EP0730134A2 - Echangeur de chaleur à plaques empilées - Google Patents

Echangeur de chaleur à plaques empilées Download PDF

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Publication number
EP0730134A2
EP0730134A2 EP96107859A EP96107859A EP0730134A2 EP 0730134 A2 EP0730134 A2 EP 0730134A2 EP 96107859 A EP96107859 A EP 96107859A EP 96107859 A EP96107859 A EP 96107859A EP 0730134 A2 EP0730134 A2 EP 0730134A2
Authority
EP
European Patent Office
Prior art keywords
side plate
plate
hole
channels
seal
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.)
Granted
Application number
EP96107859A
Other languages
German (de)
English (en)
Other versions
EP0730134B1 (fr
EP0730134A3 (fr
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/ja
Priority claimed from JP28872590A external-priority patent/JP2741950B2/ja
Priority claimed from JP7287191A external-priority patent/JP2877237B2/ja
Application filed by Matsushita Refrigeration Co filed Critical Matsushita Refrigeration Co
Publication of EP0730134A2 publication Critical patent/EP0730134A2/fr
Publication of EP0730134A3 publication Critical patent/EP0730134A3/fr
Application granted granted Critical
Publication of EP0730134B1 publication Critical patent/EP0730134B1/fr
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 present invention relates to a layer-built heat exchanger for exchanging heat between a first coolant and a second coolant, and is 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. S61-243297).
  • 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 and outlet pipes 6-7 and 8-9 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 first-side plate 2
  • 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 19 in the seal plate 3, and flows out through the hole 19 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 distance from the ends of the channels 11 or 16 to the center of the hole 10 or 18 is long because the channels 11 or 16 of the first-side plate 2 or second-side plate 4 are the same length and the ends of the channels form a line with respect to the hole 10 or 18.
  • the first or second coolant must therefore travel a greater distance before it enters the channels, and coolant flow is impeded by this increased distance.
  • 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.
  • the holes in the end plate 5b must be countersunk so that the inlet/outlet pipes 6, 7, 8 and 9 can be positioned.
  • an object of the present invention is to provide a layer-built heat exchanger for shortening the distance between the inlet/outlet holes and channel ends in the first-side plate and the second-side plate, and thus reducing the flow resistance.
  • a further object is to provide a layer-built heat exchanger wherein there is minimal parallel overlap between the channels of the first-side plate and the second-side plate through the seal plate.
  • a further object is to provide a layer-built heat exchanger wherein there is no error in the assembly order of the first-side plate, seal plate, and the second-side plate.
  • a further object is to provide a layer-built heat exchanger whereby positioning of the inlet/outlet pipes to the end plate is simplified.
  • a layer-built heat exchanger comprises channels in the first- and second-side plates of different lengths such that the ends of the channels form a V-shape with an approximately equal distance between the end of each channel and the hole. Furthermore, the channels of the second-side plate are positioned over the dividers forming the channels of the first-side plate, and the channels of the first-side plate are positioned over the dividers forming the channels of the second-side plate. This prevents deformation of the seal plate between the first-side plate and the second-side plate.
  • a convex member that has a height less than the plate thickness is formed on two different sides of the first-side plate and the second-side plate, and concave portions are formed in the seal plate at a position to mate with the convex members of the first- and second-side plates. Omission of the seal plate during assembly is thus less likely to be forgotten.
  • the diameter of the holes in the first-side plate or the second-side plate is smaller than the diameter of the holes to which the inlet/outlet pipes are inserted in the end plates, thus controlling the depth to which the inlet/outlet pipes can be inserted.
  • inlet/outlet pipes are inserted from one end plate to the other, and a hole is provided at the position of the round holes in the first-side plate, second-side plate, and seal plate to control the depth of inlet/outlet pipe insertion.
  • 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 the 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 the 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.
  • 41 is the end plate comprising plural inlet/outlet members 42
