EP2643644B1 - Groupe frigorifique avec échangeur thermique résistant à la corrosion - Google Patents

Groupe frigorifique avec échangeur thermique résistant à la corrosion Download PDF

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Publication number
EP2643644B1
EP2643644B1 EP11784915.8A EP11784915A EP2643644B1 EP 2643644 B1 EP2643644 B1 EP 2643644B1 EP 11784915 A EP11784915 A EP 11784915A EP 2643644 B1 EP2643644 B1 EP 2643644B1
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EP
European Patent Office
Prior art keywords
refrigeration unit
tube
recited
refrigerant
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.)
Active
Application number
EP11784915.8A
Other languages
German (de)
English (en)
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EP2643644A2 (fr
Inventor
Michael F. Taras
Mark J. Perkovich
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
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Filing date
Publication date
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Publication of EP2643644A2 publication Critical patent/EP2643644A2/fr
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Publication of EP2643644B1 publication Critical patent/EP2643644B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D21/00—Defrosting; Preventing frosting; Removing condensed or defrost water
    • F25D21/14—Collecting or removing condensed and defrost water; Drip trays
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D11/00—Self-contained movable devices, e.g. domestic refrigerators
    • F25D11/003—Transport containers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D19/00—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors
    • F25D19/003—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors with respect to movable containers
    • 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
    • F28D1/0233—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 air flow channels
    • F28D1/024—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 air flow channels with an air driving element
    • 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
    • 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
    • F28F1/24—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 and extending transversely
    • F28F1/32—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 and extending transversely the means having portions engaging further tubular elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/04—Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D2500/00—Problems to be solved
    • F25D2500/02—Geometry problems

