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EP3224565A2 - Échangeur de chaleur à microcanaux tolérant au gel - Google Patents

Échangeur de chaleur à microcanaux tolérant au gel

Info

Publication number
EP3224565A2
EP3224565A2 EP15804285.3A EP15804285A EP3224565A2 EP 3224565 A2 EP3224565 A2 EP 3224565A2 EP 15804285 A EP15804285 A EP 15804285A EP 3224565 A2 EP3224565 A2 EP 3224565A2
Authority
EP
European Patent Office
Prior art keywords
heat exchange
heat exchanger
slab
exchange tube
heat
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.)
Granted
Application number
EP15804285.3A
Other languages
German (de)
English (en)
Other versions
EP3224565B1 (fr
Inventor
Arindom Joardar
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.)
Carrier Corp
Original Assignee
Carrier Corp
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 Corp filed Critical Carrier Corp
Publication of EP3224565A2 publication Critical patent/EP3224565A2/fr
Application granted granted Critical
Publication of EP3224565B1 publication Critical patent/EP3224565B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/02—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the heat-exchange media travelling at an angle to one another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • F28F19/006—Preventing deposits of ice
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0475—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 bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend
    • F28D1/0476—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 bent, e.g. in a serpentine or zig-zag the conduits having a single U-bend the conduits having a non-circular cross-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
    • 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
    • F28F1/128—Fins with openings, e.g. louvered 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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • 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
    • F28D2001/0253—Particular components
    • F28D2001/026—Cores
    • F28D2001/0266—Particular core assemblies, e.g. having different orientations or having different geometric features
    • 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
    • F28D2001/0253—Particular components
    • F28D2001/026—Cores
    • F28D2001/0273—Cores having special shape, e.g. curved, annular
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • 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
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels

Definitions

  • This invention relates generally to heat pump and refrigeration applications and, more particularly, to a microchannel heat exchanger configured for use in a heat pump or refrigeration system.
  • HVAC&R Heating, ventilation, air conditioning and refrigeration
  • a microchannel heat exchanger includes two or more containment forms, such as tubes, through which a cooling or heating fluid (i.e. refrigerant or a glycol solution) is circulated.
  • the tubes typically have a flattened cross-section and multiple parallel flow channels.
  • Fins are typically arranged to extend between the tubes to assist in the transfer of thermal energy between the heating/cooling fluid and the surrounding environment.
  • the fins have a corrugated pattern, incorporate louvers to boost heat transfer, and are typically secured to the tubes via brazing.
  • microchannel heat exchangers commonly have substantially identical fins throughout the heat exchanger core.
  • moisture present in the airflow provided to the heat exchanger for cooling may condense and then freeze on the external heat exchanger surfaces.
  • the ice or frost formed may block the flow of air through the heat exchanger, thereby reducing the efficiency and functionality of the heat exchanger and HVAC&R system.
  • Microchannel heat exchangers tend to freeze faster than the round tube and plate fin heat exchangers and therefore require more frequent defrosts, reducing useful heat exchanger utilization time and overall performance. Consequently, it is desirable to construct the microchannel heat exchanger with improved frost tolerance and enhanced performance.
  • a heat exchanger including a first manifold, a second manifold, and a plurality of heat exchange tube segments fluidly coupling the first and second manifold.
  • the heat exchange tube segments include a bend defining a first slab and a second arranged at an angle to one another.
  • Each of the heat exchange tube segments includes at least a first heat exchange tube and a second heat exchange tube at least partially connected by a web extending there between.
  • the first heat exchange tube and the second heat exchange tube are asymmetrical such that a cross-sectional flow area of the first heat exchange tube is different than that of the second heat exchange tube.
  • a fluid flows sequentially through the first heat exchange tubes of the first slab and the second slab, and then through the second heat exchange tubes of the second slab and first slab.
  • an airflow across the heat exchanger moves from the first slab toward the second slab.
  • an airflow across the heat exchanger moves from the second slab toward the first slab.
  • the cross-sectional flow area of the first heat exchange tubes is smaller than the cross- sectional area of the second heat exchange tubes.
  • the fluid within the first heat exchange tubes includes a liquid or liquid-vapor mixture including less than 20% vapor by mass.
  • the fluid within the second heat exchange tubes includes a vapor or liquid-vapor mixture including at least 50% vapor by mass.
  • the cross-sectional flow area of the first heat exchange tubes is larger than the cross-sectional area of the second heat exchange tubes.
  • the fluid within the second heat exchange tubes includes a liquid or liquid-vapor mixture including less than 20% vapor by mass.
  • the fluid within the first heat exchange tubes includes a vapor or liquid-vapor mixture including at least 50% vapor by mass.
  • a heat exchanger including a first manifold, a second manifold, and a plurality of heat exchange tube segments fluidly coupling the first and second manifold.
  • the heat exchange tube segments include a bend defining a first slab and a second arranged at an angle to one another.
  • Each of the heat exchange tube segments includes at least a first heat exchange tube and a second heat exchange tube at least partially connected by a web extending there between.
  • a fluid flow sequentially through the first heat exchange tubes and the second heat exchange tubes of the heat exchanger such that the fluid within the first heat exchange tubes is a liquid and the fluid within the second heat exchange tubes is a vapor.
  • first heat exchange tube and the second heat exchange tube are asymmetrical such that a cross-sectional flow area of the first heat exchange tube is different than a cross-sectional flow area of the second heat exchange tube.
  • the cross-sectional flow area of the first heat exchange tubes is smaller than the cross- sectional area of the second heat exchange tubes.
  • an airflow across the heat exchanger moves from the first slab toward the second slab.
  • FIG. 1 is a schematic diagram of an example of a vapor refrigeration cycle of a refrigeration system
  • FIG. 2 is a side view of a microchannel heat exchanger according to an embodiment of the invention prior to a bending operation
  • FIG. 3 is a cross-sectional view of a tube segment of a microchannel heat exchanger according to an embodiment of the invention.
  • FIG. 4 is a cross-sectional view of a tube segment of a microchannel heat exchanger according to an embodiment of the invention.
  • FIG. 5 is a perspective view of a microchannel heat exchanger according to an embodiment of the invention.
  • FIG. 6 is a cross-sectional view of a microchannel heat exchanger according to another embodiment of the invention.
  • FIG. 7 is a cross-sectional view of a microchannel heat exchanger according to yet an embodiment of the invention.
  • FIG. 8 is a cross-sectional view of a microchannel heat exchanger according to yet an embodiment of the invention.
  • a vapor compression refrigerant, cycle 20 of an air conditioning or refrigeration system is schematically illustrated.
  • Exemplary air conditioning or refrigeration systems include, but are not limited to, split, packaged, chiller, rooftop, supermarket, and transport refrigeration systems for example.
  • a refrigerant R is configured to circulate through the vapor compression cycle 20 such that the refrigerant R absorbs heat when evaporated at a low temperature and pressure and releases heat when condensed at a higher temperature and pressure.
  • the refrigerant R flows in a counterclockwise direction as indicated by the arrow.
  • the compressor 22 receives refrigerant vapor from the evaporator 24 and compresses it to a higher temperature and pressure, with the relatively hot vapor then passing to the condenser 26 where it is cooled and condensed to a liquid state by a heat exchange relationship with a cooling medium (not shown) such as air.
  • the liquid refrigerant R then passes from the condenser 26 to an expansion device 28, wherein the refrigerant R is expanded to a low temperature two-phase liquid/vapor state as it passes to the evaporator 24.
  • the low pressure vapor then returns to the compressor 22 where the cycle is repeated. It has to be understood that the refrigeration cycle 20 depicted in FIG.
  • the heat pump refrigerant cycle includes a four-way valve (not shown) disposed downstream of the compressor with respect to the refrigerant flow that allows reversing the refrigerant flow direction throughout the refrigerant cycle to switch between the cooling and heating mode of operation for the environment to be conditioned.
  • the heat exchanger 30 may be used as either a condenser 24 or an evaporator 28 in the vapor compression system 20.
  • the heat exchanger 30 includes at least a first manifold or header 32, a second manifold or header 34 spaced apart from the first manifold 32, and a plurality of tube segments 36 extending in a spaced, parallel relationship between and connecting the first manifold 32 and the second manifold 34.
  • the first header 32 and the second header 34 are oriented generally horizontally and the heat exchange tube segments 36 extend generally vertically between the two headers 32, 34.
