EP0108525A1 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

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Publication number
EP0108525A1
EP0108525A1 EP83306295A EP83306295A EP0108525A1 EP 0108525 A1 EP0108525 A1 EP 0108525A1 EP 83306295 A EP83306295 A EP 83306295A EP 83306295 A EP83306295 A EP 83306295A EP 0108525 A1 EP0108525 A1 EP 0108525A1
Authority
EP
European Patent Office
Prior art keywords
tube
fluid
heat exchanger
fluid heat
tubes
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP83306295A
Other languages
German (de)
English (en)
Inventor
Richard W. Sievers
Ajit K. Ramachandran
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Thermodynetics Inc
Original Assignee
Thermodynetics Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Thermodynetics Inc filed Critical Thermodynetics Inc
Publication of EP0108525A1 publication Critical patent/EP0108525A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits

Definitions

  • This invention relates generally to the field of heat exchangers, and more particularly to high performance, compact fluid heat exchangers in which annularly corrugated tubing is utilized as part of tube-in-tube, shell and tube, or coil and shell (with or without centerbodies) heat exchangers which may have straight, "J"-shape, helix or similar configurations.
  • Heat exchangers of many types and configurations are well known and used to transfer heat from one fluid to another, to heat, cool, desuperheat, condense, evaporate or otherwise change the thermal energy level of a fluid. Heat transfer is accomplished by placing the two fluids in sufficiently close proximity to each other so that the cooler fluid will absorb the heat from the warmer fluid. Of course the heat transfer must occur without allowing the fluids to mix since, for example, if the cooler fluid is a refrigerant, brine solution or the like and the warmer fluid potable water, mixture would render the potable water useless. Likewise the warmer fluid could be contaminated and thus must be kept out of contact with the cooler fluid to avoid its contamination.
  • Heat exchanger structures made from helical twisted tubing have several disadvantages.
  • finned tubes may have relatively large surface area, such tubes are expensive to fabricate. Further, configurations of heat exchangers using finned tubes suffer from a substantial increase in the flow resistance in the area of the fins. In such case, fluid flowing over the fin direction transverse to the plane of the fin may tend to deposit any impurities or contaminants near the base of the fin in the area having the lower flow velocity. Such stagnation areas detract from the efficiency of the otherwise high-performing tube-in-tube heat exchanger.
  • finned tubes Another problem resulting from the use of finned tubes is the loss of heat exchange efficiency due to the high thermal resistance between the tube and the fin.
  • the junction of the two components adds thermal resistance and lowers the efficiency of the heat exchanger.
  • the fins added to the outside of the tube also tend to add to the rigidity of the assembly, which is disadvantageous in the many configurations of heat exchangers in which flexibility of the tube is required.
  • an improved fluid heat exchanger comprising a first tube having a passage therein, and a first and a second end, for carrying a first fluid in a first direction; a second tube disposed within said passage, and having a plurality of annular corrugations thereon, for carrying a second fluid in a second direction; an inlet connected to said first end of said first tube for introducing said first fluid to said first tube; and an outlet connected to said second end of said first tube, to remove said first fluid therefrom.
  • annularly corrugated tubes in the heat exchangers of the present invention provides improved heat transfer resulting from the greatly increased effective surface area of the heat exchanger boundary.
  • annularly corrugated inner tube provides in the range of 40-60% more useful heat transfer area (i.e., surface area) than a similar length of smooth wall tubing. This may be compared with the surface area of known twisted tubing, which provides merely 25-28% more area than smooth wall tubing.
