US3811496A - Heat transfer device - Google Patents

Heat transfer device Download PDF

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Publication number
US3811496A
US3811496A US00303270A US30327072A US3811496A US 3811496 A US3811496 A US 3811496A US 00303270 A US00303270 A US 00303270A US 30327072 A US30327072 A US 30327072A US 3811496 A US3811496 A US 3811496A
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United States
Prior art keywords
wire
bore
tube wall
section
heat transfer
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Expired - Lifetime
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US00303270A
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English (en)
Inventor
G Asselman
A Dirne
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US Philips Corp
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US Philips Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
    • F28D15/02—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/04—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
    • F28D15/046—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 characterised by the material or the construction of the capillary structure
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making
    • Y10T29/49353—Heat pipe device making

Definitions

  • ABSTRACT A heat transfer device (heat pipe) in which the layer of material having a capillary structure for the transport of condensate from the condensor to the evaporator is formed by helically wound wire which has grooves transversely to the axis of the wire.
  • the invention relates to a heat transfer device comprising a closed tubular container having at one end a first tube wall section, at the other end a second tube wall section, and an intermediate third tube wall section.
  • the container comprises a heat transfer medium which absorbs thermal energy from the first tube wall section while changing from the liquid phase into the vapour phase and delivers thermal energy to the second tube wall section while changing from the vapour phase into the liquid phase.
  • the container furthermore comprises a layer of material having a capillary structure and covering the tube wall for transporting condensed medium from the second to the first tube wall section.
  • the layer of material having a capillary structure ensures that condensate can flow back in all circumstances from the second to the first tube wall section, even against gravity or without gravity field. Gauzes of wire or band-shaped material often serve as a layer of material having a capillary structure in heat pipes.
  • a drawback of the use of gauzes is that the condensate transport capacity and hence the heat transfer capacity of the device is restricted by it. This is caused by the fact that the large number of wires of the gauze structure which extend transversely to the direction of condensate transport inhibit flow of condensate.
  • the heat transfer device is characterized in that the layer of material is formed by at least one wire which is wound helically against the tube wall in the direction of the tube axis and which is provided with several capillary grooves which are distributed over the length of the wire, and extend transversely to the axis of the wire over at least that part of the circumference of the wire which faces the adjacent tube wall surface.
  • the grooves can be provided in the wire in an easy and admissible manner.
  • the wire which is provided with grooves may then be wound helically and be inserted into the tubular container in the wound-condition so as to fit accurately. It is alternatively possible to arrange the wire against the tube wall in the container while winding.
  • a layer of material having a capillary structure is obtained in a simple manner in which the capillary grooves in the wire also bounded by the tube wall extend mainly in the axial direction, namely the condensate transport direction, of the device.
  • the present system of grooves may have the same large condensate transport capacity as heat transfer devices having axial grooves in the wall of the tubular container.
  • the wire should be wound with such a pitch that gaps between the turns do not become too large.
  • gap width is too large, heat transfer medium condensate remains no longer caught in the capillary structure and the operation of the device is disturbed.
  • the turns of the wire section which covers the third tube wall section mutually engage each other.
  • the winding of said wire section is much simpler but the engaging turns also constitute a closed surface which separates medium condensate in the transport zone from medium vapour present in said zone. Due to the absence of a free phase surface area of heat transfer medium in vapour and in liquid form in the transport zone, no liquid particles from the layer of material having capillary structure can be dragged along by medium vapour. As a result of this a large heat transfer capacity is maintained.
  • a further favorable embodiment of the heat transfer device according to the invention is characterized in that the capillary grooves in the wire section which covers the first part of the tube wall extend throughout the circumference of the wire.
