EP2980509B1 - Einlassverteiler für einen verdampfer, herstellungsverfahren eines solchen verteilers, verdampfer, der einen solchen verteiler umfasst, und thermische anlage mit zweiphasen-wärmeübertragungsmittel - Google Patents

Einlassverteiler für einen verdampfer, herstellungsverfahren eines solchen verteilers, verdampfer, der einen solchen verteiler umfasst, und thermische anlage mit zweiphasen-wärmeübertragungsmittel Download PDF

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Publication number
EP2980509B1
EP2980509B1 EP15178404.8A EP15178404A EP2980509B1 EP 2980509 B1 EP2980509 B1 EP 2980509B1 EP 15178404 A EP15178404 A EP 15178404A EP 2980509 B1 EP2980509 B1 EP 2980509B1
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EP
European Patent Office
Prior art keywords
manifold
dispatcher
distributor
ribs
evaporator
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EP15178404.8A
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English (en)
French (fr)
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EP2980509A1 (de
Inventor
Fabien Couturier
Slimane Meziani
Eddy LHENORET
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Compagnie Industrielle dApplications Thermiques SA CIAT
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Compagnie Industrielle dApplications Thermiques SA CIAT
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    • 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
    • F25B45/00—Arrangements for charging or discharging refrigerant
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/09—Improving heat transfers

