+

WO1997045689A1 - Echangeur de chaleur a plaques - Google Patents

Echangeur de chaleur a plaques Download PDF

Info

Publication number
WO1997045689A1
WO1997045689A1 PCT/CH1997/000195 CH9700195W WO9745689A1 WO 1997045689 A1 WO1997045689 A1 WO 1997045689A1 CH 9700195 W CH9700195 W CH 9700195W WO 9745689 A1 WO9745689 A1 WO 9745689A1
Authority
WO
WIPO (PCT)
Prior art keywords
channels
connection
plate
heat exchanger
plates
Prior art date
Application number
PCT/CH1997/000195
Other languages
German (de)
English (en)
Inventor
Arthur FLÜCK
Original Assignee
Nek Umwelttechnik Ag
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 Nek Umwelttechnik Ag filed Critical Nek Umwelttechnik Ag
Priority to DE59701152T priority Critical patent/DE59701152D1/de
Priority to AT97920477T priority patent/ATE189924T1/de
Priority to EP97920477A priority patent/EP0901602B1/fr
Publication of WO1997045689A1 publication Critical patent/WO1997045689A1/fr

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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0017—Flooded core heat exchangers
    • 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
    • F28D9/0012—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 apparatus having an annular form
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/02—Details of evaporators
    • F25B2339/024—Evaporators with refrigerant in a vessel in which is situated a heat exchanger
    • F25B2339/0241—Evaporators with refrigerant in a vessel in which is situated a heat exchanger having plate-like elements
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/043—Condensers made by assembling plate-like or laminated elements
    • 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
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • the invention relates to heat exchangers according to the preamble of claim 1 and to a device for performing a cyclic process.
  • Heat exchangers should enable the fastest possible and complete heat transfer between two fluids with different starting temperatures.
  • the two fluids are guided on both sides by heat-conducting contact surfaces.
  • the fluids are usually led through complex channel systems.
  • Tube bundle exchangers enable efficient duct routing for heat exchange, but are very complex.
  • Plate heat exchangers are much simpler in construction. Plate heat exchangers are now known, in which channels for one and the other fluid are alternately arranged between plates arranged in parallel in such a way that similarly complex channel systems are produced as in tube bundle exchangers.
  • the channels for both fluids are designed in such a way that flow paths that are as long and highly structured as possible are created.
  • first channel system must be designed such that at least some of the channels as first and second main channels for at least one first fluid over their entire length essentially along a first and a second main direction run.
  • first connection areas are preferably arranged in such a way that they are directly connected by at least one, but in particular by several main channels.
  • the two main directions run at an angle of less than 60 °, in particular less than 40 °, preferably of essentially 30 ° to one another.
  • the main directions are so orientable for operation that at least one main direction makes an angle to the vertical which is less than 30 ° , in particular less than 20 °, optionally substantially 0 °.
  • both main directions can preferably be aligned such that they are inclined between 10 ° and 20 °, preferably both essentially by 15 ° to the vertical.
  • the two first connection areas of the first channels for the first fluid are arranged on two mutually opposite circumferential areas of the plates and possibly merge into one another.
  • the two first connection areas are arranged one above the other and are at least in part of the main channels directly connected to each other. Because at least one main direction to the vertical encloses an angle that is less than 30 °, in particular less than 20 °, possibly essentially 0 °, or preferably 15 °, the first two connection areas are directly through Main channels connected, which run in a direction that is inclined less than 30 ° to the vertical. This ensures a good rise of gas bubbles or, in the case of condensation heat exchangers, a good sinking of condensed liquid drops.
  • the second channels are constructed similarly to the first and include third and fourth main channels for the second fluid, which essentially run along a main direction.
  • the first and second or the third and fourth channels are optionally connected to one another in outer end regions, but preferably in all crossing regions.
  • the first and second or third and fourth main channels are formed on both sides of a first and second connection level as open channels that are open to the connection level.
  • the first and second or third and fourth main channels lie openly against one another in the first and second connection levels, so that the first and second channels each have to be regarded as channel networks formed by the main channels with the connections in the intersection areas .
  • Plate stacks with the described channel networks are constructed from alternately adjoining first and second plates, the fourth and second half channels being formed on one side of the first and second plates and the first and third half channels on the other. All channels of a plate run essentially parallel to each other.
  • the two are second Connection areas for the second channels carrying the second fluid are formed as chambers running transversely to the plates. These two chambers are mutually connected only via the second channels and completely separated from the first channels.
