WO2013161038A1 - Échangeur de chaleur et procédé d'échange de chaleur - Google Patents

Échangeur de chaleur et procédé d'échange de chaleur Download PDF

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Publication number
WO2013161038A1
WO2013161038A1 PCT/JP2012/061232 JP2012061232W WO2013161038A1 WO 2013161038 A1 WO2013161038 A1 WO 2013161038A1 JP 2012061232 W JP2012061232 W JP 2012061232W WO 2013161038 A1 WO2013161038 A1 WO 2013161038A1
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WO
WIPO (PCT)
Prior art keywords
heat exchange
pipe
lower header
pipes
refrigerant
Prior art date
Application number
PCT/JP2012/061232
Other languages
English (en)
Japanese (ja)
Inventor
岡崎　多佳志
石橋　晃
相武 李
拓也 松田
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to US14/391,466 priority Critical patent/US20150083383A1/en
Priority to JP2014512239A priority patent/JP6104893B2/ja
Priority to CN201280073357.1A priority patent/CN104335000B/zh
Priority to PCT/JP2012/061232 priority patent/WO2013161038A1/fr
Priority to ES12875231T priority patent/ES2702291T3/es
Priority to EP12875231.8A priority patent/EP2863161B1/fr
Priority to CN2013202178156U priority patent/CN203323459U/zh
Publication of WO2013161038A1 publication Critical patent/WO2013161038A1/fr

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Classifications

    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/14—Heat exchangers specially adapted for separate outdoor units
    • F24F1/16—Arrangement or mounting thereof
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0417—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with particular circuits for the same heat exchange medium, e.g. with the heat exchange medium flowing through sections having different heat exchange capacities or for heating/cooling the heat exchange medium at different temperatures
    • 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
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • 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
    • 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
    • F25B2400/12—Inflammable refrigerants
    • F25B2400/121—Inflammable refrigerants using R1234
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • 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

