EP0292245A1 - Wärmeaustauscher mit flachen Platten - Google Patents

Wärmeaustauscher mit flachen Platten Download PDF

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Publication number
EP0292245A1
EP0292245A1 EP88304471A EP88304471A EP0292245A1 EP 0292245 A1 EP0292245 A1 EP 0292245A1 EP 88304471 A EP88304471 A EP 88304471A EP 88304471 A EP88304471 A EP 88304471A EP 0292245 A1 EP0292245 A1 EP 0292245A1
Authority
EP
European Patent Office
Prior art keywords
plates
group
heat exchanger
fluid flow
fluid
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP88304471A
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English (en)
French (fr)
Inventor
Anthony Matthew Johnston
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.)
HEATRIC Pty Ltd
Original Assignee
HEATRIC Pty Ltd
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 HEATRIC Pty Ltd filed Critical HEATRIC Pty Ltd
Publication of EP0292245A1 publication Critical patent/EP0292245A1/de
Withdrawn legal-status Critical Current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
    • F28D9/0081—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 a single plate-like element ; the conduits for one heat-exchange medium being integrated in one single plate-like element
    • 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
    • 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

Definitions

  • This invention relates to a heat exchanger of a type having flat plates which are formed within their thickness with fluid passages and which are bonded together as laminations without any intervening gaskets.
  • Such heat exchangers have been developed to provide for counterflow, crossflow or coflow of heat exchange fluids but, in all cases, the fluid passages in individual plates have been formed to provide for flow which is generally unidirectional.
  • the flow paths in some cases have incorporated turbulence inducing geometries such as zig-zag channels or flow diverters.
  • some plates have been formed with distribution zone channels and smoothing zone channels which may extend transversely or obliquely to the general direction of passages in the heat exchange region of the plates.
  • the individual plates have been designed and arranged to provide for flow in one direction only in the heat exchange region of the plates and the passages within such region do not provide for reverse direction flow of fluid within the length or width of the plates.
  • the present invention provides a structure having plates which are formed with fluid flow passages which make an odd number of passes across the width or along the length of the plates and which, in so doing, provide for reversal of fluid flow within the boundaries of each of the plates.
  • the present invention may be broadly defined as providing a heat exchanger which comprises a plurality of flat metal plates which are bonded together as laminations in face-to-face contact without any intervening gaskets.
  • a first group of the plates has a first fluid flow passage formed in one face of each plate of the group, and a second group of the plates has a second fluid flow passage formed in one face of each plate of the group.
  • Means are associated with the first group of plates for directing a first fluid into and from the fluid flow passages in that group of plates and for keeping the first fluid separate from a second fluid which is in use directed through the fluid flow passages in the second group of plates.
  • the first and second fluid flow passages in the respective plates each comprise a plurality of channels which are formed within the thickness of the respective plates.
  • the channels in at least the first group of plates make an odd number of passes across the width or along the length of the plates and the channels within each fluid flow passage have approximately the same length.
  • the present invention enables a single plate size to be used to produce a very wide range of heat exchange characteristics, without substantial variation in passage size. Also, the present invention avoids the need for a distribution zone and thus obviates the pressure drop and inefficient heat transfer which is normally associated with a distribution zone. Consequently, counterflow exchange may be no more costly to produce than crossflow exchange.
  • the present invention permits a single plate size and shape to be used to handle fluids with widely different flow rates and/or viscosities, without there being a need for extreme length-to-width ratios.
  • counterflow can be approached to any desired approximation by pursuing the fluid back and forth across the width or along the length of the plates and by appropriately patterning adjacent plates, without complex baffling being required in fluid headers.
  • small diameter fluid headers may be employed for fluids which are directed through those plates which provide for reversal of flow, and the heat load from side-to-side of the plate may be more even in the heat exchanger as contemplated by the present invention.
