US20200370836A1 - Heat exchanger comprising a multi-channel distribution element - Google Patents

Heat exchanger comprising a multi-channel distribution element Download PDF

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Publication number
US20200370836A1
US20200370836A1 US16/636,165 US201816636165A US2020370836A1 US 20200370836 A1 US20200370836 A1 US 20200370836A1 US 201816636165 A US201816636165 A US 201816636165A US 2020370836 A1 US2020370836 A1 US 2020370836A1
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United States
Prior art keywords
heat exchanger
fluid
distribution
channels
passage
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Abandoned
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US16/636,165
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English (en)
Inventor
Frederic Crayssac
Sebastien Cadalen
Marc Wagner
Quentin SANIEZ
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LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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LAir Liquide SA pour lEtude et lExploitation des Procedes Georges Claude
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Publication of US20200370836A1 publication Critical patent/US20200370836A1/en
Abandoned legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0282—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by varying the geometry of conduit ends, e.g. by using inserts or attachments for modifying the pattern of flow at the conduit inlet or outlet
    • 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
    • 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
    • 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
    • F25J2290/32—Details on header or distribution passages of heat exchangers, e.g. of reboiler-condenser or plate 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
    • 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
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
    • F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
    • F28F9/0268—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box in the form of multiple deflectors for channeling the heat exchange medium

Definitions

  • the present invention relates to a distribution element configured to be arranged in a distribution zone of a heat exchanger of the plate and fin type, and to a heat exchanger comprising such a distribution element and at least one set of passages for a fluid to be put into a heat-exchange relationship with at least one other fluid.
  • the element according to the invention allows more homogeneous distribution of the fluid across the width of said passages.
  • the present invention finds application notably in the field of the cryogenic separation of gases, in particular the cryogenic separation of air, in what is known as an ASU (air separation unit) used to produce pressurized gaseous oxygen.
  • the present invention may be applied to a heat exchanger that vaporizes a flow of liquid, for example oxygen, nitrogen and/or argon by exchange of heat with a gas.
  • the present invention may also be applied to a heat exchanger that vaporizes at least one flow of liquid-gas mixture, in particular a flow of multi-constituent mixture, for example a mixture of hydrocarbons, through exchange of heat with at least one other fluid, for example natural gas.
  • a heat exchanger that vaporizes at least one flow of liquid-gas mixture, in particular a flow of multi-constituent mixture, for example a mixture of hydrocarbons, through exchange of heat with at least one other fluid, for example natural gas.
  • the technology commonly used for a heat exchanger is that of aluminum brazed plate and fin heat exchangers, which make it possible to obtain devices that are very compact and afford a large heat-exchange surface area.
  • These heat exchangers comprise plates, between which are inserted heat-exchange corrugations, formed of a succession of fins or corrugation legs, thereby constituting a stack of passages for the various fluids to be put into a heat-exchange relationship.
  • These passages comprise zones referred to as distribution zones, which are arranged, in the overall direction of flow of the fluid in the passage in question, upstream and downstream of the actual heat-exchange zone.
  • the distribution zones are fluidly connected to semi-tubular headers configured to distribute the various fluids selectively to the various passages, and to remove said fluids from said passages.
  • these distributors generally comprise distribution corrugations, arranged in the form of corrugated sheets between two successive plates.
  • the distribution corrugations are generally perforated straight corrugations cut into the shape of triangles or trapeziums. They divert the fluid coming from the inlet header of the heat exchanger in order to spread it across the width of the heat-exchange zones, and recover the fluid coming from said heat-exchange zone.
  • the distribution corrugations also act as spacers in order to ensure the mechanical integrity upon brazing and during operation of the distribution zone of the passage.
  • Such distribution corrugations are known from the documents U.S. Pat. No. 6,044,902 and EP-A-0507649. Also known, from the document EP-A-3150952, is a plate heat exchanger in which the distribution elements are formed by the actual plates, which are pressed.
  • the distribution zones are occupied by at least two pads of corrugations in order to optimize the offcuts from the shaping process, thus increasing the risk of clearance between the pads.
  • the assembly of the corrugation pads can also cause incidents along the flow path of the fluid, and this contributes to increasing the pressure drops in the distribution zones. Because of these imperfections in the distribution zones, variations in flow rate with an amplitude of around 10% may arise, these being detrimental to the correct operation of the heat exchanger.
  • the distribution zone of a passage extends typically along a length, measured in a longitudinal direction corresponding to the direction of flow of the fluid in the heat-exchange zone of the same passage, of around 200 to 600 mm, and across a width, measured perpendicularly to said longitudinal direction, of around 500 to 1500 mm. Since the distribution zones constitute parts with lower mechanical integrity than the heat-exchange zones, it is desirable to limit the longitudinal extent thereof as much as possible in order to ensure better resistance of the heat exchanger during the circulation of fluids at high pressure within the passages.
  • the solution according to the invention is therefore a heat exchanger of the brazed plate and fin type, comprising:
  • the element of the invention may comprise one or more of the following technical features:
  • FIG. 1 is a three-dimensional schematic view of a heat exchanger of the plate and fin type
  • FIG. 2 is a partial schematic view in longitudinal section of a distribution zone according to one embodiment of the invention.
  • FIG. 3A is a partial schematic view in longitudinal section of distribution zones according to other embodiments of the invention.
  • FIG. 3B is a partial schematic view in longitudinal section of distribution zones according to other embodiments of the invention.
  • FIG. 4 is a partial schematic view in longitudinal section of distribution zones according to other embodiments of the invention.
  • FIG. 5A is a schematic view in longitudinal section of a distribution zone according to another embodiment of the invention.
  • FIG. 5B is a three-dimensional schematic view of a distribution zone according to another embodiment of the invention.
  • FIG. 6A presents a result of a simulation carried out with a distribution element as depicted schematically in FIG. 5B ;
  • FIG. 6B presents a result of a simulation carried out with a distribution element as depicted schematically in FIG. 58 ;
  • FIG. 6C presents a result of a simulation carried out with a distribution element as depicted schematically in FIG. 5B ;
  • FIG. 7 presents a result of a simulation carried out with a distribution element as depicted schematically in FIG. 5 .
  • a heat exchanger 1 of the plate and fin type comprises a stack of plates 2 that extend in two dimensions, length and width, in the longitudinal direction z and the lateral direction y, respectively.
  • the plates 2 are disposed parallel to and above one another with a spacing, and thus form several sets of passages 3 , 4 , 5 for fluids F 1 , F 2 , F 3 to be put into an indirect heat-exchange relationship via the plates 2 .
  • the lateral direction y is orthogonal to the longitudinal direction z and parallel to the plates 2 .
  • the longitudinal axis is vertical when the heat exchanger 1 is in operation.
  • each passage has a flat and parallelepipedal shape.
  • the passages extend lengthwise in the longitudinal direction z and widthwise in the lateral direction y. The separation between two successive plates is small in comparison with the length and the width of each successive plate.
  • Each passage 3 , 4 , 5 is divided, in the longitudinal direction z, into at least one distribution zone 20 and one heat-exchange zone 21 .
  • the flow of the fluids within the distribution zones takes place overall parallel to the longitudinal direction z.
  • the distribution zone 20 and heat-exchange zone 21 are preferably juxtaposed along the longitudinal axis z.
  • two distribution zones 20 are arranged on either side of the heat-exchange zone 21 , one serving to carry the fluid F 1 toward the heat-exchange zone 21 and the other serving to evacuate it from said zone.
  • Conventional distribution corrugations made in the form of corrugated products are shown in the distribution zones 20 .
  • the heat exchanger 1 comprises semi-tubular headers 7 , 9 provided with openings 10 for introducing the fluids into the heat exchanger 1 and evacuating the fluids from the heat exchange 1 .
  • These headers have openings that are less wide than the passages.
  • the distribution zones 20 serve to distribute the fluids introduced through the openings in the headers across the entire width of the passages.
  • a distribution element is arranged in at least one distribution zone 20 of a passage 3 of the heat exchanger, this element comprising a plurality of dividing walls 25 that are arranged so as to divide said distribution zone 20 into a plurality of channels 26 for the fluid F 1 to flow through.
  • Said channels 26 define flow paths with different lengths and have variable passage sections for fluid along said flow paths. Subdividing the distribution zone into a plurality of separate channels with variable lengths and sections makes it possible to divert the fluid while finely controlling the flow conditions for the fluid within each channel.
  • the distribution element confers structural rigidity on the distribution zone of the heat exchanger since the spacer function can be ensured by the dividing walls.
  • the heat exchanger is of the brazed plate and fin type, meaning that the separate elements that make up the heat exchangers are secured, directly or indirectly, by brazing.
  • the distribution element according to the invention is separate from the plates 2 .
  • Brazed support is understood as meaning that the support is connected or secured by brazing to an adjacent plate of the heat exchanger via at least a portion of the respective surfaces thereof.
  • passage section for fluid means the area through which the fluid flows within the channel, this being measured in a plane perpendicular to the direction of movement of the fluid F 1 in said channel, i.e. perpendicular to the stream lines of the moving fluid F 1 .
  • the length of the flow paths is understood to be the distance to be covered by the fluid F 1 between the inlet and the outlet of the channel in question.
  • the distribution element also comprises a support 27 configured to keep the walls 25 secured together.
  • a support 27 configured to keep the walls 25 secured together. An example of such an element is presented in FIG. 5B .
  • the distribution element is not a corrugated product, in contrast to the distribution corrugations conventionally disposed in the distribution zones of a brazed plate and fin heat exchanger.
  • the walls 25 are secured together via one and the same support 27 , thereby conferring greater rigidity on the distribution element. This also makes it possible to simplify the brazing operations. Moreover, such a configuration affords greater design freedom for the distribution element and geometric freedom for the channels thereof.
  • walls 25 with a relatively great height, typically at least 2 mm, preferably at least 5 mm, more preferably up to 15 mm, or more, in the passages, this not being the case with heat exchangers in which the walls result from pressing of the dividing plates.
  • said support comprises a bottom 27 , preferably a flat bottom that can be formed from a flat sheet, from which the dividing walls 25 are erected.
  • the walls 25 are preferably erected in the vertical direction x.
  • the walls 25 can have heights h of typically between 2 and 15 mm. Preferably, the heights are chosen such that the walls 25 extend over virtually all, if not all, of the height of the passage in the vertical direction x.
  • the configuration of the distribution element 22 according to the invention in which the distribution element is a separate part from the plates, also makes it possible to design different distribution profiles on either side of one and the same plate.
  • a distribution element according to the invention is housed in several, if not all, of the distribution zones of one or more sets of passages of the heat exchanger. Said element extends over virtually all, if not all, of the height of the passages, measured in the vertical direction x, such that the structure is advantageously in contact with each plate 2 forming the passage 20 .
  • the channels are preferably fluidically isolated from one another.
  • the flow parameters of each channel are thus controlled independently of those of the adjacent channels, thereby making it possible to precisely adjust the distribution of the fluid across the width of the passages at the outlet of the distribution zone.
  • the separating walls 25 are erected perpendicularly to the plates 2 .
  • the number of channels 26 is at least 6, more preferably between 5 and 50.
  • the number of channels 26 on the one hand has to be high enough to give the element 22 its mechanical rigidity but on the other hand should not be too high in order to leave enough free volume for the fluid to flow and to limit pressure drops.
  • the distribution element 22 comprises a first end 23 forming an inlet or an outlet for the fluid F 1 , and a second end 24 fluidically connected to the heat-exchange zone 21 .
  • the passages 3 to 5 are bordered by closure bars 6 , which do not completely shut off the passages but leave free openings 23 , 24 for the inlet or outlet of the corresponding fluids.
  • FIG. 2 schematically partially depicts the “inlet” part of a passage 3 of a heat exchanger according to one embodiment of the invention.
  • a fluid header 7 is arranged in the left-hand corner of the heat exchanger, the first end 23 being fluidically connected to the header 7 and forming an inlet for the fluid F 1 , the flow of which is schematically depicted by dashed arrows.
  • the first and second ends 23 , 24 extend preferably in a plane parallel to the lateral direction y and perpendicular to the longitudinal direction z.
  • the dividing walls 25 extend between the first and second ends 23 , 24 and form channels 26 that lead out at the second end 24 and are configured to distribute the fluid F 1 uniformly in the lateral direction y so as to obtain homogeneous or quasi-homogeneous distribution towards or from the entire width of the heat-exchange zone 21 when the other of said first and second ends 23 , 24 is fed with fluid F 1 .
  • each channel is provided with first openings 26 a and second openings 26 b .
  • the first and second openings 26 a , 26 b are situated at the first and second ends 23 , 24 , respectively, the dividing walls 25 extending continuously from the first end 23 to the second end 24 .
  • the flow path of the fluid F 1 corresponds to the path to be followed between the openings 26 a and 26 b .
  • Each of the ends 23 , 24 can thus be divided into a series of openings 26 a and a series of openings 26 b , respectively.
  • the openings 26 a , 26 b of the channels 26 could have passage sections for fluid that are identical or variable depending on the channels 26 in question.
  • the passage sections for fluid of the openings 26 a and 26 b correspond to the internal areas of the channels 26 measured at the first and second ends 23 , 24 in a plane parallel to the lateral direction y.
  • At least one first opening 26 a has a passage section for fluid that is different than the passage section for fluid of another first opening 26 a
  • at least one second opening 26 b has a passage section for fluid that is different than the passage section for fluid of another second opening 26 b.
  • first openings 26 a and/or the second openings 26 b of one and the same channel 26 have passage sections for fluid that are larger the longer the flow path defined by said channel 26 , i.e. the greater the distance to be covered by the fluid F 1 between the first opening 26 a and the second opening 26 b.
  • the first end 23 is subdivided into a first series of first openings 26 a that have passage sections for fluid that increase in the lateral direction y. This encourages the supply of the channels that are configured to distribute the fluid F 1 from the header 7 toward the part of the second end 23 that is diagonally opposite said extreme edge.
  • the first openings 26 a which are arranged, preferably symmetrically, on either side of the plane M, have passage sections for fluid that increase with increasing distance from said median plane M.
  • the first end 23 is situated by the inlet header 7 of the heat exchanger and forms an inlet for the fluid F 1 .
  • the first openings 26 a in the first end 23 have passage sections for fluid that are variable depending on their position along the lateral direction y.
  • openings 26 a By virtue of the use of openings 26 a with different passage sections, it is notably possible to overfeed the channels that are less favorable to the passage of the fluid, specifically from the inlet of the fluid F 1 into the distribution zone 20 , this causing fewer pressure drops and thus leading to a more efficient fluid distribution system.
  • all or some of the channels 26 comprise means 28 for modifying the linear flow resistance of said channels 26 .
  • the linear flow resistance of each channel can thus be adjusted depending on the flow characteristics desired in each channel 26 , in particular fluid flow rate and velocity.
  • the linear flow resistance of the channels can be adjusted such that each channel 26 has a similar overall flow resistance.
  • the characteristics of the fluid at the outlet of the channels 26 are thus homogenized in the lateral direction y, thereby allowing uniform distribution toward or from the heat-exchange zone 21 .
  • flow resistance is understood to mean the capability of the channel not only to generate viscous friction but also to divert the flow (pressure force normal to the wall). This resistance is expressed in the form of a reaction force of the solid structure to the flow in newtons, this resulting in the fluid in a pressure drop in pascals. This force depends firstly on the kinetic energy of the fluid (rho*u 2 ) and secondly on the Reynolds number (rho*u*D/mu).
  • the linear flow resistance corresponds to the flow resistance of the channel expressed per unit of length.
  • a channel 26 will comprise modification means 28 that are configured to produce an increase in the linear flow resistance that is all the greater the closer the opening 26 a of said channel is, in terms of distance to be covered by the fluid F 1 , to the other opening 26 b .
  • the channels 26 comprise modification means 28 that are configured to produce an increase in linear flow resistance that is increasingly small in the lateral direction y. Specifically, this makes it possible to compensate for the natural preferred passage of the fluid along the axis rather than along the side of the heat exchanger, and thus to obtain good distribution of the fluid.
  • the fluid resistance of a channel will be all the greater the closer it is to the median plane M.
  • the channels 26 could have internal profiles that are shaped to produce different variations in flow resistance.
  • Obstacles 28 that produce different flow resistances could also be arranged within one or more channels 26 .
  • the insertion of a porous structure 28 , for example a metal foam, into a channel will make it possible to increase the flow resistance thereof.
  • the linear flow resistance of the channels 26 could thus be adjusted by varying the characteristics of the inserted structures 28 , such as volume, density, etc. in accordance with the channels.
  • the volume taken up by the porous structures 28 decreases in the lateral direction y, so as to produce variations in linear flow resistance that are smaller along y.
  • partitions 28 can be arranged in one or more channels 26 so as to create an additional stage for dividing the distribution zone 22 . This makes it possible to vary the linear flow resistance and to control the flow parameters of the fluid distributed toward or recovered from the heat-exchange zone 21 even more finely.
  • additional partitions 28 is notably advantageous when the first end 23 of the distribution element has a width that is too small to be able to be divided into a sufficient number of channels 26 .
  • the dividing walls 25 and/or the partitions 28 may have, in longitudinal section, rectilinear profiles, as illustrated in FIGS. 2 and 4 , or curvilinear profiles, as illustrated in FIGS. 3A, 3B and 5A, 5B .
  • the dividing walls 25 have predetermined curvilinear profiles comprising at least one inflection point P.
  • Such a geometry makes it possible to divert the fluid more quickly, that is to say over a shorter distance L 1 , specifically across a great width of the passage of the heat exchanger. It is thus possible to reduce the longitudinal extent of the distribution zone 20 and consequently to increase the mechanical integrity of the heat exchanger since the compactness of what is known as the “weak” zone of the heat exchanger is increased.
  • the first end 23 forming the inlet or outlet of the distribution element 22 has, in the lateral direction y, a width L 3 of between 50 and 1000 mm, more preferably between 100 and 500 mm.
  • the distribution element 22 has, parallel to the longitudinal direction z, a length L 1 less than 500 mm, preferably between 50 and 200 mm, more preferably between 80 and 100 mm.
  • the length L 1 of the distribution element 22 represents less than 20% of the length of the heat-exchange zone 21 .
  • the distribution element 22 Parallel to the lateral direction y, the distribution element 22 has a width L 2 , the ratio between a length L 1 and the width L 2 being less than 20%, preferably between 5 and 10%.
  • the width L 2 is preferably between 500 and 1500 mm.
  • the distribution element 22 is advantageously formed from a metal material, preferably aluminum or an aluminum alloy.
  • the element may be formed in particular from a porous material, preferably with closed pores, for example a metal foam.
  • the distribution element 22 is monolithic, thereby making it possible to minimize incidents along the flow paths of the fluid.
  • the element 22 may be manufactured using an additive manufacturing method, preferably by thermal spraying, making it possible to produce parts with complex geometries in one piece.
  • a cold spray method could be used.
  • additive manufacturing method can also be referred to as “3D printing”.
  • Additive manufacturing makes it possible to produce a real object using a specific printer, which deposits and/or solidifies material, layer by layer, to obtain the final part.
  • the stack of these layers makes it possible to create a volume.
  • the element 22 may also be manufactured using the following additive manufacturing methods:
  • the distribution element 22 may be manufactured by casting. This manufacturing method makes it possible to produce parts with complex geometries at a relatively low cost compared with additive manufacturing.
  • the element 22 is formed from an aluminum alloy by casting, that is to say an alloy of which the main constituent is aluminum, with a density lower than intended to be converted by casting techniques.
  • these advantageously comprise heat-exchange structures 8 disposed between the plates 2 , as shown in FIG. 1 .
  • These structures have the function of increasing the heat-exchange area of the heat exchanger and act as spacers between the plates 2 , notably during the assembly of the exchanger by brazing, in order to avoid any deformation of the plates during the use of pressurized fluids.
  • these structures comprise heat-exchange corrugations 8 which advantageously extend across the width and along the length of the passages of the heat exchanger, parallel to the plates 2 .
  • These corrugations 8 may be formed in the form of corrugated sheets.
  • the corrugation legs that connect the successive tops and bottoms of the corrugation are referred to as “fins”.
  • the heat-exchange structures 8 can also cover other particular shapes defined depending on the desired fluid flow characteristics. More generally, the term “fins” covers blades or other secondary heat-exchange surfaces, which extend from the primary heat-exchange surfaces, that is to say the plates of the heat exchanger, into the passages of the heat exchanger.
  • the distribution element 22 according to the invention and the heat-exchange structure 8 are preferably juxtaposed along the longitudinal axis z, that is to say positioned end to end. Note that a small clearance can exist between these elements in order not to block the channels of the heat-exchange zone 21 which face the walls 25 of the channels of the distribution zone 22 .
  • the first end 23 of the element 22 is arranged end to end with at least one part of the header 7
  • the second end 24 is arranged end to end with at least one part of the structure 8 .
  • the structure 8 , the header 7 and/or the element 22 are connected by brazing to the plate 2 and are connected indirectly together via their respective connections to the plates 2 .
  • the element 22 is assembled on the plates 2 by brazing the support 27 to the plates 2 , the support or bottom 27 comprising at least one face coated with a brazing agent.
  • This face is positioned next to a plate 2 so as to form a connecting surface with said plate 2 .
  • the plate 2 entirely or partially have at least one face coated at least partially with a brazing agent layer.
  • the dimensional characteristics of the distribution element 22 were as follows:
  • FIGS. 6A, 6B, 6C and 7 show plots of the velocities, pressures and temperatures of the fluid flowing within the channels 26 of the distribution element 22 .
  • FIG. 7 indicates the change in the values of what is known as the axial velocity, that is to say the velocity in the longitudinal direction z, that are obtained at the outlet of the element 22 , depending on the position in the lateral direction y. The change thus starts from the center of the distribution element 22 (position at 0 mm) as far as the edge of the second end 23 (position at 485 mm).
  • the distribution of the velocity values along the lateral direction y is characterized by a standard deviation of 0.9% and a maximum deviation of 2.8% with respect to the mean value of the velocity in the heat-exchange zone, this being much less than the variations found with the conventional distribution elements, for which the standard deviations are around 3%.
  • the velocity variations are thus reduced in the lateral direction at the outlet of the distribution zone, making it possible to distribute the fluid as homogeneously as possible across the entire width of the heat-exchange zone.
  • a distribution element according to the invention may thus be arranged in any distribution zone of the heat exchanger, in one or more series of passages 3 , 4 , 5 of the heat exchanger, upstream and/or downstream of one or more of the headers of the heat exchanger. For example, FIG.
  • FIG. 5B illustrates the case in which a heat-exchanger passage comprises two distribution elements according to the invention arranged on either side of the heat-exchange zone 21 (schematically depicted with a deliberately shortened length). It should also be noted that passages 3 , 4 , 5 of the heat exchanger can be formed equally well between two successive plates 2 and between a closure bar 6 of the heat exchanger and an immediately adjacent plate 2 .

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
US16/636,165 2017-08-04 2018-07-16 Heat exchanger comprising a multi-channel distribution element Abandoned US20200370836A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR1757539 2017-08-04
FR1757539A FR3069918B1 (fr) 2017-08-04 2017-08-04 Echangeur de chaleur comprenant un element de distribution a canaux multiples
PCT/FR2018/051804 WO2019025691A1 (fr) 2017-08-04 2018-07-16 Echangeur de chaleur comprenant un element de distribution a canaux multiples

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US20200370836A1 true US20200370836A1 (en) 2020-11-26

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CN113993346A (zh) * 2021-10-20 2022-01-28 联想(北京)有限公司 导风装置及导风装置的制造方法
CN118936203A (zh) * 2024-09-09 2024-11-12 空调国际(上海)有限公司 换热器翅片及板式换热器
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CN120846110A (zh) * 2020-09-29 2025-10-28 台达电子工业股份有限公司 水冷装置及其集流器
CN114688898B (zh) * 2020-12-31 2026-06-05 浙江三花汽车零部件有限公司 一种换热器
JP7247251B2 (ja) * 2021-03-30 2023-03-28 本田技研工業株式会社 熱交換器
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CN113993346A (zh) * 2021-10-20 2022-01-28 联想(北京)有限公司 导风装置及导风装置的制造方法
US20240410661A1 (en) * 2023-06-08 2024-12-12 Rtx Corporation Uniform chemical milling
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FR3069918B1 (fr) 2020-01-17
WO2019025691A1 (fr) 2019-02-07
CN111065879B (zh) 2021-08-24
JP7150819B2 (ja) 2022-10-11
JP2020529572A (ja) 2020-10-08
EP3662222A1 (fr) 2020-06-10
FR3069918A1 (fr) 2019-02-08
EP3662222B1 (fr) 2021-05-26
CN111065879A (zh) 2020-04-24

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