WO2011126529A1 - Échangeur de chaleur - Google Patents

Échangeur de chaleur Download PDF

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Publication number
WO2011126529A1
WO2011126529A1 PCT/US2010/062043 US2010062043W WO2011126529A1 WO 2011126529 A1 WO2011126529 A1 WO 2011126529A1 US 2010062043 W US2010062043 W US 2010062043W WO 2011126529 A1 WO2011126529 A1 WO 2011126529A1
Authority
WO
WIPO (PCT)
Prior art keywords
inlet
manifold
heat exchanger
heat transfer
disposed
Prior art date
Application number
PCT/US2010/062043
Other languages
English (en)
Inventor
John T. Steele
Eric Johnson
Lester G. Harrington
Christopher G. Repice
Jason A. Gough
Scott D. Fulmer
Original Assignee
Carrier Corporation
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 Carrier Corporation filed Critical Carrier Corporation
Priority to EP10801072A priority Critical patent/EP2553374A1/fr
Priority to US13/638,864 priority patent/US20130175016A1/en
Publication of WO2011126529A1 publication Critical patent/WO2011126529A1/fr

Links

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
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F28D1/0443—Combination of units extending one beside or one above the other
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05391—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators
    • 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
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • the present invention relates generally to heat exchangers, and particularly to heat exchangers having structures operable to decrease thermal mechanical fatigue therein.
  • a typical two-pass microchannel condenser includes a plurality of parallel microchannel tubes that extends between a first manifold and a second manifold.
  • the first manifold includes an inlet section connected to a refrigerant inlet, and an outlet section connected to a refrigerant outlet.
  • the refrigerant inlet is disposed at a top end of the inlet section.
  • refrigerant is directed into the inlet section of the first manifold through the refrigerant inlet.
  • the inlet section of the first manifold directs the refrigerant through a first set of the microchannel tubes and into the second manifold.
  • the second manifold then redirects the refrigerant through a second set of the microchannel tubes to the outlet section of the first manifold.
  • thermal energy is transferred from the refrigerant in the tubes into the ambient air, thereby cooling the refrigerant.
  • the temperature of the refrigerant passing through the condenser can be reduced more than 100- 150 degrees Fahrenheit (°F).
  • a temperature drop of this magnitude can subject elements of the condenser (e.g., a section of the first manifold between the inlet section and the outlet section) to a relatively large temperature gradient.
  • elements of the condenser e.g., a section of the first manifold between the inlet section and the outlet section
  • the portion of the tubes proximate the top corner of the condenser can also be subjected to a substantial temperature gradient.
  • Substantial temperature gradients within elements of the condenser can result in relatively high thermally induced stresses in those elements. The high stresses can, in turn, cause mechanical fatigue and failure in the elements.
  • a heat exchanger includes a first manifold, a second manifold and a plurality of parallel heat transfer tubes.
  • the first manifold includes an inlet manifold section fluidly connected to an inlet.
  • the inlet manifold section extends along a centerline between a first end and a second end.
  • the heat transfer tubes extend between and fluidly connect the first and the second manifolds.
  • An integer "N” number of the heat transfer tubes are disposed along the centerline between the inlet and the first end of the inlet manifold section.
  • An integer “M” number of the heat transfer tubes are disposed along the centerline between the inlet and the second end of the inlet manifold section. "N" is approximately equal to "M”.
  • a heat exchanger includes a first manifold, a second manifold and a plurality of parallel heat transfer tubes.
  • the first manifold includes a plurality of manifold sections. A first one of the manifold sections is disposed adjacent to, and configured discrete from, a second one of the manifold sections.
  • the heat transfer tubes extend between and fluidly connect the first and the second manifolds. At least some of the heat transfer tubes are disposed with the first manifold section. At least some of the heat transfer tubes are disposed with the second manifold section.
  • a heat exchanger includes a first manifold, a second manifold and a plurality of parallel heat transfer tubes.
  • the first manifold includes an inlet manifold section connected to an inlet.
  • the heat transfer tubes extend between and fluidly connect the first and the second manifolds.
  • a region of the heat exchanger, between the first and the second manifolds, is adapted having a reduced heat transfer coefficient. This reduced heat transfer coefficient region is disposed proximate the inlet.
  • FIG. 1 is a diagrammatic illustration of an exemplary embodiment of a heat exchange system.