  • the second connection regions are spaced apart from one another transversely to the bisecting angle of the two main directions, so that they are not directly connected to one another by individual main channels. The connection is thus only possible through at least two interconnected channel sections, at least one channel section being aligned in the first and at least one in the second main direction.
  • the plate heat exchanger In order to make the plate heat exchanger as simple as possible, it is preferably constructed from essentially identical plates or sheets. Grooves running on both sides in a main direction are arranged in each plate. Since the plates are preferably designed as sheets, these grooves provided on both sides can be formed as sinks by a pressing or stamping process, which appear as recesses on one side of the sheet and as burr-shaped projections on the other side of the sheet.
  • a first flat contact surface is provided along the entire plate circumference in a first plane that borders the plate on a first side. In a second plane bordering the plate on the second side, two contact areas are provided, each of which is arranged around a passage opening.
  • the plates or sheets of the heat exchanger close together with the same sides or levels.
  • contact surfaces and contact areas always adjoin one another and are each tightly connected to one another, in particular smoldered or soldered to one another.
  • the substantially parallel beads or their longitudinal axes enclose an angle to a normal plane of the connecting line between the centers of the passage openings, which angle is less than 30 °, in particular less than 20 °, but is preferably essentially 15 °.
  • the beads start from the first level and have their ridge lines protruding from the rear in the second level.
  • the depressions between the ridge lines preferably have essentially the same shape as the beads, that is to say in cross section the parallel beads form a wavy line, in particular with half-waves in the shape of a trapezoid, the small side of which is rounded.
  • the rounding of the ridge line preferably has a small radius.
  • the plate packing of the heat exchanger constructed from the plates or sheets described above can be connected with its two first or second connection areas to first or second connection lines.
  • the design of the connection areas, the connection lines and the connections between them can be adapted to the respective use.
  • connections are preferably designed so that there is a clear separation between inflow and outflow for both fluids, or that both fluid volumes passed through the heat exchanger must flow completely through one channel system each. It can be expedient to design the two channel systems and their connection areas essentially the same, in particular as described for the second channels. If necessary, the complete penetration of a duct network is limited to one fluid and the other fluid forms a bath, for example, in which the plate packing with the closed duct system is opened. is taken. However, at least some of the bath fluid must flow through main channels in the plate pack, for example as a convection flow, in order to ensure a sufficiently large heat exchange.
  • the plate pack is preferably arranged partially in m or above a bath area for the first fluid
  • the liquid level in the working state is selected such that a large part of the plate packing or of the first channel network is filled with the liquid phase of the first fluid.
  • a large area of the contact area between the two fluids is used to heat the fluid to be evaporated.
  • Separator can be returned to the bathroom. Gas escaping in the liquid can rise through the first and / or second main channels into the gas area. Gas that arises when you enter the bath due to relaxation or in the bath can rise from the side of the plate pack through the bath into the gas area.
  • a particularly compact and effective evaporator or evaporation heat exchanger comprises a housing with a refrigerant attachment that has been attached for the liquid phase of the refrigerant and with a separator in the highest area of the housing above a liquid direction arranged refrigerant outlet for the gas phase of the refrigerant, as well as a plate pack with inlet and outlet connections for a heat transfer fluid through the housing.
  • the plate pack In the operating state, the plate pack is largely in the liquid phase of the refrigerant.
  • a relaxation chamber connects to the refrigerant inlet opening, from which gas escaping during the expansion can rise into the gas area above the liquid and can reach the refrigerant outlet opening there.
  • the liquid phase passes directly from the expansion chamber, if necessary, or via a level chamber into the bath area with the plate packing, where the liquid essentially fills the first channels up to the liquid level.
  • the coolant fluid flows through the second channels and loses the heat necessary for the evaporation of the refrigerant.
  • the liquid level is selected such that it lies below the condenser plate pack, at least in the working state, so that liquid drops occurring in the plate pack flow down through first and / or second main channels and out of the plate pack can exit.
  • the heat of condensation is absorbed by the recooling agent passed through the second channels of the condenser plate pack.
  • a simple and efficient refrigeration machine or heat pump can be put together.
  • the gas is led from the evaporator to the condenser via a compressor.
  • the liquid phase of the refrigerant reaches the evaporator from the condenser via a throttle valve.
  • the evaporator and the condenser are used as communicating vessels due to the line with the throttle are at standstill or when the compressor is switched off, both have a refrigerant level essentially at the same level.
