EP1864060A1 - Systeme d'echangeur de chaleur - Google Patents

Systeme d'echangeur de chaleur

Info

Publication number
EP1864060A1
EP1864060A1 EP05856007A EP05856007A EP1864060A1 EP 1864060 A1 EP1864060 A1 EP 1864060A1 EP 05856007 A EP05856007 A EP 05856007A EP 05856007 A EP05856007 A EP 05856007A EP 1864060 A1 EP1864060 A1 EP 1864060A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
flat tube
flow
refrigerant
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.)
Withdrawn
Application number
EP05856007A
Other languages
German (de)
English (en)
Other versions
EP1864060A4 (fr
Inventor
Parmesh Verma
Tobias H. Sienel
Hans-Joachim Huff
Yu Chen
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
Publication of EP1864060A1 publication Critical patent/EP1864060A1/fr
Publication of EP1864060A4 publication Critical patent/EP1864060A4/fr
Withdrawn legal-status Critical Current

Links

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
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; 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
    • 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
    • F28D1/0478—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 the conduits having a non-circular cross-section
    • 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
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/01—Geometry problems, e.g. for reducing size
    • 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
    • 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
    • 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
    • F28D2021/0073—Gas coolers

Definitions

  • the invention relates to the design of the tube of a heat exchanger and, more particularly, to the design of a heat exchanger for use in applications where space for the heat exchanger is in short supply, and/or in connection with transcritical vapor compression systems.
  • Heat exchange efficiency is a concern in connection with heat exchangers, for example heat exchangers used in various refrigeration and other air handling applications.
  • Various types of heat exchangers have been provided, including tubes having fins and the like. The need remains, however, for a heat exchanger configuration which provides excellent heat exchange efficiency while occupying a relatively small space.
  • Other objects and advantages of the present invention will appear herein.
  • 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 at least one of the first heat exchanger and the second heat exchanger comprises a flat tube heat exchanger.
  • the flat tube heat exchanger is preferably a heat exchanger defined by a serpentine bending of a single flat tube heat exchanger.
  • the flat tube heat exchanger itself advantageously comprises a conduit for carrying refrigerant, wherein the conduit has a height or minor dimension, and a width or major dimension, and wherein the heat exchanger is arranged with the short dimension facing into the flow of heat exchange medium such as air.
  • FIG. 1 is a schematic illustration of a vapor compression system
  • FIG. 2 is an illustration of a cassette with a single serpentine flat tube heat exchanger according to the invention
  • FIG. 3 is a schematic illustration of CO 2 vapor compression system cassette
  • FIGs. 4 and 5 are schematic illustrations a flat tube single serpentine single row heat exchanger according to the invention
  • FIG. 6 illustrates a flat tube two row counterflow serpentine heat exchanger according to the invention
  • FIGs. 7 and 8 are illustrations of a flat tube single serpentine evaporator according to the invention.
  • FIGs. 9(a) and 9(b) are schematic cross sections of embodiments of the flat tube heat exchanger of the present invention.
  • the invention relates to vapor compression systems and, more particularly, to a heat exchanger tube configuration for such systems, particularly for transcritical vapor compression systems such as those operated with CO 2 .
  • the heat exchanger should have uniform refrigerant distribution and satisfactory condensate drainage in order to improve overall heat exchanger effectiveness and reliable operation of the compressor.
  • the heat exchanger combines the benefits of flat surfaces, single/multiple ports, single serpentine, multiple rows, counterflow, cross-counterflow, high heat transfer coefficients, low cost, suitable materials, corrosion resistant, high burst strength, ease of manufacturing, and reduced air blockage which helps to achieve size, efficiency, cost and reliability constraints of a CO 2 bottle cooler refrigeration system.
  • One of the ways to increase overall heat exchanger effectiveness is to have a flat tube heat exchanger.
  • Fig. 1 shows a refrigeration system 10 having a compressor 12, a heat rejection heat exchanger 14 which in a normal mode of operation, as illustrated by the arrows in Fig. 1, is a downstream heat exchanger when considered with respect to compressor 12, an expansion device 16 which is positioned downstream of heat exchanger 14, and a heat absorption heat exchanger 18 which is downstream of expansion device 16.