Definitions

  • the present invention relates to an inlet distributor for an evaporator of a two-phase refrigerant thermal installation, as well as to a method of manufacturing this distributor.
  • the invention also relates to an evaporator belonging to a thermal installation and comprising such a distributor.
  • the invention relates to a thermal installation with two-phase refrigerant which comprises such an evaporator.
  • a heat pump comprising an evaporator, a compressor, a condenser and an expander.
  • the evaporator allows heat to be taken from an area, called a cold source, by means of a refrigerant.
  • the fluid consists of two phases, a vapor phase and a liquid phase, 80% of the fluid being generally still in the liquid phase.
  • a heat source transmits heat energy to the fluid. This having a weak pressure, it evaporates.
  • all of the fluid is in gaseous form and is sucked in by the compressor.
  • An evaporator comprises a bundle of tubes, in which the refrigerant circulates, allowing the latter to be in contact with the heat source over a large surface area.
  • the overall performance of the evaporator, and therefore of the entire heat pump depends on the temperature uniformity of the fluid contained in each channel.
  • the fluid passing through the evaporator must heat up in the same way in each of the channels of the evaporator, so that the temperature is the same at the outlet of each channel of the bundle.
  • a temperature in one of the channels lower than the temperature in the other channels, reduces the temperature of the fluid leaving the evaporator and therefore the overall efficiency of the heat pump.
  • an evaporator comprises, at the entry of the refrigerant fluid into its internal volume, a distributor whose role is to distribute the fluid evenly.
  • a two-phase refrigerant distributor comprising a cup-shaped grid, onto which is welded a metal cone forming a distributor.
  • This distributor is installed at the inlet of an evaporator, at the end of an inlet pipe.
  • the cone creates an obstacle to the passage of the fluid which accelerates the fluid and allows it to be distributed over the edges of the grid.
  • the fluid passes through orifices in the grid and is projected radially, outwardly relative to the center of the cup.
  • This distributor allows the fluid to be distributed in an acceptable manner in the channels of the evaporator.
  • the distribution of the fluid in the pipes is not optimal and there are temperature differences between the channels.
  • EP 0 895 051 A1 discloses a dispenser according to the preamble of claim 1.
  • JP-A-2000 111 205 teaches providing a core with a conical tip for a distributor intended for use with an evaporator of the "direct expansion exchange coil" type.
  • This type of distributor is not directly suitable for use with a multitubular type evaporator.
  • a cover In known equipment, a cover must be placed downstream of the core, to allow the connection of the capillary tubes of the direct expansion exchange coil, which cannot be transposed to a distributor for a multitubular exchanger.
  • US-A-5,059,226 discloses a centrifugal distributor which comprises a conical central hub arranged in a cylindrical part with circular section of a body which has, moreover, a frustoconical portion, the smallest section of which faces downstream.
  • the top of the conical central hub is disposed at the junction between the cylindrical and frustoconical portions of the body of the distributor and does not protrude relative to them. The flow of the heat transfer fluid around the conical central hub is not optimized.
  • the invention more particularly intends to remedy by proposing a new inlet distributor making it possible to better mix the two phases of the fluid and to obtain a more homogeneous distribution in the channels of the evaporator.
  • the invention relates to an inlet distributor for a multitubular evaporator of a thermal installation with two-phase refrigerant, this distributor comprising a diffusion grid and a distributor of generally conical shape, having a top and a base fixed to the diffusion grid respectively directed towards an upstream side and a downstream side of the distributor.
  • This distributor also comprises a member pierced with a tapered bore centered on the axis of the distributor and which surrounds this distributor, while the smallest area section of the tapered bore of the insert is directed towards the upstream side. from the distributor.
  • the top of the distributor protrudes from the frustoconical bore of the insert upstream, over a non-zero distance.
  • a confined passage volume for the two-phase refrigerant is created around the distributor and inside the frustoconical bore of the insert.
  • This confined passage volume ensures a circumferential distribution of the refrigerant around the central axis of the distributor, even in the event of a relatively low flow rate of the refrigerant inside the distributor. Thanks to the fact that the top of the distributor protrudes upstream from the frustoconical bore of the insert, the flow of refrigerant can be established around the distributor before this flow propagates inside the tapered bore. This facilitates the distribution of the fluid around the distributor, in particular in the case where the latter is provided with ribs for guiding the refrigerant.
