WO1983001998A1 - Heat exchanger plate - Google Patents

Heat exchanger plate Download PDF

Info

Publication number
WO1983001998A1
WO1983001998A1 PCT/SE1982/000393 SE8200393W WO8301998A1 WO 1983001998 A1 WO1983001998 A1 WO 1983001998A1 SE 8200393 W SE8200393 W SE 8200393W WO 8301998 A1 WO8301998 A1 WO 8301998A1
Authority
WO
WIPO (PCT)
Prior art keywords
plate
recessed parts
passages
heat exchanger
supporting points
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.)
Ceased
Application number
PCT/SE1982/000393
Other languages
French (fr)
Inventor
Ab Alfa-Laval
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.)
Alfa Laval AB
Original Assignee
Alfa Laval AB
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 Alfa Laval AB filed Critical Alfa Laval AB
Priority to DE8282903492T priority Critical patent/DE3262352D1/en
Priority to AT82903492T priority patent/ATE11822T1/en
Publication of WO1983001998A1 publication Critical patent/WO1983001998A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F28D9/0031—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 paired plates touching each other
    • F28D9/0037—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 paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/355—Heat exchange having separate flow passage for two distinct fluids
    • Y10S165/356—Plural plates forming a stack providing flow passages therein
    • Y10S165/393—Plural plates forming a stack providing flow passages therein including additional element between heat exchange plates
    • Y10S165/394—Corrugated heat exchange plate

Definitions

  • This invention relates to a plate for a plate heat exchanger provided with a corrugation pattern of ridges and grooves arranged to rest intersectingly against the corrugation pattern of an adjacent plate such that a great number of supporting points are formed.
  • the function of the supporting points partly is to absorb compres sive forces and partly to generate turbulence or increased convection, usually followed by increased pressure drop.
  • the above mentioned limitation is a drawback since it is sometimes desirable to be able to bring about asymmetrical passages, i.e. to change the flow characteristics of the passages for the two media independently of each other, for instance when having the same type of medium in liquid state and the same allowed pressure drop and essentially the same viscosity and when the flows of the media are unequal in size, i.e. when the task of the heat exchange is asymmetrical.
  • the heat exchanger in this example must be dimensioned for that medium that has the largest flow such that desired pressure drop is achieved in the passages through which this medium passes. Due to this, fact the passages for the other medium, which have the same capacity, will be over-dimensioned for the actual flow.
  • the object of this invention is to bring about a heat exchanger plate making it possible to adapt the flow characteristics of the passages to mutual flows of unequal size of the two heat exchanging media under essential retention of area enlarging effect of the corrugation.
  • each heat exchanging passage shall, if possible, have flow characteristics adapted to the medium flow passing through the passage.
  • Figs. 1 and 2 show a section and a plan view respectively of a fragment of a series of heat exchanger plates according to the invention and Figs. 3-6 show corresponding views of other embodiments of the invention.
  • Fig. 1 shows fragments of three identical plates 1, of which the intermediate one is turned 180° around its longitudinal axis in order to bring about a mutual intersecting corrugation pattern, which forms supporting points 2, in which the plates rest against each other.
  • the grooves 3 are running uninterruptedly, while the ridges 4 are provided with recesses 5 approximately positioned flush with the central plane of the plate.
  • the recesses 5 are arranged in line with each other.
  • the recesses 5 are positioned on such places where corrugation ridges turned to each other inter sect each other, whereby the number of supporting points are reduced in the passages 7.
  • every third supporting point is eliminated. Due to this fact a substantial reduction of the pressure drop is achieved in every second heat exchanging passage.
  • Figs. 3 and 4 plates 11 are shown that are arranged in the same way as are the plates 1 in Figs. 1 and 2 but differ from those by being provided with deeper recesses 15, the depth of which corresponds to the whole embossing depth of the plates. Due to this fact the recesses 15 form continuous resting lines, which bring about a division of the passages 18 into several parallel part passages. Such a division is advantageous in order to prevent flow instability, unbalanced distribution or undesirable flow distribu tion, which under certain circumstances particularly in connection with evaporation or condensation has a tendency to appear, since the width of the heat exchanging passage is too large in relation to its thickness and length.
  • the division into part passages has also that advantage that the flow speed in the part passages can be influenced to Increase or to be reduced and generally for guaranteeing a flow, for Instance in condensate outlets or exhaust gas channels in a condensor.
  • the tightness over the resting lines can be secured for Instance by glueing, soldering or welding or by means of gaskets.
  • restrictions of the flow which In a way known of those skilled in the art, can be brought about by means of some suitable form of area restriction, as small inlet and outlet openings or particular restriction means put into suitable places in the passages.
  • restriction as to evaporators of different types and boilers are suitably placed in the inlet of each part passage and as to condensors in the outlets of non-condensable gases and/or condensate.
  • Figs. 5 and 6 disclosed embodiment two plates 11 according to Fig. 3 have been combined with an intermediate conventio nal plate 20 without recesses. Due to that fact has been formed a passage 27 with reduced number of supporting points 22, and a passage 28 with retained number of supporting points but without longitudinal resting lines.
  • the recesses can have any arbitrary placement, which in each particular case can appear to be suitable of resistance reasons or flow-technical reasons. They can for instance be arranged in rows across or obliquely against the longitudinal direction of the plate or in interrupted rows in someone of these directions or not at all in line.