  • Each plate may be formed in each of its faces with fluid passages or, in the alternative, each plate may be formed in one face only with the fluid passages. Also, a complete heat exchanger may be constructed with all of its plates being of one type or the other, or with a mixture of the two types of plates. When the plates are formed in both faces with the fluid passages, adjacent plates may be bonded together to create double-depth passages, or adjacent plates may be separated by spacer plates which serve to separate the fluid streams.
  • heat exchangers will be constructed with plates which are formed in one face only with fluid passages and, in such case, two groups of interleaved plates will be provided within the heat exchanger, one group being used to convey one fluid and the second group being used to convey the other fluid.
  • both groups of plates may provide for reversal of fluid flow, although the heat exchanger may be constructed such that the passages in one group of plates provide for reversal of fluid flow while the passages in the other group of plates provide for straight-through fluid flow.
  • both groups of plates are formed with passages which provide for reversal of fluid flow
  • one group of plates may be provided with passages which extend predominantly in a longitudinal direction and the other group of plates with passages which extend predominantly in a transverse direction.
  • both groups of plates may be provided with passages which extend predominantly in the same direction.
  • All of the channels which serve to form one fluid flow passage preferably have the same dimension, and each channel preferably has a cross-sectional dimension and shape which is substantially constant along the full length of the channel.
  • Each channel preferably has a depth in the range 0.2 to 1.5mm and a width not greater than approximately 5mm. It is most preferred that each channel has a width less than 3mm.
  • One heat exchange fluid would normally be directed into and from the heat exchanger by headers connecting with the inlet and outlet ends of the passages in one group of the plates.
  • the other heat exchange fluid may be caused to pass through the heat exchanger by simply placing the exchanger in a fluid stream or bath.
  • a first pair of headers will be employed for directing a first fluid into and from a first group of plates in the heat exchanger, while a second pair of headers will be provided for directing a second fluid into and from a second group of plates in the exchanger.
  • the fluid flow channels may be linear, but for direction reversing bends in the channels, or the channels may be shaped in any desired manner, for example, to follow a serpentine or zig-zag path.
  • the heat exchanger is constructed from a plurality of flat stainless steel plates 10 and 11 which are interleaved, laminated and bonded together in face-to-face relationship.
  • the plates 10 and 11 are sandwiched between metal end plates 12 and all of the plates are diffusion bonded together at their contacting surfaces.
  • the plates are pressed together whilst subjected to a temperature approaching the melting point of the metal, whereby interfacial crystal growth is promoted. Compression is applied to the stack of plates during the bonding process in order to assure a sound bond and to compensate for any lack of plate flatness.
  • the plate 10 is formed with a fluid passage 13 which extends from an inlet region 14 in one edge 15 of the plate to an outlet region 16 in the opposite edge 17 of the plate.
  • the fluid passage is constituted by a plurality of channels 18, each of which extends transversely across the plate in a first direction, downwardly in a longitudinal direction of the plate, transversely across the plate in a reverse direction, downwardly again in the longitudinal direction and then transversely of the plate in the first direction.
  • the fluid passage as constituted by the channels 18 makes three passes across the width of the plate, although, in an alternative embodiment, the passage may make five or any other odd number of multiple passes as may be required. All of the channels 18 within the passage have approximately the same length and this is achieved only if the passage makes an odd number of passes.
  • the channels 18 are formed within the thickness of each plate and metal is removed to form the channels by a chemical or an electro-chemical process.
  • the channels 18 have a width in the range 1.0mm to 5.0mm and a depth in the order of 0.2mm to 1.5mm.
  • the plate may have a thickness in the order of 1.0mm to 2.0mm and the end plates 12 may have a thickness in the order of 10.0mm.
  • each plate which is not occupied by the channels 18, that is the marginal region 19 and the ridges between each of the channels, is used to provide metal-to- metal contact with adjacent plates in the diffusion bonding of the adjacent plates.
  • the plate 11 as shown in Figure 3 is constructed and formed in much the same manner as the plate 10, except that it has a unidirectional passage 20 which extends downwardly from an outlet region 21 in the top end 22 of the plate to an inlet region 23 in the bottom end 24 of the plate.
  • the passage is constituted by a plurality of linear channels 25 (each of which is indicated by a single line in Figure 3) and the channels are separated by intervening ridges.
  • Opposite side regions 26 of the plate are unchannelled and these regions, together with the channel-separating ridges, are bonded in face-to-face contact with adjacent plates during diffusion bonding to all of the plates of the heat exchanger.
