US20080184713A1 - Heat Exchanger Arrangement - Google Patents

Heat Exchanger Arrangement Download PDF

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Publication number
US20080184713A1
US20080184713A1 US11/908,408 US90840807A US2008184713A1 US 20080184713 A1 US20080184713 A1 US 20080184713A1 US 90840807 A US90840807 A US 90840807A US 2008184713 A1 US2008184713 A1 US 2008184713A1
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US
United States
Prior art keywords
flow path
heat exchanger
refrigerant
flow
heat exchange
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.)
Abandoned
Application number
US11/908,408
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English (en)
Inventor
Hans-Joachim Huff
Tobias H. Sienel
Yu Chen
Parmesh Verma
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.)
Taylor Commercial FoodService LLC
Original Assignee
Carrier Comercial Refrigeration Inc
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Carrier Comercial Refrigeration Inc filed Critical Carrier Comercial Refrigeration Inc
Priority to US11/908,408 priority Critical patent/US20080184713A1/en
Assigned to CARRIER COMMERCIAL REFRIGERATION, INC. reassignment CARRIER COMMERCIAL REFRIGERATION, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HUFF, HANS-JOACHIM, VERMA, PARMESH, CHEN, YU, SIENEL, TOBIAS H.
Publication of US20080184713A1 publication Critical patent/US20080184713A1/en
Abandoned legal-status Critical Current

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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
    • F28D1/047—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
    • F28D1/0477—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 being bent in a serpentine or zig-zag
    • 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
    • F25B6/00—Compression machines, plants or systems, with several condenser circuits
    • F25B6/04—Compression machines, plants or systems, with several condenser circuits arranged in series
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25D19/02—Arrangement or mounting of refrigeration units with respect to devices or objects to be refrigerated, e.g. infrared detectors plug-in type
    • 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
    • F28F1/122—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 being formed of wires
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F28F9/262—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators for radiators
    • 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
    • F25D—REFRIGERATORS; COLD ROOMS; ICE-BOXES; COOLING OR FREEZING APPARATUS NOT OTHERWISE PROVIDED FOR
    • F25D23/00—General constructional features
    • F25D23/003—General constructional features for cooling refrigerating machinery
    • 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
    • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
    • F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
    • F25D2317/065—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air return
    • F25D2317/0651—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air return through the bottom
    • 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
    • F25D2317/00—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass
    • F25D2317/06—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation
    • F25D2317/066—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air supply
    • F25D2317/0661—Details or arrangements for circulating cooling fluids; Details or arrangements for circulating gas, e.g. air, within refrigerated spaces, not provided for in other groups of this subclass with forced air circulation characterised by the air supply from the bottom
    • 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
    • F25D2323/00—General constructional features not provided for in other groups of this subclass
    • F25D2323/002—Details for cooling refrigerating machinery
    • F25D2323/0026—Details for cooling refrigerating machinery characterised by the incoming air flow
    • F25D2323/00264—Details for cooling refrigerating machinery characterised by the incoming air flow through the front bottom part
    • 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
    • F25D2323/00—General constructional features not provided for in other groups of this subclass
    • F25D2323/002—Details for cooling refrigerating machinery
    • F25D2323/0027—Details for cooling refrigerating machinery characterised by the out-flowing air
    • F25D2323/00271—Details for cooling refrigerating machinery characterised by the out-flowing air from the back bottom
    • 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