  • the pressure in the compressor lowers the level in the condenser and raises it in the evaporator.
  • the relative vertical arrangement of the evaporator and the condenser is selected such that the refrigerant level in the evaporator and in the condenser is in a desired range relative to the plate packs in the operating state.
  • the condenser plate pack should lie essentially above the corresponding mirror and the evaporator plate pack should largely be in the liquid phase of the refrigerant. Due to the essentially identical structure of the evaporator and condenser, the refrigeration machine can be easily dimensioned, installed and regulated.
  • Heat exchangers according to the invention can be used in any devices for carrying out processes with a heat exchange step. Due to the essentially straight main channels for a first fluid, which can be aligned at a small angle to the vertical, escaping gas as well as heated liquid of a bath in the sense of a guided convection flow can flow out in these channels.
  • the main channels for the first fluid also allow good drainage of condensate drops.
  • Corresponding configurations of the connection areas make it possible to use the first and second channels according to the respective use with direct main channels between the connection areas or with connections via at least two differently oriented channel sections.
  • heat exchangers according to the invention also include fractional evaporation and distillation.
  • the heat exchangers according to the invention are thus versatile and have a simple structure.
  • FIG. 2- a section (II-II of FIG. 1) through four
  • FIG. 3 and 4 a view of first a) and second b) channels formed between two plates
  • FIG. 5 a longitudinal section through a heat exchanger
  • FIG. 6 cross sections through a heat exchanger, wherein a) through the plane AA and b) goes through BB according to FIG. 5
  • FIG. 7 a schematic illustration of a refrigeration machine
  • the plates are in the form of sheets la and lb in the form of circular disks with a ring-shaped contact surface 2a, 2b forming the outer edge of the disk, with two contact areas 4a, 4t> arranged around passage openings 3a, 3b and with parallel directed main channels formed by beads 5a, 5b, arranged on both sides.
  • the beads 5a extend over the entire sheet metal area, which is not designed as a contact surface 2a and not as a contact area 4a.
  • the beads 5a of an upper plate la project upwards from a second plane - the plane of the drawing - in which the contact surface 2a lies.
  • the beads 5b of a lower plate 1b project downward from the same plane, so that after the contact surface 2a of the upper plate 1a has been tightly connected to the contact surface 2b of the lower plate 1b, a second channel system is formed which is formed by the main channels Through openings 3a, 3b is accessible.
  • the axes of the main channels of the upper and lower plates la, lb are inclined at a first angle of 30 ° to one another.
  • the main channels which are open to one another, are connected to one another in the connection areas 6, in which they lie opposite one another.
  • the contact areas 4a, 4b are facing away from one another, so that a second fluid can enter or exit the second channel system between the illustrated sheets 1a and 1b through the through openings 3a, 3b.
  • the formation of the sheets la, lb and the second channel system formed by the main channels is further illustrated by the section shown in FIG. 2.
  • Fig. 2 shows a section (II-II, according to Fig. 1) through four sheets la, lb, lc, ld.
  • the view shown in FIG. 1 is labeled BB in FIG. 2, this level being referred to as the first level 7.
  • Another first level 7 'lies between the sheets 1b and 1c.
  • the above-mentioned second level is identified by 8 between the sheets la and 1b and by 8 'between the sheets 1c and 1d.
  • the sheets la and lb are in contact with one another with their contact surfaces 2a and 2b in the second plane 8.
  • the of the two Bumps 5a and 5b which go away from level 8 extend with their outer ridge lines 9a and 9b, like the contact areas 4a and 4b, to the first levels 7 and 7 '.
  • the second channel system is sealed off by the tight connection of the contact areas 4b and 4c, the sheets 1b and 1c.
  • the second chambers 10, which extend through the through openings, are connected to the second channels 11 formed between the two sheets 1a and 1b and form the second connection regions.
  • the main channels of the second channel system depart from the connecting areas 6 as half channels in the two directions of the beads, which is indicated by the hatching shown.
  • the first channels 12 are formed between the two sheets 1b and 1c, analogous to the second channels 11 on both sides of the first plane 7 ', half channels extend in the directions of the beads.
  • the first connection areas are arranged between the contact surfaces 2b and 2c.
  • the division of the annular first connection regions in an influx and p ⁇ nen Ausstr ⁇ mbe- yields rich by the operation, in particular by the Flus ⁇ stechniksspiegel of the bath or by di ⁇ fact that drops of condensate can only flow out through downward-feeling channels.
  • the first connection regions are delimited by tight connections between the contact surfaces 2b and 2c, or, as in the case of the second chambers, 10 clearly defined orsto chambers are formed.
  • Fig. 3 and Fig. 4 show the characteristically different flow paths for the two fluids for an evaporation heat exchanger using two differently oriented plate packs.
  • the first channel system 1? is trained that direct channels between the lower and the upper edge region of the plate pack, or the sheets 1, as first and second main channels 13 and 14 run over their entire length along a first and a second main direction.
