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
  • F25J3/04636—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 using a hybrid air separation unit, e.g. combined process by cryogenic separation and non-cryogenic separation techniques
• • 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
  • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
  • F28F9/02—Header boxes; End plates
  • F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
  • F28F9/027—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes
  • F28F9/0273—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of distribution pipes with multiple holes
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • 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
  • F28F9/0278—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits in the form of stacked distribution plates or perforated plates arranged over end plates
• • 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
  • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
• • 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
  • F25J2290/32—Details on header or distribution passages of heat exchangers, e.g. of reboiler-condenser or plate heat exchangers

Definitions

• the present invention relates to a heat exchanger comprising a dispensing device configured to dispense a refrigerant into the heat exchanger.
• the heat exchanger can in particular be a vaporizer used in an air separation column by cryogenic distillation to ensure the vaporization of a column bottom liquid, for example liquid oxygen, by heat exchange with a caloric gas, for example air or nitrogen.
• the present invention finds particular application in the field of gas separation by cryogenics, in particular the separation of air by cryogenics (known by the acronym "ASU" for air separation unit) exploited for the production of oxygen gas under pressure.
• ASU air separation unit
• the present invention can be applied to a heat exchanger which vaporizes a liquid flow, for example oxygen, nitrogen and / or argon by heat exchange with a gas.
• the heat exchanger is in the tank of a distillation column, it can constitute a vaporizer operating as a thermosiphon for which the exchanger is immersed in a bath of liquid descending the column or a vaporizer operating in vaporization with a film fed directly by the liquid falling from the column and / or by a recirculation pump.
• phase change exchangers consist of brazed plate and finned aluminum exchangers, which make it possible to obtain very compact members with a large exchange surface.
• These exchangers consist of plates between which fins are inserted, thus forming a stack of vaporization passages and condensation passages, one intended to vaporize refrigerant and the others to condense a caloric gas.
• WO-A-201 11 10782 discloses a dispensing device comprising parallel plates, which define passages for the refrigerant, and a plurality of fins which extend in each passage and which have orifices for distributing the refrigerant in the lateral direction.
• EP-A-0130122 A known solution of EP-A-0130122 is to drill holes in the parallel plates of the dispensing device in order to achieve a rough predistribution of the refrigerant liquid along the passages for said liquid.
• the number of orifices arranged along the heat exchanger is limited so as not to complicate its manufacture or to weaken its structure and the effect of uniformization of the distribution of the liquid remains insufficient.
• the present invention is intended in particular to solve, totally or partially, the problems mentioned above, by providing a dispensing device in which the distribution of the refrigerant is as uniform as possible.
• the subject of the invention is a heat exchanger configured for transferring heat from at least one heat-generating fluid, for example nitrogen, to at least one refrigerant, for example oxygen
• the heat exchanger comprising at least plates arranged parallel to each other so as to define a first series of passages configured to channel refrigerant liquid generally in a longitudinal direction, extending in the vertical direction during operation, each passage being defined between two successive plates, and a second series of passages configured to channel a circulating fluid globally in the longitudinal direction, each passage being defined between two successive plates, the passages of the second series being interposed between two passages of the first series, at least one connected refrigerant inlet to discharge the refrigerant only into the passages of the first series and means of distribution, located in the upper end of the exchanger in passages of the first series only, comprising
• each passage of the first series housing a plurality of fins succeeding one another along the longitudinal direction each fin having orifices configured to allow flow of the refrigerant;
• At least one fin having an upper portion and a lower portion, the altitude of the upper portion being greater than the altitude of the lower portion when the dispensing device is in use and the longitudinal direction extends in the vertical direction,
• said at least one lower portion and the plate secured to said at least one lower portion defining at least one distribution channel configured for channeling refrigerant in the lateral direction
• the orifices of said at least one fin being formed by overflow openings in said at least one upper portion, the overflow openings being configured so that the refrigerant flows through the overflow openings when the at least one distribution channel is full of refrigerant.
