[go: up one dir, main page]

US20150083383A1 - Heat exchanger and heat exchange method - Google Patents

Heat exchanger and heat exchange method Download PDF

Info

Publication number
US20150083383A1
US20150083383A1 US14/391,466 US201214391466A US2015083383A1 US 20150083383 A1 US20150083383 A1 US 20150083383A1 US 201214391466 A US201214391466 A US 201214391466A US 2015083383 A1 US2015083383 A1 US 2015083383A1
Authority
US
United States
Prior art keywords
heat exchange
pipe
refrigerant
pipes
lower header
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.)
Abandoned
Application number
US14/391,466
Other languages
English (en)
Inventor
Takashi Okazaki
Akira Ishibashi
Sangmu Lee
Takuya Matsuda
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.)
Mitsubishi Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Mitsubishi Electric Corp filed Critical Mitsubishi Electric Corp
Assigned to MITSUBISHI ELECTRIC CORPORATION reassignment MITSUBISHI ELECTRIC CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MATSUDA, TAKUYA, ISHIBASHI, AKIRA, LEE, SANGMU, OKAZAKI, TAKASHI
Publication of US20150083383A1 publication Critical patent/US20150083383A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
    • 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
    • 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.
  • a parallel flow type heat exchanger As one type of the heat exchanger, a parallel flow type heat exchanger is given.
  • This heat exchanger includes a pair of header pipes, and a plurality of flat pipes provided between those header pipes. This heat exchanger is configured so that after a fluid, which has flowed into one of the headers, flows through the plurality of flat pipes, the fluid flows out to the other of the header pipes.
  • the parallel flow type heat exchanger may have such a structure that the pair of header pipes is horizontally arranged, to thereby suppress the influence of the gravity mutually between the plurality of flat pipes.
  • an existing outdoor unit of an air conditioner may have such a structure that heat exchange surfaces are arranged in a plurality of surfaces of a housing of the outdoor unit.
  • the above-mentioned parallel flow type heat exchanger having the pair of header pipes horizontally arranged is caused to exert its function in the plurality of surfaces of the housing of the outdoor unit, it is necessary to curve each of the header pipes along the plurality of surfaces.
  • the header pipe is curved into, for example, an L-shape or a U-shape, significant loads are applied, and hence there arise problems in that the apparatus is upsized and cost is increased.
  • Patent Literature 1 a heat exchanger disclosed in Patent Literature 1 is given.
  • a pair of header pipes has been prepared separately for each of a plurality of surfaces.
  • Patent Literature 1 has employed such a mode that after the refrigerant, which has flowed through a plurality of flat pipes in certain one surface (first surface), is collected to the header pipe on the outflow side of the one surface (first surface), the refrigerant is guided from this header pipe to the header pipe on the inflow side of the next surface (second surface) and distributed through a plurality of flat pipes of the next surface (second surface), and subsequently, the refrigerant is likewise guided to the next surface in sequence depending on the number of surfaces.
  • the present invention has been made in view of the foregoing, and it is therefore an object of the present invention to provide a heat exchanger and the like, each of which is capable of suppressing, even with a plurality of heat exchange function surface units, an influence of the gravity exerted on refrigerant, and suppressing reduction of heat exchange performance in each of the surfaces.
  • a heat exchanger comprising: a plurality of heat exchange function surface units; each of the plurality of heat exchange function surface units having an upper header pipe, a lower header pipe, and a plurality of heat exchange pipes provided between a pair of the upper header pipe and the lower header pipe; the plurality of heat exchange function surface units having a parallel connection relationship; a plurality of the lower header pipes being connected to a lower collection pipe through a branch current adjusting section.
  • a heat exchange method of carrying out heat exchange in a plurality of surfaces including: preparing an upper header pipe, a lower header pipe, and a plurality of heat exchange pipes provided between a pair of the upper header pipe and the lower header pipe in each of a plurality of heat exchange function surface units; connecting the plurality of heat exchange function surface units in parallel, and connecting a plurality of the lower header pipes to a lower collection pipe through a branch current adjusting section; and branching, by the branch current adjusting section, refrigerant inside the lower collection pipe in parallel to the plurality of heat exchange function surface units, subjecting the refrigerant to the heat exchange in the each of the plurality of heat exchange function surface units, and causing the refrigerant to flow out from a plurality of the upper header pipes so as to be joined together to an upper side collection pipe.
