EP0503080B1 - Laminated heat exchanger - Google Patents

Laminated heat exchanger Download PDF

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Publication number
EP0503080B1
EP0503080B1 EP91916786A EP91916786A EP0503080B1 EP 0503080 B1 EP0503080 B1 EP 0503080B1 EP 91916786 A EP91916786 A EP 91916786A EP 91916786 A EP91916786 A EP 91916786A EP 0503080 B1 EP0503080 B1 EP 0503080B1
Authority
EP
European Patent Office
Prior art keywords
side plate
channels
plate
plates
hole
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.)
Expired - Lifetime
Application number
EP91916786A
Other languages
German (de)
French (fr)
Other versions
EP0503080A1 (en
EP0503080A4 (en
Inventor
Tsuyoshi Matsunaga
Kenji Fujino
Takashi Sugahara
Hiroaki Kan
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.)
Panasonic Holdings Corp
Original Assignee
Matsushita Refrigeration 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
Priority claimed from JP26099290A external-priority patent/JP2741949B2/en
Priority claimed from JP28872590A external-priority patent/JP2741950B2/en
Priority claimed from JP7287191A external-priority patent/JP2877237B2/en
Priority to EP96107859A priority Critical patent/EP0730134B1/en
Priority to EP96107852A priority patent/EP0730132A3/en
Application filed by Matsushita Refrigeration Co filed Critical Matsushita Refrigeration Co
Priority to EP96107853A priority patent/EP0730133A3/en
Publication of EP0503080A1 publication Critical patent/EP0503080A1/en
Publication of EP0503080A4 publication Critical patent/EP0503080A4/en
Publication of EP0503080B1 publication Critical patent/EP0503080B1/en
Application granted granted Critical
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • F28D9/0075—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements the plates having openings therein for circulation of the heat-exchange medium from one conduit to another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2280/00—Mounting arrangements; Arrangements for facilitating assembling or disassembling of heat exchanger parts
    • F28F2280/04—Means for preventing wrong assembling of parts