Definitions

  • This invention relates generally to refrigeration units and gas cooler/condenser heat exchangers and, more particularly, to improving condensate drainage and corrosion durability on gas cooler/condenser heat exchangers of transport refrigeration units.
  • Perishable goods are commonly transported in a controlled environment within an enclosed space such as an insulated cargo box of a truck, trailer, container, or intermodal container.
  • a refrigeration system also known as a transport refrigeration unit, is used in operative association with the enclosed space within the cargo box for controlling the temperature of the air within the enclosed space within a desired temperature range selected for the particular type of perishable goods stowed within the cargo box.
  • the refrigeration unit is mounted to a wall of the cargo box, typically to the forward end of the cargo box, opposite the doors to the cargo box which at typically at the rear of the cargo box.
  • the refrigeration unit includes a refrigerant compressor and condenser disposed externally of the cargo box and an evaporator disposed within the enclosed space of the cargo box, the compressor, condenser and evaporator being connected in a refrigerant circuit in series refrigerant flow relationship.
  • air to be cooled is drawn from within the enclosed space, passes through an evaporator in heat exchange relationship with the refrigerant vapor passing through the heat exchange tubes of the evaporator, and then supplied back to the enclosed space.
  • the refrigerant vapor having traversed the evaporator is compressed in the compressor to a high temperature, high pressure vapor and then passed through the condenser which functions as a refrigerant heat rejection heat exchanger wherein the high temperature refrigerant vapor passes is heat exchange relationship with cooler air, typically ambient air, or water/glycol solution.
  • the condenser includes a standard round tube plate fin (RTPF) heat exchanger having an array of round tubes penetrating a pack of spaced plate fins.
  • RTPF round tube plate fin
  • a plurality of round tubes are inserted through holes in the plates of the fin pack so as to extend longitudinally through the plates of the fin pack and a pair of tube sheets disposed at opposite ends of the fin pack.
  • the ends of the round tubes penetrating the tube sheets are connected by tube bends or return bends to form one or more refrigerant flow circuits through heat exchanger.
  • the condenser heat exchanger is arranged with the round tubes extended longitudinally in a generally horizontal direction and the fin plates extend in a generally vertical plane.
  • the fin plates are generally flat plates or wavy plates and may include louvers or other fin enhancements to improve air-side heat transfer performance.
  • the condenser heat exchanger With the condenser heat exchanger extending in a horizontal position as in the prior art, a large amount of space is required.
  • the horizontal arrangement of the heat exchanger coil ensures that any condensate that deposits on the surface of the fins naturally drains off the fins due to the vertical orientation of the plate fins. It is desirable to avoid condensate accumulation on the fin surface as water is an electrolyte, the presence of which on the fin surface can lead to accelerated corrosion. Accordingly, a desire exists for a more compact condenser heat exchanger coil design that promotes adequate water drainage and provides acceptable corrosion durability.
  • Document US2694553 discloses a refrigerated vehicle comprising an elongated enclosure, louvered doors pivoted to each of the sides of said enclosure at one end, an electricity generating unit mounted in said enclosure with its axis of rotation extending transversely of said enclosure, a refrigerant compressing unit mounted in said enclosure with its axis of rotation extending transversely of said enclosure, said refrigerant compressing unit being energized by said electricity generating unit, a refrigerant condenser mounted in said enclosure above said refrigerant compressing unit, means for conducing refrigerant from said refrigerant compressing unit to said refrigerant condenser, and opening in the roof of said enclosure, a duct extending from said refrigerant condenser to said opening and means for moving air into said enclosure through said louvered doors, through said refrigerant condenser and discharging said air from said enclosure through said duct, an evaporator, means for conducting refrigerant from said condenser to
  • each linear tube segment extends longitudinally at an inclination angle in the range from at least 20 degrees to 90 degrees.
  • Each heat exchange loop may have a generally square configuration, a generally rhombus-like configuration, a generally hexagon-like configuration or other configuration without any significant length of vertically extending tube segments.
  • the fins may be flat plate fins or wavy plate fins, with or without further airside heat transfer enhancements such as louvers, offsets or the like.
  • the cargo container 10 has an insulated box-like structure formed of a forward or front wall 12, a back or rear wall 14, a pair of opposed sidewalls 13 and 15, a ceiling 16 and a floor 18.
  • the box-like structure defines a cargo space 11 in which the bins, cartons or pallets of cargo 100 being transported are stacked on the floor 18.
  • the rear wall 14 is provided with one or more doors (not shown) through which access to the cargo space may be had for loading the cargo 18 into the container 10. When the doors are closed, a substantially air-tight, sealed cargo space is established within the container 10 which prevents inside air from escaping the cargo space 11.
  • a refrigeration unit 20 is mounted to a wall of the container 10.
  • the refrigeration unit 20 is received in an opening in the forward wall 12 of the container 10 and mounted around its perimeter to the forward wall 12 of the container 10, for example as depicted in FIG. 1 , for conditioning the air within the refrigerated chamber 11, i.e. the cargo space of the container 10.
  • the refrigeration unit 20 includes a compressor 22 with an associated compressor drive motor and a condenser/gas cooler module 24 isolated from the cargo space 11, and an evaporator module operatively associated with the cargo space 11 defined within the container 10.