  • All of the channels 25 in the plate 11 are open to the top and bottom of the heat exchanger as shown in Figure 1 and, thus, permit the flow of a first fluid in a vertical direction through alternative ones of the plates in the heat exchanger.
  • all of the channels 18 in the plates 10 open to the side edges of the heat exchanger in the inlet and outlet regions 14 and 16.
  • the inlet and outlet regions 14 and 16 are covered by inlet and outlet headers 27 and 28 which permit a second fluid to be directed into and from the passage in the alternately stacked plates 10.
  • the heat exchanger as shown in Figure 1 may be employed, for example, for chilling water.
  • Water is directed into the upper header 27 by way of an inlet pipe 29 and out through the lower header 28 from which it is conveyed by a pipe 30.
  • the water makes three transverse passes across the plates 10, reversing in direction during the second pass.
  • the complete heat exchanger is intended to be submerged in a refrigerant, so that the refrigerant when boiling is driven upwardly through the vertically extending passages in the plates 11 by buoyancy effects.
  • headers could be mounted to the lower and upper ends of the heat exchanger for conveying refrigerant into and from the plates 11.
  • FIG. 4 of the drawings shows a heat exchanger of a type which incorporates inlet and outlet headers for directing each of two fluids into and from the heat exchanger.
  • the heat exchanger in this case includes one pair of inlet and outlet headers 31 and 32 for directing a first heat exchange fluid through one group of plates 10 (as shown in Figure 2), while a second pair of inlet and outlet headers 33 and 34 is employed for directing a second fluid through a second group of alternately located (interleaved) plates 35 or 36.
  • the plate 35 is shown in detail in Figure 5A and it can be seen to have a passage 37 which makes three vertically extending passes along a substantial part of the length of the plate.
  • the passage 37 in this plate is formed in much the same way as that which has been described in the context of the plate shown in Figure 2 and it is constituted by a plurality of channels 38 extending between inlet and outlet regions 39 and 40 in the bottom and top of the plate.
  • the plate 36 in Figure 5B is similar to that which is shown in Figure 5A, except that it has a passage 41 which makes three horizontal passes across a substantial part of the plate and which is constituted by a plurality of channels 57. However, unlike the plate which is shown in Figure 2 which also makes horizontal passes, the plate which is shown in Figure 5B has a passage which connects with lower and upper inlet and outlet regions of the plate.
  • coflow, counterflow and crossflow heat exchange may be achieved.
  • counterflow thermal contact between fluid streams e.g. two water streams
  • a combination of coflow, counterflow and crossflow heat exchange may be achieved.
  • FIGs 6 and 7 illustrate two further heat exchanger arrangements which, in each case, incorporate plates of the type shown in Figure 3 interlaced with plates 43 of the type shown in Figure 8.
  • the plate 43 as shown in Figure 8 is similar to that which is shown in Figure 2, except that it includes two separate fluid flow passages 44 and 45 which are each constituted by a plurality of channels 58. These passages each make three passes across the width of the plate and they have separate inlet zones 46 and 47 in one edge 48 of the plate. However, both of the passages terminate or exit in a common outlet zone 49 in an opposite edge 50 of the plate.
  • the heat exchanger as shown in Figure 6 provides for the merging of two inlet streams into one outlet stream, this permitting the possible combination of crossflow, counterflow and coflow heat exchange within the exchanger.
  • Two headers 51 and 52 are employed for directing separate streams of a first fluid into the inlet zones 46 and 47 in the plates 43 and a single outlet header 53 is employed to cover the outlet zone 49 in the plates 43.
  • the second fluid is directed upwardly through the heat exchanger from header 33 to header 34.
  • an inlet header 54 is provided for directing a first heat exchange fluid into the heat exchanger and an outlet header 55 is provided on the same side of the heat exchanger for conveying the same fluid from the heat exchanger.
  • a further header 56 is located on the opposite edge of the heat exchanger and it functions simply to bridge all of the channels at the outlet zone 49 of the plates 43.
  • the invention has been hereinbefore described and illustrated in terms of a heat exchanger which incorporates two types of plates or, more particularly, which incorporates plates which have two separate fluid flow passages through which two heat exchange fluids are directed for themal contact.
  • the heat exchanger may be constructed to incorporate further fluid flow passages for conveying further fluids which may be required to participate in an exchange of heat.
  • the following claims should not be construed as excluding heat exchanger constructions which have three or more separate heat exchange passages for accommodating three or more heat exchange fluids.