  • the present invention it is possible to suppress, even with the plurality of heat exchange function surface units, the influence of the gravity exerted on the refrigerant, and suppress the reduction of the heat exchange performance in each of the surfaces.
  • FIG. 1 is a view illustrating a structure of a heat exchanger according to a first embodiment of the present invention.
  • FIG. 2 is a perspective view of a lower header pipe, for illustrating a perforated pipe.
  • FIG. 3 is a diagram illustrating liquid distribution characteristics of a lower header pipe as an example for comparing.
  • FIG. 4 is a diagram illustrating liquid distribution characteristics of a perforated pipe built-in type lower header pipe according to the first embodiment of the present invention.
  • FIG. 5 is a view illustrating an external appearance and plan view of a multi-air conditioner outdoor unit for a building according to the first embodiment of the present invention.
  • FIG. 6 is a view illustrating an external appearance and plan view of a package air conditioner outdoor unit according to a second embodiment of the present invention.
  • FIG. 1 is a view illustrating a structure of a heat exchanger according to a first embodiment of the present invention.
  • the heat exchanger of this embodiment functions as an outdoor unit of an air conditioner that is installed in a space of intended use, and carries out heating and cooling. Therefore, the heat exchanger is a parallel flow type heat exchanger in which when the heat exchanger operates as a condenser in a phase of the cooling, refrigerant flows from the top to the bottom as indicated by dotted line arrows in FIG. 1 , and when the heat exchanger operates as an evaporator in a phase of the heating, the refrigerant flows from the bottom to the top as indicated by solid line arrows in FIG. 1 .
  • a heat exchanger 1 has a plurality of heat exchange function surface units 3 .
  • FIG. 1 illustrates an example in which three heat exchange function surface units 3 are provided.
  • the adjacent heat exchange function surface units 3 are structured so as to be directed orthogonal to each other.
  • 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 are provided in each of the heat exchange function surface units 3 .
  • a flat pipe is used as the heat exchange pipe 9 .
  • a fin 11 (specifically, a corrugated fin) is provided between the heat exchange pipes 9 .
  • One end of an upper communication pipe 13 is connected to each of the upper header pipes 5 .
  • the other end side of the upper communication pipe 13 is connected to an upper collection pipe 15 .
  • Each of the lower header pipes 7 is connected to a lower collection pipe 19 through a branch current adjusting section 17 described later.
  • the plurality of heat exchange function surface units 3 are arranged in a parallel connection relationship between the upper collection pipe 15 and the lower collection pipe 19 . Note that, although an illustration is omitted, it is assumed that a pair of the adjacent heat exchange function surface units 3 is covered with a blocking member such as a metallic plate so that the fluid to be subjected to the heat exchange is not bypassed.
  • the branch current adjusting section 17 serves to adjust a dryness and a flow rate of the refrigerant to be supplied to the plurality of lower header pipes 7 .
  • this embodiment is described in the form of a configuration in which when the refrigerant flows from the bottom to the top in the phase of the heating, gas-liquid two phase refrigerant is supplied to the plurality of heat exchange function surface units 3 with the equal dryness and flow rate.
  • the branch current adjusting section 17 includes a distributer 21 and at least one (two in the illustration) flow rate adjusting section 23 .
  • One end side of the distributer 21 is connected to the lower collection pipe 19 , and a plurality of connection ports on the other end side thereof are connected to ends on one side of corresponding lower communication pipes 25 .
  • ends on the other side of the lower communication pipes 25 are connected to collection side inlet and outlet ports 7 a of the corresponding lower header pipes 7 , respectively.
  • the distributer 21 connected in such a manner supplies the refrigerant to the plurality of lower communication pipes 25 with the equal dryness.
  • a capillary is used as the flow rate adjusting section 23 .
  • the flow rate adjusting section 23 is provided between the distributer 21 and the corresponding lower header pipe 7 , that is, in the lower communication pipe 25 , the flow rate adjusting section 23 is not necessarily arranged in all the lower communication pipes 25 .
  • the collection side inlet and outlet port 7 a of the lower header pipe 7 and a collection side inlet and outlet port 5 a of the upper header pipe 5 are positioned mutually opposite to each other in a direction in which the header pipe extends.
  • the collection side inlet and outlet port 7 a of the lower header pipe 7 is provided on one end side of the lower header pipe 7
  • the collection side inlet and outlet port 5 a of the upper header pipe 5 is provided on the other end side of the upper header pipe 5 . That is, refrigerant distribution paths between the collection side inlet and outlet port 5 a and the collection side inlet and outlet port 7 a are designed so as to be approximately equal in flow path length even via any of the heat exchange pipes 9 .