  • FIG. 2 is a diagrammatic illustration of one embodiment of a heat exchanger for use in the heat exchanger system in FIG. 1.
  • FIG. 3 is a diagrammatic illustration of another embodiment of a heat exchanger for use in the heat exchanger system in FIG. 1.
  • FIG. 4 is a diagrammatic illustration of another embodiment of a heat exchanger for use in the heat exchanger system in FIG. 1.
  • FIG. 5 is a diagrammatic illustration of an enlarged section of the heat exchanger shown in FIG. 4 proximate a refrigerant inlet aperture.
  • FIG. 6 is a diagrammatic illustration of another embodiment of a heat exchanger for use in the heat exchanger system in FIG. 1.
  • FIG. 7 is a diagrammatic illustration of a section of the heat exchanger shown in
  • an exemplary heat exchanger system 10 (hereinafter “FIX system”) is shown that includes a closed loop refrigerant circuit 12 (hereinafter “refrigerant circuit”).
  • the refrigerant circuit 12 includes a plurality of components including a compressor 14, a condenser 16, an evaporator 18 and, optionally, a subcooler 20.
  • the FTX system 10 shown in FIG. 1 can cool an environment by cycling refrigerant (or coolant) through the refrigerant circuit 12.
  • the compressor 14 directs compressed refrigerant into the condenser 16.
  • the refrigerant is directed into the subcooler 20.
  • additional heat energy is transferred from the refrigerant within the subcooler 20 into the ambient air.
  • the refrigerant is directed into the evaporator 18.
  • the FTX system 10 can further include an expansion valve 22, a pressure relief valve 24, a liquid-to-liquid heat exchanger 26, etc.
  • a heat exchanger 28 configured having one or more liquid-to-air (or air-to-liquid) heat exchanger sections 30 and 32.
  • Each heat exchanger section 30, 32 can be adapted to operate as the condenser 16, the subcooler 20 or the evaporator 18 of the HX system 10 in FIG. 1; however, the present invention is not limited to the functionalities of these components.
  • a heat exchanger section includes a condenser section 30 adapted to operate as the condenser 16, and a subcooler section 32 adapted to operate as the subcooler 20.
  • the heat exchanger 28 includes a first manifold 34 (sometimes referred to as a "header"), a second manifold 36 and a plurality of heat transfer tubes 38 (hereinafter the ' ⁇ tubes").
  • the heat exchanger 28 can further include a plurality of cooling fins 40, a region 42 having a reduced heat transfer coefficient (hereinafter the "reduced HTC region") (see FIGS. 4 to 6) and/or a plurality of mounting brackets 44, 46, 48 and 50.
  • the first manifold 34 extends along a first centerline 52 (e.g., parallel to the y- axis) between two ends 54 and 56.
  • the first manifold 34 includes one or more manifold sections 58, 60, 62 and one or more refrigerant inlet/outlet apertures 64, 66, 68 (hereinafter "I/O apertures").
  • the manifold sections include a condenser inlet section 58, a condenser outlet section 60 and a subcooler inlet section 62.
  • Each manifold section 58, 60, 62 extends along the first centerline 52 between a first (e.g., top) end 54, 70, 72 and a second (e.g., bottom) end 74, 76, 56 defining a height extending therebetween.
  • Each manifold section 58, 60, 62 is fluidly separated from an adjacent manifold section 58, 60, 62 by a baffle 78 or any other suitable fluid flow obstruction.
  • two adjacent manifold sections e.g., the condenser inlet section 58 and the condenser outlet section 60
  • the condenser inlet section 58 is configured discrete from the condenser outlet section 60 and the subcooler inlet section 62; however, the present invention is not limited to such a configuration.
  • the I/O apertures include a condenser inlet 64, a condenser outlet 66 and a subcooler inlet 68.
  • the condenser inlet 64 is fluidly connected to the condenser inlet section 58.
  • the condenser inlet 64 is disposed approximately halfway between the top and the bottom ends 54, 74 of the condenser inlet section 58; however, the present invention is not limited to this configuration.
  • the condenser inlet 64 can be disposed proximate the top end 54 of the condenser inlet section 58.
  • the condenser outlet 66 is fluidly connected to the condenser outlet section 60.
  • the subcooler inlet 68 is fluidly connected to the subcooler inlet section 62.
  • the second manifold 36 extends along a second centerline 82 (e.g., parallel to the y-axis) between two ends 84 and 86.
  • the second manifold 36 includes one or more manifold sections 88, 90 and at least one I O aperture 92.
  • the manifold sections include a condenser return section 88 and a subcooler outlet section 90.
  • Each manifold section 88, 90 extends along the second centerline 82 between a first (e.g., top) end 84, 94 and a second (e.g., bottom) end 96, 86, defining a height extending therebetween.
  • Each manifold section 88, 90 can be fluidly separated from an adjacent manifold section 88, 90 by a baffle 98 or other suitable flow obstruction.
  • the second manifold sections 88 and 90 can be physically separate from one another.
  • the I/O aperture is adapted as a subcooler outlet 92.
