EP2392881A1 - Caloporteur pour un moyen de refroidissement à changement de phase doté d'un conduit de répartition et de collecte horizontal - Google Patents

Caloporteur pour un moyen de refroidissement à changement de phase doté d'un conduit de répartition et de collecte horizontal Download PDF

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Publication number
EP2392881A1
EP2392881A1 EP10164993A EP10164993A EP2392881A1 EP 2392881 A1 EP2392881 A1 EP 2392881A1 EP 10164993 A EP10164993 A EP 10164993A EP 10164993 A EP10164993 A EP 10164993A EP 2392881 A1 EP2392881 A1 EP 2392881A1
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EP
European Patent Office
Prior art keywords
heat exchanger
refrigerant
tube
cross
section
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
EP10164993A
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German (de)
English (en)
Other versions
EP2392881B1 (fr
Inventor
Klaus Koch
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.)
Thermofin GmbH
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Thermofin GmbH
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.)
Filing date
Publication date
Application filed by Thermofin GmbH filed Critical Thermofin GmbH
Priority to EP10164993A priority Critical patent/EP2392881B1/fr
Priority to BR112012030597-2A priority patent/BR112012030597B1/pt
Priority to PCT/EP2011/058421 priority patent/WO2011151218A1/fr
Publication of EP2392881A1 publication Critical patent/EP2392881A1/fr
Priority to US13/687,191 priority patent/US9945593B2/en
Priority to CL2012003394A priority patent/CL2012003394A1/es
Application granted granted Critical
Publication of EP2392881B1 publication Critical patent/EP2392881B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/02—Auxiliary systems, arrangements, or devices for feeding steam or vapour to condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/08—Auxiliary systems, arrangements, or devices for collecting and removing condensate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/02—Centrifugal separation of gas, liquid or oil
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/03—Suction accumulators with deflectors
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F28D1/047—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 bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—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 bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • 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
    • F28D1/05316—Assemblies of conduits connected to common headers, e.g. core type radiators
    • F28D1/05341—Assemblies of conduits connected to common headers, e.g. core type radiators with multiple rows of conduits or with multi-channel conduits combined with a particular flow pattern, e.g. multi-row multi-stage radiators

Definitions

  • the invention relates to a multi-flow heat exchanger for a refrigerant circuit.
  • Generic heat exchangers are used for example as a condenser or evaporator in refrigeration or heat pump circuits with phase-changing refrigerant.
  • Mehrflutige heat exchangers consist essentially of a manifold which distributes the refrigerant to a plurality of heat exchanger tubes, a plurality of heat exchanger tubes in which the refrigerant is indirectly brought into contact with the medium to be cooled or heated and a collector in which the refrigerant after heat transfer from the different, mostly parallel heat exchanger tubes is brought together before the refrigerant then leaves the heat exchanger.
  • multi-flow heat exchangers are usually formed in a vertical position of the manifolds and collectors with horizontally disposed heat transfer tubes, often the manifolds and manifolds are formed segmented, so realized in a vertical component areas for collecting and distributing refrigerant.
  • a heat exchanger in a horizontal arrangement or position goes from the DE 101 11 384 B4 out. Due to the structural dimensions This heat exchanger is suitable for larger refrigeration or heat pump systems with installation on flat roofs or outdoors.
  • a disadvantage of the aforementioned designs is that an effective oil separation and an effective refrigerant collector function must be taken over by additional components, which makes the use of horizontal heat exchangers more difficult and more expensive.
  • the task is derived to provide a heat exchanger available at the lowest possible space and low height, the refrigerant gas or liquid distribution and oil separation before heat transfer in the heat exchanger tubes and the Kältesch remplikeits- or gas collection after heat transfer in the heat exchanger tubes with the possibility allows the phase separation of liquid and gaseous refrigerant phase.
  • the object is achieved by a heat exchanger for phase-changing refrigerant with horizontal distributor tube and horizontal collector tube and intermediate refrigerant heat transfer tubes, wherein for the condenser operation of the multi-flow heat exchanger of the refrigerant gas inlet into the heat exchanger tubes in the upper region of the cross section of the manifold and the refrigerant liquid exit from the heat exchanger tubes in the upper Area of the cross section of the collector tube are arranged such that in the lower region of the cross section of the manifold Oil separation and in the lower part of the cross section of the header pipe, the refrigerant liquid separation takes place.
  • the separation of the liquid from the gaseous phase in both the header and the distributor tube is realized by the arrangement of the means for taking out the phases in the respective regions of the horizontal header and distributor tubes.
  • the collection or distribution of the gaseous phase takes place in each case in the upper region and the collection and distribution of the liquid phase in each case in the lower region of the collector or distributor tube cross-section.
  • a horizontally arranged refrigerant gas and oil inlet nozzle are provided on the manifold and in the lower region of the cross section of the manifold a vertically arranged oil collection pipe with oil return.
  • the refrigerant gas-oil mixture entering the distributor pipe is separated, whereby the gaseous phase accumulates in the horizontal distributor pipe in the upper region and the liquid oil phase in the lower region.
  • the liquid oil phase is then withdrawn in the lower area via the oil collection pipe and the oil return, whereas in the upper area of the refrigerant vapor enters the heat exchanger tubes.
  • the gas inlet arc enters the distributor tube horizontally in the lower part of the cross-section of the distributor tube and finally extends vertically upwards, forming a 90 ° bend.
  • the gas inlet arc ends with the opening for the refrigerant gas inlet.
  • the upper end of the gas inlet arc is bevelled to form a maximum baffle in the flow direction of the refrigerant vapor for the refrigerant oil droplets.
  • a vertically arranged liquid outlet nozzle for the liquid refrigerant phase is provided in the lower region of the cross section of the collector tube.
  • the condensed liquid phase of the refrigerant collects density-driven in the lower region of the cross section of the collector tube and then runs down through the liquid outlet nozzle.
  • the refrigerant liquid outlet is formed from the heat exchanger tube in the upper region of the cross section of the collector tube via a liquid inlet arc.
  • the horizontal heat exchanger tube is connected to the horizontal end of the liquid inlet arc.
  • the liquid inlet arc runs, forming a 90 ° bend vertically downwards, to the collector tube and ends with the opening for the refrigerant liquid inlet in the upper region of the cross section of the collector tube.
  • the invention is preferably realized in that the ratio of the tube diameter of heat exchanger tubes to distributor or collector tube is less than 0.7. This ensures that sufficient volume is made available for phase separation in the manifold and in the collector tube. According to an advantageous embodiment of the invention, a ratio of 0.2 to 0.25 is given as optimal.
  • a connection for measuring devices, sensors or the like is preferably further arranged.
  • the liquid outlet nozzle on the collector tube is preferably connected to a heat exchanger for subcooling the refrigerant liquid.
  • the heat exchanger can be used as a flooded evaporator, wherein the horizontal distribution pipe is used in the case as a collector and the horizontal header pipe as a distributor for the refrigerant.
  • FIG. 1 a heat exchanger 1 is shown in horizontal, horizontal design.
  • a horizontal embodiment of the heat exchanger 1 is to be understood as meaning that the heat exchanger tubes 3 are connected to the horizontal distributor 2 horizontally in one plane in a multiple flow. This results in the flooding of the heat exchanger from the number of the Distributor tube 2 outgoing heat exchanger tubes 3.
  • the heat exchanger tubes 3 pass through the heat exchanger 1 in different levels down and are introduced into the collector tube 4 in the lowest level.
  • the distributor tube 2 has two gas and oil inlet connection pieces 5, via which the refrigerant vapor / oil mixture flows into the distributor tube 2 via the gas and oil inlet connection pieces 5.
  • the gas and oil droplet mixture is distributed horizontally, wherein a separation takes place within the cross section of the distributor tube 2 such that the refrigerant vapor in the upper region of the cross section and the liquid and deposited on the walls of oil settle in the lower region of the cross section.
  • the separated refrigerant oil passes via the vertically downwards from the manifold 2 outgoing oil collection pipe 7 in an oil return 8, which feeds the oil to the refrigerant circuit at a suitable location in front of the compressor, not shown again.
  • the collector tube 4 forms the lowest point of the heat exchanger 1 for the accumulation of refrigerant liquid and the heat exchanger tubes 3 run in the upper region of the cross section of the collector tube 4, preferably at the highest point for the accumulation of refrigerant vapor and foreign gases.
  • the condensed in the function as a condenser in the heat exchanger 1 refrigerant vapor passes as a liquid refrigerant thus in the upper region of the collector tube 4 and there is a separation possibly still existing refrigerant vapor and the refrigerant liquid over the cross section of the space of the collector tube 4 of the shape that condensed liquid refrigerant phase accumulates in the lower region and the gaseous phase of the refrigerant remains in the upper region of the collector tube 4 and there is the possibility of backward degassing in each of the collector tube 4 outgoing heat exchanger tube 3.
  • the subcooling of the refrigerant remains in the heat exchanger, which has a positive effect on the efficiency of the process.
  • this also leads to a lower volume for the components.
  • the gas passage is effectively suppressed with pressure change due to load change, which in turn leads to an increase in the efficiency of the refrigerant circuit.
  • FIG. 2 the structural configurations are shown in detail.
  • the gas inlet 9 has its tapered opening for the refrigerant gas inlet in the upper region of the cross section of the manifold 2, extending vertically downwards in the arc to the side in the lower region of the manifold 2 and the distribution pipe 2 finally penetrates in the horizontal direction.
  • the horizontal heat exchanger tubes 3 are connected to the horizontal ends of the gas inlet bends 9. The refrigerant gas passes via the gas inlet in the upper region of the cross section of the distributor tube 2 into the gas inlet bend 9 and through it into the heat exchanger tubes 3.
  • the multiple deflection of the flow direction of the refrigerant gas ensures a separation of the entrained refrigerant oil droplets, which are deposited on the walls of the manifold 2 and the gas inlet bends 9 and the contours of the manifold 2 following flow down and collect in the lower part of the manifold 2.
  • the refrigerant oil is discharged via the oil collector tube 7 from the manifold 2 and passes through an oil return 8 at a suitable point back into the refrigerant circuit.
  • the refrigerant gas which finally passes from the distributor tube 2 via the gas inlet bends 9 into the heat exchanger tubes 3, is now indirectly brought into thermal contact with the cooling air flow and liquefied on the way through the heat exchanger 1 down.
  • the exit of the liquefied refrigerant from the heat exchanger tube 3 takes place according to FIG. 2 via a liquid inlet bend 10, which opens into the upper region of the collector tube 4.
  • the end of the liquid inlet arc 10 is directly connected to the upper vertex of the collector tube 4 and soldered or welded in this, for example.
  • the refrigerant liquid thus flows in the upper region in the circular cross-section space of the collector tube 4, wherein vaporous components of the refrigerant are separated from the mass flow and accumulate in the upper region of the collector tube 4.
  • the refrigerant vapor in the header pipe 4 is thus able to be driven by the low density to flow back into the heat exchanger tubes 3 and then to condense further.
  • the collector tube 4 has a connection as a liquid outlet nozzle 6, through which the condensate leaves the heat exchanger 1.
  • a subcooler in which the condensed refrigerant is additionally subcooled to improve the efficiency of the cooling process.
  • the refrigerant vapor and oil separation in the manifold 2 by the additional surfaces of the outer shell of the gas inlet arc 9 is particularly efficient and thus only very little refrigerant oil in the heat exchanger tubes 3, since the oil in a high degree in Distributed pipe 2 and discharged via the oil collector tube 7 and the oil return 8.
  • the heat exchanger 1 can fulfill the function of the refrigerant collector, in particular by the volume of the collector tube 4 in a refrigerant circuit and it can be completely saved within the refrigerant circuit, the additional component of the collector.
  • a particular advantage of the invention is that the refrigerant charge can be reduced by 40% to 50% by this design.
  • FIG. 3 the front view of a heat exchanger 1 is shown.
  • the manifold 2 and the two gas and ⁇ leinhoffsstutzen 5 form the upper horizontal position of the heat exchanger 1.
  • the oil collector tube 7 and the oil return 8 are arranged approximately centrally and derive the separated refrigerant oil.
  • Below the manifold 2 the levels of Heat exchanger tubes 3 visible, which are interconnected by means of sheets.
  • the lowest level of the heat exchanger tubes 3 emerges horizontally from the image plane and is discharged via the gas inlet bends 9 vertically downwards.
  • the gas inlet bends 9 open into the uppermost point of the collector tube 4, so that the condensed refrigerant runs down into the collector and leaves the heat exchanger 1 through the liquid outlet nozzle 6.
  • the compact design of the heat exchanger 1 is very clearly visible and in particular it is shown that no additional space and in particular no additional height is required by the functional integration of oil collector and refrigerant collector in the heat exchanger.
  • the heat exchanger 1 can also be used as a flooded evaporator, for example in a heat pump cycle.
  • the distributor tube 2 forms the collector for the refrigerant gas from the evaporator
  • the collector tube 4 is the distributor for the refrigerant liquid in the heat exchanger 1, which is connected as a flooded evaporator.
  • Another advantage of the realization of the invention is that an efficient backward degassing in each heat exchanger tube 3 is possible. As a result, complex measures to ensure the degassing within a refrigerant circuit are not required, which leads to further cost reductions.
  • the conceptional principle of the invention is applicable to a variety of heat exchanger tasks, a particularly important application for the invention is the formation of the heat exchanger 1 as an air-cooled condenser.
  • Preferred applications of the heat exchanger 1 in refrigeration circuits are in the field of stationary refrigeration, especially in the supermarket cooling.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
EP10164993A 2010-06-04 2010-06-04 Caloporteur pour un moyen de refroidissement à changement de phase doté d'un conduit de répartition et de collecte horizontal Active EP2392881B1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP10164993A EP2392881B1 (fr) 2010-06-04 2010-06-04 Caloporteur pour un moyen de refroidissement à changement de phase doté d'un conduit de répartition et de collecte horizontal
BR112012030597-2A BR112012030597B1 (pt) 2010-06-04 2011-05-24 trocador de calor
PCT/EP2011/058421 WO2011151218A1 (fr) 2010-06-04 2011-05-24 Échangeur de chaleur pour agent réfrigérant à changement de phase, présentant un tube distributeur et collecteur horizontal
US13/687,191 US9945593B2 (en) 2010-06-04 2012-11-28 Heat exchanger for phase-changing refrigerant, with horizontal distributing and collecting tube
CL2012003394A CL2012003394A1 (es) 2010-06-04 2012-12-03 Intercambiador de calor para refrigerante de cambio de fase, posee un tubo distribuidor horizontal, un tubo colector horizontal y tubos intercambiadores de calor con una entrada de gas refrigerante dispuesta en la region superior de la sección transversal del tubo distribuidor, y la salida del liquido refrigerante esta dispuesta en la region superior de la seccion transversal del tubo colector.

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP10164993A EP2392881B1 (fr) 2010-06-04 2010-06-04 Caloporteur pour un moyen de refroidissement à changement de phase doté d'un conduit de répartition et de collecte horizontal

Publications (2)

Publication Number Publication Date
EP2392881A1 true EP2392881A1 (fr) 2011-12-07
EP2392881B1 EP2392881B1 (fr) 2013-01-02

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EP10164993A Active EP2392881B1 (fr) 2010-06-04 2010-06-04 Caloporteur pour un moyen de refroidissement à changement de phase doté d'un conduit de répartition et de collecte horizontal

Country Status (5)

Country Link
US (1) US9945593B2 (fr)
EP (1) EP2392881B1 (fr)
BR (1) BR112012030597B1 (fr)
CL (1) CL2012003394A1 (fr)
WO (1) WO2011151218A1 (fr)

Families Citing this family (4)

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Publication number Priority date Publication date Assignee Title
US10712062B2 (en) * 2015-10-26 2020-07-14 Mitsubishi Electric Corporation Refrigerant distributor and air-conditioning apparatus using the same
WO2017168669A1 (fr) * 2016-03-31 2017-10-05 三菱電機株式会社 Échangeur de chaleur et appareil à cycle de réfrigération
EP3446049B1 (fr) * 2016-04-18 2023-03-15 Johnson Controls Tyco IP Holdings LLP Système condenseur évaporateur destiné aux systèmes frigorifiques
US10274221B1 (en) * 2017-12-22 2019-04-30 Mitek Holdings, Inc. Heat exchanger

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BR112012030597A2 (pt) 2017-06-20
WO2011151218A1 (fr) 2011-12-08
CL2012003394A1 (es) 2013-07-05
US9945593B2 (en) 2018-04-17
EP2392881B1 (fr) 2013-01-02
BR112012030597B1 (pt) 2020-07-28
US20130327503A1 (en) 2013-12-12

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