  • FIG. 2 is a perspective view of the lower header pipe, for illustrating the perforated pipe.
  • the plurality of heat exchange pipes 9 and communication holes with the plurality of heat exchange pipes 9 which are supposed to be positioned above the lower header pipe 7 , are omitted in illustration thereof.
  • the perforated pipe 27 is a block-shaped or pipe-shaped member, and is provided approximately in the vicinity of the center of the space inside the lower header pipe 7 in a state in which the perforated pipe 27 is floated from an inner surface of the lower header pipe 7 .
  • a large number of distribution holes 29 are formed in the perforated pipe 27 .
  • the distribution holes 29 are arranged approximately in the lower section of the perforated pipe 27 .
  • a double pipe structure is obtained by a combination of such a perforated pipe 27 and the lower header pipe 7 . Therefore, for example, in the phase of the heating, after the refrigerant, which flows through the lower communication pipe 25 , temporarily flows into the perforated pipe 27 , the refrigerant equally flows out from the large number of distribution holes 29 to the outside of the perforated pipe 27 in a depth direction (in a horizontal direction of the drawing sheet of FIG. 2 ). Further, the refrigerant is equally dispersed inside the lower header pipe 7 to be equally supplied from the communication holes (not shown) of the upper surface of the lower header pipe 7 to the plurality of heat exchange pipes 9 .
  • FIG. 3 is a diagram illustrating liquid distribution characteristics of a lower header pipe as an example for comparing, which is horizontally arranged and does not have the perforated pipe.
  • FIG. 4 is a diagram illustrating liquid distribution characteristics of a perforated pipe built-in type lower header pipe according to this embodiment, which is horizontally arranged.
  • an axis of abscissa represents a path number, that is, numbers of flow paths of the heat exchange pipes arranged in the depth direction of the lower header pipe (flow paths of 28 flat pipes vertically inserted into the upper surface of the lower header pipe).
  • An axis of ordinate represents a liquid distribution ratio for each path number.
  • any of the cases is out of an example of an equal distribution line indicated in parallel with the axis of abscissa.
  • FIG. 5 is a view illustrating an outer appearance and plan view of the multi-air conditioner outdoor unit for a building.
  • the multi-air conditioner outdoor unit for a building is employed as a high-performance apparatus that is larger in size than an outdoor unit for general home use.
  • the heat exchange function surface units 3 are allocated to three surfaces of a housing 103 , respectively.
  • a propeller fan 105 is arranged at the center of these heat exchange function surface units 3 .
  • air is drawn into the housing 103 from three side surfaces of the housing 103 and is subjected to the heat exchange in the heat exchange function surface units 3 .
  • the air is ejected from an air outlet formed in a fan guard 109 provided on an upper surface of the housing 103 (top-flow type).
  • the heat exchanger 1 serving as the outdoor unit operates as an evaporator.
  • the gas-liquid two phase refrigerant, which has entered the distributer 21 becomes a uniform mist flow when passing through an orifice (not shown) to be supplied to each of the lower communication pipes 25 .
  • the uniform mist flow is adjusted in flow rate thereof in each of the flow rate adjusting sections 23 to flow into the lower header pipe 7 of the corresponding heat exchange function surface unit 3 .
  • the refrigerant which has flowed into the lower header pipe 7 through the collection side inlet and outlet port 7 a of the lower header pipe 7 , is ejected from the distribution holes 29 of the perforated Pipe 27 to be equally distributed to the heat exchange pipes 9 .
  • the perforated pipe 27 when the dryness is large, minute droplets are ejected from the small holes. When the dryness is small, the bubbles are ejected to the liquid part collected in the annular section. Therefore, the equal distribution is realized independently of the dryness and the flow rate.
  • the refrigerant After the refrigerant is subjected to the heat exchange with the air (not shown) when having passed through the heat exchange pipes 9 , the refrigerant flows into the upper header pipe 5 and then flows out through the collection side inlet and outlet port 5 a on the opposite side to the collection side inlet and outlet port 7 a of the lower header pipe 7 .
  • the refrigerant which has flowed out through each of the collection side inlet and outlet ports 5 a , passes through the corresponding upper communication pipe 13 to join another refrigerant in the upper collection pipe 15 . Note that, in the phase of the cooling operation, the heat exchanger 1 operates as the condenser, and hence the flow of the refrigerant is reversed.
  • the header pipes are directed in the horizontal direction, and hence the influence of the gravity can be suppressed for the refrigerant distribution, and the refrigerant can be equally distributed to the plurality of heat exchange pipes.