  • Flow in system 10 from heat exchanger 18 returns back to compressor 12.
  • Fig. 1 shows a first flow 20 of heat exchange medium, for example, air, which is driven across heat exchanger 14 by a fan 22. This flow serves to take the heat rejected by refrigerant passing through heat exchanger 14.
  • Fig. 1 also shows another flow 24 of air which is driven by a fan 26 past heat exchanger 18.
  • Flow 24 represents a portion of air in the treated space, and this air is cooled by refrigerant passing through heat exchanger 18.
  • an improved heat exchanger tube configuration is provided which is particularly useful in vapor compression systems which use a transcritical refrigerant, for example, CO 2 .
  • FIG. 2 shows a portion of a transcritical vapor compression system 28 and shows compressor 12, heat exchanger 14 and heat exchanger 18 in positions they occupy in this particular configuration.
  • FIG. 3 is a side schematic of a similar structure, and also shows compressor
  • the flat tube heat exchanger in accordance with the present invention provides enhanced function per space occupied by the heat exchanger tubes, and can therefore be utilized to allow the heat exchanger to take up less space, thereby freeing up such space for use in other capacities.
  • the flat tube heat exchanger of the present invention when implemented as heat exchanger 14, allows for a single heat exchanger to be used as shown in Fig. 2 as compared to several different components of the heat exchanger as shown in Fig. 3.
  • FIGs. 4 - 8 illustrate various embodiments of the present invention in connection with a flat tube heat exchanger as described.
  • Fig. 4 shows a schematic illustration of flat tube 30 which is formed into a substantially serpentine structure as illustrated, and which is positioned to receive air flow 32 such that air flows along the long dimension of flat tube 30 and thereby improves heat exchange efficiency between the medium of air flow 32 and the refrigerant within flat tube 30.
  • Fig. 4 further shows fins 34 which can advantageously be positioned extending from flat tubes 30 or otherwise connected with a flat tube heat exchanger according to the invention, so as to extend further across air flow 32 and enhance heat exchange capacity between the medium and the refrigerant.
  • FIG. 5 shows a single row flat tube heat exchanger configured into a substantially serpentine configuration or structure 36 such that the single flat tube defining the structure is bent in a serpentine manner to define a plurality of portions 37 or flow paths, which are substantially parallel to each other.
  • Fig. 5 shows a single refrigerant inlet 38 and a single refrigerant outlet 40 to handle flow of refrigerant through structure 36.
  • Structure 36 is advantageously positioned to interact with a flow 39 of air as shown, preferably with the narrow edge of flat tube 30 facing into flow 39, and with the longer dimension or width of flat tube 30 being substantially parallel to flow 39.
  • the flat tube heat exchanger in accordance with the present invention is defined by a refrigerant conduit which has a substantially rectangular outer shape and which has an internally-defined flow passage for carrying refrigerant.
  • the outside shape of flat tube 46 also referring to Figs. 9a and b, is substantially rectangular.
  • This substantially rectangular outer shape has a relatively shorter side 47 and a relatively longer side 49, and the substantially shorter side 47 has a length which is preferably between about 0.45 and about 4mm.
  • the relatively longer side 49 or dimension of the rectangular out shape preferably has a length or dimension which is between about 12.7 and about 101.6 mm.
  • the substantially serpentine structure 36 of flat tube heat exchanger in accordance with the present invention defines a series of substantially parallel flow paths.
  • a tube pitch 50 or distance between the tubes of the substantially parallel flow paths, as measured from transverse center to center, is preferably between about 5 and about 50 mm.
  • fins it is preferred to position fins, where possible, to further enhance heat exchange as desired.
  • fins it is preferred that such fins be positioned in a fin density of up to about 20 fins/inch.
  • serpentine substantially flat tube heat exchanger structures 36 can be provided in a plurality of rows 42, 44 so as to treat a flow 39 of air through a first row 42 and then through second row 44.
  • heat exchangers can be provided with up to at least about 20 rows, and will provide excellent results in accordance with the present invention.
  • the internal flow path for refrigerant defined within a flat tube heat exchanger can have a variety of different shapes.
  • Figs. 9a and 9b illustrate two embodiments. In the embodiment of Fig. 9a, a cross section through a flat tube 46 in accordance with the present invention is shown wherein the entire internal space of flat tube 46 is provided for flow of refrigerant.
  • Fig. 9b shows flat tube 46 having flow passages defined as a series of substantially circular flow paths 48, in this case five (5) circular flow paths, which extend in substantially parallel relationship along the length of flat tube 46.