  • the subcooler outlet 92 is fluidly connected to the subcooler outlet section 90.
  • the HT tubes 38 are arranged in parallel rows that extend (e.g., substantially perpendicular to the first and the second centerlines 52 and 82) between the first and the second manifolds 34 and 36.
  • the HT tubes 38 can further be arranged into a plurality of HT tube sets 100, 102, 104.
  • the HT tubes 38 in the heat exchanger 28 in FIG. 2 are arranged into a first set 100, a second set 102 and a third set 104.
  • the first set of HT tubes 100 fluidly connects the condenser inlet section 58 of the first manifold 34 to the condenser return section 88 of the second manifold 36.
  • an integer "N” number of these first set HT tubes 100 (where N > 1) are disposed along the first centerline 52 between the condenser inlet 64 and the top end 54 of the condenser inlet section 58.
  • An integer “M” number of these first set HT tubes 100 (where M and N are equal or approximately equal to one another) are disposed along the first centerline 52 between the condenser inlet 64 and the bottom end 74 of the condenser inlet section 58.
  • the present invention is not limited to this specific configuration.
  • the second set of HT tubes 102 fluidly connects the condenser return section 88 of the second manifold 36 to the condenser outlet section 60 of the first manifold 34.
  • the third set of HT tubes 104 fluidly connects the subcooler inlet section 62 of the first manifold 34 to the subcooler outlet section 90 of the second manifold 36.
  • each HT tube 38 is disposed a distance 106 (e.g., along the first and/or the second centerlines 52, 82) from each adjacent HT tube 38.
  • one or more of the HT tubes 38 includes a plurality of parallel microchannels 108 disposed within the tubes 38. Examples of suitable microchannel tube configurations are disclosed in U.S. Patent Nos. 7,281,387 and 7,000,415 both to Daddis, Jr. et al, which are hereby incorporated by reference in their entirety. The present invention, however, is not limited to the aforesaid microchannel tube configuration.
  • the cooling fins 40 are arranged into a plurality of rows 110, 112 and 114. Each row of cooling fins 110, 112, 114 is respectively disposed between a pair of adjacent HT tubes 38 within each heat exchanger section 30, 32. In some embodiments, a row of cooling fms can also be disposed between a pair of HT tubes 38 that are each disposed in different heat exchanger sections 30, 32 (not shown).
  • the cooling fin 40 in each row 110, 112, 114 that is disposed closest to the first manifold 34 i.e., the "first fin" can be adjacent or in contact with the first manifold (e.g., see FIG. 2).
  • the "first fin" 40 in a given row can be disposed a distance 116, 117, 119 (e.g., perpendicular to the first centerline 52) away from, the first manifold 34 (e.g., see FIG. 5).
  • the cooling fin 40 in a given row e.g., row 110, 112, 114 that is disposed closest to the second manifold 36 (i.e., the "last fin") can be adjacent or in contact with the second manifold 36 (e.g., see FIG. 2), or disposed a distance away from the second manifold 36.
  • each V-shaped cooling fin extends between a first end 120 and a second end 122, and has a mid-point 124 (i.e., where a slope of the fin reverses) therebetween.
  • adjacent rows of cooling fins 110, 112, 114 can be staggered relative to each other such that, for example, the first ends 120 of the V-shaped cooling fins in a first row 110 are aligned (along the x-axis) with the midpoints 124 of the V-shaped cooling fins in a second row 112.
  • Other suitable examples of cooling fin configurations are disclosed in the afore-referenced U.S. Patent Nos. 7,281,387 and
  • the reduced HTC region 42 is adapted to reduce thermal gradients and the typically accompanying stress and fatigue.
  • the reduced HTC region 42 is located proximate the condenser inlet 64, between the condenser inlet section 58 of the first manifold 34 and the condenser return section 88 of the second manifold 36.
  • the reduced HTC region 42 includes a plurality of finless regions 126; i.e., regions between the HT tubes 38 without cooling fins 40. These finless regions 126 are configured to incrementally decrease in size with each tube 38 further away from the condenser inlet 64.
  • the distance 116, 117, 119 disposed between the condenser inlet section 58 and the cooling fin 40 closest thereto in a respective row 110, 112, 114, for Q number of cooling fin rows (where Q > 2), is incrementally decreased as the respective cooling fin rows 110, 112, 114 are disposed farther away from the condenser inlet 64 (i.e., as the distance 128, 130, 132 disposed between the respective cooling fin row 110, 112, 114 and the condenser inlet 64 increases).
  • the distance 116 between the condenser inlet section 58 and the "first fin” 40 in the first cooling fin row 110 is greater than the distance 117 between the condenser inlet section 58 and the "first fin” 40 in the second cooling fin row 112, which is greater than the distance 119 between the condenser inlet section 58 and the "first fin” 40 in the third cooling fin row 114, etc.
  • the number of rows used in the reduced HTC can vary depending upon the application. The present invention, however, is not limited to the aforesaid embodiment.