  • This arrangement therefore makes it possible to channel the two-phase mixture from the cylindrical supply pipe where the speed is the highest and where the vapor-liquid mixture is in homogeneous form, which eliminates the risk of stratification, in particular at load. partial.
  • This thus contributes to balancing the mass flow rates circulating in each channel formed between two helical ribs when the distributor is formed of such ribs.
  • the jet passing through the grid located at the base of the cone has a radial symmetry suitable for irrigating the bundle of tubes as well as possible.
  • the invention also relates to a method of manufacturing a dispenser as mentioned above.
  • the distributor is manufactured by three-dimensional printing.
  • the invention relates to a multitubular evaporator of a thermal installation with two-phase refrigerant comprising a distributor as mentioned above installed upstream of an internal distribution volume of the evaporator, itself arranged upstream of a two-phase refrigerant distribution system, the top of the distributor being directed upstream and the grid downstream, in the direction of the internal distribution volume, according to the direction of flow of the two-phase refrigerant .
  • the invention relates to a two-phase refrigerant installation which comprises an evaporator as mentioned above.
  • the figure 1 partially represents a multitubular evaporator 1 equipped with a distributor 2 in accordance with the invention.
  • This distributor 2 is attached to the end of an inlet pipe 4, at the inlet of the evaporator 1.
  • a two-phase refrigerant flows from the intake pipe 4 to an internal volume 3 of the evaporator 1 passing through the distributor 2.
  • X4 is denoted by the longitudinal and central axis of the pipe 4.
  • the evaporator 1 belongs to a thermal installation, in particular of the heat pump type, with two-phase refrigerant.
  • This installation which is not represented other than by the part of the evaporator visible at figure 1 , also includes a compressor, condenser and expansion valve.
  • the evaporator 1 is of the multitubular type and comprises an assembly of rectilinear tubes 6 held at each of their ends by crimping or expanding in a perforated plate 7 called a tube plate. All the tubes form the tube bundle inside which the refrigerant at low pressure evaporates.
  • the tube bundle is enclosed in a metal shell 8 usually called a shell in which circulates a coolant in liquid phase, such as water or glycol water, etc., which gives way, by heat exchange through the wall of the tubes. 6 tubes its heat to the refrigerant.
  • the flow of this heat transfer fluid is represented by the arrow F2 at the figure 1 , from a sleeve 9 entering the grille.
  • baffles are regularly arranged along the tube bundle, the purpose of which is to increase the intensity of the heat transfer between the two fluids .
  • the evaporator can be of the known type of FR-A-2 997 174 .
  • the evaporator 1 comprises, in the end wall 13, an orifice 14 for entering the two-phase refrigerant into the volume 3.
  • the pipe 4 makes it possible to direct the two-phase refrigerant to the distributor 2, which is fixed in the orifice 14. More precisely, an insert 16, which belongs to the distributor 2, is mounted in the orifice 14.
  • the pipe 4 is connected to an external or upstream face 162 of the insert 16 which is oriented upstream of the refrigerant flow when insert 16 is in place in bore 14 and when evaporator 1 is in use.
  • the two-phase refrigerant flows along and inside the intake pipe 4 then within the distributor 2 before being distributed to the various channels 8 within the volume 3 as represented by the arrows F1 '. We call upstream the direction from which the refrigerant comes and downstream its destination direction. On the figure 1 , the arrows F1 and F1 'are directed from upstream to downstream.
  • the distributor 2 comprises a grid 20 in the form of a cup, on which is fixed a distributor 30 of generally conical shape. More precisely, the grid 20 has the shape of a truncated sphere, centered on an axis X20 with its concavity turned towards the distributor 30, that is to say downward on the figure 4 .
  • the grid 20 comprises, in its center, a circular opening 22, defining an internal peripheral edge 24 of the grid 20.
  • a surface 25 of the grid is pierced with orifices 26, regularly spaced.
  • the grid 20 comprises an outer peripheral edge 28, making it possible to fix it on the insert 16 or on the periphery of the orifice 14 of the evaporator 1, on the downstream side thereof.
  • the edge 28 is planted and perpendicular to the axis X20.
  • the edge 28 is pierced with three orifices 29, regularly spaced around the axis X20, and of diameter adapted to the passage of a screw.
  • the grid can be screwed or attached to the wall 13.
  • the edge 28 is circular. However, it may have a different shape, for example lobed.
