EP3334991B1 - Mikrokanal-wärmetauscher - Google Patents

Mikrokanal-wärmetauscher Download PDF

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Publication number
EP3334991B1
EP3334991B1 EP16753806.5A EP16753806A EP3334991B1 EP 3334991 B1 EP3334991 B1 EP 3334991B1 EP 16753806 A EP16753806 A EP 16753806A EP 3334991 B1 EP3334991 B1 EP 3334991B1
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EP
European Patent Office
Prior art keywords
tube
heat exchanger
heat exchange
tube segments
manifold
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EP16753806.5A
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English (en)
French (fr)
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EP3334991A1 (de
Inventor
Jason Scarcella
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Carrier Corp
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Carrier Corp
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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
    • 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
    • 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
    • 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
    • F28D2021/007—Condensers
    • 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 disclosure 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
  • condensers and evaporators include heat exchangers to transfer heat between the refrigerant circulating within the system and surroundings.
  • a relatively recent advancement in heat exchanger technology includes the development and application of parallel flow (also referred to as microchannel or minichannel) heat exchangers as condensers and evaporators.
  • Microchannel heat exchangers are provided with a plurality of parallel heat exchange tubes, each of which has multiple flow passages through which refrigerant is distributed and flown in a parallel manner.
  • the heat exchange tubes can be orientated substantially perpendicular to a refrigerant flow direction in the inlet, intermediate and outlet manifolds that are in flow communication with the heat exchange tubes.
  • US 2003/0106677 A1 discloses a heat exchanger having heat flow interrupters located in fins, wherein the fins are between adjacent tube runs.
  • US 2008/0173434 A1 discloses a heat exchanger tube having a first section and a second section, the second section being arranged at an angle with respect to the first section.
  • CN 102384673 A discloses a heat exchanger comprising at least two rows of heat exchange tubes formed by bending general heat exchange tube rows.
  • US 2011/0168362 A1 discloses a microchannel heat exchanger.
  • a heat exchanger including a first manifold; a second manifold separated from the first manifold; a plurality of heat exchange tube segments arranged in spaced parallel relationship and fluidly coupling the first manifold and the second manifold, the plurality of heat exchange tube segments including a fold forming a first tube bank and a second tube bank parallel to one another and wherein the first tube bank and the second tube bank are configured for sequential flow there through of a first heat transfer fluid; and a first bend formed in the first tube bank and the second tube bank; characterised in that: the tube segments comprise a tube depth measured from a leading edge to a trailing edge of the tube segment wherein the tube depth is less than 14 millimeters, and wherein the heat exchanger further comprises a second bend (70b).
  • the plurality of heat exchange tube segments may be microchannel tubes having a plurality of discrete flow channels formed therein.
  • a plurality of fins may extend from at least a portion of the heat exchange tube segments.
  • the heat exchanger may be configured for a second heat transfer fluid to sequentially flow through the first tube bank followed by flow through the second tube bank.
  • the fluid may be a high pressure refrigerant configured for use at pressures exceeding 750 psig (51.7 bar).
  • the heat exchanger may include two folds defining three tube banks.
  • the second tube bank and the third tube bank may be in substantially parallel relation along a portion of a flow path length of the first heat transfer fluid.
  • the flow path of the first heat transfer may include a plurality of passes relative to a second heat transfer fluid.
  • a method of manufacturing a heat exchanger including forming a plurality of heat exchange tube segments; folding the plurality of heat exchanger tube segments to define a first tube bank and a second tube bank wherein a first center line of the first tube bank and a second center line of the second tube bank are parallel; forming a first bend and a second bend in the plurality of heat exchanger tube segments, the bend having an angle other than 180° such that the heat exchanger has a non-linear configuration; wherein the tube segments comprise a tube depth measured from a leading edge to a trailing edge of the tube segment wherein the tube depth is less than 14 millimeters.
  • the method may include the folding of the plurality of heat exchange tube segments occurs about an axis arranged perpendicular to a longitudinal axis of the plurality of heat exchange tube segments.