Landscapes

  • 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)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Power Steering Mechanism (AREA)
  • Thermotherapy And Cooling Therapy Devices (AREA)
  • Separation By Low-Temperature Treatments (AREA)

Abstract

Une plaque (1) pour un échangeur de chaleur à plaques présente une configuration d'ondulations d'arêtes (4) et de rainures (3) qui repose contre les ondulations sur une plaque adjacente en formant un grand nombre de points de support (2). Selon l'invention, la plaque, au moins sur un côté, possède des arêtes pourvues de parties en retrait (5), dans les régions des points de support (2). Grâce à cet agencement, le nombre de points de support générant des turbulences et par conséquent la résistance à l'écoulement sont réduits dans un passage adjacent d'échange de chaleur (7).A plate (1) for a plate heat exchanger has a configuration of corrugations of edges (4) and grooves (3) which rests against the corrugations on an adjacent plate by forming a large number of support points (2 ). According to the invention, the plate, at least on one side, has edges provided with recessed parts (5), in the regions of the support points (2). Thanks to this arrangement, the number of support points generating turbulence and therefore the resistance to flow are reduced in an adjacent heat exchange passage (7).

Description

Heat exchanger plate
This invention relates to a plate for a plate heat exchanger provided with a corrugation pattern of ridges and grooves arranged to rest intersectingly against the corrugation pattern of an adjacent plate such that a great number of supporting points are formed. The function of the supporting points partly is to absorb compres sive forces and partly to generate turbulence or increased convection, usually followed by increased pressure drop.
In heat exchangers built up by plates with mutual intersecting corrugations it is known to change the flow resistence of the heat exchange passages and consequently also the so called thermal length by varying the press depth and the mutual angle of the cor rugations of adjacent plates and by combining different press depths and angles. The possibilities to influence the flow characteristics of the passages with such arrangements, however, are limited to changes equal in size of the passages for the two media. A change of the passages for one of the media thus causes a corresponding change of the passages for the other medium.
The above mentioned limitation is a drawback since it is sometimes desirable to be able to bring about asymmetrical passages, i.e. to change the flow characteristics of the passages for the two media independently of each other, for instance when having the same type of medium in liquid state and the same allowed pressure drop and essentially the same viscosity and when the flows of the media are unequal in size, i.e. when the task of the heat exchange is asymmetrical. The heat exchanger in this example must be dimensioned for that medium that has the largest flow such that desired pressure drop is achieved in the passages through which this medium passes. Due to this, fact the passages for the other medium, which have the same capacity, will be over-dimensioned for the actual flow. Which medium that becomes limiting depends on size of flow, state of aggregation, the highest allowed pressure drop, type of fluid etc. Thus, also during condensation and/or evaporation the passages for one of the media usually becomes limiting, while the upper limit of the pressure drop for the other medium cannot be utilized. Accordingly, the heat exchanging surfaces of the apparatus are not utilized in the best way, which is unfavourable from an economic point of view.
In order to master this problem heat exchanger plates have been suggested provided with an unsymmetrical cor.rugation pattern having narrow ridges and wide grooves or vice versa. By means of such plates it is possible to bring about a heat exchanger, in which the passages for the two media have mutual different volume and consequently different flow characteristics. The difference in flow characteristics achieved in this way, however, is small at the same time as the area enlargement of the pattern has to be reduced. Therefore, this solution has appeared not to be so suitable in practice.
