EP2980509A1 - 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
EP2980509A1
EP2980509A1 EP15178404.8A EP15178404A EP2980509A1 EP 2980509 A1 EP2980509 A1 EP 2980509A1 EP 15178404 A EP15178404 A EP 15178404A EP 2980509 A1 EP2980509 A1 EP 2980509A1
Authority
EP
European Patent Office
Prior art keywords
distributor
dispenser
evaporator
ribs
upstream
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.)
Granted
Application number
EP15178404.8A
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English (en)
French (fr)
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EP2980509B1 (de
Inventor
Fabien Couturier
Slimane Meziani
Eddy LHENORET
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.)
Compagnie Industrielle dApplications Thermiques SA CIAT
Original Assignee
Compagnie Industrielle dApplications Thermiques SA CIAT
Priority date (The priority date 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 date listed.)
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Publication of EP2980509A1 publication Critical patent/EP2980509A1/de
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Publication of EP2980509B1 publication Critical patent/EP2980509B1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • 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 two-phase refrigerant thermal installation which comprises such an evaporator.
  • a heat pump comprising an evaporator, a compressor, a condenser and a pressure reducer.
  • the evaporator allows to take the heat of a zone, called cold source, by means of a refrigerant.
  • the fluid consists of two phases, a vapor phase and a liquid phase, 80% of the fluid is generally still in the liquid phase.
  • a heat source transmits heat energy to the fluid. This one having a weak pressure, it evaporates.
  • the entire fluid is in gaseous form and is sucked by the compressor.
  • An evaporator comprises a bundle of tubes, in which the refrigerant circulates, allowing it 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 homogeneity of the fluid contained in each channel.
  • the fluid passing through the evaporator must be heated in the same way in each of the channels of the evaporator, so that the temperature is the same at the exit of each channel of the beam.
  • a temperature in one of the channels, lower than the temperature in the other channels decreases the temperature of the fluid leaving the evaporator and therefore the overall efficiency of the heat pump.
  • an evaporator comprises, at the inlet of the refrigerant in its internal volume, a distributor whose role is to distribute the fluid homogeneously.
  • a diphasic refrigerant dispenser comprising a cup-shaped grid, on which is welded a metal cone forming a tundish.
  • This distributor is installed at the inlet of an evaporator, at the end of an intake pipe.
  • the cone creates an obstacle to the passage of fluid that accelerates the fluid and distributes it on the edges of the grid.
  • the fluid passes through orifices of the grid and is projected radially outwardly relative to the center of the cup.
  • This distributor makes it possible to start acceptably the fluid in the channels of the evaporator.
  • the distribution of fluid in the pipes is not optimal and there are differences in temperature between the channels.
  • JP-A-2000 111 205 teaches to provide a core with a tapered tip for a dispenser for use with a "direct expansion battery” type evaporator.
  • This type of dispenser is not directly adapted for use with a multitubular type evaporator.
  • a cover In known equipment, a cover must be arranged downstream of the core, to allow the connection of the capillary tubes of the direct expansion exchange battery, which is not transferable to a distributor for a multitubular exchanger.
  • US-A-5,059,226 discloses a centrifugal distributor which comprises a conical central hub disposed in a cylindrical portion of circular section of a body which has, moreover, a frustoconical portion, the smallest section is oriented downstream.
  • the top of the conical central hub is disposed at the junction between the cylindrical and frustoconical portions of the dispenser body and does not protrude therefrom. The flow of heat transfer fluid around the conical central hub is not optimized.
  • the invention intends to remedy more particularly by proposing a new intake manifold for better mixing the two phases of the fluid and to obtain a distribution in the channels of the more homogeneous evaporator.
  • the invention relates to an inlet distributor for a multitubular evaporator of a two-phase refrigerant thermal installation, this distributor comprising a diffusion grid and a generally conical shaped distributor, having a top and a base fixed to the diffusion grid respectively directed to an upstream side and a downstream side of the distributor.
  • This distributor also comprises a member pierced with a frustoconical bore centered on the axis of the distributor and which surrounds this distributor, while the smallest area section of the frustoconical bore of the insert is directed to the upstream side of the distributor.
  • the top of the distributor exceeds the frustoconical bore of the insert upstream, over a non-zero distance.
  • a confined passage volume of 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 case of relatively low flow of refrigerant inside the dispenser. Thanks to the fact that the top of the distributor extends upstream relative to the frustoconical bore of the insert, the flow of refrigerant can be established around the distributor before this flow is propagated inside the tapered bore. This facilitates the distribution of the fluid around the distributor, especially in the case where it is provided with guide ribs of the refrigerant.
  • This arrangement thus makes it possible to channel the two-phase mixture from the cylindrical feed 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 dependent partial. This thus contributes to balancing the mass flow rates flowing in each channel formed between two helical ribs when the splitter is formed of such ribs.
