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EP1899669A2 - Plate heat exchanger with exchanging structure forming several channels in a passage - Google Patents

Plate heat exchanger with exchanging structure forming several channels in a passage

Info

Publication number
EP1899669A2
EP1899669A2 EP06778947A EP06778947A EP1899669A2 EP 1899669 A2 EP1899669 A2 EP 1899669A2 EP 06778947 A EP06778947 A EP 06778947A EP 06778947 A EP06778947 A EP 06778947A EP 1899669 A2 EP1899669 A2 EP 1899669A2
Authority
EP
European Patent Office
Prior art keywords
passage
channels
passages
exchange
channel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06778947A
Other languages
German (de)
French (fr)
Other versions
EP1899669B1 (en
Inventor
Frédéric Crayssac
Sophie Deschodt
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.)
Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
Original Assignee
Air Liquide SA
LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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 Air Liquide SA, LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude filed Critical Air Liquide SA
Publication of EP1899669A2 publication Critical patent/EP1899669A2/en
Application granted granted Critical
Publication of EP1899669B1 publication Critical patent/EP1899669B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J3/00—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification
    • F25J3/02—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream
    • F25J3/04—Processes or apparatus for separating the constituents of gaseous or liquefied gaseous mixtures involving the use of liquefaction or solidification by rectification, i.e. by continuous interchange of heat and material between a vapour stream and a liquid stream for air
    • F25J3/04763—Start-up or control of the process; Details of the apparatus used
    • F25J3/04866—Construction and layout of air fractionation equipments, e.g. valves, machines
    • F25J3/04975—Construction and layout of air fractionation equipments, e.g. valves, machines adapted for special use of the air fractionation unit, e.g. transportable devices by truck or small scale use
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
    • F25J5/002—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J5/00—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants
    • F25J5/002—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger
    • F25J5/005—Arrangements of cold exchangers or cold accumulators in separation or liquefaction plants for continuously recuperating cold, i.e. in a so-called recuperative heat exchanger in a reboiler-condenser, e.g. within a column
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0062—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by spaced plates with inserted elements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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
    • 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
    • F28F3/025—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being corrugated, 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2250/00—Details related to the use of reboiler-condensers
    • F25J2250/02—Bath type boiler-condenser using thermo-siphon effect, e.g. with natural or forced circulation or pool boiling, i.e. core-in-kettle heat exchanger
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2250/00—Details related to the use of reboiler-condensers
    • F25J2250/04—Down-flowing type boiler-condenser, i.e. with evaporation of a falling liquid film
    • 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
    • F25J—LIQUEFACTION, SOLIDIFICATION OR SEPARATION OF GASES OR GASEOUS OR LIQUEFIED GASEOUS MIXTURES BY PRESSURE AND COLD TREATMENT OR BY BRINGING THEM INTO THE SUPERCRITICAL STATE
    • F25J2290/00—Other details not covered by groups F25J2200/00 - F25J2280/00
    • F25J2290/20—Particular dimensions; Small scale or microdevices
    • 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
    • F28D2021/0033—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for cryogenic applications
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2260/00—Heat exchangers or heat exchange elements having special size, e.g. microstructures
    • F28F2260/02—Heat exchangers or heat exchange elements having special size, e.g. microstructures having microchannels

