US3455376A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US3455376A
US3455376A US662443A US3455376DA US3455376A US 3455376 A US3455376 A US 3455376A US 662443 A US662443 A US 662443A US 3455376D A US3455376D A US 3455376DA US 3455376 A US3455376 A US 3455376A
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Prior art keywords
liquid
throats
wall
exchanger
heat
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Expired - Lifetime
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US662443A
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English (en)
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Charles A Beurtheret
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Compagnie Francaise Thomson Houston SA
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Compagnie Francaise Thomson Houston SA
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • F28F13/187—Heat-exchange surfaces provided with microstructures or with porous coatings especially adapted for evaporator surfaces or condenser surfaces, e.g. with nucleation sites
    • 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
    • G—PHYSICS
    • G21—NUCLEAR PHYSICS; NUCLEAR ENGINEERING
    • G21C—NUCLEAR REACTORS
    • G21C17/00—Monitoring; Testing ; Maintaining
    • G21C17/02—Devices or arrangements for monitoring coolant or moderator
    • G21C17/038—Boiling detection in moderator or coolant
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01J—ELECTRIC DISCHARGE TUBES OR DISCHARGE LAMPS
    • H01J19/00—Details of vacuum tubes of the types covered by group H01J21/00
    • H01J19/28—Non-electron-emitting electrodes; Screens
    • H01J19/32—Anodes
    • H01J19/36—Cooling of anodes
    • 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
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0028—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cooling heat generating elements, e.g. for cooling electronic components or electric devices
    • F28D2021/0029—Heat sinks
    • 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
    • Y10S165/911—Vaporization