• the or each distribution channel forms a kind of gutter extending between the overflow openings and an intersection of the lower portion and the plate secured to this lower portion.
• the or each distribution channel is generally horizontal when the dispensing device is in use.
• the cooperation of the or each distribution channel with the overflow openings of the fin (s) allows to distribute the refrigerant as evenly as possible in the lateral direction, which limits or even avoids the risk of solid deposition of impurities in the heat exchanger.
• the plates extend in two dimensions, length and width, respectively in the longitudinal direction and the lateral direction.
• the fins In each passage, the fins have elongated shapes and they extend along the width (lateral direction) of the two successive plates.
• the longitudinal direction is vertical when the dispensing device is in use.
• the refrigerant flows globally in the longitudinal direction and by gravity. So the refrigerant flows globally vertically and downward.
• the dispensing device can comprise a number of plates greater than 20, or even greater than 100. These plates thus form a stack of plates, between which are defined passages of refrigerant liquid, possibly alternating with ducts for the circulating fluid.
• the dispensing device may have a number of refrigerant passages greater than 10, or even greater than 50.
• the dispensing device In use, the dispensing device is traversed by the refrigerant.
• the dispensing device has i) an upstream portion configured for the refrigerant inlet, and ii) a downstream portion configured for the refrigerant outlet.
• the fins extend between this upstream part and this downstream part.
• each passage has a parallelepipedal and flat shape.
• the gap between two successive plates is small in front of the length and the width of each successive plate.
• all or part of the fins extends from one plate to the next plate. In other words, these fins are in contact with the two plates. This construction makes it possible to braze the fins on the two plates, which increases the mechanical strength of the dispensing device.
• following means that a direction is substantially parallel or substantially collinear with another direction or plane.
• the volume of a respective distribution channel is less than 15%, preferably less than 10%, of the total volume defined:
• each distribution channel prevents fins having overflow openings generate too high pressure drop.
• a low pressure drop avoids reducing the flow of refrigerant through the fins having overflow openings, which optimizes the regulation of this flow.
• the fins having overflow openings therefore rather fulfill a function of distribution of the refrigerant, generating only a small loss of load.
• Each distribution channel is defined by at least a lower portion and the plate secured to said at least a lower portion.
• the overflow openings are distributed on a fin uniformly in the lateral direction.
• uniformly distributed overflow openings maximize the uniformity of the refrigerant distribution.
• some overflow openings may be non-uniformly distributed in the lateral direction.
• an opening report having:
• the total area of overflow openings in a fin with overflow openings for numerator, the total area of overflow openings in a fin with overflow openings, and
• each overflow opening has an area of between 1.5 mm 2 and 10.0 mm 2 , preferably between 2.0 mm 2 and 5.0 mm 2 .
• overflow openings have ellipse shapes, for example circular.
• a shape has a width of the overflow opening which increases gradually, which limits the height of the refrigerant when the flow of refrigerant increases.
• overflow openings have triangular shapes pointing towards said at least one lower portion.
• a shape has a width of the overflow opening which increases gradually, which limits the height of the refrigerant when the flow of refrigerant increases.
• an interval, measured along the lateral direction, between two successive overflow openings is between 1 mm and 6 mm.
• such an interval helps to ensure a uniform distribution of the refrigerant in the lateral direction, while minimizing the pressure drop generated by the fins having overflow openings.
• said interval is constant for the overflow openings of at least one fin.
• Such an interval contributes to maximizing the uniformity of the refrigerant distribution along the lateral direction.
• a minimum distance between i) an overflow opening and ii) the plate secured to said at least one lower portion is between 1 mm and 4 mm, the minimum distance preferably being the same. for the majority or all of the overflow openings of a respective fin.
• several fins have respective upper portions having overflow openings.