Definitions

  • the present invention relates to a plate and fin heat exchanger.
  • plate and fin heat exchangers there are different types of plate and fin heat exchangers, each adapted to a field of use.
  • the invention is advantageously applied to a heat exchanger of an air separation unit or H 2 / CO (hydrogen / carbon monoxide) mixtures by cryogenic distillation.
  • This exchanger can be a main exchange line of an air separation apparatus, which cools the incoming air by indirect heat exchange with the cold products from the distillation column, subcooler or vaporizer. condenser.
  • the technology commonly used for these exchangers is that of aluminum exchangers with brazed plates and fins, which make it possible to obtain very compact members with a large exchange surface.
  • exchangers consist of plates between which are inserted waves or fins, thus forming a stack of so-called “cold” passages and so-called “hot” passages.
  • Commonly used exchange waves are straight waves, perforated waves, and partial offset or "serrated” waves.
  • h (mm) height of the wave (from 3 to 10 mm).
  • e (mm) thickness of the wave (from 0.2 to 0.6 mm).
  • n (m “1 or inch “ 1 ) number of waves per unit length (from 177 to
  • the hydraulic diameters (Dh) of the waves conventionally used in soldered plate and fin exchangers are between 1 and 6 mm.
  • These exchange waves are currently formed using a press.
  • Various means make it possible to increase the exchange surface.
  • the exchange surface that separates two fluids consists of a so-called “primary” surface corresponding to the flat surface between the two fluids and a so-called “secondary” surface generally consisting of fins perpendicular to the primary surface and forming thus an exchange wave. It is the number of inserted fins (density of the wave) and the height of the fins which create the increase of the exchange surface.
  • the denser the wave the larger the exchange surface.
  • the press tool used to manufacture the wave makes it possible to obtain maximum densities of 1023 to 1102 waves per meter.
  • the density of the selected wave may be smaller when it is preferable to limit the pressure drops.
  • safety constraints limit the number of waves per meter to values well below the maximum values that can be manufactured.
  • the fins have a temperature gradient. Beyond a certain height of fin (wave), the area in the middle of the fin exchange significantly less well. There is therefore an optimum wave height corresponding to an optimum fin coefficient value.
  • the wavelengths commonly used vary from 3 to 10 mm. It is also possible to increase the exchange coefficient.
  • This turbulence can be generated by a modification of the shape of the channels or by the insertion of obstacles generating turbulence (ex: perforated straight wave, partial offset or "serrated”, with sinuous generators or “herringbone”, with shutters, insertion of mini-fins, windows, ).
  • nucleation sites are micro-cavities of various sizes and shapes (re-entrant cavities) present on the surface or through a porous layer.
  • the thickness of the liquid film deteriorates the exchange coefficient. It is therefore interesting to drain the liquid by the presence of grooves, perforations or reliefs.
  • micro-exchangers are exchangers having channels of hydraulic diameters smaller than one millimeter. The reduction in the size of the channels makes it possible to develop the heat exchange surface (gain in compactness of the apparatus). The exchange coefficient then becomes practically inversely proportional to the hydraulic diameter.
  • microchannels such as: 1 mm ⁇ Dh ⁇ 3mm (corresponding to the Dh values of the current wave), c Mini-channels such as: 200 ⁇ m ⁇ Dh ⁇ 1 mm c Micro-channels such as: Dh ⁇ 200 ⁇ m.
  • EP-A-1008826 discloses a plate heat exchanger in which at least one of the passages contains closed tube-shaped auxiliary passages, the maximum width of which is greater than 50% of the distance between two adjacent plates.
  • ⁇ kxSxAT
  • the improvement of the exchangers can only be carried out by increasing the exchange coefficient (k) and / or by increasing the exchange surface (S).
  • micro-channel type technology is very expensive (channel micro-machining) and remains today reserved for very small heat exchangers: it does not currently concern applications, such as air separation in which the flow rate and the difference in temperature are important.
  • the proposed solution aims to increase the exchange surface by incorporating the already existing surfaces (called “primary” and “secondary”) a third exchange surface called “tertiary” surface.
  • a brazed plate heat exchanger of the type comprising a stack of parallel plates which define a plurality of generally flat fluid circulation passages, closing bars which delimit these passages. and dispensing means for dispensing a fluid at each passage of a first series of passages and means for sending another fluid to a second series of passages in which at least one passage contains at least one organized exchange structure which forms a plurality of channels in the width of the passage, each channel being in contact with either at least two other channels or at least one other channel and a plate and characterized in that the structure also forms at least three channels, preferably at least five channels, in the height of the passage.
  • each channel is in contact with at least three other channels or a plate and two other channels.
  • the plate may be a plate defining a passage or a secondary plate located in the passage. According to other optional aspects:
  • the structure is composed of a plurality of cylinders
  • the structure is formed of a superposition of exchange waves, each pair of adjacent exchange waves possibly being separated by a secondary plate;
  • the structure is formed of a single body containing a plurality of channels
  • a channel has a hydraulic diameter of between 1 and 6 mm; a channel has a hydraulic diameter of between 200 ⁇ m and 1 mm;
  • a channel has a hydraulic diameter of less than 200 ⁇ m
  • the channels have a circular, oval, square, rectangular, triangular or diamond-shaped section.
  • an air separation apparatus in which a main exchange line and / or a vaporizer-condenser and / or a subcooler is an exchanger as described above.
  • FIGS. 3A, 4A and 5A show an exchanger passage seen in the fluid flow direction according to the prior art
  • FIGS. 3B, 4B, 4C and 5B show an exchanger passage seen in the direction of flow. fluids according to the invention.
  • the heat exchanger 1 shown consists of a stack of parallel rectangular plates 2 all identical, which define between them a plurality of passages for fluids to put in indirect heat exchange relationship.
  • these passages are successively and cyclically passages 3 for a first fluid, 4 for a second fluid and 5 for a third fluid. It will be understood that the invention covers two-fluid exchangers only or any number of fluids.
  • Each passage 3 to 5 is bordered by closing bars 6 which delimit it leaving free windows 7 input / output of the corresponding fluid.
  • wave-waves or corrugated fins 8 serving both thermal fins, spacers between the plates, especially during brazing and to prevent any deformation of the plates during the implementation of fluids under pressure and guiding the flow of fluids.
  • the stack of plates, closing bars and spacer waves is generally made of aluminum or aluminum alloy and is assembled in a single operation by soldering in the oven.
  • Fluid inlet / outlet boxes 9, of generally semi-cylindrical shape, are then welded to the heat exchanger body thus produced so as to cover the rows of corresponding inlet / outlet windows, and they are connected to conduits 10 for supplying and evacuating fluids.
  • the channels can be formed using various techniques, as described in Anton GRUSS's "Micro heat exchangers" in Techniques de l'In deepur, 06-2002.
  • FIG. 3B The solution of FIG. 3B consists in replacing the conventionally used exchange wave of FIG. 3A by several exchange waves 13 of the same type but of smaller wavelength. These new waves inserted in the same passage of the exchanger are assembled using thin sheets covered with solder 13. These sheets called “tertiary surface sheet” constitute the added surface called “tertiary”. In the example there are two sheets separating three waves.
  • All commercially available wave types can be used by modifying and adapting only the wave height.
  • all the parameters constituting the geometry of a wave type are adjustable (thickness, density, perforation of the wave, etc.).
  • the other parameters are:
  • the hydraulic diameters are of the order of magnitude of the channel width of a conventional wave (1 / n-e).
  • n * number of waves on the height of a passage (with thicknesses of tertiary surface sheets of 0.2mm).
  • w width of a channel
  • h channel height of a channel.
  • the increase in the number of waves to be stacked in the exchanger causes an increase in the manufacturing cost thereof.
  • the installation cost remains the same.
  • FIG. 4B consists in replacing the conventionally used exchange wave of FIG. 4A by a structured wave 17 comprising numerous mini-channels 19 with a square section.
  • This wave can be manufactured by extrusion.
  • the extrusion manufacturing method makes it possible to imagine any type of channel section shape (rectangular, triangular, round, rhombic, ).
  • Figure 4C shows triangular section channels.
  • the main parameters are the height of the passage, the number of channels per passage height, the number of channels per meter of passage width and all the parameters which concern the geometric shape of the channels used (height, width, diameter of the channel ,. ..).
  • This method of manufacture also allows the possibility of inserting micro or mini fins inside the channels to further increase the exchange surface and / or drain a liquid.
  • the length of the channels (fluid exchange length) can be divided into several extruded wave modules spaced a few millimeters apart to allow inter-channel communication.
  • Dh hydraulic diameter of the channels
  • Dh is between 200 microns and 1 mm (minichannels).
  • the solution of Figure 5B is to replace the conventionally used exchange wave of Figure 5A with an adequate number of capillary tubes.
  • the arrangement of the capillary tubes is easily arranged because of their shape.
  • the capillary tubes are covered with solder to ensure the mechanical assembly of the assembly.
  • the adjustable parameters are the height of the passage, the diameter of the capillary tubes, the thickness of the capillary tubes or the number of capillary tubes per m 2 .
  • the diameter of the capillary corresponds to the maximum diameter in order to obtain a gain in exchange surface area compared to the conventional solution, a smaller diameter will give a much greater gain in exchange surface area.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

The invention concerns a heat exchanger with brazed plates comprising a stack of parallel plates defining a plurality of generally flat fluid circulating passages, closure bars which delimit said passages and distributing means for distributing a fluid to each passage of a first series of passages and means for conveying another fluid to a second series of passages wherein at least one passage contains organized exchanging structures (15) which form a plurality of channels (19) in the width of the passage and also at least three channels (19) in the height of the passage. The invention is useful for air separation by cryogenic distillation.