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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)
EP88304471A 1987-05-21 1988-05-17 Wärmeaustauscher mit flachen Platten Withdrawn EP0292245A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AU2056/87 1987-05-21
AU205687 1987-05-21

Publications (1)

Publication Number Publication Date
EP0292245A1 true EP0292245A1 (de) 1988-11-23

Family

ID=3692567

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88304471A Withdrawn EP0292245A1 (de) 1987-05-21 1988-05-17 Wärmeaustauscher mit flachen Platten

Country Status (2)

Country Link
EP (1) EP0292245A1 (de)
JP (1) JPS643496A (de)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0393937A2 (de) * 1989-04-19 1990-10-24 John Francis Urch Wärmeaustauscher
EP0408751A1 (de) * 1989-02-03 1991-01-23 Zaporozhsky Avtomobilny Zavod 'kommunar' (Proizvodstvennoe Obiedinenie 'avtozaz') Plattenwärmeaustauscher
DE4327857A1 (de) * 1992-08-28 1994-03-03 Rekuper Miroslav Moravec Liber Wärmetauscher
US6409072B1 (en) * 1997-02-20 2002-06-25 Atotech Deutschland Gmbh Chemical microreactors and method for producing same
WO2004042293A1 (fr) * 2002-10-31 2004-05-21 Valeo Thermique Moteur Condenseur, notamment pour un circuit de climatisation de vehicule automobile, et circuit comprenant ce condenseur
US7087651B2 (en) 2001-12-05 2006-08-08 Gtl Microsystems Ag Process and apparatus for steam-methane reforming
US7186388B2 (en) 2001-10-18 2007-03-06 Compactgtl Plc Catalytic reactor
WO2007025766A1 (de) * 2005-09-01 2007-03-08 Syntics Gmbh Wärmetauschervorrichtung zum schnellen aufheizen oder abkühlen von fluiden
US7201883B2 (en) 2001-10-12 2007-04-10 Compactgtl Plc Catalytic reactor
US7223373B2 (en) 2001-10-18 2007-05-29 Compactgtl Plc Catalytic reactor
EP2228615A2 (de) * 2009-03-12 2010-09-15 Behr GmbH & Co. KG Vorrichtung zum Austausch von Wärme, insbesondere zur Wärmerückgewinnung aus Abgasen eines Kraftfahrzeugs
WO2010103259A2 (en) 2009-03-09 2010-09-16 Bp Alternative Energy International Limited Separation of carbon dioxide and hydrogen
WO2011089383A1 (en) 2010-01-21 2011-07-28 Bp Alternative Energy International Limited Separation of gases
WO2011089382A2 (en) 2010-01-21 2011-07-28 Bp Alternative Energy International Limited Purification of a co2-rich stream
US8021633B2 (en) 2001-12-05 2011-09-20 Compactgtl Plc Process an apparatus for steam-methane reforming
US8118889B2 (en) 2001-07-11 2012-02-21 Compactgtl Plc Catalytic reactor
CN104833245A (zh) * 2015-05-21 2015-08-12 上海利策科技股份有限公司 多流程微孔换热器
CN105157456A (zh) * 2015-09-25 2015-12-16 航天海鹰(哈尔滨)钛业有限公司 一种工业级微通道换热器
CN105509513A (zh) * 2014-09-22 2016-04-20 苏州皓璟兄弟照明设计工程有限公司 间壁式换热器
CN106370043A (zh) * 2016-10-31 2017-02-01 航天海鹰(哈尔滨)钛业有限公司 一种新型换热器芯部
FR3051244A1 (fr) * 2016-05-13 2017-11-17 Areva Np Echangeur de chaleur a plaques, procede de fabrication et utilisation correspondante
CN107990759A (zh) * 2018-01-18 2018-05-04 上海森松压力容器有限公司 一种模块化换热单体及使用该模块化换热单体的换热器
CN108088290A (zh) * 2018-01-18 2018-05-29 上海森松压力容器有限公司 一体式机加工换热器
US10281219B2 (en) 2014-10-01 2019-05-07 Mitsubishi Heavy Industries Compressor Corporation Plate laminated type heat exchanger
CN116907253A (zh) * 2023-09-14 2023-10-20 珠海格力电器股份有限公司 一种板式换热器及具有其的换热系统