Definitions

  • the present invention concerns improvements in methods and devices for heat exchange between a wall and a liquid circulated on contact therewith. It is more especially concerned with devices of this type in which the transfer of an intense thermal flux is effected essentially by local vaporization of liquid on contact with the hot wall, and recondensation of the vapor thus formed in the mass of the circulating liquid.
  • ribs must be of small height and far enough away from each other so that the creation of nests of bubbles will not occur, which could be considered as establishing hot points capable of triggering the burnout phenomenon. If it is desired to designate by throats the intervals between ribs, these throats are thus wider than they are deep; recent research work has confirmed this practice in recommending, moreover even accentuating this ratio of dimensions in making the width of the throats up to ten or even twenty times their depth. In these conditions, the depth is then smaller than a millimeter, and the entire heat exchanger surface operates practically isothermically.
  • the exchanger wall comprises parallel ribs separated by narrow, deep throats.
  • This exchanger is capable of transmitting a thermal flux several times greater than the critical flux of the liquid, and this even if the liquid is already at its boiling temperature. Its performance is even more increased in the presence of a cooler liquid, by natural convection. Rapid circulation forced on the liquid pushing the dissipation of this exchanger even highor as in exchangers having induced circulation.
  • the improvements proposed by the invention concern all devices for heat exchange between a wall and a liquid by local evaporation, accompanied by a recondensation in the mass of moving liquid, in which a heat transfer surface of the heat exchanger wall is formed with depressions, or grooves, in particular in the form of throats, which is exposed to a forced liquid circulation in a confined space, limited by a guide wall.
  • the depth of the depressions or throats is chosen greater than the distance separating their opposed edges; contrary to prior practice liquid is forcibly circulated in a direction of flow which is transverse to the longitudinal direction of the throats, that is to say, a direction forming locally angles comprised between 45 and preferably between 60" and 90, with the longitudinal direction of the throats.
  • the invention is based on the resulting differing paths of flow presented to the liquid from the entry to the outlet of the device, namely a first path essentially external to the overall geometric volume of the exchanger wall and a second path essentially internal to this overall volume, and formed by the assembly of throats.
  • a first path essentially external to the overall geometric volume of the exchanger wall
  • a second path essentially internal to this overall volume, and formed by the assembly of throats.
  • Common sense suggests that the most effective heat exchange would be obtained when the liquid flow through the second path is as large as possible, the passage through the throats ensuring, at first blush, intimate contact between the liquid and the wall, whatever be the form of the throats.
  • the invention proposes the contrary, namely, to create a main flow path exteriorly of the wall and the throats, in the confined space, limited by the overall surface of the wall of the exchanger and the guide wall.
  • the path constituted by the overall assembly of throats in the heat exchanger in accordance with the invention will have a large hydrodynamic resistance relative to the path defined by the confined space, between the heat exchanger wall and the guide wall.
  • FIG. 1 is a perspective view, the wall being shown partly removed to reveal the structure of the exchanger wall therebeneath, of a heat exchanger with a plane exchanger wall;
  • FIG. 2 is an enlarged section of a part of the exchanger of FIG. 1 in a plane perpendicular to the exchanger wall and arrow 11 of FIG. 1;
  • FIG. 3 is an elevational view of a heat exchanger comprising a cylindrical wall provided with helichordal throats, forming the anode of an electronic tube, a part of the casing of the exchanger being removed;
  • FIG. 4 is a part sectional elevation of a heat exchanger comprising an exchanger wall provided with circular throats, the exchanger wall and flow director elements being shown in elevation, the remainder of the device being shown in section;
  • FIG. 5 is a fragmentary section of a heat exchanger comprising a rounded conical exchanger wall provided with circular throats;
  • FIG. 6 is a section through a heat exchanger comprising a cylindrical exchanger wall provided with throats parallel to its axis, this section being taken on the line BB of FIG. 7;
  • FIG. 7 is a section through the heat exchanger shown in FIG. 6 taken on the line AA of FIG. 6.
  • the heat exchanger shown in FIGURES 1 and 2 is constituted by an exchanger wall 1, a guide wall 2, disposed parallel to the wall 1 and at a short distance 2 therefrom, a liquid distribution chamber 3, provided with an inlet tube 4, a collecting chamber 5, provided with an outlet tube 6, and two lateral closing walls 7 and 8.