  • the fluid level 15 determines in which channels the liquid phase of the first fluid enters and thus also the connection area in the liquid flows.
  • the upwardly open ends of the channels 13 and 14 open into the connection area into which the gas produced flows out.
  • first and / or second channels are only slightly inclined to the vertical and there is a direct connection between the inflow connection area or the channel area in the gas bubble and the outflow connection area, there is hardly any impeded flow 13a and 14a ensured by the first fluid
  • two partial flows in the adjoining first and second main channels flow crosswise past one another with boundary layer contact, which leads to a slight turbulence excitation in both partial flows Channel walls adjacent heated boundary layer dissolved and the heat transfer between the channel wall and the first fluid improved.
  • the two main directions run at an angle of less than 60 °, in particular less than 40 °, preferably of essentially 30 ° to one another.
  • the main directions can be aligned for operation such that at least one
  • Main direction to the vertical an angle that is less than 30 °, in particular less than 20 °.
  • the channels 14 are preferably oriented essentially vertically. 3, however, both main directions are inclined essentially by 15 ° to the vertical.
  • the first and / or the second main channels ensure the selected orientations a good rise of gas bubbles or, in the case of condensation heat exchangers, a good decrease in condensed liquid drops.
  • the second channels are constructed analogously to the first and include third and fourth main channels 16, 17 for the second fluid, which essentially run along a main direction and are closed at the ends by the contact surfaces 2a, 2b connected to one another.
  • the third and fourth main channels openly abut each other on both sides of the second connection levels 8, 8 '.
  • the second channel system that arises is constructed in the form of a network. Because the second connection areas 10 have small dimensions and are arranged on a line running transversely to the main directions, there are no main channels 16, 17 which connect the two connection areas 10 directly to one another.
  • the flow paths 18 extend over at least two, but preferably over at least three, main channel sections 16, 17 and the intersection areas 6 connecting them.
  • the second channel system is suitable for a fluid which does not undergo a phase transition, in particular for a liquid.
  • the second fluid must therefore travel a long way with strong ones between the two second connection regions 10
  • the duct network formed by the third and fourth main ducts 16, 17 is advantageous regardless of the orientation of the plate pack (FIGS. 3 and 4 b).
  • FIG. 5 and 6 show a particularly compact and effective evaporator or evaporative heat exchanger, which comprises a housing 20 with a laterally attached refrigerant inlet opening 21 for the liquid phase of the refrigerant and with a refrigerant outlet opening 23 for the gas phase of the refrigerant arranged in the highest housing area above a liquid separation device 22, as well as a plate packing 24 with inlet and outlet connections 25 for a heat transfer fluid through the housing 20.
  • the plate pack 24 is largely in the liquid phase of the refrigerant.
  • a expansion chamber 26 connects to the refrigerant inlet opening 21, from which gas escaping during the expansion flows via a partition wall 27 and under a deflection element 28 through the gas region 29 lying above the liquid and from there via lateral guide elements 22a of the separating device 22 can reach the refrigerant outlet opening 23.
  • the liquid phase passes directly from the relaxation chamber 26, or via a level chamber 30, which is formed between a housing wall 20a or the relaxation chamber 26 and the partition wall 27, a bath area 31 with the plate pack 24, where the liquid fills the first channels essentially up to a liquid level 32.
  • two filling bodies 39 are preferably arranged on both sides of the plate pack 24 between the latter and the inner wall of the housing 20.
  • a supply channel 40 remains free, through which the liquid can reach the first channels connected in parallel.
  • the refrigerant carrier fluid flows through the inlet and outlet connections 25 and through the second channels of the plate pack 24 and thereby loses the heat necessary for the evaporation of the refrigerant.
  • FIG. 7 shows a refrigeration machine or heat pump 33, with an evaporation heat exchanger 34 and a condensation heat exchanger 35, both of which comprise a plate packing described above.
  • the gas is led from the evaporator 34 to the condenser 35 via a compressor 36.
  • the liquid phase of the refrigerant passes from the condenser 35 via a throttle valve 37 or an orifice into the evaporator 34.
  • the evaporator 34 comprises refrigerant connections 25 and the condenser 35 recooling connections 38. It goes without saying that all known Ver ⁇ vaporizable refrigerant and all appropriate refrigerant and recooling agents can be used.
  • a refrigerant level is set substantially at the same level.
  • the pressure in the compressor 36 lowers the mirror 35a in the condenser 35 and raises the mirror 34a in the evaporator 34.
  • the relative vertical arrangement of the evaporator 34 and the condenser 35 is selected such that the refrigerant level in the evaporator and in the condenser 34a and 35a in the operating state lies in a desired range relative to the plate packs 24a and 24b.
  • the condenser plate pack 24b should lie essentially above the corresponding mirror 35a and the evaporator-l'larton pack 24a should largely lie in the liquid phase dt s refrigerant. Because the evaporator 34 and condenser 35 are of essentially the same construction, the refrigerator can be easily dimensioned, assembled and regulated.