  • Such a heat exchanger provides higher overall heat transfer coefficients owing to higher refrigerant mass fluxes (hence higher CO 2 heat transfer coefficient) and lower air-side pressure drop due to reduced air-side blockage by a flat tube compared to a conventional round tube. Based on the flow cross-sectional area of the flat tube, the overall length of the flat tube could be designed such that the CO 2 pressure drop is below an acceptable limit enabling higher cycle efficiencies for the range of operating conditions.
  • the use of a single circuit could eliminate CO 2 maldistribution, which is inherently present in the case of a heat exchanger (conventional or flat tube) with multiple inlets and outlets.
  • the heat exchanger orientation should be such that the tubes lie in the vertical plane as shown in Fig. 4 and the fins can be provided with slots/louvers. This .would ensure satisfactory condensate drainage from flat tube and fin surfaces, which would otherwise be a limiting factor for use of a flat-tube heat exchanger as an evaporator.
  • the flat tube heat exchanger could have one or multiple ports. Multiple ports help to withstand high operating pressures, an inherent characteristic of a transcritical CO 2 vapor compression refrigeration system, and reduces CO 2 pressure drop which in turn helps to improve thermal performance.
  • the flat tube (single or multi ports) could be easily made out of Copper or Aluminum or other suitable material that can withstand high burst pressures of transcritical CO 2 refrigeration system and could be bent and/or brazed at one or both ends to form one continuous serpentine heat exchanger as shown in the drawings.
  • the fins could be connected mechanically or brazed to the flat surface of the tubes.
  • the tube and/or fin material may be treated (coating, heat etc.) to increase corrosion resistance of such heat exchangers.
  • This invention is especially beneficial for compact commercial refrigeration systems such as bottle coolers etc.
  • heat exchangers use of such heat exchangers is limited by major technical challenges like maldistribution of refrigerant, poor condensate drainage, reduced burst strength, cross-flow arrangement, and high cost and complexity of fabrication including, but not limited to, expensive brazing of multiple tubes connected to manifolds at either ends, brazing of fins to tube surfaces, and low thermal conductivity material of the tubes for ease of brazing etc.
  • Such a heat exchanger is not found to exist for transcritical CO 2 bottle cooler systems wherein minimization of the temperature gradient between hot and cold fluids at the exit of the gas cooler (high-side heat exchanger) is highly critical to maintain peak- efficiency.
  • the single serpentine vertical tube configuration eliminates major technical challenges like maldistribution and condensate drainage which otherwise would limit use of such heat exchangers as evaporators, while still maintaining high CO 2 heat transfer coefficients and reduced CO 2 pressure drop.
  • the heat exchanger combines benefits of flat surfaces, single or multiple ports, single serpentine, multiple rows, high heat transfer coefficients, low cost, suitable materials, corrosion resistance, high burst strength, ease of manufacturing, and reduced air blockage which helps to achieve size, efficiency, cost and reliability constraints of a bottle cooler refrigeration system.
  • the compact characteristic of the flat surface heat exchanger can allow changes to the physical location of the heat exchanger inside the beverage cooler such that the entire footprint of the beverage cooler can be reduced while maintaining or increasing the system efficiency.
  • the high-side heat exchanger can be moved to other locations, thereby creating additional space which can be utilized for other purposes such as air management for the hot or cold surfaces etc.
  • the compact characteristics of such a heat exchanger would also result in reduction in the amount of refrigerant or charge within the refrigeration system and therefore reduce cost which is highly constrained for bottle cooler applications.
  • range of different specifications of such flat tube heat exchangers could be, tube width or major dimension from 12.7mm to 101.6mm; tube height or minor dimension from 0.5mm to 4mm; single or multi-port, circular or non- circular ports, flow hydraulic diameter from 0.1mm to 3mm; tube pitch or transverse center to center distance between tubes from 5mm to 50mm; row pitch or longitudinal center to center distance between tubes from 12.7mm to 50mm; fin density from 0 to 20 fins per inch, single or multiple rows up to 20.
  • a preferred embodiment proposed for the high-side heat exchanger or gas cooler for bottle or beverage cooler applications would have, 25.4mm tube width, 2.0mm tube height, 12 circular ports, 1.0mm port hydraulic diameter, 12.7mm tube pitch, 4 fins per inch, single row heat exchanger.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)