  • the exchanger wall 1 comprises a rectangular metal plate, for example, in copper, and its heat transfer face which is visible in the figures comprises a network of depressions in the form of parallel throats 9, separated by ridges or ribs 10. As is shown in FIGURE 2, the depth b of these throats is clearly greater than the distance d separating their edges.
  • the throats form angles of less than 45 with each of these two edges.
  • a flow of liquid entering through the tube 4 thus forms, between the exchanger wall 1 and the guide wall, a sheet flowing in one direction, designated by the arrow 11, which is substantially that of the lines connecting the chambers 3 and 5 the shortest way.
  • the direction of flow thus forms, with the longitudinal direction 12 of the throats, an angle comprised between 45 and Only a small proportion of the output of liquid is diverted in the direction 12 of the throats and flows thereinto.
  • the throats do not themselves discharge into the chambers 3 and 5, their entry being prevented by a part of a casing 13 of these chambers.
  • discharge can be effected into one or both chambers, but in both cases, the hydrodynamic resistance of the direct flow path from the distribution chamber to the collecting chamber is less than that offered by the assembly of the network of liquid flowing in the throats.
  • FIG. 1 there is also shown, in a very schematic manner, outer accessories, ensuring the circulation of liquid in a closed circuit.
  • the liquid discharging from the outlet tube is cooled in the secondary chamber 14, of known construction, and reinjected by a pump 15, into the inlet tube 4.
  • the installation comprises, moreover, a reservoir 26, if desired pressurized, and conventional safety devices not shown.
  • FIG. 2 The heat exchange process being effected in the device of FIGURE 1 is explained with reference to FIG. 2.
  • Arrows 16 symbolize the heat flux entering by the inlet surface 17 of the wall 1.
  • a small part of this heat is exchanged by direct conduction between the terminal parts 18 of the sides 10 and the liquid which circulates rapidly on contact therewith in the main flow path 19, between the entire surface 25 of the exchanger wall and the guide wall 2.
  • the exchange is effected in the throats 9 by vaporization of the liquid which they contain, by a complex boiling operation stabilized by the gradient of temperature which is established on the sides of the ribs 10, and this with a mean density of flux in the neighborhood of the critical flux, the value of which no longer constitutes a limit.
  • the liquid is water under an absolute pressure of two atmospheres (one atmosphere of overpressure) for which the boiling temperature is 120 C.
  • the temperature of this liquid is already up to at the moment when it reaches the throat shown in the center of the figure, and that the mean speed in the space 19 is several meters per second.
  • temperatures there are found, for example, in the end zone 18 of the ribs a temperature in the neighborhood of C. and on a zone extending along their sides, between the points 20 and 21, temperatures ranging from 135 to 250 C. favoring complex boiling. Lower down, towards the base 22 of the throats, the temperature is even higher and gives rise to a purely film like vaporization.
  • the liquid to be vaporized in the depressions of the exchanger wall is introduced thereinto by branching off from a small part of the main flow which is arranged to occur outwardly of the wall 1.
  • This branching results on the one hand from the component of speed which the flow can present in the preferred direction of the depressions-the longitudinal direction 12 of the throats in the example of FIGURE l and, on the other hand, in the turbulence of the liquid in Jerusalem due to the component of its direction 11, transverse to the depressions. This latter fact is only due from the necessary branching, if the flow direction no longer PQS.
  • the width e of the space in which the main flow is confined is not very critical but, when determining this Width, there must be taken into account that the efiiciency of heat exchange by condensation is increased with the speed and the turbulence of the liquid in circulation. A speed of several meters per second is already sufficient to ensure good performance. As the angle a approaches the speed may be increased. Keeping speed constant requires choice of a width e which increases proportionally to the length of the main flow path, since the necessary output is proportional to the power to be dissipated, and thus to the length of the exchanger wall in the main flow direction. There have been obtained good results with widths 2 equal to where L is the length of the main flow path and k a number between 0.3 and 3.
  • the temperature received at the outlet of the exchanger can be in the neighborhood of its boiling temperature, for example, in the region of 100 C. for water under normal atmospheric pressure, and C. for a pressure of 2 atmospheres. From this there result the following points of view for the choice of the factor k:
  • the hydrodynamic resistance is high, thus compatible with small outputs which have high heating; for example, of 75 C. with flow of water of 0.2 liter/ min./ kw.
  • the inlet temperature must, in this case, be fairly low, so that, for example, town water can be used without reuse, since only small quantities are needed; further, there is obtained as a byproduct some very hot water which can be put to various uses.