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)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention concerne un échangeur de chaleur à plaques comportant un bloc de plaques (24) comprenant de premières et de secondes plaques (1a, 1b, 1c, 1d) disposées par rangées en alternance, entre lesquelles sont formés des premiers et des deuxièmes canaux (11, 12), reliés par l'intermédiaire de premières et de secondes zones de raccordement à de premières et de secondes ouvertures de raccordement (21, 23, 25). Les premières ouvertures de raccordement (21, 23), les premières zones de raccordement et les premiers canaux (12) sont entièrement séparés des deuxièmes (25, 11). Les premières et les secondes plaques (1a, 1b, 1c, 1d) comportent chacune de part et d'autre une pluralité de canaux principaux (13, 17; 14, 16) essentiellement droits, alignés parallèlement dans chaque plaque (1a, 1b, 1c, 1d). Les premiers (12) et les deuxièmes (11) canaux comprennent des premiers et des deuxièmes canaux principaux (13, 14) et des troisièmes et des quatrièmes canaux principaux (16, 17) qui forment conjointement un premier angle et sont formés de part et d'autre d'un premier (7, 7') et d'un deuxième (8, 8') plan de jonction, sous forme de demi-canaux ouverts en direction du plan de jonction. Les quatrièmes (17) et les deuxièmes canaux principaux (14) sont formés sur une des faces d'une première (1b, 1d) et d'une seconde (1a, 1c) plaque, et les premiers (13) et les troisièmes canaux principaux (16) sont formés sur l'autre face. Les plaques sont des plaques de tôle dont les canaux principaux situés de part et d'autre se présentent sous forme de moulures (5a, 5b) qui apparaissent sous forme de cavités sur une face des plaques de tôle et sous forme de parties saillantes de type arête sur l'autre face. Sur une des faces des plaques de tôle, il est prévu une surface de contact (2a, 2b, 2c, 2d) le long de la périphérie et deux zones de contact (4a, 4b, 4c, 4d) comprenant chacune un orifice de passage sur l'autre face de la plaque de tôle, de manière que le fait de réunir des plaques de tôle ayant des côtés ou des plans identiques permette d'obtenir dans tous les cas des surfaces de contact (2a, 2b, 2c, 2d) et des zones de contact (4a, 4b, 4c, 4d) alternées, aboutées les unes aux autres et interconnectées de manière étanche, notamment par soudage ou brasage, afin de séparer de manière étanche les premiers et les deuxièmes canaux (12, 11).
PCT/CH1997/000195 1996-05-24 1997-05-20 Echangeur de chaleur a plaques WO1997045689A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE59701152T DE59701152D1 (de) 1996-05-24 1997-05-20 Wärmetauscher und Vorrichtung zum Durchführen eines Kreisprozesses
AT97920477T ATE189924T1 (de) 1996-05-24 1997-05-20 Wärmetauscher und vorrichtung zum durchführen eines kreisprozesses
EP97920477A EP0901602B1 (fr) 1996-05-24 1997-05-20 Echangeur de chaleur et appareil pour réaliser un cycle réversible