• the overflow openings present in a fin are positioned offset in the lateral direction relative to the overflow openings present in the neighboring vane.
• said offset between the overflow openings present in two neighboring fins represents between 40% and 60% of the length of said gap.
• the overflow openings of two successive fins in the longitudinal direction are arranged substantially staggered.
• At least one fin has a flat shape and extends to said two successive plates and obliquely to each of said two successive plates so as to form, in section in a plane perpendicular to the plates and in the lateral direction, an acute oblique angle, the oblique angle preferably being between 30 ° and 60 °, more preferably between 40 ° and 50 °.
• each fin has, parallel to the longitudinal direction, a length of between 4 mm and 10 mm, and in which each fin has, parallel to the direction lateral, a width of between 4 mm and 10 mm, each fin may for example have a length and an equal width.
• such a length and such a width can incorporate a large number of fins in the dispensing device, which increases the uniformity of the distribution of the refrigerant.
• each fin has a fixing portion which is fixed to a plate, for example by brazing.
• At least one, preferably each, overflow opening is defined by a through orifice.
• at least one overflow opening may be defined by a notch extending to an edge of the corresponding fin.
• the dispensing device comprises at least one fin having orifices and placed upstream of the fin (s) having overflow openings, the orifices being distributed in the lateral direction, the number of overflow openings per fin being greater than 3 times, preferably 5 times, the number of orifices per fin.
• the fins having orifices can fulfill a function of controlling the flow rate of the refrigerant entering the distribution device, generating a high pressure drop, whereas the fins having overflow openings rather fulfill a distribution function, generating only a small loss of load. This limits the number of components to be assembled in the dispensing device, because the fins having orifices dispense with providing a perforated bar like that of WO-A-201 10782 to generate a high pressure drop.
• At least two fins having orifices having orifices, the number of orifices per fin increasing in the direction from upstream to downstream.
• the interval between two successive orifices, measured along the lateral direction of the fin having the most upstream orifices, is between 40 mm and 60 mm, and in which the interval between two successive orifices, measured in the lateral direction, of the fin having the most downstream orifices is between 6 mm and 20 mm.
• the fin having the orifices located furthest upstream has the least orifices, while the fin having the orifices situated furthest downstream has the most orifices; the fins having overflow openings being located downstream of the fin having orifices located furthest downstream.
• the pressure drop generated by the fins having orifices decreases from upstream to downstream, while increasing the uniformity of the distribution of the refrigerant liquid.
• At least one fin may have, in addition to overflow openings, at least one bleed hole which is provided at the bottom of the lower portion.
• the distribution channel is then formed of several sections separated two by two by a purge hole through which the refrigerant can flow.
• a purge hole makes it possible to empty the distribution channel.
• the area of the or each bleed hole is smaller than the area of an overflow opening.
• the total area of the openings, or even overflow openings, for a given fin increases in the longitudinal direction, preferably by increasing the number and / or the area of the openings.
• the subject of the present invention is a dispensing method for dispensing a refrigerant liquid in a heat exchanger, the dispensing method comprising the steps of:
• the subject of the present invention is a heat exchanger, configured to transfer heat from at least one heat-generating fluid, for example dinitrogen, to at least one refrigerant, for example oxygen, the heat exchanger.
• the heat exchanger comprising at least one heat exchange unit, at least one refrigerant inlet, the heat exchanger being characterized in that it comprises a dispensing device according to any one of the preceding claims, the dispensing device being arranged to supply the refrigerant unit with the heat exchange unit.