The object of this invention is to bring about a heat exchanger plate making it possible to adapt the flow characteristics of the passages to mutual flows of unequal size of the two heat exchanging media under essential retention of area enlarging effect of the corrugation. In other words, each heat exchanging passage shall, if possible, have flow characteristics adapted to the medium flow passing through the passage. This has been achieved by means of a heat exchanger plate of the type mentioned by way of introduction, which plate according to the invention is characterized by the fact that at least on its one side it has ridges, provided with recessed parts arranged in the areas of the supporting points, whereby in an adjacent heat exchanging passage the number of supporting points generating convection or turbulence and consequently also the flow resistance are reduced.
The invention is described more closely below with reference to the accompanying drawings, in which Figs. 1 and 2 show a section and a plan view respectively of a fragment of a series of heat exchanger plates according to the invention and Figs. 3-6 show corresponding views of other embodiments of the invention.
Fig. 1 shows fragments of three identical plates 1, of which the intermediate one is turned 180° around its longitudinal axis in order to bring about a mutual intersecting corrugation pattern, which forms supporting points 2, in which the plates rest against each other. As is revealed in the best way in Fig. 2, the grooves 3 are running uninterruptedly, while the ridges 4 are provided with recesses 5 approximately positioned flush with the central plane of the plate. The recesses 5 are arranged in line with each other. As is revealed in Fig. 1 the recesses 5 are positioned on such places where corrugation ridges turned to each other inter sect each other, whereby the number of supporting points are reduced in the passages 7. In the embodiment according to Figs. 1 and 2 every third supporting point is eliminated. Due to this fact a substantial reduction of the pressure drop is achieved in every second heat exchanging passage.
In the passages for the other medium, which are represented by the lower passage 8 in Fig. 1, the number of supporting points is not reduced and, therefore, the flow characteristics are changed in a substantially less extension, but since the volume of the passages is reduced, their flow resistance will usually increase to some extent.
In Figs. 3 and 4 plates 11 are shown that are arranged in the same way as are the plates 1 in Figs. 1 and 2 but differ from those by being provided with deeper recesses 15, the depth of which corresponds to the whole embossing depth of the plates. Due to this fact the recesses 15 form continuous resting lines, which bring about a division of the passages 18 into several parallel part passages. Such a division is advantageous in order to prevent flow instability, unbalanced distribution or undesirable flow distribu tion, which under certain circumstances particularly in connection with evaporation or condensation has a tendency to appear, since the width of the heat exchanging passage is too large in relation to its thickness and length. The division into part passages has also that advantage that the flow speed in the part passages can be influenced to Increase or to be reduced and generally for guaranteeing a flow, for Instance in condensate outlets or exhaust gas channels in a condensor. The tightness over the resting lines can be secured for Instance by glueing, soldering or welding or by means of gaskets.
In order to bring about a good distribution of the flow between the"different part passages it Is in this connection suitable to arrange restrictions of the flow, which In a way known of those skilled in the art, can be brought about by means of some suitable form of area restriction, as small inlet and outlet openings or particular restriction means put into suitable places in the passages. The restrictions as to evaporators of different types and boilers are suitably placed in the inlet of each part passage and as to condensors in the outlets of non-condensable gases and/or condensate.
In that In Figs. 5 and 6 disclosed embodiment two plates 11 according to Fig. 3 have been combined with an intermediate conventio nal plate 20 without recesses. Due to that fact has been formed a passage 27 with reduced number of supporting points 22, and a passage 28 with retained number of supporting points but without longitudinal resting lines.
It is easily perceived that besides the above described embodiments many changes of the recesses are possible as to form, dimensions and orientation over the surface of the plate. By the disclosed placement of the recesses in rows In the longitudinal direction of the plate, the pressure drop sinking effect is strengthened, but the recesses can have any arbitrary placement, which in each particular case can appear to be suitable of resistance reasons or flow-technical reasons. They can for instance be arranged in rows across or obliquely against the longitudinal direction of the plate or in interrupted rows in someone of these directions or not at all in line.

