WO2006043864A1 - Echangeur thermique à plaques et module de plaque - Google Patents

Echangeur thermique à plaques et module de plaque Download PDF

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Publication number
WO2006043864A1
WO2006043864A1 PCT/SE2005/001409 SE2005001409W WO2006043864A1 WO 2006043864 A1 WO2006043864 A1 WO 2006043864A1 SE 2005001409 W SE2005001409 W SE 2005001409W WO 2006043864 A1 WO2006043864 A1 WO 2006043864A1
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WO
WIPO (PCT)
Prior art keywords
plate
heat exchanger
inlet channel
channel
interspaces
Prior art date
Application number
PCT/SE2005/001409
Other languages
English (en)
Inventor
Claes Stenhede
Mats STRÖMBLAD
Original Assignee
Alfa Laval Corporate 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 Corporate Ab filed Critical Alfa Laval Corporate Ab
Priority to DE112005002226T priority Critical patent/DE112005002226T5/de
Publication of WO2006043864A1 publication Critical patent/WO2006043864A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
    • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/022—Evaporators with plate-like or laminated 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
    • F28D9/0031—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
    • F28D9/0043—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 plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—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 plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0011—Ejectors with the cooled primary flow at reduced or low pressure

Definitions

  • the present invention refers generally to a plate heat exchanger, in particular a plate heat exchanger in the form of an evaporator, i.e. a plate heat exchanger designed to cool a fluid through evaporation of a cooling medium in a cooling medium circuit for various, preferably industrial applications, such as air conditioning, cooling systems, heat pump systems, etc.
  • the present invention refers especially to a plate heat exchanger comprising a plate package, which comprises a number of heat exchanger plates that are provided beside each other in such a way that a first plate interspace for a cooling medium is formed between every second pair of adjacent heat exchanger plates, and a second plate interspace for a fluid between remaining pairs of adjacent heat exchanger plates, wherein the first plate interspaces and the second plate interspaces are separated from each other and provided beside each other in an alternating order in the plate package, wherein substantially each heat exchanger plate has at least a first porthole and a second porthole, wherein the first portholes enclose an inlet channel for the cooling medium to the first plate interspaces and the second portholes enclose an outlet channel for the cooling medium from the first plate interspaces, wherein the inlet channel is adapted to permit separation of the cooling medium to a substantially gaseous phase and a substantially liquid phase, wherein the plate heat exchanger includes at least a primary passage for conveying the gaseous phase from the inlet channel to the
  • the invention also refers to a plate module for a plate package in a plate heat exchanger, wherein the plate module comprises two heat exchanger plates which are provided beside each other in such a way that a plate interspace for a cooling medium is formed between the heat exchanger plates, wherein substantially each heat exchanger plate has at least a first porthole and a second porthole, wherein the first portholes form an inlet channel for the cooling medium to the plate interspace and the second portholes form an outlet channel for the cooling medium from the plate interspace, wherein the inlet channel is designed to permit separation of the cooling medium into a substantially gaseous phase and a substantially liquid phase, wherein the plate module comprises at least a primary passage for conveying the gaseous phase from the inlet channel to the plate interspace and at least a secondary passage for conveying the liquid phase from the inner channel to the plate interspace, and wherein the primary passage and the secondary passage meet in an area for re-mixing of the liquid phase into the gaseous phase for transport of this mixture further into the plate interspace.
  • the cooling medium which is supplied to the inlet channel of such a plate heat exchanger for evaporation of the cooling medium, is usually present in both a gaseous state and a liquid state. It is then difficult to provide an optimum distribution of the cooling medium to the different plate interspaces in the evaporator so that the same quantity of cooling medium is supplied and flows through each plate interspace intended for the cooling medium. If the cooling medium has a relatively high velocity into the inlet channel, the liquid phase is inclined to be transported to the inner end of the inlet channel. If the cooling medium has a relatively low velocity into the plate heat exchanger, the liquid phase is inclined to reach only the plate interspaces located at the outer end of the inlet channel.