  • 41a is another end plate to seal the coolant
  • 43 is the first-side plate comprising channels 36 formed with dividers 34
  • 44 is the second-side plate comprising channels 37 formed with dividers 35
  • 45 is a seal plate 45.
  • Plural convex members 46 that are shallower than the plate thickness h are formed on two different sides of the first-side plate 43 and the second-side plate 44, and concave portions 47 are formed in the seal plate 45 at a position to mate with the convex members 46 of the first- and second-side plates.
  • first-side plate 43 and the second-side plate 44 mate with the seal plate 45 during assembly, and if the seal plate 45 is forgotten and not inserted during manufacture, a gap is formed between the first-side plate 43 and the second-side plate 44 by the convex members 46, having a height less than the plate thickness h, formed on two different sides of the first- and second-side plates 43 and 44.
  • the mistake can be easily discovered by visual inspection.
  • the holes 48 overlap one another when assembled and positioning during assembly is made easier.
  • the ribbed edges prevent the plates from slipping out of position.
  • the layer-built heat exchanger 51 is an assembly of plural first-side plates 2, seal plates 3, and second-side plates 4 alternately placed one over the other in said order, and the assembled layers are sealed between a first end plate (not shown) and a second end plate 5b, which end plate 5b comprises an inlet pipe 6 and an outlet pipe (not shown).
  • the layers are bonded together by adhesive material or wax so that the fluid can flow through the first-side plate 2 and the second-side plate 4 without leaking.
  • the first coolant flows in through the inlet pipe 6, guided along the holes 10, 22, and 19 and flows through the channels 36 of the first-side plate 2 to the holes 10, 22, and 19 on the opposite side to flow out from the outlet pipe (not shown).
  • the second coolant flows in through the inlet pipe (not shown), guided along the holes 13, 23, and 18 and flows through the channels 37 of the second-side plate 4, and flows out through the holes 13, 23, and 18 on the opposite side to the outlet pipe (not shown).
  • Heat is exchanged between the first and second coolants through the seal plate 3 as the coolants flow through the respective plates.
  • the diameter D of the holes 10 in the plates following the end plate 5b in the assembly i.e., the first-side plate 2 or the second-side plate 4 is made smaller than the outside diameter E of the inlet/outlet pipes 6 and 7, and at the same time, the diameter of the semi-circular member 15 of the first-side plate 2 opposite the inlet/outlet pipes 8 and 9 is made smaller than the diameter of the of the inlet/outlet pipes 8 and 9.
  • the type of plate can be determined by visual inspection after plate assembly to easily determine whether or not the plates are assembled in the correct order.
  • the inlet pipe 61 for the first coolant passes through the end plate 5b, the round holes 10 in the first-side plates 2, the holes 22 in the seal plates 3, and the holes 19 in the second-side plates 4 to the other end plate 5a.
  • a slit hole 62 is formed in the inlet pipe 61 at the position corresponding to the holes 10, 22, and 19.
  • the outlet pipe for the first coolant and the inlet/outlet pipes for the second coolant are similarly formed through each of the plates to the end plate 5a.
  • plural parallel channels 36 extending in a winding manner from a position adjacent one round hole 10 in the first-side plate 32 to a position adjacent the other round hole 10 are formed by plural dividers 36.
  • the length of each channel 36 increases as the distance of the channel 36 from the center of the hole 10 increases, so that the ends of the channels 36 form an approximate V-shape around the center of the round hole 10 with the end of each channel 36 as close as possible to the center of the round hole 10.
  • plural parallel channels 37 winding from a position adjacent one round hole 18 in the second-side plate 33 to a position adjacent the other round hole 18 are formed by plural dividers 35.
  • each channel 37 increases as the distance of the channel 37 from the center of the hole 18 increases, so that the ends of the channels 37 form an approximate V-shape around the center of the round hole 18 with the end of each channel 37 as close as possible to the center of the round hole 18.
  • the average distance between the end of the channels 36 and 37 and the holes 10 and 18 is therefore shortened, improving the flow and distribution of coolant into the channels 36 and 37.
  • 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.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP96107859A 1990-09-28 1991-09-27 Echangeur de chaleur à plaques empilées Expired - Lifetime EP0730134B1 (fr)