• Figure 1 is a schematic sectional view, in a plane perpendicular to the lateral direction, of a portion of a dispensing device according to a first embodiment of the invention
• Figure 2 is a schematic sectional view along the plane II in Figure 1 which is parallel to the longitudinal direction and the lateral direction of the portion of the dispensing device of Figure 1;
• Figure 3 is a schematic sectional view, in a plane perpendicular to the lateral direction, of a portion of a heat exchanger comprising the dispensing device according to the first embodiment of the invention
• Figure 4 is a view similar to Figure 1 illustrating the operation of the dispensing device of Figure 3;
• FIG. 5 is a view similar to Figure 2 illustrating the operation of the dispensing device of Figure 3;
• Figures 6 and 7 are views similar respectively to Figures 1 and 2 and illustrating a portion of a dispensing device according to a second embodiment of the invention
• FIGS. 8 and 9 are views similar respectively to FIGS. 1 and 2 and illustrating a portion of a dispensing device according to a third embodiment of the invention.
• Figure 10 is a view similar to Figure 1 and illustrating a portion of a dispensing device according to a fourth embodiment of the invention.
• Figure 11 is a view similar to Figure 10 and illustrating a portion of a dispensing device according to a fifth embodiment of the invention.
• Figure 12 is a view similar to Figure 10 and illustrating a portion of a dispensing device according to a sixth embodiment of the invention.
• Figure 13 is a view similar to Figure 1 and illustrating a portion of a dispensing device according to a seventh embodiment of the invention
• Figure 14 is a view similar to Figure 1 and illustrating a portion of a dispensing device according to an eighth embodiment of the invention; and Figure 15 illustrates a method of dispensing according to the invention.
• FIGs 1, 2 and 3 illustrate a dispensing device 1 which is configured to dispense a refrigerant F1, in this case liquid oxygen, in a heat exchanger 2.
• the heat exchanger 2 is configured to transfer heat of a heat transfer fluid F2, here nitrogen gas, to the refrigerant, here oxygen.
• the refrigerant F1 ( Figure 3) is in a holding tank 3 belonging to the heat exchanger 2.
• the dispensing device 1 comprises plates 1 1, 12, 13, 14 and the like which are arranged parallel to each other.
• the dispensing device 1 comprises a number of stacked plates approximately equal to 200.
• Each of the plates 1 1, 12, 13, 14 extends in two dimensions, respectively its length and its width, which are respectively defined in a longitudinal direction X and a lateral direction Y.
• the lateral direction Y is orthogonal to the longitudinal direction X and is parallel to the plates 1 1, 12, 13, 14.
• the longitudinal direction X is vertical when the dispensing device 1 is in use.
• the refrigerant F1 flows globally vertically and in the downward direction.
• the plates 1 1, 12, 13, 14 are arranged to define passages 20, 30 and the like which are configured to channel the refrigerant F1 generally in the longitudinal direction X.
• Each passage 20 or 30 is defined between two successive plates. 1 1, 12, 13, 14.
• Each passage 20, 30 has a parallelepipedal and flat shape. The distance between two successive plates 1 1 and 12 is small in front of the length (along X) and width (along Y) of each successive plate 1 1 or 12.
• the passages 20, 30 of F1 refrigerant alternates with parallelepipedic and flat shaped passages not shown for the circulating fluid.
• the dispensing device 1 further comprises fins 21, 22, 23, 24 and 31, 32, 33, 34, which extend respectively in each passage 20 and 30 generally in the lateral direction Y.
• the fins 21, 22, 23, 24 extend in the passage 20, while the fins 31, 32, 33, 34 extend in the passage 30.
• the fins 21, 22, 23, 24, 31, 32, 33 and 34 have elongate shapes and they extend in the lateral direction Y of the two successive plates 1 1 and 12 or 13 and 14.
• Each fin 21, 22, 23, 24, 31, 32, 33 or 34 has a flat shape and extends to the two successive plates 1 1 and 12 or 13 and 14.
• Each fin 21 or equivalent extends obliquely to each of the two successive plates 1 1 and 12 or 13 and 14 so as to form, in section in a plane perpendicular to the plates and the lateral direction Y (here the plane of Figure 1), an oblique angle A21 which is acute.
• the oblique angle A21 is here 45 degrees.
