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US20060254757A1 - Intermediate cooler for air-conditioning refrigerant - Google Patents

Intermediate cooler for air-conditioning refrigerant Download PDF

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Publication number
US20060254757A1
US20060254757A1 US11/418,611 US41861106A US2006254757A1 US 20060254757 A1 US20060254757 A1 US 20060254757A1 US 41861106 A US41861106 A US 41861106A US 2006254757 A1 US2006254757 A1 US 2006254757A1
Authority
US
United States
Prior art keywords
heat exchanger
compartment
vessel
tube
refrigerant
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
US11/418,611
Other languages
English (en)
Inventor
Hubertus Kamsma
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.)
Modine Manufacturing Co
Original Assignee
Modine Manufacturing Co
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 Modine Manufacturing Co filed Critical Modine Manufacturing Co
Publication of US20060254757A1 publication Critical patent/US20060254757A1/en
Assigned to MODINE MANUFACTURING COMPANY reassignment MODINE MANUFACTURING COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KAMSMA, HUBERTUS R.
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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
    • F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
    • 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/106—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
    • 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
    • F28F9/005—Other auxiliary members within casings, e.g. internal filling means or sealing means
    • 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
    • F25B2500/18—Optimization, e.g. high integration of refrigeration components
    • 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
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
    • F28F2009/224—Longitudinal partitions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
    • F28F2255/16—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes extruded