  • the object of the present invention is to provide an improved plate heat exchanger for evaporation of a cooling medium.
  • a further object is to provide such a plate heat exchanger, which contributes to a proper distribution of the cooling medium to all plate interspaces for the cooling medium.
  • a further object is to provide such a plate heat exchanger which is compact and can be manufactured in an easy manner.
  • the plate heat exchanger initially defined, which is characterised in that the primary passage is designed to increase the velocity of the gaseous phase and to convey the gaseous phase to and past the liquid phase in said area in such a way that liquid is re-mixed into the gaseous phase by means of an ejector action.
  • the gaseous phase and the liquid phase of the incoming cooling medium will be separated from each other and thereafter re-mixed prior to the entry into the first plate interspaces.
  • the separated gaseous phase may be used to bring a part of the liquid phase into each of the first plate interspaces in such a way that the liquid phase is distributed uniformly between all first plate interspaces of the plate heat exchanger. Thanks to the created ejector action an efficient mixing of liquid in the gaseous phase is achieved substantially immediately before the cooling medium is distributed in the first plate interspaces.
  • the inlet channel is connected to at least an upper outlet which forms an inlet to the primary passage, and at least a lower outlet which forms an inlet to the secondary passage.
  • the primary passage may then extend to the secondary passage.
  • the plate heat exchanger is adapted to be provided in such a way that the lower outlet is located beneath the upper outlet, wherein the lower outlet is dimensioned in such a way that it permits liquid from the liquid phase to be collected upstream the lower outlet.
  • the liquid in the liquid phase may then be collected in a lower part of the inlet channel, preferably along substantially the whole length of the inlet channel. In such a way, there will always be liquid to be brought, by the gaseous phase in the primary passage, into each of the first plate interspaces.
  • the primary passage has a total minimum flow area and the secondary passage has a total minimum flow area, wherein the minimum flow area of the secondary passage is less than the minimum flow area of the primary passage.
  • the heat exchanger plates are compression-moulded in such a way that a substantially closed channel, which extends around at least a part of the inlet channel is formed in substantially each of the first plate interspaces, wherein these closed channels are comprised by the primary passage.
  • the arrangement with the separate primary and secondary passages for the gaseous phase and the liquid phase, respectively may in an easy manner be provided during the compression-moulding of the heat exchanger plates. No further components than the heat exchanger plates are necessary for the achievement of the desired function.
  • the heat exchanger plates may then be compression-moulded in such a way that the upper outlet is designed as a channel extending from the inlet channel to the substantially closed channel in substantially each of the first plate interspaces.
  • the heat exchanger plates may also be compression-moulded in such a way that the lower outlet is designed as a channel, which extends from the inlet channel in substantially each of the first plate interspaces. Also these two channels, forming an outlet from the inlet channel, may thus in an easy manner be provided during the compression-moulding of the heat exchanger plates.
  • the primary passage comprises two primary portions, which from an area at an upper part of the inlet channel extend in a respective direction around the inlet channel, wherein the two primary portions meet substantially immediately downstream the lower outlet. Consequently, the two upper outlets for each of the first plate interspaces may extend from the inlet channel. Alternatively, the primary passage may substantially immediately downstream the upper outlet be divided into the two primary portions.
  • each heat exchanger plate is designed in such a way that it comprises a lower aperture which is located beneath the first porthole and which is delimited from the first porthole by means of a first partitioning portion, wherein the first partitioning portion is designed to permit at least said liquid phase to pass the first partitioning portion and wherein the lower apertures form a liquid channel which extends through the plate package substantially in parallel to the inlet channel.
  • the lower outlet may then extend from the liquid channel. According to this embodiment, liquid may thus be collected in the liquid channel, wherein the liquid is discharged successively from the liquid channel in a controlled manner through the lower outlet.