  • b is the depth of the throats, defined previously and measured in centimeters, a the mean width of the straight section of the ribs measured in centimeters, c the thermal conductivity of the constituent material of the exchanger wall, measured in watts/cm., degree centigrade, and m a numerical factor of the order of 1, preferably comprised between 0.7 and 1.8.
  • Width d of the throats there are advantageously adopted values which are less than preferably less than of their depth b thus defined. Similar dimensions, although for heat exchangers with recondensation, have already been given previously by the applicant.
  • an advantageous arrangement likewise covered by the invention, consists in cutting off the ends of the ribs separating the throats in the form of crenellations.
  • This arrangement locally increases the turbulence of the liquid in the opening region of the throats.
  • it accentuates the specific effect sought by the invention, namely, supplying a sufficient quantity of liquid in the throats without resulting in a uselessly high flow in the direction of their length.
  • the ribs can be cut in a direction which is substantially orthogonal, by a reduced number of draining members or channels, which contribute to the feeding of the throats without effecting a flow in the direction of their length.
  • FIG. 3 shows a heat exchanger constructed in accordance with the invention, the exchanger wall 1 of which, in cylindrical form, constitutes the outer anode of an electronic tube 27.
  • the guide wall 2 forms, with the distribution chamber 3 and the collecting chamber 5, a casing by the open end of which there is introduced the anode of the electronic tube until a flange 28 surrounding the anode abuts against a water-tight joint 29, itself mounted on a ledge 30 in the said casing.
  • Wing nuts, such as 31, 32 ensure the connection and the watertightness of the assembly.
  • the exchange device thus constructed presents again the following differences with respect to those of FIG.
  • the throats have a rectangular section and form parallel helices coaxial with the wall of 1; the throats discharge not only into the distribution chamber 3 but also into the collecting chamber 5; finally, the main direction of flow substantially transverse to the direction of the throats, is ensured by the joint effect of the chambers 3 and 5, disposed at the ends of the cylindrical guide wall 2, and of a series of direction blades 33, disposed parallel to the axis of the device in the confined space 19. These blades can be fixed either to the guide wall 2 or to the exchanger wall 1.
  • the exchanger shown in FIG. 4 serving likewise to cool the anode of an electronic tube, presents with respect to the proceeding example the following differences: the ribs are disposed circularly around the anode, and the bases of the throats are rounded.
  • the main flow is directed to be slightly inclined with respect to the generatrices of the cylindrical exchanger wall, by a series of blades 34, extending, as seen obliquely, between the exchanger wall 1 and the guide wall 2.
  • the guide wall does not constitute the complete envelope of the device. It is surrounded by a spaced sleeve 35.
  • a dilatable elastic body 37 for example, in an outlet tube 6 inserted in its flat base.
  • a dilatable elastic body 37 for example, in the form of a hollow rubber toroid kept in place by a grid 38 is located in this space. Such an elastic body deadens and even eliminates certain abrupt pressure variations which can accompany the condensation in the turbulent system in the confined space.
  • the throats can, for example, present a width of d of 2. mm. and a depth b of 7 mm.
  • the width a of the ribs can likewise be 2 mm. and the distance e between the ribs and the guide wall 2 may be 0.3 to 3 mm.
  • the changer wall present an inlet surface for heat of 150 cm. is capable of continuously dissipating more than 250 kw., with a water flow in the order of one liter per second, the water temperature at the outlet being of the order of 100 C.
  • FIG. 5 shows an exchanger, the exchanger wall 1 of which constitutes the anode of an electron beam tube.
  • the impact surface for the electrons thus the heat receiving surface 17 of the wall 1
  • the Wall 1 comprises outer throats 3 disposed in circular formation.
  • the distribtution chamber 3 and the outlet tube 6 are arranged in such a manner that the liquid flows along the generatrices of the conical wall, thus at an angle on of with respect to the direction of the throats.
  • the distance between the exchanger wall 1 and the guide wall 2 increases from the base of the cone towards its apex, so that the flow speed is substantially the same along the whole exchanger surface.
  • the circulation of the liquid can be established at random in the direction of the arrows or in the opposite direction.
  • the heat exchanger shown in FIGURES 6 and 7 possesses, as in the exchangers shown in FIGURES 3 and 4, a cylindrical exchanger wall but with the difference that in that exchanger, the two ends of the cylindrical body to be cooled are outside the heat exchange device, an arrangement which would be adopted, for example, for cooling the cylinders of internal combustion engines.