Claims

Claims
1. Plate for a plate heat exchanger, provided with a corrugation pattern of ridges (4) and grooves (3) arranged to rest intersectIngly against the corrugation pattern of an adjacent plate such that a great number of supporting points are formed, c ha r a c t e r i z e d in that at least on its one side it has ridges provided with recessed parts arranged In the areas of the supporting points, whereby in an adjacent heat exchanging passage the number of supporting points, generating convection or turbulence and consequently also the flow resistance, are reduced.
2. Plate according to claim 1, c h a r a c t e r i z e d in that the recessed parts (5, 15) of the plate are arranged in line with each other along one or several lines.
3. Plate according to claim 2, ch a r a c t e r i z e d in that the recessed parts (5, 15) are arranged in interrupted rows.
4. Plate according to anyone of the claims 1-3, c h a r a cte r i z e d in that the recessed parts (5, 15) are arranged in line with each other in the longitudinal or transversal direction of the plate.
5. Plate according to anyone of the claims 1-4, c h a r a c t e r i z e d in that the recessed parts (5, 15) have a depth corresponding to a part of the embossing depth of the plate.
6. Plate according to claim 1, c h a r a c t e r i z e d in that the recessed parts (15) have a depth corresponding to the whole embossing depth of the plate and are arranged in one or several rows in the longitudinal direction of the plate, whereby at least every second heat exchanging passage are divided into several parallel part passages.
PCT/SE1982/000393 1981-11-26 1982-11-23 Heat exchanger plate Ceased WO1983001998A1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE8282903492T DE3262352D1 (en) 1981-11-26 1982-11-23 Heat exchanger plate
AT82903492T ATE11822T1 (en) 1981-11-26 1982-11-23 HEAT EXCHANGE PLATE.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE8107040-1811126 1981-11-26
SE8107040A SE443870B (en) 1981-11-26 1981-11-26 PLATE HEAT EXCHANGERS WITH CORRUGATED PLATES WHICH CORRUGATES SUPPORTS NEARBY PLATES CORRUGATIONS WITHOUT A NUMBER OF CONSUMPTION PARTIES

Publications (1)

Publication Number Publication Date
WO1983001998A1 true WO1983001998A1 (en) 1983-06-09

Family

ID=20345131

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/SE1982/000393 Ceased WO1983001998A1 (en) 1981-11-26 1982-11-23 Heat exchanger plate

Country Status (7)

Country Link
US (1) US4605060A (en)
EP (1) EP0094954B1 (en)
JP (2) JPS58502016A (en)
AT (1) ATE11822T1 (en)
DE (1) DE3262352D1 (en)
SE (1) SE443870B (en)
WO (1) WO1983001998A1 (en)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0252275A3 (en) * 1986-07-03 1988-03-02 W. Schmidt GmbH & Co. KG Panel heat exchanger
US4915165A (en) * 1987-04-21 1990-04-10 Alfa-Laval Thermal Ab Plate heat exchanger
WO1999024772A1 (en) * 1997-11-12 1999-05-20 Marconi Communications, Inc. Heat exchanger
EP0984238A3 (en) * 1998-09-01 2000-06-07 IP Compact AB Heat exchanger
US6364007B1 (en) 2000-09-19 2002-04-02 Marconi Communications, Inc. Plastic counterflow heat exchanger
US6660198B1 (en) 2000-09-19 2003-12-09 Marconi Communications, Inc. Process for making a plastic counterflow heat exchanger
USD579101S1 (en) 2007-05-30 2008-10-21 Catacel Corp. Heat exchanger
US7591301B2 (en) 2005-09-13 2009-09-22 Catacel Corp. Low-cost high-temperature heat exchanger
US7594326B2 (en) 2005-09-13 2009-09-29 Catacel Corp. Method for making a low-cost high-temperature heat exchanger
US8047272B2 (en) 2005-09-13 2011-11-01 Catacel Corp. High-temperature heat exchanger
EP1630510B2 (en) † 2004-08-28 2014-03-05 SWEP International AB A plate heat exchanger
WO2014074063A1 (en) * 2012-11-07 2014-05-15 Andri Engineering Ab A heat exchanger and a ventilation assembly comprising it
FR3024225A1 (en) * 2014-07-25 2016-01-29 Airbus Helicopters HEAT EXCHANGER WITH PLATES AND IMPROVED THERMAL EFFICIENCY FOR TURBOMOTEUR
US9534854B2 (en) 2010-06-24 2017-01-03 Alfa Laval Corporate Ab Heat exchanger plate and a plate heat exchanger
US10234212B2 (en) 2014-08-22 2019-03-19 Alfa Laval Corporate Ab Heat transfer plate and plate heat exchanger
CN113701545A (en) * 2021-09-09 2021-11-26 浙江锦欣节能科技有限公司 Heat exchange plate group and heat exchanger