Definitions

  • the invention relates to a layer-built heat exchanger comprising a first-side plate having plural channels for coolant flow formed by dividers on a flat rectangular panel, a hole at one end of the channels, and a hole on a diagonal line to the first hole on a different side of the plate, a second-side plate having plural channels for coolant flow formed by dividers on a flat rectangular panel, a hole formed separately at one end of the channels continuously to the corresponding hole in the first-side plate, and a hole on a diagonal line to the first hole on a different side of the plate continuously to the corresponding hole in the first-side plate, and a seal plate between the first-side plate and the second-side plate.
  • a heat exchanger is known from JP-A-61-243297.
  • the present invention is particularly used in a radiator for coolant oil in machine tools or in an air conditioner.
  • a conventional layer-built heat exchanger is described below with reference to Figs. 1 - 5 (Japanese Patent Laid-Open No. 61-243297).
  • the conventional layer-built heat exchanger 1 combines plural first-side plates 2, seal plates 3, and second-side plates 4 between end plates 5a and 5b.
  • the inlet pipes 6,8 and outlet pipes 7,9 for the first and second coolants, respectively, are connected to the one end plate 5b.
  • the first-side plate 2 has a rectangular shape with a pair of round holes 10, provided offset from the center at each end of the plate, for the first coolant flow.
  • a series of parallel and winding channels 11 are formed by dividers 12 for conducting the coolant from a position near the round hole 10 at one end of the first-side plate 2 to a position near the round hole 10 at the other end.
  • Holes 13 for the flow of the second coolant are also formed on a diagonal line on the first-side plate 2 on the sides different from those on which the round holes 10 are formed.
  • Each hole 13 has a rectangular shaped area 14 and a semi-circular shaped area 15 at the middle of the long side of the rectangular shaped area 14.
  • the second-side plate 4 has a similar rectangular shape with a series of parallel and winding channels 16 formed by dividers 17 to conduct the coolant between the two round holes 18.
  • These round holes 18 are formed correspondingly to the holes 13 in the first-side plate 2 with part of each hole 18 tracing the same arc as the semi-circular shaped area 15 of the corresponding hole 13 in the first-side plate 2.
  • Holes 19 are also provided correspondingly to the round holes 10 in the first-side plate 2.
  • Each hole 19 also consists of a rectangular shaped area 20 and a semi-circular shaped area 21 at the middle of the long side of the rectangular shaped area 20 such that part of each semi-circular shaped area 21 traces the same arc as the corresponding round hole 10 in the first-side plate 2.
  • the seal plate-3 has holes 22 and 23 similarly shaped to the corresponding holes 13 and 19 in the first- and second-side plates 2 and 4, respectively.
  • the length of the rectangular shaped area 14 and 20 of the holes 13 and 19 is made long enough to cover the ends of each of the channels 11 and 16, respectively.
  • first-side plate 2 seal plate 3
  • second-side plate 4 seal plate 3
  • first-side plate 2 seal plate 3
  • seal plate 3 a seal plate
  • the first coolant flows in through the inlet pipe 6, is diffused to the channels 11 of the first-side plate 2 in the rectangular shaped area of the hole 22 in the seal plate 3, and flows through the channels 11 to the hole 22 on the opposite side to flow out from the outlet pipe 7.
  • the second coolant flows in through the inlet pipe 8 is diffused to the channels 16 of the second-side plate 4 in the rectangular shaped area of the hole 23 in the seal plate 3, and flows out through the hole 23 on the opposite side to the outlet pipe 8.
  • Heat is exchanged between the first and second coolants through the seal plate 3, which is made from a material with good thermal conductivity for greater heat exchange efficiency.
  • the seal plate 3 When there is a pressure difference between the first and second coolants, the seal plate 3 tends to become deformed where the channels 11 of the first-side plate 2 and the channels 16 of second-side plate 4 are positioned one over the other through the seal plate 3 because the seal plate 3 is the only member separating the channels 11 and 16 of the first- and second-side plates 2 and 4. This deformation also interferes with the coolant flow. It is therefore necessary to increase the thickness H of the seal plate 3 to prevent this deformation. The overall size and cost of the heat exchanger therefore increase.
  • a layer-built heat exchanger as defined in the preamble of the patent claim is characterized by the dividers of the channels in the second-side plate being positioned opposite the channels in the first-side plate, and the dividers of the first-side plate being positioned opposite the channels in the second-side plate, with the seal plate in between.
  • the layer-built heat exchanger 31 is an assembly of plural first-side plates 32, seal plates 3, and second-side plates 33 assembled in alternating layers and sealed between a first end plate 5a and a second end plate 5b, which comprises inlet/outlet pipes 6 and 8, so that the fluid can flow through the first-side plate 32 and the second-side plate 33 without leaking.
  • the first coolant flowing in from the inlet pipe 6 flows into the plural channels 36, divided by dividers 34, in the first-side plate 32, and flows out from the outlet pipe 7.
  • the second coolant flowing in from the inlet pipe flows into the plural channels 37, divided by dividers 35, in the second-side plate 33, and flows out from the outlet pipe (not shown). Heat is exchanged through the seal plate 3 between the two different fluids flowing through the upper and lower plates.
  • the channels 37 of the second-side plate 33 are formed over the dividers 34 of the first-side plate 32, and the channels 36 of the first-side plate 32 are formed over the dividers 35 of the second-side plate 33, two seal plates 3 and the divider 34 of one second-side plate 33 or the divider 35 of one first-side plate 32 are positioned between any two channels 36 or channels 37.
  • the thickness of the solid material located between the channels 36 or 37 becomes great, so as to prevent deformation of the seal plate 3 even when there is a high differential pressure between the first and second coolants. Thus, the coolant flow can be maintained.
  • the channels 37 of the second-side plate 33 are formed over the dividers 34 of the first-side plate 32, and the channels 36 of the first-side plate 32 are formed over the dividers 35 of the second-side plate 33, two seal plates 3 and one second-side plate 33 divider 34 or first-side plate 32 divider 35 are positioned between any two channels 37 or channels 36.
  • the greater total seal plate 3 thickness between the channels 37 or 36 therefore prevents deformation of the seal plate 3 even when there is a high differential pressure between the first and second coolants, and the coolant flow can thus be maintained.
  • a layer-built heat exchanger is suited to exchanging heat between the first and second coolants of an air conditioner. It is also suited for exchanging heat from a working oil in machine tools and other machinery by circulation with another coolant such as water.

