Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
  • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
  • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
  • 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
  • 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
  • F25J3/04151—Purification and (pre-)cooling of the feed air; recuperative heat-exchange with product streams
  • F25J3/04187—Cooling of the purified feed air by recuperative heat-exchange; Heat-exchange with product streams
  • F25J3/04236—Integration of different exchangers in a single core, so-called integrated cores
• • 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
  • F28D9/0093—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
• • 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
  • 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
  • F25J2290/40—Vertical layout or arrangement of cold equipments within in the cold box, e.g. columns, condensers, heat exchangers etc.
• • 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
  • F25J2290/44—Particular materials used, e.g. copper, steel or alloys thereof or surface treatments used, e.g. enhanced surface

Definitions

• the present invention relates to a set of heat exchangers for forming a non-contact heat transfer unit between a primary fluid and a secondary fluid, for example a cryogenic gas separation unit. Furthermore, the present invention relates to a cryogenic air separation installation comprising such a set of heat exchangers.
• the present invention finds particular application in the field of the separation of gas, for example air, by cryogenics.
• a cryogenic air separation unit generally comprises brazed plate main heat exchangers which form the main heat exchange line of the cryogenic air separation unit.
• heat exchangers put in heat exchange relation, on the one hand, the air at ambient temperature and, on the other hand, cryogenic fluids coming from the distillation column (or columns).
• the air At the exit of such a heat exchanger, the air has a temperature of the order of -175 ° C, while the heated fluids are substantially at room temperature (about 25 ° C).
• the thermal gradient is about 200 K between the inlet and the outlet of a heat exchanger and the average logarithmic difference in temperature is between 2 K and 10 K.
• Each heat exchanger comprises a stack of parallel plates delimiting fluid passages, as well as spacers or heat exchange waves defining channels for these fluids. Peripheral closure bars seal the fluid passages.
• such a heat exchanger In a manner known per se, such a heat exchanger generally has the shape of a rectangular parallelepiped.
• the length of such a heat exchanger is typically from 4 to 8 m, its width from 1 to 1.5 m and its height from
• the length of a heat exchanger is the largest dimension of the parallel plates delimiting fluid passages.
• the width of a heat exchanger is measured perpendicular to the length.
• the height of a heat exchanger is measured in the stacking direction of its plates.
• the state of the art for such heat exchangers is to perform countercurrent heat exchange with a direction of flow of the fluids in the lengthwise direction so as to benefit from the largest dimension to realize the flow. heat exchange.
• FR-A-2844040 proposes to use such an exchanger with a direction of flow of the fluids in the direction of the width so as to reduce considerably (typically by a factor of 4 to 6) the number of exchangers to be arranged in parallel .
• WO-A-2007149345 describes a set of heat exchangers comprising two juxtaposed heat exchangers. In this case, the number of solder exchangers is reduced by only a factor of 2 to 3, a factor that is still very important.
• the heat exchanger assembly of WO-A-2007149345 comprises means for fluidically connecting the heat exchangers juxtaposed.
• the primary fluid is high pressure compressed air and the secondary fluid is low pressure nitrous.
• the primary fluid is collected by oblique distribution spacers which direct the secondary fluid to two lateral feed boxes (one on each side of the heat exchanger) and which have a small debiting section, which generates significant losses of load.
• the primary fluid is fed into the second heat exchanger by two lateral feed boxes and oblique distribution spacers, which generates significant pressure drops.
• the present invention aims to solve, in whole or in part, the problems mentioned above.