• Each fin 21 or equivalent has, parallel to the longitudinal direction X, a length X21 which is here equal to 5 mm.
• Each fin 21 or equivalent has, parallel to the lateral direction Y, a width Y21 which is here equal to 5 mm, thus equal to the length X21.
• Each fin 21 or equivalent here has a fastening portion 21 .5 which is flat and is soldered to a respective plate 11 or equivalent. All the fins 21, 22, 23, 24 extend from a plate 1 1 to the successive plate 12. In other words, these fins 21, 22, 23, 24 are in contact with the two plates 1 1 and 12. The fins 21, 22, 23, 24 are soldered to the two plates 11 and 12.
• Each passage 20 or 30 here houses four fins, respectively 21, 22, 23, 24 and 31, 32, 33, 34, which follow one another in the longitudinal direction X.
• Each fin 21 or equivalent has orifices 40, which are configured to allow the flow of the refrigerant F1 through the respective fin 21 or equivalent.
• each fin 21, 22, 23, 24, 31, 32, 33 or 34 has an upper portion 21 .1 and equivalent and a lower portion 21 .2 and equivalent.
• the altitude of the upper portion 21 1 is greater than the altitude of the lower portion 21 2.
• Each lower portion 21 .2 or equivalent and the respective plate, 1 1 or equivalent, secured to the lower portion 21 .2 define a distribution channel 42, which is configured to channel refrigerant F1 in the lateral direction Y.
• each fin 21 or equivalent are formed by overflow openings 40 which are located in each respective upper portion 21 .1 or equivalent. All fins 21 and the like have respective top portions 21 and equivalent which have overflow openings 40. For obvious reasons of clarity, all overflow openings 40 are not referenced in FIGS. 1-5.
• the overflow openings 40 of each fin 21 or equivalent are configured so that the refrigerant F1 flows through the overflow openings 40 when the distribution channel 42 is full of refrigerant F1.
• All the overflow openings 40 have here triangular shapes pointing to each respective lower portion 21 .2.
• the overflow openings 40 are here distributed over a respective fin 21 or equivalent in a uniform manner along the lateral direction Y.
• a gap D40, measured along the lateral direction, between two successive overflow openings 40, is here constant and equal to 4 mm for the overflow openings 40 of each fin 21 or equivalent.
• a minimum distance H40 between i) an overflow opening 40 and ii) the plate 1 1 secured to the respective lower portion 21 .2 is equal to 3 mm. This minimum distance H40 is the same (constant) for all the overflow openings 40 of a respective fin 21 or equivalent.
• the overflow openings 40 present in a fin 21 are positioned offset in the lateral direction Y with respect to the overflow openings 40 present in the neighboring vane 22.
• the offset D40 / 2 between the overflow openings 40 present in two adjacent fins 21 and 22 here represent 50% of the length of the interval D40.
• Each overflow opening 40 here has an area equal to 4 mm 2 .
• the total area of the overflow openings 40 located in a fin 21 or equivalent having overflow openings 40 the total area of the overflow openings 40 located in a fin 21 or equivalent having overflow openings 40
• FIGS. 4 and 5 illustrate more particularly the operation of the dispensing device 1.
• the refrigerant F1 is shown in gray. As shown in FIGS. 4 and 5, the refrigerant F1 overflows with each overflow opening 40 and fills each distribution channel 42 with the fins 21, 22, 23, 24, 31, 32, 33 and 34.
• each distribution channel 42 (greyed out in FIG. 4 or 5) is less than 10% of the total volume (in grid in FIG. 4) delimited:
• FIG. 15 illustrates a dispensing method according to the invention for distributing the refrigerant F1 in the heat exchanger 2. This dispensing method comprises in particular the steps:
• each distribution channel 42 is generally horizontal when the dispensing device 1 is in use. The cooperation of each distribution channel 42 with the overflow openings 40 makes it possible to distribute the refrigerant F1 as uniformly as possible along the lateral direction Y.