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH131496 1996-05-24
CH1314/96 1996-05-24

Publications (1)

Publication Number Publication Date
WO1997045689A1 true WO1997045689A1 (fr) 1997-12-04

Family

ID=4207550

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CH1997/000195 WO1997045689A1 (fr) 1996-05-24 1997-05-20 Echangeur de chaleur a plaques

Country Status (4)

Country Link
EP (1) EP0901602B1 (fr)
AT (1) ATE189924T1 (fr)
DE (1) DE59701152D1 (fr)
WO (1) WO1997045689A1 (fr)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999045332A1 (fr) * 1998-03-04 1999-09-10 Vahterus Oy Plaque d'echangeur thermique et echangeur thermique a plaques
WO2002016852A1 (fr) * 2000-08-23 2002-02-28 Vahterus Oy Echangeur thermique a structure de plaques
WO2002018861A1 (fr) 2000-08-28 2002-03-07 Mueller Regula Echangeur de chaleur
WO2003031896A1 (fr) * 2001-10-09 2003-04-17 Vahterus Oy Echangeur de chaleur soude a structure en plaques
WO2003060411A1 (fr) * 2002-01-17 2003-07-24 York Refrigeration Aps Evaporateur immerge a echangeur thermique integre
WO2004090450A1 (fr) * 2003-04-08 2004-10-21 Vahterus Oy Echangeur de chaleur a plaques et plaque de guidage du flux
WO2004111564A1 (fr) * 2003-06-18 2004-12-23 Alfa Laval Corporate Ab Ensemble de plaques
US7004237B2 (en) 2001-06-29 2006-02-28 Delaware Capital Formation, Inc. Shell and plate heat exchanger
WO2007045719A1 (fr) * 2005-10-20 2007-04-26 Vahterus Oy Echangeur de chaleur a plaques et procede de construction d'un echangeur de chaleur a plaques resistant a la pression
EP1811258A2 (fr) 2001-12-27 2007-07-25 Vahterus Oy Amélioration de l'échange thermique d'une plaque circulaire d'échangeur de chaleur
WO2007057025A3 (fr) * 2005-11-21 2007-09-13 York Denmarks Aps Systeme de refroidissement avec condenseur integre et soupape de dilatation
US8453721B2 (en) 2007-01-31 2013-06-04 Tranter, Inc. Seals for a stacked-plate heat exchanger
WO2013060939A3 (fr) * 2011-10-25 2013-06-20 Vahterus Oy Échangeur thermique à plaques
CN104334983A (zh) * 2012-04-04 2015-02-04 瓦特鲁斯公司 用于汽化介质和分离液滴和用于冷凝介质的设备
EP2843324A1 (fr) 2013-08-27 2015-03-04 Johnson Controls Denmark ApS Échangeur de chaleur calandre-plaque et utilisation d'un tel échangeur de chaleur
DE102007021726B4 (de) * 2006-05-09 2015-06-18 Modine Manufacturing Co. Dualer Plattenwärmetauscher mit gestapelten Platten und zwei Durchläufen
JP2015121396A (ja) * 2013-11-19 2015-07-02 株式会社前川製作所 冷媒熱交換器
EP3372938A1 (fr) * 2017-03-10 2018-09-12 Alfa Laval Corporate AB Ensemble de plaques utilisant une plaque d'échangeur de chaleur avec canal de drainage intégré et un échangeur de chaleur comportant un tel ensemble de plaques

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004022433B4 (de) * 2004-05-06 2007-01-04 Joachim Schult Profilierte Wärmeübertragungsplatte für einen geschweissten Wärmeüberträger
CN106885396B (zh) * 2015-12-15 2019-07-19 丹佛斯微通道换热器（嘉兴）有限公司 入口整流结构和板式换热器

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1930815A1 (de) * 1968-06-26 1970-04-16 Air Preheater Platten-Waermetauscher
WO1995017272A1 (fr) * 1993-12-20 1995-06-29 Mauri Kontu Echangeur de chaleur a plaques et son procede de fabrication

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1930815A1 (de) * 1968-06-26 1970-04-16 Air Preheater Platten-Waermetauscher
WO1995017272A1 (fr) * 1993-12-20 1995-06-29 Mauri Kontu Echangeur de chaleur a plaques et son procede de fabrication