  • the method may include forming the plurality of heat exchange tube segments includes extruding the plurality of heat exchange tube segments.
  • the method may include the plurality of heat exchange tube segments are microchannel tubes having a plurality of discrete flow channels formed therein.
  • the method may include further comprising mounting a plurality of fins to at least a portion of the heat exchange tube segments.
  • the method may include attaching a first manifold to a first end of the plurality of heat exchange tube segments and attaching a second manifold to a second, opposite end of the plurality of heat exchange tube segments.
  • the method may include that the first manifold and the second manifold may be configured for use with a high pressure refrigerant exceeding 750 psig (51.7 bar).
  • 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 may include a mechanism (not shown) for reversing the refrigerant flow direction throughout the refrigerant cycle (e.g., including a four way valve, a piping tee, a shutoff valve, a bi-directional valve, a three way valve, a reversible compressor, a separate reverse compressor, or a combination including at least one of the foregoing, and the like) to switch between the cooling and heating mode of operation for the environment to be conditioned.
  • a mechanism for reversing the refrigerant flow direction throughout the refrigerant cycle (e.g., including a four way valve, a piping tee, a shutoff valve, a bi-directional valve, a three way valve, a reversible compressor, a separate reverse compressor, or a combination including at least one of the foregoing, and the like) 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 vertically and the heat exchange tube segments 36 extend generally horizontally between the two headers 32, 34.
  • other configurations, such as where the first and second headers 32, 34 are arranged substantially horizontally are also within the scope of the invention.
  • FIG. 3 illustrates a cross-sectional view of a portion of the plurality of heat exchanger tube segments 36.
  • the heat exchanger tube segments 36 may include any cross-sectional shape.
  • the cross sectional shape of the heat exchanger tube segments 36 can include circular, elliptical, polygonal having straight and/or curved sides, such as a rounded rectangular shape as shown in FIG. 3 .
  • the tube segments 36 can have a leading edge 38, a trailing edge 40, a first side 42, and a second, opposite side 44.
  • the leading edge 38 of the heat exchange tube 36 is upstream from its respective trailing edge 40 with respect to the flow of a second heat transfer fluid A (e.g., air, nitrogen, and the like) through the heat exchanger 30.
  • a second heat transfer fluid A e.g., air, nitrogen, and the like
  • the respective leading and trailing edges of the tube segments 36 can be rounded, thereby providing a blunt leading edge 38 and a blunt trailing edge 40.
  • the respective leading and trailing edges of the tube segments 36 may be formed in other configurations (e.g., diverging, converging, elliptical, airfoil like, polygonal having straight or curved sides, and the like).
  • the tube segment 36 can have any suitable tube depth T ( FIG. 3 ) defined as the distance between the leading edge 38 and trailing edge 40.
  • the tube depth T can be less than 16 millimeters (mm), for example, less than 14 mm, or, 6 mm to 14 mm, or, 8 mm to 12 mm, or, 10 mm.
  • the heat exchanger tube segments 36 illustrated and described herein are intended as an example only and tube segments 36 having other constructions are within the scope of the disclosure.
  • the tube segments 36 may have a plurality of tube portions separated by a web as disclosed in US 2014/0231056 A1, filed September 25, 2012 , and US 2015/0027677 A1, filed on January 29, 2013 .
  • a plurality of fins 50 may be mounted to a portion, such as the exterior for example, of the plurality of tube segments 36, and serve as a secondary heat transfer surface configured to transfer heat between a second heat transfer fluid (e.g., air, nitrogen, and the like) and a first heat transfer fluid (e.g., refrigerant, including low global warming potential (GWP) refrigerants such as CO 2 , or other fluid flowing through the tube segments 36).
  • a second heat transfer fluid e.g., air, nitrogen, and the like
  • a first heat transfer fluid e.g., refrigerant, including low global warming potential (GWP) refrigerants such as CO 2 , or other fluid flowing through the tube segments 36.
  • GWP low global warming potential
  • each of the plurality of tube segments 36 of the heat exchanger 30 can include one or more folds 60.