  • the wire section which covers the first section of the tube wall with circumferential grooves, the advantage is obtained from a point of view of winding technology that the turns can engage each other while medium evaporating on the first section of the tube wall can nevertheless freely reach the vapour space since the circumferential grooves ensure apertures in the continuous row of turns of wire.
  • the capillary grooves in the wire section which covers the second section of the tube wall may also extend throughout the circumference of the wire. It must be be possible for medium vapour to condense freely on the second tube wall section forming the condensation zone. This remains the case when the turns of the wire section which covers the second tube wall section engage each other, since the circumferential grooves again constitute apertures in the closed row of turns.
  • a further favorable embodiment of the heat transfer device according to the invention is characterized in that the capillary grooves in the wire section which covers the first tube wall section have a smaller hydraulic diameter and center distance than the capillary grooves in the wire section covering the third tube wall section.
  • the hydraulic diameter is defined as 4 X (surface cross-section/circumference) of the groove. Since comparatively many and small grooves are present per unit of length of wire in the wire section which covers the first tube wall section (evaporation zone) a large capillary suction force is produced, the driving force for condensate transport, relative to the wire section which covers the third tube wall section (transport zone) and which comprises comparatively few and large grooves. Due to the few large grooves the flow losses in the transport zone are small. All this is of particular advantage in heat transfer devices having transport zones and/or evaporation zones of alarge length.
  • the capillary grooves in the wire section which covers the second tube wall section may have a smaller hydraulic diameter and center distance than the capillary grooves in the wire section covering the third tube wall section.
  • the helically wound wire is a helical spring which engages the tube wall by resilience. This offers the advantage that an extra connection of the wire against the tube wall, for example by'sintering, is not necessary.
  • the helical spring is internally hollow.
  • the closed cavity contains a filling medium the pressure of which, at least at the operating temperature of the device, is higher than the pressure in the container, and the helical spring remains pressed against the tube wall under the influence of the pressure differential across it.
  • the pressure of the filling medium in the helical spring need not always be higher than the pressure which prevails in that case in the container but it may then be equal to or even lower than the pressure in the container.
  • the resilience of the helical spring at room temperature usually is sufficient to keep the spring pressed against the tube wall.
  • the pressure in the container is otherwise usually low since the container is often evacuated in order that the evaporation-condensation process of the heat transfer medium can run off smoothly.
  • All kinds of material which are solid, liquid or gaseous at room temperature may be considered as a filling medium, provided the vapour pressure and gas pressure, respectively, of said materials is higher than the pressure in the container at any rate at the operating temperature of the device and possibly also at room temperature.
  • potassium or calcium may be used as a filling medium.
  • the filling medium is an inert gas. This offers the advantage that in the case of an unexpected leakage of the helical spring, no chemical reactions occur between the heat transfer medium and the filling medium. In that case the device is not damaged.
  • FIG. 1a shows in elevation view in section the heat transfer device of this invention.
  • FIG. lb shows a cross-sectional view of the device taken along lines lblb in FIG. la.
  • FIG. 10 shows a longitudinal sectional view of the grooves of FIG. la.
  • FIG. 1d is a sectional view of the wire taken along line ldld in FIG. 1c.
  • FIG. 2a, 3a, 4a and 5 show other embodiments of the heat transfer device in sectional, elevation views.
  • FIG. 2b is a cross-sectional view taken on the line IIb-IIb in the evaporation zone of the device shown in FIG. 2a.
  • FIGS. 2c and 2d are a longitudinal cross-sectional view and a cross-sectional view of wire which is provided with circumferential grooves, which wire is present on the first and the second tube wall section 2 and 3, respectively.
  • FIG. 3b is a sectional view taken on the line IIIbIIIb of FIG. 3a.
  • FIG. 4a shows in sectional, elevation view another embodiment of this invention.
  • FIG. 4b is a sectional view of the device taken along line IVb-IVb in FIG. 4a.
  • FIG. 5 is an elevation view in section of another embodiment of the device of this invention.
  • Reference numeral 1 in FIG. 1a denotes a closed cylindrical container having at one end a first tube wall section 2 and at the other end a second tube wall section 3 separated from each other by an intermediate third tube wall section 4.