  • the grid is formed by a layer of metal a few millimeters thick and can in particular be made of steel and obtained by stamping.
  • the distributor 30 of generally conical shape is fixed on the internal edge 24 of the grid 20. It comprises a circular base 32 centered on an axis X30 to which it is perpendicular and a vertex 34.
  • the diameter of the base 32 of the distributor 30 is substantially equal to the diameter of the circular opening 22 of the grid 20.
  • the edge 36 of the base is fixed to the internal edge 24 of the grid 20 and the axes X20 and X30 are combined, in an axis X2, in the assembled configuration of the distributor 2.
  • the axis X2 passes through the center 33 of the base 32 and through the top 34.
  • X16 denotes a central axis of the insert 16. This insert is pierced with a cylindrical bore 17 and a tapered bore 18 both centered on the axis X16.
  • the bore 17 extends from the upstream face 162, up to the bore 18, which extends from the bore 17 towards a downstream face 164 of the insert 16, opposite the upstream face 162.
  • L ' bore 18 diverges in the upstream downstream direction of insert 16, that is to say going from face 162 to face 164.
  • S18 denotes the smallest area section of the bore 18 and S18 'its largest area section.
  • the section S18 is the junction section between the bores 17 and 18. It is oriented upstream of the distributor 2, that is to say towards the face 162, relative to the rest of the bore 18, while section S18 'is axially aligned with face 164.
  • ⁇ the half-angle at the top of the frustoconical surface 182 which delimits the bore 18 inside the insert 16.
  • the top 34 of the distributor 30 is directed upstream, the axes X2, X4, X16, X20 and X30 are merged and the distributor 30 protrudes upstream, relative to section S18 and in the direction of face 162 of insert 16, over a non-zero distance d, which is preferably greater than 20 mm for a distributor 2 whose base 32 has a diameter of the order of 70 mm and a length, measured along the axis X2 between this base and the top 34, of the order of 85 mm while the wall 13 has a thickness of the order of 60 mm.
  • the top 34 protrudes from the bore 18 over the distance d and the distributor 30 extends partially into the bore 17.
  • the distance d is non-zero ensures that the refrigerant begins to circulate around the outer surface 37 of the distributor 30, while it is still upstream of the bore 18. This facilitates the flow of the refrigerant and also participates in maintaining a homogeneous jet through the grid 20, in particular at partial load, when the flow rate of refrigerant, and therefore the speed in the pipe 4, are reduced. This also makes it possible to promote the distribution of the flow around the distributor when the mass content of vapor is reduced, in particular in the case of low condensing temperature operation of the refrigeration unit and / or use of an economizer. This also allows the refrigerant to have a higher homogeneous density, which means that, for the same mass flow, the volume flow and therefore the speed are also reduced.
  • the distributor 30 comprises on its outer surface 37, which is conical, between its base 32 and its top 34, ribs 38.
  • the ribs 38 extend from the top 34 of the distributor 30 to its base 32 and have a shape twisted, generally like a propeller pressed against a cone.
  • each rib 38 is denoted by H38, measured perpendicularly to the surface 37, between this surface and the edge 382 of the rib.
  • the edge 382 of a rib is the edge of this rib opposite to the surface 37.
  • the height H38 of a rib 38 is the distance between its edge 382 and a junction line 384, measured perpendicular to the surface 37.
  • the height H38 increases along the axis X2 going from the top 34 towards the base 32. In other words, the height H38 of the ribs is greater at the level of the base 32 of the distributor 30 than at its top 34.
  • the distributor 30 is provided with six ribs 38, regularly spaced around the axis X2.
  • the number of ribs can be higher or lower.
  • the distributor 30 can include three, four, five, six or eight ribs 38, regularly spaced.
  • the ribs 38 are not regularly spaced, in order to generate an irregular movement of the two-phase fluid, making it possible to agitate it more as it passes through the orifice 14.
  • the surfaces 182 and 37 define between them a volume V2 for the passage of the refrigerant which extends around the axes X2, X4, X16, X20 and X30 combined.
  • this volume V2 has a cross section, perpendicular to the aforementioned axes, the area of which is relatively small, it is permanently force-fed by the refrigerant coming from the pipe 4, even if the evaporator 1 operates at partial load.
  • the refrigerant fluid is distributed homogeneously around the distributor 30, without having a tendency to separate into a gaseous part located above the axis X2 and a liquid part located below this axis.
  • the purpose of the ribs 38 is to guide the fluid entering the evaporator 1.
  • the curvature of the ribs 38 around the axis X2 makes it possible to give the fluid a rotational movement around the axes X2 and X4 combined at the outlet of the distributor, as represented by arrows F3 at the figure 7 .