  • a fold 60 may be arranged at any location along a length, L, of the tube segments 36 (e.g., measured along an x-axis dimension corresponding to the longest dimension of the tube segment 36, as shown in FIG. 2 ).
  • a fold 60 can be formed about an axis extending parallel to a manifold (e.g., the first manifold 32, the second manifold 34, or the like) and substantially perpendicular to the longitudinal axis of the tube segment 36 (along which the length of the tube segment 36 can be measured).
  • a manifold e.g., the first manifold 32, the second manifold 34, or the like
  • the fold 60 may be formed such that two portions of the heat exchange tube segment 36 adjacent to and on opposite sides of a respective fold 60 are arranged in substantially parallel relation.
  • substantially parallel as used herein, can be defined as where an angle ⁇ , measured between two centerlines corresponding to each of the two elements described as in “substantially parallel” relation (see FIG. 5 ), is less than or equal to 5°, for example, less than or equal to 3°, or, less than or equal to 1°, or less than or equal to 0.5° (e.g., such as accounting for variations due to tooling tolerances, or manufacturing variations in a tube segment).
  • the portions of a heat exchanger tube segment 36 on opposite sides of a respective fold 60 are generally arranged at an angle ⁇ between 175° and 185° relative to one another.
  • the fold 60 is a ribbon fold wherein the tube segments 36 are partially twisted to achieve a substantially parallel orientation of the two portions on opposing sides of the fold 60 without causing the tube segment 36 to collapse.
  • the tube segments 36 may be free of fins 50 at a selected portion 52 (see FIG. 2 ) within or surrounding the location of a fold 60.
  • Each fold 60 is configured to change the flow direction by a flow angle of about 180° (measured between the direction of flow through the interior passages of the tube segment 36 adjacent to and on opposite sides of the fold 60) such that the heat exchanger 30 has a multipass configuration relative to the direction of flow A of the second heat transfer fluid (e.g., air, nitrogen, and the like), e.g., where the second heat transfer fluid passes the first heat transfer fluid two or more times.
  • the tube segments 36 on opposing sides of the fold 60 can form a plurality of tube banks, e.g., a first tube bank 80 and a second tube bank 82.
  • the second tube bank 82 can be arranged downstream or behind the first tube bank 80 with respect to the direction of a flow A of the second heat transfer fluid (e.g., forming a two-pass configuration for the first heat transfer fluid).
  • the heat exchanger 30 has a first tube bank 80 and a second tube bank 82 defined by the fold 60, with the second tube bank 82 being arranged in substantially parallel relation to a first tube bank 80.
  • the heat exchanger 30 illustrated in FIG. 5 includes two folds 60 which form a first tube bank 80, a second tube bank 82, and a third tube bank 84.
  • the heat exchanger 30 can have any number of folds 60, for example, 1 to 20 folds, or, 1 to 10 folds, or 1 to 5 folds, or, 1 to 3 folds, or 1 to 2 folds.
  • the plurality of tube segments 36 includes at least two bends 70 having an angle other than 180° (relative to the direction of flow through a tube segment) such that at least one of the tube banks of the heat exchanger 30 has a non-linear configuration as measured along the flow direction through the interior flow passages of the tube segment 36.
  • the heat exchanger 30 includes a first bend 70a, imparting a first flow angle ⁇ 1 other than 180° on a fluid flowing through the tube segment 36, and a second bend 70b imparting a second flow angle ⁇ 2 other than 180°.
  • the first flow angle ⁇ 1 can be equal to the second flow angle ⁇ 2, or the two angles can be unequal.
  • the bend 70 has an angle of less than 180°.
  • Heat exchangers 30 having any non-linear configuration are within the scope of the invention.
  • the heat exchanger 30 can be configured for a counter flow relation, cross flow relation, or a combination including at least one of the foregoing of the two fluids exchanging heat in the heat exchanger.