  • the header pipes are horizontally arranged in such a manner, a plurality of surfaces can be controlled to exhibit the heat exchange function without being impeded by the actual situation that the curve of the header pipe is difficult to form.
  • the heat exchange is carried out in a plurality of surfaces, the refrigerant is branched in distribution thereof in parallel to the plurality of heat exchange function surface units.
  • the upstream/downstream relationship is not generated mutually among the plurality of heat exchange function surface units, and hence the satisfactory heat exchange efficiency can be maintained in each of the heat exchange function surface units.
  • the refrigerant is supplied to the heat exchange function surface units in a distributive manner. Therefore, the very satisfactory heat exchange performance can be obtained in all the heat exchange function surface units.
  • the entire heat exchanger does not have such a flow path that the refrigerant, which has been subjected to the heat exchange in the plurality of heat exchange pipes, is collected once, and is branched to the plurality of heat exchange pipes again. Therefore, there is no such problem that the refrigerant cannot be equally supplied to the plurality of heat exchange pipes.
  • the heat exchanger and the heat exchange method of this embodiment even with the plurality of heat exchange function surface units, the influence of the gravity exerted on the refrigerant can be suppressed, and the reduction of the heat exchange performance in each of the surfaces can be suppressed.
  • the inlet and outlet port of the lower header pipe and the inlet and outlet port of the upper header pipe are arranged on opposite sides to each other. Therefore, even when the refrigerant passes through any of the heat exchange pipes, the pressure losses become approximately equal to each other, that is, the equal distribution of the gas-liquid two phase flow can be realized.
  • the perforated pipe is provided inside the lower header pipe, with the result that the minute droplets or the bubbles are ejected from the distribution holes to the annular section of the double structure, to thereby also promote the equal distribution of the gas-liquid two phase refrigerant.
  • the number of distributions to the heat exchange pipes is increased, and the number of times of the distribution is suppressed low (in the example described above, the number of times of the distribution is only one). Therefore, although innumerable heat exchange pipes are used in order to prepare the plurality of heat exchange function surface units, the refrigerant pressure loss can be suppressed low relative to the number of heat exchange pipes. Therefore, in particular, low-pressure refrigerant (such as refrigerant exhibiting a large refrigerant pressure loss), for example, HFO1234yf, HFO1234ze, or R134a can also be effectively utilized.
  • low-pressure refrigerant such as refrigerant exhibiting a large refrigerant pressure loss
  • FIG. 6 A description is made of a second embodiment of the present invention with reference to FIG. 6 .
  • the first embodiment described above exemplifies such a mode that the refrigerant dryness is equally adjusted for the plurality of heat exchange function surface units, and the refrigerant flow rate is changed depending on the heat loads (mainly depend on the passing air velocity in the heat exchange section), which are different from one another in the heat exchange function surface units.
  • the present invention is not limited to that mode. That is, the present invention also encompasses such a mode that the refrigerant drynesses and/or the refrigerant flow rates are adjusted so as to be different from one another in the plurality of heat exchange function surface units.
  • FIG. 6 illustrates an external appearance and plan view of the application to the package air conditioner outdoor unit.
  • the heat exchange function surface units 3 are allocated to a side surface and a back surface of a housing 203 , respectively.
  • a propeller fan 205 By rotation of a propeller fan 205 , as indicated by arrows 207 , the air is drawn into the housing 203 from the side surface and the back surface of the housing 203 , and is subjected to the heat exchange in the heat exchange function surface units 3 . Then, as indicated by arrows 211 , the air is ejected from an air outlet provided in the front surface of the housing 203 .
  • the influence of the gravity exerted on the refrigerant can be suppressed, and the reduction of the heat exchange performance in each of the surfaces can be suppressed.
  • the mode of formation of the distribution holes is not limited thereto, and the orientation, the number, and the hole shape of the distribution holes may be suitably changed.
  • the structure of the branch current adjusting section described above is also merely an example, and hence may be suitably changed.
  • a branch current adjusting section having such a mode that height positions of a plurality of outlet port side branching pipes such as Y-shaped branching pipes or low-pressure loss distributers are made different from one another, a rate of a branch current of a liquid phase is changed by an influence of the gravity, and the dryness and the flow rate are simultaneously adjusted.