Definitions

  • the present invention relates to a heat exchanger and a heat exchange method.
  • This heat exchanger includes a pair of header pipes and a plurality of flat tubes provided between the header pipes. After the fluid flowing into one header flows through the plurality of flat tubes, , Was configured to flow out to the other header pipe.
  • each header pipe is bent along the plurality of surfaces.
  • bending the header pipe into, for example, an L-shape or a U-shape has a problem that an excessive load is applied, the device is increased in size, and the cost is increased.
  • Patent Document 1 there is one disclosed in Patent Document 1, for example.
  • a pair of header pipes are prepared separately for each of a plurality of surfaces.
  • the present invention has been made in view of the above, and while having a plurality of heat exchange function surfaces, it is possible to suppress the influence of gravity on the refrigerant and to suppress a decrease in heat exchange performance on each surface. It aims at providing the heat exchanger etc. which can do.
  • the heat exchanger of the present invention that achieves the above-described object has a plurality of heat exchange function surfaces, and each of the heat exchange function surfaces includes an upper header pipe, a lower header pipe, and a pair of upper and lower header pipes.
  • the plurality of heat exchange function surfaces are in a parallel connection relationship, and the plurality of lower header pipes are connected to the lower collecting pipe via a flow dividing adjustment section.
  • the heat exchanging method of the present invention that achieves the same object is a heat exchanging method for exchanging heat on a plurality of surfaces, and in each of a plurality of heat exchanging function surfaces, an upper header pipe and a lower header pipe, Preparing a plurality of heat exchange pipes provided between a pair of header pipes, connecting the plurality of heat exchange function surfaces in parallel, and the plurality of lower header pipes are connected to a lower assembly via a flow dividing adjustment unit
  • the refrigerant in the lower collecting pipe is diverted in parallel with the plurality of heat exchange function surfaces in the diversion adjusting unit, and heat exchange is performed on each of the plurality of heat exchange function surfaces, Outflow from the upper header pipe and join the upper collecting pipe.
  • the present invention while having a plurality of heat exchange function surfaces, it is possible to suppress the influence of gravity on the refrigerant and to suppress a decrease in heat exchange performance on each surface.
  • FIG. 1 It is a figure which shows the structure of the heat exchanger which concerns on Embodiment 1 of this invention. It is a perspective view of the lower header pipe for demonstrating a porous pipe. It is a figure which shows the liquid distribution characteristic of the lower header pipe as a comparative example. It is a figure which shows the liquid distribution characteristic of the lower pipe
  • FIG. 1 is a diagram illustrating a configuration of a heat exchanger according to the first embodiment.
  • the heat exchanger according to the present embodiment functions as an outdoor unit of an air conditioner that is installed in a target space and performs air conditioning. Therefore, when operating as a condenser during cooling, the refrigerant flows from top to bottom as shown by the dotted arrows in FIG. 1, and when operating as an evaporator during heating, the refrigerant is as shown in FIG.
  • the parallel flow type heat exchanger flows from bottom to top as indicated by solid arrows in FIG.
  • the heat exchanger 1 has a plurality of heat exchange function surfaces 3.
  • FIG. 1 shows an example in which there are three heat exchange function surfaces 3. Moreover, in the example of FIG. 1, it is comprised so that the adjacent heat exchange functional surface 3 may face the direction orthogonal.
  • Each of the heat exchange function surfaces 3 is provided with an upper header pipe 5, a lower header pipe 7, and a plurality of heat exchange pipes 9 provided between the pair of upper and lower header pipes 5, 7.
  • the heat exchange pipe 9 is a flat tube. Fins 11 (specifically corrugated fins) are provided between the heat exchange pipes 9.
  • One end of the upper communication pipe 13 is connected to each of the upper header pipes 5.
  • the other end side of the upper connecting pipe 13 is connected to the upper collecting pipe 15.
  • Each of the lower header pipes 7 is connected to a lower collecting pipe 19 via a flow dividing adjusting unit 17 described later.
  • the plurality of heat exchange function surfaces 3 are arranged in parallel connection between the upper collecting pipe 15 and the lower collecting pipe 19.
  • closing members such as a metal plate, so that the fluid to be heat-exchanged may not bypass.
  • the diversion adjusting unit 17 adjusts the dryness and flow rate of the refrigerant supplied to the plurality of lower header pipes 7.
  • the present embodiment supplies the gas-liquid two-phase refrigerant to the plurality of heat exchange function surfaces 3 at a uniform dryness and flow rate when the refrigerant flows from bottom to top during heating. The configuration will be described.
  • the diversion adjusting unit 17 includes a distributor 21 and at least one (two in the drawing) flow rate adjusting unit 23.