Description

Echangeur de chaleur à plaques avec structure d'échange formant plusieurs canaux dans un passagePlate heat exchanger with exchange structure forming several channels in a passage
La présente invention se rapporte à un echangeur de chaleur à plaques et ailettes.The present invention relates to a plate and fin heat exchanger.
Il existe différents types d'échangeurs de chaleur à plaques et ailettes, adaptés chacun à un domaine d'utilisation. En particulier, l'invention s'applique de façon avantageuse à un echangeur de chaleur d'une unité de séparation d'air ou de mélanges H2/CO (hydrogène/monoxyde de carbone) par distillation cryogénique.There are different types of plate and fin heat exchangers, each adapted to a field of use. In particular, the invention is advantageously applied to a heat exchanger of an air separation unit or H 2 / CO (hydrogen / carbon monoxide) mixtures by cryogenic distillation.
Cet echangeur peut être une ligne d'échange principale d'un appareil de séparation d'air, qui refroidit l'air entrant par échange de chaleur indirect avec les produits froids issus de la colonne de distillation, un sous-refroidisseur ou un vaporiseur/condenseur. La technologie couramment utilisée pour ces échangeurs est celle des échangeurs en aluminium à plaques et ailettes brasés, qui permettent d'obtenir des organes très compacts offrant une grande surface d'échange.This exchanger can be a main exchange line of an air separation apparatus, which cools the incoming air by indirect heat exchange with the cold products from the distillation column, subcooler or vaporizer. condenser. The technology commonly used for these exchangers is that of aluminum exchangers with brazed plates and fins, which make it possible to obtain very compact members with a large exchange surface.
Ces échangeurs sont constitués de plaques entre lesquelles sont insérées des ondes ou ailettes, formant ainsi un empilage de passages dits « froids » et de passages dits « chauds ».These exchangers consist of plates between which are inserted waves or fins, thus forming a stack of so-called "cold" passages and so-called "hot" passages.
Les ondes d'échange couramment utilisées sont des ondes droites, ondes perforées, et ondes à décalage partiel ou « serrated ».Commonly used exchange waves are straight waves, perforated waves, and partial offset or "serrated" waves.
Ces ondes se caractérisent à l'aide des paramètres suivants : h (mm) : hauteur de l'onde (de 3 à10 mm). e (mm) : épaisseur de l'onde (de 0,2 à 0,6 mm). n (m"1 ou pouce"1) : nombre d'ondes par unité de longueur (de 177 àThese waves are characterized by the following parameters: h (mm): height of the wave (from 3 to 10 mm). e (mm): thickness of the wave (from 0.2 to 0.6 mm). n (m "1 or inch " 1 ): number of waves per unit length (from 177 to
1102 ondes/m). perf (%) : taux de perforation (5% pour les ondes perforées). ls (mm) : longueur de décalage (pour les ondes à décalage partiel ou « serrated »).1102 waves / m). perf (%): perforation rate (5% for perforated waves). l s (mm): offset length (for partial offset or "serrated" waves).
Ainsi les diamètres hydrauliques (Dh) des ondes classiquement utilisées dans les échangeurs à plaques et ailettes brasées sont compris entre 1 et 6 mm. Ces ondes d'échange sont actuellement formées à l'aide d'une presse. Divers moyens permettent d'augmenter la surface d'échange. La surface d'échange qui sépare deux fluides, se compose d'une surface dite « primaire » correspondant à la surface plane entre les deux fluides et d'une surface dite « secondaire » généralement constituée d'ailettes perpendiculaires à la surface primaire et formant ainsi une onde d'échange. C'est le nombre d'ailettes insérées (densité de l'onde) et la hauteur des ailettes qui créent l'augmentation de la surface d'échange.Thus, the hydraulic diameters (Dh) of the waves conventionally used in soldered plate and fin exchangers are between 1 and 6 mm. These exchange waves are currently formed using a press. Various means make it possible to increase the exchange surface. The exchange surface that separates two fluids, consists of a so-called "primary" surface corresponding to the flat surface between the two fluids and a so-called "secondary" surface generally consisting of fins perpendicular to the primary surface and forming thus an exchange wave. It is the number of inserted fins (density of the wave) and the height of the fins which create the increase of the exchange surface.
Plus l'onde est dense, plus la surface d'échange est grande. Cependant il existe une limite de fabrication ou des contraintes dus au procédé. L'outil de presse utilisé pour fabriquer l'onde, permet d'obtenir des densités maximales de 1023 à 1102 ondes par mètre. La densité de l'onde sélectionnée peut être plus petite lorsqu'il est préférable de limiter les pertes de charge. De plus, dans certaines conditions de fonctionnement comme celui des vaporiseurs/condenseurs à bain, des contraintes liées à la sécurité limitent le nombre d'ondes par mètre à des valeurs bien inférieures aux valeurs maximales qui peuvent être fabriquées. Les ailettes présentent un gradient de température. Au-delà d'une certaine hauteur d'ailette (d'onde), la zone située au milieu de l'ailette échange nettement moins bien. Il existe donc une hauteur d'onde optimale correspondant à une valeur de coefficient d'ailette optimale. Les hauteurs d'onde couramment utilisées varient de 3 à 10 mm. II est également possible d'augmenter le coefficient d'échange.The denser the wave, the larger the exchange surface. However, there is a manufacturing limit or constraints due to the process. The press tool used to manufacture the wave, makes it possible to obtain maximum densities of 1023 to 1102 waves per meter. The density of the selected wave may be smaller when it is preferable to limit the pressure drops. In addition, under certain operating conditions such as bath vaporizers / condensers, safety constraints limit the number of waves per meter to values well below the maximum values that can be manufactured. The fins have a temperature gradient. Beyond a certain height of fin (wave), the area in the middle of the fin exchange significantly less well. There is therefore an optimum wave height corresponding to an optimum fin coefficient value. The wavelengths commonly used vary from 3 to 10 mm. It is also possible to increase the exchange coefficient.