  • each heat exchanger plate is designed in such a way that it comprises an upper aperture which is delimited from the first porthole by means of a second partitioning portion, wherein the upper apertures form a gas channel extending through the plate package in parallel to the inlet channel. Also such an aperture may be provided in connection with the compression-moulding and the punching of the heat exchanger plates. The upper outlet may then extend from the inlet channel to the gas channel and the closed channel may extend from the gas channel.
  • the plate heat exchanger comprises a first pipe, which extends through the first portholes of substantially each heat exchanger plate and which forms the inlet channel.
  • the plate heat exchanger may be produced by means of common heat exchanger plates, wherein the first pipe is introduced into the inlet channel for forming the primary passage and the secondary passage.
  • the upper outlet and the lower outlet may then extend through the first pipe, wherein the primary passage extends around at least a part of the first pipe.
  • the primary passage may thus extend in the relatively thin gap formed between the inlet channel and the outer side of the first pipe.
  • the plate heat exchanger comprises a partitioning plate, which is provided with an angle of inclination in the first pipe and which extends along substantially the whole length of the inlet channel, wherein the upper outlet is located above the partitioning plate and the lower outlet is located beneath the partitioning plate and wherein the partitioning plate in a lower area has an aperture for the liquid phase. Liquid may thus be collected in a lower area of the first pipe, especially in an area beneath the partitioning plate.
  • the plate heat exchanger comprises a second pipe which extends in the first pipe along substantially the whole length of the inlet channel, wherein the second pipe comprises at least an aperture for discharging the gaseous phase and the liquid phase into the first pipe.
  • the plate heat exchanger comprises a first end plate and a second end plate, between which the heat exchanger plates are provided.
  • each heat exchanger plate may comprise a third porthole and a fourth porthole, wherein the third portholes form an inlet channel for said fluid to the second interspaces, and the fourth portholes form an outlet channel for said fluid from the second plate interspaces.
  • the inlet channels and the outlet channels may then extend through the first end plate.
  • the heat exchanger plates may also be permanently connected to each other in pairs, wherein each pair encloses one of the first plate interspaces.
  • the object is also achieved by means of the initially defined plate module, which is characterised in that the primary passage is designed to increase the velocity of the gaseous phase and to convey the gaseous phase to and past the liquid phase in said area in such a way that liquid is re-mixed into the gaseous phase by means of an ejector action.
  • Fig. 1 discloses schematically a sideview of a plate heat exchanger according to a first embodiment of the invention.
  • Fig. 2 discloses schematically a front view of the plate heat exchanger in Fig. 1 .
  • Fig. 3 discloses schematically a plan view of a heat exchanger plate of the plate heat exchanger in Fig. 1.
  • Fig. 4 discloses schematically a plan view of an area around a porthole of the heat exchanger plate in Fig. 3.
  • Fig. 5 discloses schematically a sectional view through a number of heat exchanger plates along the line V-V in Fig. 4.
  • Fig. 6 discloses schematically a plan view of an area around a porthole of a heat exchanger plate according to a second embodiment of the invention.
  • Fig. 7 discloses schematically a plan view of an area around a porthole of a heat exchanger plate according to a third embodiment of the invention.
  • Figs. 1 to 5 disclose a first embodiment of the plate heat exchanger according to the invention.
  • the plate heat exchanger comprises a plate package P, which comprises a number of compression-moulded heat exchanger plates 1 that are provided beside each other.
  • the heat exchanger plates 1 are provided in such a way that a first interspace 3 for a cooling medium is formed between every second pair of adjacent heat exchanger plates 1 , and a second plate interspace 4 for a fluid between the remaining pairs of adjacent heat exchanger plates 1.
  • the first plate interspaces 3 and the second plate interspaces 4 are thus separated from each other and provided beside each other in an alternating order in the plate package P.
  • the plate heat exchanger comprises a first end plate 5 and a second end plate 6, between which the heat exchanger plates 1 are provided.
  • the first end plate 5 is a so-called pressure plate
  • the second end plate 6 is a so-called frame plate.