Abstract

In a laminated heat exchanger wherein partitions are provided in a plate (32) on a primary side and a plate (33) on a secondary side to form channels therein, and a plurality of the plates (32) on the primary side and the plates (33) on the secondary side are laminated one upon another with respective seal plates (3) therebetween, each of the partitions (35) of the plates (33) on the secondary side are located at positions opposed to each of the channels (11) of the plates (32) on the primary side and each of the partitions (34) of the plates (32) of the primary side are located at positions opposed to each of the channels (17) of the plates (33) on the secondary side, thereby preventing the seal plates (3) from being deformed even if pressure of the coolant flowing through the channels becomes nonuniform. Furthermore, sides of the plates (32) on the primary side, the plates (33) on the secondary side and the seal plates (3) are formed into shapes different from one another, thereby making it easy to identify falling-off of a plate.

Description

  • The invention relates to a layer-built heat exchanger comprising a first-side plate having plural channels for coolant flow formed by dividers on a flat rectangular panel, a hole at one end of the channels, and a hole on a diagonal line to the first hole on a different side of the plate, a second-side plate having plural channels for coolant flow formed by dividers on a flat rectangular panel, a hole formed separately at one end of the channels continuously to the corresponding hole in the first-side plate, and a hole on a diagonal line to the first hole on a different side of the plate continuously to the corresponding hole in the first-side plate, and a seal plate between the first-side plate and the second-side plate. Such a heat exchanger is known from JP-A-61-243297.
  • The present invention is particularly used in a radiator for coolant oil in machine tools or in an air conditioner.
  • Demand has risen for layer-built heat exchangers capable of using chlorofluorocarbons (CFC) and water and oil coolants in combination as first and second coolants for exchanging heat between CFC and CFC, CFC and water, water and water, or oil and water. A conventional layer-built heat exchanger is described below with reference to Figs. 1 - 5 (Japanese Patent Laid-Open No. 61-243297).
  • As shown in the figures, the conventional layer-built heat exchanger 1 combines plural first-side plates 2, seal plates 3, and second-side plates 4 between end plates 5a and 5b. The inlet pipes 6,8 and outlet pipes 7,9 for the first and second coolants, respectively, are connected to the one end plate 5b.
  • The first-side plate 2 has a rectangular shape with a pair of round holes 10, provided offset from the center at each end of the plate, for the first coolant flow. A series of parallel and winding channels 11 are formed by dividers 12 for conducting the coolant from a position near the round hole 10 at one end of the first-side plate 2 to a position near the round hole 10 at the other end.
  • Holes 13 for the flow of the second coolant are also formed on a diagonal line on the first-side plate 2 on the sides different from those on which the round holes 10 are formed. Each hole 13 has a rectangular shaped area 14 and a semi-circular shaped area 15 at the middle of the long side of the rectangular shaped area 14.
  • The second-side plate 4 has a similar rectangular shape with a series of parallel and winding channels 16 formed by dividers 17 to conduct the coolant between the two round holes 18. These round holes 18 are formed correspondingly to the holes 13 in the first-side plate 2 with part of each hole 18 tracing the same arc as the semi-circular shaped area 15 of the corresponding hole 13 in the first-side plate 2. Holes 19 are also provided correspondingly to the round holes 10 in the first-side plate 2. Each hole 19 also consists of a rectangular shaped area 20 and a semi-circular shaped area 21 at the middle of the long side of the rectangular shaped area 20 such that part of each semi-circular shaped area 21 traces the same arc as the corresponding round hole 10 in the first-side plate 2.
  • The seal plate-3 has holes 22 and 23 similarly shaped to the corresponding holes 13 and 19 in the first- and second- side plates 2 and 4, respectively. The length of the rectangular shaped area 14 and 20 of the holes 13 and 19 is made long enough to cover the ends of each of the channels 11 and 16, respectively.
  • The plates are then assembled in successive layers in the order of first-side plate 2, seal plate 3, second-side plate 4, seal plate 3, first-side plate 2, seal plate 3, ..... as shown in Fig. 5, and are sealed between the seal end plate 5a on one end and the end plate 5b provided with the first and second coolant inlet pipes 6,8 and outlet pipes 7,9.
  • With this construction the first coolant flows in through the inlet pipe 6, is diffused to the channels 11 of the first-side plate 2 in the rectangular shaped area of the hole 22 in the seal plate 3, and flows through the channels 11 to the hole 22 on the opposite side to flow out from the outlet pipe 7. Similarly, the second coolant flows in through the inlet pipe 8, is diffused to the channels 16 of the second-side plate 4 in the rectangular shaped area of the hole 23 in the seal plate 3, and flows out through the hole 23 on the opposite side to the outlet pipe 8.