Plus le fluide est turbulent, meilleur est le coefficient d'échange. Cette turbulence peut être générée par une modification de la forme des canaux ou par l'insertion d'obstacles générateurs de turbulence (ex : onde droite perforée, à décalage partiel ou « serrated », à génératrices sinueuses ou « herringbone », à persiennes, insertion de mini-ailettes, fenêtres, ...).The more turbulent the fluid, the better the exchange coefficient. This turbulence can be generated by a modification of the shape of the channels or by the insertion of obstacles generating turbulence (ex: perforated straight wave, partial offset or "serrated", with sinuous generators or "herringbone", with shutters, insertion of mini-fins, windows, ...).
Dans le cas de la vaporisation d'un fluide, une surface qui comporte un plus grand nombre de sites de nucléation présente un meilleur coefficient d'échange. Ces sites de nucléation sont des micro-cavités de diverses tailles et formes (cavités ré-entrantes) présents en surface ou au travers d'une couche poreuse. Dans le cas de la condensation d'un fluide, l'épaisseur du film liquide détériore le coefficient d'échange. Il est donc intéressant de drainer le liquide par la présence de rainures, de perforations ou de reliefs.In the case of the vaporization of a fluid, a surface that has a larger number of nucleation sites has a better exchange coefficient. These nucleation sites are micro-cavities of various sizes and shapes (re-entrant cavities) present on the surface or through a porous layer. In the case of the condensation of a fluid, the thickness of the liquid film deteriorates the exchange coefficient. It is therefore interesting to drain the liquid by the presence of grooves, perforations or reliefs.
Récemment il est apparu un type d'échangeurs appelés micro-échangeurs. II s'agit d'échangeurs ayant des canaux de diamètres hydrauliques inférieurs au millimètre. La diminution de la taille des canaux permet de développer la surface d'échange thermique (gain en compacité de l'appareil). Le coefficient d'échange devient alors pratiquement inversement proportionnel au diamètre hydraulique.Recently there appeared a type of exchangers called micro-exchangers. These are exchangers having channels of hydraulic diameters smaller than one millimeter. The reduction in the size of the channels makes it possible to develop the heat exchange surface (gain in compactness of the apparatus). The exchange coefficient then becomes practically inversely proportional to the hydraulic diameter.
S. Kandlikar dans "First International Conférence on microchannels and minichannels 2003, « Extending the applicability of the flow boiling corrélation to low Reynolds number flows in microchannels » propose la classification suivante, en fonction du diamètre hydraulique des canaux : c Mini-canaux tels que : 1 mm<Dh<3mm (correspondants aux grandeurs de Dh des ondes actuelles), c Mini-canaux tels que : 200μm<Dh<1 mm. c Micro-canaux tels que : Dh<200μm.S. Kandlikar in "First International Conference on microchannels and minichannels 2003," Extending the applicability of the flow boiling correlation to low Reynolds number flows in microchannels "proposes the following classification, depending on the hydraulic diameter of the channels: c Mini-channels such as : 1 mm <Dh <3mm (corresponding to the Dh values of the current wave), c Mini-channels such as: 200μm <Dh <1 mm c Micro-channels such as: Dh <200μm.
Pour les mini-canaux (200μm<Dh<3mm) : les lois des écoulements pour les conduites classiques s'appliquent encoreFor mini-channels (200μm <Dh <3mm): the flow laws for conventional pipes still apply
Pour les micro-canaux (Dh<200μm) : Les effets de surface prennent une importance considérable et les lois d'écoulement classiques ne s'appliquent plus.For micro-channels (Dh <200μm): Surface effects are of considerable importance and conventional flow laws no longer apply.
EP-A-1008826 décrit un échangeur à plaques dont au moins un des passages contient des passages auxiliaires fermés en forme de tube, dont la largeur maximale est supérieure à 50% de la distance entre deux plaques adjacentes.EP-A-1008826 discloses a plate heat exchanger in which at least one of the passages contains closed tube-shaped auxiliary passages, the maximum width of which is greater than 50% of the distance between two adjacent plates.
La quantité de flux échangée à travers un échangeur est donnée par la relation suivante : φ = kxSxAT Pour un ΔT donné, l'amélioration des échangeurs ne peut s'effectuer que par l'augmentation du coefficient d'échange (k) et/ou par l'augmentation de la surface d'échange (S).The quantity of flow exchanged through an exchanger is given by the following relation: φ = kxSxAT For a given ΔT, the improvement of the exchangers can only be carried out by increasing the exchange coefficient (k) and / or by increasing the exchange surface (S).
Dans le cas des échangeurs à plaques et ailettes brasées, l'augmentation de la surface d'échange par une surface dite « secondaire » atteint ses limites de part la fabrication et/ou des contraintes de procédé. L'augmentation du coefficient d'échange par la création de turbulences est intéressante mais présente deux contraintes principales : • une augmentation des pertes de charge induite par l'augmentation des turbulences.In the case of brazed plate and fin exchangers, the increase of the exchange surface by a so-called "secondary" surface reaches its limits due to manufacturing and / or process constraints. The increase of the exchange coefficient by the creation of turbulence is interesting but presents two main constraints: • an increase in pressure losses induced by the increase in turbulence.
• une augmentation du coût de fabrication dû à la complexité des géométries. Ainsi, la création d'une nouvelle forme d'onde ne peut engendrer des gains de coefficient d'échange nettement meilleurs par rapport aux ondes déjà existantes. Quant à la création de sites de nucléation et au drainage de liquide, ces deux méthodes ne concernent qu'un type particulier d'échange à savoir la vaporisation ou la condensation. II semble donc difficile d'améliorer fortement les échangeurs à plaques et ailettes brasées en utilisant les mêmes axes de développement que ceux décrits précédemment.• an increase in the manufacturing cost due to the complexity of the geometries. Thus, the creation of a new waveform can not generate much better exchange coefficient gains compared to existing waves. As regards the creation of nucleation sites and liquid drainage, these two methods only concern a particular type of exchange, namely vaporization or condensation. It therefore seems difficult to greatly improve the brazed plate and fin exchangers using the same axes of development as those described above.