• the subject of the invention is a set of heat exchangers intended to form a non-contact heat transfer unit between a primary fluid and a secondary fluid, the set of heat exchangers comprising two exchangers, namely a first heat exchanger and a second heat exchanger adapted to exchange heat between at least one primary fluid, for example compressed air at high pressure, and at least one secondary fluid, for example low-pressure nitrogen,
• each exchanger comprising a stack of several plates arranged parallel to each other in a so-called stacking direction, so as to delimit at least i) primary passages shaped for the primary fluid flow and ii) secondary passages shaped for the secondary fluid flow, the primary passages and the secondary passages succeeding one another in a predetermined stacking pattern,
• the stack of the plates of the first exchanger defining a first connection face fluidly connected to the primary passages of the first exchanger
• the stack of the plates of the second exchanger defining a second connection face fluidly connected to the primary passages of the second exchanger
• the heat exchanger assembly being characterized in that the first heat exchanger and the second heat exchanger are arranged so that the first connecting face is adjacent to the second connecting face;
• At least one primary compartment arranged in the enclosure volume for channeling all or part of the primary fluid between the first exchanger and the second exchanger through the first connection face and the second connection face,
• At least one secondary compartment which is separate from said at least one primary compartment and which is arranged in the enclosure volume for channeling all or part of the secondary fluid between the first exchanger and the second exchanger through the first connection face and the second connecting face.
• the present invention involves increasing the number of primary fluid supply boxes (number strictly greater than 2) by passing the primary fluid through the same connecting face as the secondary fluid.
• adjacent refers to an element located in the vicinity of another element, so close to or adjacent to this other element.
• two connecting surfaces are adjacent when in contact along respective edges or respective portions.
• the term "low pressure nitrous” refers to a fluid which is enriched in nitrogen relative to air and which is produced at a pressure substantially lower than that of air entering a heat exchanger. heat.
• the predetermined stacking pattern may comprise a succession "-SPS-" with a primary passage “P” surrounded by two secondary passages "S”. This stacking pattern is repeated over the entire height of the corresponding heat exchanger.
• the predetermined stacking pattern may comprise a succession of a primary passage "P” and a secondary passage "S", the secondary passages being of greater height than the primary passages with the exception of the passages secondary end "S '" so as not to unbalance the heat exchange at the ends.
• the succession would have as reason: "S'-P-S-P-S-P-S-" and "-S-P-S-P-S" ".
• the primary (s) and secondary (s) compartment (s) can transfer all the primary fluid and all the secondary fluid of a heat exchanger to the neighboring heat exchanger, through the first connecting face and the second connection face. Therefore, such a set of heat exchangers makes it possible to increase the exchange surface between the primary and secondary fluids, without modifying the manufacturing tools, in particular the soldering furnaces.
• the enclosure volume is defined by enclosure walls that envelop the enclosure volume.
• enclosure walls define a sealed or near-sealed enclosure volume.
• the term "quasi-sealed" qualifies a volume for which the leakage rate is acceptable, that is to say less than 5%, or even less than 1% of the total volume of fluid entering.
• the first connection face is generally flat and perpendicular to said plates of the first exchanger
• the second connection face is generally flat and perpendicular to the plates of the second exchanger
• each exchanger has the overall shape of a rectangular parallelepiped.
• the first connection face is generally flat and perpendicular to said plates of the first exchanger
• the second connection face is generally flat and perpendicular to the plates of the second exchanger
• the first connection face and the second connection face are parallel and arranged opposite one another.
• such a set of heat exchangers can be very compact, with a minimum enclosure volume, which makes it possible to reduce the pressure drops in the flows of the primary and secondary fluids.
• the first exchanger and the second exchanger are arranged side by side, the first connection face and the second connection face being oriented in respective normal directions which are substantially parallel, the first connecting face and the second connecting face being preferably arranged so as to have an adjacent edge or merged.
• the enclosure generally has the shape of a half-cylinder or half-ring.
• a set of heat exchangers may have a relatively small dimension in a direction perpendicular to the first and the second connection face.
• this arrangement of the heat exchangers simplifies the manufacture of the heat exchanger assembly, since there is more space to weld and connect the heat exchangers.
• the first connecting face and the second connecting face are substantially orthogonal to each other, the first connecting face and the second connecting face being preferably arranged so as to present an adjacent or confused edge.