  • One end side of the distributor 21 is connected to the lower collecting pipe 19, and a plurality of connection ports on the other end side are respectively connected to one end of the corresponding lower connecting pipe 25. Further, the other ends of the lower communication pipes 25 are respectively connected to the collecting side entrances 7 a of the corresponding lower header pipes 7.
  • the distributor 21 connected in this way supplies the refrigerant with a uniform dryness to the plurality of lower communication pipes 25.
  • the flow rate adjusting unit 23 is a capillary tube.
  • the flow rate adjusting unit 23 is provided between the distributor 21 and the corresponding lower header pipe 7, that is, in the lower communication pipe 25, but is not necessarily arranged in all the lower communication pipes 25.
  • the collecting side inlet / outlet 7 a of the lower header pipe 7 and the collecting side inlet / outlet 5 a of the upper header pipe 5 are located in mutually opposite directions in the direction in which the header pipe extends.
  • the gathering side entrance 7a of the lower header pipe 7 is provided on one end side of the lower header pipe 7, and the gathering side entrance 5a of the upper header pipe 5 is provided on the other end side of the upper header pipe 5. ing. That is, the refrigerant flow path between the collecting side inlet / outlet 5a and the collecting side inlet / outlet 7a is designed so that the flow path lengths are substantially equal regardless of which heat exchange pipe 9 is passed through.
  • FIG. 2 is a perspective view of the lower header pipe for explaining the perforated pipe.
  • a plurality of heat exchange pipes 9 to be above the lower header pipe 7 and communication holes with the heat exchange pipes 9 are not shown. Yes.
  • the perforated pipe 27 is a block-like or pipe-like member, and is provided in a state of being floated from the inner surface of the lower header pipe 7 around the center of the space in the lower header pipe 7.
  • the porous tube 27 is provided with a number of distribution holes 29. As an example, the distribution hole 29 is disposed substantially below the perforated tube 27.
  • a double pipe structure is obtained by combining the perforated pipe 27 and the lower header pipe 7.
  • the refrigerant flowing through the lower connecting pipe 25 once flows into the porous pipe 27, and then equally from the multiple distribution holes 29 in the depth direction (left and right direction in FIG. 2), It flows out of the perforated pipe 27, is further uniformly distributed in the lower header pipe 7, and is evenly supplied to the plurality of heat exchange pipes 9 from communication holes (not shown) on the upper surface of the lower header pipe 7.
  • FIG. 3 is a diagram showing the liquid distribution characteristics of a lower header pipe as a comparative example which is horizontally arranged and does not have a porous tube inside
  • FIG. 4 is a lower portion of a porous tube built-in type according to the present embodiment which is horizontally arranged. It is a figure which shows the liquid distribution characteristic of a header pipe.
  • the graphs in FIGS. 3 and 4 have a path No. on the horizontal axis. That is, the flow number of the heat exchange pipes arranged in the depth direction of the lower header pipe (the flow paths of the 28 flat tubes inserted perpendicularly to the upper surface of the lower header pipe) is shown. The liquid distribution ratio for each is shown. In addition, experimental results of three cases 1, 2, and 3 in which the refrigerant flow rate Gr [kg / hour] and the inlet dryness X are changed are shown for each of the comparative example and the lower header pipe of the present embodiment.
  • the three cases 1, 2, and 3 are good substantially along the wiring evenly regardless of the refrigerant flow rate and the inlet dryness. It can be seen that excellent liquid distribution characteristics are obtained. This is because the porous tube 27 is inserted into the lower header pipe 7 and the distribution hole 29 is disposed downwardly of the porous tube 27 so that the inner surface of the lower header pipe 7 and the outer surface of the porous tube 27 are surrounded. The action of stirring the liquid film of the refrigerant in the annular region by the bubbles ejected from the bottom of the perforated tube 27 is obtained as desired regardless of the dryness of the inlet and the flow rate. Even distribution is realized.
  • FIG. 5 is a diagram illustrating an appearance and a plan view of a multi-air conditioner outdoor unit for buildings. Multi-air conditioner outdoor units for buildings are larger than those for general households and are used as high-processing devices.
  • the building multi-air conditioner outdoor unit 101 has the heat exchange function surface 3 assigned to each of the three surfaces of the housing 103, and the propeller fan 105 is arranged in the center in plan view. Yes. Then, air is sucked into the housing 103 as indicated by an arrow 107 from each of the three side surfaces of the housing 103, and heat is exchanged by each heat exchange function surface 3, and a fan provided on the upper surface of the housing 103. From the air outlet formed in the guard 109, it discharges as shown by the arrow 111 (top flow type).