Landscapes

  • 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)
US14/391,466 2012-04-26 2012-04-26 Heat exchanger and heat exchange method Abandoned US20150083383A1 (en)

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)

Publication Number Publication Date
US20150083383A1 true US20150083383A1 (en) 2015-03-26

Family

ID=49482407

Family Applications (1)

Application Number Title Priority Date Filing Date
US14/391,466 Abandoned US20150083383A1 (en) 2012-04-26 2012-04-26 Heat exchanger and heat exchange method

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 (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120199313A1 (en) * 2009-10-13 2012-08-09 Peugeot Citroen Automobiles Sa Cooling Device For a Hybrid Vehicle
KR20180000492U (ko) 2016-08-11 2018-02-21 삼성중공업 주식회사 음극화 보호 장치
US10415860B2 (en) * 2015-09-09 2019-09-17 Mitsubishi Electric Corporation Air-conditioning apparatus
US11333401B2 (en) * 2017-07-04 2022-05-17 Mitsubishi Electric Corporation Refrigeration cycle apparatus
CN115768034A (zh) * 2021-09-06 2023-03-07 英业达科技有限公司 冷凝器
US20230076784A1 (en) * 2021-09-06 2023-03-09 Inventec (Pudong) Technology Corporation Heat dissipation assembly and electronic assembly
CN115776796A (zh) * 2021-09-06 2023-03-10 英业达科技有限公司 散热组件以及电子组件
EP4506629A4 (fr) * 2022-04-01 2025-05-21 Mitsubishi Electric Corporation Unité extérieure et climatiseur équipé de celle-ci

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015162689A1 (fr) * 2014-04-22 2015-10-29 三菱電機株式会社 Conditionneur d'air
WO2016181509A1 (fr) * 2015-05-12 2016-11-17 三菱電機株式会社 Échangeur de chaleur du type à ailettes ondulées, dispositif à cycle de réfrigération, dispositif pour la production d'ailettes ondulées, et procédé de production d'échangeur de chaleur du type à ailettes ondulées
JP6650752B2 (ja) * 2015-12-24 2020-02-19 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
JP2019152367A (ja) * 2018-03-02 2019-09-12 パナソニックＩｐマネジメント株式会社 熱交換器ユニットおよびそれを用いた空気調和機
CN112204333B (zh) * 2018-06-11 2023-02-21 三菱电机株式会社 制冷剂分配器、热交换器及空气调节装置
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
CN213747274U (zh) * 2020-09-01 2021-07-20 浙江盾安热工科技有限公司 组合式换热器
CN112066602A (zh) * 2020-09-14 2020-12-11 珠海格力电器股份有限公司 一种换热器及空调、空调控制方法及装置
WO2024236763A1 (fr) * 2023-05-17 2024-11-21 三菱電機株式会社 Échangeur de chaleur, unité extérieure équipée d'un échangeur de chaleur et dispositif de climatisation équipé d'une unité extérieure
WO2025169459A1 (fr) * 2024-02-09 2025-08-14 三菱電機株式会社 Échangeur de chaleur et dispositif de climatisation
WO2025182083A1 (fr) * 2024-03-01 2025-09-04 三菱電機株式会社 Échangeur de chaleur, unité extérieure de dispositif de climatisation ayant un échangeur de chaleur, et dispositif de climatisation ayant une unité extérieure de dispositif de climatisation
JP7756847B1 (ja) * 2025-04-11 2025-10-20 三菱電機株式会社 熱交換器