Definitions

  • the present invention relates to heat exchangers, and more particularly toward intermediate cooling of refrigerant circulating in an air-conditioning loop.
  • Air-conditioning loops commonly include a refrigerant flowing through a compressor, gas cooler, evaporator (heat exchanger) and expansion valve, where the refrigerant passes through a high pressure side and a low pressure side in which the refrigerant has a different temperature.
  • An intermediate heat exchanger is also disclosed in DE 103 22 028 B4, which is integrated as a coaxial tube in the collecting tube of the evaporator. This is a compact configuration which provides some ease of manufacture.
  • the present invention is directed toward improving upon the prior art to provide an easy to manufacture, compact heat exchanger for high and low pressure sides of an air-conditioning loop which provides efficient heat exchange.
  • an intermediate heat exchanger for refrigerant which passes through a high pressure side and a low pressure side in which the refrigerant has a different temperature circulating in an air conditioning loop.
  • the heat exchanger includes a thin pressure-stable vessel defining at least one longitudinal compartment therein, and a flat multi-chamber tube through which refrigerant on one side flows.
  • the tube extends through the at least one compartment and is spaced from at least two opposing walls of the compartment. Heat exchange ribs roughly fill the compartment between the tube and the two opposing walls, wherein refrigerant on the other side flows through the compartment between the tube and the two opposing walls.
  • At least one of the opposing walls is curved, and the ribs fill the compartment between the curved wall and the flat multi-chamber tube.
  • At least one longitudinal wall divides the vessel into at least two compartments, wherein the. multi-chamber tube extends in the longitudinal direction of the compartments and is substantially straight through at least one compartment.
  • the flat multi-chamber tube has a U-bend between two parallel straight portions, wherein the straight portions separately extend through two parallel compartments separated by the at least one longitudinal wall.
  • the heat exchange ribs are arranged so as to be exposed to essentially no pressure loads.
  • the vessel is substantially cylindrical with closing covers at each end of the cylinder.
  • a plurality of longitudinal walls divide the vessel into a plurality of parallel longitudinal compartments.
  • a flat multi-chamber tube extends through each vessel compartment, with the tubes being arranged in series with one tube configured to input or output the refrigerant, and at least one other tube configured to output or input, respectively, the refrigerant.
  • the one tube has a greater cross-section than the other tubes.
  • the vessel is substantially cylindrical, and the one tube extends substantially along the center plane of the cylindrical vessel.
  • the vessel is substantially cylindrical, and the cross-sectional shape of the compartments is generally rectangular.
  • the chambers in the flat multi-chamber tube have a diameter of about 1.20 mm or less.
  • the length to diameter ratio (L/D) of the vessel is at least 3:1.
  • both the vessel and the multi-chamber tube are extruded.
  • the ribs have walls extending longitudinally through the compartment.
  • FIG. 1 is a longitudinal cross-section through a first embodiment of an intermediate heat exchanger incorporating the present invention
  • FIG. 2 is an axial cross-section through heat exchanger of FIG. 1 ;
  • FIG. 3 is a perspective view of one end of the heat exchanger of FIG. 1 showing inlets and outlets for the refrigerant;
  • FIG. 4 is an axial cross-section through a second embodiment of a heat exchanger incorporating the present invention.
  • FIG. 5 is a longitudinal schematic view of a third embodiment of a heat exchanger incorporating the present invention.
  • FIG. 6 is an axial cross-section through a fourth embodiment of a heat exchanger incorporating the present invention.
  • FIG. 7 is an axial cross-section through a fifth embodiment of a heat exchanger incorporating the present invention.
  • FIG. 8 is an axial cross-section through a sixth embodiment of a heat exchanger incorporating the present invention.
  • FIG. 9 is an axial cross-section through a seventh embodiment of a heat exchanger incorporating the present invention.
  • a vessel 20 is formed as a round tube produced by extrusion.
  • the tube has two longitudinal walls 22 and 24 , which divide the tube into three compartments 26 , 28 , 30 , each of which include a flat extruded multi-chamber tube 34 extending roughly the entire length of the compartments (the multi-chamber tube 34 could also be a soldered or welded tube with an internal insert forming the chambers).
  • each multi-chamber tube 34 has two rows of passages 36 having a diameter of about 1.20 mm or less.
  • each multi-chamber tube 34 is provided with one or more heat-conducting ribs 40 that fills up the cross-section of the corresponding compartmet, preferably as fully as possible, so that the refrigerant flowing there does not flow through large, free cross-sectional spaces and therefore heat exchange with the tubes 34 is enhanced.
  • the refrigerant on the high pressure side flows on the top through the middle connection opening into the flat and larger multi-chamber tube 34 (in the center of the vessel 20 ).
  • the refrigerant then flows downward through that tube, and at the vessel bottom is distributed to the two other smaller multi-chamber tubes 34 , through which the refrigerant flows back up.
  • the refrigerant flows via two outflow openings to an expansion device (not shown), and then, for example, through an evaporator.
  • the refrigerant on the low pressure side flows into a corresponding inflow opening 44 either into the middle compartment 28 (in which case it flows downward through the heat exchange ribs 40 in the middle compartment 28 and then is distributed to the two other compartments to flow up through them), or the refrigerant on the low pressure side is distributed from the inflow opening 44 to all three compartments 26 , 28 , 30 (in which case it flows downward through all three compartments 26 , 28 , 30 and then to the compressor [not shown] in the loop).
  • the tube on the top and bottom has appropriate covers 48 , which complete the vessel 20 .
  • flow channels for the refrigerant on the high pressure side are formed in cover 48 .
  • the above described components may advantageously be made of aluminum, which parts may be assembled and joined by soldering.