  • the throats 9 are arranged parallel to the axis of the wall 1 and present as do the ribs 10 which separate them, a section of triangular form.
  • a guide surface 2 with which there are associated a distribution chamber 3, provided with an inlet tube 4, and a collecting chamber 5, provided with an outlet tube 6.
  • the lower lateral walls 40 and 41 of the distribution chamber are concave so as to inject the liquid tangentially into the confined space 19. Due to this arrangement, the main flow of liquid is constituted by an annular sheet in rotational movement around the exchanger wall, thus perpendicular to the direction of the throats 9. The flow of this liquid in circular motion can be greater than that entering by the chamber 3 and leaving by the chamber 5. It is not necessary for these two chambers to be disposed in diametrically opposite regions of the guide wall 2 as in FIGURES 6 and 7 shown by way of example only.
  • the heat exchanger in accordance with the invention has been described in structures to cool electronic tubes and parts of thermal motors.
  • the invention may also advantageously be applied to different apparatus, in which intense thermal energy must be removed, for example, to parts of chemical reactors and to nuclear fuel elements.
  • there can be grouped together several of these parts in the same casing for example, several cylinders of a thermal motor or clusters of nuclear fuel elements.
  • the casing of the device can be used to constitute the guide wall or a part thereof, other means for guiding being disposed inside the assembly for directing the main flow in the required direction relative to the throats of each of the exchanger walls.
  • the convex as well as the concave surface can form the outlet surface for heat.
  • these can be disposed in such a manner that each serves as a guide wall for the other.
  • a heat exchange arrangement to transfer heat from a heated wall to a circulating heat removing liquid by local evaporation accompanied by recondensation in the mass of the liquid comprising a heat transfer surface formed with a plurality of longitudinally extending throats having side walls;
  • each said throat being greater than the distance separating the edges between any one pair of side walls of said throats;
  • said liquid flow directing means comprising a distribtuion chamber arranged adjacent said inlet and a collecting chamber adjacent said outlet, said chambers being contiguous with a confined space limited by the heat transfer surface and the guide wall, 'and extending in a direction which is between parallel and 45 with respect to said throats, whereby the direction of flow will be essentially over said throats.
  • a heat exchange arrangement according to claim 1, wherein the transfer surface is cylindrical and the throats are of helical form arranged between the distribution chamber and the collecting chamber.
  • liquid flow directing means comprises guide blades disposed in the space confined by the heat transfer surface and the guide wall.
  • a heat exchange arrangement according to claim 1, wherein said heat transfer surface is a surface of revolution and the throats are formed circularly and coaxially with respect thereto.
  • a heat exchange arrangement according to claim 1, wherein said heat transfer surface is cylindrical and the throats are formed on a plurality of helices.
  • said throats have straight sections, the mean width of which is less than /3 the depth of the said throats.
  • b and a are expressed in centimeters
  • c designates the thermal conductivity of the constituent material of the heated wall expressed in watts/centimeterx C.
  • m is a numeric factor of the order of 1 comprised between the limits 0.7 and 1.8.
  • L is the mean length of the main flow path and k a numeric factor of the order of 1 comprised between the limits 3 and 0.3.
  • the device comprises means forcibly circulating a major part of the liquid over said surface and in a direction of flow which, with respect to the longitudinal direction (12) of the throats (9) forms an angle at between and 90.
  • Heat exchange device wherein the angle a is in the range of from to whereby the direction of said flow will be essentially transverse to said throats.
  • a method of removing heat from a heat-exchange surface having a plurality of substantially parallel deeper than wide grooves formed therein including the step of circulating a heat exchange fluid in contact with said surface, the improvement comprising the step of contacting the interior of said grooves with heat exchange fluid to remove heat from the walls defining said grooves by local evaporation, while forcibly circulating liquid heat-exchange fluid over the heat-exchange surface to re-condense said evaporating heat-exchange fluids into the mass of said circulating liquid fluid.
  • Method according to claim 14 wherein the steps of contacting the interior of said grooves and recondensing said fluid includes a step of forcibly circulating said liquid fluid over said surface in a direction essentially transverse with respect to said grooves and forming an angle with the major extent of said grooves of from between 45 to 90.
  • step of circulating said liquid fluid includes the step of circulating said liquid fluid 'at an angle with respect to the grooves of from between 80 to 90.

