US3229759A - Evaporation-condensation heat transfer device - Google Patents

Evaporation-condensation heat transfer device Download PDF

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Publication number
US3229759A
US3229759A US327559A US32755963A US3229759A US 3229759 A US3229759 A US 3229759A US 327559 A US327559 A US 327559A US 32755963 A US32755963 A US 32755963A US 3229759 A US3229759 A US 3229759A
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US
United States
Prior art keywords
container
heat
region
vapour
capillary
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Expired - Lifetime
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US327559A
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English (en)
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George M Grover
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Individual
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Priority to GB1027719D priority Critical patent/GB1027719A/en
Application filed by Individual filed Critical Individual
Priority to US327559A priority patent/US3229759A/en
Priority to FR996190A priority patent/FR1415208A/fr
Priority to SE14435/64A priority patent/SE307799B/xx
Priority to DEU11233A priority patent/DE1264461B/de
Priority to NL6413971A priority patent/NL6413971A/xx
Priority to JP6742364A priority patent/JPS417278B1/ja
Priority to BE656515D priority patent/BE656515A/xx
Application granted granted Critical
Publication of US3229759A publication Critical patent/US3229759A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • G—PHYSICS
    • G21—NUCLEAR PHYSICS; NUCLEAR ENGINEERING
    • G21C—NUCLEAR REACTORS
    • G21C15/00—Cooling arrangements within the pressure vessel containing the core; Selection of specific coolants
    • G21C15/02—Arrangements or disposition of passages in which heat is transferred to the coolant; Coolant flow control devices
    • 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
    • F28D15/04—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 tubes having a capillary structure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
    • F28F21/08—Constructions of heat-exchange apparatus characterised by the selection of particular materials of metal
    • F28F21/081—Heat exchange elements made from metals or metal alloys
    • G—PHYSICS
    • G21—NUCLEAR PHYSICS; NUCLEAR ENGINEERING
    • G21C—NUCLEAR REACTORS
    • G21C15/00—Cooling arrangements within the pressure vessel containing the core; Selection of specific coolants
    • G21C15/24—Promoting flow of the coolant
    • G21C15/257—Promoting flow of the coolant using heat-pipes
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E30/00—Energy generation of nuclear origin
    • Y02E30/30—Nuclear fission reactors
    • 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
    • Y10S165/00—Heat exchange
    • Y10S165/905—Materials of manufacture

Definitions

  • 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 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.
  • 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.
  • 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,
  • 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.
  • FIGURE 1 The principle of operation of a heat pipe is shown schematically in FIGURE 1.
  • the wick is saturated with a Wetting liquid.
  • P P O The resulting difference in vapor pressure, 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • the shape of the device is a matter of discretion. Hollow plates, rods, etc., are equally adaptable to the present inventive concept.
  • the pipe be heated at one end and condense at the other.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Plasma & Fusion (AREA)
  • High Energy & Nuclear Physics (AREA)
  • Mechanical Engineering (AREA)
  • Sustainable Development (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Lasers (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Common Detailed Techniques For Electron Tubes Or Discharge Tubes (AREA)
US327559A 1963-12-02 1963-12-02 Evaporation-condensation heat transfer device Expired - Lifetime US3229759A (en)

Priority Applications (8)

Application Number Priority Date Filing Date Title
GB1027719D GB1027719A (enrdf_load_stackoverflow) 1963-12-02
US327559A US3229759A (en) 1963-12-02 1963-12-02 Evaporation-condensation heat transfer device
FR996190A FR1415208A (fr) 1963-12-02 1964-11-25 Procédé et appareil pour le transfert de chaleur
SE14435/64A SE307799B (enrdf_load_stackoverflow) 1963-12-02 1964-11-30
DEU11233A DE1264461B (de) 1963-12-02 1964-12-01 Waermerohr
NL6413971A NL6413971A (enrdf_load_stackoverflow) 1963-12-02 1964-12-02
JP6742364A JPS417278B1 (enrdf_load_stackoverflow) 1963-12-02 1964-12-02
BE656515D BE656515A (enrdf_load_stackoverflow) 1963-12-02 1964-12-02

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US327559A US3229759A (en) 1963-12-02 1963-12-02 Evaporation-condensation heat transfer device

Publications (1)

Publication Number Publication Date
US3229759A true US3229759A (en) 1966-01-18

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Family Applications (1)

Application Number Title Priority Date Filing Date
US327559A Expired - Lifetime US3229759A (en) 1963-12-02 1963-12-02 Evaporation-condensation heat transfer device

Country Status (7)

Country Link
US (1) US3229759A (enrdf_load_stackoverflow)
JP (1) JPS417278B1 (enrdf_load_stackoverflow)
BE (1) BE656515A (enrdf_load_stackoverflow)
DE (1) DE1264461B (enrdf_load_stackoverflow)
GB (1) GB1027719A (enrdf_load_stackoverflow)
NL (1) NL6413971A (enrdf_load_stackoverflow)
SE (1) SE307799B (enrdf_load_stackoverflow)

Cited By (116)

* Cited by examiner, † Cited by third party
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DE1264461B (de) 1968-03-28
JPS417278B1 (enrdf_load_stackoverflow) 1966-04-21
BE656515A (enrdf_load_stackoverflow) 1965-04-01
SE307799B (enrdf_load_stackoverflow) 1969-01-20
GB1027719A (enrdf_load_stackoverflow)
NL6413971A (enrdf_load_stackoverflow) 1965-06-03

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