  • the jet passing through the grid located at the base of the cone has a radial symmetry adapted to best irrigate the tube bundle.
  • the invention also relates to a method of manufacturing a dispenser as mentioned above.
  • the splitter is manufactured by three-dimensional printing.
  • the invention relates to a multitubular evaporator of a two-phase refrigerant thermal installation 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 gate downstream towards 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 according to the invention.
  • This distributor 2 is attached to the end of an intake pipe 4, at the inlet of the evaporator 1.
  • a two-phase refrigerant whose flow is represented by the arrow F1 to the figure 1 , flows from the intake pipe 4 to an internal volume 3 of the evaporator 1 passing through the distributor 2.
  • X4 is noted 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 otherwise than by the part of the evaporator visible to the figure 1 , also includes a compressor, a condenser and a pressure reducer.
  • 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 tubular plate.
  • the set of tubes forms the tubular bundle inside which evaporates the refrigerant at low pressure.
  • the tubular bundle is enclosed in a metal shell 8 usually called a shell in which circulates a coolant in the liquid phase, such as water or glycol water ..., which gives way, by heat exchange through the wall of the tubes 6 its heat to the refrigerant.
  • the flow of this coolant is represented by the arrow F2 at the figure 1 from a sleeve 9 entering the shell.
  • the evaporator can be of the known type of FR-A-2 997 174 .
  • the evaporator 1 comprises, in the end wall 13, a port 14 for entering the two-phase refrigerant into the volume 3.
  • the pipe 4 makes it possible to direct the two-phase refrigerant towards the distributor 2, which is fixed in the orifice 14. More specifically, an insert 16, which belongs to the distributor 2, is mounted in the orifice 14.
  • the pipe 4 is connected to an outer or upstream face 162 of the insert 16 which is oriented upstream of the flow of refrigerant when the insert 16 is in place in the bore 14 and when the evaporator 1 is in use.
  • the two-phase refrigerant flows along and inside the intake pipe 4 and then within the distributor 2 before being distributed to the various channels 8 within the volume 3 as represented by the arrows F1 '.
  • the direction from which the refrigerant originates and downstream of its direction of destination is called upstream.
  • 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 specifically, the gate 20 has a truncated sphere shape, centered on an axis X20 with its concavity facing the splitter 30, that is to say down on the figure 4 .
  • the grid 20 comprises, in its center, a circular opening 22, defining an inner peripheral edge 24 of the grid 20.
  • a surface 25 of the grid is pierced with orifices 26, regularly spaced apart.
  • the grid 20 comprises an outer peripheral edge 28, for attaching it to the insert 16 or the periphery of the orifice 14 of the evaporator 1, the downstream side thereof.
  • the edge 28 is plant 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.
  • edge 28 is circular. It can however have a different shape, for example lobed.
  • the grid is formed by a metal layer of a few millimeters thick and may in particular be made of steel and obtained by stamping.
  • the distributor 30 of generally conical shape is fixed on the inner 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 gate 20.
  • the edge 36 of the base is fixed to the inner edge 24 of the gate 20 and the axes X20 and X30 coincide, in an axis X2, in an assembled configuration of the distributor 2.
  • the axis X2 passes through the center 33 of the base 32 and the top 34.
  • X16 is a central axis of the insert 16. This insert is pierced with a cylindrical bore 17 and a frustoconical bore 18 both centered on the axis X16.
  • the bore 17 extends from the upstream face 162, to the bore 18, which extends from the bore 17 to a downstream face 164 of the insert 16, opposite to the upstream face 162.
  • the bore 18 is divergent in the downstream upstream direction of the insert 16, that is to say going from the face 162 to the 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 directed 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.
  • ⁇ is the half-angle at the top of the frustoconical surface 182 which defines 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 the section S18 and in the direction of the face 162 of the 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 about 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 gate 20, in particular at partial load, when the flow rate of refrigerant, and therefore the speed in the tubing 4, are reduced. This also makes it possible to promote the distribution of the flow around the distributor when the mass weight of steam is reduced, especially in the case of operation at low condensing temperature of the refrigeration unit and / or use of an economizer. This also allows the refrigerant to have a larger homogeneous density, which means that for an identical mass flow rate, the volume flow rate and hence the velocity 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, overall like a propeller plated on a cone.
  • H38 is the height of each rib 38, 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 the surface 37.
  • the height H38 of a rib 38 is the distance between its edge 382 and a connecting line 384, measured perpendicular to the surface 37.
  • the height H38 increases along the axis X2 from the vertex 34 to the base 32. In other words, the height H38 of the ribs is greater at the the base 32 of the distributor 30 only at its top 34.
  • the distributor 30 is provided with six ribs 38, regularly spaced about the axis X2. In variants of the invention, the number of ribs may be higher or lower. Preferably but not exclusively, the splitter 30 may include three, four, five, six or eight ribs 38, regularly spaced.
  • the ribs 38 are not evenly spaced, in order to generate an irregular movement of the two-phase fluid, allowing it to be further agitated when the orifice 14 passes.
  • An imaginary cone passing through the portion of the edge 382 of all the ribs 38 which is furthest from the axis X30 is considered.
  • This imaginary cone is the conical envelope of the splitter 30.
  • ⁇ the half-angle at the top of this imaginary cone.
  • the angles ⁇ and ⁇ are chosen equal, so that, when the distributor 30 is introduced into the bores 18 and 17, in the direction of the arrow F4 to the figure 3 , the edges 382 of the ribs 38 extend in the immediate vicinity or in contact with the surface 182.
  • a clearance must effectively exist between the edges 382 and the surface 182 so that the assembly can be assembled without the bore 18 crushing the top of the edges. However, care must be taken that the clearance is minimum, ie less than 1 mm, so that the cells have a sufficient seal between them to avoid the mixing of the sub-flows.
  • the surfaces 182 and 37 define between them a volume V2 for the passage of refrigerant which extends around the axes X2, X4, X16, X20 and X30 together.
  • this volume V2 has a cross section, perpendicular to the aforementioned axes, whose area is relatively small, it is permanently filled with refrigerant from the pipe 4, even if the evaporator 1 operates at partial load. This has the consequence that the refrigerant is distributed homogeneously around the distributor 30, without tending to separate into a gaseous portion located above the axis X2 and a liquid portion located below this axis.
  • the ribs 38 are intended to guide the fluid entering the evaporator 1. Indeed, the curvature of the ribs 38 around the axis X2 makes it possible to give the fluid a rotational movement about the axes X2 and X4 coinciding at the exit of the distributor, as represented by the arrows F3 at the figure 7 . This rotational movement agitates 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 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 exceed from the bore 18 upstream, over the distance d.
  • the insert 16 reduces the volume of passage of the fluid around the distributor 30 and forces the passage thereof 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 opening section is adapted to the diameter of the bore 17, that is to say the smallest diameter of the frustoconical bore 18 of the insert 16.
  • the refrigerant is fed into the evaporator 1 through the intake pipe 4, in which all the components of the fluid have substantially the same speed.
  • the fluid flows parallel to the axis X4 and is called fluid flow front a surface perpendicular to the arrow F1 and corresponding to the fluid passage section.
  • the refrigerant comes into contact with the top 34 distributor 30 and the fluid passage section decreases inside the pipe 4, until the front flow of the fluid 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 represent the arrows F1 '.
  • the distributor 30 may be made of metal, in particular 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 mode of manufacture gives a great freedom to the designer. It makes it possible to produce a distributor 30 according to various geometries. Thus, it is possible to make a large number of variants 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 inexpensively and quickly, which would be difficult to achieve by a conventional machining method.
  • the grid 20 is preferably monobloc with the distributor 30 and obtained by the same manufacturing technique. This ensures a geometric and mechanical continuity between these parts, without having to proceed to a bonding or welding.
  • the gate 20 has no circular opening 22 and the distributor 30 is fixed on an inner central surface of the gate 20.
  • the grid 20 may have a shape different from that described above.
  • the holes 26 may be formed as grooves or have large dimensions, so that the grid has four large holes and the inner edge 24 of the grid is held in position by four metal tabs connected to the edge 28 which allows to fix the grid on the evaporator 1.
  • the distributor 2 may comprise 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 represented on the Figures 1 to 8 and in which the ribs provided on the insert 16 also contribute to the guidance of the refrigerant in the circular space defined between the outer surface of the distributor 30 and the surface 182.
  • the guide ribs of 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 surfaces 37 and 182 opposite when the distributor 30 is in place in the insert 16, as shown in FIG. figure 9 , this annular slot being identified as a volume V2 characteristic of the distributor 2.
  • the half-angle at the apex ⁇ of the surface 182 is equal to the half-angle at the apex ⁇ of the surface 37, so that the The thickness of the annular slot V 2 is constant along the axis X2. This is not mandatory and, by playing on the relative value of the angles ⁇ and ⁇ , it is possible that this annular slot is itself divergent or convergent from the upstream to the downstream of the distributor 2, that is, from face 162 to face 164.
  • the smallest section S18 of the bore 18 is directed upstream with respect to this bore, that is to say 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 non-zero, in particular greater than 20 mm. explained above.
  • the invention is represented 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 defining 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)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
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 true EP2980509A1 (de) 2016-02-03
EP2980509B1 EP2980509B1 (de) 2020-11-04

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EP15178404.8A Active EP2980509B1 (de) 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

Country Status (3)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2025514921A (ja) * 2022-05-25 2025-05-13 浙江盾安人工環境股▲ふん▼有限公司 インペラ及びディスペンサ

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5059226A (en) 1989-10-27 1991-10-22 Sundstrand Corporation Centrifugal two-phase flow distributor
FR2766914A1 (fr) 1997-07-29 1999-02-05 D Applic Thermiques Comp Ind Distributeur destine a equiper les echangeurs thermiques intratubulaires des installations de refroidissement a fluide frigorigene de type diphasique
JP2000111205A (ja) 1998-10-07 2000-04-18 Hitachi Ltd 分配器及び空気調和機
FR2806156A1 (fr) 2000-03-07 2001-09-14 Ciat Sa Echangeur de chaleur a plaques
EP1914494A2 (de) * 2006-07-27 2008-04-23 GI.DI. Meccanica S.p.A. Vorrichtung zur Verteilung von Fluiden, v.a. Gas
EP2264384A1 (de) * 2009-06-02 2010-12-22 Johnson Controls Technology Company Kühlmittelverteilvorrichtung für Kühlsystem
JP2011231972A (ja) * 2010-04-27 2011-11-17 Mitsubishi Electric Corp 冷媒分配器、蒸発器及び冷媒噴射方法
FR2997174A1 (fr) 2012-10-18 2014-04-25 Ciat Sa Evaporateur a tubes et procede de fabrication d'un tel evaporateur

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU1275199A1 (ru) * 1985-07-22 1986-12-07 Специальное Конструкторско-Технологическое Бюро Компрессорного И Холодильного Машиностроения Распределитель хладагента
RU2377462C1 (ru) * 2008-06-20 2009-12-27 Открытое акционерное общество "Сибирский химический комбинат" Испаритель криогенной жидкости

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5059226A (en) 1989-10-27 1991-10-22 Sundstrand Corporation Centrifugal two-phase flow distributor
FR2766914A1 (fr) 1997-07-29 1999-02-05 D Applic Thermiques Comp Ind Distributeur destine a equiper les echangeurs thermiques intratubulaires des installations de refroidissement a fluide frigorigene de type diphasique
JP2000111205A (ja) 1998-10-07 2000-04-18 Hitachi Ltd 分配器及び空気調和機
FR2806156A1 (fr) 2000-03-07 2001-09-14 Ciat Sa Echangeur de chaleur a plaques
EP1914494A2 (de) * 2006-07-27 2008-04-23 GI.DI. Meccanica S.p.A. Vorrichtung zur Verteilung von Fluiden, v.a. Gas
EP2264384A1 (de) * 2009-06-02 2010-12-22 Johnson Controls Technology Company Kühlmittelverteilvorrichtung für Kühlsystem
JP2011231972A (ja) * 2010-04-27 2011-11-17 Mitsubishi Electric Corp 冷媒分配器、蒸発器及び冷媒噴射方法
FR2997174A1 (fr) 2012-10-18 2014-04-25 Ciat Sa Evaporateur a tubes et procede de fabrication d'un tel evaporateur

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2025514921A (ja) * 2022-05-25 2025-05-13 浙江盾安人工環境股▲ふん▼有限公司 インペラ及びディスペンサ

Also Published As

Publication number Publication date
RU2015131090A3 (de) 2019-02-04
RU2684062C2 (ru) 2019-04-03
RU2015131090A (ru) 2017-02-02
FR3024218A1 (fr) 2016-01-29
EP2980509B1 (de) 2020-11-04
FR3024218B1 (fr) 2019-05-24

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