• the enclosure has the overall shape of a quarter cylinder or ring.
• a set of heat exchangers can have a size suitable for certain applications.
• this arrangement of the heat exchangers simplifies the manufacture of the heat exchanger assembly, since there is more space to weld and connect the heat exchangers.
• the enclosure volume forms the secondary compartment.
• the set of heat exchangers comprises sealing means between, on the one hand, the enclosure and, on the other hand, the first connection face and the second face of connection.
• sealing means guarantee the seal between the enclosure.
• the first connection face generally has the shape of a rectangle whose edges are defined by the length and the height, in the stacking direction, of the first exchanger, and in which the second connecting face has generally the shape of a rectangle whose edges are defined by the length and the height, in the stacking direction, of the second exchanger.
• each exchanger has the overall shape of a rectangular parallelepiped.
• heat exchangers have relatively simple shapes to achieve.
• the length is much greater, preferably by a factor greater than four, the height measured in the stacking direction.
• the primary compartments are formed by primary pipes which each extend between the connecting faces and parallel to the stacking direction, the primary pipes being distributed with predetermined intervals, preferably at regular intervals, in a direction transverse to the stacking direction, the primary lines being in fluid communication with the primary passages of each heat exchanger so as to allow the flow of the primary fluid between the exchangers; and each secondary compartment is formed by the walls of the enclosure and by the walls of two successive primary pipes.
• the primary lines are shaped for the flow of a high pressure fluid, while the secondary compartments are for the flow of a low pressure fluid.
• the primary pipes comprise: i) a tubular longitudinal collector, preferably of circular section, and ii) primary tubes fluidly connecting the collector to the first connecting face and the second face of the pipe. connection.
• a tubular longitudinal collector preferably of circular section
• primary tubes fluidly connecting the collector to the first connecting face and the second face of the pipe. connection.
• each primary pipe has the shape of a rectangular base prism or a curvilinear base cylinder and whose generatrices are parallel to the stacking direction.
• the walls of the primary pipes are flat and parallel to the stacking direction.
• such a rectangular section limits the pressure losses in the primary and secondary compartments.
• each primary pipe is composed of at least two parts joined together by mechanical securing means, the mechanical securing means being preferably selected from the group consisting of screws, flanges , rivets, crimping elements, embedding elements, latching elements, fitting elements and complementary shapes such as dovetails.
• a closure member in each secondary passage, is placed on the respective primary pipe so as to prevent the flow of secondary fluid in said primary pipe.
• each heat exchanger generally has the shape of a rectangular parallelepiped, and in which each connecting face has generally the shape of a rectangle, said so-called stacking direction being parallel to the height of the rectangular parallelepiped, the spacers extending parallel to the length of the rectangular parallelepiped, and each connecting face generally forming a plane which is perpendicular to said so-called stacking direction and which is parallel to the length and width of the rectangular parallelepiped.
• such a geometry makes it possible to obtain an extended exchange surface, while limiting the pressure losses induced by changes in flow direction of the primary and secondary fluids.
• such a geometry maximizes the size of the exchanger assembly, because it maximizes the occupation of a brazing furnace.
• the primary compartments and the secondary compartments are totally or partially delimited by walls of flexible material, the flexible material preferably being selected from the group consisting of a stainless steel, aluminum, an aluminum alloy and low-temperature soft organic materials, such as polytetrafluoroethylene.
• the set of heat exchangers according to the invention further comprises an additional heat exchanger called subcooler, the subcooler being in fluid communication with one of the exchangers of heat juxtaposed.
• each heat exchanger comprises, on its periphery, primary supply boxes and secondary supply boxes which are shaped to introduce or discharge primary fluid or secondary fluid respectively in or outside the primary passages or secondary passages, the primary supply boxes and the secondary supply boxes being preferably arranged so that the primary fluid flows in the opposite direction of the secondary fluid.