En outre, la technologie type micro-canaux est très coûteuse (microusinage des canaux) et reste aujourd'hui réservée à des échangeurs de très petite dimension : elle ne concerne pas aujourd'hui les applications, telle que la séparation d'air dans lesquelles le débit et la différence de température sont importants.In addition, micro-channel type technology is very expensive (channel micro-machining) and remains today reserved for very small heat exchangers: it does not currently concern applications, such as air separation in which the flow rate and the difference in temperature are important.
La solution proposée vise à augmenter la surface d'échange en incorporant aux surfaces déjà existantes (dites « primaire » et « secondaire ») une troisième surface d'échange dite surface « tertiaire ».The proposed solution aims to increase the exchange surface by incorporating the already existing surfaces (called "primary" and "secondary") a third exchange surface called "tertiary" surface.
Nous proposons trois dispositifs qui permettent d'ajouter une surface dite « tertiaire » aux ondes d'échange actuellement utilisées dans les échangeurs à plaques et ailettes brasées :We propose three devices that allow to add a so-called "tertiary" surface to the exchange waves currently used in brazed plate and fin exchangers:
• passage d'échange « multi-ondes » • ondes d'échange « mini-canaux », ondes extrudées• "multi-wave" exchange passage • "mini-channel" exchange waves, extruded waves
• ondes d'échange « mini-canaux », tubes capillaires• "mini-channel" exchange waves, capillary tubes
Selon un objet de l'invention, il est prévu un échangeur de chaleur à plaques brasées, du type comprenant un empilement de plaques parallèles qui définissent une pluralité de passages de circulation de fluide de forme générale plate, des barres de fermeture qui délimitent ces passages et des moyens de distribution pour distribuer un fluide à chaque passage d'une première série de passages et des moyens pour envoyer un autre fluide à une deuxième série de passages dans lequel au moins un passage contient au moins une structure d'échange organisée qui forme une pluralité de canaux dans la largeur du passage, chaque canal étant en contact avec soit au moins deux autres canaux soit au moins un autre canal et une plaque et caractérisé en ce que la structure forme également au moins trois canaux, de préférence au moins cinq canaux, dans la hauteur du passage.According to one object of the invention, there is provided a brazed plate heat exchanger, of the type comprising a stack of parallel plates which define a plurality of generally flat fluid circulation passages, closing bars which delimit these passages. and dispensing means for dispensing a fluid at each passage of a first series of passages and means for sending another fluid to a second series of passages in which at least one passage contains at least one organized exchange structure which forms a plurality of channels in the width of the passage, each channel being in contact with either at least two other channels or at least one other channel and a plate and characterized in that the structure also forms at least three channels, preferably at least five channels, in the height of the passage.
De préférence chaque canal est en contact avec au moins trois autres canaux ou une plaque et deux autres canaux. La plaque peut être une plaque définissant un passage ou une plaque secondaire située dans le passage. Selon d'autres aspects facultatifs :Preferably each channel is in contact with at least three other channels or a plate and two other channels. The plate may be a plate defining a passage or a secondary plate located in the passage. According to other optional aspects:
- la structure est composée d'une pluralité de cylindres ;the structure is composed of a plurality of cylinders;
- à l'intérieur d'un passage, il y a au moins une plaque secondaire de forme générale plate parallèle aux plaques définissant les passages ;- Inside a passage, there is at least one secondary plate of generally flat shape parallel to the plates defining the passages;
- la structure est formée d'une superposition d'ondes d'échange, chaque paire d'ondes d'échange adjacentes étant éventuellement séparée par une plaque secondaire ;the structure is formed of a superposition of exchange waves, each pair of adjacent exchange waves possibly being separated by a secondary plate;
- la structure est formée d'un corps unique contenant une pluralité de canaux ;the structure is formed of a single body containing a plurality of channels;
- un canal a un diamètre hydraulique d'entre 1 et 6 mm ; - un canal a un diamètre hydraulique entre 200 μm et 1 mm ;a channel has a hydraulic diameter of between 1 and 6 mm; a channel has a hydraulic diameter of between 200 μm and 1 mm;
- un canal a un diamètre hydraulique inférieur à 200 μm ;a channel has a hydraulic diameter of less than 200 μm;
- un passage a une hauteur d'entre 3 et 18 mm ;a passage at a height of between 3 and 18 mm;
- les canaux ont une section circulaire, ovale, carrée, rectangulaire, triangulaire ou en losange. Selon une autre objet de l'invention, il est prévu un appareil de séparation cryogénique comprenant au moins un échangeur tel que décrit ci-dessus.the channels have a circular, oval, square, rectangular, triangular or diamond-shaped section. According to another object of the invention, there is provided a cryogenic separation apparatus comprising at least one exchanger as described above.
Selon une autre objet de l'invention, il est prévu un appareil de séparation d'air dans lequel une ligne d'échange principale et/ou un vaporiseur-condenseur et/ou un sous-refroidisseur est un échangeur tel que décrit ci-dessus. L'invention sera décrite en plus de détail en se référant aux dessins dans lesquels :According to another object of the invention, there is provided an air separation apparatus in which a main exchange line and / or a vaporizer-condenser and / or a subcooler is an exchanger as described above. . The invention will be described in more detail with reference to the drawings in which:
La Figure 2 des dessins annexés représente en perspective, avec des arrachements partiels, un exemple d'un tel échangeur de chaleur, de structure classique, auquel s'applique l'invention. Les Figures 3A, 4A et 5A représentent un passage d'échangeur vu dans le sens d'écoulement des fluides selon l'art antérieur et les Figures 3B, 4B, 4C et 5B représentent un passage d'échangeur vu dans le sens d'écoulement des fluides selon l'invention. Dans la Figure 2, l'échangeur de chaleur 1 représenté est constitué d'un empilement de plaques rectangulaires parallèles 2 toutes identiques, qui définissent entre elles une pluralité de passages pour des fluides à mettre en relation d'échange thermique indirect. Dans l'exemple représenté, ces passages sont successivement et cycliquement des passages 3 pour un premier fluide, 4 pour un deuxième fluide et 5 pour un troisième fluide. Il sera compris que l'invention couvre des échangeurs à deux fluides seulement ou à n'importe lequel nombre de fluides.Figure 2 of the accompanying drawings shows in perspective, with partial cutaway, an example of such a heat exchanger of conventional structure, to which the invention applies. FIGS. 3A, 4A and 5A show an exchanger passage seen in the fluid flow direction according to the prior art, and FIGS. 3B, 4B, 4C and 5B show an exchanger passage seen in the direction of flow. fluids according to the invention. In Figure 2, the heat exchanger 1 shown consists of a stack of parallel rectangular plates 2 all identical, which define between them a plurality of passages for fluids to put in indirect heat exchange relationship. In the example shown, these passages are successively and cyclically passages 3 for a first fluid, 4 for a second fluid and 5 for a third fluid. It will be understood that the invention covers two-fluid exchangers only or any number of fluids.
Chaque passage 3 à 5 est bordé de barres de fermeture 6 qui le délimitent en laissant libres des fenêtres 7 d'entrée/sortie du fluide correspondant. Dans chaque passage sont disposées des ondes-entretoises ou ailettes ondulées 8 servant à la fois d'ailettes thermiques, d'entretoises entre les plaques, notamment lors du brasage et pour éviter toute déformation des plaques lors de la mise en oeuvre de fluides sous pression, et de guidage des écoulements de fluides.Each passage 3 to 5 is bordered by closing bars 6 which delimit it leaving free windows 7 input / output of the corresponding fluid. In each passage are disposed wave-waves or corrugated fins 8 serving both thermal fins, spacers between the plates, especially during brazing and to prevent any deformation of the plates during the implementation of fluids under pressure and guiding the flow of fluids.
L'empilement des plaques, des barres de fermeture et des ondes- entretoises est généralement réalisé en aluminium ou en alliage d'aluminium et est assemblé en une seule opération par brasage au four.The stack of plates, closing bars and spacer waves is generally made of aluminum or aluminum alloy and is assembled in a single operation by soldering in the oven.
Des boîtes 9 d'entrée/sortie de fluides, de forme générale semi-cylindrique, sont ensuite soudées sur le corps d'échangeur ainsi réalisé de façon à coiffer les rangées de fenêtres d'entrée/sortie correspondantes, et elles sont reliées à des conduites 10 d'amenée et d'évacuation des fluides.Fluid inlet / outlet boxes 9, of generally semi-cylindrical shape, are then welded to the heat exchanger body thus produced so as to cover the rows of corresponding inlet / outlet windows, and they are connected to conduits 10 for supplying and evacuating fluids.
Les canaux peuvent être formés en utilisant diverses techniques, tels que décrits dans « Micro échangeurs thermiques » d'Anton GRUSS dans Techniques de l'Ingénieur, 06-2002.The channels can be formed using various techniques, as described in Anton GRUSS's "Micro heat exchangers" in Techniques de l'Ingénieur, 06-2002.
La solution de la Figure 3B consiste à remplacer l'onde d'échange classiquement utilisée de la Figure 3A par plusieurs ondes d'échange 13 de même type mais de hauteur d'onde plus petite. Ces nouvelles ondes insérées dans un même passage de l'échangeur sont assemblées à l'aide de fines tôles recouvertes de brasure 13. Ces tôles appelées « tôle de surface tertiaire » constituent la surface ajoutée dite « tertiaire ». Dans l'exemple il y a deux tôles séparant trois ondes.The solution of FIG. 3B consists in replacing the conventionally used exchange wave of FIG. 3A by several exchange waves 13 of the same type but of smaller wavelength. These new waves inserted in the same passage of the exchanger are assembled using thin sheets covered with solder 13. These sheets called "tertiary surface sheet" constitute the added surface called "tertiary". In the example there are two sheets separating three waves.
Tous les types d'ondes qui existent dans le commerce peuvent être utilisés en modifiant et adaptant uniquement la hauteur de l'onde. De ce fait, tous les paramètres qui constituent la géométrie d'un type d'onde sont ajustables (épaisseur, densité, perforation de l'onde,...). Les autres paramètres sont :All commercially available wave types can be used by modifying and adapting only the wave height. As a result, all the parameters constituting the geometry of a wave type are adjustable (thickness, density, perforation of the wave, etc.). The other parameters are:
• la hauteur du passage,• the height of the passage,
• le nombre d'ondes d'échange par passage,• the number of exchange waves per pass,
• l'épaisseur de la tôle de la surface tertiaire (à priori égale à l'épaisseur de l'onde),• the thickness of the sheet of the tertiary surface (a priori equal to the thickness of the wave),
• la forme de la tôle de la surface tertiaire : pleine ou avec des perforations judicieusement positionnées.• the shape of the sheet of the tertiary surface: solid or with perforations judiciously positioned.
Pour cette technologie "multi-ondes", les diamètres hydrauliques sont de l'ordre de grandeur de la largeur du canal d'une onde classique (1/n-e).For this "multi-wave" technology, the hydraulic diameters are of the order of magnitude of the channel width of a conventional wave (1 / n-e).
On donne ici les gains en surface d'échange pour différentes hauteurs d'onde et par rapport à l'onde classique de densité n équivalente :Here we give the exchange surface gains for different wave heights and with respect to the classical wave of density n equivalent:
n* = nombre d'ondes sur la hauteur d'un passage (avec des épaisseurs de tôles de surface tertiaire de 0.2mm). w = largeur d'un canal, h canal = hauteur d'un canal. n * = number of waves on the height of a passage (with thicknesses of tertiary surface sheets of 0.2mm). w = width of a channel, h channel = height of a channel.
On se limite ici à des hauteurs de canaux (h canal) de 2 mm minimum (pour des raisons de brasage).Here we limit ourselves to channel heights (h channel) of 2 mm minimum (for brazing reasons).