  • other suitable heat exchange tube segments 36 extend generally vertically between the two headers 32, 34.
  • first and second headers 32, 34 are arranged substantially vertically are also within the scope of the invention.
  • each of the plurality of tube segments 36 extending between the first manifold 32 and the second manifold 34 is a multiport extruded (MPE) tube segment 36 and includes at least a first heat exchange tube 38 and a second heat exchange tube 40 connected by a web 42 extending at least partially there between.
  • MPE multiport extruded
  • the web 42 arranged at the outermost tube segments 36 includes a plurality of openings.
  • each heat exchange tube 38,40 may be divided by interior walls into a plurality of discrete flow channels 44a, 44b that extend over the length of the tube segments 36 and establish fluid communication between the respective first and second manifolds 32, 34.
  • the interior flow passages of the first heat exchange tubes 38 may be divided into a different number of discrete flow channels 44 than the interior flow passages of the second heat exchange tubes 40.
  • the flow channels 44a, 44b may have any shape cross-section, such as a circular cross-section, a rectangular cross-section, a trapezoidal cross-section, a triangular cross-section, or another non-circular cross-section for example.
  • the plurality of heat exchange tube segments 36 including the discrete flow channels 44a, 44b may be formed using known techniques, such as extrusion for example.
  • Each first heat exchange tube 38 and second heat exchange tube 40 has a respective leading edge 46a, 46b, a trailing edge 48a, 48b, a first surface 50a, 50b, and a second surface 52a, 52b (FIG. 3).
  • the leading edge 46a, 46b of each heat exchange tube 38, 40 is upstream of its respective trailing edge 48a, 48b with respect to an airflow A through the heat exchanger 30.
  • the first heat exchange tubes 38 and the second heat exchanger tubes 40 are substantially different or asymmetric.
  • the second heat exchange tubes 40 are wider and have a greater number of discrete flow channels 44 than the first heat exchange tube 38, resulting in a larger cross-sectional flow area.
  • the second heat exchange tube 40 as illustrated in FIG. 3, is wider than the first heat exchange tube 38, other configurations, such as where the plurality of first heat exchange tubes 38 have a greater cross-sectional flow area than the plurality of second heat exchange tubes 40 for example, are within the scope of the invention.
  • the ratio of asymmetry between the first heat exchange tubes 38 and the second heat exchanger tubes 40 may depend on any of a variety of parameters of the heat exchanger, such as capacity,
  • each tube segment 36 of the heat exchanger 30 includes at least one bend 60, such that the heat exchanger 30 has a multi-pass configuration relative to the airflow A.
  • the bend 60 is generally formed about an axis extending substantially perpendicular to the longitudinal axis or the discrete flow channels 44a, 44b of the tube segments 36.
  • the bend 60 is a ribbon fold; however other types of bends are within the scope of the invention.
  • the bend 60 is formed at an approximate midpoint of the tube segments 36 between the opposing first and second manifolds 32, 34.
  • the bend 60 at least partially defines a first section or slab 62 and a second section or slab 64 of the plurality of tube segments 36. As shown in the FIG., the bend 60 can be formed such that the first slab is positioned at an obtuse angle with respect to the second slab 64. Alternatively, or in addition, the bend 60 can also be formed such that the first slab 62 is arranged at either an acute angle or substantially parallel to the second slab 64.
  • the bend 60 allows for the formation of a heat exchanger 30 having a conventional A-coil or V-coil shape.
  • first slab 62 and the second slab 64 are arranged substantially parallel, the lengths of the first slab 62 and the second slab 64 may vary to offset the position of the first manifold 32 relative to the second manifold 34.
  • the free ends of the first slab 62 and the second slab 64 may angle or flare away from one another to accommodate the manifolds 32, 34.
  • the heat exchanger 30 includes a multi-pass
  • the heat exchanger 30 is configured such that both the first heat exchanger tube 38 and the second heat exchanger tube 40 of a tube segment 36 within the first slab 62 define a first pass relative to an airflow A. Similarly, both the first heat exchanger tube 38 and the second heat exchanger tube 40 within the second slab 64 of the same tube segment 36 define a subsequent pass relative to the airflow.
  • the fluid or refrigerant has a counter flow orientation relative to the direction of the airflow, other embodiments where the refrigerant has a parallel flow orientation are also within the scope of the invention. [0037] In another embodiment, as illustrated in FIGS.
  • the first heat exchanger tube 38 and the second heat exchanger tube 40 within the same first slab 62 or second slab 64 are configured as different passes within the refrigerant flow path of the heat exchanger 30.
  • the heat exchanger 30 may be configured such that refrigerant flows sequentially through the first heat exchanger tube 38 of both the first slab 62 and the second slab 64 prior to flowing through the second heat exchanger tube 40 of the second slab 64 and the first slab 62.
  • the refrigerant may enter the heat exchanger 30 at the same slab as the airflow, as shown in the embodiments of FIGS. 7 and 8, or alternatively, may enter the heat exchanger at a different slab as the airflow.
  • the flow through the first heat exchanger tube 38 has a first configuration and the flow through the second heat exchanger tube 40 has a second configuration, different from the first configuration.
  • the flow within the first heat exchanger tube 38 is parallel to the direction of the airflow A, and the flow within the second heat exchanger tube 40 is counter to the airflow A.
  • the refrigerant is first provided to the second heat exchanger tubes 40, as shown in FIG. 8, the flow within the second heat exchanger tubes 40 is parallel to the direction of the airflow A, and the flow within the first heat exchanger tubes 38 is counter to the airflow A.
  • the flow path of the refrigerant through the heat exchanger 30 may be configured such that the liquid or two phase portion of the refrigerant flows through the heat exchanger tube having a smaller cross- sectional flow area and the vapor portion of the refrigerant flows through the heat exchanger tube having a larger cross-sectional flow area.
  • the second heat exchanger tube 40 has a smaller cross-sectional flow area than the first heat exchanger tube 38.
  • the airflow is configured to flow from the first slab 62 to the second slab 64, and the liquid or two-phase refrigerant is input to the second heat exchanger tubes 40 of the first slab 62.
  • the refrigerant By the time the refrigerant reaches first heat exchange tubes 38 of the first slab 62, the refrigerant is a superheated vapor which is at a higher temperature than the saturation temperature. As a result, the amount of heat transfer that occurs between the airflow A and first heat exchange tubes 38 of the first slab 62 is limited.
  • the liquid or liquid vapor mixture within the second heat exchange tubes 40 is less than 20% vapor by mass and the vapor or liquid-vapor mixture within the first heat exchanger tubes 38 is at least 50% vapor by mass.
  • first heat exchanger tubes 38 may have a cross-sectional flow area smaller than that of the second heat exchanger tubes 40 such that the liquid or liquid vapor mixture within the first heat exchange tubes 38 is less than 20% vapor by mass and the vapor or liquid-vapor mixture within the second heat exchanger tubes 40 is at least 50% vapor by mass.