  • the container 1 comprises a suitably chosen quantity of sodium as a heat transfer medium and is otherwise evacuated.
  • a wire 5 which is wound helically in the axial direction of the cylinder.
  • the wire comprises grooves which extend transversely to the wire axis over half the circumference of the wire and which face the adjoining tube wall surface.
  • the grooves in the wire are shown in detail in FIG. which is a longitudinal sectional view of the wire.
  • the turns of the wire 5 in the container 1 engage each other very closely in this case so that there are very narrow gaps between the turns.
  • liquid sodium absorbs thermal energy through the first tube wall section 2 serving as an evaporator from a heat source not shown, as a result of which said, sodium evaporates.
  • sodium vapour then flows to the second tube wall section 3 (condensor) as a result of the lower vapour pressure there due to a slightly lower temperature at that area.
  • the sodium vapour condenses on the second tube wall section while giving off thermal energy.
  • the condensate then flows through the grooves in the wire 5 on the basis of capillary action, while using the surface tension of the condensate, back to the first tube wall section 2 to be evaporated there again.
  • the third tube wall section 4 constitutes a transport zone.
  • FIGS. 2 to 5 the same reference numerals are used for parts corresponding to the device shown in FIG. 1 except that numerals of FIG. 2 have added, FIG. 3 have added, FIG. 4 have (r) added, and FIG. 5 have (s) added.
  • the turns of wire 5' readily engage each other.
  • the wire sections which cover the first and the second tube wall section 2' and 3' have grooves which extend throughout the circumference of the wire as is shown in detail in the longitudinal sectional view of FIG. 2c and in a cross-sectional view of the wire shown in FIG. 2d.
  • the wire section which covers the third tube wall section 4' on the contrary has grooves which extend only over a part of the circumference of the wire.
  • the lastmentioned wire section has fewer and larger grooves than the wire sections which cover the first and the second tube wall section 2' and 3. Since all the wire turns engage each other mutually, winding is very simple.
  • the continuous row of turns at the area of the third tube wall section 4 beautifully forms a partition between sodium condensate and sodium vapour. Sodium vapour on its way from the first to the second tube wall section cannot drag along condensate drops of the third tube wall section 4', which would mean a reduction of the heat transfer capacity of the device. Due to the few coarse grooves in the wire section on the third tube wall section 4 the condensate flowing through it will have small flow losses.
  • the many small circumferential grooves extending transversely to the wire axis over the circumference of the wire in the wire section which covers the first tube wall section provide apertures in the continuous row of turns so that sodium can freely evaporate via said apertures of the relevant wall section. They furthermore ensure a large liquid vapour phase surface area so that a large heat flow can be conveyed through a surface unit of the tube wall section. Finally they produce a large capillary suction force which ensures the transport of condensate.
  • Analogous construction of the wire section which covers the second tube wall section provides the advantage of an easy removal of condensate owing to on the one hand the many apertures in the closed row of turns and on the other hand the large capillary suction force.
  • the heat transfer device shown in FIG. 3 comprises a tubular container 1" which has parts of different diameters and which is rectangular in cross-section.
  • two helical springs 6 and 7 are present which remain'pressed against the walls of the container by resilience.
  • the helical spring 6 covers the first tube wall section 2" while the helical spring 7 covers the second tube wall section 3" and the third tube wall section 4
  • Helical spring 6 only has circumferential grooves divided over the whole wire length transversely to the wire axis; helical spring 7 only over the wire section which covers the second tube wall section 3".
  • FIG. 4a shows a cylindrical heat transfer device in which the first tube wall section 2r bounds a cylindrical space which is present within the dimensions of the heat transfer device.
  • the device is otherwise the same as that of FIG. 2.
  • FIG. 5 shows a heat transfer device in which a helical spring 8 is present in a closed container is which spring comprises circumferential grooves which extend transversely to the wire axis and are distributed over the whole length of the wire.
  • Helical spring 8 is internally hollow.
  • the cavity 9 constitutes a closed space in which a quantity of argon is present as a filling medium.
  • the operating temperature of the heat transfer device is, for example, 1 K
  • the vapour pressure of the sodium in the otherwise evacuated container 1 is 450 Torr (1 Torr 1 mm mercury pressure).
  • a suitable chosen quantity of argon in the helical spring 8 it is achieved that at the said high temperature the argon pressure in the spring is higher than 450 Torr, for example, 2 atmosphere.