  • Further improvement in the heat transfer effected by the device stems from the lack of extraneous (heat) conductive material on the surface of the tube, such as in conventionally configured tubes. Only the thickness of the tubing separates the two fluids.
  • annularly corrugated tube is far more flexible than known tubing. Not only does this arrangement avoid the introduction of inflexible exterior configurations to the tube, but it renders the tube more flexible than a smooth tube, or even a threaded tube.
  • annularly corrugated tubes since the manufacture of annularly corrugated tubes is well-known, it is possible to make such tubes with flat land portions thereon, which may further serve to increase the utility thereof.
  • the improved heat exchanger of the present invention has particular utility in the biomedical field as part of a blood oxygenator or a cardioplegia unit. It is particularly suitable for such applications since the annularly corrugated tubing has an increase in surface area per unit length. When the heat exchanger is used for such biomedical applications it is essential that the flow of blood through the heat exchanger remain in the laminar range to avoid undue frothing of the blood. Since the amount of heat transfer is substantially proportional to the surface area, the improved heat exchanger of the present invention, by increasing the surface area per unit length of the tube, makes it possible to obtain substantially the same degree of heat transfer at a lower flow rate.
  • a heat exchanger (made in accordance with the present invention) can have a smaller overall volume than a heat exchanger formed from a twisted helical tube of other prior art construction yet still have comparable performance.
  • the improved performance of the heat exchanger of the present invention overall requires that a lesser volume of blood need be removed from the patient's body during use of the blood oxygenator or cardioplegia unit.
  • annularly corrugated tubing in such biomedical applications is the reduced fill volume for the blood flow passages when all other dimensions remain constant. Since the annularly corrugated tubing occupies more volume than comparably sized helical twisted tubing necessarily there is less space for blood to flow. Since the increased surface area of the annularly corrugated tubing results in increased heat transfer there is no corresponding degradation in heat exchange performance although a smaller volume of blood is present in the biomedical unit.
  • FIGS. 1 and 2 there is shown a basic configuration of a tube-in-tube heat exchanger made in accordance with the present invention generally designated by the reference numeral 5.
  • a first, inner tube 10 is located within a second, outer tube 20 having an interior passage 21.
  • Inner tube 10 is formed with a series of annular corrugations 12, having troughs 13 and associated ridges 14 having a diameter less than the diameter of passage 21.
  • a first fluid 16 passes therethrough in a first direction designated generally by arrow 18.
  • Outer tube 20 is generally cylindrical, and attached to a feeder tube or inlet 22 and an exit tube or outlet 24 by connectors 26 and 28 respectively.
  • a second fluid 30 passes through feeder tube 22 into connector 26 in the direction designated by arrow 32, and follows feeder tube 22 to connector 28, and there exits from exit tube 24 in the direction designated generally by arrow 34.
  • the inner tube 10 comprises an alternating series of raised and lowered portions forming the annular corrugations.
  • the manufacture of annularly corrugated tubing is well known, and may be accomplished, for example, by rolling or finger forming. Methods for manufacturing such tubing are described in U.S. Patents Nos. 2,845,988 (Andersen); 2,864,591 (Frink); and 2,913,009 (Kuthe).
  • first fluid 16 or second fluid 30 could be the warmer, that the indicated opposing flow of the subject fluids is illustrative only, that both fluids may flow in the same direction, in that either may be at rest at some point and that the specific configuration of feeder tube 22 and exit tube 24 shown may be varied.
