EP3548824B1 - Vorrichtung zur homogenisierung der verteilung eines kältemittels im innern von rohren eines einen kältemittelkreislauf bildenden wärmetauschers - Google Patents

Vorrichtung zur homogenisierung der verteilung eines kältemittels im innern von rohren eines einen kältemittelkreislauf bildenden wärmetauschers Download PDF

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Publication number
EP3548824B1
EP3548824B1 EP17816951.2A EP17816951A EP3548824B1 EP 3548824 B1 EP3548824 B1 EP 3548824B1 EP 17816951 A EP17816951 A EP 17816951A EP 3548824 B1 EP3548824 B1 EP 3548824B1
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EP
European Patent Office
Prior art keywords
mixing
homogenizing device
distribution
heat exchanger
refrigerant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
EP17816951.2A
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English (en)
French (fr)
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EP3548824A1 (de
Inventor
Jérémy BLANDIN
Kamel Azzouz
Julien Tissot
Patrick LEBLAY
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Valeo Systemes Thermiques SAS
Original Assignee
Valeo Systemes Thermiques SAS
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Publication date
Priority claimed from FR1661754A external-priority patent/FR3059414B1/fr
Priority claimed from FR1661742A external-priority patent/FR3059394B1/fr
Priority claimed from FR1661755A external-priority patent/FR3061282B1/fr
Application filed by Valeo Systemes Thermiques SAS filed Critical Valeo Systemes Thermiques SAS
Publication of EP3548824A1 publication Critical patent/EP3548824A1/de
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Publication of EP3548824B1 publication Critical patent/EP3548824B1/de
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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
    • F28F9/0273—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
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
    • F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
    • F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators

Definitions

  • the field of the present invention is that of heat exchangers constituting a refrigerant fluid circuit equipping a motor vehicle.
  • the subject of the invention is a device for homogenizing the distribution of a refrigerant fluid inside the tubes of such a heat exchanger.
  • a motor vehicle is commonly equipped with a ventilation, heating and/or air conditioning installation for thermally treating the air present or sent inside a passenger compartment of the motor vehicle.
  • a ventilation, heating and/or air conditioning installation for thermally treating the air present or sent inside a passenger compartment of the motor vehicle.
  • an installation is associated with a closed circuit inside which a refrigerant fluid circulates.
  • the refrigerant circuit successively comprises a compressor, a condenser or gas cooler, an expansion device and a heat exchanger.
  • the heat exchanger is housed inside the ventilation, heating and/or air conditioning installation to allow heat exchange between the refrigerant fluid and a flow of air circulating inside said installation, previously to delivery of the air flow inside the passenger compartment.
  • the heat exchanger is used as an evaporator to cool the air flow.
  • the refrigerant fluid is compressed inside the compressor, then the refrigerant fluid is cooled inside the condenser or gas cooler, then the refrigerant fluid undergoes expansion inside the expansion device and finally the refrigerant captures calories from the air flow inside the heat exchanger.
  • the refrigerant, at the outlet of the expansion device 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 collector box and a return box between which a bundle of tubes is interposed.
  • the coolant is admitted inside the heat exchanger through an inlet that includes the header box. Then, the coolant flows between the collector box and the return box by borrowing the tubes of the bundle.
  • a general problem posed resides in a difficulty in supplying the tubes of the bundle in a homogeneous manner with regard to the different phases, liquid and gaseous, of the refrigerant fluid.
  • the document US2015/0121950 proposes to house, inside the collector box, a device for homogenizing the distribution of the coolant inside the tubes of the bundle.
  • This device comprises a conduit provided with a plurality of orifices.
  • the duct comprises a first end part which is connected with a first inlet mouth for the refrigerant fluid inside the heat exchanger.
  • the duct is arranged in a cylindrical tube delimiting an interior volume in one piece inside which the refrigerant fluid circulates.
  • the liquid-phase refrigerant fluid is projected through the orifices provided through the pipe in the form of droplets.
  • Such an organization is not optimal from the point of view of the homogenization of the distribution of refrigerant fluid inside the heat exchanger. More particularly, the tubes of the bundle furthest from the first end part are frequently undersupplied with refrigerant fluid.