  • FIG. 3 shows inflow and outflow of the refrigerant on the high pressure side and low pressure side one embodiment such as described in connection with FIGS. 1-2 above.
  • Reference numbers 44 , 50 , 52 show flow passages of the refrigerant on the low pressure side, with this low pressure refrigerant flowing at 44 into the middle compartment 28 (or flowing out of this compartment there).
  • a connection block 54 includes channels and may be soldered with the other mentioned components, and includes two additional inflow (or outflow) openings or channels 50 , 52 that communicate with the other two compartments 28 , 30 . Openings or channels 60 , 62 , 64 , 66 , 68 are also provided for the refrigerant on the high pressure side, such openings being formed in the upper cover 48 and communicate with the multi-chamber tubes 34 .
  • FIG. 4 illustrates another practical example in which only the middle compartment 28 is occupied by the multi-chamber tube 34 and heat exchange ribs 40 .
  • Refrigerant on the low pressure side flows through the ribs 40 in the middle compartment 28 , and may (or may not) also flow in the two other compartments 26 , 30 .
  • the longitudinal walls 70 can be made significantly thinner than is illustrated by FIG. 4 , since roughly the same pressure is present in the compartments 26 , 28 , 30 ).
  • FIG. 5 schematically shows another embodiment incorporating the present invention, wherein the vessel 20 may have with a somewhat smaller degree of thinness.
  • the multi-chamber tube 34 in this embodiment has a U-shaped bend 74 , whereby inflow and outflow of the refrigerant may both occur on the upper cover 48 (where the reference HP stands for the high pressure side and LP for the low pressure side).
  • the lower cover 48 A is arched and the longitudinal wall 22 ends so that the refrigerant on the low pressure side can flow from compartment 26 back to the other compartment 28 , with the remaining cross-section of both compartments 26 , 28 being filled by heat exchange ribs 40 such as previously described.
  • FIGS. 6 and 7 show embodiments which facilitate insertion of the heat exchange ribs 40 with the multi-chamber tube 34 into the corresponding compartments, where the cross-section of compartments 26 and 30 in vessel 20 is configured with an appropriate shape.
  • the wall thickness of the vessel 20 is partially increased somewhat at reference number 78
  • recesses 80 are included in the wall of vessel 20 .
  • Such embodiments are easy to produce by extrusion.
  • ordinary corrugated ribs can be used as heat exchange ribs 40 , which are wound coil-like around the corresponding multi-chamber tube 34 and then inserted together with the tube into the appropriate compartment 26 , 28 , 30 X.
  • FIG. 8 Perhaps the simplest form of the present invention is shown in FIG. 8 , wherein the multi-chamber tube 34 extends linearly through the vessel 20 along its center longitudinal plane.
  • the semicircular cross-sections of the compartments 26 of vessel 20 created by the multi-chamber tube 34 are filled up with heat-conducting ribs 40 which have a rib height adapted to the round shape of vessel 20 .
  • FIG. 9 illustrates yet another embodiment of an intermediate heat exchanger incorporating the present invention, which embodiment is particularly suitable for manufacture.
  • two longitudinal walls 22 A, 24 A include bent longitudinal edges 84 , preferably having some elasticity, which lie against the inside of the vessel wall.
  • the multi-chamber tube 34 , the heat-conducting ribs 40 and the two longitudinal walls 22 A, 24 A may be advantageously combined into a stack and pushed together into the vessel 20 so that the longitudinal edges 84 abut the vessel wall, whereby perfect solder connections are made possible or supported.
  • the compartment 28 is filled up by heat-conducting ribs 40 that have a uniform rib height and are therefore favorable to manufacture.
  • the suitability for manufacture of intermediate heat exchangers incorporating the present invention can be understood from the description and the drawings. Further, it should be appreciated that the efficiency of heat exchange, and the ability to fit into limited space requirements, are further of heat exchangers according to the present invention because of a very thin configuration of the vessel 20 .
  • the thinness of the vessel 20 expressed by the length L/diameter D ratio (see FIG. 1 ), may be advantageously at least 3:1, although an L/D ration of 6:1 or even thinner is preferred.
  • the vessel 20 over its entire length is designed as a heat exchanger, good results in terms of heat exchange efficiency can be achieved.
  • the vessel 20 and the intermediate heat exchanger have a noticeably slim appearance and are therefore particularly suitable for applications in which narrow spaces are present (according to the present invention, vessels with a length/diameter ratio of at least 3:1 or larger are considered slim vessels).
  • the multi-chamber tubes 34 extend essentially straight through the compartments 26 , 28 , 30 (i.e., it need not be deformed), they may be readily assembled in the compartments together with the heat exchange ribs 40 almost completely filling up the remaining compartment cross-section, thereby providing both easy assembly and good heat exchange efficiency.
  • the round shape of the longitudinal wall of the vessel 20 is able to withstand enormously high pressures, and therefore the heat exchange ribs 40 can be made from a very thin sheet material since it is not exposed to significant pressure stresses.
  • the extrusion process for production of the vessel 20 makes it possible to design cross-section of the internal compartments 26 , 28 , 30 in the otherwise preferably round pressure vessel 20 to be rectangular, and as a result the heat exchange ribs 40 can be very favorably inserted there without significant squeezing and in so doing almost completely fill up the compartment as mentioned.
  • Roughly rectangular or square compartment cross-sections can be advantageously achieved either by partially increasing the wall thickness of the vessel 20 or by including gradations of the otherwise round vessel in the longitudinal direction of the vessel 20 , both of which can be efficiently manufactured by the deformation method of extrusion.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US11/418,611 2005-05-10 2006-05-05 Intermediate cooler for air-conditioning refrigerant Abandoned US20060254757A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005021464A DE102005021464A1 (de) 2005-05-10 2005-05-10 Vorrichtung zur Zwischenkühlung
DEDE102005021464.9 2005-05-10