• the heat exchanger 2 comprises a heat exchange unit, partially visible with the reference 4 in Figure 3.
• the heat exchanger 2 comprises a heat transfer fluid inlet F2 and an inlet 8 of refrigerant F1.
• the inlet 8 is here formed by perforations of a perforated bar 9.
• the heat exchanger 2 further comprises the dispensing device 1, which is arranged to supply the refrigerant unit F1 with the heat exchange unit 4.
• the heat exchanger 2 includes a retention tank 3, in which the refrigerant F1 is stored, before flowing to the dispensing device 1. In use, the dispensing device 1 is traversed by the refrigerant F1.
• Second and third embodiments of the invention have in common that the total area of all overflow openings 140, 240, 241 for a given fin 121, 122, 123, 124 increases from top to bottom. This can be accomplished by increasing the number and / or area of openings.
• Figures 6 and 7 illustrate a portion of a dispensing device 101 according to the second embodiment of the invention.
• the dispensing device 101 is similar to the dispensing device 1, the description of the dispensing device 1 given above in relation to FIGS. 1 to 5 can be transposed to the dispensing device 101, with the exception of notable differences set out below.
• a component of the dispensing device 101 identical or corresponding, in structure or function, to a dispensing device component 1 has the same numerical reference increased by 100.
• plates 1 1 1, 1 12, fins 121 are defined.
• the dispensing device 101 differs from the dispensing device 1 because the overflow openings 140 have elliptical shapes.
• each orifice of each fin 121, 122, 123, 124 forms an overflow opening 140.
• the fins 121, 123 have the same number of overflow openings but the areas of the openings 140 of the vane 123, lower are smaller than those of the openings 140 of the upper vane 123.
• the openings 140 of the fin 121 are fewer but have the same shape as that of the fin 122 below. This is also the case for the apertures of the fins 123 and 124.
• the total area of the openings increases in the direction going from the upstream to the downstream direction (downward direction in FIG. 7) and therefore downwards during the operation of the exchanger.
• Figures 8 and 9 illustrate a portion of a dispensing device 201 according to a third embodiment of the invention.
• the dispensing device 201 is similar to the dispensing device 101, the description of the dispensing device 101 given above in relation to FIGS. 6 and 7 can be transposed to the dispensing device 201, with the exception of notable differences set out below.
• a component of the distribution device 201 identical or corresponding, by structure or function, to a distribution device component 101 has the same numerical reference increased by 100.
• plates 21, 212, fins 221, 222 are defined.
• the dispensing device 201 differs from the dispensing device 101, since two fins 221 and 222 have orifices 241 which do not form overflow openings 240. Only the fins 223 and 224 have overflow openings 240. In fact, the orifices 221 and 222 have openings 241 which do not form overflow openings 240. 241 are few on the fins 221 and 222, so that the orifices 241 are rather embedded when the dispensing device 201 is in use.
• the fins 221 and 222 are placed upstream of the fins 223 and 224 having overflow openings 240.
• the orifices 241 are distributed in the lateral direction.
• the number of overflow openings 240 per fin 223 or 224 is greater than 5 times the number of orifices 241 per fin 221 or 222.
• the number of orifices 241 per fin 221 or 222 increases in the direction from upstream to downstream (downward direction in FIG. 9) and therefore downwards during the operation of the exchanger.
• the interval D241 .1 between two successive orifices 241, measured along the lateral direction of the fin 221 having the orifices 241 situated furthest upstream (at the top in FIG. 9), is here equal to 51 mm.
• the gap 1 1 -12 between the plates 1 1 and 12 is approximately equal to 51 mm.
• the interval D241.2 between two successive orifices 241, measured along the lateral direction, of the fin 222 having the orifices 241 situated the most downstream is here equal to 20 mm.