  • An object of the invention is to perfect the homogeneity of the distribution of refrigerant fluid inside the heat exchanger, in order finally to improve its efficiency and its output, with a view to delivering inside the passenger compartment air flow at the desired temperature.
  • Another object of the invention is to improve the distribution of refrigerant fluid inside the heat exchanger, including when the latter is present inside of the heat exchanger in two distinct phases, liquid and gas, in variable respective proportions.
  • Another object is to propose a device for distributing a coolant fluid inside the tubes of the bundle which ensures an equivalent supply of coolant fluid to the tubes of the bundle, including those which are furthest from the first end part. of the duct, which first receives the refrigerant fluid.
  • Another object is to propose a device for dispensing a coolant fluid which is arranged to avoid an accumulation of the coolant fluid in a zone of the latter.
  • a device of the present invention is a device for homogenizing the distribution of the refrigerant fluid inside the tubes of a heat exchanger with the characteristics of claim 1.
  • the device for homogenizing the distribution comprises a conduit provided at least one window through which the coolant is able to enter inside the duct and at least one orifice through which the coolant is able to exit the duct.
  • the duct houses at least one mixing member arranged to direct the refrigerant fluid from a center of the duct towards an internal face of the duct.
  • the invention also relates to a header box delimiting a first chamber housing at least one such device for homogenizing the distribution.
  • the invention also relates to a heat exchanger comprising such a box collector 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 present invention also relates to a use of such a heat exchanger as an evaporator housed inside a casing of a ventilation, heating and/or air conditioning installation fitted to a motor vehicle.
  • the refrigerant circuit 1 successively comprises, in a direction S1 of circulation of the refrigerant FR inside the refrigerant circuit 1, a compressor 2 for compressing the refrigerant FR, a condenser or a gas cooler 3 for cooling the refrigerant fluid FR, an expansion member 4 inside which the refrigerant fluid FR undergoes expansion and a heat exchanger 5.
  • the heat exchanger 5 is housed inside a housing 6 of an installation 7 for ventilation, heating and/or air conditioning inside which a flow of air circulates.
  • the heat exchanger 5 allows heat transfer between the refrigerant fluid FR and the air flow FA coming into contact with it and/or passing through it, as illustrated in the figure 2 . According to the mode of operation of the refrigerant circuit 1 described above, the heat exchanger 5 is used as an evaporator to cool the air flow FA, during the passage of the air flow FA in contact and / or right through the heat exchanger 5.
  • the heat exchanger 5 comprises a header box 8 and a return box 9 between which a bundle of tubes 10, 10a, 10b is interposed.
  • the heat exchanger 5 extends parallel to a first plane P1 containing the header box 8, the bundle of tubes 10, 10a, 10b and the return box 9.
  • the header box 8 overhangs the bundle of tubes 10, 10a, 10b, which are themselves located above the box of reference 9, in particular in the position of use of the heat exchanger 5 mounted inside the housing 6.
  • the collector box 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 air flow FA flows through the heat exchanger 5 in a direction preferably orthogonal to the foreground P1.
  • the tubes 10, 10a, 10b are for example straight and extend along a first general extension axis A1 between the header box 8 and the return box 9.
  • the header box 8 extends along a second extension axis general A2 and the transmission box 9 extends along a third axis of general extension A3.
  • the second general extension axis A2 and the third general extension axis A3 are mutually parallel, being orthogonal to the first general extension axis A1.
  • the bundle of tubes 10, 10a, 10b is provided with fins 15 which are interposed between two successive tubes 10, 10a, 10b, to promote heat exchange between the air flow FA and the tubes 10, 10a, 10b, when of a passage of the air flow FA through the heat exchanger 5, the air flow FA circulating in a direction substantially orthogonal to the foreground P1.
  • 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 inlet mouth for the refrigerant fluid FR in a first chamber 13 , which is delimited inside the collector box 8.
  • the heat exchanger 5 comprises a second mouth 17 through which the refrigerant FR is evacuated from the heat exchanger 5.
  • the heat exchanger 5 is a heat exchanger inside which the refrigerant fluid FR flows along a path arranged in an “I”.
