner|
|WO2003071215A1||Sep 13, 2002||Aug 28, 2003||John Gruzleski||Heat pipe|
|U.S. Classification||165/104.26, 165/905, 376/367, 174/15.1, 62/513, 62/487|
|International Classification||G21C15/02, F28D15/04, G21C15/257|
|Cooperative Classification||Y02E30/40, G21C15/02, F28D15/04, G21C15/257, Y10S165/905|
|European Classification||F28D15/04, G21C15/02, G21C15/257|