  • Figure 3 illustrates another embodiment of the invention, wherein elements corresponding generally to those of FIGS. 1 and 2 are indicated by similar numerals with the prefix "3" added thereto (e.g., first fluid 316).
  • second fluid 330 is the primary fluid (e.g., potable water, air) to be cooled by refrigerant 316.
  • This embodiment has been discovered also to have particular utility for condensers, as the annular grooves allow the formation of droplets therein.
  • FIGS. 4 and 5 A third embodiment of the invention is illustrated in FIGS. 4 and 5, in which the elements similar to those shown in FIGS. 1 and 2 have been identified with the prefix "4" followed by the corresponding reference numeral (e.g., first fluid 416).
  • This configuration of the present invention has particular utility as a blood oxygenator or cardioplegia unit when the additional known elements are added (by Spurgers).
  • This embodiment will be particularly described as such a device, although, as it will be appreciated, this configuration has other uses as a heat exchanger.
  • second fluid 430 would be blood
  • first fluid 416 would be coolant, generally tap water.
  • the configuration comprises an inner tube 410 carrying coolant 416 disposed within a shell (outer tube) 420 through which the second fluid, blood 430,passes.
  • Inner tube 410 is helically wound about a center body 440, which occupies the central volume of shell 420 to restrict the blood flow and thus ensure that the blood 430 passes close to the cooling inner tube 410.
  • Oxygenation of the blood will be performed by a Spurger (not shown) in the bottom of the shell 420 in known fashion.
  • FIG. 5 shows the arrangement of centerbody 440 which may be solid or hollow.
  • the outer surface of centerbody 440 and the inner surface of shell 420 define a flow path for the second fluid 430. Since the second tube 410 is located in the flow path, the second fluid 430 must flow through the small areas between adjacent annular corrugations on the surface of inner tube 410 and the inner surface of shell 420 in a direction parallel to the annular corrugation. Such restricted flow path results in much improved heat transfer.
  • the added flexibility of the annularly corrugated tube permits the inner tube 410 to be wraped more completely about the centerbody 440. This results in several key benefits.
  • more inner tubing 410 may be placed in the same volume of shell. This, taken together with the increased surface area of the unit length of inner tube (resulting from the annular corrugation configuration, as described above) drastically increases the heat transfer performance of the device. More importantly, the same amount of cooling may be performed by a smaller device.
  • the present invention when used as a blood oxygenator or cardioplegia unit, the absolute minimum volume of blood need be removed from the patient's body. When the patient is a child, the need to remove a small volume of blood is increased.
  • a flow path parallel to the annular corrugation results in much less turbulance within the shell.
  • this turbulance may lead to undesirable agitation and "frothing" of the blood.
  • the present invention when used as a blood oxygenator or cardioplegic device it may be possible to pass the blood through the device while still attaining the same degree of heat transfer.
  • the device pictured in FIG. 6 illustrates a tube in shell arrangement.
  • the elements common to those shown in FIGS. 1 and 2 have the prefix "6", (e.g., first fluid 616).
  • a plurality of inner tubes 610 are positioned within shell (outer tube) 620.
  • a series of alternating baffles 650 are disposed along its length. These baffles direct the flow of second fluid 630 in an "up/down" flow pattern, so that the flow is generally parallel to the annular corrugation 612.
  • heat exchange performance is optimized.
  • flat lands 660 may be disposed at predetermined locations along the length of inner tube(s) 610, and that these lands may serve the advantageous purpose of providing a place to which baffles 650 may be secured to inner tube 610.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP83306295A 1982-11-03 1983-10-17 Echangeur de chaleur Withdrawn EP0108525A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US43892082A 1982-11-03 1982-11-03
US438920 1982-11-03