• the fins 221 and 222 having orifices 241 can fulfill a function of controlling the flow rate of the refrigerant entering the dispensing device 201, generating a high pressure drop, while the fins 223 and 224 having overflow openings 240 rather perform a distribution function, generating only a small pressure drop.
• Figure 10 illustrates a portion of a dispensing device 301 according to a third embodiment of the invention.
• the dispensing device 301 is similar to the dispensing device 1, the description of the dispensing device 301 given above in relation with FIGS. 1 to 5 can be transposed to the dispensing device 301, with the exception of notable differences set out below.
• a component of the dispensing device 301 that is identical or corresponding, in structure or function, to a dispensing device component 1 has the same numerical reference increased by 300.
• the dispensing device 301 differs from the dispensing device 101, since the fins 321, 322, 323, 324 and the plates 31 1 and 312 are disposed in an area of the dispensing device 301 where the passage 320 is relatively wide, since this zone is devoid of the conduits of circulating fluid F2. Indeed, each duct of circulating fluid F2 is obstructed by a shutter 350 and the unrepresented outlet of the heat-exchange fluid ducts F2 is on a lateral face of the dispensing device 301.
• the passages 320 can be deployed over the entire height, measured in the Z direction, of the dispensing device 301, while the passages 20 and 30 alternate with respective fluid conduits.
• the gap 31 1 .312 between the plates 31 1 and 312 is approximately equal to 1 10 mm
• the gap 1 1 - 12 between the plates 1 1 and 12 is approximately equal to 51 mm.
• each fin 321, 322, 323, 324 is relatively small, which reduces the stresses on solder fades formed between the plate and the fin.
• the fins 321, 322, 323, 324 may have orifices and overflow openings configured as the first embodiment (FIGS. 1 to 5: number of constant overflow openings) or as the third embodiment (FIG. Figures 8 and 9: gradual increase in the number of orifices).
• Figure 11 illustrates a portion of a dispensing device 401 according to a fifth embodiment of the invention.
• the dispensing device 401 combines:
• Each heat transfer fluid duct F2 is obstructed by a shutter 450 and the unrepresented outlet of the heat-exchange fluid ducts F2 is located on a lateral face of the dispensing device 301.
• FIG 11 illustrates a portion of a dispensing device 501 according to a sixth embodiment of the invention.
• the dispensing device 501 is similar to the dispensing device 1.
• the dispensing device 501 comprises plates 51 1, 512 and the like, an inlet 508 of refrigerant, fins 521 and the like and a shutter 550 for obstructing the heating medium conduits F2.
• the dispensing device 501 differs from the dispensing device 1 because the area where the holding tank 503 is disposed is wider than the area where the holding tank 3 is arranged, which makes it possible to increase the distance between the plates 51. 1 and 512 and each orifice forming the inlet 508 of the refrigerant. Thus, it reduces or avoids the risk of partial or total closure of each of these orifices by capillarity of the solders. In addition, this wider zone makes it possible to define larger orifices for the flow of the refrigerant liquid.
• the fins may have profiles other than flat and oblique.
• Figure 13 illustrates a portion of a dispensing device 601 whose fins are flat and composed of an oblique band and a side band that is horizontal when the dispensing device is in use.
• Figure 13 illustrates a portion of a dispensing device 601 whose fins are flat and sinusoidal.

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

Applications Claiming Priority (2)

Publications (2)

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ID=53404659

Family Applications (1)

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• 2015
  • 2015-02-06 FR FR1550960A patent/FR3032521B1/fr not_active Expired - Fee Related
• 2016
  • 2016-02-05 CN CN201680007397.4A patent/CN107208986B/zh active Active
  • 2016-02-05 EP EP16703139.2A patent/EP3254045B1/de not_active Not-in-force
  • 2016-02-05 WO PCT/EP2016/052524 patent/WO2016124748A1/fr active Application Filing
  • 2016-02-05 US US15/547,314 patent/US20180023899A1/en not_active Abandoned

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