Cited By (39)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999045332A1 (fr) * 1998-03-04 1999-09-10 Vahterus Oy Plaque d'echangeur thermique et echangeur thermique a plaques
WO2002016852A1 (fr) * 2000-08-23 2002-02-28 Vahterus Oy Echangeur thermique a structure de plaques
KR100829902B1 (ko) 2000-08-23 2008-05-16 파테루스 오와이 플레이트 구조를 갖는 열교환기
US6918433B2 (en) 2000-08-23 2005-07-19 Vahterus Oy Heat exchanger with plate structure
CN1295473C (zh) * 2000-08-23 2007-01-17 瓦特鲁斯公司 带板结构的热交换器
WO2002018861A1 (fr) 2000-08-28 2002-03-07 Mueller Regula Echangeur de chaleur
US7004237B2 (en) 2001-06-29 2006-02-28 Delaware Capital Formation, Inc. Shell and plate heat exchanger
US7204300B2 (en) 2001-10-09 2007-04-17 Vahterus Oy Welded heat exchanger with plate structure
WO2003031896A1 (fr) * 2001-10-09 2003-04-17 Vahterus Oy Echangeur de chaleur soude a structure en plaques
CN100359278C (zh) * 2001-10-09 2008-01-02 瓦特鲁斯公司 带有板结构的焊接热交换器
EP1811258A2 (fr) 2001-12-27 2007-07-25 Vahterus Oy Amélioration de l'échange thermique d'une plaque circulaire d'échangeur de chaleur
US7472563B2 (en) 2002-01-17 2009-01-06 Alfa Laval Corporate Ab Submerged evaporator with integrated heat exchanger
CN1308643C (zh) * 2002-01-17 2007-04-04 阿尔法·拉瓦尔股份公司 包括沉入式蒸发器的壳体
WO2003060411A1 (fr) * 2002-01-17 2003-07-24 York Refrigeration Aps Evaporateur immerge a echangeur thermique integre
EP1479985A3 (fr) * 2002-01-17 2009-04-29 Alfa Laval Corporate AB Echangeur de chaleur à plaques pour utilisation dans un casing en tant qu'évaporateur immergé
US7347253B2 (en) 2003-04-08 2008-03-25 Vahterus Oy Plate heat exchanger and flow guide plate
WO2004090450A1 (fr) * 2003-04-08 2004-10-21 Vahterus Oy Echangeur de chaleur a plaques et plaque de guidage du flux
KR101113078B1 (ko) * 2003-04-08 2012-06-12 파테루스 오와이 플레이트 열 교환기 및 유동 가이드 플레이트
WO2004111564A1 (fr) * 2003-06-18 2004-12-23 Alfa Laval Corporate Ab Ensemble de plaques
US7594538B2 (en) 2003-06-18 2009-09-29 Alfa Laval Corporate Ab Plate package
WO2007045719A1 (fr) * 2005-10-20 2007-04-26 Vahterus Oy Echangeur de chaleur a plaques et procede de construction d'un echangeur de chaleur a plaques resistant a la pression
WO2007057025A3 (fr) * 2005-11-21 2007-09-13 York Denmarks Aps Systeme de refroidissement avec condenseur integre et soupape de dilatation
DE102007021726B4 (de) * 2006-05-09 2015-06-18 Modine Manufacturing Co. Dualer Plattenwärmetauscher mit gestapelten Platten und zwei Durchläufen
US8453721B2 (en) 2007-01-31 2013-06-04 Tranter, Inc. Seals for a stacked-plate heat exchanger
CN104053967A (zh) * 2011-10-25 2014-09-17 瓦特鲁斯公司 板式换热器
WO2013060939A3 (fr) * 2011-10-25 2013-06-20 Vahterus Oy Échangeur thermique à plaques
US9989319B2 (en) 2011-10-25 2018-06-05 Vahterus Oy Plate heat exchanger
US20140311723A1 (en) * 2011-10-25 2014-10-23 Vahterus Oy Plate heat exchanger
CN104334983A (zh) * 2012-04-04 2015-02-04 瓦特鲁斯公司 用于汽化介质和分离液滴和用于冷凝介质的设备
CN105473958A (zh) * 2013-08-27 2016-04-06 江森控制丹麦有限公司 一种壳板式热交换器及壳板式热交换器的使用
WO2015028021A1 (fr) 2013-08-27 2015-03-05 Johnson Controls Denmark Aps Échangeur de chaleur à plaques et calandre et utilisation d'un échangeur de chaleur à plaques et calandre
EP2843324A1 (fr) 2013-08-27 2015-03-04 Johnson Controls Denmark ApS Échangeur de chaleur calandre-plaque et utilisation d'un tel échangeur de chaleur
JP2015121396A (ja) * 2013-11-19 2015-07-02 株式会社前川製作所 冷媒熱交換器
EP3372938A1 (fr) * 2017-03-10 2018-09-12 Alfa Laval Corporate AB Ensemble de plaques utilisant une plaque d'échangeur de chaleur avec canal de drainage intégré et un échangeur de chaleur comportant un tel ensemble de plaques
WO2018162201A1 (fr) * 2017-03-10 2018-09-13 Alfa Laval Corporate Ab Groupement de plaques faisant appel à une plaque d'échangeur de chaleur à canal d'évacuation intégré, et échangeur de chaleur doté dudit groupement de plaques
TWI673460B (zh) * 2017-03-10 2019-10-01 瑞典商阿爾法拉瓦公司 使用具有整合式排水通道之熱交換器板的板封裝及包含此種板封裝的熱交換器
CN110382988A (zh) * 2017-03-10 2019-10-25 阿法拉伐股份有限公司 使用带有整体排出通道的换热器板的板组和包括此板组的换热器
JP2020506366A (ja) * 2017-03-10 2020-02-27 アルファ−ラヴァル・コーポレート・アーベー 一体化された排出チャネルを備えた熱交換プレート使用したプレート・パッケージおよびそのようなプレート・パッケージを含む熱交換器
US11371781B2 (en) 2017-03-10 2022-06-28 Alfa Laval Corporate Ab Plate package using a heat exchanger plate with integrated draining channel and a heat exchanger including such plate package