Landscapes

  • 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)
  • Other Air-Conditioning Systems (AREA)

Abstract

L'invention concerne un échangeur de chaleur comprenant un premier collecteur, un second collecteur et une pluralité de segments de tube d'échange de chaleur reliant en couplage fluidique le premier et le second collecteur. Les segments de tube d'échange de chaleur comportent une courbure délimitant une première et une seconde dalle disposées à un angle l'une par rapport à l'autre. Chacun des segments de tube d'échange de chaleur comprend au moins un premier tube d'échange de chaleur et un second tube d'échange de chaleur au moins partiellement reliés par une bande s'étendant entre ceux-ci. Le premier tube d'échange de chaleur et le second tube d'échange de chaleur sont asymétriques de telle sorte qu'une surface d'écoulement en coupe transversale du premier tube d'échange de chaleur est différente de celle du second tube d'échange de chaleur. Un fluide s'écoule de manière séquentielle à travers les premiers tubes d'échange de chaleur de la première dalle et de la seconde dalle, puis à travers les seconds tubes d'échange de chaleur de la seconde dalle et de la première dalle.
EP15804285.3A 2014-11-26 2015-11-20 Échangeur de chaleur à microcanaux tolérant au gel Active EP3224565B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201462084752P 2014-11-26 2014-11-26
PCT/US2015/061902 WO2016085817A2 (fr) 2014-11-26 2015-11-20 Échangeur de chaleur à microcanaux tolérant au gel

Publications (2)

Publication Number Publication Date
EP3224565A2 true EP3224565A2 (fr) 2017-10-04
EP3224565B1 EP3224565B1 (fr) 2023-12-27

Family

ID=54771215

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15804285.3A Active EP3224565B1 (fr) 2014-11-26 2015-11-20 Échangeur de chaleur à microcanaux tolérant au gel

Country Status (5)

Country Link
US (1) US20170356700A1 (fr)
EP (1) EP3224565B1 (fr)
CN (1) CN107003073A (fr)
RU (1) RU2693946C2 (fr)
WO (1) WO2016085817A2 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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Also Published As

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WO2016085817A2 (fr) 2016-06-02
US20170356700A1 (en) 2017-12-14
WO2016085817A3 (fr) 2016-07-14
RU2693946C2 (ru) 2019-07-08
RU2017121846A (ru) 2018-12-26
EP3224565B1 (fr) 2023-12-27
CN107003073A (zh) 2017-08-01
RU2017121846A3 (fr) 2019-05-17

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