  • One or more folds 60 and at least two bends 70 can be used to build up the thickness of the heat exchanger 30 (relative to the flow of the second heat transfer fluid) which can allow for the manufacture of many different thicknesses without changing the basic tube segment design. In this way, the capacity of the heat exchanger 30 can be altered without altering the manufacturing tooling (e.g., extrusion equipment in the case of an extruded tube).
  • the manufacturing tooling e.g., extrusion equipment in the case of an extruded tube.
  • a plurality of heat exchange tube segments 36 having a length extending between an first inlet end and a second outlet end equal to a total length of the flow path are formed, for example via extrusion.
  • the first manifold 32 is connected to the first end of each of the plurality of tube segments 36 and the second manifold 34 is connected to the second, opposite end of each of the plurality of tube segments 36.
  • Each of the plurality of folds 60 and bends 70, is then formed in the tube segments 36 at various locations to achieve a heat exchanger 30 having a desired configuration and flow path.
  • Formation of a heat exchanger 30 as described herein provides the benefit that the same manufacturing equipment can be used to fabricate a heat exchanger 30 having any of a variety of configurations. Further, formation of a heat exchanger 30 as described herein eliminates the need for intermediate manifolds, thereby reducing complexity and cost.
  • the overall size of the plurality of heat exchange tube segments 36 may also be decreased via extrusion. Because the first manifold and second manifold 32, 34 are configured to couple to the heat exchanger tube segments 36 of only one tube bank, the size of the manifolds 32, 34, may also be reduced.
  • the heat exchanger 30 may provide the structural integrity necessary for use with high pressure refrigerants, for example such as carbon dioxide (CO 2 ) or ethane (C 2 H 6 ).
  • High pressure refrigerants can be operated in transcritical and/or supercritical systems where the refrigerant pressure within the system can be greater than 720 psig (49.6 bar), for example, greater than 750 psig (51.7 bar), or, greater than 1,100 psig (75.8 bar), or, greater than 1,500 psig (103.4 bar), or, from 750 psig (51.7 bar) to 2,000 psig (137.9 bar).
  • psig refers to gauge pressure measure in pounds per square inch relative to ambient pressure.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Claims (13)

  1. Wärmetauscher (10), der Folgendes umfasst:
    einen ersten Verteiler (32);
    einen zweiten Verteiler (34), der von dem ersten Verteiler getrennt ist;
    eine Vielzahl von Wärmetauschrohrsegmenten (36), die in einer beabstandeten parallelen Beziehung angeordnet sind und den ersten Verteiler und den zweiten Verteiler fluidisch koppeln, wobei die Vielzahl von Wärmetauschrohrsegmenten eine Faltung (60) beinhaltet, die ein erstes Rohrbündel (80) und ein zweites Rohrbündel (82) bildet, die zueinander parallel sind, und wobei das erste Rohrbündel und das zweite Rohrbündel für eine sequentielle Strömung eines ersten Wärmeübertragungsfluids dort hindurch konfiguriert sind; und
    einen erste Bogen (70a), der in dem ersten Rohrbündel und dem zweiten Rohrbündel gebildet ist;
    dadurch gekennzeichnet, dass:
    die Rohrsegmente eine Rohrtiefe umfassen, die von einer Vorderkante (38) zu einer Hinterkante (40) des Rohrsegments gemessen wird, wobei die Rohrtiefe geringer als 14 Millimeter ist, und
    wobei der Wärmetauscher ferner einen zweiten Bogen (70b) umfasst, der in dem ersten und zweiten Rohrbündel gebildet ist, wobei die Bogen einen anderen Winkel als 180° aufweisen.
  2. Wärmetauscher nach Anspruch 1, wobei es sich bei der Vielzahl von Wärmetauschrohrsegmenten um Mikrokanalrohre handelt, die eine Vielzahl von einzelnen Strömungskanälen aufweisen, die darin gebildet sind.
  3. Wärmetauscher nach einem der vorhergehenden Ansprüche, wobei eine Vielzahl von Rippen (50) sich von mindestens einem Abschnitt der Wärmetauschrohrsegmente erstreckt.