  • the plate package P is in the first embodiment kept together by means of a number of tie bolts 7, which extend outside the heat exchanger plates 1 but through the end plates 5 and 6.
  • the plate package P is compressed by means of nuts 8 threaded on the tie bolts 7.
  • the heat exchanger plates 1 are permanently connected to each other in pairs.
  • the two heat exchanger plates 1 in each pair may thus be welded to each other by means of a weld joint 9, see Fig. 3.
  • the heat exchanger plates 1 in one pair may also be brazed to each other, or permanently connected in any other way.
  • Such a permanently connected pair forms a plate module 10, see Fig. 5.
  • the two heat exchanger plates 1 in a plate module 10 encloses between themselves one of the first plate interspaces 3.
  • the second plate interspaces 4 are enclosed between adjacent plate modules 10.
  • the second plate interspaces 10 may be sealed by means of gaskets 11 in a manner known per se. It is to be noted, that the invention also is applicable to plate heat exchangers where every plate interspace 3, 4 is sealed by means of gaskets, or plate heat exchangers where all heat exchanger plates 1 are brazed to a permanently connected plate package.
  • each heat exchanger plate 1 comprises a first porthole 12, a second porthole 12, a third porthole 12 and a fourth porthole 12, see Fig. 3.
  • the first portholes 12 enclose an inlet channel 13 for the cooling medium to the first plate interspaces 3.
  • the second portholes 12 enclose an outlet channel 14 for the cooling medium from the first plate interspaces 3.
  • the third portholes 12 enclose an inlet channel 15 for said fluid to the second plate interspaces 4.
  • the fourth portholes 12 enclose an outlet channel 16 for said fluid from the second plate interspaces 4.
  • each heat exchanger plate A, B between the portholes 12 there is an active heat transfer area 18, which is provided with a corrugation of ridges and valleys in a manner known per se.
  • the corrugations extend in a herringbone-like pattern, wherein the corrugations of adjacent heat exchanger plates 1 points in opposite directions.
  • the heat transfer area 18 may of course have other kinds of patterns, compare Fig. 4.
  • Each heat exchanger plate 1 has a longitudinal centre axis x, see Figs. 2 and 3.
  • the heat exchanger plates 1 and the plate heat exchanger are in all embodiments disclosed adapted to be provided in such a way that the centre axis x extends substantially vertically.
  • the inlet channel 13 for the cooling medium and the outlet channel 16 for the fluid will then be located in the proximity of a lower end of the plate heat exchanger, whereas the outlet channel 14 for the cooling medium and the inlet channel 15 for the fluid will be located in the proximity of an upper end of the plate heat exchanger.
  • the cooling medium preferably flows upwardly through the plate heat exchanger.
  • the plate heat exchanger is designed as a counter current configuration. The invention is however also applicable to a parallel flow configuration.
  • the cooling medium supplied to an evaporator is normally a mixture of a gas and a liquid.
  • the gas is first to be separated from the liquid.
  • the inlet channel 13 is arranged to permit separation of the cooling medium entering the inlet channel 13 to a substantially gaseous phase and a substantially liquid phase.
  • the gaseous phase and the liquid phase are to be conveyed separated from each other to an area 19 in each of the first plate interspaces 3.
  • the liquid phase and the gaseous phase meet and are re-mixed with each other.
  • the plate heat exchanger comprises to this end at least a primary passage for conveying the gaseous phase from the inlet channel 13 to the first plate interspaces 3, and at least a secondary passage for conveying the liquid phase from the inlet channel 13 to the first plate interspaces 3.
  • the primary passage and the secondary passage meet in said area 19 in the proximity of the first plate interspaces 3 for re-mixing of the liquid phase in the gaseous phase.
  • the primary passage is designed to increase the velocity of the gaseous phase and to convey the gaseous phase to and past the liquid phase at a relatively high velocity in such a way that liquid is re-mixed in the gaseous phase by means of an ejector action in said area 19.
  • the primary passage comprises in substantially each of the first plate interspaces 3 an upper outlet 20 which is designed as a channel extending from the inlet channel 13. Furthermore, the primary passage comprises in each of the first plate interspaces 3 two substantially closed channels 21 , which extend from the upper ogtlet 20 around a respective half of the inlet channel 13 to said area 19 located beneath the inlet channel 13.
  • the secondary passage comprises in substantially each of the first plate interspaces 3 a lower outlet 22, which is designed as a channel extending from the inlet channel 13 to said area 19 beneath the inlet channel 13.