Applications Claiming Priority (10)

Application Number Priority Date Filing Date Title
JP260992/90 1990-09-28
JP26099290 1990-09-28
JP26099290A JP2741949B2 (ja) 1990-09-28 1990-09-28 積層型熱交換器
JP288725/90 1990-10-26
JP28872590 1990-10-26
JP28872590A JP2741950B2 (ja) 1990-10-26 1990-10-26 積層式熱交換器
JP7287191 1991-04-05
JP72871/91 1991-04-05
JP7287191A JP2877237B2 (ja) 1991-04-05 1991-04-05 積層式熱交換器
EP91916786A EP0503080B1 (fr) 1990-09-28 1991-09-27 Echangeur de chaleur a structure stratifiee

Related Parent Applications (2)

Application Number Title Priority Date Filing Date
EP91916786A Division EP0503080B1 (fr) 1990-09-28 1991-09-27 Echangeur de chaleur a structure stratifiee
EP91916786.6 Division 1991-09-27

Publications (3)

Publication Number Publication Date
EP0730134A2 true EP0730134A2 (fr) 1996-09-04
EP0730134A3 EP0730134A3 (fr) 1998-01-14
EP0730134B1 EP0730134B1 (fr) 2001-01-03

Family

ID=27301059

Family Applications (4)

Application Number Title Priority Date Filing Date
EP96107859A Expired - Lifetime EP0730134B1 (fr) 1990-09-28 1991-09-27 Echangeur de chaleur à plaques empilées
EP91916786A Expired - Lifetime EP0503080B1 (fr) 1990-09-28 1991-09-27 Echangeur de chaleur a structure stratifiee
EP96107852A Withdrawn EP0730132A3 (fr) 1990-09-28 1991-09-27 Echangeur de chaleur à plaques empilées
EP96107853A Withdrawn EP0730133A3 (fr) 1990-09-28 1991-09-27 Echangeur de chaleur à plaques empilées

Family Applications After (3)

Application Number Title Priority Date Filing Date
EP91916786A Expired - Lifetime EP0503080B1 (fr) 1990-09-28 1991-09-27 Echangeur de chaleur a structure stratifiee
EP96107852A Withdrawn EP0730132A3 (fr) 1990-09-28 1991-09-27 Echangeur de chaleur à plaques empilées
EP96107853A Withdrawn EP0730133A3 (fr) 1990-09-28 1991-09-27 Echangeur de chaleur à plaques empilées

Country Status (3)

Country Link
EP (4) EP0730134B1 (fr)
DE (2) DE69132499T2 (fr)
WO (1) WO1992006343A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2880106A1 (fr) * 2004-12-29 2006-06-30 Framatome Anp Sas Dispositif d'echange de chaleur entre deux fluides comportant des couches de mousse metallique
KR20160129144A (ko) * 2015-04-29 2016-11-09 린나이코리아 주식회사 다열의 판재를 이용한 수로부 구조를 갖는 열교환기 및 그 제조방법

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1278832B1 (it) * 1995-05-25 1997-11-28 Luca Cipriani Piastra per scambiatore di calore a piastre ad alta pressione di esercizio e scambiatore dotato di tali piastre
DE19639114B4 (de) * 1995-08-01 2006-01-05 Behr Gmbh & Co. Kg Wärmeübertrager mit Plattenstapelaufbau
DE19635455B4 (de) * 1995-08-01 2007-02-15 Behr Gmbh & Co. Kg Wärmeübertrager mit Plattenstapelaufbau und Verfahren zu seiner Herstellung
US5911273A (en) * 1995-08-01 1999-06-15 Behr Gmbh & Co. Heat transfer device of a stacked plate construction
DE19528117B4 (de) * 1995-08-01 2004-04-29 Behr Gmbh & Co. Wärmeübertrager mit Plattenstapelaufbau
JPH10170177A (ja) * 1996-08-31 1998-06-26 Behr Gmbh & Co プレートパイル構造を有する熱交換器とその製造方法
DE19707648B4 (de) * 1997-02-26 2007-11-22 Behr Gmbh & Co. Kg Parallelstrom-Wärmeübertrager mit Plattenstapelaufbau
DE19815218B4 (de) * 1998-04-04 2008-02-28 Behr Gmbh & Co. Kg Schichtwärmeübertrager
ES2150395B1 (es) * 1999-04-21 2001-06-01 Cortes Jesus Esteban Sistema intercambiador de calor.
US6893619B1 (en) * 2000-09-13 2005-05-17 Ford Global Technologies, Llc Plate-frame heat exchange reactor with serial cross-flow geometry
DE10134761C2 (de) * 2001-07-12 2003-05-28 Visteon Global Tech Inc Wärmeübertrager, insbesondere zur thermischen Kopplung eines Glykol-Wasser-Kreislaufes und eines Hochdruckkältemittelkreislaufes
DE10328746A1 (de) * 2003-06-25 2005-01-13 Behr Gmbh & Co. Kg Vorrichtung zum mehrstufigen Wärmeaustausch und Verfahren zur Herstellung einer derartigen Vorrichtung
DE10352880A1 (de) 2003-11-10 2005-06-09 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere Ladeluft-/Kühlmittel-Kühler
DE10352881A1 (de) 2003-11-10 2005-06-09 Behr Gmbh & Co. Kg Wärmeübertrager, insbesondere Ladeluft-/Kühlmittel-Kühler
US7637112B2 (en) 2006-12-14 2009-12-29 Uop Llc Heat exchanger design for natural gas liquefaction
EP2154879A1 (fr) 2008-08-13 2010-02-17 Thomson Licensing Détecteur d'images CMOS doté de regroupement câblé sélectionnable
CN102003899B (zh) * 2010-12-01 2012-05-02 杭州沈氏换热器有限公司 一种微通道换热器
DE102010063324A1 (de) * 2010-12-17 2012-06-21 Behr Gmbh & Co. Kg Vorrichtung zur Kühlung von Ladeluft, System zum Konditionieren von Ladeluft und Ansaugmodul für einen Verbrennungsmotor