  • the invention relates to a heat exchanger arrangement for a vapor compression system, especially a transcritical vapor compression system.
  • the heat rejection process in transcritical vapor compression refrigeration applications and systems occurs at a pressure above the critical pressure of the refrigerant.
  • the refrigerant does not undergo a phase change during this process and the temperature of the refrigerant changes throughout the entire heat rejection process.
  • the energy efficiency of the refrigeration system increases if the heat exchanger arrangement approaches an ideal counter flow arrangement with the heat sink.
  • a refrigeration system which comprises a compressor for driving a refrigerant along a flow path in at least a first mode of system operation; a first heat exchanger along the flow path downstream of the compressor in the first mode; a second heat exchanger along the flow path upstream of the compressor in the first mode; and a pressure regulator or expansion device in the flow path downstream of the first heat exchanger and upstream of the second heat exchanger in the first mode, wherein the first heat exchanger is positioned within a housing which defines a flow path for heat exchange fluid and the housing defines a zone of reduced flow area along the flow path, and wherein the first heat exchanger is positioned in the zone of reduced flow area.
  • a refrigeration system which includes a compressor for driving a refrigerant along a flow path in at least a first mode of system operation; a first heat exchanger along the flow path downstream of the compressor in the first mode; a second heat exchanger along the flow path upstream of the compressor in the first mode; and a pressure regulator or expansion device in the flow path downstream of the first heat exchanger and upstream of the second heat exchanger in the first mode, wherein the first heat exchanger comprises a plurality of substantially parallel refrigerant flow paths, and wherein heat exchange fluid for the first heat exchanger is directed in counter flow substantially transverse to the refrigerant flow paths.
  • a preferred embodiment is drawn to transcritical vapor compression operation using CO 2 refrigerant fluid.
  • Serpentine and/or parallel modular refrigerant flow paths are provided.
  • a particular environment of use for the invention is in connection with so-called bottle coolers, or cooling units for cooling and storing beverages.
  • Such coolers can be in the form of vending machines are refrigerator cases, for example.
  • the housing of the beverage cooler defines an internal flow area for heat exchange fluid such as air, and this flow area has a flow restriction which serves to speed flow of the heat exchange fluid therethrough.
  • the refrigerant flow paths are positioned at the flow restriction.
  • FIG. 1 is a schematic illustration of a counter flow heat exchanger arrangement according to the invention
  • FIG. 2 is a schematic illustration of an alternate counter flow heat exchanger arrangement according to the invention.
  • FIG. 3 is an illustration of a preferred structure for a beverage cooler including the heat exchanger arrangement of the present invention
  • FIG. 4 illustrates a preferred type of heat exchanger according to the invention.
  • FIG. 5 illustrates a preferred embodiment of the structure shown in FIG. 3 .
  • the invention relates to refrigeration systems and, more particularly, to systems operating in a transcritical vapor compression regime, one particular embodiment of which is a beverage cooler.
  • a heat exchanger configuration is utilized which provides efficient exchange of heat between a refrigerant fluid and a heat exchange fluid.
  • a transcritical vapor compression system operates at pressures above the critical pressure of the refrigerant and, therefore, the refrigerant does not undergo a phase change during the process.
  • a counter flow arrangement of the heat rejection heat exchanger with respect to the heat exchange fluid provides better efficiency in operation, and this counter flow arrangement can be approached by a heat exchanger consisting of a single flow path of several parallel flow path segments.
  • FIG. 1 shows a refrigerant system 10 having a compressor 12 , a first heat exchanger 14 , a second heat exchanger 16 , an expansion device 18 and refrigerant lines connecting these components in serial fashion as illustrated.
  • FIG. 3 further illustrates a beverage cooler 20 into which system 10 is positioned.
  • FIG. 3 shows compressor 12 as well as first heat exchanger 14 and second heat exchanger 16 .
  • Cooler 20 has a housing which defines a first heat exchange fluid flow path (arrows 22 ) wherein external air is drawn from an inlet 24 , past first heat exchanger 14 , and to an outlet 26 .
  • a second fluid flow path (arrows 28 ) is also defined, and passes from within the space of the beverage cooler, past second heat exchanger 16 , and back to the refrigerated space.
  • flow path 22 passes through the housing and passes through a zone 23 of reduced flow area. At zone 23 , air flowing through the housing increases in velocity. According to the invention, it is preferred to position heat exchanger 14 at zone 23 .
  • FIG. 1 shows a simplified configuration of first heat exchanger 14 in accordance with the invention, and shows the heat exchanger in the form of a single refrigerant flow path or tube formed into a series of substantially parallel flow path segments.
  • the segments are serially fed with refrigerant fluid from compressor 12 such that the flow path segments include an upstream flow path segment 30 and a downstream flow path segment 32 .
  • all flow path segments are part of a single serpentine path and, thus, each segment is progressively further downstream as it relates to flow of refrigerant, when considered from upstream segment 30 to downstream segment 32 .
  • First heat exchanger 14 is positioned within the housing of beverage cooler 20 such that incoming heat exchange fluid 22 first passes the downstream refrigerant flow path segment 32 , and then passed increasingly over the next flow path segments in order until finally passing upstream flow path 30 .
  • This configuration has been found, according to the invention, to provide for good heat exchange between the heat exchange fluid and the refrigerant. particularly when the system defined is a transcritical vapor compression system.
  • FIG. 2 shows an alternative embodiment wherein the flow path segments are broken up into two main groups or components of the heat exchanger, and wherein the groups are positioned so as to define an upstream and a downstream component. Within each component, segments are defined in parallel. Incoming heat exchange fluid, as shown, passes first over the downstream component and then over the upstream component.