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US4723601A (en) * 1985-03-25 1988-02-09 Nippondenso Co., Ltd. Multi-layer type heat exchanger
US4815534A (en) * 1987-09-21 1989-03-28 Itt Standard, Itt Corporation Plate type heat exchanger
SE468685B (en) * 1991-06-24 1993-03-01 Alfa Laval Thermal Ab PLATE HEAT EXCHANGE WITH PLATTER THAT HAS AASAR AND RAENNOR THERE AASAR ON A PLATE BASED ON PARALLEL WITH THE SAME CURRENT AASAR ON THE OTHER PLATE
SE470339B (en) * 1992-06-12 1994-01-24 Alfa Laval Thermal Flat heat exchangers for liquids with different flows
JP3543993B2 (en) * 1994-03-28 2004-07-21 株式会社日阪製作所 Plate heat exchanger
JPH07260384A (en) * 1994-03-28 1995-10-13 Hisaka Works Ltd Plate heat exchanger
JP3543992B2 (en) * 1994-03-28 2004-07-21 株式会社日阪製作所 Plate heat exchanger
AT406301B (en) * 1998-06-24 2000-04-25 Ernst P Fischer Maschinen Und PLATE HEAT EXCHANGER
AU5167000A (en) 1999-05-27 2000-12-18 Thomas & Betts International, Inc. Compact high-efficient air heater
DE60000493T2 (en) * 1999-07-30 2003-02-20 Denso Corp., Kariya Exhaust gas heat exchanger with gas guide segments arranged at an angle
GB2451113A (en) * 2007-07-19 2009-01-21 Rolls Royce Plc Corrugations of a heat exchanger matrix having first and second different amplitudes
EP2207001B1 (en) * 2009-01-12 2012-12-05 Alfa Laval Vicarb Reinforced heat exchanger plate
CN101909416A (en) * 2009-06-04 2010-12-08 富准精密工业(深圳)有限公司 heat sink
TR201809058T4 (en) * 2009-06-26 2018-07-23 Swep Int Ab Asymmetric heat exchanger.
JP2011133166A (en) * 2009-12-24 2011-07-07 Mitsubishi Electric Corp Plate type heat exchanger
WO2012094652A2 (en) * 2011-01-06 2012-07-12 Clean Rolling Power, LLC Multichamber heat exchanger
JP6398469B2 (en) * 2014-08-27 2018-10-03 三浦工業株式会社 Heat exchanger
JP6069425B2 (en) * 2015-07-03 2017-02-01 株式会社日阪製作所 Plate heat exchanger
FR3050519B1 (en) * 2016-04-25 2019-09-06 Novares France HEAT EXCHANGER OF PLASTIC MATERIAL AND VEHICLE COMPRISING THIS HEAT EXCHANGER
CN108999705A (en) * 2018-07-09 2018-12-14 武汉英康汇通电气有限公司 Regenerator core and regenerator including regenerator core
US10903537B2 (en) 2019-01-31 2021-01-26 Toyota Motor Engineering & Manufacturing North America, Inc. Optimized heat conducting member for battery cell thermal management
SE544387C2 (en) 2019-12-23 2022-05-03 Swep Int Ab A heat exchanger with indentations for avoiding stagnant media
SE545748C2 (en) 2020-01-30 2023-12-27 Swep Int Ab A heat exchanger and refrigeration system and method
SE545690C2 (en) 2020-01-30 2023-12-05 Swep Int Ab A brazed plate heat exchanger and use thereof
CN112556461B (en) * 2020-11-27 2025-10-17 上海齐耀热能工程有限公司 Corrugated plate for plate heat exchanger and plate heat exchanger