  • Heat is exchanged between the first and second coolants through the seal plate 3, which is made from a material with good thermal conductivity for greater heat exchange efficiency.
  • When there is a pressure difference between the first and second coolants, the seal plate 3 tends to become deformed where the channels 11 of the first-side plate 2 and the channels 16 of second-side plate 4 are positioned one over the other through the seal plate 3 because the seal plate 3 is the only member separating the channels 11 and 16 of the first- and second- side plates 2 and 4. This deformation also interferes with the coolant flow. It is therefore necessary to increase the thickness H of the seal plate 3 to prevent this deformation. The overall size and cost of the heat exchanger therefore increase.
  • It is an object of the present invention to provide a layer-built heat exchanger of the kind as defined above which does not have the drawback of deformation of the seal plate under pressure of the coolants in the channels of the side plates.
  • According to the invention, a layer-built heat exchanger as defined in the preamble of the patent claim is characterized by the dividers of the channels in the second-side plate being positioned opposite the channels in the first-side plate, and the dividers of the first-side plate being positioned opposite the channels in the second-side plate, with the seal plate in between.
    • Fig. 1 is an oblique view of a conventional layer-built heat exchanger,
    • Fig. 2 is a plan view of the first-side plate in Fig. 1,
    • Fig. 3 is a plan view of the seal plate in Fig. 1,
    • Fig. 4 is a plan view of the second-side plate in Fig. 1,
    • Fig. 5 is a cross sectional view of line V-V in Fig. 1,
    • Fig. 6 is a cross sectional view corresponding to Fig. 5 for a layer-built heat exchanger according to an embodiment of the present invention,
    • Fig. 7 is a plan view of the first-side plate in Fig. 6,
    • Fig. 8 is a plan view of the seal plate in Fig. 6,
    • Fig. 9 is a plan view of the second-side plate in Fig. 6.
  • A preferred embodiment of the present invention will now be described below with reference to the accompanying Figs. 6 - 9. It is to be noted that like parts in the preferred embodiments and the prior art described above are referred to by like reference numbers, and further description of said like parts is omitted hereinbelow.
  • As shown in the figures, the layer-built heat exchanger 31 according to the present invention is an assembly of plural first-side plates 32, seal plates 3, and second-side plates 33 assembled in alternating layers and sealed between a first end plate 5a and a second end plate 5b, which comprises inlet/ outlet pipes 6 and 8, so that the fluid can flow through the first-side plate 32 and the second-side plate 33 without leaking.
  • The first coolant flowing in from the inlet pipe 6 flows into the plural channels 36, divided by dividers 34, in the first-side plate 32, and flows out from the outlet pipe 7. Similarly, the second coolant flowing in from the inlet pipe (not shown) flows into the plural channels 37, divided by dividers 35, in the second-side plate 33, and flows out from the outlet pipe (not shown). Heat is exchanged through the seal plate 3 between the two different fluids flowing through the upper and lower plates.
  • Because the channels 37 of the second-side plate 33 are formed over the dividers 34 of the first-side plate 32, and the channels 36 of the first-side plate 32 are formed over the dividers 35 of the second-side plate 33, two seal plates 3 and the divider 34 of one second-side plate 33 or the divider 35 of one first-side plate 32 are positioned between any two channels 36 or channels 37. The thickness of the solid material located between the channels 36 or 37 becomes great, so as to prevent deformation of the seal plate 3 even when there is a high differential pressure between the first and second coolants. Thus, the coolant flow can be maintained.
  • Because the channels 37 of the second-side plate 33 are formed over the dividers 34 of the first-side plate 32, and the channels 36 of the first-side plate 32 are formed over the dividers 35 of the second-side plate 33, two seal plates 3 and one second-side plate 33 divider 34 or first-side plate 32 divider 35 are positioned between any two channels 37 or channels 36. The greater total seal plate 3 thickness between the channels 37 or 36 therefore prevents deformation of the seal plate 3 even when there is a high differential pressure between the first and second coolants, and the coolant flow can thus be maintained.
  • A layer-built heat exchanger according to the present invention is suited to exchanging heat between the first and second coolants of an air conditioner. It is also suited for exchanging heat from a working oil in machine tools and other machinery by circulation with another coolant such as water.