  • the heat exchanger 1 that is an outdoor unit operates as an evaporator, and the gas-liquid two-phase refrigerant that has entered the distributor 21 becomes a homogeneous spray flow when passing through an orifice (not shown).
  • the flow rate is adjusted by each flow rate adjusting unit 23 and flows into the lower header pipe 7 of the corresponding heat exchange function surface 3.
  • the refrigerant flowing in from the collecting side inlet / outlet 7 a of the lower header pipe 7 is ejected from the distribution hole 29 of the perforated pipe 27 and is evenly distributed to the heat exchange pipes 9.
  • the refrigerant exchanges heat with air (not shown) when passing through each heat exchange pipe 9, and then flows into the upper header pipe 5 from the collection side entrance / exit 5 a that is opposite to the collection side entrance / exit 7 a of the lower header pipe 7. leak.
  • the refrigerant flowing out from each collecting side entrance / exit 5a passes through the corresponding upper connecting pipe 13 and joins in the upper collecting pipe 15.
  • the heat exchanger 1 operates as a condenser and the refrigerant flow is reversed.
  • the header pipes are oriented horizontally, so that the influence of gravity on the refrigerant flow can be suppressed, and the refrigerant can be evenly distributed to a plurality of heat exchange pipes. it can. Furthermore, while the header pipes are horizontally arranged in such a manner, it is possible to exert a heat exchange function on a plurality of surfaces without being hindered by the fact that it is difficult to form a curved header pipe. . Furthermore, while heat exchange is performed on each of the plurality of surfaces, the refrigerant flow is divided in parallel with respect to the plurality of heat exchange function surfaces.
  • the refrigerant dryness and flow rate are adjusted as desired according to the conditions of each heat exchange function surface via the distributor and the flow rate adjustment unit, and then distributed and supplied to the heat exchange function surface. In all heat exchange functions, extremely good heat exchange performance can be obtained.
  • the refrigerant that has exchanged heat once with a plurality of heat exchange pipes is collected in the heat exchanger as a whole and does not have a flow path that is again divided into the plurality of heat exchange pipes, There is no problem that the refrigerant cannot be evenly supplied to the exchange pipe.
  • the influence of gravity on the refrigerant can be suppressed and the heat on each surface can be suppressed while having a plurality of heat exchange function surfaces. It is possible to suppress a decrease in exchange performance.
  • the refrigerant has almost the same pressure loss regardless of the heat exchange pipe, That is, uniform distribution of the gas-liquid two-phase flow can be realized.
  • fine droplets and bubbles are ejected from the distribution holes to the annular structure of the double structure, which also promotes uniform distribution of the gas-liquid two-phase refrigerant Is done.
  • the number of distribution to the heat exchange pipe is increased and the number of distribution is kept low (in the above example, the number of distribution is limited to one time), so that a very large number of heat exchange functional surfaces are prepared.
  • the refrigerant pressure loss can be kept low for the number of heat exchange pipes. Therefore, in particular, a low-pressure refrigerant (such as a refrigerant having a large refrigerant pressure loss) such as HFO1234yf, HFO1234ze, or R134a can be effectively used.
  • FIG. A second embodiment of the present invention will be described with reference to FIG.
  • the heat load (it mainly depends on the passing wind speed of a heat exchange part) which adjusts a refrigerant
  • coolant flow volume was illustrated, this invention is not limited to this. That is, the present invention includes an aspect in which the refrigerant dryness and / or the refrigerant flow rate are adjusted to be different in a plurality of heat exchange function surfaces.
  • a specific application example is application to a packaged air conditioner outdoor unit.
  • FIG. 6 is a diagram illustrating an appearance and a plane of the packaged air conditioner outdoor unit.
  • the heat exchange function surface 3 is assigned to each of the side surface and the back surface of the housing 203.
  • the propeller fan 205 By rotation of the propeller fan 205, air is sucked into the housing 203 as indicated by an arrow 207 from each of the side surface and the back surface of the housing 203, and heat is exchanged at each heat exchange function surface 3, and the front surface of the housing 203 As shown by the arrow 211, it discharges from the blower outlet provided in.
  • the distribution hole formation mode is not limited to this, and the orientation, number, and shape of the distribution holes are appropriately changed. Is possible.
  • the above-described configuration of the flow dividing adjustment unit is merely an example, and can be modified as appropriate.
  • the height position of multiple outlet side branch paths such as Y-shaped branch pipes and low-pressure loss distributors are made different from each other, the ratio of the liquid phase diversion is changed by the influence of gravity, and the dryness and flow rate are adjusted simultaneously. It is also possible to use the diversion adjusting unit of the aspect.