  • the evaporator module includes a pair of evaporator fans 26 disposed within an upper portion of the refrigeration unit in air flow communication with the interior volume of the cargo box 11 and an evaporator heat exchanger (not shown) having a plurality of refrigerant conveying tubes through which refrigerant vapor flowing through the refrigeration circuit of the refrigeration unit 20 passes in heat exchange relationship with air to be cooled that is drawn from within cargo space 11 by the evaporator fans 26, passed over the evaporator heat exchanger surface and supplied back to the cargo space.
  • the condenser/gas cooler module 24 includes a condenser fan 28 and a refrigerant heat rejection heat exchanger 30 mounted in the forward section of the refrigeration unit 20 external to the cargo space 11.
  • the refrigerant heat rejection heat exchanger 30 may function either as a condenser or as a gas cooler.
  • the refrigerant heat rejection heat exchanger functions as condenser, that is to condense the high temperature, high pressure refrigerant vapor passing therethrough to a high pressure, lower temperature refrigerant liquid.
  • the refrigerant heat rejection heat exchanger In refrigeration units wherein the refrigerant heat rejection heat exchanger is a component of a refrigerant vapor compression system operating in a transcritical cycle, the refrigerant heat rejection heat exchanger functions only as a gas cooler, that is to cool, but not condense, the high temperature, high pressure refrigerant vapor passing there through to a high pressure, lower temperature refrigerant vapor.
  • the refrigerant heat rejection heat exchanger 30 comprises a finned tube heat exchanger that wraps around the condenser fan 28.
  • the wraparound finned tube coil 32 has a plurality of heat exchange tube loops 34 and a plurality of plate fins 40 mounted to the plurality of heat exchange tube loops 34.
  • the fins 40 may be flat plate fins or wavy plate fins, as depicted in FIG. 5 , with or without further airside heat transfer enhancements, such as louvers, offsets, corrugations or the like.
  • the wraparound finned tube coil 32 has several tube rows, typically from two to twelve, with several tube loops 34, typically two to four, per row. In the embodiment depicted in FIGs. 3-5 , the wraparound finned tube heat exchanger 32 has five tube rows with three heat exchange tube loops 34 per row.
  • the condenser fan 28 draws ambient outdoor air through the refrigerant heat rejection heat exchanger 30 behind the front panel 21 (incoming air flow in direction of arrows) and discharges that air back into the outdoor environment through and an opening 23 in the front panel 21 of the refrigeration unit 20 about the condenser/gas cooler fan 28. Both configurations with fan 28 positioned upstream or downstream of the condenser/gas cooler may be employed, however the latter arrangement is thermodynamically more effective.
  • each heat exchange tube loop 34 is formed by a plurality of linear tube segments or hairpins 36 connected by return bends 38.
  • Each heat exchange tube loop 34 may be formed of a continuous heat exchange tube extending between a pair of tube sheets 42 and 44.
  • the ends of the heat exchange tubes penetrating each tube sheet 42 and 44 may be interconnected by U-bends (not shown) to form one or more refrigerant flow circuits, as desired, through the heat exchanger 30 in a manner well-known to those skilled in the art.
  • each heat exchange tube loop 34 the heat exchange tube is bent as appropriate to delineate a desired shape.
  • the heat exchange tube loop 34 may take the shape of a parallelogram, such as illustrated in the exemplary embodiment depicted in FIG. 6 , the heat exchange tube loop 34 is formed by bending the heat exchange tube to delineate a generally square (rhombus with equal included angles) shape extending between tube sheets 42 and 44.
  • the heat exchange tube loop 34 may delineate other shapes also, for example such as in the exemplary embodiment depicted in FIG. 7 , where the heat exchange tube loop 34 is formed by bending the heat exchange tube to delineate a generally hexagonal shape extending between the tube sheets 42 and 44.
  • the heat exchange tube loop 34 may also be formed as a non-linear tube loop having, for example, a generally circular configuration such as illustrated in FIG. 9 or a generally oval confirmation such as illustrated in FIG. 10 .
  • each linear tube segment 36 of each heat exchange loop 34 extends longitudinally at an inclination angle, ⁇ , with respect to vertical, V, of at least 20 degrees.
  • each linear tube segment extends longitudinally at an inclination angle in the range from at least 20 degrees up to and including 90 degrees, which represents a horizontally extending tube segment.
  • the angle of indication, ⁇ is measured as the interior included angle between the longitudinal axis of the linear tube segment 36 and a vertical axis, V.
  • the plate fins 40 would extend generally horizontally which would in no way promote drainage of water from the within surface and, in the case of wavy plate fins, allow accumulation of water in the valleys of the wavy plate fins. Over time, since water accumulating on the surface of the plate fins acts as an electrolyte initiating and accelerating the corrosion process, the corrosion durability of the plate fins would be significantly shortened.
  • heat rejection heat exchanger construction can comprise more than one heat rejection heat exchanger.
  • condenser/gas cooler and intercooler as well as condenser/gas cooler and radiator can be integrated in a single module and formed (bent) at the same time.
  • the former configurations may be utilized in high efficiency systems and the latter designs applied in the HVAC&R systems driven by the engine.
  • wraparound finned tube heat exchanger 32 was described herein as having round heat exchange tubes, it is to be understood that the heat exchange tubes could instead be non-round tubes, such as multichannel flattened tubes of generally rectangular or oval cross-section. Therefore, it is intended that the present disclosure not be limited to the particular embodiment(s) disclosed as, but that the disclosure will include all embodiments falling within the scope of the appended claims.