  • This rotational movement stirs the fluid, mixes the two gaseous and liquid phases of the fluid and makes it possible to obtain a better distribution of the fluid in the volume 3 and the channels 8.
  • the bore 18 surrounds only a part of the distributor 2, namely its part closest to the base 32. In this way, the top 34 and the ribs 38 of the distributor 30 protrude. from bore 18 upstream, over distance d.
  • the insert 16 reduces the volume of passage of the fluid around the distributor 30 and forces the passage of the latter along the grooves 38 of the distributor 30, which accelerates the fluid and increases the efficiency of the ribs 38.
  • the intake pipe 4 is mounted against the insert 16 and its emerging section is adapted to the diameter of the bore 17, that is to say to the smallest diameter of the frustoconical bore 18 of the insert 16.
  • the refrigerant is brought into the evaporator 1 through the inlet pipe 4, in which all the components of the fluid have substantially the same speed.
  • the fluid flows parallel to the axis X4 and a surface perpendicular to the arrow F1 and corresponding to the passage section of the fluid is called the fluid flow front.
  • the refrigerant comes into contact with the top 34 distributor 30 and the passage section of the fluid decreases inside the pipe 4, until the front fluid flow reaches the bore 18.
  • the refrigerant then passes between the outer surface 37 of the distributor 30 and the inner surface 182 of the insert 16 and then through the orifices 26 of the grid 20. It is then projected into the internal volume 3 of the evaporator 1, which the arrows F1 'represent.
  • the distributor 30 can be made of metal, in particular of steel. In this case, it can be assembled to the grid 20 by welding.
  • the distributor 30 of the distributor 2 is made of synthetic material and manufactured by three-dimensional printing.
  • This manufacturing method gives the designer great freedom. It makes it possible to produce a distributor 30 according to various geometries. Thus, it is possible to achieve a large number of variations in the shape of the ribs 38. In addition, this method makes it possible to adapt the dimensions of the distributor 30 to the dimensions of the evaporator 1, more particularly to those of the bore 18. Furthermore, three-dimensional printing makes it possible to produce complex shapes at a lower cost and rapidly, which would be difficult to produce by a conventional machining process.
  • the grid 20 is preferably integral with the distributor 30 and obtained by the same manufacturing technique. This ensures geometric and mechanical continuity between these parts, without having to proceed with gluing or welding.
  • the grid 20 does not have a circular opening 22 and the distributor 30 is fixed to an internal central surface of the grid 20.
  • the grid 20 may have a shape different from that described above.
  • the holes 26 can be formed in the form of grooves or have large dimensions, so that the grid has four large holes and the inner edge 24 of the grid is only held in position by four metal tabs. connected to edge 28 which allows the grid to be fixed on evaporator 1.
  • the distributor 2 may include a distributor 30 formed by a smooth cone, while the surface 182 of the insert 16, which defines the frustoconical bore 18, is provided with ribs which extend in the direction of the X16 axis.
  • This embodiment is based on a mirror solution compared to that shown on the figures 1 to 8 and in which the ribs provided on the insert 16 also contribute to guiding the refrigerant in the circular space defined between the outer surface of the distributor 30 and the surface 182.
  • ribs for guiding the refrigerant can be provided on both surfaces 37 and 182.
  • the outer surface 37 of the distributor 30 is smooth, that is to say devoid of ribs, as is the surface 182 which defines the frustoconical bore 18 inside the insert 16.
  • annular slot is defined between the facing surfaces 37 and 182 when the distributor 30 is in place in the insert 16, as shown in figure 9 , this annular slot being identified as a volume V2 characteristic of the distributor 2.
  • the half-angle at the top ⁇ of the surface 182 is equal to the half-angle at the top ⁇ of the surface 37, so that the thickness of the annular slot V 2 is constant along the axis X2.
  • this annular slot is itself divergent or convergent from upstream to downstream of the distributor 2, that is i.e. from face 162 to face 164.
  • section S18 of smaller area of the bore 18 is directed upstream with respect to this bore, that is to say on the side of the face 162.
  • the top 34 of the distributor 30 protrudes upstream with respect to the smallest section S18 of the frustoconical bore 18, over a distance d which is not zero, in particular greater than 20 mm as explained above.
  • the invention is shown in the case where an insert 16 is installed in the opening 14 of the wall 13.
  • the wall 13 itself can define a frustoconical bore for receiving the distributor 30 of the distributor 2.
  • the member which defines this frustoconical bore is the wall 13 itself which partly belongs to the distributor 2.

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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)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Claims (15)

  1. Ansaugverteiler (2) für einen Rohrbündel-Verdampfer (1) einer Zweiphasenkältemittel-Heizanlage, wobei der Verteiler umfasst: ein Diffusionsgitter (20) und einen auf einer Achse (X30) zentrierten, insgesamt kegelförmigen Austeiler (30), umfassend eine Spitze (34) sowie eine auf dem Diffusionsgitter befestigte Basis (32), die jeweils auf eine vor- (162) bzw. nachgelagerte Seite (164) des Verteilers gerichtet ist, wobei der Verteiler dadurch gekennzeichnet ist, dass er ferner ein Element (16) mit einer auf der Achse (X30) des Austeilers (30) zentrierten kegelstumpfförmigen Bohrung (18) umfasst, das den Austeiler umgibt, dass der kleinere Querschnitt (S18) der kegelstumpfförmigen Bohrung auf die vorgelagerte Seite (162) des Verteilers (2) gerichtet ist, und dass die Spitze (34) des Austeilers (30) in einem Abstand (d) ungleich Null über die kegelstumpfförmige Bohrung (18) des Einsatzes (16) nach unten hinausgeht.
  2. Verteiler (2) nach Anspruch 1, dadurch gekennzeichnet, dass der Austeiler (30) auf dessen Außenfläche zwischen dessen Basis (32) und dessen Spitze (34) Rippen (38) zur Führung des Kältemittels aufweist.
  3. Verteiler (2) nach Anspruch 2, dadurch gekennzeichnet, dass die Rippen (38) verdrillt und insgesamt als auf einem Kegel angeordnete Helix ausgestaltet sind.
  4. Verteiler (2) nach einem der Ansprüche 2 oder 3, dadurch gekennzeichnet, dass sich die Rippen (38) von der Spitze (34) zur Basis (32) des Austeilers (30) erstrecken.
  5. Verteiler (2) nach einem der Ansprüche 2 - 4, dadurch gekennzeichnet, dass die Rippen (38) relativ zu einer Außenfläche (37) des Austeilers (30) hervorstehen, wobei die Außenfläche (37) kegelförmig ist.
  6. Verteiler (2) nach Anspruch 5, dadurch gekennzeichnet, dass die zwischen der Außenfläche (37) des Austeilers (30) und einer der Außenfläche entgegengesetzten Kante (382) der Rippe, senkrecht zur Außenfläche, gemessene Höhe (H38) jeder Rippe (38) von der Spitze (34) hin zur Basis (32) des Austeilers (30) zunimmt.
  7. Verteiler nach einem der Ansprüche 2 - 6, dadurch gekennzeichnet, dass die Rippen (38) des Austeilers (30) ebenfalls stromaufwärts über die kegelstumpfförmige Bohrung (18) des Einsatzes (16) über den Abstand (d) ungleich Null hinausragen.
  8. Verteiler nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die kegelstumpfförmige Bohrung (18) auf deren entlang der Mittelachse (X2) dem Austeiler (30) zugewandter Oberfläche (182) mit Rippen zur Führung des Kältemittels versehen ist.
  9. Verteiler nach einem der Ansprüche 2 - 8, dadurch gekennzeichnet, dass es einen Spielraum zwischen einer Kante (382) der Rippen (38) und einer die kegelstumpfförmige Bohrung (18) abgrenzenden Oberfläche (182) im Inneren des Einsatzes (16) gibt.
  10. Verteiler (2) nach einem der Ansprüche 2 - 7, dadurch gekennzeichnet, dass die Rippen (38) um eine Mittelachse (X30) des Austeilers (30) regelmäßig voneinander beabstandet sind.
  11. Verteiler nach Anspruch 1, dadurch gekennzeichnet, dass der Austeiler (30) und die Bohrung (18) keine Rippen aufweisen und gemeinsam einen ringförmigen Durchgangsschlitz (V2) für das Kältemittel abgrenzen.
  12. Verteiler (2) nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass der Abstand (d), in dem die Spitze (34) des Austeilers (30) über die kegelstumpfförmige Bohrung (18) des Einsatzes (16) stromaufwärts hinausgeht, 20 mm übersteigt.
  13. Verfahren zur Herstellung eines Verteilers (2) nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass es umfasst: Herstellen des Auseilers (30) durch 3D-Druck.
  14. Rohrbündel-Verdampfer (1) einer Zweiphasenkältemittel-Heizungsanlage, dadurch gekennzeichnet, dass er umfasst: einen einem internen Verteilungsvolumen (3) des Verdampfers vorgelagerten Verteiler (2) nach einem der Ansprüche 1 - 12, der einem System (6 - 8) zur Verteilung von Zweiphasenkältemittel vorgelagert ist, und dass die Spitze (34) des Austeilers (30) stromaufwärts gerichtet und das Gitter (20) in Richtung des internen Verteilungsvolumens (3) in einer Strömungsrichtung (F1) des Kältemittels stromabwärts gerichtet ist.
  15. Zweiphasenkältemitte-Heizungsanlage, dadurch gekennzeichnet, dass sie einen Verdampfer nach Anspruch 14 umfasst.
EP15178404.8A 2014-07-28 2015-07-27 Einlassverteiler für einen verdampfer, herstellungsverfahren eines solchen verteilers, verdampfer, der einen solchen verteiler umfasst, und thermische anlage mit zweiphasen-wärmeübertragungsmittel Active EP2980509B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR1457266A FR3024218B1 (fr) 2014-07-28 2014-07-28 Distributeur d'admission pour un evaporateur, procede de fabrication d'un tel distributeur, evaporateur comprenant un tel diffuseur et installation thermique a fluide caloporteur diphasique

Publications (2)

Publication Number Publication Date
EP2980509A1 EP2980509A1 (de) 2016-02-03
EP2980509B1 true EP2980509B1 (de) 2020-11-04

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EP (1) EP2980509B1 (de)
FR (1) FR3024218B1 (de)
RU (1) RU2684062C2 (de)

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JP6957857B2 (ja) 2016-10-13 2021-11-02 株式会社Ihi 流体分散装置及び熱処理装置
CN110455017A (zh) * 2019-07-01 2019-11-15 上海昶协实业有限公司 一种组合结构分液头
US11709020B2 (en) 2021-04-21 2023-07-25 Lennox Industries Inc. Efficient suction-line heat exchanger
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RU2015131090A3 (de) 2019-02-04
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RU2684062C2 (ru) 2019-04-03
FR3024218B1 (fr) 2019-05-24
EP2980509A1 (de) 2016-02-03

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