  • FIGS. 1 and 2 are examples of the counter flow arrangement of the present invention, and that alterations to these specific structures could of course be made by a person of skill in the art, well within the broad scope of the present invention.
  • a heat exchanger for use in accordance with the invention is a wire-on-tube heat exchanger, an example of which is illustrated in FIG. 4 .
  • FIG. 4 shows a portion of a heat exchanger 50 defined by a single flow tube 52 which has a serpentine flow configuration as illustrated in FIG. 1 and which also is configured to have a vertical structure as well.
  • heat exchanger 50 is shaped to have alternating angled sections 54 , 56 when considered in the direction of air flow as shown by arrow 58 .
  • a series of wires 60 are positioned along heat exchanger 50 in a substantially transverse direction to the paths defined by tube 52 , and wires 60 preferably follow tube 52 along the sections 54 , 56 .
  • Wires 60 can advantageously be positioned on both sides of tube 52 as shown in FIG. 4 .
  • FIG. 4 illustrates several turns of a wire-on-tube heat exchanger. It should be appreciated that the actual heat exchanger could continue for one or more additional angled sections 54 , 56 , to provide for the desired flow length of the heat exchanger.
  • FIG. 3 shows a further embodiment of the present invention wherein system 10 is incorporated into a beverage cooler 20 .
  • the beverages would be stored in a refrigerated area positioned above the portion illustrated, and communicated with the flow of air along path 28 .
  • Flow path 22 represents flow of outside or ambient air which enters through an inlet 24 located at the front 34 of cooler 20 and passes a first component 14 a of first heat exchanger 14 and then a second component 14 b of first heat exchanger 14 , and then to an outlet 26 preferably at the rear 36 of cooler 20 .
  • An inner housing wall 38 separates the area of flow path 22 from the area of flow path 28 .
  • This wall also serves to define a zone along flow path 22 where the cross sectional area, or flow area, is constricted. This reduction in flow area along path 22 serves to increase the velocity of flow through same.
  • second component 14 b of first heat exchanger 14 is preferably positioned at the zone of restricted flow as shown so that the increased flow velocity of heat exchange fluid passes over this heat exchanger. It has been found, according to the invention, that this positioning helps to further increase the efficiency in heat exchange between the heat exchange fluid and the refrigerant.
  • Reduced flow area zone 23 is in this embodiment shown toward the rear of path 22 , and is substantially completely filled with heat exchanger component 14 b.
  • a heat exchanger such as the wire-on-tube heat exchanger of FIG. 4 can advantageously be positioned at the zone 23 of increased flow velocity, and this heat exchanger is particularly efficient in exchanging heat with the flow of air passing through zone 23 .
  • a heat exchanger is advantageously positioned within the housing at a zone 23 where there is a decreased air flow area and a resulting increase in air flow velocity, and it is further preferred to position a wire on tube heat exchanger in zone 23 .
  • a wire-on-tube heat exchanger is considered to be a heat exchanger defined by one or more tubes, preferably a single tube, which has wires positioned for interaction with a passing air flow to increase heat exchange efficiency.
  • a heat exchanger is particularly desirable for positioning in a zone such as zone 23 since most heat exchangers would have too great of a resistance to air flow to position in such a location.
  • a wire-on-tube heat exchanger has sufficiently low resistance to air flow that positioning of such a heat exchanger in zone 23 does not significantly interfere with the flow dynamics of the system, and further the wire-on-tube heat exchanger is particularly efficient at heat exchange under such flow conditions.
  • FIG. 3 shows one embodiment of structure used to generate flow along paths 22 and path 28 .
  • Flow along flow path 22 can be generated using a fan 40 driven by a motor 42 as shown.
  • flow along path 28 can be generated by a fan 44 driven by a motor 46 as shown.
  • Other structures for generating the desired flows would be well known to a person of skill in the art and are well within the scope of the present invention.
  • first heat exchanger 14 and its components 14 a , 14 b can be formed as tubes, micro-channels or mini-channels, or the like.
  • the secondary fluid surface area of the tube can be increased, for example with fins attached to the tube.
  • the fins can be of any type, and can be in the shape of plates, wires, louvered fins or any other shape.
  • One preferred embodiment is that referred to as a “wire-on-tube” configuration as described above and illustrated in FIG. 4 .
  • this invention offers particular benefits.
  • This invention allows utilizing the space in a volume available for the heat exchanger most effectively.
  • the high operating pressure of CO 2 refrigeration applications reduces the effect of pressure drop on the system performance. Therefore, the high pressure drop in a single-tube serpentine arrangement of the heat exchanger as shown in FIG. 1 does not reduce the system performance significantly, while the effective utilization of the volume available for the heat exchanger paths maximizes the system performance.
  • the volume normally occupied by a heat exchanger 14 a ( FIG. 3 ) can be utilized for other system components, or to make existing components larger and/or more efficient.
  • the system according to the invention is discussed herein in terms of having upstream and downstream relationship with various components of the refrigerant circuit in at least one mode of operation. This takes into account that a device such as a beverage cooler utilizing the apparatus of the present invention could have more than one mode of operation, and/or intermittent modes of operation, aside from the “normal” cooling mode wherein the first heat exchanger gives off heat and the second heat exchanger cools air within a refrigerated space.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
US11/908,408 2005-03-18 2005-12-30 Heat Exchanger Arrangement Abandoned US20080184713A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US11/908,408 US20080184713A1 (en) 2005-03-18 2005-12-30 Heat Exchanger Arrangement