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JP2007292394A (ja) * 2006-04-25 2007-11-08 Calsonic Kansei Corp 積層型熱交換器
JP4660510B2 (ja) * 2007-07-13 2011-03-30 株式会社神戸製鋼所 リアクタ及びリアクタを用いた反応方法
EP2377605B1 (de) 2009-01-13 2015-03-11 Kabushiki Kaisha Kobe Seiko Sho Flüssigkeitswegstruktur, reaktor und reaktionsverfahren mit dem reaktor
JP6659374B2 (ja) * 2016-01-22 2020-03-04 株式会社神戸製鋼所 熱交換器及び熱交換方法
JP6988035B2 (ja) * 2018-07-13 2022-01-05 株式会社三井Ｅ＆Ｓマシナリー 気化器
JP6950128B2 (ja) * 2018-07-13 2021-10-13 株式会社三井Ｅ＆Ｓマシナリー 気化器
JP6888211B2 (ja) * 2018-07-13 2021-06-16 株式会社三井Ｅ＆Ｓマシナリー 気化器
WO2020013319A1 (ja) * 2018-07-13 2020-01-16 株式会社三井Ｅ＆Ｓマシナリー 気化器

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1662870A (en) * 1924-10-09 1928-03-20 Stancliffe Engineering Corp Grooved-plate heat interchanger
GB429412A (en) * 1933-06-30 1935-05-29 Freerk De Boer Improvements in or relating to apparatus for pasteurizing milk and the like
GB1153403A (en) * 1966-09-26 1969-05-29 Trane Co Plate Type Heat Exchangers.
US3490522A (en) * 1968-02-20 1970-01-20 United Aircraft Corp Heat exchanger pass separator construction
US3590914A (en) * 1969-10-01 1971-07-06 Trane Co Countercurrent flow plate-type heat exchanger with leak detector
US4179781A (en) * 1976-07-26 1979-12-25 Karen L. Beckmann Method for forming a heat exchanger core
EP0212878A1 (de) * 1985-08-08 1987-03-04 Heatric Pty. Limited Kreuzstromplattenwärmetauscher

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1662870A (en) * 1924-10-09 1928-03-20 Stancliffe Engineering Corp Grooved-plate heat interchanger
GB429412A (en) * 1933-06-30 1935-05-29 Freerk De Boer Improvements in or relating to apparatus for pasteurizing milk and the like
GB1153403A (en) * 1966-09-26 1969-05-29 Trane Co Plate Type Heat Exchangers.
US3490522A (en) * 1968-02-20 1970-01-20 United Aircraft Corp Heat exchanger pass separator construction
US3590914A (en) * 1969-10-01 1971-07-06 Trane Co Countercurrent flow plate-type heat exchanger with leak detector
US4179781A (en) * 1976-07-26 1979-12-25 Karen L. Beckmann Method for forming a heat exchanger core
EP0212878A1 (de) * 1985-08-08 1987-03-04 Heatric Pty. Limited Kreuzstromplattenwärmetauscher