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5806586A (en) * 1993-07-03 1998-09-15 Ernst Flitsch Gmbh & Co. Plate heat exchanger with a refrigerant distributor
US6729386B1 (en) * 2001-01-22 2004-05-04 Stanley H. Sather Pulp drier coil with improved header
US7143605B2 (en) * 2003-12-22 2006-12-05 Hussman Corporation Flat-tube evaporator with micro-distributor
US7331195B2 (en) * 2004-10-01 2008-02-19 Advanced Heat Transfer Llc Refrigerant distribution device and method
WO2009117159A2 (fr) * 2008-03-20 2009-09-24 Carrier Corporation Echangeur de chaleur à micro-canaux qui convient au pliage
CN101949663A (zh) * 2010-09-13 2011-01-19 三花丹佛斯（杭州）微通道换热器有限公司 制冷剂导管和具有该制冷剂导管的换热器
US20110127023A1 (en) * 2008-07-10 2011-06-02 Taras Michael F Design characteristics for heat exchangers distribution insert
US20110226005A1 (en) * 2010-03-17 2011-09-22 Hyung Jun Lee Distributor, and evaporator and refrigerating machine with the same
US8113270B2 (en) * 2005-02-02 2012-02-14 Carrier Corporation Tube insert and bi-flow arrangement for a header of a heat pump
US8408284B2 (en) * 2011-05-05 2013-04-02 Delphi Technologies, Inc. Heat exchanger assembly

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4373353A (en) * 1977-08-17 1983-02-15 Fedders Corporation Refrigerant control
JPH0626783A (ja) * 1992-07-10 1994-02-04 Kobe Steel Ltd 液化天然ガスの気化装置
JPH06159840A (ja) * 1992-11-18 1994-06-07 Nippondenso Co Ltd ヒートポンプ式空気調和機
FR2713320B1 (fr) * 1993-12-02 1996-02-02 Mc International Procédé de commande et de dégivrage en continu d'un échangeur frigorifique et installation équipée d'un tel échangeur.
JPH0942743A (ja) * 1995-07-27 1997-02-14 Hitachi Ltd 空気調和機及びこれに用いる冷媒分岐ユニット
JPH10185358A (ja) * 1996-10-24 1998-07-14 Showa Alum Corp 蒸発器
KR100497847B1 (ko) * 1996-10-24 2005-09-30 쇼와 덴코 가부시키가이샤 증발기
JPH10160382A (ja) * 1996-11-29 1998-06-19 Toyo Radiator Co Ltd 空調用熱交換器およびその製造方法
US5842351A (en) * 1997-10-24 1998-12-01 American Standard Inc. Mixing device for improved distribution of refrigerant to evaporator
US7597137B2 (en) * 2007-02-28 2009-10-06 Colmac Coil Manufacturing, Inc. Heat exchanger system
JP2010038439A (ja) * 2008-08-05 2010-02-18 Sharp Corp 熱交換器
JP5385589B2 (ja) 2008-10-30 2014-01-08 シャープ株式会社 空気調和機の室外機
CN101907376B (zh) * 2009-06-02 2012-07-25 江森自控楼宇设备科技(无锡)有限公司 用于制冷系统中的制冷剂的分配装置
CN101762201B (zh) * 2010-01-05 2012-07-04 华北电力大学 一种应用于联箱分支管两相流均匀分配的笛形均流器
JP5608478B2 (ja) * 2010-08-31 2014-10-15 日立アプライアンス株式会社 熱交換器及びそれを用いた空気調和機

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5806586A (en) * 1993-07-03 1998-09-15 Ernst Flitsch Gmbh & Co. Plate heat exchanger with a refrigerant distributor
US6729386B1 (en) * 2001-01-22 2004-05-04 Stanley H. Sather Pulp drier coil with improved header
US7143605B2 (en) * 2003-12-22 2006-12-05 Hussman Corporation Flat-tube evaporator with micro-distributor
US7331195B2 (en) * 2004-10-01 2008-02-19 Advanced Heat Transfer Llc Refrigerant distribution device and method
US8113270B2 (en) * 2005-02-02 2012-02-14 Carrier Corporation Tube insert and bi-flow arrangement for a header of a heat pump
WO2009117159A2 (fr) * 2008-03-20 2009-09-24 Carrier Corporation Echangeur de chaleur à micro-canaux qui convient au pliage
US20110094257A1 (en) * 2008-03-20 2011-04-28 Carrier Corporation Micro-channel heat exchanger suitable for bending
US20110127023A1 (en) * 2008-07-10 2011-06-02 Taras Michael F Design characteristics for heat exchangers distribution insert
US20110226005A1 (en) * 2010-03-17 2011-09-22 Hyung Jun Lee Distributor, and evaporator and refrigerating machine with the same
CN101949663A (zh) * 2010-09-13 2011-01-19 三花丹佛斯（杭州）微通道换热器有限公司 制冷剂导管和具有该制冷剂导管的换热器
US20130199764A1 (en) * 2010-09-13 2013-08-08 Danfoss A/S Refrigerant guiding pipe and heat exchanger having refrigerant guiding pipe
US8408284B2 (en) * 2011-05-05 2013-04-02 Delphi Technologies, Inc. Heat exchanger assembly