A volume équivalent, l'augmentation du nombre d'ondes à empiler dans l'échangeur entraîne une augmentation du coût de fabrication de celui-ci. Le coût d'installation reste cependant le même.At an equivalent volume, the increase in the number of waves to be stacked in the exchanger causes an increase in the manufacturing cost thereof. The installation cost, however, remains the same.
La solution de la Figure 4B consiste à remplacer l'onde d'échange classiquement utilisée de la Figure 4A par une onde structurée 17 comportant de nombreux mini-canaux 19 à section carrée. Cette onde peut être fabriquée par extrusion. La méthode de fabrication par extrusion permet d'imaginer tout type de forme de section de canaux (rectangulaires, triangulaires, ronds, en losange,...). La Figure 4C montre des canaux de section triangulaire.The solution of FIG. 4B consists in replacing the conventionally used exchange wave of FIG. 4A by a structured wave 17 comprising numerous mini-channels 19 with a square section. This wave can be manufactured by extrusion. The extrusion manufacturing method makes it possible to imagine any type of channel section shape (rectangular, triangular, round, rhombic, ...). Figure 4C shows triangular section channels.
Les principaux paramètres sont la hauteur du passage, le nombre de canaux par hauteur de passage, le nombre de canaux par mètre de largeur de passage et tous les paramètres qui concernent la forme géométrique des canaux utilisés (hauteur, largeur, diamètre du canal,...).The main parameters are the height of the passage, the number of channels per passage height, the number of channels per meter of passage width and all the parameters which concern the geometric shape of the channels used (height, width, diameter of the channel ,. ..).
Cette méthode de fabrication permet également la possibilité d'insérer des micro ou mini ailettes à l'intérieur des canaux afin d'augmenter encore la surface d'échange et/ou de drainer un liquide. La longueur des canaux (longueur d'échange du fluide) peut être divisée en plusieurs modules d'ondes extrudées, espacés de quelques millimètres entre-eux afin de permettre une communication entre canaux.This method of manufacture also allows the possibility of inserting micro or mini fins inside the channels to further increase the exchange surface and / or drain a liquid. The length of the channels (fluid exchange length) can be divided into several extruded wave modules spaced a few millimeters apart to allow inter-channel communication.
On distingue 3 catégories de géométrie en fonction du diamètre hydraulique des canaux (Dh) : - canaux tels que Dh soit de l'ordre de grandeur de la largeur des canaux dans les ondes classiques (w=1/n-e).There are 3 categories of geometry according to the hydraulic diameter of the channels (Dh): - channels such that Dh is of the order of magnitude of the width of the channels in the classical waves (w = 1 / n-e).
- canaux tels que Dh soit compris entre 200 microns et 1 mm (minicanaux).- Channels such as Dh is between 200 microns and 1 mm (minichannels).
- canaux tels que Dh soit inférieur à 200 microns (micro-canaux). Les gains en surface d'échange obtenus pour les 3 catégories citées ci- dessus sont les suivants :- Channels such as Dh is less than 200 microns (micro-channels). The exchange area gains obtained for the 3 categories mentioned above are as follows:
Pour les canaux tels que Dh soit de l'ordre de grandeur de la largeur des canaux dans les ondes classiques (w=1/n-e), on donne ici les gains en surface d'échange (se) pour différentes hauteurs d'onde et par rapport à une onde classique de même hauteur et de densité n équivalente.For the channels such that Dh is of the order of magnitude of the width of the channels in the classical waves (w = 1 / ne), we give here the exchange surface gains (se) for different wavelengths and compared to a classical wave of the same height and density n equivalent.
Pour les canaux tels que Dh soit compris entre 200 microns et 1 mm (minicanaux), on donne ici les gains en surface d'échange (se) pour différentes hauteurs d'onde et par rapport à une onde classique de même hauteur et de forte densité n. For channels such as Dh is between 200 microns and 1 mm (minichannels), here we give the exchange surface gains (se) for different wavelengths and compared to a conventional wave of the same height and strong density n.
Pour les canaux tels que Dh soit inférieur à 200 microns (micro-canaux), on donne ici les gains en surface d'échange (se) pour différentes hauteurs d'onde et par rapport à une onde classique de même hauteur et de forte densité n.For the channels such that Dh is less than 200 microns (micro-channels), here we give the exchange surface gains (se) for different wave heights and compared to a conventional wave of the same height and high density not.
La solution de la Figure 5B consiste à remplacer l'onde d'échange classiquement utilisée de la Figure 5A par un nombre adéquat de tubes capillaires. L'arrangement des tubes capillaires s'ordonne facilement du fait de leur forme. Les tubes capillaires sont recouverts de brasure afin d'assurer l'assemblage mécanique de l'ensemble.The solution of Figure 5B is to replace the conventionally used exchange wave of Figure 5A with an adequate number of capillary tubes. The arrangement of the capillary tubes is easily arranged because of their shape. The capillary tubes are covered with solder to ensure the mechanical assembly of the assembly.
Les paramètres ajustables sont la hauteur du passage, le diamètre des tubes capillaires, l'épaisseur des tubes capillaires ou encore le nombre de tubes capillaires par m2.The adjustable parameters are the height of the passage, the diameter of the capillary tubes, the thickness of the capillary tubes or the number of capillary tubes per m 2 .
On donne ici les gains en surface d'échange (se) pour différentes hauteurs d'onde et par rapport à une onde classique de densité équivalente. Dext est le diamètre externe du tube capillaire.We give here the exchange surface gains (se) for different wave heights and with respect to a conventional wave of equivalent density. D ex t is the external diameter of the capillary tube.
Dans chaque exemple le diamètre du capillaire correspond au diamètre maximal pour obtenir un gain en surface d'échange par rapport à la solution classique, un diamètre plus faible donnera un gain nettement plus important de surface d'échange. In each example, the diameter of the capillary corresponds to the maximum diameter in order to obtain a gain in exchange surface area compared to the conventional solution, a smaller diameter will give a much greater gain in exchange surface area.