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0408751A1 (de) * 1989-02-03 1991-01-23 Zaporozhsky Avtomobilny Zavod 'kommunar' (Proizvodstvennoe Obiedinenie 'avtozaz') Plattenwärmeaustauscher
EP0408751A4 (en) * 1989-02-03 1991-10-30 Zaporozh Avtomobil Plate heat exchanger
EP0393937A3 (de) * 1989-04-19 1991-10-09 John Francis Urch Wärmeaustauscher
EP0393937A2 (de) * 1989-04-19 1990-10-24 John Francis Urch Wärmeaustauscher
DE4327857A1 (de) * 1992-08-28 1994-03-03 Rekuper Miroslav Moravec Liber Wärmetauscher
US6409072B1 (en) * 1997-02-20 2002-06-25 Atotech Deutschland Gmbh Chemical microreactors and method for producing same
US8118889B2 (en) 2001-07-11 2012-02-21 Compactgtl Plc Catalytic reactor
US7201883B2 (en) 2001-10-12 2007-04-10 Compactgtl Plc Catalytic reactor
US7186388B2 (en) 2001-10-18 2007-03-06 Compactgtl Plc Catalytic reactor
US7223373B2 (en) 2001-10-18 2007-05-29 Compactgtl Plc Catalytic reactor
US8021633B2 (en) 2001-12-05 2011-09-20 Compactgtl Plc Process an apparatus for steam-methane reforming
US7087651B2 (en) 2001-12-05 2006-08-08 Gtl Microsystems Ag Process and apparatus for steam-methane reforming
US7469554B2 (en) 2002-10-31 2008-12-30 Valeo Systeme Thermiques Condenser, in particular for a motor vehicle air conditioning circuit, and circuit comprising same
US8122736B2 (en) 2002-10-31 2012-02-28 Valeo Systemes Thermiques Condenser for a motor vehicle air conditioning circuit, and circuit comprising same
WO2004042293A1 (fr) * 2002-10-31 2004-05-21 Valeo Thermique Moteur Condenseur, notamment pour un circuit de climatisation de vehicule automobile, et circuit comprenant ce condenseur
WO2007025766A1 (de) * 2005-09-01 2007-03-08 Syntics Gmbh Wärmetauschervorrichtung zum schnellen aufheizen oder abkühlen von fluiden
WO2010103259A2 (en) 2009-03-09 2010-09-16 Bp Alternative Energy International Limited Separation of carbon dioxide and hydrogen
US9618271B2 (en) 2009-03-12 2017-04-11 Mahle International Gmbh Device for the exchange of heat and motor vehicle
EP2228615B1 (de) * 2009-03-12 2018-04-25 MAHLE Behr GmbH & Co. KG Vorrichtung zum Austausch von Wärme, insbesondere zur Wärmerückgewinnung aus Abgasen eines Kraftfahrzeugs
EP2228615A2 (de) * 2009-03-12 2010-09-15 Behr GmbH & Co. KG Vorrichtung zum Austausch von Wärme, insbesondere zur Wärmerückgewinnung aus Abgasen eines Kraftfahrzeugs
WO2011089383A1 (en) 2010-01-21 2011-07-28 Bp Alternative Energy International Limited Separation of gases
WO2011089382A2 (en) 2010-01-21 2011-07-28 Bp Alternative Energy International Limited Purification of a co2-rich stream
CN105509513A (zh) * 2014-09-22 2016-04-20 苏州皓璟兄弟照明设计工程有限公司 间壁式换热器
US10281219B2 (en) 2014-10-01 2019-05-07 Mitsubishi Heavy Industries Compressor Corporation Plate laminated type heat exchanger
CN104833245A (zh) * 2015-05-21 2015-08-12 上海利策科技股份有限公司 多流程微孔换热器
CN105157456A (zh) * 2015-09-25 2015-12-16 航天海鹰(哈尔滨)钛业有限公司 一种工业级微通道换热器
FR3051244A1 (fr) * 2016-05-13 2017-11-17 Areva Np Echangeur de chaleur a plaques, procede de fabrication et utilisation correspondante
CN106370043A (zh) * 2016-10-31 2017-02-01 航天海鹰(哈尔滨)钛业有限公司 一种新型换热器芯部
CN107990759A (zh) * 2018-01-18 2018-05-04 上海森松压力容器有限公司 一种模块化换热单体及使用该模块化换热单体的换热器
CN108088290A (zh) * 2018-01-18 2018-05-29 上海森松压力容器有限公司 一体式机加工换热器
CN116907253A (zh) * 2023-09-14 2023-10-20 珠海格力电器股份有限公司 一种板式换热器及具有其的换热系统
CN116907253B (zh) * 2023-09-14 2024-01-16 珠海格力电器股份有限公司 一种板式换热器及具有其的换热系统

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