Publications (1)

Publication Number Publication Date
EP0108525A1 true EP0108525A1 (fr) 1984-05-16

Family

ID=23742583

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83306295A Withdrawn EP0108525A1 (fr) 1982-11-03 1983-10-17 Echangeur de chaleur

Country Status (2)

Country Link
EP (1) EP0108525A1 (fr)
JP (1) JPS59100392A (fr)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0174319A1 (fr) * 1984-02-27 1986-03-19 Omnis Surgical Inc Echangeur de chaleur pour dispositif de transfert de masse.
FR2579313A1 (fr) * 1985-03-20 1986-09-26 Klein Schanzlin & Becker Ag Echangeur de chaleur a tube double coude
EP0217523A1 (fr) * 1985-09-09 1987-04-08 Zwick Energy Research Organization Système de refroidissement des gaz d'échappement d'un moteur à combustion interne
EP0247989A2 (fr) * 1986-05-27 1987-12-02 Level 1 Technologies, Inc. Dispositif autonome et transportable pour chauffer un liquide physiologique
EP0256653A2 (fr) * 1986-07-10 1988-02-24 Haemonetics Corporation Echangeur de chaleur compatible avec le sang
US4735775A (en) * 1984-02-27 1988-04-05 Baxter Travenol Laboratories, Inc. Mass transfer device having a heat-exchanger
US4872503A (en) * 1986-03-13 1989-10-10 Marriner Raymond E Air heat exchanger
US4895203A (en) * 1985-03-22 1990-01-23 Harold L. Hayes Heat exchanger with helically coiled conduct in casing
DE3932871A1 (de) * 1989-10-02 1990-02-01 Andreas Hahn Waermerueckgewinnungsrohr nach dem gegenstromprinzip, insbesondere fuer kuechen- und sanitaerinstallationen
EP0192506B1 (fr) * 1985-01-21 1990-04-04 Gaz De France Appareil de réchauffage d'un fluide, notamment accumulateur d'eau chaude sanitaire
GB2228563A (en) * 1989-02-28 1990-08-29 Michael John Nunnerley Heat exchange system
DE19624937A1 (de) * 1996-06-22 1998-01-02 Dickgreber Johannes Wärmetauscher
EP0985894A3 (fr) * 1998-09-08 2000-10-11 Witzenmann GmbH Metallschlauch-Fabrik Pforzheim Refroidisseur de carburant
WO2002001125A1 (fr) * 2000-06-28 2002-01-03 Igc Polycold Systems, Inc. Evaporateur d'appareil frigorifique a liquide
EP1136780A3 (fr) * 2000-03-23 2002-11-06 Senior Investments AG Echangeur de chaleur à tubes doubles
AT412293B (de) * 2003-01-13 2004-12-27 Porpaczy Johann Ing Wärmetauscher für zu kühlendes abwasser
US7063133B2 (en) * 2003-12-29 2006-06-20 Bradford White Corporation Multi-wall heat exchanger for a water heater
US7866378B2 (en) 2004-11-09 2011-01-11 Denso Corporation Double-wall pipe, method of manufacturing the same and refrigerant cycle device provided with the same
EP2295915A2 (fr) 2009-08-04 2011-03-16 Horst Valentin Tuyau à deux enveloppes doté d'un retour intégré
WO2011057594A1 (fr) * 2009-11-11 2011-05-19 Az Vermögensverwaltung Gmbh & Co. Kg Échangeur thermique à tubes concentriques
EP2354743A3 (fr) * 2010-01-15 2012-10-31 LG Electronics Inc. Échangeur thermique à double tuyau
DE102011100692A1 (de) * 2011-05-06 2012-11-08 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Flexibel anpassbarer Wärmetauscher für eine Kraftfahrzeug-Klimaanlage
DE102013105943A1 (de) * 2013-06-07 2014-12-11 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Kühlanordnung für einen Kraftfahrzeugantriebsstrang
US9279621B2 (en) 2010-08-12 2016-03-08 GM Global Technology Operations LLC Internal heat exchanger for a motor vehicle air-conditioning system
US11835301B2 (en) 2021-04-07 2023-12-05 Ecoinnovation Technologies Incorporée Modular heat exchanger and method of assembly thereof

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0579267U (ja) * 1992-03-23 1993-10-29 株式会社三浦研究所 過冷却水用熱交換器の水管形状
JPH06292226A (ja) * 1993-03-31 1994-10-18 Sanyo Electric Co Ltd 輝度信号／色信号／高域輝度信号分離装置
JP2012254553A (ja) * 2011-06-08 2012-12-27 Seiko Epson Corp 液体噴射装置

