EP4001799B1 - Dispositif de distribution d'un fluide pour un échangeur de chaleur, de préférence un évaporateur - Google Patents

Dispositif de distribution d'un fluide pour un échangeur de chaleur, de préférence un évaporateur Download PDF

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Publication number
EP4001799B1
EP4001799B1 EP21209132.6A EP21209132A EP4001799B1 EP 4001799 B1 EP4001799 B1 EP 4001799B1 EP 21209132 A EP21209132 A EP 21209132A EP 4001799 B1 EP4001799 B1 EP 4001799B1
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EP
European Patent Office
Prior art keywords
fluid
outlet
distributing
zone
channels
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EP21209132.6A
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German (de)
English (en)
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EP4001799A1 (fr
Inventor
Sandro ORTOLANO
Roberto Maran
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Thermokey SpA
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Thermokey SpA
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Classifications

    • 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
    • F28F9/0275—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 branch pipes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • F25B39/028—Evaporators having distributing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators

Definitions

  • the present invention concerns a device for distributing a fluid for a heat exchanger, preferably, but not exclusively, for an evaporator, even more preferably for an evaporator with a refrigeration cycle, in which the fluid comprises a liquid part and a gaseous part.
  • the distribution device according to the present invention is configured to be disposed upstream of a heat exchange coil of the heat exchanger, and has the function of mixing the liquid part and the gaseous part present in the fluid at inlet, uniformly redistributing the fluid in a plurality of flows exiting from the distribution device in a homogeneous manner.
  • a device according to the preamble of claim 1 is disclosed for example in document JP 2008267689 A .
  • Devices for distributing fluids are known, for use in heat exchangers, for example evaporators. Their function is to distribute the flow of a fluid at inlet, coming for example from a lamination valve, and to convey it in a plurality of capillary pipes exiting toward a heat exchange coil.
  • the so-called “simple” distributors are included, that is, provided with an inlet channel, or zone, with a plurality of outlet channels and an intermediate accumulation zone between the inlet channel and the plurality of outlet channels.
  • the accumulation zone allows the fluid to be distributed in the direction of the outlet channels.
  • the fluid exiting from the lamination valve is both in the liquid state and also in the vapor state.
  • the vapor quality of the fluid is low (for example, 10-20% m/m), but according to the laws of state, the percentage in volume of the liquid in the vapor state is very high (for example, > 50% V/V).
  • distributors having a neck in the intermediate accumulation zone as described, for example in the Japanese document JP-S5435468 .
  • distributors with a neck only partly solve the problem of the lack of homogeneity of the vapor quality of the fluid in the outlet channels.
  • the neck causes a pressure drop, accelerating the fluid and creating a turbulent motion that allows the mixing of the fluid in the liquid state and in the vapor state, homogenizing the vapor quality of the fluid entering the various capillary pipes, but not always optimally.
  • Such distributors with a neck and/or grooves on the inlet channel also have the disadvantage that they do not guarantee complete efficiency when the heat exchanger with which they are combined works in a partialized condition, that is, with a different flow rate, in particular lower than the nominal design one, so the problem of a distribution of the fluid with a non-uniform quality in the different outlet channels remains unsolved.
  • One purpose of the present invention is to provide a device for distributing a fluid for a heat exchanger, preferably, but not exclusively, an evaporator, which can optimally homogenize the vapor quality at outlet, for example toward the capillary pipes of the heat exchanger, and such as not to lose the efficiency of the latter on which the device is installed, even when working in a partialized condition.
  • Another purpose of the present invention is to provide a device for distributing a fluid for a heat exchanger, preferably, but not exclusively, an evaporator, which can maintain a high efficiency as the fluid passing through it varies, without having to vary the sizes thereof, or of some of its components such as for example the distribution device, for each type of fluid.
  • Another purpose of the present invention is to provide a method to manufacture said distribution device which allows to manufacture the device in a versatile and flexible way according to the most suitable geometry based on the operating specifications of the heat exchanger, including the type of fluid that passes through it.
  • the Applicant has devised, tested and embodied the present invention to overcome the shortcomings of the state of the art and to obtain these and other purposes and advantages.
  • a device for distributing a fluid having a liquid component and a gaseous component in a heat exchanger comprises an inlet zone of the fluid and an outlet zone of the fluid, wherein the outlet zone of the fluid comprises a plurality of outlet channels independent from each other.
  • the device for distributing a fluid also comprises mixing means disposed between the inlet zone and the outlet zone of the fluid, the mixing means being configured to create a swirling motion of the fluid in order to homogenize the vapor quality of the fluid portions exiting from the plurality of outlet channels.
  • the distribution device also comprises a hollow body in which there is a cylindrical conduit defining a main, or mixing, channel which extends from the inlet zone to a distribution zone disposed at the beginning of the plurality of outlet channels.
  • the mixing means comprise at least one groove present on the internal surface of the cylindrical conduit, or both on the internal surface of the cylindrical conduit and also on the internal surface of at least one portion of one or more of the outlet channels.
  • the at least one groove has a substantially helical shape, and it is disposed coaxial to a longitudinal axis of the cylindrical conduit.
  • the mixing means comprise one or more secondary channels, each of which begins in the inlet zone, extends inside the cylindrical conduit and ends in the main channel, so that each of the secondary channels can allow at least a part of the fluid coming from the inlet zone to pass, in order to introduce it into the main channel.
  • each of the one or more secondary channels has a curved trajectory, so as to terminate substantially tangent to the internal surface of the cylindrical conduit.
  • the one or more secondary channels enter the main channel at different heights along the longitudinal axis.
  • in the inlet zone there is a reduction of the passage section of the fluid coming from a connection pipe and directed into the main channel, thus forming a neck.
  • the plurality of outlet channels is defined by a corresponding plurality of outlet conduits independent from each other, which spread apart preferably in a substantially symmetrical manner with respect to the longitudinal axis.
  • the mixing means can comprise a discoidal element provided with one or more through fissures configured so that the fluid passes through them in the path from the inlet zone to the outlet zone or, alternatively, a plurality of fins. Both the discoidal element and also the fins are preferably disposed according to a transversal orientation, more in particular orthogonal, with respect to the flow of the fluid between the inlet zone and the outlet zone.
  • a heat exchanger comprising at least one compressor, a condenser, a heat exchange coil, and possibly a lamination valve, which is interposed between the condenser and the heat exchange coil, also comprises at least one device for distributing a fluid as above.
  • a device 10 for distributing a fluid is configured to be installed in a heat exchanger 11, preferably an evaporator, even more preferably an evaporator with refrigeration cycle.
  • fig. 1 shows an operating diagram of the heat exchanger 11, for example of the multi-circuit type.
  • the heat exchanger 11 comprises a compressor 12 configured to convey the fluid in the direction of a condenser 13, as indicated by the arrows, which releases at least part of the heat Q of the fluid to the outside of the circuit.
  • the condenser 13 is connected to a lamination valve 14, the output of which is connected to a heat exchange coil 16 by means of the distribution device 10.
  • the distribution device 10 is configured to divide the fluid into a plurality of capillary pipes 15 which continue their path inside the heat exchange coil 16, in which the fluid acquires heat from the outside and subsequently restarts its path from the compressor 12. In the case of an evaporator, the fluid evaporates in the process of acquiring heat from the outside.
  • the fluid used in the event that the heat exchanger 11 is an evaporator with refrigeration cycle is a refrigerant fluid, for example R448A, which is formed by a mixture of different refrigerant fluids; however, other refrigerant fluids can also be used, such as for example R449A, R407H, R134A, or other suitable ones, depending on the application.
  • the distribution device 10 ( figs. 2, 3 and 4 ) comprises a hollow body 17, having an inlet zone 18 ( figs. 2 and 4 ), preferably flared toward the inside, and an outlet zone 19 of the fluid.
  • the hollow body 17 comprises a cylindrical conduit 20 having a main, or mixing, channel 21 coaxial to its own longitudinal axis Z ( fig. 4 ) and a plurality of outlet conduits 22, independent from each other, which define a corresponding plurality of outlet channels 23, each of which ends in the outlet zone 19.
  • a main, or mixing, channel 21 coaxial to its own longitudinal axis Z ( fig. 4 ) and a plurality of outlet conduits 22, independent from each other, which define a corresponding plurality of outlet channels 23, each of which ends in the outlet zone 19.
  • there are twelve outlet conduits and channels 22, 23 there could be more, but also fewer, as a function of the application requirements of the distribution device 10 in the heat exchanger 11.
  • the number of outlet channels 23 can be comprised between 2 and 100, preferably between 2 and 63.
  • the diameter D 1 of the mixing channel 21 is comprised between 3 mm and 20 mm, preferably between 5 mm and 12 mm, while each of the outlet channels 23 can have a diameter D2 comprised between about 1 mm and about 10 mm, preferably between about 3 mm and about 6 mm.
  • the outlet conduits 22, and therefore the outlet channels 23, spread apart in a substantially symmetrical manner with respect to the longitudinal axis Z and are preferably distanced radially in a substantially uniform manner.
  • the plurality of outlet conduits 22 could be replaced by a single cone containing the plurality of outlet channels 23, or have other shapes.
  • the cylindrical conduit 20 is configured to be connected to a connection pipe 24 which represents the output of the lamination valve 14 ( fig. 1 ); their connection can be made with any suitable mean, such as for example threaded members, clamps, or by welding.
  • Each outlet conduit 22, in its outlet zone 19, comprises a connection seating 25 in which the end of a corresponding capillary pipe 15 can be inserted, for example by interlocking or by welding.
  • a distribution zone 26 in the center of which there is a distribution cone 27, which is configured to equally divide the fluid into the plurality of outlet channels 23.
  • the inlet zone 18 is shaped in such a way as to create a neck, that is, a narrowing of the section for the fluid at inlet up to the diameter D1 of the mixing channel 21. This narrowing of the section causes an acceleration of the fluid in the mixing channel 21.
  • the distribution device 10 can be made of various suitable materials, for example aluminum or its alloys, stainless steel, metallic materials, such as brass, or plastic materials.
  • the distribution device 10 also comprises mixing elements, or means, configured to obtain a swirling motion of the fluid inside the mixing channel 21 and the distribution zone 26.
  • the mixing means ( figs. 3, 4 and 5 ) comprise at least one groove 28 ( fig. 4 ) present on the internal surface of the mixing channel 21 and one or more secondary, or bypass, channels 29, made in the cylindrical conduit 20, in an intermediate zone between its external cylindrical surface and the cylindrical conduit 20.
  • the groove 28 has a substantially helical shape, it is coaxial to the longitudinal axis Z, it resembles an internal thread, which can be single-start or double-start, with a screwing sense from the inlet zone 18 to the distribution zone 26, and it preferably extends over the entire axial extension of the mixing channel 21.
  • Each groove 28 could also have a shape other than a helical one; for example it could be cylindrical, with the center in the longitudinal axis Z.
  • the helical shaped grooves 28 allow to give the fluid a swirling motion with respect to the longitudinal axis Z, thus causing a mixing of the fluid in the liquid state and in the vapor state, in such a way as to uniform the vapor quality in the distribution zone 26.
  • the fluid distributed by means of the distribution cone 27 into the plurality of outlet channels 23 will therefore have substantially the same vapor quality in each outlet channel 23 and therefore in each capillary pipe 15 of the heat exchange coil 16 ( fig. 1 ).
  • the pitch, the height of the crest of each groove 28 ( fig. 4 ), and the number of grooves 28 are calculated on the basis of the diameter D1 of the mixing channel 21 and on the basis of the chemical and physical properties of the fluid, as well as on the basis at least of speed, pressure, temperature, in order to achieve the desired swirling effect.
  • the height of the crest of the grooves 28 is comprised between about 0.5 mm and about 3 mm.
  • the secondary channels 29 ( figs. 3, 4 and 5 ) can be of a variable number, preferably from one to ten, as a function of the sizes of the hollow body 17. In the embodiment described here, there are three secondary channels 29 disposed angularly at 120°, with the center on the longitudinal axis Z ( fig. 3 ).
  • the secondary channels 29, by way of example, have a diameter comprised between about 0.5 mm and about 4 mm, preferably between about 0.5 mm and about 2 mm.
  • Each secondary channel 29 has a shape such that it is as if it were partly screwed into the hollow body 17, starting from the inlet zone 18 and then continuing with a curved path until it flows into the distribution channel 21, tangent to the internal surface of the cylindrical conduit 20. Furthermore, when there are at least two secondary channels 29, they preferably flow out at different heights of the mixing channel 21, in the direction of the longitudinal axis Z, in order to allow a better mixing of the fluid in the liquid state and in the vapor state. These heights can correspond, for example, to approximately 30%, 60% and 90% of the length of the mixing channel 21.
  • each secondary channel 29, in a first initial part thereof, is substantially parallel to the longitudinal axis Z, while after this, in a second part thereof, it is inclined toward the mixing channel 21 in order to introduce the fluid inside it.
  • each secondary channel 29 follows a curved trajectory, with a sense preferably concordant with the direction of rotation of each groove 28 of the grooves 29.
  • the radial coordinate with respect to the longitudinal axis Z in which a single secondary channel 29 flows into the mixing channel 21 is different from its starting radial coordinate, in the inlet zone 18.
  • each secondary channel 29 flows into the mixing channel 21 is flared, so as to facilitate the exit of the fluid in the latter and increase the swirl of the flow inside the mixing channel 21.
  • the secondary channels 29 have been described with an approximate and schematized development in order to emphasize their effect; however, they could also have different shapes. For example, each of them could have a first part parallel to the longitudinal axis Z and a second part that flows tangent in a straight line onto the mixing channel 21, or a first part parallel to the longitudinal axis Z and a second part coplanar with respect to the longitudinal axis Z, or flow directly into the distribution zone 26.
  • a first part of the flow present in the inlet zone 18 passes through the mixing channel 21, while a second part enters the one or more secondary channels 29 and is introduced into the mixing channel 21 in order to create turbulence and/or swirling in the flow.
  • the mixing means can comprise only one or more grooves 28, or only one or more secondary channels 29.
  • the distribution device 10 described heretofore advantageously provides to mix and distribute the fluid in the liquid state and in the vapor state with a homogeneous quality in the different capillary pipes downstream of the device.
  • This characteristic is also maintained in a partialized condition and is a very important aspect, since heat exchangers, in particular evaporators, are subject to variations of the flow rate both during the day and also over the course of a year.
  • the uniformity of the vapor quality of the fluid contributes to the increase in the efficiency of the heat exchange in the heat exchanger, in particular if it is a multi-circuit evaporator.
  • the uniformity of the vapor quality of the fluid in the outlet channels 23 and the efficiency of the operation in the partialized condition allow a net increase in the efficiency of the entire heat exchange apparatus.
  • the distribution device 10 designed in a manner coherent with the embodiment described above, including its variants, also performs well when the characteristics of the fluid flowing through it vary, keeping the efficiency of each individual embodiment stable for a plurality of fluids that can flow through it.
  • the mixing means comprise a discoidal element 30, preferably disposed inside the main channel 21, in particular disposed orthogonal with respect to the longitudinal axis Z.
  • the discoidal element 30 is provided with one or more through fissures 31, configured so that the fluid passes through them in the path from the inlet zone 18 to the outlet zone 19.
  • the fissures 31 can be in a number other than four and/or have a different geometric configuration, in terms of sizes and orientation, based on the fluid dynamic effect to be imparted to the fluid by means of the discoidal element 30.
  • the main channel 21 is without the grooves 28, but in other embodiments, not shown, the discoidal element 30 can be provided in combination with the grooves 28.
  • the mixing means comprise a plurality of fins 32, protruding from the internal surface of the main channel 21 toward the center of the channel itself, that is, toward the longitudinal axis Z.
  • the mixing means comprise a plurality of fins 32, protruding from the internal surface of the main channel 21 toward the center of the channel itself, that is, toward the longitudinal axis Z.
  • the fins 32 can be in a number other than six and/or assume a different geometric configuration, in terms of sizes, shapes and orientation, based on the fluid dynamic effect to be imparted to the fluid by means of the fins 32.
  • the fins can be arched or straight, configured as seams or ribs, or according to yet other shapes, and even be disposed parallel to the longitudinal axis Z, or with a certain inclination with respect to the latter.
  • the main channel 21 is without the grooves 28; however, in other embodiments according to the invention, not shown, the fins 32 are provided in combination with the grooves 28.
  • the mixing means are configured as the grooves 28 described above.
  • the grooves 28, in addition to being present on the internal surface of the main channel 21, are also present on the internal surface of one or more outlet conduits 22, for at least a portion of the respective outlet channels 23.
  • the grooves 28 are also made on the mouth portion of the outlet channel 23 shown on the left, and for the entire length of the outlet channel 23 shown on the right. This advantageously allows to impart different pressure drops to the fluid flowing through different outlet conduits 22.
  • the fluid flowing through the outlet conduit 22 shown on the right will undergo a greater distributed pressure drop than the fluid flowing through the other outlet conduit 22 shown on the left, due to the presence of the grooves 28 along the entire respective outlet conduit 23.
  • the mixing means are configured as the grooves 28 described above.
  • at least some of the outlet channels 23 can have a diameter D2 different from that of the other outlet channels 23.
  • the difference between the diameters is shown in fig. 9 , in which, by way of example, a first outlet channel 23 (on the left) is shown having a diameter, indicated with the reference D2', which is smaller than the diameter of a second outlet channel 23 (on the right), in turn indicated with the reference D2".
  • the other outlet channels 23 not shown in the section of fig. 9 can have diameters equal to the diameters D2', D2" mentioned above, or diameters that further differ from them.
  • This embodiment also advantageously allows to impart different pressure drops to the fluid that flows through different outlet conduits 22.
  • outlet conduits 22 have different structures from each other is particularly useful in the case of heat exchangers 11, configured for example as evaporators, comprising a large number of capillary pipes 15, and consequently a heat exchange coil 16 of a significant size.
  • heat exchangers 11 configured for example as evaporators, comprising a large number of capillary pipes 15, and consequently a heat exchange coil 16 of a significant size.
  • the problem of the homogeneous distribution of the fluid having the same vapor quality in the parallel circuits is more pronounced.
  • the mixing means impart differentiated pressure drops to the fluid that passes through them, this facilitates achieving the desired homogenization, preventing technicians from having to intervene directly at the time of installation, adopting improvised and empirical solutions on the basis of the evidence of the different frosting that characterizes the different circuits at the start of the exchanger.
  • the mixing means are configured as the grooves 28 and the secondary channels 29 described above.
  • a second group of secondary channels is provided, indicated by the numerical reference 29', disposed downstream with respect to the secondary channels 29 with reference to the flow of the fluid between the inlet zone 18 and the outlet zone 19.
  • Each secondary channel 29' of this second group departs from the distribution channel 21 and flows into one of the outlet channels 23, preferably in an initial segment thereof.
  • the secondary channels 29' of this second group can be substantially similar in shape and size to the secondary channels 29 described above.
  • each secondary channel 29' can open onto the walls of the distribution channel 21 and of the outlet channel 23 in a direction tangent thereto, screwing into the cylindrical conduit in the manner described above.
  • the number of secondary channels 29' of this second group is equal to or lower than the number of outlet conduits 22, that is, equal to or lower than twelve in the example provided here.
  • the position of the distribution cone 27 can be at a higher vertical height than that shown in the drawings, penetrating further into the main channel 21.
  • the distribution device 10 can be made by means of known additive manufacturing techniques. This allows to make the different embodiments of the device previously described, as well as their variants, with great versatility. Thanks to additive manufacturing techniques, it is possible to make distribution devices 10 with customized geometries based on the fluid dynamic needs of the plant in which the device is integrated. It should also be noted that additive manufacturing techniques allow to obtain complex shapes, such as for example those of the secondary channels 29, 29', or of the fins 32, or of the outlet channels 23 having differentiated diameters D2', D2" or grooved segments with different lengths, which would be difficult to obtain with other traditional manufacturing techniques, such as for example molding, die casting or mechanical machining by chip removal.
  • the method can provide to deposit a succession of layers of suitable printing materials of a known type on top of each other, such as for example metal powders or resins or polymer materials, or a mixture thereof.
  • suitable printing materials of a known type on top of each other, such as for example metal powders or resins or polymer materials, or a mixture thereof.
  • the three-dimensional printing device of the type known in the state of the art, can be easily selected by the person of skill in the art from among known apparatuses suitable to print three-dimensional objects with such materials.

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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)

Claims (12)

  1. Dispositif (10) de distribution d'un fluide ayant une composante liquide et une composante gazeuse dans un échangeur thermique, comprenant une zone d'entrée (18) dudit fluide et une zone de sortie (19) dudit fluide, ladite zone de sortie (19) comprenant une pluralité de canaux de sortie (23) indépendants les uns des autres, des moyens de mélange (28, 29, 29', 30, 31, 32) étant prévus entre ladite zone d'entrée (18) et ladite zone de sortie (19), configurés pour créer un mouvement tourbillonnant dudit fluide afin d'homogénéiser la qualité de vapeur des portions de fluide sortant de ladite pluralité de canaux de sortie (23), le dispositif (10) comprenant également un corps creux (17) dans lequel se trouve un conduit cylindrique (20) définissant un canal principal (21) qui s'étend depuis ladite zone d'entrée (18) jusqu'à une zone de distribution (26) disposée au début de ladite pluralité de canaux de sortie (23), et lesdits moyens de mélange comprenant au moins une rainure (28) présents sur la surface interne dudit conduit cylindrique (20), ou à la fois sur la surface interne dudit conduit cylindrique (20) et également sur la surface interne d'au moins une partie d'un ou plusieurs desdits canaux de sortie (23), le dispositif (10) étant caractérisé en ce que lesdits moyens de mélange comprennent un ou plusieurs canaux secondaires (29), dont chacun débute dans ladite zone d'entrée (18), s'étend à l'intérieur dudit conduit cylindrique (20) et se termine dans ledit canal principal (21), de sorte que chaque canal parmi lesdits canaux secondaires (29) puisse laisser passer au moins une partie dudit fluide provenant de ladite zone d'entrée (18), afin de l'introduire dans ledit canal principal (21).
  2. Dispositif (10) de distribution d'un fluide selon la revendication 1, caractérisé en ce que ladite au moins une rainure (28) a une forme sensiblement hélicoïdale et est disposée coaxialement à un axe longitudinal (Z) dudit conduit cylindrique (20).
  3. Dispositif (10) de distribution d'un fluide selon la revendication 1 ou la revendication 2, caractérisé en ce que chaque canal parmi lesdits un ou plusieurs canaux secondaires (29) présente un développement courbe, de manière à se terminer sensiblement tangentiellement à la surface interne dudit conduit cylindrique (20).
  4. Dispositif (10) de distribution d'un fluide selon l'une quelconque des revendications précédentes, caractérisé en ce que lesdits un ou plusieurs canaux secondaires (29) pénètrent dans ledit canal principal (21) à différentes hauteurs le long dudit axe longitudinal (Z).
  5. Dispositif (10) de distribution d'un fluide selon l'une quelconque des revendications précédentes, caractérisé en ce qu'il y a trois desdits canaux secondaires (29), disposés radialement selon un angle d'environ 120° les uns par rapport aux autres, par rapport audit axe longitudinal (Z).
  6. Dispositif (10) de distribution d'un fluide selon l'une quelconque des revendications précédentes, caractérisé en ce que lesdits moyens de mélange comprennent un deuxième groupe de canaux secondaires (29'), dont chacun débute dans ledit canal principal (21), s'étend à l'intérieur dudit conduit cylindrique (20) et se termine dans un canal respectif parmi lesdits canaux de sortie (23), de sorte que chaque canal parmi lesdits canaux secondaires (29') dudit deuxième groupe puisse laisser passer au moins une partie dudit fluide provenant de ladite zone d'entrée (18), afin de l'introduire dans ledit canal de sortie (23) respectif.
  7. Dispositif (10) de distribution d'un fluide selon l'une quelconque des revendications précédentes, caractérisé en ce que dans ladite zone d'entrée (18), il y a une réduction de la section de passage dudit fluide venant d'une conduite de raccordement (24) et dirigé jusque dans ledit canal principal (21), formant ainsi un col.
  8. Dispositif (10) de distribution d'un fluide selon l'une quelconque des revendications précédentes, caractérisé en ce que ladite pluralité de canaux de sortie (23) est définie par une pluralité correspondante de conduits de sortie (22) indépendants les uns des autres, qui s'écartent de préférence selon un de manière sensiblement symétrique par rapport audit axe longitudinal (Z).
  9. Dispositif (10) de distribution d'un fluide selon la revendication 8, caractérisé en ce qu'un ou plusieurs desdits canaux de sortie (23) ont un diamètre (D2) différent du diamètre des canaux de sortie restants (23).
  10. Dispositif (10) de distribution d'un fluide selon l'une quelconque des revendications précédentes, caractérisé en ce que lesdits moyens de mélange comprennent un élément discoïde (30) pourvu d'une ou plusieurs fissures traversantes (31) configurées pour que le fluide les traverse entre ladite zone d'entrée (18) et ladite zone de sortie (19), ledit élément discoïdal (30) étant disposé de préférence selon une orientation transversale, plus particulièrement orthogonale, par rapport à l'écoulement du fluide entre ladite zone d'entrée (18) et ladite zone de sortie (19).
  11. Dispositif (10) de distribution d'un fluide selon l'une quelconque des revendications précédentes, caractérisé en ce que lesdits moyens de mélange comprennent une pluralité d'ailettes (32), lesdites ailettes (32) étant disposées de préférence selon une orientation transversale, plus particulièrement orthogonale, par rapport à l'écoulement du fluide entre ladite zone d'entrée (18) et ladite zone de sortie (19).
  12. Échangeur de chaleur, comprenant au moins un compresseur (12), un condenseur (13), un enroulement d'échange thermique (16), et optionnellement une vanne de laminage (14), qui est interposée entre ledit condenseur (13) et ledit enroulement d'échange thermique (16), caractérisé en ce qu'il comprend également au moins un dispositif (10) de distribution d'un fluide selon l'une quelconque des revendications 1 à 11.
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JPS5435468B2 (fr) 1973-06-02 1979-11-02
JPS5435468U (fr) * 1977-08-16 1979-03-08
JPS5573787U (fr) * 1978-11-15 1980-05-21
JP2000320929A (ja) 1999-05-06 2000-11-24 Hitachi Ltd 冷媒分流器
JP2003090644A (ja) * 2001-09-19 2003-03-28 Daikin Ind Ltd 冷媒分流器
JP2003090646A (ja) * 2001-09-20 2003-03-28 Hitachi Cable Ltd 空気調和機用熱交換器
US7600393B2 (en) * 2005-03-09 2009-10-13 Lg Electronics Inc. Refrigerant distributing device for multi-type air conditioner
JP2008267689A (ja) 2007-04-20 2008-11-06 Hitachi Appliances Inc 冷媒分配器
US20170089643A1 (en) * 2015-09-25 2017-03-30 Westinghouse Electric Company, Llc. Heat Exchanger

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