  • wires When several wires are used in one heat transfer device, said wires may mutually have different diameters and/or be manufactured from different materials. Wires having a comparatively small diameter could then cover the first and the second tube wall section while a wire having a comparatively large diameter is used for the third tube wall section. Furthermore, one or more wound wires can be combined with one or more helical springs in one heat transfer device.
  • a heat transfer device comprising a closed tubular container having at one end a first tube wall section, at the other end a second tube wall section, and an intermediate third tube wall section, said container comprising a heat transfer medium which absorbs thermal energy from the first tube wall section while changing from the liquid phase into the vapour phase and delivers thermal energy to the second tube wall section while changing from the vapour phase into the liquid phase, the container furthermore comprising a layer of material having a capillary structure and covering the tube wall for the transport of condensed medium from the second in the first tube wall section, characterized in that the layer of material is formed by at least one wire which is wound helically against the tube wall in the direction of the tube axis and which comprises several capillary grooves distributed over the length of the wire and extending transversely to the wire axis over at least thatpart of the wire circumference which faces the adjacent tube wall surface.
  • aheat-pipe heat transfer device formed as a closed container having walls whose inner surfaces define a tubular bore which has a longitudinal axis, said bore comprising a first section extending from one end of the bore inward, a second section extending from inward from the other end of the bore, and a third section intermediate said first and second sections, the device further including within said bore a heat transfer medium which changes from liquid to vapor phase upon absorbing thermal energy and changes from vapor to liquid phase while giving up thermal energy, the improvement in combination therewith, a helically wound wire within said bore with the outer surface of the wire adjacent said bore surface and said helical axis thereof generally aligned with said bore axis, said wire further comprising on at least that part of its outer surface adjacent said bore surface, capillary grooves which extend generally transversely of the wire axis, whereby said grooves and bore surface comprise a capillary structure and said medium when condensed to a liquid will be transportable along said bore by capillary action therein.
  • a heat transfer device according to claim 2 wherein the capillary grooves in the wire section which covers the first tube wall section have a smaller hydraulic diameter and center distance than the capillary grooves in the wire section covering the third tube wall section.
  • a heat transfer device according to claim 2 wherein the capillary grooves in the wire section which covers the second tube wall section have a smaller bydraulic diameter and center distance than the capillary grooves in the wire section covering the third tube wall section.
  • a heat transfer device wherein the helical wound wire is a helical spring whose resilience urges same outward to engage said bore surface.
  • a heat transfer device wherein the helical spring is tubular having walls which define a closed cavity, the device further comprising in said cavity a filling medium the pressure of which, at least at the operating temperature of the device, is higher than the pressure of said medium in the container for urging the helical spring against said bore surface due to the influence of the pressure differential across the springs tubular walls 7.
  • Apparatus according to claim 2 wherein said wound wire comprises turns and the turns in said third section of the bore are mutually engaged which thereby form a tubular section that separates the bore through said turns from space outside said turns.
  • a heat transfer device according to claim 8 wherein the filling medium is an inert gas.
  • a heat-pipe heat transfer device comprising a closed container having walls whose inner surfaces define a tubular bore which has a longitudinal axis, said bore comprising a first section extending from one end of the bore inward, a second section extending inward from the other end of the bore, and a third section intermediate said first and second sections, the device further comprising within said bore a heat transfer medium which changes from liquid to vapor phase upon absorbing thermal energy and changes from vapor to liquid phase while giving up thermal energy, and a helically wound wire within said bore with the outer surface of the wire adjacent said bore surface and said helical-axis thereof generally aligned with said bore axis, said wire further comprising on at least that part of its outer surface adjacent said bore surface, capillary grooves which extend generally transversely of the wire axis, whereby said grooves and bore surface comprise a capillary structure and said medium when condensed to a liquid will be transportable along said bore by capillary action therein.