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1176522A (fr) * 1956-07-02 1959-04-13 Calumet & Hecla Tubes ondulés pour échangeurs de chaleur
US3219106A (en) * 1961-02-14 1965-11-23 United Aircraft Corp High-temperature radiator tube design
US3267997A (en) * 1962-09-20 1966-08-23 Aero Chatillon Corp Fluid cooled washer
FR1499286A (fr) * 1965-09-22 1967-10-27 Hackethal Draht & Kabelwerk Ag Tube échangeur de chaleur ainsi qu'appareil échangeur de chaleur constitué avec lesdits tubes
DE2236954A1 (de) * 1971-07-27 1973-02-08 Alfa Romeo Spa Waermetauscher
US3921708A (en) * 1970-10-07 1975-11-25 Ygnis Sa Heat exchanger and method of operation thereof
FR2322345A1 (fr) * 1975-08-29 1977-03-25 Multifluid En Echangeur de chaleur pour equipement de chauffage thermodynamique
FR2404824A1 (fr) * 1977-10-03 1979-04-27 Fortschritt Veb K Chambre annulaire de transfert thermique avec deux ou plusieurs tuyaux concentriques
US4171634A (en) * 1977-09-29 1979-10-23 Spiral Tubing Corporation Method of making corrugated tubing with graduated pitch
US4270601A (en) * 1980-01-07 1981-06-02 The Budd Company Heater for pre-heating fuel with a heated liquid

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1176522A (fr) * 1956-07-02 1959-04-13 Calumet & Hecla Tubes ondulés pour échangeurs de chaleur
US3219106A (en) * 1961-02-14 1965-11-23 United Aircraft Corp High-temperature radiator tube design
US3267997A (en) * 1962-09-20 1966-08-23 Aero Chatillon Corp Fluid cooled washer
FR1499286A (fr) * 1965-09-22 1967-10-27 Hackethal Draht & Kabelwerk Ag Tube échangeur de chaleur ainsi qu'appareil échangeur de chaleur constitué avec lesdits tubes
US3921708A (en) * 1970-10-07 1975-11-25 Ygnis Sa Heat exchanger and method of operation thereof
DE2236954A1 (de) * 1971-07-27 1973-02-08 Alfa Romeo Spa Waermetauscher
FR2322345A1 (fr) * 1975-08-29 1977-03-25 Multifluid En Echangeur de chaleur pour equipement de chauffage thermodynamique
US4171634A (en) * 1977-09-29 1979-10-23 Spiral Tubing Corporation Method of making corrugated tubing with graduated pitch
FR2404824A1 (fr) * 1977-10-03 1979-04-27 Fortschritt Veb K Chambre annulaire de transfert thermique avec deux ou plusieurs tuyaux concentriques
US4270601A (en) * 1980-01-07 1981-06-02 The Budd Company Heater for pre-heating fuel with a heated liquid