  • a lower outlet 22 which is designed as a channel extending from the inlet channel 13 to said area 19 beneath the inlet channel 13.
  • the lower outlet 22 is dimensioned in such a way that it permits liquid from the liquid phase to be collected in a lower area of the inlet channel 13 upstream the lower outlet 13.
  • the secondary passage then has in the lower outlet 22 a minimum flow area which is relatively small and less than a minimum flow area of the primary passage.
  • the primary passage is in the first embodiment divided into two primary portions, which from an area at an upper part of the inlet channel 13 extend in a respective direction around the inlet channel 13.
  • the two primary portions meet substantially immediately downstream the lower outlet 22.
  • heat exchanger plates 1 which are compression-moulded and punched in such a way that the primary passage and the secondary passage are produced, are also employed. Each heat exchanger plate 1 is then compression-moulded and punched in such a way that it has the first porthole 12. Also in the second embodiment, the first portholes 12 form the inlet channel 13. Each heat exchanger plate also has a lower aperture 30 which is located beneath the first porthole 12. The lower aperture 30 is delimited from the first porthole 12 by means of a first partitioning portion 31. The lower apertures 30 form a liquid channel 32 extending through substantially the whole plate package 1 1 substantially in parallel to the inlet channel 13.
  • the first partitioning portion 31 is designed to permit that at least the liquid phase is conveyed from the inlet channel 13 over the partitioning portion 31 down to the liquid channel 32.
  • the lower outlet 22 extends from the liquid channel 32 and in particular through a ridge 33 delimiting the liquid channel 32 downwards.
  • Each heat exchanger plate 1 is furthermore compression- moulded and punched in such a way that it has an upper aperture 34, which is delimited from the first porthole by means of a second partitioning portion 35.
  • the upper apertures 35 form a gas channel 36 extending through substantially the whole plate package P substantially in parallel to the inlet channel 13.
  • the upper outlet 20 extends from the inlet channel 13 to the upper aperture 35 and the gas channel 36 via the second partitioning portion 35 and in particular around an upper ridge
  • the closed channel 21 extends up to the area 19 where the gaseous phase, which is transported through the closed channel 21 , meets the liquid phase from the lower outlet 22.
  • the area 19 is, also according to the second embodiment, located beneath the lower outlet 22. The mixture of the gaseous phase and the liquid phase are then transported from the area 19 to the heat transfer area 18 via an outlet channel 38 in each of the first plate interspaces 3.
  • heat exchanger plates 1 are employed, which are provided for forming the first plate interspaces 3 between every second pair of adjacent plates 1 , and the second plate interspaces 4 between the remaining pairs of adjacent plates 1.
  • the plates 1 may be connected to each other in all possible ways, for instance pressed against each other between two end plates 5 and 6, permanently connected to each other in pairs, or the whole plate package P may be brazed.
  • the plate heat exchanger comprises a first pipe 40, which extends through the first portholes 12 of substantially each heat exchanger plate 1.
  • the first pipe 40 form the inlet channel 13.
  • the upper outlet 20 and the lower outlet 22 extend through the pipe 40, wherein the primary passage extends around at least a part of said pipe.
  • a partitioning plate 41 is provided in the first pipe 40.
  • the partitioning plate 41 has an angle of inclination in relation to the centre axis x.
  • the partitioning plate 41 extends along substantially the whole length of the first pipe 40 and the inlet channel 13.
  • the upper outlet 20 is located above the partitioning plate 41
  • the lower outlet 22 is located beneath the partitioning plate 41 .
  • the partitioning plate 41 has in a lower area an aperture 42 through which the liquid phase may pass.
  • the plate heat exchanger also comprises a second pipe 43 for the supply of the cooling medium to the plate heat exchanger.
  • the second pipe 43 extends in the first pipe 40 along substantially the whole length of the inlet channel 13.
  • the second pipe 43 comprises at least one aperture 44 for discharging the cooling media, i. e. the gaseous phase and the liquid phase, into the first pipe 40 above the partitioning plate 41.
  • the gaseous phase will thus be discharged through the upper outlets 20 and then pass through the primary passage along the outer side of the first pipe 40 down to said area 19 which is located beneath the lower outlets 22. From the area 19, the mixture is transported out into the heat transfer area in each of the first plate interspaces 3.