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
US66396205P 2005-03-18 2005-03-18
US11/908,408 US20080184713A1 (en) 2005-03-18 2005-12-30 Heat Exchanger Arrangement
PCT/US2005/047523 WO2006101562A2 (en) 2005-03-18 2005-12-30 Heat exchanger arrangement

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US20080184713A1 true US20080184713A1 (en) 2008-08-07

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US (1) US20080184713A1 (ja)
EP (1) EP1869374A4 (ja)
JP (1) JP2008533424A (ja)
CN (1) CN101184963A (ja)
WO (1) WO2006101562A2 (ja)

Cited By (7)

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ES2352723A1 (es) * 2009-02-04 2011-02-22 Carlos Momplet Vivas Condensador térmico de doble batería perfeccionada.
DE102010010858A1 (de) * 2010-02-10 2011-08-11 Liebherr-Hausgeräte Ochsenhausen GmbH, 88416 Kühl- und/oder Gefriergerät
US20160356509A1 (en) * 2015-06-03 2016-12-08 Mitsubishi Electric Research Laboratories, Inc. System and Method for Controlling Vapor Compression Systems
EP2653808A3 (de) * 2012-04-18 2018-01-10 Liebherr-Hausgeräte Ochsenhausen GmbH Kühl- und/oder Gefriergerät
EP3244145A4 (en) * 2015-01-05 2018-06-20 Samsung Electronics Co., Ltd. Cooling device
EP3343129A1 (en) * 2014-03-07 2018-07-04 Mitsubishi Electric Corporation Refrigeration cycle apparatus
US11397014B2 (en) * 2019-03-26 2022-07-26 Johnson Controls Tyco IP Holdings LLP Auxiliary heat exchanger for HVAC system

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Publication number Priority date Publication date Assignee Title
JP5647352B2 (ja) * 2011-08-26 2014-12-24 住友重機械工業株式会社 圧縮装置、冷凍装置
ITUB20152983A1 (it) * 2015-08-07 2017-02-07 De Longhi Appliances Srl Condizionatore portatile perfezionato
JP2018185054A (ja) * 2015-09-24 2018-11-22 日本電産テクノモータ株式会社 冷却庫

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US2278226A (en) * 1941-03-03 1942-03-31 Halsey W Taylor Fluid cooler
US4207748A (en) * 1967-06-22 1980-06-17 Nebgen William H Heat exchange device and method
US5157941A (en) * 1991-03-14 1992-10-27 Whirlpool Corporation Evaporator for home refrigerator
US6158235A (en) * 1996-04-29 2000-12-12 Lancer Partnership, Ltd. Evaporator coil
US6467279B1 (en) * 1999-05-21 2002-10-22 Thomas J. Backman Liquid secondary cooling system
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JP2008533424A (ja) 2008-08-21
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EP1869374A2 (en) 2007-12-26
CN101184963A (zh) 2008-05-21
EP1869374A4 (en) 2011-11-16

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