Cited By (36)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0174319A4 (fr) * 1984-02-27 1986-07-08 Omnis Surgical Inc Echangeur de chaleur pour dispositif de transfert de masse.
EP0174319A1 (fr) * 1984-02-27 1986-03-19 Omnis Surgical Inc Echangeur de chaleur pour dispositif de transfert de masse.
US4735775A (en) * 1984-02-27 1988-04-05 Baxter Travenol Laboratories, Inc. Mass transfer device having a heat-exchanger
EP0192506B1 (fr) * 1985-01-21 1990-04-04 Gaz De France Appareil de réchauffage d'un fluide, notamment accumulateur d'eau chaude sanitaire
FR2579313A1 (fr) * 1985-03-20 1986-09-26 Klein Schanzlin & Becker Ag Echangeur de chaleur a tube double coude
US4895203A (en) * 1985-03-22 1990-01-23 Harold L. Hayes Heat exchanger with helically coiled conduct in casing
EP0217523A1 (fr) * 1985-09-09 1987-04-08 Zwick Energy Research Organization Système de refroidissement des gaz d'échappement d'un moteur à combustion interne
US4872503A (en) * 1986-03-13 1989-10-10 Marriner Raymond E Air heat exchanger
EP0247989A2 (fr) * 1986-05-27 1987-12-02 Level 1 Technologies, Inc. Dispositif autonome et transportable pour chauffer un liquide physiologique
USRE39075E1 (en) * 1986-05-27 2006-04-18 Smiths Medical Asd, Inc. Heater for physiological fluids
EP0247989A3 (en) * 1986-05-27 1990-11-22 Level 1 Technologies, Inc. Self-contained portable unit for heating physiological fluids
EP0256653A3 (fr) * 1986-07-10 1990-01-17 Haemonetics Corporation Echangeur de chaleur compatible avec le sang
EP0256653A2 (fr) * 1986-07-10 1988-02-24 Haemonetics Corporation Echangeur de chaleur compatible avec le sang
GB2228563A (en) * 1989-02-28 1990-08-29 Michael John Nunnerley Heat exchange system
DE3932871A1 (de) * 1989-10-02 1990-02-01 Andreas Hahn Waermerueckgewinnungsrohr nach dem gegenstromprinzip, insbesondere fuer kuechen- und sanitaerinstallationen
DE19624937A1 (de) * 1996-06-22 1998-01-02 Dickgreber Johannes Wärmetauscher
EP0985894A3 (fr) * 1998-09-08 2000-10-11 Witzenmann GmbH Metallschlauch-Fabrik Pforzheim Refroidisseur de carburant
EP1136780A3 (fr) * 2000-03-23 2002-11-06 Senior Investments AG Echangeur de chaleur à tubes doubles
WO2002001125A1 (fr) * 2000-06-28 2002-01-03 Igc Polycold Systems, Inc. Evaporateur d'appareil frigorifique a liquide
AT412293B (de) * 2003-01-13 2004-12-27 Porpaczy Johann Ing Wärmetauscher für zu kühlendes abwasser
US7063133B2 (en) * 2003-12-29 2006-06-20 Bradford White Corporation Multi-wall heat exchanger for a water heater
US7063132B2 (en) 2003-12-29 2006-06-20 Bradford White Corporation Multi-wall heat exchanger for a water heater
US7866378B2 (en) 2004-11-09 2011-01-11 Denso Corporation Double-wall pipe, method of manufacturing the same and refrigerant cycle device provided with the same
US9669499B2 (en) 2004-11-09 2017-06-06 Denso Corporation Double-wall pipe, method of manufacturing the same and refrigerant cycle device provided with the same
DE102005052973B4 (de) * 2004-11-09 2014-11-20 Denso Corporation Doppelwandiges Rohr und Herstellungsverfahren dafür
DE102009035986B4 (de) * 2009-08-04 2013-03-28 Horst Valentin Doppelmantelrohr mit integriertem Rücklauf und Entlüftung
DE102009035986A1 (de) * 2009-08-04 2011-04-07 Horst Valentin Doppelmantelrohr mit integriertem Rücklauf und Entlüftung
EP2295915A2 (fr) 2009-08-04 2011-03-16 Horst Valentin Tuyau à deux enveloppes doté d'un retour intégré
WO2011057594A1 (fr) * 2009-11-11 2011-05-19 Az Vermögensverwaltung Gmbh & Co. Kg Échangeur thermique à tubes concentriques
EP2354743A3 (fr) * 2010-01-15 2012-10-31 LG Electronics Inc. Échangeur thermique à double tuyau
KR101620106B1 (ko) 2010-01-15 2016-05-13 엘지전자 주식회사 이중 열교환기
US9279621B2 (en) 2010-08-12 2016-03-08 GM Global Technology Operations LLC Internal heat exchanger for a motor vehicle air-conditioning system
DE102011100692A1 (de) * 2011-05-06 2012-11-08 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Flexibel anpassbarer Wärmetauscher für eine Kraftfahrzeug-Klimaanlage
DE102013105943A1 (de) * 2013-06-07 2014-12-11 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Kühlanordnung für einen Kraftfahrzeugantriebsstrang
DE102013105943B4 (de) * 2013-06-07 2016-02-18 Getrag Getriebe- Und Zahnradfabrik Hermann Hagenmeyer Gmbh & Cie Kg Kühlanordnung für einen Kraftfahrzeugantriebsstrang
US11835301B2 (en) 2021-04-07 2023-12-05 Ecoinnovation Technologies Incorporée Modular heat exchanger and method of assembly thereof

Also Published As

Publication number Publication date
JPS59100392A (ja) 1984-06-09

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