Claims (1)

  1. A layer-built heat exchanger (31) comprising: a first-side plate (32) having plural channels (36) for coolant flow formed by dividers (34) on a flat rectangular panel, a hole (10) at one end of the channels (36), and a hole (13) on a diagonal line to the first hole (10) on a different side of the plate; a second-side plate (33) having plural channels (37) for coolant flow formed by dividers (35) on a flat rectangular panel, a hole (19) formed separately at one end of the channels (37) continuously to the corresponding hole (10) in the first-side plate (32), and a hole (18) on a diagonal line to the first hole (19) on a different side of the plate continuously to the corresponding hole (13) in the first-side plate (32); and a seal plate (3) between the first-side plate (32) and the second-side plate (33); characterized by the dividers (35) of the channels (37) in the second-side plate (33) being positioned opposite the channels (36) in the first-side plate (32), and the dividers (34) of the first-side plate (32) being positioned opposite the channels (37) in the second-side plate (33), with the seal plate (3) in between.
EP91916786A 1990-09-28 1991-09-27 Laminated heat exchanger Expired - Lifetime EP0503080B1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP96107853A EP0730133A3 (en) 1990-09-28 1991-09-27 Layer-built heat exchanger
EP96107859A EP0730134B1 (en) 1990-09-28 1991-09-27 Layer-built heat exchanger
EP96107852A EP0730132A3 (en) 1990-09-28 1991-09-27 Layer-built heat exchanger

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
JP26099290A JP2741949B2 (en) 1990-09-28 1990-09-28 Stacked heat exchanger
JP260992/90 1990-09-28
JP288725/90 1990-10-26
JP28872590A JP2741950B2 (en) 1990-10-26 1990-10-26 Stacked heat exchanger
JP72871/91 1991-04-05
JP7287191A JP2877237B2 (en) 1991-04-05 1991-04-05 Stacked heat exchanger
PCT/JP1991/001292 WO1992006343A1 (en) 1990-09-28 1991-09-27 Laminated heat exchanger

Related Child Applications (6)

Application Number Title Priority Date Filing Date
EP96107859A Division EP0730134B1 (en) 1990-09-28 1991-09-27 Layer-built heat exchanger
EP96107852A Division EP0730132A3 (en) 1990-09-28 1991-09-27 Layer-built heat exchanger
EP96107853A Division EP0730133A3 (en) 1990-09-28 1991-09-27 Layer-built heat exchanger
EP96107859.9 Division-Into 1996-05-17
EP96107853.2 Division-Into 1996-05-17
EP96107852.4 Division-Into 1996-05-17

Publications (3)

Publication Number Publication Date
EP0503080A1 EP0503080A1 (en) 1992-09-16
EP0503080A4 EP0503080A4 (en) 1994-06-08
EP0503080B1 true EP0503080B1 (en) 1997-04-23

Family

ID=27301059

Family Applications (4)

Application Number Title Priority Date Filing Date
EP96107859A Expired - Lifetime EP0730134B1 (en) 1990-09-28 1991-09-27 Layer-built heat exchanger
EP91916786A Expired - Lifetime EP0503080B1 (en) 1990-09-28 1991-09-27 Laminated heat exchanger
EP96107852A Withdrawn EP0730132A3 (en) 1990-09-28 1991-09-27 Layer-built heat exchanger
EP96107853A Withdrawn EP0730133A3 (en) 1990-09-28 1991-09-27 Layer-built heat exchanger

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP96107859A Expired - Lifetime EP0730134B1 (en) 1990-09-28 1991-09-27 Layer-built heat exchanger

Family Applications After (2)

Application Number Title Priority Date Filing Date
EP96107852A Withdrawn EP0730132A3 (en) 1990-09-28 1991-09-27 Layer-built heat exchanger
EP96107853A Withdrawn EP0730133A3 (en) 1990-09-28 1991-09-27 Layer-built heat exchanger

Country Status (3)

Country Link
EP (4) EP0730134B1 (en)
DE (2) DE69125819T2 (en)
WO (1) WO1992006343A1 (en)

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US7637112B2 (en) 2006-12-14 2009-12-29 Uop Llc Heat exchanger design for natural gas liquefaction
US7717165B2 (en) 2003-11-10 2010-05-18 Behr Gmbh & Co. Kg Heat exchanger, especially charge-air/coolant radiator
US7721795B2 (en) 2003-11-10 2010-05-25 Behr Gmbh & Co. Kg Heat exchanger, especially charge-air/coolant cooler