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  • Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Filling Or Discharging Of Gas Storage Vessels (AREA)
US00303270A 1971-11-06 1972-11-02 Heat transfer device Expired - Lifetime US3811496A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
NL7115318A NL7115318A (enrdf_load_stackoverflow) 1971-11-06 1971-11-06

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US3811496A true US3811496A (en) 1974-05-21

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US00303270A Expired - Lifetime US3811496A (en) 1971-11-06 1972-11-02 Heat transfer device

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US (1) US3811496A (enrdf_load_stackoverflow)
JP (1) JPS5320150B2 (enrdf_load_stackoverflow)
CA (1) CA962997A (enrdf_load_stackoverflow)
DE (1) DE2252292C3 (enrdf_load_stackoverflow)
FR (1) FR2158548B1 (enrdf_load_stackoverflow)
GB (1) GB1403447A (enrdf_load_stackoverflow)
IT (1) IT970221B (enrdf_load_stackoverflow)
NL (1) NL7115318A (enrdf_load_stackoverflow)
SE (1) SE375152B (enrdf_load_stackoverflow)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3862481A (en) * 1972-10-14 1975-01-28 Philips Corp Method of manufacturing tubes provided with longitudinal grooves in inner wall and/or outer wall, and tubes manufactured by this method
US4616699A (en) * 1984-01-05 1986-10-14 Mcdonnell Douglas Corporation Wick-fin heat pipe
BE1006926A3 (nl) * 1993-03-24 1995-01-24 Philips Electronics Nv Warmtetransportinrichting, hogedrukontladingslamp voorzien van een warmtetransportinrichting en elektrodeloze lagedrukontladingslamp voorzien van een warmtetransportinrichting.
US20060108103A1 (en) * 2004-11-19 2006-05-25 Delta Electronics, Inc. Heat pipe and wick structure thereof
RU2313733C1 (ru) * 2006-03-10 2007-12-27 Сергей Дмитриевич Дмитриев Устройство для вентиляции помещения
US20080029249A1 (en) * 2006-08-01 2008-02-07 Inventec Corporation Supporting column having porous structure
US20080245511A1 (en) * 2007-04-09 2008-10-09 Tai-Sol Electronics Co., Ltd. Flat heat pipe
US20100326630A1 (en) * 2009-06-24 2010-12-30 Fu Zhun Precision Industry (Shen Zhen) Co., Ltd. Heat spreader with vapor chamber and method for manufacturing the same
US20130081620A1 (en) * 2011-09-30 2013-04-04 Neil Korneff Fluted heater wire
US9067036B2 (en) 2011-09-30 2015-06-30 Carefusion 207, Inc. Removing condensation from a breathing circuit
US9212673B2 (en) 2011-09-30 2015-12-15 Carefusion 207, Inc. Maintaining a water level in a humidification component
US9272113B2 (en) 2012-03-30 2016-03-01 Carefusion 207, Inc. Transporting liquid in a respiratory component
US9867959B2 (en) 2011-09-30 2018-01-16 Carefusion 207, Inc. Humidifying respiratory gases
US10168046B2 (en) 2011-09-30 2019-01-01 Carefusion 207, Inc. Non-metallic humidification component

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS50117450U (enrdf_load_stackoverflow) * 1974-03-08 1975-09-25
JPS5155460U (enrdf_load_stackoverflow) * 1974-10-28 1976-04-28
JPS5312544A (en) * 1976-07-20 1978-02-04 Sharp Corp Heat pipe
JPS5389064A (en) * 1977-01-14 1978-08-05 Oki Electric Cable Wick type heat tube
DE2834593A1 (de) * 1978-08-07 1980-02-28 Kabel Metallwerke Ghh Waermetauscher in form eines rohres
JPS55155192A (en) * 1979-05-21 1980-12-03 Agency Of Ind Science & Technol Thermosyphon type heat pipe
GB2117104A (en) * 1982-03-11 1983-10-05 Mahdjuri Sabet Faramarz Heat pipe for collecting solar radiation
DE3530645A1 (de) * 1985-08-28 1987-03-12 Philips Patentverwaltung Luft-luft-waermeaustauscher mit waermerohren

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3305005A (en) * 1965-12-03 1967-02-21 George M Grover Capillary insert for heat tubes and process for manufacturing such inserts
US3414475A (en) * 1965-05-20 1968-12-03 Euratom Heat pipes
US3498369A (en) * 1968-06-21 1970-03-03 Martin Marietta Corp Heat pipes with prefabricated grooved capillaries and method of making
US3554183A (en) * 1968-10-04 1971-01-12 Acf Ind Inc Heat pipe heating system for a railway tank car or the like
US3576210A (en) * 1969-12-15 1971-04-27 Donald S Trent Heat pipe