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Publication number Priority date Publication date Assignee Title
DE434787C (en) * 1925-07-24 1927-03-12 Wilhelm Hohbach Lamellar cooler
SE134030C1 (en) * 1945-08-29 1951-12-27 Philips Nv Heat exchangers with facing walls provided with grooves
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SE353602B (en) * 1967-01-19 1973-02-05 Apv Co Ltd
SE342904B (en) * 1967-05-24 1972-02-21 Apv Co Ltd
SE349388B (en) * 1967-09-18 1972-09-25 Apv Co Ltd
SE320678B (en) * 1968-03-12 1970-02-16 Alfa Laval Ab
GB1272285A (en) * 1969-04-29 1972-04-26 Kyffhauserhutte Arten Veb Masc Plate-type heat exchanger
SE353954B (en) * 1971-02-19 1973-02-19 Alfa Laval Ab
SE384567B (en) * 1973-08-24 1976-05-10 Nevsky Mashinostroitelny Z Im PLATE HEAT EXCHANGER

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0252275A3 (en) * 1986-07-03 1988-03-02 W. Schmidt GmbH & Co. KG Panel heat exchanger
US4915165A (en) * 1987-04-21 1990-04-10 Alfa-Laval Thermal Ab Plate heat exchanger
WO1999024772A1 (en) * 1997-11-12 1999-05-20 Marconi Communications, Inc. Heat exchanger
EP0984238A3 (en) * 1998-09-01 2000-06-07 IP Compact AB Heat exchanger
US6364007B1 (en) 2000-09-19 2002-04-02 Marconi Communications, Inc. Plastic counterflow heat exchanger
US6660198B1 (en) 2000-09-19 2003-12-09 Marconi Communications, Inc. Process for making a plastic counterflow heat exchanger
EP1630510B2 (en) † 2004-08-28 2014-03-05 SWEP International AB A plate heat exchanger
US7594326B2 (en) 2005-09-13 2009-09-29 Catacel Corp. Method for making a low-cost high-temperature heat exchanger
US7591301B2 (en) 2005-09-13 2009-09-22 Catacel Corp. Low-cost high-temperature heat exchanger
US8047272B2 (en) 2005-09-13 2011-11-01 Catacel Corp. High-temperature heat exchanger
USD579101S1 (en) 2007-05-30 2008-10-21 Catacel Corp. Heat exchanger
US9534854B2 (en) 2010-06-24 2017-01-03 Alfa Laval Corporate Ab Heat exchanger plate and a plate heat exchanger
WO2014074063A1 (en) * 2012-11-07 2014-05-15 Andri Engineering Ab A heat exchanger and a ventilation assembly comprising it
FR3024225A1 (en) * 2014-07-25 2016-01-29 Airbus Helicopters HEAT EXCHANGER WITH PLATES AND IMPROVED THERMAL EFFICIENCY FOR TURBOMOTEUR
EP2982925A1 (en) 2014-07-25 2016-02-10 Airbus Helicopters A plate heat exchanger of improved thermal efficiency for a turboshaft engine
US10234212B2 (en) 2014-08-22 2019-03-19 Alfa Laval Corporate Ab Heat transfer plate and plate heat exchanger
CN113701545A (en) * 2021-09-09 2021-11-26 浙江锦欣节能科技有限公司 Heat exchange plate group and heat exchanger
CN113701545B (en) * 2021-09-09 2024-04-26 浙江星煜机电科技股份有限公司 Heat exchange plate group and heat exchanger

Also Published As

Publication number Publication date
ATE11822T1 (en) 1985-02-15
SE443870B (en) 1986-03-10
US4605060A (en) 1986-08-12
EP0094954B1 (en) 1985-02-13
JPH0545477U (en) 1993-06-18
JPS58502016A (en) 1983-11-24
SE8107040L (en) 1983-05-27
EP0094954A1 (en) 1983-11-30
DE3262352D1 (en) 1985-03-28

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