Claims (12)

  1. Groupe frigorifique de transport (20) pour le conditionnement de l'air à l'intérieur d'une boîte de chargement réfrigérée (10) pour loger des denrées périssables au cours du transport, comprenant :
    un échangeur thermique de rejet de chaleur de réfrigérant (30) et un ventilateur (28) associé de manière fonctionnelle à l'échangeur thermique (30), l'échangeur thermique de rejet de chaleur de réfrigérant (30) incluant une bobine de tube à ailettes enveloppante (32) s'étendant le long d'une périphérie radialement à l'extérieur du ventilateur (28), la bobine de tube à ailettes enveloppante (32) ayant une pluralité de boucles de tube d'échange thermique (34) et une pluralité de plaques-ailettes (40) montées sur la pluralité de boucles de tube d'échange thermique (34),
    dans lequel chaque boucle de tube d'échange thermique (34) est formée par une pluralité de segments de tube linéaires (36) reliés par des coudes de tube (38), la pluralité de boucles de tube d'échange thermique (34) sont agencées dans une pluralité de rangées de tubes, chaque rangée de tubes incluant une pluralité de boucles de tube (34), et chaque segment de tube linéaire (36) s'étendant longitudinalement selon un angle d'inclinaison (θ) par rapport à la verticale d'au moins 20 degrés, dans lequel les plaques-ailettes (40) s'étendent perpendiculairement à l'axe longitudinal des segments de tube linéaires (36) des boucles de tube d'échange thermique (34) afin d'assurer un drainage approprié de l'eau s'accumulant à la surface des plaques-ailettes (40).
  2. Groupe frigorifique de transport (20) selon la revendication 1, dans lequel chaque segment de tube linéaire (36) s'étend longitudinalement selon un angle d'inclinaison (θ) dans la plage allant d'au moins 20 degrés à 90 degrés.
  3. Groupe frigorifique de transport (20) selon la revendication 1, dans lequel la pluralité de plaques-ailettes (40) comprend une pluralité de plaques ayant une configuration ondulée.
  4. Groupe frigorifique de transport (20) selon la revendication 3, dans lequel la pluralité de plaques-ailettes (40) inclut des éléments d'amélioration de transfert de chaleur.
  5. Groupe frigorifique de transport (20) selon la revendication 1, dans lequel chaque boucle de tube d'échange thermique (34) a une configuration généralement de type carrée.
  6. Groupe frigorifique de transport (20) selon la revendication 1, dans lequel chaque boucle de tube d'échange thermique (34) a une configuration généralement de type en losange.
  7. Groupe frigorifique de transport (20) selon la revendication 1, dans lequel chaque boucle de tube d'échange thermique (34) a une configuration généralement de type hexagonale.
  8. Groupe frigorifique de transport (20) selon la revendication 1, dans lequel le groupe frigorifique (20) fonctionne dans un cycle subcritique et l'échangeur thermique de rejet de chaleur de réfrigérant (30) fonctionne en tant que condenseur.
  9. Groupe frigorifique de transport (20) selon la revendication 1, dans lequel le groupe frigorifique (20) fonctionne dans un cycle transcritique et l'échangeur thermique de rejet de chaleur de réfrigérant (30) fonctionne en tant que refroidisseur de gaz.
  10. Groupe frigorifique de transport (20) selon la revendication 1, dans lequel l'échangeur thermique de rejet de chaleur de réfrigérant (30) comprend plusieurs échangeurs thermiques de rejet de chaleur de réfrigérant (30) .
  11. Groupe frigorifique de transport (20) selon la revendication 1, dans lequel les plusieurs échangeurs thermiques de rejet de chaleur (30) incluent un condenseur/refroidisseur de gaz et un refroidisseur intermédiaire.
  12. Groupe frigorifique de transport (20) selon la revendication 1, dans lequel les plusieurs échangeurs thermiques de rejet de chaleur (30) incluent un condenseur/refroidisseur de gaz et un radiateur.
EP11784915.8A 2010-11-24 2011-11-14 Groupe frigorifique avec échangeur thermique résistant à la corrosion Active EP2643644B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US41681510P 2010-11-24 2010-11-24
PCT/US2011/060535 WO2012071202A2 (fr) 2010-11-24 2011-11-14 Groupe frigorifique avec échangeur thermique résistant à la corrosion