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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)

Abstract

Un échangeur thermique à plaques comprend un ensemble de plaques (P)formées par un certain nombre de plaques d'échangeur thermique formant un premier intervalle d'espace de plaques pour un milieu de refroidissement entre chaque paires de plaques d'échangeur thermique contiguës et un second intervalle d'espace de plaques pour un liquide entre les paires restantes. Le premier et le second intervalle d'espace de plaques sont séparés l'un de l'autre et placés en alternance. Chaque plaque d'échangeur thermique (1) possèdent au moins un premier orifice (12). Les premiers orifices ferment un canal d'entrée (13) destiné au milieu de refroidissement vers le premier intervalle d'espace de plaques. Le canal d'entrée permet la séparation du milieu de refroidissement en une phase sensiblement gazeuse et en une phase sensiblement liquide. Cet échangeur thermique à plaques comprend un passage principal pour la phase gazeuse vers le premier intervalle d'espace de plaques et un passage auxiliaire pour la phase liquide vers les premiers intervalles d'espace de plaques. Le passage principal et le passage auxiliaire se rencontrent dans une zone (19) de façon à remélanger la phase liquide dans la phase gazeuse en vue d'un nouveau transport de ce mélange dans les premiers intervalles d'espace de plaques.
PCT/SE2005/001409 2004-10-21 2005-09-22 Echangeur thermique à plaques et module de plaque WO2006043864A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE112005002226T DE112005002226T5 (de) 2004-10-21 2005-09-22 Plattenwärmetauscher und Plattenmodul

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
SE0402548A SE531267C2 (sv) 2004-10-21 2004-10-21 Plattvärmeväxlare och plattmodul
SE0402548-2 2004-10-21

Publications (1)

Publication Number Publication Date
WO2006043864A1 true WO2006043864A1 (fr) 2006-04-27

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PCT/SE2005/001409 WO2006043864A1 (fr) 2004-10-21 2005-09-22 Echangeur thermique à plaques et module de plaque

Country Status (3)

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DE (1) DE112005002226T5 (fr)
SE (1) SE531267C2 (fr)
WO (1) WO2006043864A1 (fr)

Cited By (9)

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Publication number Priority date Publication date Assignee Title
WO2010036183A1 (fr) * 2008-09-23 2010-04-01 Alfa Laval Corporate Ab Échangeur de chaleur à plaques
WO2014116660A1 (fr) * 2013-01-24 2014-07-31 Alcoil Usa Llc Échangeur thermique
WO2017004058A1 (fr) * 2015-06-29 2017-01-05 Carrier Corporation Évaporateur distributeur à deux phases
WO2018100300A1 (fr) * 2016-11-30 2018-06-07 Valeo Systemes Thermiques Dispositif de distribution d'un fluide réfrigérant à l'intérieur d'une boîte collectrice d'un échangeur thermique
WO2018100299A1 (fr) * 2016-11-30 2018-06-07 Valeo Systemes Thermiques Dispositif d'homogénéisation de la distribution d'un fluide réfrigérant à l'intérieur de tubes d'un échangeur de chaleur constitutif d'un circuit de fluide réfrigérant
FR3061280A1 (fr) * 2016-11-30 2018-06-29 Valeo Systemes Thermiques Dispositif de distribution d'un fluide refrigerant a l'interieur d'une boite collectrice d'un echangeur thermique pour une installation de conditionnement d'air d'un vehicule
WO2020110685A1 (fr) * 2018-11-26 2020-06-04 三菱電機株式会社 Échangeur de chaleur de type à plaques et système de distribution d'eau chaude de type à pompe à chaleur
WO2021160370A1 (fr) * 2020-02-14 2021-08-19 Alfa Laval Corporate Ab Plaque d'échangeur de chaleur et échangeur de chaleur à plaques
CN114688765A (zh) * 2020-12-30 2022-07-01 广东美的白色家电技术创新中心有限公司 换热器和空调器