Abstract

Cette invention concerne un système de réfrigération comprenant: un compresseur faisant circuler le réfrigérant le long d'un trajet selon au moins un premier mode du système; un premier échangeur de chaleur sur ledit trajet en aval du compresseur dans le premier mode; un second échangeur de chaleur sur le trajet en amont du compresseur selon le premier mode; et un régulateur de pression ou un dispositif d'expansion sur le trajet en aval du premier échangeur de chaleur et en amont du second échangeur de chaleur selon le premier mode, au moins l'un des deux échangeurs de chaleur étant du type à tubes plats.
EP05856007A 2005-03-18 2005-12-30 Systeme d'echangeur de chaleur Withdrawn EP1864060A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US66395705P 2005-03-18 2005-03-18
PCT/US2005/047527 WO2006101565A1 (fr) 2005-03-18 2005-12-30 Systeme d'echangeur de chaleur

Publications (2)

Publication Number Publication Date
EP1864060A1 true EP1864060A1 (fr) 2007-12-12
EP1864060A4 EP1864060A4 (fr) 2010-09-29

Family

ID=37024107

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05856007A Withdrawn EP1864060A4 (fr) 2005-03-18 2005-12-30 Systeme d'echangeur de chaleur

Country Status (5)

Country Link
US (1) US20080184734A1 (fr)
EP (1) EP1864060A4 (fr)
JP (1) JP2008533427A (fr)
CN (1) CN101142452A (fr)
WO (1) WO2006101565A1 (fr)

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DE102008043920A1 (de) * 2008-11-20 2010-05-27 BSH Bosch und Siemens Hausgeräte GmbH Kondensationstrockner mit einer Wärmepumpe sowie Verfahren zu seinem Betrieb
FR2939187B1 (fr) * 2008-12-01 2013-02-22 Valeo Systemes Thermiques Echangeur de chaleur a spires et dispositif de climatisation comprenant un tel echangeur de chaleur
US20110024083A1 (en) * 2009-07-31 2011-02-03 Steimel John C Heat exchanger
FR2963418B1 (fr) * 2010-07-28 2014-12-26 Muller & Cie Soc Echangeur pour pompe a chaleur
KR102103951B1 (ko) * 2012-07-06 2020-04-24 삼성전자주식회사 냉장고
CN105371687B (zh) * 2015-10-27 2017-07-11 珠海格力电器股份有限公司 换热组件、换热器及制冷系统
CN108072285A (zh) * 2017-12-06 2018-05-25 广东美的制冷设备有限公司 辐射换热器、空调室内机及空调器
TWI809691B (zh) * 2022-01-27 2023-07-21 魏均倚 異形管致冷及散熱系統
CN114777549B (zh) * 2022-06-20 2022-09-20 甘肃蓝科石化高新装备股份有限公司 一种设有管翅桥的气体分区流动的翅片管

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US20080184734A1 (en) 2008-08-07
EP1864060A4 (fr) 2010-09-29
JP2008533427A (ja) 2008-08-21
WO2006101565A1 (fr) 2006-09-28
CN101142452A (zh) 2008-03-12

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