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3414475A (en) * 1965-05-20 1968-12-03 Euratom Heat pipes
US3305005A (en) * 1965-12-03 1967-02-21 George M Grover Capillary insert for heat tubes and process for manufacturing such inserts
US3498369A (en) * 1968-06-21 1970-03-03 Martin Marietta Corp Heat pipes with prefabricated grooved capillaries and method of making
US3554183A (en) * 1968-10-04 1971-01-12 Acf Ind Inc Heat pipe heating system for a railway tank car or the like
US3576210A (en) * 1969-12-15 1971-04-27 Donald S Trent Heat pipe

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3862481A (en) * 1972-10-14 1975-01-28 Philips Corp Method of manufacturing tubes provided with longitudinal grooves in inner wall and/or outer wall, and tubes manufactured by this method
US4616699A (en) * 1984-01-05 1986-10-14 Mcdonnell Douglas Corporation Wick-fin heat pipe
BE1006926A3 (nl) * 1993-03-24 1995-01-24 Philips Electronics Nv Warmtetransportinrichting, hogedrukontladingslamp voorzien van een warmtetransportinrichting en elektrodeloze lagedrukontladingslamp voorzien van een warmtetransportinrichting.
US20060108103A1 (en) * 2004-11-19 2006-05-25 Delta Electronics, Inc. Heat pipe and wick structure thereof
RU2313733C1 (ru) * 2006-03-10 2007-12-27 Сергей Дмитриевич Дмитриев Устройство для вентиляции помещения
US20080029249A1 (en) * 2006-08-01 2008-02-07 Inventec Corporation Supporting column having porous structure
US20080245511A1 (en) * 2007-04-09 2008-10-09 Tai-Sol Electronics Co., Ltd. Flat heat pipe
US20100326630A1 (en) * 2009-06-24 2010-12-30 Fu Zhun Precision Industry (Shen Zhen) Co., Ltd. Heat spreader with vapor chamber and method for manufacturing the same
US9067036B2 (en) 2011-09-30 2015-06-30 Carefusion 207, Inc. Removing condensation from a breathing circuit
US9642979B2 (en) * 2011-09-30 2017-05-09 Carefusion 207, Inc. Fluted heater wire
US20130081620A1 (en) * 2011-09-30 2013-04-04 Neil Korneff Fluted heater wire
US9205220B2 (en) * 2011-09-30 2015-12-08 Carefusion 207, Inc. Fluted heater wire
US9212673B2 (en) 2011-09-30 2015-12-15 Carefusion 207, Inc. Maintaining a water level in a humidification component
US9242064B2 (en) * 2011-09-30 2016-01-26 Carefusion 207, Inc. Capillary heater wire
US20160051789A1 (en) * 2011-09-30 2016-02-25 Carefusion 207, Inc. Fluted heater wire
US10168046B2 (en) 2011-09-30 2019-01-01 Carefusion 207, Inc. Non-metallic humidification component
US9289572B2 (en) 2011-09-30 2016-03-22 Carefusion 207, Inc. Humidifying gas for respiratory therapy
US20160101258A1 (en) * 2011-09-30 2016-04-14 Carefusion 207, Inc. Capillary heater wire
US20130081625A1 (en) * 2011-09-30 2013-04-04 Andre M. Rustad Capillary heater wire
US9724490B2 (en) * 2011-09-30 2017-08-08 Carefusion 207, Inc. Capillary heater wire
US9867959B2 (en) 2011-09-30 2018-01-16 Carefusion 207, Inc. Humidifying respiratory gases
US9272113B2 (en) 2012-03-30 2016-03-01 Carefusion 207, Inc. Transporting liquid in a respiratory component

Also Published As

Publication number Publication date
DE2252292C3 (de) 1980-04-17
IT970221B (it) 1974-04-10
FR2158548A1 (enrdf_load_stackoverflow) 1973-06-15
DE2252292B2 (de) 1979-08-09
CA962997A (en) 1975-02-18
JPS5320150B2 (enrdf_load_stackoverflow) 1978-06-24
NL7115318A (enrdf_load_stackoverflow) 1973-05-08
FR2158548B1 (enrdf_load_stackoverflow) 1976-08-20
SE375152B (enrdf_load_stackoverflow) 1975-04-07
JPS4858435A (enrdf_load_stackoverflow) 1973-08-16
DE2252292A1 (de) 1973-05-10
GB1403447A (en) 1975-08-28

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