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US20060254757A1 true US20060254757A1 (en) 2006-11-16

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EP (1) EP1724535B1 (fr)
DE (2) DE102005021464A1 (fr)

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US20110132586A1 (en) * 2009-12-08 2011-06-09 Visteon Global Technologies, Inc. Heat exchanger with tube bundle
US20120199334A1 (en) * 2011-02-04 2012-08-09 Lockheed Martin Corporation Heat exchanger with foam fins
US20140124171A1 (en) * 2011-06-27 2014-05-08 Carrier Corporation Micro-port shell and tube heat exchanger
US9464847B2 (en) 2011-02-04 2016-10-11 Lockheed Martin Corporation Shell-and-tube heat exchangers with foam heat transfer units
US9513059B2 (en) 2011-02-04 2016-12-06 Lockheed Martin Corporation Radial-flow heat exchanger with foam heat exchange fins
US9951997B2 (en) 2011-02-04 2018-04-24 Lockheed Martin Corporation Staged graphite foam heat exchangers

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FR2908871B1 (fr) * 2006-11-21 2008-12-26 Valeo Systemes Thermiques Echangeur de chaleur interne pour circuit de fluide refrigerant
ES2335953B1 (es) * 2007-08-13 2010-10-25 Valeo Termico, S.A. Intercambiador de calor para gases, y su correspondiente procedimiento de fabricacion.
DE102009024202A1 (de) * 2009-06-08 2010-12-09 Andreas Jahn Wärmetauscher für eine Kältemaschine und Verfahren zur Herstellung eines Wärmetauschers
ITMO20090290A1 (it) * 2009-12-11 2011-06-12 Highftech Engineering S R L Scambiatore di calore.
DE102011012577A1 (de) * 2011-02-26 2012-08-30 Volkswagen Ag Wärmeaustauschvorrichtung
DE102012224353A1 (de) * 2012-12-21 2014-06-26 Behr Gmbh & Co. Kg Wärmeübertrager
DE102017216943A1 (de) * 2017-09-25 2019-03-28 BSH Hausgeräte GmbH Kältegerät mit Lagerkammer und Verdampferkammer
EP3819580B1 (fr) * 2019-11-06 2022-08-31 Valeo Autosystemy SP. Z.O.O. Échangeur de chaleur

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Also Published As

Publication number Publication date
DE102005021464A1 (de) 2006-11-16
EP1724535B1 (fr) 2010-09-01
EP1724535A2 (fr) 2006-11-22
DE502006007755D1 (de) 2010-10-14
EP1724535A3 (fr) 2008-07-02

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