  • the tubes 10 are arranged parallel to each other and are aligned inside the first plane P1.
  • the tubes 10 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 header box 8.
  • the return box 9 forms the base of the "I” while the header box 8 forms the top of the "I”.
  • the second mouth 17 equips the return box 9.
  • the refrigerant fluid FR penetrates inside the heat exchanger 5 through the first mouth 16 that includes the collector box 8. Then, the refrigerant fluid FR is distributed along the header box 8 along the second extension axis A2 by a distribution homogenization device 18. Then, the refrigerant fluid FR flows between the header box 8 and the return box 9 via the tubes 10. Finally, the refrigerant FR is evacuated from the heat exchanger 5 through the second mouth 17 of the return box 9.
  • the heat exchanger is a heat exchanger inside which the refrigerant fluid FR flows along a path arranged in a “U”.
  • the tubes 10a, 10b are arranged parallel to one another, being distributed along two layers 11, 12, including a first layer 11 of first tubes 10a and a second layer 12 of second tubes 10b.
  • the first ply 11 and the second ply 12 are arranged inside respective planes which are parallel to each other and parallel to the first plane P1.
  • the first tubes 10a of the first layer 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 return box 9 and a fourth end 104 which is in fluid communication with a second chamber 14, also delimited inside the header box 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 general extension axis A4 and the fifth general extension axis A5 together define a second plane P2, which is preferably orthogonal to the first plane P1.
  • the return box 9 forms the base of the "U” while the first layer 11 and the second layer 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 FR enters the interior of the heat exchanger 5 through the first mouth 16 of the first chamber 13, being distributed along the box collector 8 along the second axis of general extension A2 by the distribution homogenization device 18. Then, the refrigerant fluid FR flows between the first chamber 13 of the collector box 8 and the return box 9 by borrowing the first tubes 10a of the first layer 11. Then, the FR refrigerant fluid flows between the return box 9 and the second chamber 14 by borrowing the second tubes 10b of the second layer 12. Finally, the FR refrigerant fluid is evacuated outside of the heat exchanger 5 through the second mouth 17, after having circulated through the second chamber 14.
  • a first tube 10a of the first sheet 11 is aligned with a second tube 10b of the second sheet 12 inside a third plane P3 which is perpendicular to the first plane P1 and which is parallel to the first axis of general expansion A1.
  • the collector box 8 houses the device 18 for homogenizing the distribution of the refrigerant fluid FR inside the tubes 10, 10a, 10b.
  • a device for homogenizing the distribution 18 aims to evenly distribute the refrigerant FR, in the two-phase liquid-gas state, along the header box 8 and ultimately inside all the tubes. 10, 10a, 10b.
  • Such a device for homogenizing the distribution 18 aims more particularly to distribute the refrigerant fluid FR homogeneously 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 variable respective proportions.
  • the distribution homogenization device 18 comprises for example a duct 19 extending along a sixth axis of general extension A6, parallel, or even coincident, with the second axis of general extension A2 and/or the fourth axis of general extension A4, between a first end part 20 and a second end part 21 of conduit 19.
  • any element which extends along the sixth axis of general extension A6 which is defined by the largest dimension of the conduit 19 is qualified as longitudinal.
  • the first end part 20 is formed from one end of the duct 19, while the second end part 21 is formed from the other end of the duct 19, longitudinally opposite the first end part 20.
  • the first terminal part 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 duct 19 whose first end part 20 is placed in fluid communication with a pipe of the refrigerant circuit 1.
  • the second end part 21 is blind and forms a cul-de-sac with regard to the circulation of the refrigerant fluid FR at the inside of duct 19.
  • the duct 19 is for example shaped like a cylinder, or even like a parallelepiped or even like any other shape having an axis of symmetry A7, which is preferably parallel, or even coincident, with the sixth axis of general extension A6.
  • the duct 19 comprises a peripheral wall 23 which is of cylindrical cross-section when the duct 19 is shaped like a cylinder, of parallelepiped cross-section when the duct 19 is a parallelepiped.
  • the peripheral wall 23 is the one which gives the overall shape of the duct 19.