Also Published As

Publication number Publication date
EP0901602A1 (fr) 1999-03-17
EP0901602B1 (fr) 2000-02-23
DE59701152D1 (de) 2000-03-30
ATE189924T1 (de) 2000-03-15

Similar Documents

Publication Publication Date Title
WO1997045689A1 (fr) Echangeur de chaleur a plaques
EP0131270B1 (fr) Absorbeur utilisant une matière solide pour un cycle d'absorption
EP0706633B1 (fr) Echangeur de chaleur a plaques avec dispositif permettant de repartir des agents frigorigenes
DE69626295T2 (de) Plattenwärmetauscher
DE69409647T2 (de) Plattenwärmetauscher
EP1287302B1 (fr) Condenseur a bain a plusieurs etages
DE69406847T2 (de) Kühleinheit und Abflussbehälter für Klimaanlagen
DE69922984T2 (de) Plattenwärmetauscher
DE3017701C2 (de) Plattenwärmetauscher in Stapelbauweise für mindestens drei Wärmetauschermedien
DE69102755T2 (de) Plattenverdampfer.
DE3856032T2 (de) Wärmetauscher mit verbesserter Kondensatsammlung
DE2657308C3 (de) Querstrom-Wärmetauscher, mit einer Mehrzahl im wesentlichen identischer Platten, welche parallele Strömungswege bilden
DE69818488T2 (de) Sammelbehälter
DE69808160T2 (de) Kühlmittelverdampfer mit mehrere Röhren
DE10328746A1 (de) Vorrichtung zum mehrstufigen Wärmeaustausch und Verfahren zur Herstellung einer derartigen Vorrichtung
DE102006018681A1 (de) Wärmetauscher für ein Fahrzeug
DE112005000797T5 (de) Wärmetauscher
DE19815584A1 (de) Zusammengesetzter Tankkörper eines Aufnahmetanks
DE10220532A1 (de) Wärmetauscher
DE68905070T2 (de) Frostfreier Wärmeaustauscher.
DE19730136A1 (de) Gerät der Klimatechnik sowie dessen Komponenten
DE102005046346A1 (de) Integrierter Kondensatorölkühler mit einem Zwischenbehälter/Trockner
DE102007034710B4 (de) Zweistufiger Absorptionskühler
DE102020007211A1 (de) Adsorptionskältevorrichtung und Verfahren zum Erzeugen von Adsorptionskälte aus Wärme
DE112005001295T5 (de) Wärmetauscher

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): BR CA CN JP US

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): AT BE CH DE DK ES FI FR GB GR IE IT LU MC NL PT SE

DFPE Request for preliminary examination filed prior to expiration of 19th month from priority date (pct application filed before 20040101)
121 Ep: the epo has been informed by wipo that ep was designated in this application
WWE Wipo information: entry into national phase

Ref document number: 1997920477

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: JP

Ref document number: 97541330

Format of ref document f/p: F

WWP Wipo information: published in national office

Ref document number: 1997920477

Country of ref document: EP

NENP Non-entry into the national phase

Ref country code: CA

WWG Wipo information: grant in national office

Ref document number: 1997920477

Country of ref document: EP

点击 这是indexloc提供的php浏览器服务，不要输入任何密码和下载