  • the geometry of the HTC region can be varied to suit the application at hand. For example, in other embodiments, sets of two or more of the finless regions can incrementally decrease in size as each set is disposed further away from the condenser inlet, etc.
  • the reduced HTC region 42 includes an airflow reduction element 134 that is disposed with the condenser section 30 proximate the condenser inlet 64.
  • the airflow reduction element 134 includes a sheet of material (e.g., insulation) that is semi -permeable or impermeable to airflow.
  • the airflow reduction element 134 may be disposed on one or both sides of the condenser section 30 of the heat exchanger 28.
  • the mounting brackets 44, 46, 48 and 50 are adapted to secure the heat exchanger 28 as a single unit to a housing (not shown).
  • the number and configuration of the mounting brackets can be varied to suit the application at hand.
  • refrigerant provided from the compressor 14 is directed through the condenser inlet 64 and into the condenser inlet section 58 of the first manifold 34.
  • the condenser inlet section 58 distributes the refrigerant into the first set of HT tubes 110.
  • some embodiments of the present invention locate the condenser inlet 64 intermediately between the : 'N" and the "M" numbers of HT tubes 38. By so locating the inlet 64 relative to the HT tubes 38, the refrigerant more uniformly distributes within the HT tubes 110, and thereby decreases the potential for a substantial thermal gradient within the region.
  • the potential for a thermal gradient adjacent the condenser inlet 64 is addressed by reducing the heat transfer coefficient in the region 138 proximate the condenser inlet 64; i.e., in the reduced HTC region 42.
  • the heat transfer coefficient of the structure in the HTC region is reduced relative to the remainder of the heat exchanger.
  • the rate at which thermal energy is transferred between the refrigerant and the ambient air in this region is reduced and the potential for a large temperature gradient is reduced.
  • the finless regions 126 reduce the outer surface area of the condenser section 30 in the reduced HTC region 42.
  • the reduction in surface area decreases the rate at which heat energy can be transferred between the refrigerant and the ambient air. Additionally, the finless regions 126 and the staggered arrangement of the cooling fins 40 can compensate for thermal growth of the condenser inlet section 58 (e.g., along the first centerline) by permitting relative movement between adjacent HT tubes 38.
  • a sheet of insulation 134 insulates the tubes in the reduced HTC region 42, and reduces or prevents the flow of ambient air therethrough. The reduction of airflow serves to decrease the heat transfer rate between the refrigerant and the ambient air within the region, thereby reducing the thermal gradient and potential for thermally induced stresses.
  • the refrigerant flows through the first set of HT tubes 110 and into the condenser return section 88, thereby completing a first pass through the condenser section.
  • the condenser return section 88 redirects the refrigerant, which was collected from the first set of HT tubes 110, into the second set of HT tubes 112.
  • the refrigerant flows through this second set of HT tubes 112 and into the condenser outlet section 60, thereby completing a second pass through the condenser section.
  • the condenser outlet section 60 directs the refrigerant, which was collected from the second set of HT tubes 112, out of the heat exchanger 28 through the condenser outlet 66.
  • the refrigerant can be cooled more than, for example, 100-150 degrees Fahrenheit ( ° F) as it flows through the first and the second passes of the condenser section 30.
  • ° F degrees Fahrenheit
  • such a temperature drop can subject a mid section of a prior art manifold, between an inlet manifold section and an outlet manifold section, to a relatively sharp temperature gradient.
  • mechanical stresses potentially associated with such a large temperature gradient can be mitigated by providing the physical separation between the condenser inlet section 58 and the condenser outlet section 60.
  • these manifold sections 58 and 60 can independently thermally grow and/or move relative to each other without subjecting the heat exchanger 28 to additional mechanical stresses.
  • the subcooler inlet section 62 distributes the refrigerant into the third set of HT tubes 114.
  • the refrigerant flows through this third set of HT tubes 114 and into the subcooler outlet section 90, thereby completing a first pass through the subcooler section.
  • the subcooler outlet section 90 directs the refrigerant, which was collected from the third set of HT tubes 114, back out of the heat exchanger 28 through the subcooler outlet 92.
  • first and/or the second manifolds 34 and 36 can each include additional manifold sections (e.g., return sections) such that the refrigerant can complete additional passes through one or more of the heat exchanger sections. Accordingly, the present invention is not to be restricted except in light of the attached claims and their equivalents.