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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)
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US662443A 1966-09-15 1967-08-22 Heat exchanger Expired - Lifetime US3455376A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR76446A FR1502797A (fr) 1966-09-15 1966-09-15 Perfectionnements aux dispositifs d'échange de chaleur entre une paroi et un liquide

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US (1) US3455376A (fr)
JP (1) JPS5025181B1 (fr)
CH (1) CH485191A (fr)
DE (1) DE1601173B2 (fr)
FR (1) FR1502797A (fr)
GB (1) GB1194249A (fr)
NL (1) NL159806B (fr)
OA (1) OA04925A (fr)

Cited By (16)

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Publication number Priority date Publication date Assignee Title
US4546697A (en) * 1984-10-03 1985-10-15 Black & Decker, Inc. Drip coffeemaker hot water generator
US4796693A (en) * 1985-10-31 1989-01-10 Wieland-Werke Ag Finned tube with indented groove base and method of forming same
FR2627898A1 (fr) * 1988-02-26 1989-09-01 Thomson Csf Tube electronique refroidi par circulation d'un fluide
US4904054A (en) * 1987-09-17 1990-02-27 Pioneer Electronic Corporation Projection apparatus for projection television receiver
US5034688A (en) * 1988-05-05 1991-07-23 Ets Gourdon Temperature conditioning support for small objects such as semi-conductor components and thermal regulation process using said support
US5040596A (en) * 1988-04-13 1991-08-20 Mitsubishi Aluminum Kabushiki Kaisha Heat exchanger core
FR2686190A1 (fr) * 1991-08-30 1993-07-16 Eev Ltd Magnetron muni d'un dispositif de refroidissement.
US6531206B2 (en) 2001-02-07 2003-03-11 3M Innovative Properties Company Microstructured surface film assembly for liquid acquisition and transport
US20050106360A1 (en) * 2003-11-13 2005-05-19 Johnston Raymond P. Microstructured surface building assemblies for fluid disposition
US20070000644A1 (en) * 2005-06-29 2007-01-04 Microvection, Inc. Microchannel cooling device for small heat sources
US20080073061A1 (en) * 2006-09-27 2008-03-27 Rajen Dias Variable depth microchannels
US20100091457A1 (en) * 2008-06-18 2010-04-15 Brusa Elektronik Ag Cooling system for electronic structural units
US20110100603A1 (en) * 2005-06-29 2011-05-05 Science Research Laboratory, Inc. Microchannel cooling device for small heat sources
US20160014930A1 (en) * 2012-03-08 2016-01-14 International Business Machines Corporation Cold plate with combined inclined impingement and ribbed channels
US10270220B1 (en) 2013-03-13 2019-04-23 Science Research Laboratory, Inc. Methods and systems for heat flux heat removal
US11598518B2 (en) * 2011-05-13 2023-03-07 Rochester Institute Of Technology Devices with an enhanced boiling surface with features directing bubble and liquid flow and methods thereof

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5387841A (en) * 1991-08-30 1995-02-07 Eev Limited Magnetron having an anode with cooling channels
CN113168923B (zh) * 2018-10-31 2024-08-30 陆地能源美国公司 发电站

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US2098380A (en) * 1936-07-19 1937-11-09 Telefunken Gmbh Gas discharge device
US2863078A (en) * 1955-07-07 1958-12-02 Sperry Rand Corp Electrode heat exchanger for electron discharge tubes
US2969957A (en) * 1956-01-10 1961-01-31 Thomson Houston Comp Francaise Electric discharge device cooling systems
US3046429A (en) * 1958-06-06 1962-07-24 Thomson Houston Comp Francaise High frequency energy interchange device
FR1349387A (fr) * 1962-12-05 1964-01-17 Commissariat Energie Atomique Perfectionnements apportés aux échangeurs de chaleur
US3235004A (en) * 1962-02-23 1966-02-15 Thomson Houston Comp Francaise Heat dissipating structure

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2098380A (en) * 1936-07-19 1937-11-09 Telefunken Gmbh Gas discharge device
US2863078A (en) * 1955-07-07 1958-12-02 Sperry Rand Corp Electrode heat exchanger for electron discharge tubes
US2969957A (en) * 1956-01-10 1961-01-31 Thomson Houston Comp Francaise Electric discharge device cooling systems
US3046429A (en) * 1958-06-06 1962-07-24 Thomson Houston Comp Francaise High frequency energy interchange device
US3235004A (en) * 1962-02-23 1966-02-15 Thomson Houston Comp Francaise Heat dissipating structure
FR1349387A (fr) * 1962-12-05 1964-01-17 Commissariat Energie Atomique Perfectionnements apportés aux échangeurs de chaleur

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4546697A (en) * 1984-10-03 1985-10-15 Black & Decker, Inc. Drip coffeemaker hot water generator
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Also Published As

Publication number Publication date
OA04925A (fr) 1980-10-31
SU441722A3 (ru) 1974-08-30
FR1502797A (fr) 1967-11-24
CH485191A (fr) 1970-01-31
DE1601173B2 (de) 1976-11-11
NL6712389A (fr) 1968-03-18
GB1194249A (en) 1970-06-10
NL159806B (nl) 1979-03-15
DE1601173A1 (de) 1970-06-18
JPS5025181B1 (fr) 1975-08-21

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