• the primary power boxes and the secondary power boxes allow a so-called "countercurrent" heat exchange, which is particularly effective.
• each heat exchanger comprises spacers which define primary passages or secondary passages and which are formed by offset type of exchange waves having a linear density greater than 800 waves per meter, having an offset length of less than 5 mm and having a wave height of between 3 m and 20 mm, preferably between 5 mm and 15 mm.
• each heat exchanger is configured so that the direction of flow of the primary and secondary fluids in each exchanger is a transverse direction extending along the width of a heat exchanger.
• the subject of the present invention is a cryogenic air separation installation, comprising at least one set of heat exchangers according to the invention, the primary fluid being compressed air at high pressure, the secondary fluid being low-pressure dinitrogen.
• FIG. 1 is a schematic perspective view of a set of heat exchangers according to a first embodiment of the invention
• Figure 2 is a section along the plane II in Figure 1;
• Figure 3 is a section along the plane III in Figure 1;
• FIG. 4 is an enlarged view of detail IV in FIG. 2;
• Figure 5 is an enlarged view of detail V in Figure 3;
• Figure 6 is a view similar to Figure 4 of an alternative embodiment in Figure 4;
• Figure 7 is a view similar to Figure 4 of an alternative embodiment in Figure 4;
• Figure 8 is a section along the line VIII-VIII; and Figure 9 is a schematic perspective view of a set of heat exchangers according to a second embodiment of the invention.
• Figure 10 is a schematic perspective view of a set of heat exchangers according to a third embodiment of the invention.
• Figure 1 1 is a section along the plane XI in Figure 10; and Figure 12 is a schematic perspective view of a set of heat exchangers according to a fourth embodiment of the invention.
• Figures 1, 2 and 3 illustrate a set of heat exchangers 1, to form a non-contact heat transfer unit 5 between a primary fluid and a secondary fluid.
• the unit 5 is intended to be integrated in a cryogenic air separation installation, which comprises the set of heat exchangers 1, and in which the primary fluid is high pressure compressed air, and the secondary fluid of the low pressure nitrogen. Compressed air is the circulating fluid and the nitrogen is the refrigerant. Nevertheless, the primary and secondary fluids could be other fluids, depending on the application of the heat transfer unit.
• the heat exchanger assembly comprises a plurality of heat transfer fluids and / or a plurality of refrigerants.
• the heat exchanger assembly 1 comprises two heat exchangers 10 and 50 which are juxtaposed along respective adjacent surfaces January 1 and 51.
• the adjacent surfaces 1 1 and 51 are flat.
• the heat exchanger 10 comprises a stack of several plates, some of which are shown schematically in FIG. 1 with reference numeral 12.
• the heat exchanger 50 comprises a stack of several plates some of which are shown schematically in FIG. reference 52.
• the plates 12 are arranged parallel to each other in a so-called stacking direction Z, so as to delimit i) primary passages 12P shaped for the flow of the primary fluid, and ii) secondary passages 12S shaped for the flow secondary fluid.
• the primary passages 12P and the secondary passages 12S follow one another in a predetermined stacking pattern (here "-Primary-Secondary- Primary-").
• each primary passage 12P alternates with a secondary passage 12S.
• the stacking pattern could be of the type comprising two secondary passages surrounding a primary passage ("- Secondary-Primary-Secondary-").
• the plates 52 are arranged parallel to each other in a so-called stacking direction Z, so as to delimit i) primary passages 52P shaped for the flow of the primary fluid, and ii) secondary passages 52S shaped to the secondary fluid flow.
• the primary passages 52P and the secondary passages 52S follow each other in a predetermined stacking pattern. In the example of FIGS. 1 to 3, each primary passage 52P alternates with a secondary passage 52S.
• the stack of the plates 12 of the first exchanger 10 defines a first connection face 12F which is fluidly connected to the primary passages 12P of the first exchanger 10.