Claims

REVENDICATIONS
1. Echangeur de chaleur à plaques brasées, du type comprenant un empilement de plaques parallèles (2) qui définissent une pluralité de passages (3, 4, 5) de circulation de fluide de forme générale plate, des barres de fermeture qui délimitent ces passages et des moyens de distribution pour distribuer un fluide à chaque passage d'une première série de passages (3, 5) et des moyens pour envoyer un autre fluide à une deuxième série de passages (4) dans lequel au moins un passage (3) contient au moins une structure d'échange organisée (15, 17, 21 ) qui forme une pluralité de canauxBrazed plate heat exchanger, of the type comprising a stack of parallel plates (2) which define a plurality of generally flat fluid circulation passages (3, 4, 5), closing bars which delimit these passages and dispensing means for dispensing a fluid at each passage of a first series of passages (3, 5) and means for sending another fluid to a second series of passages (4) in which at least one passage (3) contains at least one organized exchange structure (15, 17, 21) that forms a plurality of channels
(19) dans la largeur du passage, chaque canal (19) étant en contact avec soit au moins deux autres canaux soit au moins un autre canal et une plaque (2, 13) et caractérisé en ce que la structure forme également au moins trois canaux dans la hauteur du passage.(19) in the width of the passage, each channel (19) being in contact with either at least two other channels or at least one other channel and a plate (2, 13) and characterized in that the structure also forms at least three channels in the height of the passage.
2. Echangeur selon la revendication 1 dans lequel la structure est composée d'une pluralité de cylindres (21 ).2. Exchanger according to claim 1 wherein the structure is composed of a plurality of cylinders (21).
3. Echangeur selon l'une des revendications précédentes comprenant à l'intérieur d'un passage (3), au moins une plaque secondaire (13) de forme générale plate parallèle aux plaques (2) définissant les passages.3. Exchanger according to one of the preceding claims comprising inside a passage (3), at least one secondary plate (13) of generally flat shape parallel to the plates (2) defining the passages.
4. Echangeur selon la revendication 1 dans lequel la structure est formée d'une superposition d'ondes d'échange (15), chaque paire d'ondes d'échange adjacentes étant éventuellement séparée par une plaque secondaire (13).4. Exchanger according to claim 1 wherein the structure is formed of a superposition of exchange waves (15), each pair of adjacent exchange waves being optionally separated by a secondary plate (13).
5. Echangeur selon la revendication 1 dans lequel la structure est formée d'un corps unique (17) contenant une pluralité de canaux (19).The exchanger of claim 1 wherein the structure is formed of a single body (17) containing a plurality of channels (19).
6. Echangeur selon l'une des revendications précédentes dans lequel un canal (19) a un diamètre hydraulique d'entre 1 et 6 mm.6. Exchanger according to one of the preceding claims wherein a channel (19) has a hydraulic diameter of between 1 and 6 mm.
7. Echangeur selon les revendications 1 à 5 dans lequel un canal (19) a un diamètre hydraulique entre 200 μm et 1 mm. 7. Exchanger according to claims 1 to 5 wherein a channel (19) has a hydraulic diameter between 200 microns and 1 mm.
8. Echangeur selon les revendications 1 à 5 dans lequel un canal (19) a un diamètre hydraulique inférieur à 200 μm8. Exchanger according to claims 1 to 5 wherein a channel (19) has a hydraulic diameter of less than 200 microns
9. Echangeur selon l'une des revendications précédentes dans lequel les canaux (19) ont une section circulaire, ovale, carrée, rectangulaire, triangulaire ou en losange.9. Exchanger according to one of the preceding claims wherein the channels (19) have a circular section, oval, square, rectangular, triangular or diamond.
10. Appareil de séparation cryogénique comprenant au moins un echangeur (1) selon l'une des revendications précédentes.10. Cryogenic separation apparatus comprising at least one exchanger (1) according to one of the preceding claims.
11. Appareil de séparation d'air selon la revendication 10 dans lequel une ligne d'échange principale et/ou un vaporiseur-condenseur et/ou un sous- refroidisseur est un echangeur selon l'une des revendications 1 à 9. 11. Air separation apparatus according to claim 10 wherein a main exchange line and / or a vaporizer-condenser and / or subcooler is an exchanger according to one of claims 1 to 9.
EP06778947.9A 2005-06-09 2006-06-06 Plate heat exchanger with exchanging structure forming several channels in a passage Not-in-force EP1899669B1 (en)

Applications Claiming Priority (2)

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FR0551560A FR2887020B1 (en) 2005-06-09 2005-06-09 PLATE HEAT EXCHANGER WITH EXCHANGE STRUCTURE FORMING MULTIPLE CHANNELS IN A PASSAGE
PCT/FR2006/050600 WO2006131685A2 (en) 2005-06-09 2006-06-06 Plate heat exchanger with exchanging structure forming several channels in a passage

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EP1899669A2 true EP1899669A2 (en) 2008-03-19
EP1899669B1 EP1899669B1 (en) 2015-08-12

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US20120090354A1 (en) 2012-04-19
JP2008545946A (en) 2008-12-18
EP1899669B1 (en) 2015-08-12
CN101871744A (en) 2010-10-27
CN101194137B (en) 2010-11-24
FR2887020B1 (en) 2007-08-31
CN101194137A (en) 2008-06-04
WO2006131685A3 (en) 2007-05-18
US20080210415A1 (en) 2008-09-04
WO2006131685A2 (en) 2006-12-14
FR2887020A1 (en) 2006-12-15

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