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Publication number Priority date Publication date Assignee Title
DE102014001499A1 (de) * 2014-02-06 2015-08-06 Api Schmidt-Bretten Gmbh & Co. Kg Zum Wärme- und/oder Stoffaustausch geeigneter Plattenapparat

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WO2010036183A1 (fr) * 2008-09-23 2010-04-01 Alfa Laval Corporate Ab Échangeur de chaleur à plaques
US9046310B2 (en) 2008-09-23 2015-06-02 Alfa Laval Corporate Ab Plate heat exchanger
WO2014116660A1 (fr) * 2013-01-24 2014-07-31 Alcoil Usa Llc Échangeur thermique
US9459057B2 (en) 2013-01-24 2016-10-04 Alcoll USA LLC Heat exchanger
WO2017004058A1 (fr) * 2015-06-29 2017-01-05 Carrier Corporation Évaporateur distributeur à deux phases
CN107850396A (zh) * 2015-06-29 2018-03-27 开利公司 两相分配器蒸发器
FR3061950A1 (fr) * 2016-11-30 2018-07-20 Valeo Systemes Thermiques Dispositif d’homogeneisation de la distribution d’un fluide refrigerant a l’interieur de tubes d’un echangeur de chaleur constitutif d’un circuit de fluide refrigerant
WO2018100299A1 (fr) * 2016-11-30 2018-06-07 Valeo Systemes Thermiques Dispositif d'homogénéisation de la distribution d'un fluide réfrigérant à l'intérieur de tubes d'un échangeur de chaleur constitutif d'un circuit de fluide réfrigérant
FR3061280A1 (fr) * 2016-11-30 2018-06-29 Valeo Systemes Thermiques Dispositif de distribution d'un fluide refrigerant a l'interieur d'une boite collectrice d'un echangeur thermique pour une installation de conditionnement d'air d'un vehicule
FR3061951A1 (fr) * 2016-11-30 2018-07-20 Valeo Systemes Thermiques Dispositif de distribution d'un fluide refrigerant a l'interieur d'une boite collectrice d'un echangeur thermique.
WO2018100300A1 (fr) * 2016-11-30 2018-06-07 Valeo Systemes Thermiques Dispositif de distribution d'un fluide réfrigérant à l'intérieur d'une boîte collectrice d'un échangeur thermique
CN110234951A (zh) * 2016-11-30 2019-09-13 法雷奥热系统公司 用于将制冷剂流体分配在热交换器的收集箱内的装置
CN110234951B (zh) * 2016-11-30 2021-08-03 法雷奥热系统公司 用于将制冷剂流体分配在热交换器的收集箱内的装置
JPWO2020110685A1 (ja) * 2018-11-26 2021-06-03 三菱電機株式会社 プレート式熱交換器及びヒートポンプ式給湯システム
WO2020110685A1 (fr) * 2018-11-26 2020-06-04 三菱電機株式会社 Échangeur de chaleur de type à plaques et système de distribution d'eau chaude de type à pompe à chaleur
WO2021160370A1 (fr) * 2020-02-14 2021-08-19 Alfa Laval Corporate Ab Plaque d'échangeur de chaleur et échangeur de chaleur à plaques
TWI773128B (zh) * 2020-02-14 2022-08-01 瑞典商阿爾法拉瓦公司 熱交換器板及板式熱交換器
JP2023513908A (ja) * 2020-02-14 2023-04-04 アルファ－ラヴァル・コーポレート・アーベー 伝熱プレートおよびプレート式熱交換器
JP7410314B2 (ja) 2020-02-14 2024-01-09 アルファ－ラヴァル・コーポレート・アーベー 伝熱プレートおよびプレート式熱交換器
CN114688765A (zh) * 2020-12-30 2022-07-01 广东美的白色家电技术创新中心有限公司 换热器和空调器

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SE0402548L (sv) 2006-04-22
DE112005002226T5 (de) 2007-09-27
SE531267C2 (sv) 2009-02-03

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