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JPH10170177A (en) * 1996-08-31 1998-06-26 Behr Gmbh & Co Heat exchanger having plate pile construction and method for producing the same
DE19707648B4 (en) * 1997-02-26 2007-11-22 Behr Gmbh & Co. Kg Parallel flow heat exchanger with plate stack construction
ES2150395B1 (en) * 1999-04-21 2001-06-01 Cortes Jesus Esteban HEAT EXCHANGER SYSTEM.
US6893619B1 (en) * 2000-09-13 2005-05-17 Ford Global Technologies, Llc Plate-frame heat exchange reactor with serial cross-flow geometry
DE10134761C2 (en) * 2001-07-12 2003-05-28 Visteon Global Tech Inc Heat exchanger, in particular for the thermal coupling of a glycol-water circuit and a high pressure refrigerant circuit
DE10328746A1 (en) * 2003-06-25 2005-01-13 Behr Gmbh & Co. Kg Multi-stage heat exchange apparatus and method of making such apparatus
FR2880106B1 (en) * 2004-12-29 2007-06-01 Framatome Anp Sas DEVICE FOR EXCHANGING HEAT BETWEEN TWO FLUIDS COMPRISING METAL FOAM LAYERS
EP2154879A1 (en) 2008-08-13 2010-02-17 Thomson Licensing CMOS image sensor with selectable hard-wired binning
CN102003899B (en) * 2010-12-01 2012-05-02 杭州沈氏换热器有限公司 Microchannel heat exchanger
DE102010063324A1 (en) 2010-12-17 2012-06-21 Behr Gmbh & Co. Kg Device for cooling charge air, system for conditioning charge air and intake module for an internal combustion engine
KR101719545B1 (en) * 2015-04-29 2017-03-27 린나이코리아 주식회사 Heat Exchanger with Watercourse Part Structure Using Multifid Plate and the Method of Manufacturing Thereof

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GB2145511B (en) * 1983-08-23 1986-09-03 Apv Int Ltd Improved heat transfer apparatus
JPS6066978U (en) * 1983-10-07 1985-05-13 株式会社日立製作所 laminated heat exchanger
JPS6155584A (en) * 1984-08-24 1986-03-20 Matsushita Electric Ind Co Ltd Laminated heat exchanger
JPS61122493A (en) * 1984-11-16 1986-06-10 Hisaka Works Ltd Plate type heat exchanger
JPS61122494A (en) * 1984-11-20 1986-06-10 Ebara Corp Plate type heat exchanger
JPS61243297A (en) 1985-04-19 1986-10-29 Matsushita Electric Ind Co Ltd Lamination type heat exchanger
JPS6237694A (en) * 1985-08-12 1987-02-18 Kobe Steel Ltd Heat exchanger
JPS62213688A (en) * 1986-03-13 1987-09-19 Ishikawajima Harima Heavy Ind Co Ltd Plate fin heat exchanger
JPS6330776U (en) * 1986-08-13 1988-02-29
JPS6414595A (en) * 1987-07-03 1989-01-18 Matsushita Refrigeration Lamination type heat exchanger
US4815534A (en) * 1987-09-21 1989-03-28 Itt Standard, Itt Corporation Plate type heat exchanger
JPH0731020B2 (en) * 1988-07-29 1995-04-10 松下冷機株式会社 Stacked heat exchanger
JPH0363496A (en) * 1989-07-28 1991-03-19 Matsushita Refrig Co Ltd Layer type heat exchanger

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19815218B4 (en) * 1998-04-04 2008-02-28 Behr Gmbh & Co. Kg Bed heat exchanger
US7717165B2 (en) 2003-11-10 2010-05-18 Behr Gmbh & Co. Kg Heat exchanger, especially charge-air/coolant radiator
US7721795B2 (en) 2003-11-10 2010-05-25 Behr Gmbh & Co. Kg Heat exchanger, especially charge-air/coolant cooler
US7637112B2 (en) 2006-12-14 2009-12-29 Uop Llc Heat exchanger design for natural gas liquefaction

Also Published As

Publication number Publication date
EP0503080A1 (en) 1992-09-16
EP0503080A4 (en) 1994-06-08
DE69125819T2 (en) 1997-12-11
EP0730134B1 (en) 2001-01-03
DE69132499T2 (en) 2001-04-19
EP0730134A2 (en) 1996-09-04
EP0730133A2 (en) 1996-09-04
EP0730133A3 (en) 1998-01-14
EP0730134A3 (en) 1998-01-14
EP0730132A2 (en) 1996-09-04
DE69132499D1 (en) 2001-02-08
DE69125819D1 (en) 1997-05-28
EP0730132A3 (en) 1998-01-14
WO1992006343A1 (en) 1992-04-16

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