  • the peripheral wall 23 comprises at least orifices 22 which are made at the through the peripheral wall 23 of the duct 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 to the axis of symmetry A7.
  • the orifices 22 are equidistant from each other. According to another variant, the orifices 22 are separated from each other by a variable distance.
  • the orifices 22 are, for example, orifices of circular section, but may be of any conformation, rectangular, elliptical, oblong in particular.
  • the duct 19 constitutes an envelope which delimits an internal space 24 around which the duct 19 is provided.
  • the conduit 19 borders the internal space 24 that the conduit 19 surrounds.
  • the internal space 24 is for example cylindrical or else parallelepipedic, or else of any other shape provided around the axis of symmetry A7.
  • the peripheral wall 23 of the duct 19 comprises an internal face 23a which adjoins and which delimits the internal space 24, the internal 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 in particular provided to direct the refrigerant fluid FR from a center C of the conduit 19 towards the internal face 23a of the conduit 19.
  • the mixing member 25 is more particularly arranged to direct the refrigerant fluid FR from the center C of conduit 19 to the internal face 23a of the latter.
  • the mixing member 25 is a member allowing and facilitating a particularly centrifugal circulation of the refrigerant fluid FR from the center C of the duct towards the internal face 23a of the latter.
  • the mixing member 25 is also provided to avoid an accumulation of the refrigerant fluid in the liquid state in a lower zone of the conduit 19, in the position of use of the latter.
  • the mixing member 25 is also provided to disturb a laminar flow of the refrigerant fluid FR inside the conduit 19, with a view to 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, 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 the sixth axis of general extension A6 of the duct 19. According to the embodiments shown in the figures 4 to 12 , the mixing member 25 is arranged around a seventh axis of general extension A9, preferably parallel to, or even merging with, the axis of symmetry A7 of the conduit 19, when the mixing member 25 is positioned at the inside the duct 19, as shown in the figures 4 to 6 .
  • the mixing member 25 extends inside the entire internal space 24.
  • the mixing member 25 fills the entire volume delimited by the duct 19.
  • the mixing member 25 is of a conformity and / or a geometry similar to that of the internal space 24.
  • the mixing member 25 is likely to be of cylindrical shape or well parallelepipedic, or any other form arranged around the axis of symmetry A7. It will be understood that such a shape is globally defined by a peripheral edge 31 of the mixing member 25.
  • the peripheral edge 31 of the mixing member 25 is formed by the surfaces of the mixing member 25 which are arranged opposite each other. opposite pipe 19.
  • the internal face 23a of the peripheral wall 23 is preferably smooth to allow easy insertion of the mixing member 25 inside the duct 19, the peripheral edge 31 of the mixing member 25 resting against the internal face 23a. This characteristic of the internal face 23a is particularly advantageous when the mixing member 25 fills the whole of the volume delimited by the duct 19, as illustrated in the figure 4 .
  • the mixing member 25 only partially encumbers the internal space 24, an interstitial space 26 being provided between the mixing member 25 and the internal wall 23a of the conduit 19.
  • Such an interstitial space 26 facilitates flow of the refrigerant FR parallel to the sixth axis of general extension A6 inside the duct 19.
  • the refrigerant fluid FR does not encounters any obstacle inside the interstitial space 26, which facilitates the longitudinal circulation of the refrigerant fluid FR along the sixth axis of general extension A6, the mixing member 25 improving the transverse circulation of the refrigerant fluid FR from the center C of the conduit 19 towards the internal face 23a.
  • the interstitial space 26 has a volume which is less than the volume of the mixing member 25.
  • the volume of the interstitial space 26 is less than half the volume of the mixing member 25, or even less than a third of the volume of the mixing member 25, or even even less than a quarter of the mixing member 25.
  • Such an arrangement nevertheless allows the mixing member 25 to sufficiently disturb the flow refrigerant fluid FR to remove any laminar character from the latter, including in the presence of the interstitial space 26.
  • the conduit 19 is provided with two end walls 27, 28, of which a first end wall 27 fitted to the first end part 20 and a second end wall 28 fitted to the second end part 21.
  • the first end wall 27 and the second end wall 28 are for example flat and provided along the transverse plane Pt orthogonal to the sixth axis of general extension A6 and/or to the axis of symmetry A7.