  4. Wärmetauscher nach einem der vorhergehenden Ansprüche, wobei das Fluid ein Hochdruckkühlmittel ist, das für eine Verwendung bei Drücken, die 750 psig (51,7 bar) überschreiten, konfiguriert ist.
  5. Wärmetauscher nach einem der vorhergehenden Ansprüche, wobei der Wärmetauscher zwei Faltungen (60) beinhaltet, die drei Rohrbündel (80, 82, 84) definieren.
  6. Wärmetauscher nach einem der vorhergehenden Ansprüche, wobei der Strömungsweg der ersten Wärmeübertragung eine Vielzahl von Durchläufen relativ zu einem zweiten Wärmeübertragungsfluid beinhaltet.
  7. Verfahren zur Herstellung eines Wärmetauschers (30), das Folgendes umfasst:
    Bilden einer Vielzahl von Wärmetauschrohrsegmenten (36);
    Falten der Vielzahl von Wärmetauscherrohrsegmenten, um ein erstes Rohrbündel (80) und ein zweites Rohrbündel (82) zu definieren, wobei eine erste Mittellinie des ersten Rohrbündels und eine zweite Mittellinie des zweite Rohrbündels parallel sind;
    Bilden eines ersten Bogens (70a) und eines zweiten Bogens (70b) in der Vielzahl von Wärmetauscherrohrsegmenten, wobei der Bogen einen anderen Winkel als 180° aufweist, sodass der Wärmetauscher eine nichtlineare Konfiguration aufweist;
    wobei die Rohrsegmente eine Rohrtiefe umfassen, die von einer Vorderkante (38) zu einer Hinterkante (40) des Rohrsegments gemessen wird, wobei die Rohrtiefe geringer als 14 Millimeter ist.
  8. Verfahren nach Anspruch 7, wobei die Faltung der Vielzahl von Wärmetauschrohrsegmenten um eine Achse erfolgt, die senkrecht zu einer Längsachse der Vielzahl von Wärmetauschrohrsegmenten angeordnet ist.
  9. Verfahren nach einem der Ansprüche 7 oder 8, wobei das Bilden der Vielzahl von Wärmetauschrohrsegmenten ein Extrudieren der Vielzahl von Wärmetauschrohrsegmenten beinhaltet.
  10. Verfahren nach einem der Ansprüche 7 bis 9, wobei es sich bei der Vielzahl von Wärmetauschrohrsegmenten um Mikrokanalrohre handelt, die eine Vielzahl von einzelnen Strömungskanälen aufweisen, die darin gebildet sind.
  11. Verfahren nach einem der Ansprüche 7 bis 10, ferner umfassend:
    Montieren einer Vielzahl von Rippen (50) an mindestens einem Abschnitt der Wärmetauschrohrsegmente.
  12. Verfahren nach einem der Ansprüche 7 bis 11, ferner umfassend:
    Anbringen eines ersten Verteilers (32) an einem ersten Ende der Vielzahl von Wärmetauschrohrsegmenten; und
    Anbringen eines zweiten Verteilers (34) an einem zweiten, gegenüberliegenden Ende der Vielzahl von Wärmetauschrohrsegmenten.
  13. Verfahren nach Anspruch 12, wobei der erste Verteiler und der zweite Verteiler für eine Verwendung mit einem Hochdruckkühlmittel konfiguriert sind, die 750 psig (51,7 bar) überschreitet.
EP16753806.5A 2015-08-14 2016-08-12 Mikrokanal-wärmetauscher Active EP3334991B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201562205347P 2015-08-14 2015-08-14
PCT/US2016/046664 WO2017030922A1 (en) 2015-08-14 2016-08-12 Microchannel heat exchanger

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EP3334991A1 EP3334991A1 (de) 2018-06-20
EP3334991B1 true EP3334991B1 (de) 2020-09-30

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EP (1) EP3334991B1 (de)
CN (1) CN107923712A (de)
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CN107923712A (zh) 2018-04-17
EP3334991A1 (de) 2018-06-20

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