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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)
  • Combustion & Propulsion (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Other Air-Conditioning Systems (AREA)

Abstract

La présente invention concerne un échangeur de chaleur (1) possédant plusieurs surfaces fonctionnelles d'échange de chaleur, capable de supprimer l'effet de la gravité sur un fluide réfrigérant et supprimant une diminution de la performance d'échange de chaleur au niveau de chaque surface. Selon l'invention, l'échangeur de chaleur comporte les plusieurs surfaces fonctionnelles d'échange de chaleur (3) et, dans chaque surface fonctionnelle d'échange de chaleur, des tuyaux collecteurs supérieurs (5), des tuyaux collecteurs inférieurs (7) et plusieurs tuyaux d'échange de chaleur (9) disposés entre chaque paire de tuyaux collecteurs supérieurs et inférieurs. Les plusieurs surfaces fonctionnelles d'échange de chaleur sont dans une disposition raccordée en parallèle et les plusieurs tuyaux collecteurs inférieurs sont raccordés à une tubulure collectrice inférieure (19) par le biais d'une unité de régulation d'écoulement de dérivation (17).
PCT/JP2012/061232 2012-04-26 2012-04-26 Échangeur de chaleur et procédé d'échange de chaleur WO2013161038A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
US14/391,466 US20150083383A1 (en) 2012-04-26 2012-04-26 Heat exchanger and heat exchange method
JP2014512239A JP6104893B2 (ja) 2012-04-26 2012-04-26 熱交換器、冷凍サイクル装置、空気調和機及び熱交換方法
CN201280073357.1A CN104335000B (zh) 2012-04-26 2012-04-26 换热器及热交换方法
PCT/JP2012/061232 WO2013161038A1 (fr) 2012-04-26 2012-04-26 Échangeur de chaleur et procédé d'échange de chaleur
ES12875231T ES2702291T3 (es) 2012-04-26 2012-04-26 Intercambiador de calor y método de intercambio de calor
EP12875231.8A EP2863161B1 (fr) 2012-04-26 2012-04-26 Échangeur de chaleur et procédé d'échange de chaleur
CN2013202178156U CN203323459U (zh) 2012-04-26 2013-04-26 热交换器

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2012/061232 WO2013161038A1 (fr) 2012-04-26 2012-04-26 Échangeur de chaleur et procédé d'échange de chaleur

Publications (1)

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WO2013161038A1 true WO2013161038A1 (fr) 2013-10-31

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PCT/JP2012/061232 WO2013161038A1 (fr) 2012-04-26 2012-04-26 Échangeur de chaleur et procédé d'échange de chaleur

Country Status (6)

Country Link
US (1) US20150083383A1 (fr)
EP (1) EP2863161B1 (fr)
JP (1) JP6104893B2 (fr)
CN (2) CN104335000B (fr)
ES (1) ES2702291T3 (fr)
WO (1) WO2013161038A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPWO2015162689A1 (ja) * 2014-04-22 2017-04-13 三菱電機株式会社 空気調和装置
JP2017116169A (ja) * 2015-12-24 2017-06-29 株式会社前川製作所 空冷式熱交換ユニット及びクーラユニット
JP2018109455A (ja) * 2016-12-28 2018-07-12 株式会社前川製作所 空冷式熱交換ユニット及びクーラユニット
JPWO2020100897A1 (ja) * 2018-11-12 2021-06-10 三菱電機株式会社 熱交換器及び熱交換器の製造方法

Families Citing this family (8)

* Cited by examiner, † Cited by third party
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FR2951114B1 (fr) * 2009-10-13 2011-11-04 Peugeot Citroen Automobiles Sa Dispositif de refroidissement pour vehicule hybride
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ES2702291T3 (es) 2019-02-28
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