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61243297A (ja) 1985-04-19 1986-10-29 Matsushita Electric Ind Co Ltd 積層式熱交換器

Family Cites Families (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE229510C (fr) *
FR812049A (fr) * 1935-12-07 1937-04-28 Bergedorfer Eisenwerk Ag Perfectionnements aux échangeurs-récupérateurs de chaleur à plateaux
FR885659A (fr) * 1940-01-15 1943-09-22 Aluminium Plant & Vessel Co Lt Perfectionnements aux échangeurs de chaleur à surface
US2582871A (en) * 1948-07-31 1952-01-15 Pfaudler Co Inc Heat exchanger
GB788185A (en) * 1954-06-28 1957-12-23 Separator Ab Improvements in or relating to plate heat exchangers
FR1345756A (fr) * 1962-11-02 1963-12-13 Alfa Laval Ag échangeur de chaleur
GB1131124A (en) * 1966-02-10 1968-10-23 Serck Radiators Ltd Plate-type heat exchangers
FR1603631A (en) * 1968-12-13 1971-05-10 Liquid distribution in liquid/liquid contact-ing units
JPS4734948Y1 (fr) * 1970-06-18 1972-10-23
FR2184536A1 (en) * 1972-05-19 1973-12-28 Anvar Very low temperature heat exchangers - partic suitable for helium 3 and helium 4
JPS553172U (fr) * 1978-06-22 1980-01-10
JPS55121394A (en) * 1979-03-13 1980-09-18 Teijin Ltd Total heat exchanger
US4503908A (en) * 1979-10-01 1985-03-12 Rockwell International Corporation Internally manifolded unibody plate for a plate/fin-type heat exchanger
JPS57196091A (en) * 1981-05-25 1982-12-01 Toshiba Corp Heat exchanger
GB2145511B (en) * 1983-08-23 1986-09-03 Apv Int Ltd Improved heat transfer apparatus
JPS6066978U (ja) * 1983-10-07 1985-05-13 株式会社日立製作所 積層熱交換器
JPS6155584A (ja) * 1984-08-24 1986-03-20 Matsushita Electric Ind Co Ltd 積層式熱交換器
JPS61122493A (ja) * 1984-11-16 1986-06-10 Hisaka Works Ltd プレ−ト式熱交換器
JPS61122494A (ja) * 1984-11-20 1986-06-10 Ebara Corp プレ−ト式熱交換器
JPS6237694A (ja) * 1985-08-12 1987-02-18 Kobe Steel Ltd 熱交換器
JPS62213688A (ja) * 1986-03-13 1987-09-19 Ishikawajima Harima Heavy Ind Co Ltd プレ−トフイン熱交換器
JPS6330776U (fr) * 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 (ja) * 1988-07-29 1995-04-10 松下冷機株式会社 積層式熱交換器
JPH0363496A (ja) * 1989-07-28 1991-03-19 Matsushita Refrig Co Ltd 積層式熱交換器

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61243297A (ja) 1985-04-19 1986-10-29 Matsushita Electric Ind Co Ltd 積層式熱交換器

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2880106A1 (fr) * 2004-12-29 2006-06-30 Framatome Anp Sas Dispositif d'echange de chaleur entre deux fluides comportant des couches de mousse metallique
WO2006072686A1 (fr) * 2004-12-29 2006-07-13 Areva Np Dispositif d'echange de chaleur entre deux fluides comportant des couches de mousse metallique
KR20160129144A (ko) * 2015-04-29 2016-11-09 린나이코리아 주식회사 다열의 판재를 이용한 수로부 구조를 갖는 열교환기 및 그 제조방법

Also Published As

Publication number Publication date
DE69125819T2 (de) 1997-12-11
DE69132499D1 (de) 2001-02-08
EP0503080A1 (fr) 1992-09-16
EP0730133A2 (fr) 1996-09-04
EP0503080A4 (en) 1994-06-08
EP0730132A3 (fr) 1998-01-14
EP0503080B1 (fr) 1997-04-23
EP0730134B1 (fr) 2001-01-03
EP0730132A2 (fr) 1996-09-04
WO1992006343A1 (fr) 1992-04-16
DE69125819D1 (de) 1997-05-28
EP0730133A3 (fr) 1998-01-14
EP0730134A3 (fr) 1998-01-14
DE69132499T2 (de) 2001-04-19

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