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
  • F28F9/0273—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
  • 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
  • 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
  • F28F9/028—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using inserts for modifying the pattern of flow inside the header box, e.g. by using flow restrictors or permeable bodies or blocks with channels
• • 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
  • F28D2021/0061—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for phase-change applications
  • F28D2021/0064—Vaporizers, e.g. evaporators

Definitions

• the field of the present invention is that of the heat exchangers constituting a fluid circuit refrigerant equipping a motor vehicle.
• the subject of the invention is a mixing member which constitutes a device for homogenizing the distribution of a refrigerant fluid inside tubes of such a heat exchanger.
• a motor vehicle is commonly equipped with a ventilation, heating and / or air conditioning system for heat treating the air present or sent inside a passenger compartment of the motor vehicle. To do this, such an installation is associated with a closed circuit inside which circulates a refrigerant fluid.
• the refrigerant circuit comprises successively a compressor, a condenser or gas cooler, an expansion member and a heat exchanger.
• the heat exchanger is housed inside the ventilation, heating and / or air conditioning system to allow a heat exchange between the refrigerant and a flow of air circulating inside said installation, previously a delivery of the air flow inside the passenger compartment.
• heat exchanger is used as an evaporator to cool the air flow.
• the refrigerant is compressed inside the compressor, then the cooling fluid is cooled inside the condenser or gas cooler, then the refrigerant is expanded within the expansion device and finally the refrigerant captures calories to the airflow inside the heat exchanger.
• the refrigerant fluid, at the outlet of the expansion member and at the inlet of the heat exchanger, is in the two-phase state and is present in a liquid phase and a gaseous phase.
• the heat exchanger comprises a header and a return box between which a bundle of tubes is interposed.
• the refrigerant is admitted inside the heat exchanger through a mouth of entry that includes the collector box. Then, the coolant flows between the manifold and the gearbox by borrowing the tubes of the beam.
• a general problem posed lies in the difficulty of feeding the tubes of the bundle homogeneously with respect to the different phases, liquid and gaseous, of the refrigerant fluid.
• a heterogeneity of supply of refrigerant fluid tubes of the beam generates a heterogeneity of the temperature of the air flow through the heat exchanger. This heterogeneity is likely to induce untimely and undesired temperature differences between zones of the passenger compartment, which is detrimental.
• the document US2015 / 0121950 proposes to house, inside the manifold, a device for homogenizing the distribution of the refrigerant fluid inside the tubes of the bundle.
• This device comprises a conduit provided with a plurality of orifices.
• the conduit has a first end portion which is in connection with a first inlet mouth of the refrigerant fluid inside the heat exchanger.
• the conduit is arranged in a cylindrical tube delimiting an internal volume in one piece within which circulates the refrigerant fluid.
• the coolant in the liquid phase is projected through the orifices formed through the conduit in the form of droplets.
• Such an organization is not optimal from the point of view of the homogenization of the coolant distribution inside the heat exchanger. More particularly, the tubes of the beam farthest from the first end portion are frequently underfed with refrigerant fluid.
• An object of the invention is to perfect the homogeneity of the coolant distribution inside the heat exchanger, in order to improve its efficiency and efficiency, in order to deliver inside the passenger compartment. a flow of air at the desired temperature.
• Another object of the invention is to improve the distribution of refrigerant inside the heat exchanger, including when the latter is present inside the heat exchanger in two distinct phases, liquid. and gas, in respective variable proportion.
• Another goal is to design a mixing device whose forms are easily demoldable. Another object is to propose a device for distributing a refrigerant fluid inside the tubes of the bundle which provides an equivalent supply of refrigerant fluid to the tubes of the bundle, including those furthest away from the first end portion. duct, which receives the first coolant. Another object is to provide a device for dispensing a refrigerant fluid which is arranged to prevent the refrigerant from accumulating in a zone of the latter.
• a mixer of the present invention is a mixer for mixing a liquid phase and a gaseous phase of a refrigerant circulating inside a header of a heat exchanger.
• the mixing member comprises at least one centrifugal wall having a plurality of mixing patterns which are arranged to direct the coolant to a peripheral edge of the mixing member.
• the mixing patterns are successively repeated along an axis of elongation.
• a mixing pattern extends between a first flange and a second flange.
• a first mixing pattern succeeds a second mixing pattern along the axis of elongation.
• the first flange and the second flange of the same mixing pattern form with each other a flange angle which is between 0 ° and 90 °, preferably between 0 ° and 20 °.
• Such a mixing member promotes the mixing of the liquid phase and the gas phase of the cooling fluid which runs along it.
• Such a mixing member also includes shapes with clearance angles that allow simple demolding of the mixing.
• the rim here is an area that delimits a mixing pattern.
• a rim takes the form of an inversion of slopes of the wall of the mixing member.
• the flange of the invention does not necessarily have an edge, but may be formed by a curved area of the wall.
• a protocol for measuring the flange angle involves passing a first straight transverse to the axis of elongation and along the first flange of the mixing pattern, a second straight transverse to the axis of elongation and along the second rim of the same mixing pattern, then project on a plane perpendicular to the axis of elongation the first straight line and the second right.
• the mixing member is thus recognizable when an angle between these two projected lines is between 0 ° and 90 °.
• the mixing member advantageously has at least one of the following features, taken alone or in combination:
• At least one edge is delimited by a ridge and a bottom which extend in a plane transverse to the axis of elongation between two adjacent mixing patterns.
• the wall is continuous from one mixing pattern to another.
• the wall is arranged to centrifuge the coolant flowing along the mixing member.
• the first edge of a first mixing pattern coincides with the second edge of a second mixing pattern immediately adjacent to the first mixing pattern.
• the flange angle is between 0 ° and 10 °.
• the first mixing pattern and the second mixing pattern are identical and arranged head to tail one after the other along the axis of elongation.
• each mixing pattern is arranged in a helix portion.
• the first mixing pattern is twisted in a clockwise direction about the axis of elongation while the second mixing pattern is twisted in a counterclockwise direction about the axis of elongation.
• the first rim of a first mixing pattern and the second rim of a second adjacent mixing pattern together form a pattern angle that is zero.
• each mixing element extends between a first edge and a second edge which form between them an edge angle which is zero.
• the first edge of a mixing element forms with a second edge of an adjacent mixing element an element angle which is zero.
• the first mixing pattern and the second mixing pattern adjacent to the first mixing pattern together form a mixing element repeated, for example identically, along the axis of elongation.
• the angles chosen above will be measured according to the measurement protocol described above, that is to say by projection of lines on a plane perpendicular to the axis of elongation.
• the subject of the invention is also a device for homogenizing the distribution of the refrigerant inside tubes of a heat exchanger, the homogenizing device being intended to be housed in a heat exchanger collector box, the homogenization device of the distribution comprising a duct provided with at least one window through which the refrigerant fluid is able to enter the duct and at least one orifice through which the refrigerant fluid is able to exit the duct, the duct housing at least one such mixing member.
• the homogenization device of the distribution advantageously has at least one of the following characteristics, taken alone or in combination:
• the duct delimits an internal volume within which at least partially extends the mixing device.
• the duct delimits an internal section occupied entirely by the mixing member, such an internal section corresponding to a section perpendicular to the longitudinal axis of the duct in a portion thereof having a plurality of orifices.
• the mixing member occupies the entire internal volume.
• the mixing member is centered inside the duct.
• the invention also relates to a manifold defining a first chamber housing at least one such homogenization of the distribution device.
• the invention also relates to a heat exchanger comprising such a header and a return box between which is interposed a bundle of tubes.
• the invention also relates to a refrigerant circuit comprising at least one such heat exchanger.
• the invention also relates to a process for obtaining such a mixing member from a mold comprising a first matrix and a second matrix which together form a conformation reserve identical to the mixing member.
• the invention also relates to a use of such a heat exchanger as an evaporator housed inside a housing of a ventilation, heating and / or air conditioning equipment equipping a motor vehicle.
• FIG. 1 is a schematic illustration of a refrigerant circuit comprising a heat exchanger of the present invention
• FIG. 2 is a diagrammatic perspective illustration of a first embodiment of a heat exchanger illustrated in FIG. 1;
• FIG. 3 is a diagrammatic perspective illustration of a second variant embodiment of a heat exchanger illustrated in FIG. 1;
• FIG. 4 is a cut-away illustration in perspective of a device for homogenizing the distribution of the refrigerant fluid intended to equip the heat exchanger shown in FIGS. 2 or 3,
• FIG. 5 is a schematic perspective illustration of a mixing device constituting the device for homogenizing the distribution of the refrigerant fluid shown in FIG. 4.
• the figures and their description set forth the invention in detail and according to particular methods of its implementation. They can be used to better define the invention, if necessary.
• the refrigerant circuit 1 successively comprises, in a direction SI of circulation of the refrigerant fluid FR inside the refrigerant circuit 1, a compressor 2 for compressing the refrigerant fluid FR, a condenser or a gas cooler 3 for cooling the refrigerant FR, an expansion member 4 within which the cooling fluid FR undergoes expansion and a heat exchanger 5.
• the heat exchanger 5 is housed inside a housing 6 of a ventilation system 7, heating and / or air conditioning inside which circulates a flow of air.
• the heat exchanger 5 allows a heat transfer between the refrigerating fluid FR and the airflow FA coming into contact with it and / or passing through it, as illustrated in FIG. 2.
• the heat exchanger 5 is used as an evaporator to cool the air flow FA, during the passage of the air flow FA to the contact and / or from one side of the heat exchanger 5.
• the heat exchanger 5 comprises a manifold 8 and a gearbox 9 between which a tube bundle 10, 10a, 10b is interposed.
• the heat exchanger 5 extends parallel to a first plane PI containing the manifold 8, the bundle of tubes 10, 10a, 10b and the return box 9.
• the manifold 8 overhangs the bundle of tubes 10, 10a, 10b, which are themselves located above the return box 9, in particular in the position of use of the heat exchanger 5 mounted inside the housing 6.
• the manifold 8 is an upper box of the heat exchanger 5 while the return box 9 is a lower box of the heat exchanger 5.
• the airflow FA flows through the heat exchanger 5 in a direction preferably orthogonal to the first plane P 1.
• the tubes 10, 10a, 10b are for example rectilinear and extend along a first axis of general extension Al between the manifold 8 and the return box 9.
• the box manifold 8 extends along a second axis of general extension A2 and the gearbox 9 extends along a third axis of general extension A3.
• the second axis of general extension A2 and the third axis of general extension A3 are mutually parallel, being orthogonal to the first axis of general extension Al.
• the bundle of tubes 10, 10a, 10b is provided with fins 15 which are interposed between two successive tubes 10, 10a, 10b, to promote a heat exchange between the air flow FA and the tubes 10, 10a, 10b, when a passage of the air flow FA through the heat exchanger 5, the airflow FA flowing in a direction substantially orthogonal to the first plane P 1.
• the heat exchanger 5 comprises a first mouth 16 through which the refrigerant fluid FR enters the interior of the heat exchanger 5.
• the first mouth 16 constitutes an intake port of the refrigerant fluid FR in a first chamber 13 , which is delimited inside the manifold 8.
• the heat exchanger 5 comprises a second mouth 17 through which the coolant FR is discharged out of the heat exchanger 5.
• the heat exchanger 5 is a heat exchanger inside which the refrigerating fluid FR flows in a path arranged in "I".
• the tubes 10 are arranged parallel to each other and are aligned inside the first plane Pl.
• the tubes 10 extend between a first end 101 which is in fluid communication with the deflection box 9 and a second end 102 which is in In other words, the gearbox 9 forms the base of the "I" while the manifold 8 forms the top of the "I".
• the second mouth 17 equips the return box 9.
• the refrigerant fluid FR enters the interior of the heat exchanger 5 through the first mouth 16 that includes the manifold 8. Then, the refrigerant fluid FR is distributed along the manifold 8 along the second extension axis A2 by a homogenization device of the distribution 18. Then, the refrigerant fluid FR flows between the manifold 8 and the 9 finally by borrowing the tubes 10. Finally, the refrigerant FR is discharged from the heat exchanger 5 through the second mouth 17 of the return box 9.
• the heat exchanger 5 is a heat exchanger inside which the refrigerating fluid FR flows along a path arranged in "U".
• the tubes 10a, 10b are arranged parallel to each other by being distributed in two plies 11, 12, including a first ply 11 of first tubes 10a and a second ply 12 of second tubes 10b.
• the first ply 11 and the second ply 12 are formed inside respective planes which are parallel to each other and parallel to the first plane Pl.
• the first tubes 10a of the first ply 11 extend between a first end 101 which is in fluid communication with the return box 9 and a second end 102 which is in fluid communication with the first chamber 13.
• the second tubes 10b of the second ply 12 extend between a third end 103 which is in fluid communication with the deflection box 9 and a fourth end 104 which is in fluid communication with a second chamber 14, also delimited inside the manifold 8.
• the first chamber 13 and the second chamber 14 are contiguous and sealed with each other.
• the first chamber 13 extends along a fourth axis of general extension A4 and the second chamber 14 extends along a fifth axis of general extension A5.
• the fourth axis of general extension A4 and the fifth axis of general extension A5 are parallel to each other and parallel to the second axis of general extension A2.
• the fourth axis of general extension A4 and the fifth axis of general extension A5 together define a second plane P2, which is preferably orthogonal to the first plane P1.
• the reference box 9 forms the base of the "U” whereas that the first ply 11 and the second ply 12 of tubes 10a, 10b form the branches of the "U", the first chamber 13 and the second chamber 14 forming the ends of the "U".
• the second mouth 17 equips the second chamber 14 of the header box 8.
• the refrigerant fluid FR enters the inside of the heat exchanger 5 through the first mouth 16 of the first chamber 13, being distributed along the manifold 8 according to the second axis of general extension A2 by the homogenization device of the distribution 18. Then, the refrigerating fluid FR flows between the first chamber 13 of the manifold 8 and the return box 9 by borrowing the first tubes 10a of the first ply 11. Then, the refrigerant FR flows between the return box 9 and the second chamber 14 by taking the second tubes 10b of the second ply 12. Finally, the refrigerant FR is discharged out of the heat exchanger 5 through the second mouth 17, after having passed through the second chamber 14.
• a first tube 10a of the first ply 11 is aligned with a second tube 10b of the second ply 12 inside a third plane P3 which is perpendicular to the first plane P1 and which is parallel to the first axis of general extension Al.
• the manifold 8 houses the homogenization device of the distribution 18 of the refrigerant FR inside the tubes 10, 10a, 10b.
• a homogenization device of the distribution 18 is intended to homogeneously distribute the refrigerant fluid FR, in the two-phase liquid-gas state, along the manifold 8 and ultimately within the set of tubes 10, 10a, 10b.
• Such a homogenization device of the distribution 18 is more particularly intended to homogeneously distribute the refrigerant fluid FR inside the heat exchanger 5, including when the refrigerant fluid FR is present inside the heat exchanger 5 in two distinct phases, liquid and gas, in respective variable proportion.
• the homogenization device of the distribution 18 comprises, for example, a duct 19 extending along a sixth axis of general extension A6, parallel to or even coincidental with the second axis of general extension A2. and / or the fourth axis of general extension A4, between a first end portion 20 and a second end portion 21 of the duct 19.
• A6 which is defined by the largest dimension of the duct 19. It is termed transversal any element which extends inside a transverse plane Pt which is orthogonal to the general extension axis A6.
• the first end portion 20 is formed of one end of the conduit 19, while the second end portion 21 is formed of the other end of the conduit 19, longitudinally opposite the first end portion 20.
• the first end portion 20 is intended to be placed in fluid communication with the first mouth 16 of the heat exchanger 5.
• the first mouth 16 houses the conduit 19
• the first end portion 20 is placed in fluid communication with a pipe of the refrigerant circuit 1.
• the second end portion 21 is blind and forms a cul-de-sac with regard to the circulation of the refrigerant fluid FR to the inside the duct 19.
• the duct 19 is for example formed in a cylinder, or in a parallelepiped or in any other form having an axis of symmetry A7, which is preferably parallel to or even coincidental with the sixth axis of general extension A6.
• the conduit 19 comprises a peripheral envelope 23 which is of cylindrical cross section when the conduit 19 is shaped in a cylinder, of parallelepipedal cross section when the conduit 19 is a parallelepiped.
• the peripheral envelope 23 is the one that gives the overall shape of the duct 19.
• the peripheral envelope 23 is capable of being formed of a plurality of peripheral surfaces, disjointed or not from each other, and which Together, the peripheral casing 23 is formed.
• the peripheral casing 23 may be formed of a plurality of peripheral surfaces arranged in strips that are disjoint or not one another.
• the peripheral envelope 23 comprises at least one orifice 22 and preferably holes 22 which are formed through the peripheral envelope 23 of the conduit 19.
• the orifices 22 are preferably aligned along an alignment axis A8 which is parallel to the sixth axis of general extension A6 and / or the axis of symmetry A7.
• the orifices 22 are equidistant from one another. According to another variant, the orifices 22 are spaced from each other by a variable distance.
• the orifices 22 are for example orifices of circular section, but are likely to be of any conformation, rectangular, elliptical, oblong in particular.
• the conduit 19 constitutes an envelope which delimits an internal space 24 around which the conduit 19 is formed.
• the duct 19 borders the internal space 24 that the duct 19 surrounds.
• the internal space 24 is for example cylindrical or parallelepipedic, or of any other shape formed around the axis of symmetry A7.
• the peripheral envelope 23 of the duct 19 has an inner face 23a which abuts and delimits the internal space 24, the inner face 23a preferably being of circular cross section.
• the conduit 19 houses a mixing member 25 which extends inside the internal space 24.
• the mixing member 25 is intended to promote mixing between the liquid and gaseous phases of the refrigerant fluid FR.
• the mixing member 25 is more particularly arranged to direct the refrigerant fluid FR to the inner face 23a of the conduit 19, so that it comes knocking it and thus increase the mixture of the liquid and gaseous phases of the coolant.
• the mixing device 25 in particular its mixing patterns 31a, 34b, is arranged so that the deflection of the coolant is alternated, as illustrated by the arrows FR of FIG. 5.
• a first mixing pattern 34a thus forces the coolant to go to a peripheral edge 31 of the mixing member which is opposite to the peripheral edge 31 which delimits the second mixing pattern 34b, with respect to the axis of extension A9 of the mixing member 25.
• the refrigerant fluid impinges on a first angular sector of the inner wall 23a of the duct 19 which is opposite a second angular sector of the inner wall 23a, with respect to the axis of elongation A9 of the mixing member 25.
• At least one of the angular sectors comprises the plurality of orifices 22.
• the mixing member 25 is a member that generates a turbulent flow, in particular centrifugal circulation, of the refrigerant fluid FR towards the face internal 23a of the conduit 19.
• the mixing member 25 is also provided to prevent an accumulation of refrigerant fluid FR in the liquid state in a lower zone of the conduit 19, in the position of use of this latest.
• the mixing member 25 is also provided to disrupt a laminar flow of the refrigerant fluid FR inside the conduit 19, for mixing the liquid and gas phases of the refrigerant fluid FR.
• the mixing member 25 forms at least one baffle, and preferably a plurality of baffles, against a laminar flow of the coolant, parallel to the sixth axis of general extension A6 and / or to the axis of symmetry A7.
• the mixing member 25 forms an obstacle to the laminar flow of the refrigerant fluid FR inside the internal space 24.
• the mixing member 25 is longitudinally extended along an axis of elongation A9 which is for example parallel to the sixth axis of general extension A6 of the conduit 19.
• the organ mixer 25 is arranged around this axis of elongation A9, preferably parallel to, or even coincident with, the axis of symmetry A7 of the duct 19, when the mixing member 25 is positioned inside the duct 19.
• the mixing member 25 occupies the entire internal section of the duct 19, advantageously a longitudinal portion of the duct 19 which has orifices. A peripheral edge 31 of the mixing member is thus in contact against the inner face 23a which delimits the conduit 19.
• the mixing member 25 extends inside the internal space 24, occupying all or part of it. In other words, the mixing member 25 can fill the entire volume defined by the conduit 19. In other words, the mixing member 25 is of a conformity and / or a geometry similar to that of the internal space 24. According to the variants described above, the mixing member 25 is likely to be of cylindrical or parallelepiped shape, or of any other shape formed around the axis of symmetry A7. It will be understood that such a shape is defined by a projection of the peripheral edge 31 of the mixing member 25. The peripheral edge 31 of the mixing member 25 is formed of at least one surface of the mixing member 25 which is disposed opposite the conduit 19. The peripheral edge 31 forms a succession of "V" abutting along the axis of extension A9 of the mixing member 25.
• the inner face 23a of the peripheral envelope 23 is preferably smooth for allow easy introduction of the mixing member 25 inside the conduit 19, the peripheral edge 31 of the mixing member 25 bearing against the inner face 23a.
• the conduit 19 is provided with two end walls 27, 28, including a first end wall 27 fitted to the first end portion 20 and a second end wall 28 fitted to the second end portion 21.
• the first end wall 27 and the second end wall 28 are for example flat and arranged along the transverse plane Pt orthogonal to the sixth axis of general extension A6 and / or the axis of symmetry A7.
• the first end wall 27 and the second end wall 28 are for example derived from a lid at least partially covering the collecting box 8.
• the first end wall 27 is equipped with at least one window 29 for the admission of the refrigerant fluid FR into the interior space 24.
• the first end wall 27 of the duct 19 is equipped with the window 29 which is for example in fluid relation with the first mouth 16 to admit the refrigerant fluid FR inside the heat exchanger 5 via the conduit 19.
• the refrigerant fluid FR is admitted to the inside the heat exchanger 5 through the conduit 19 provided with the orifices 22 through which the refrigerant fluid FR is able to be discharged from the conduit 19 to circulate inside the manifold of the heat exchanger.
• the mixing member 25 comprises a first longitudinal end 31a which is alignable with the first end wall 27 of the conduit 19.
• the mixing member 25 comprises a second longitudinal end 31b which is capable of being aligned with the second end wall 28.
• the refrigerating fluid FR penetrating inside the heat exchanger 5 penetrates inside the internal space 24 of the duct 19 by taking the window 29 formed through the first end wall 27 Then, the refrigerating fluid FR spreads inside the internal space 24 by being mixed by the mixing member 25. This results in particular a mixing of the liquid and gas phases of the refrigerating fluid FR which is then homogenized longitudinally, along the conduit 19. Then, the refrigerant FR borrows the orifices 22 to flow out of the conduit 19 to the first chamber 13. Then, the refrigerant fluid FR flows through the tube bundle 10, 10a, 10b, as described above, to the return box 9, to be evacuated out of the heat exchanger. heat 5 through the second mouth 17.
• the refrigerant fluid FR encounters multiple obstacles that promote a mixture between its liquid phases and gas.
• such a duct 19 promotes homogenization of the distribution of the refrigerant fluid FR inside the tubes 10, 10a, 10b.
• the refrigerating fluid FR is all the better sprayed, and homogeneously, as it passes through the orifices 22, that the two phases of the refrigerant fluid FR, liquid and gas, are mixed by the mixing member 25 inside the internal space 24 of the duct 19, in order to then supply homogeneously the bundle of tubes 10, 10a, 10b.
• the mixing member 25 allows a longitudinal distribution of the refrigerant fluid FR which is homogeneous along the axis of symmetry A7, the spraying of the refrigerant fluid FR through the orifices 22 taking place in the a second step, after homogenization of the refrigerant fluid FR in the internal space 24, which ensures a better homogeneous distribution of the refrigerant fluid FR at the outlet of the conduit 19, and consecutively inside the heat exchanger 5.
• the mixing member 25 comprises a wall 30 which is continuous between the first longitudinal end 31a and the second longitudinal end 31b.
• a wall 30 hereinafter referred to as a centrifugal wall 30, is designed to direct the cooling fluid which comes into contact with it in a radial direction to the mixing member.
• the centrifugal wall 30 is twisted in part or in full between the first longitudinal end 31a and the second longitudinal end 31b.
• the centrifugal wall 30 has a preferentially constant thickness between the first longitudinal end 31a and the second longitudinal end 31b.
• the centrifugal wall 30 is for example arranged in a sheet which takes the form of a twist.
• the mixing member 25 preferably extends longitudinally at a center C of the duct 19 along of the axis of elongation A9 of the mixing member 25.
• the center C of the duct 19 corresponds to a central zone of the latter, for example cylindrical, and in particular homothetic to a shape of the duct 19.
• the mixing member 25 is constituted by a plurality of mixing elements 32 which are butted to each other.
• the mixing elements 32 are for example identical to each other and iteratively repeated along the axis of elongation A9.
• the mixing elements 32 are for example similar to each other and geometrically substitutable for each other without modifying the conformation of the mixing member 25.
• the mixing elements 32 are for example repeated one another. after the other being identical to each other, manufacturing tolerances close, which gives the mixing member 25 a geometric constancy from the first longitudinal end 31a to the second longitudinal end 31b.
• Each mixing element 32 extends longitudinally between a first edge 35 and a second edge 36.
• the first edge 35 and the second edge 36 are each formed of a ridge 50 of the centrifugal wall 30 aligned with a bottom 51, both substantially orthogonal to the axis of extension A9.
• Ridge 50 forms a slope inversion line at which a convex curvature of the auger reverses.
• the bottom 51 forms a slope inversion line at which a concave curvature of the auger is reversed.
• the centrifugal wall 30 changes direction of winding, going from a clockwise direction to a counterclockwise direction or from an anti-clockwise direction. hourly clockwise.
• Each mixing element 32 is of a first length L1, measured parallel to the axis of elongation A9, between the first edge 35 and the second edge 36.
• Two successive mixing elements 32 are exactly superimposed with each other from a translation of one towards the other along the axis of elongation A9, along a distance equal to the first length L1.
• the first edge 35 and the second edge 36 are parallel to each other and orthogonal to the axis of elongation A9.
• a first edge 35 of a mixing element 32 forms with a second edge 36 of an adjacent mixing element 32 a zero angle, since the first edge 35 of a mixing element 32 forms or is merged with a second edge 36 of an adjacent mixing element 32.
• Each mixing element 32 is formed of two mixing patterns 34a, 34b, which are identical to each other to manufacturing tolerances and which are abutted head to tail along the axis of elongation A9. It will be understood by a head-to-tail abutment of two mixing patterns 34a, 34b an arrangement such that the two mixing patterns 34a, 34b are superposable in an identical configuration with each other after tilting 180 ° the one towards the other in a fourth plane P4 comprising the axis of elongation A9.
• a winding direction of a first mixing pattern 34a is opposed to a winding direction of a second adjacent mixing pattern 34b constituting a same mixing element 32.
• the centrifugal wall 30 of one rotates in a clockwise direction and the centrifugal wall 30 of the other rotates in a counterclockwise direction.
• a curvature of a first mixing pattern 34a is opposite to the curvature of the second mixing patterns 34b.
• a mixing pattern, indifferently first pattern 34a or second pattern 34b, of the mixing element 32 illustrated in Figure 5, is shaped as a helical portion rotating about the axis of elongation A9.
• Each mixing pattern 34a, 34b extends longitudinally along the axis of elongation A9 between a first flange 35 'and a second flange 36'.
• the first flange 35 'and the second flange 36' are each formed of a ridge 50 and a bottom 51 of the centrifugal wall 30, where the curvature of the latter is reversed.
• the first flange 35 'and the second flange 36' are joined to each other to ensure the continuity of the centrifugal wall 30.
• a first flange 35 'of a first mixing pattern 34a forms with a second flange 36' a second adjacent mixing pattern 34b, participating in the same mixing element 32, since the first flange 35 'of a first mixing pattern 34a and the second flange 36' of a second adjacent mixing pattern 34b are butted.
• the first flange 35 'and the second flange 36' of the same mixing pattern 34 form a flange angle ⁇ between them.
• the flange angle ⁇ is preferably between 0 ° and 90 °, or even between 0 ° and 20 °.
• the first edge 35 and / or the second edge 36 which delimits a mixing element 32, and a first flange 35 'and / or a second flange 36' which delimits a mixing pattern 34a, 34b, is formed by a ridge 50 and a bottom 51. Indeed, peak and bottom each extend in a complementary half-section of the mixing member and they are advantageously aligned.
• the ridge 50 thus extends along a line of radial extension and which originates on the axis of elongation A9, while the bottom 51 extends along a line of radial extension and which originates on the axis of extension A9.
• the mixing member 25 is in particular made from a process for obtaining a polymer material by molding.
• the mixing member 25 is arranged to be obtained by molding without undercut.
• the mixing member 25 is for example obtained by means of a mold comprising a first matrix and a second matrix which together form a reserve of identical conformation to the mixing member 25.
• the mixing device 25 described above in particular its forms and its organization, is designed not to include a draft angle. The demolding of the mixing member is facilitated.
• the mixing member 25 is a monoblock element bringing together the mixing elements 32, in one piece, which can be dismounted into several elements only from a destruction of the mixing member 25.

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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)

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• 2016
  • 2016-11-30 FR FR1661763A patent/FR3059410B1/fr active Active
• 2017
  • 2017-11-30 CN CN201780082970.2A patent/CN110168303B/zh active Active
  • 2017-11-30 EP EP17817795.2A patent/EP3548829B1/de active Active
  • 2017-11-30 WO PCT/FR2017/053314 patent/WO2018100310A1/fr not_active Ceased

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