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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)

Abstract

La présente invention concerne un échangeur de chaleur (28) qui comprend un premier collecteur (34), un second collecteur (36) et une pluralité de tubes (38) de transfert de chaleur parallèles. Le premier collecteur (34) comprend une ou plusieurs sections (58, 60, 63) de collecteur. Une première section (58) des sections de collecteur est raccordée à une entrée (64). Les tubes (38) de transfert de chaleur s'étendent entre les premier et second collecteurs (34, 36) et raccordent de façon fluidique lesdits premier et second collecteurs. Au moins un certain nombre des tubes (38) de transfert de chaleur sont disposés avec la première section (58) de collecteur.
PCT/US2010/062043 2010-03-29 2010-12-23 Échangeur de chaleur WO2011126529A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP10801072A EP2553374A1 (fr) 2010-03-29 2010-12-23 Échangeur de chaleur
US13/638,864 US20130175016A1 (en) 2010-03-29 2010-12-23 Heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US31859210P 2010-03-29 2010-03-29
US61/318,592 2010-03-29

Publications (1)

Publication Number Publication Date
WO2011126529A1 true WO2011126529A1 (fr) 2011-10-13

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US (1) US20130175016A1 (fr)
EP (1) EP2553374A1 (fr)
WO (1) WO2011126529A1 (fr)

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WO2014016324A1 (fr) * 2012-07-24 2014-01-30 Valeo Systemes Thermiques Echangeur thermique multi-fluides pour véhicules automobiles
FR2995670A3 (fr) * 2012-09-20 2014-03-21 Renault Sa Echangeur thermique ayant une partie condenseur et une partie radiateur basse temperature
CN104949394A (zh) * 2014-03-26 2015-09-30 杭州三花研究院有限公司 一种换热器

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US10578370B2 (en) * 2017-06-13 2020-03-03 Modine Manufacturing Company Integrated heat exchanger and coolant reservoir
US10895405B2 (en) * 2018-09-25 2021-01-19 Rheem Manufacturing Company Tankless water heater apparatus, system, and methods
JP6881624B1 (ja) * 2020-01-22 2021-06-02 株式会社富士通ゼネラル 熱交換器
WO2024097959A2 (fr) * 2022-11-04 2024-05-10 Intergalactic Spaceworx, LLC Échangeur de chaleur à microtubes à flux multiples et partie centrale commune

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CN104949394B (zh) * 2014-03-26 2019-05-24 杭州三花研究院有限公司 一种换热器

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