  • the first end wall 27 and the second end wall 28 come, for example, from a lid covering at least partially the header box 8.
  • the first end wall 27 is equipped with at least one window 29 for the admission of the refrigerant fluid FR inside the internal space 24.
  • the first end wall 27 of the conduit 19 is equipped with the window 29 which is for example in fluidic relationship 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 interior of the heat exchanger 5 via the conduit 19 provided with orifices 22 through which the refrigerant FR is able to be evacuated from the conduit 19 to circulate inside the heat exchanger 5 .
  • the interstitial space 26 is provided between on the one hand the mixing member 25 and on the other hand the peripheral wall 23, the first end wall 27 and the second terminal wall 28.
  • the interstitial space 26 forms a volume which surrounds the mixing member 25.
  • the mixing member 25 comprises a first longitudinal end 31a which is capable of being attached to the first wall end 27 of conduit 19.
  • Mixing member 25 comprises a second longitudinal end 31b which can be attached to second end wall 28.
  • the interstitial space 26 is provided between the mixing member 25 and the peripheral wall 23, the mixing member 25 being attached to the first end wall 27 and the second end wall 28.
  • the interstitial space 26 forms a cylindrical sleeve around the mixing member 25.
  • the mixing member 25 is fixed at its longitudinal ends 31a, 31b respectively to the first end wall 27 and to the second end wall 28.
  • the refrigerant fluid FR penetrating inside the heat exchanger 5 penetrates inside the internal space 24 by borrowing the window 29 formed through the first end wall 27. Then, the refrigerant fluid FR spreads inside the internal space 24 while being mixed by the mixing member 25. This results in particular in a mixing of the liquid and gas phases of the refrigerant fluid FR which is then homogenized longitudinally, the along conduit 19. Then, the refrigerant fluid FR borrows the orifices 22 to flow out of the conduit 19 towards the first chamber 13. Then, the refrigerant fluid FR flows through the bundle of tubes 10, 10a, 10b, as described above, to the return box 9, to be evacuated from the heat exchanger 5 via the second mouth 17.
  • the refrigerant fluid FR encounters multiple obstacles which promote mixing between its liquid and gas phases.
  • such a conduit 19 promotes homogenization of the distribution of the refrigerant fluid FR inside the tubes 10, 10a, 10b.
  • the refrigerant fluid FR is all the better sprayed, and in a homogeneous manner, during its passage through the orifices 22 that the two phases of the refrigerant fluid FR, liquid and gas, are mixed by the mixing member 25 inside of the internal space 24 of the conduit 19, with a view to then supplying the bundle of tubes 10, 10a, 10b in a homogeneous manner.
  • 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 a second step, after homogenization of the refrigerant fluid FR in the internal space 24, which guarantees a better homogeneous distribution of the refrigerant fluid FR at the outlet of the pipe 19, and subsequently inside the heat exchanger 5.
  • the mixing member 25 comprises a shaft 29 carrying at least one centrifugal wall 30.
  • the shaft 29 preferably extends longitudinally in a center C of the duct 19 along the seventh axis of general extension 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 shaft 29 is in particular of the same conformation as the duct 19.
  • the shaft 29 is also cylindrical by being provided at the center C of the duct 19.
  • the shaft 29 consists of a central core of the mixing member 25 forming a continuity of material from the first longitudinal end 31a towards the second longitudinal end 31b.
  • the shaft 29 is for example arranged transversely to the center of gravity of the mixing member 25.
  • the shaft 29 is preferably shaped as a rectilinear rod from which the centrifugal wall 30 extends.
  • the centrifugal wall 30 extends from the shaft 29 to the peripheral edge 31 of the mixing member.
  • the centrifugal wall 30 is for example unique and extends from the first longitudinal end 31a of the mixing member 25 to the second longitudinal end 31b of the mixing member 25. In such a case, the centrifugal wall 30 is considered to be continuous between the two longitudinal ends 31a, 31b of the mixing member 25, as illustrated in the figures 6 and 7 .
  • the centrifugal wall 30 is for example discontinuous. It is understood here that the mixing elements 32, constituting the centrifugal wall 30, are separated from each other others by notches 33, visible for example on the figures 9 to 11 .
  • the mixing elements 32 are for example identical to one another and iteratively repeated along the axis of symmetry A7. In other words, 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 after the other, being identical to each other, which gives the mixing member 25 geometric homogeneity from the first longitudinal end 31a to the second longitudinal end 31b.
  • Each mixing element 32 is for example still formed of two mixing patterns 34, identical to each other but butted head to tail along the axis of symmetry A7.
  • the centrifugal wall 30 is unique and winds longitudinally along the shaft 29.
  • the mixing member 25 is then shaped like a helical screw comprising a single thread formed by the centrifugal wall 30 and a central web formed by the shaft 29.
  • the pitch of the propeller is for example determined so that one pitch supplies an orifice 22. In other words, the pitch of the propeller is equal to a distance between two neighboring orifices 22 of the conduit 19.
  • the mixing member 25 comprises a plurality of centrifugal walls 30 which are continuous from the first longitudinal end 31b to the second longitudinal end 31b and which wind longitudinally along the shaft 29.
  • the mixing member 25 has six centrifugal walls 30 equidistant from each other longitudinally.
  • the mixing device 25 is shaped like a helical screw comprising, for example, six threads formed by the six centrifugal walls 30 and a central web formed by the shaft 29.
  • the pitch of the helices is equal to one helix to another.
  • the pitch of the helices is equal to a distance between two neighboring orifices 22 of conduit 19.
  • the centrifugal wall 30 comprises a plurality of mixing elements 32 separated from each other by indentations 33.
  • the mixing elements 32 are identical to each other and iteratively repeated along the seventh axis of general extension A9. In other words, the mixing elements 32 are successively butted together on shaft 29.
  • Each mixing element 32 extends longitudinally between a first leading edge 35 and a second leading edge 36.
  • the first leading edge 35 and the second leading edge 36 are each formed of an edge of the centrifugal wall 30 which is substantially orthogonal to the shaft 29 and which delimits the centrifugal wall 30 with respect to the indentations 33.
  • the first leading edge 35 and the second leading edge 36 are longitudinally opposed to each other along the seventh axis of general extension A9.
  • first leading edge 35 and the second leading edge 36 of a mixing element 32 form between them a first angle ⁇ of between 70° and 110°, preferably equal to 90°.
  • a first leading edge 35 of a mixing element 32 forms with a second leading edge 36 of an adjacent mixing element 32 a second angle ⁇ of between 70° and 110°, preferably equal to 90°.
  • Each mixing element 32 is for example formed of two mixing patterns 34, identical to each other but butted together head to tail along the axis of symmetry A7.
  • a winding direction of a mixing pattern 34 is opposed to a winding direction of an adjacent mixing pattern 34 constituting the mixing element 32.
  • the centrifugal wall 30 of one rotates clockwise and the centrifugal wall 30 of the other rotates counterclockwise.
  • FIG. 12 On the figure 12 , is shown a mixing pattern 34 of the mixing element 34 illustrated in the figures 10 and 11 , whose centrifugal wall 30 is shaped as a helix portion formed around the shaft 29.
  • Each mixing element 32 extends longitudinally between a first leading edge 35' and a second leading edge 36'.
  • the first leading edge 35' and the second leading edge 36' are each formed of an edge of the centrifugal wall 30 which is substantially orthogonal to the shaft 29 and which delimits the centrifugal wall 30 with respect to a groove 37 formed between two mixing patterns 34.
  • the first leading edge 35' and the second leading edge 36' are longitudinally opposed to each other along the seventh axis of general extension A9.
  • first leading edge 35' and the second leading edge 36' of a mixing pattern 34 are parallel.
  • a first leading edge 35' of a mixing pattern 34 forms with a second leading edge 36' of an adjacent mixing pattern 34 participating in the same mixing element 32 a third angle ⁇ between 70° and 110°, preferably equal to 90°.
  • the mixing member 25 is in particular obtained by molding a polymer.
  • the mixing device 25 is a one-piece element bringing together the shaft 29 and the mixing elements 32, in one piece, which can only be dismantled into several elements from the destruction of the mixing device 25.

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

Claims (18)

  1. Vorrichtung zur Homogenisierung der Verteilung (18) des Kältemittels (FR) im Inneren von Rohren (10, 10a, 10b) eines Wärmetauschers (5), wobei die Vorrichtung zur Homogenisierung der Verteilung (18) eine Leitung (19) umfasst, die mit mindestens einem Fenster (29) versehen ist, durch welches das Kältemittel (FR) in das Innere der Leitung (19) eintreten kann, und mindestens eine Öffnung (22), durch welche das Kältemittel (FR) aus der Leitung (19) austreten kann, wobei die Leitung (19) mindestens ein Mischorgan (25) aufnimmt, das dazu eingerichtet ist, das Kältemittel (FR) von einem Zentrum (C) der Leitung (19) zu einer Innenseite (23a) der Leitung (19) hin zu leiten, wobei das Mischorgan (25) mindestens eine Welle (29) umfasst, die mit mindestens einer Zentrifugalwand (30) ausgestattet ist, wobei die Zentrifugalwand (30) Mischelemente (32) umfasst, die von der Welle (29) getragen werden und die voneinander durch mindestens einen Ausschnitt (33) getrennt sind, dadurch gekennzeichnet, dass jedes Mischelement (32) mindestens zwei Mischmuster (34) umfasst, die identisch sind und entgegengesetzte Wickelrichtungen aufweisen.
  2. Vorrichtung zur Homogenisierung der Verteilung (18) nach Anspruch 1, wobei die Leitung (19) ein Innenvolumen (24) begrenzt, in dessen Inneren sich das Mischorgan (25) mindestens teilweise erstreckt.
  3. Vorrichtung zur Homogenisierung der Verteilung (18) nach Anspruch 2, wobei das Mischorgan (25) die Gesamtheit des Innenvolumens (24) einnimmt.
  4. Vorrichtung zur Homogenisierung der Verteilung (18) nach Anspruch 1, wobei die Welle (29) sich im Zentrum (C) der Leitung (19) erstreckt.
  5. Vorrichtung zur Homogenisierung der Verteilung (18) nach einem der Ansprüche 1 und 4, wobei die Zentrifugalwand (20) sich zwischen der Welle (29) und der Innenseite (23a) der Leitung (19) erstreckt.
  6. Vorrichtung zur Homogenisierung der Verteilung (18) nach einem der vorhergehenden Ansprüche, wobei die Innenseite (23a) glatt ist.
  7. Vorrichtung zur Homogenisierung der Verteilung (18) nach einem der Ansprüche 1 oder 4 bis 6, wobei die Welle (29) mit einer Mehrzahl von Zentrifugalwänden (30) ausgestattet ist, die zwischen zwei Längsenden (31a, 31b) des Mischorgans (25) durchgehend sind.
  8. Vorrichtung zur Homogenisierung der Verteilung (18) nach Anspruch 7, wobei die Zentrifugalwände (30) identisch zueinander sind.
  9. Vorrichtung zur Homogenisierung der Verteilung (18) nach Anspruch 1, wobei die Mischelemente (32) entlang der Welle (29) iterativ wiederholt werden.
  10. Vorrichtung zur Homogenisierung der Verteilung (18) nach einem der Ansprüche 1 und 9, wobei jedes Mischelement (32) in einem Wendelabschnitt eingerichtet ist.
  11. Vorrichtung zur Homogenisierung der Verteilung (18) nach einem der Ansprüche 1 oder 9 bis 10, wobei jedes Mischelement (32) sich zwischen einer ersten Anströmkante (35) und einer zweiten Anströmkante (36) erstreckt, die untereinander einen ersten Winkel (α) zwischen 70° und 110° bilden.
  12. Vorrichtung zur Homogenisierung der Verteilung (18) nach Anspruch 11, wobei die erste Anströmkante (35) eines Mischelements (32) mit einer zweiten Anströmkante (36) eines benachbarten Mischelements (32) einen zweiten Winkel (β) zwischen 70° und 110° bildet.
  13. Vorrichtung zur Homogenisierung der Verteilung (18) nach Anspruch 1, wobei das Mischmuster (34) sich zwischen einem ersten Anströmrand (35') und einem zweiten Anströmrand (36') erstreckt, die parallel zueinander sind.
  14. Vorrichtung zur Homogenisierung der Verteilung (18) nach Anspruch 13, wobei der erste Anströmrand (35') eines Mischmusters (34) mit einem zweiten Anströmrand (36') eines benachbarten Mischmusters (34) einen dritten Winkel (γ) zwischen 70° und 110° bildet.
  15. Endkammer (8), die einen ersten Raum (13) begrenzt, der mindestens eine Vorrichtung zur Homogenisierung der Verteilung (18) nach einem der vorhergehenden Ansprüche aufnimmt.
  16. Wärmetauscher (5), der eine Endkammer (8) nach Anspruch 15 und eine Umlenkkammer (9) umfasst, zwischen denen ein Rohrbündel (10, 10a, 10b) angeordnet ist.
  17. Kältemittelkreislauf (1), der mindestens einen Wärmetauscher (5) nach Anspruch 16 umfasst.
  18. Verwendung eines Wärmetauschers (5) nach Anspruch 16 als Verdampfer, der im Inneren eines Gehäuses (6) einer Lüftungs-, Heizungs- und/oder Klimaanlage (7) aufgenommen ist, mit der ein Kraftfahrzeug ausgestattet ist.
EP17816951.2A 2016-11-30 2017-11-30 Vorrichtung zur homogenisierung der verteilung eines kältemittels im innern von rohren eines einen kältemittelkreislauf bildenden wärmetauschers Active EP3548824B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FR1661754A FR3059414B1 (fr) 2016-11-30 2016-11-30 Dispositif d’homogeneisation de la distribution d’un fluide refrigerant a l’interieur de tubes d’un echangeur de chaleur constitutif d’un circuit de fluide refrigerant
FR1661742A FR3059394B1 (fr) 2016-11-30 2016-11-30 Dispositif d’homogeneisation de la distribution d’un fluide refrigerant a l’interieur de tubes d’un echangeur de chaleur constitutif d’un circuit de fluide refrigerant
FR1661755A FR3061282B1 (fr) 2016-11-30 2016-11-30 Echangeur de chaleur constitutif d’un circuit de changeur fluide refrigerant
PCT/FR2017/053312 WO2018100308A1 (fr) 2016-11-30 2017-11-30 Dispositif d'homogénéisation de la distribution d'un fluide réfrigérant à l'intérieur de tubes d'un échangeur de chaleur constitutif d'un circuit de fluide réfrigérant

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EP3548824B1 true EP3548824B1 (de) 2023-03-29

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CN113819774A (zh) * 2021-08-30 2021-12-21 南京航空航天大学 一种提高流动均匀性的换热装置

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US1537553A (en) * 1924-06-10 1925-05-12 Samuel W Rushmore Radiator
JPS60158294A (ja) * 1984-01-30 1985-08-19 Mitsubishi Heavy Ind Ltd 燃料改質装置
US20040156763A1 (en) * 2001-03-12 2004-08-12 Wood Mark D. Reactor apparatus and mixing inlet and methods
CN1536316A (zh) * 2003-04-11 2004-10-13 乐金电子(天津)电器有限公司 热交换器的制冷剂均匀分配装置
US7331195B2 (en) * 2004-10-01 2008-02-19 Advanced Heat Transfer Llc Refrigerant distribution device and method
JP2006336890A (ja) * 2005-05-31 2006-12-14 Calsonic Kansei Corp インタークーラ
EP2079974B1 (de) * 2006-10-13 2012-03-14 Carrier Corporation Verfahren und vorrichtung zur verbesserung der fluidverteilung in einem wärmetauscher
CN102564204B (zh) * 2010-12-08 2016-04-06 杭州三花微通道换热器有限公司 制冷剂分配装置和具有它的换热器
JP5759068B2 (ja) * 2012-05-17 2015-08-05 三菱電機株式会社 熱交換器及び冷凍サイクル装置
US9568225B2 (en) 2013-11-01 2017-02-14 Mahle International Gmbh Evaporator having a hybrid expansion device for improved aliquoting of refrigerant
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