Publications (2)

Publication Number Publication Date
EP2643644A2 EP2643644A2 (fr) 2013-10-02
EP2643644B1 true EP2643644B1 (fr) 2019-07-31

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP11784915.8A Active EP2643644B1 (fr) 2010-11-24 2011-11-14 Groupe frigorifique avec échangeur thermique résistant à la corrosion

Country Status (6)

Country Link
US (1) US20130233524A1 (fr)
EP (1) EP2643644B1 (fr)
CN (1) CN103221762B (fr)
DK (1) DK2643644T3 (fr)
SG (1) SG190390A1 (fr)
WO (1) WO2012071202A2 (fr)

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Publication number Priority date Publication date Assignee Title
JP2015198639A (ja) * 2014-03-31 2015-11-12 ダイキン工業株式会社 混合ガス供給装置及びコンテナ用冷凍装置
JP5862737B1 (ja) * 2014-09-16 2016-02-16 ダイキン工業株式会社 コンテナ用冷凍装置
CN109844428B (zh) 2016-10-12 2021-06-18 开利公司 冷藏存储集装箱空气通道
JP2022503407A (ja) 2018-11-12 2022-01-12 キャリア コーポレイション 冷凍システム用のコンパクト熱交換器アセンブリ
EP3686525A1 (fr) * 2019-01-25 2020-07-29 Carrier Corporation Bobine réfrigérante autoventilée

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US2252064A (en) * 1938-10-22 1941-08-12 Jr Edward S Cornell Heat exchange unit and system
US2363974A (en) * 1943-08-02 1944-11-28 Advance Mfg Inc Mounting for refrigerating apparatus and the like
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ITPD20050132A1 (it) * 2005-05-11 2006-11-12 Costan Spa Procedimento per raffreddare la co2 in un impianto frigorifero ed uno scambiatore di calore a batteria alettata per realizzare tale procedimento
US8381538B2 (en) * 2006-11-08 2013-02-26 Carrier Corporation Heat pump with intercooler
CA2709578A1 (fr) * 2007-12-18 2009-06-25 A-Heat Allied Heat Exchange Technology Ag Systeme d'echange de chaleur modulaire

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Also Published As

Publication number Publication date
EP2643644A2 (fr) 2013-10-02
CN103221762B (zh) 2016-10-19
CN103221762A (zh) 2013-07-24
WO2012071202A2 (fr) 2012-05-31
WO2012071202A3 (fr) 2012-11-08
US20130233524A1 (en) 2013-09-12
DK2643644T3 (da) 2019-11-04
SG190390A1 (en) 2013-06-28

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