• the stack of the plates 52 of the second exchanger 50 defines a second connection face 52F which is fluidly connected to the primary passages 52S of the second exchanger 50.
• the heat exchanger 10 or 50 has the overall shape of a rectangular parallelepiped.
• the width and the length of the heat exchanger 10 or 50 are respectively measured along X and Y axes.
• first connecting face 12F and the second connecting face 52F each have the overall shape of a rectangle.
• the first heat exchanger 10 and the second heat exchanger 50 each have the overall shape of a rectangular parallelepiped.
• the first exchanger 10 and the second exchanger 50 are arranged so that the first connecting face 12F is adjacent to the second connecting face 52F.
• the first connecting face 12F and the second connecting face 52F are parallel and arranged opposite one another.
• the first connecting face 12F is generally flat and perpendicular to the plates 12 of the first exchanger 10.
• the second connecting face 52F is generally flat and perpendicular to the plates 52 of the second exchanger 50.
• the heat exchanger 10 has spacers 14 which extend between the plates 12 so as to define i) primary channels 14P shaped for the flow of the primary fluid. Between two other successive plates 12, outside the plane of FIG. 2, the spacers 14 define ii) unrepresented secondary channels shaped for the flow of the secondary fluid.
• the spacers are usually called exchange waves or "fins".
• the heat exchanger 50 has spacers 54 which extend between the plates 52 so as to define i) primary channels 54P shaped for the flow of the primary fluid, or secondary channels not shown out of the plane of Figure 2.
• the heat exchanger 10 comprises means for fluidically connecting the heat exchangers 10 and 50.
• Each heat exchanger 10 or 50 has the overall shape of a rectangular parallelepiped.
• the stacking direction Z is parallel to the height of the rectangular parallelepiped.
• the spacers 14 or 54 extend parallel to the length of the rectangular parallelepiped.
• the first connecting face 12F has the overall shape of a rectangle whose edges are defined by the length, in the longitudinal direction X, and the height, in the stacking direction Z, of the first heat exchanger 10.
• the second connecting face 52F generally has the shape of a rectangle whose edges are defined by the length, in the longitudinal direction X, and the height, in the stacking direction Z, of the second heat exchanger 50.
• the first connecting face 12F and the second connecting face 52F each generally form a flat surface 1 1 or 51 which is perpendicular to the stacking direction Z and which is parallel to the length (X direction) and to the width (direction Y) of the rectangular parallelepiped formed by the first or second exchanger 10 or 50.
• Each heat exchanger 10 or 50 includes, on its periphery, primary supply boxes 16 or 56 and secondary supply boxes 18 or 58.
• the primary supply boxes 16 or 56 and the secondary supply boxes 18 or 58 are shaped to introduce or discharge primary fluid or secondary fluid respectively into or out of primary passages 12P or secondary passages 12S.
• the primary supply boxes 16 or 56 and the secondary supply boxes 18 or 58 are here arranged so that the primary fluid flows in the opposite direction of the secondary fluid, ie "against the current".
• the unit 5 further comprises primary collectors 6 and secondary collectors 7.
• the primary collectors 6 channel all or part of the primary fluid under high pressure and the secondary collectors 7 channel all or part of the secondary fluid under low pressure.
• a series of spacers 14 or 54 is arranged to provide at least one respective distribution space 21 P, 21 S or 61 P , 61 S.
• the distribution space 21 P, 21 S or 61 P, 61 S is devoid of spacers 14 or 54 and is delimited by the two successive plates 12 or 52 and the respective connecting face 12 or 52 , so that this distribution space 21 P, 21 S or 61 P, 61 S is in fluid communication with all or part of the primary channels 14P or secondary 14S defined by this series of spacers 14 or 54.
• the size of the distribution space in the longitudinal direction X is typically of the order of 50 mm to 100 mm.
• one or more space (s) of distribution may be devoid of any spacer or may contain spacers said distribution, that is to say, allowing a circulation of fluids in direction of the primary supply boxes 16 or 56 and / or secondary supply boxes 18 or 58, or alternatively may include a mechanical support device for brazing with maintaining a free flow of fluid transversely in the plan of the passage.
• the dispensing spaces may comprise a solid aluminum foam, a bar machined so as to remove a maximum of material while resisting pressure, pins or a pimpled sheet.
• the distribution space 21 P or 61 P is in fluid communication with primary channels 14P, while the distribution space 21 S or 61 S is in fluid communication with all or part of the secondary channels 14S.
• each series of spacers comprises all the spacers 14 or 54 which are arranged between the two successive plates 12 or 52.
• the distribution space 21 P or 61 P has the same flow section as the corresponding primary passage 12P or 52P.
• the distribution space 21P or 61P may have a flow section greater than the corresponding primary passage 12P or 52P.
• the distribution space 21 S or 61 S has the same flow section as the corresponding secondary passage 12S or 52S.
• the set of heat exchangers 1 comprises an enclosure 30 which is delimited by the first connecting face 12F, by the second connecting face 52F and by an enclosure volume V30 which extends between the first face 12F and the second 52F connection face.
• the V30 speaker volume is defined by speaker walls that surround the speaker volume.
• the enclosure 30 has primary compartments 30P and secondary compartments 30S which follow each other in the direction Y which is transverse to the stacking direction Z.
• the set of heat exchangers 1 comprises primary compartments 30P which are arranged in the enclosure volume V30 to channel all or part of the primary fluid between the first exchanger 10 and the second exchanger 50 through the first face connection 12F and the second connection face 52F.
• the set of heat exchangers 1 comprises secondary compartments 30S which are distinct from the primary compartments 30P.
• the secondary compartments 30S are arranged in the enclosure volume V30 to channel all or part of the secondary fluid between the first exchanger 10 and the second exchanger 50 through the first connecting face 12F and the second connecting face 52F.
• Each primary compartment 30P is in fluid communication with two respective primary passages 12P and 52P which respectively belong to the two heat exchangers 10 and 50, so as to allow the flow of the primary fluid between the heat exchangers 10 and 50, such as the symbolize arrows in Figure 2 or 4.
• each secondary compartment 30S is in fluid communication with two respective secondary passages 12S and 52S respectively belonging to the two heat exchangers 10 and 50, so as to allow the flow of the secondary fluid between the heat exchangers 10 and 50, as symbolize arrows in Figure 3 or 5.
• the primary compartments 30P are formed by primary lines 31P which each extend between the adjacent surfaces 11 and 51 and parallel to the stacking direction Z.
• primary pipes 31 P are distributed at regular intervals in the direction Y which is transverse to the stacking direction Z.
• the primary lines 31 P are in fluid communication with the primary passages 12P and 52P of each heat exchanger 10 or 50, so as to allow the flow of the primary fluid between the heat exchangers 10 and 50.
• each secondary compartment 30S is formed by the walls of the enclosure 30 and the walls of two successive primary pipes 31 P.
• each primary pipe 31 P is in the form of a prism with a rectangular base and whose generatrices are parallel to the stacking direction Z. Consequently, the walls of the primary pipes 31P are flat and parallel. to the stacking direction Z.
• a closure member 122S or 162S is placed on the respective primary line 131P so as to prevent the flow of secondary fluid in this primary line 131P.
• FIG. 6 illustrates part of a set of heat exchangers 101 according to an alternative embodiment of the invention.
• the description of the heat exchanger assembly 1 given above in relation with FIGS. 1 to 4 may be transposed to the set of heat exchangers 101, with the exception of the notable differences set out below.
• a component of the heat exchanger assembly 101 that is identical or corresponding, in structure or function, to a component of the heat exchanger assembly 1 has the same reference numeral increased by 100.
• the heat exchanger assembly 101 differs from the heat exchanger assembly 1, since each 131 P primary pipe is composed of three parts interconnected by complementary shapes, in this case dovetails 133 .
• FIGS. 7 and 8 illustrate part of a set of heat exchangers which is in accordance with another variant embodiment of the invention and which differs from the set of heat exchangers 101, since the parts are secured by complementary shapes that can define latching elements.
• FIGS. 1 to 4 illustrate a set of heat exchangers 301 according to a second embodiment of the invention.
• the description of the heat exchanger assembly 1 given above in relation with FIGS. 1 to 4 may be transposed to the set of heat exchangers 301, with the exception of the notable differences set forth below.
• a component of the heat exchanger assembly 301 that is identical or corresponding, in structure or function, to a component of the heat exchanger assembly 1 has the same numerical reference plus 300. heat exchangers 310 and 350.
• the heat exchanger assembly 101 differs from the heat exchanger assembly 1 because the heat exchanger assembly 101 includes an additional heat exchanger called subcooler 370.
• the subcooler 370 is fluid communication with the heat exchanger 350.
• FIGS. 1 to 4 illustrate a set of heat exchangers 401 according to a third embodiment of the invention.
• the description of the heat exchanger assembly 1 given above in relation to FIGS. 1 to 4 may be transposed to the set of heat exchangers 401, with the exception of the notable differences set forth below.
• a component of the heat exchanger assembly 401 that is identical or corresponding, in structure or function, to a component of the heat exchanger assembly 1 has the same numerical reference plus 400.
• the heat exchanger assembly 401 differs from the heat exchanger assembly 1, mainly because the first heat exchanger 410 and the second heat exchanger 450 are arranged side by side.
• the first connecting face 412F and the second connecting face 452F are oriented in respective normal directions N412F and N452F which are parallel.
• the enclosure 430 and its enclosure volume are generally in the form of a half-cylinder.
• first connecting face 412F and the second connecting face 452F are arranged to have a confused edge, as shown in FIGS. 10 and 11.
• the primary lines 431 P comprise i) a longitudinal collector 431 C of tubular shape with circular section, and ii) primary tubes 431 T fluidically connecting the collector 431 C to the first connection face 412F and to the second connection face 452F.
• the heat exchanger assembly 401 differs from the heat exchanger assembly 1, because the enclosure 430, and thus the enclosure volume, forms the secondary compartment integrally. This secondary compartment therefore extends around the primary compartments formed by the primary conduits 431 P.
• the heat exchanger assembly 401 comprises sealing means between, on the one hand, the enclosure and, on the other hand , the first connection face and the second connection face.
• FIG. 12 illustrates a set of heat exchangers 501 according to a fourth embodiment of the invention.
• the description of the heat exchanger assembly 1 given above in relation to FIGS. 1 to 4 can be transposed to the set of heat exchangers 501, with the exception of the notable differences set out below.
• a component of the heat exchanger assembly 501 that is identical or corresponding, in structure or function, to a component of the heat exchanger assembly 1 has the same numerical reference plus 500.
• the heat exchanger assembly 501 differs from the heat exchanger assembly 1, mainly because the first connection face 512F and the second connection face 552F are orthogonal to each other. 'other.
• the first connection face 512F and the second connection face 552F are arranged to have a confused edge.
• the enclosure 530 has the overall shape of a quarter cylinder.

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• Engineering & Computer Science (AREA)
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• Thermal Sciences (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

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• 2012
  • 2012-09-19 FR FR1258783A patent/FR2995671B1/fr not_active Expired - Fee Related
• 2013
  • 2013-09-09 US US14/428,862 patent/US10330391B2/en active Active
  • 2013-09-19 WO PCT/FR2013/052168 patent/WO2014044979A2/fr active Application Filing
  • 2013-09-19 EP EP13779266.9A patent/EP2898279B1/de active Active
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  • 2013-09-19 CN CN201380048482.1A patent/CN105190214B/zh active Active
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