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20120199313A1 (en) * 2009-10-13 2012-08-09 Peugeot Citroen Automobiles Sa Cooling Device For a Hybrid Vehicle
US9238994B2 (en) * 2009-10-13 2016-01-19 Peugeot Citroen Automobiles Sa Cooling device for a hybrid vehicle
US10415860B2 (en) * 2015-09-09 2019-09-17 Mitsubishi Electric Corporation Air-conditioning apparatus
KR20180000492U (ko) 2016-08-11 2018-02-21 삼성중공업 주식회사 음극화 보호 장치
US11333401B2 (en) * 2017-07-04 2022-05-17 Mitsubishi Electric Corporation Refrigeration cycle apparatus
CN115768034A (zh) * 2021-09-06 2023-03-07 英业达科技有限公司 冷凝器
US20230076784A1 (en) * 2021-09-06 2023-03-09 Inventec (Pudong) Technology Corporation Heat dissipation assembly and electronic assembly
CN115776796A (zh) * 2021-09-06 2023-03-10 英业达科技有限公司 散热组件以及电子组件
EP4506629A4 (fr) * 2022-04-01 2025-05-21 Mitsubishi Electric Corporation Unité extérieure et climatiseur équipé de celle-ci

Also Published As

Publication number Publication date
CN104335000B (zh) 2016-09-14
JP6104893B2 (ja) 2017-03-29
EP2863161A1 (fr) 2015-04-22
JPWO2013161038A1 (ja) 2015-12-21
CN104335000A (zh) 2015-02-04
EP2863161A4 (fr) 2016-03-23
CN203323459U (zh) 2013-12-04
ES2702291T3 (es) 2019-02-28
WO2013161038A1 (fr) 2013-10-31
EP2863161B1 (fr) 2018-11-14

Similar Documents

Publication Publication Date Title
US20150083383A1 (en) Heat exchanger and heat exchange method
EP2853843B1 (fr) Distributeur de fluide réfrigérant, et échangeur de chaleur équipé avec le distributeur de fluide réfrigérant
EP3217135B1 (fr) Collecteur stratifié, échangeur de chaleur et appareil de climatisation
JP6352401B2 (ja) 空気調和装置
EP3203175B1 (fr) Échangeur thermique et appareil de climatisation
EP3051245B1 (fr) Collecteur de type stratifié, échangeur thermique, et appareil de climatisation
US10168083B2 (en) Refrigeration system and heat exchanger thereof
EP2971982B1 (fr) Serpentin modulaire pour refroidisseurs refroidis par air
CN108139089A (zh) 空气调节机的室外机及室内机
WO2014205799A1 (fr) Échangeurs thermiques à microcanaux
EP4246075A2 (fr) Échangeur de chaleur pour applications de pompe à chaleur
WO2015099872A1 (fr) Distributeur pour évaporateur à film tombant
EP3087331B1 (fr) Colonne montante de frigorigène pour évaporateur
EP3077756B1 (fr) Évaporateur asymétrique
JP2017141999A (ja) ヘッダー分配器、ヘッダー分配器を搭載した室外機、及び空気調和装置
CN210892266U (zh) 微通道换热器和制冷系统
JP2018096559A (ja) 熱交換器
CN118776356A (zh) 换热器及空调器
CN117685693A (zh) 冷媒散热器及具有其的空调器
CN204345972U (zh) 客车hvac系统以及与其一起使用的微通道热交换器
KR20030042710A (ko) 공조장치의 열교환기
KR20010018410A (ko) 공기 조화기용 열교환기의 다기관

Legal Events

Date Code Title Description
AS Assignment

Owner name: MITSUBISHI ELECTRIC CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:OKAZAKI, TAKASHI;ISHIBASHI, AKIRA;LEE, SANGMU;AND OTHERS;SIGNING DATES FROM 20140908 TO 20140911;REEL/FRAME:033921/0072

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION