EP2955464A1 - Distributeur de réfrigérant et dispositif de pompe à chaleur utilisant le distributeur de réfrigérant - Google Patents

Distributeur de réfrigérant et dispositif de pompe à chaleur utilisant le distributeur de réfrigérant Download PDF

Info

Publication number
EP2955464A1
EP2955464A1 EP13873009.8A EP13873009A EP2955464A1 EP 2955464 A1 EP2955464 A1 EP 2955464A1 EP 13873009 A EP13873009 A EP 13873009A EP 2955464 A1 EP2955464 A1 EP 2955464A1
Authority
EP
European Patent Office
Prior art keywords
refrigerant
distribution device
way branch
branch pipe
inflow 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.)
Withdrawn
Application number
EP13873009.8A
Other languages
German (de)
English (en)
Other versions
EP2955464A4 (fr
Inventor
Takuya Matsuda
Keisuke Hokazono
Hiroki Okazawa
Wataru Suzuki
Takashi Nakajima
Atsushi Mochizuki
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
Publication of EP2955464A1 publication Critical patent/EP2955464A1/fr
Publication of EP2955464A4 publication Critical patent/EP2955464A4/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F25B41/42—Arrangements for diverging or converging flows, e.g. branch lines or junctions
    • 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
    • F28D1/0475—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 having a single U-bend
    • F28D1/0476—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 having a single U-bend the conduits having a non-circular cross-section
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2275/00—Fastening; Joining
    • F28F2275/04—Fastening; Joining by brazing

Definitions

  • the present invention relates to refrigerant distribution devices.
  • a refrigerant distribution device that distributes the refrigerant to the respective paths is necessary on an inlet side of the refrigerant.
  • a distributor is conventionally used as a refrigerant distribution device so that refrigerant distributed by the distributor flows into the respective heat transfer tubes of the heat exchanger by capillary tubes (for example, see Patent Literature 1).
  • Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2008-121984 (page 4, Fig. 1 )
  • Patent Literature 1 a plurality of heat transfer tubes are connected to a distributor via capillary tubes that are individually disposed at the ends of the heat transfer tubes, which serve as inlet ports for refrigerant flowing from the outside, and the number of paths of the heat exchanger and the number of the capillary tubes are the same.
  • the number of heat transfer tubes increases and thus the number of paths increases, the number of capillary tubes also increases.
  • the present invention is made to overcome such problems and provides a refrigerant distribution device that enables a reduction in the number of connected capillary tubes, a compact installation space of the capillary tubes mounted on an actual machine, and a cost reduction, and a heat pump apparatus that uses this refrigerant distribution device.
  • a refrigerant distribution device distributes refrigerant to a plurality of heat transfer tubes that constitute a heat exchanger.
  • the refrigerant distribution device includes a first distribution device dividing refrigerant into a plurality of portions, and a plurality of second distribution devices each dividing refrigerant divided by the first distribution device into two portions to flow into two of the plurality of heat transfer tubes.
  • the number of connected capillary tubes can be reduced, an installation space of the capillary tubes mounted on an actual machine can be compact, and the cost of the capillary tubes can be reduced.
  • Fig. 1 is a schematic configuration diagram showing a state in which a refrigerant distribution device according to Embodiment 1 of the present invention is connected to a heat exchanger.
  • the same reference signs refer to the same or corresponding elements throughout the whole description. Further, the forms of the elements shown in the description are for exemplary purposes only and the invention is not limited to the description.
  • a heat exchanger 1 is a fin and tube heat exchanger that includes a plurality of plate shaped fins 2 being stacked with spaces therebetween and a plurality of heat transfer tubes 3 that penetrate the plate shaped fins 2 in a stack direction and allow refrigerant to flow therein.
  • the heat transfer tubes 3 may be circular tubes or flat tubes made of copper or aluminum.
  • a plurality of heat transfer tubes 3 are connected to a refrigerant distribution device 10 at one end and a gas header 6 at the other end.
  • the refrigerant distribution device 10 includes a first distribution device 20 and a plurality of two-way branch pipes 30 as a second distribution device.
  • the first distribution device 20 is to uniformly distribute refrigerant that flows into the first distribution device 20 in a state of gas-liquid two-phase into the respective heat transfer tubes 3 of the heat exchanger 1. Accordingly, in Fig. 1 , a distributor is used as the first distribution device 20.
  • a throttle mechanism such as an orifice is inserted in the distributor such that the two-phase flow that flows therein becomes a spray flow while passing through the orifice to facilitate uniform distribution.
  • the spray flow of refrigerant is uniformly distributed to the respective capillary tubes 40.
  • a throttle mechanism such as an orifice may not be used in the distributor. It is essential that a distributor capable of uniform distribution is used as the first distribution device 20.
  • the distributor may be made of a material such as copper, aluminum and brass.
  • the capillary tube 40 has an inner diameter of approximately 3.5 mm and a length of approximately 1000 mm. These dimensions of the capillary tube 40 are merely an example.
  • the capillary tube 40 may be curved in a circular shape depending on the relationship between the length and the installation space.
  • an in-pipe pressure loss can be adjusted based on the specification (inner diameter, length) of the capillary tubes 40, thus a branch flow rate from the first distribution device 20 to each of the two-way branch pipes 30 can be adjusted.
  • An air speed of an air-sending fan (not shown in the figure) that sends air to the heat exchanger 1 is not necessarily uniform across the entire surface of the heat exchanger 1, and an air speed distribution may be present. For example, when an air-sending fan is disposed in the upper part of the heat exchanger 1, the air speed is faster in the upper part of the heat exchanger 1 than in the lower part.
  • the refrigerant passing through a part in which the air speed is fast tends to be easily evaporated and dried compared with the refrigerant passing through a part in which the air speed is slow. Accordingly, when the same amount of refrigerant flows into the respective heat transfer tubes 3, the refrigerant passing through a part in which the air speed is fast has a quality higher than the refrigerant passing through a part in which the air speed is slow. This causes variation in refrigerant state at the exit of the heat exchanger, and the refrigerant state fails to be stabilized. Therefore, it is required that a larger amount of refrigerant flows into the heat transfer tube located in a part in which the air speed is fast. As described above, when adjustment of branch flow rate is necessary, the branch flow rate can be adjusted by adjusting the specification of the capillary tubes 40.
  • the two-way branch pipes 30 are connected to the end of the capillary tubes 40 on the opposite side to the first distribution device 20. Using the two-way branch pipes 30 allows the refrigerant to be distributed to the number of branches (the number of paths) of 2 x A, where A is the number of branches of the first distribution device 20 and the number of capillary tubes 40. A configuration of the two-way branch pipe 30 will be described below.
  • Fig. 2 is a perspective view of the two-way branch pipe of Fig. 1 .
  • the two-way branch pipe 30 includes a U-bend section 31 formed by bending a circular tube in U-shape and a straight inflow section 35.
  • the U-bend section 31 includes a connection 32 and two arms 33 and 34 extending from each end of the connection 32 in parallel to each other.
  • the straight inflow section 35 is formed by performing bulge-forming process on one of the two arms 33 and 34 (in this example, the arm 34) of the U-bend section 31. In this example, the straight inflow section 35 is disposed on the arm 34.
  • Bulge-forming process is a method for forming a hollow shape, in which a pipe-shaped material is set in a mold of a press and then clamped, and after that, while the material is filled with a liquid of high pressure, the material is compressed in the axial direction so that the both ends are forced toward each other, thereby allowing the material to be expanded into the shape of the mold cavity.
  • the straight inflow section 35 of the two-way branch pipe 30 constituted as described above is connected to one end of an L-shaped pipe 36, which is bent in L-shape, while the other end of the L-shaped pipe 36 is connected to the capillary tube 40.
  • the opening ports A and B of the two arms 33 and 34 of the two-way branch pipe 30 are connected to the heat transfer tubes 3 of the heat exchanger 1.
  • the heat transfer tubes 3 are directly connected when they are circular tubes, and the heat transfer tubes 3 are connected via circular tube - flat tube joints 4 of Fig. 3 when they are flat tubes.
  • the two-way branch pipe 30 is connected to the heat exchanger 1 so that the two arms 33 and 34 extend in a parallel direction and the refrigerant flowing from the straight inflow section 35 to the arm 34 is branched and flows in the horizontal direction. The reason will be described later.
  • the dotted line arrow indicates the flow of refrigerant in the case where the heat exchanger 1 is used as an evaporator, and in the two-way branch pipe 30, the refrigerant flowing from the capillary tube 40 flows into the straight inflow section 35 via the L-shaped pipe 36.
  • the refrigerant flowing into the straight inflow section 35 is branched into the arm 33 and the arm 34, each of which flows into the respective heat transfer tubes 3.
  • the two-way branch pipe 30 allows the introduced refrigerant to be branched into two flows to the respective heat transfer tubes 3, the number of capillary tubes 40 can be reduced to half compared with the configuration in which the capillary tubes 40 are directly connected to the respective heat transfer tubes 3. Accordingly, using the refrigerant distribution device 10 of Embodiment 1 can improve installability of the capillary tubes 40.
  • the two-way branch pipe 30 is required to have a function of uniformly distributing the refrigerant flowing from the capillary tubes 40 and allowing the refrigerant to flow into the respective heat transfer tubes 3.
  • the first distribution device 20 can uniformly distribute the refrigerant into the respective capillary tubes 40, and it is also required for the two-way branch pipes 30 to uniformly distribute the refrigerant so that the refrigerant flows into the respective heat transfer tubes of the heat exchanger 1 while remaining in the uniformly distributed state.
  • the refrigerant that has passed an expansion valve of the heat pump apparatus and the refrigerant at an inlet of the evaporator is generally in a state of gas-liquid two-phase flow made up of gas refrigerant and liquid refrigerant, causing density distribution in a cross section of the refrigerant flowing in pipes.
  • a biased flow occurs due to an effect of centrifugal force, which causes the flowing liquid refrigerant to be biased to one side of the inner surface of the pipe. That is, two-phase refrigerant is separated into gas and liquid phases.
  • the refrigerant distribution device located on the inflow side of the refrigerant it is required for the refrigerant distribution device located on the inflow side of the refrigerant to have a function of preventing the above biased flow from being generated and gas and liquid phases from being separated. Further, it is required for the refrigerant distribution device to have a function of distributing the refrigerant in a state of being uniformly mixed while the ratio of the gas and liquid mass flow rate at the inlet of the refrigerant distribution device remains to be equal to the ratio of the gas and liquid mass flow rate at the outlet of the refrigerant distribution device. Moreover, as described above, as the number of paths increases by decreasing the diameter of the circular tube or flattening the tube, distributing uniform flow rate of refrigerant to the respective paths becomes a more important matter.
  • Fig. 4 is configuration explanatory views of the two-way branch pipe of the refrigerant distribution device according to Embodiment 1 of the present invention.
  • Fig. 4(a) is a front view of the two-way branch pipe 30 and
  • Fig. 4(b) is a side view of Fig. 4(a) .
  • the straight inflow section 35 is formed by bulge-forming such that an angle ⁇ 1 between a tube axis X1 of the straight inflow section 35 and a tube axis X2 of the arm 34 is 90 degrees.
  • the angle ⁇ 1 When the angle ⁇ 1 deviates from 90 degrees by 10 degrees or more, the refrigerant flowing from the straight inflow section 35 obliquely collides against a portion of the arm 34 that faces the straight inflow section 35 and generates a biased flow, leading to deterioration of heat exchange efficiency. Therefore, the angle ⁇ 1 is formed to be 90 degrees. It should be noted the angle is not limited to be exact 90 degrees, and may be slightly deviated.
  • the straight inflow section 35 has the length of 5 mm or more. This point will be described below.
  • the two-phase flow of refrigerant becomes a state in which the liquid phase of the refrigerant is biased to one side in the capillary tube 40.
  • Providing an approach section that extends until a position at which the refrigerant collides against the two-way branch and has 20 times or more of the inner diameter allows for a sufficiently stable flow.
  • ensuring a configuration with the approach section having 20 times or more of the inner diameter is difficult.
  • Embodiment 1 ensures the length of 5 mm or more for the straight inflow section 35 and the length of 15 mm or more (two times or more of the inner diameter) together with the length of the horizontal section of the capillary tube 40 or the L-shaped pipe 36.
  • the gas-liquid two-phase flow is affected by a curve of the capillary tube 40 and becomes a state in which the liquid surface is biased in the pipe of the straight inflow section 35.
  • the gas-liquid two-phase flow into the straight inflow section 35 is biased by an effect of the biased liquid surface and fails to be uniformly distributed in the two-way branch pipe 30, thereby compromising heat exchange efficiency.
  • the two-way branch pipe 30 preferably has the angle ⁇ 1 of 90 degrees between the arm 34 and the straight inflow section 35 and the length of the straight inflow section 35 of 5 mm or more.
  • the straight inflow section 35 of the two-way branch pipe 30 is formed by bulge-forming.
  • Using the bulge-forming process allows for a stable processing of the shape of 90 degrees for the angle ⁇ 1 and ensures the length of 5 mm or more for the straight inflow section 35.
  • Bulge-forming process can be applied to not only a straight pipe but also a curved pipe, and further, the straight inflow section 35 can be formed to have a long length while preventing the wall thickness from being decreased.
  • the two-way branch pipe 30 and the capillary tube 40 can be connected by inserting the L-shaped pipe 36 or the capillary tube 40 having an outer diameter smaller than an inner diameter of an inlet port of the bulge-formed straight inflow section 35 in the inlet port of the bulge-formed straight inflow section 35 and brazing thereto.
  • This provides stable manufacture without defective.
  • the straight inflow section 35 is formed without using bulge-forming, the straight inflow section 35 has a small length and a small wall thickness. Consequently, when the L-shaped pipe 36 or the capillary tube 40 is connected to the straight inflow section 35, the angle ⁇ 1 deviates from 90 degrees by a large amount. Further, in brazing connection, a part of the straight inflow section 35 is to be brazed, and stable brazing cannot be performed due to a small wall thickness and small length of the connection.
  • an angle ⁇ 2 between the straight inflow section 35 and the tube axis X2 of the arm 34 may be any degrees, the angle ⁇ 2 herein is 90 degrees as shown in Fig. 4 .
  • the reason will be described below.
  • the heat transfer tubes 3 are designed to have narrow arrangement pitch, and the mounting density of the heat transfer tubes 3 is increased.
  • using the two-way branch pipe 30 can improve instability of the capillary tubes 40.
  • providing the angle ⁇ 2 of the straight inflow section 35 of the two-way branch pipe 30 of 90 degrees can further improve connectivity of the capillary tubes 40.
  • a curvature R that is twice to three times of the inner diameter is necessary, and in the case where the angle ⁇ 2 is 0 degree, the L-shaped pipe 36 or the capillary tube 40 interferes with the two-way branch pipe 30. Accordingly, in the case where the angle ⁇ 2 is 0 degree, when the mounting density of the heat transfer tubes 3 is increased, it is difficult to connect the capillary tube 40 or the L-shaped pipe 36 to the straight inflow section 35. With the angle ⁇ 2 of 90 degrees, the connection with the capillary tube 40 or the L-shaped pipe 36 comes to the direction of air flow, which does not interfere with the two-way branch pipe 30, thereby improving connectivity.
  • the advantage of the L-shaped pipe 36 will be described below.
  • the L-shaped pipe 36 and the straight inflow section 35 of the two-way branch pipe 30 are initially connected by brazing, then each of the opening ports A and B are connected to the circular tube - flat tube joints 4 by brazing, and then the L-shaped pipe 36 and the capillary tube 40 are connected by brazing.
  • This procedure allows for a stable manufacturing process having a low defective rate.
  • the reason will be as described below. That is, the above connection by brazing is performed by a burner, and since the L-shaped pipe 36 and the capillary tube are connected by brazing at last, other pipes are less likely to be exposed to the flame of burner.
  • the L-shaped pipe 36 it becomes easy to provide the angle ⁇ 1 , at which refrigerant flowing into the two-way branch pipe, of 90 degrees and provide a long approach distance for flowing into the two-way branch pipe, thereby improving uniform distribution.
  • the capillary tube 40 is directly connected to the straight inflow section 35 of the two-way branch pipe 30. Consequently, as the capillary tube 40 is long, unstable, and non-easily routed, the angles ⁇ 1 , at which refrigerant flowing into the two-way branch pipe 30, tends to largely vary.
  • the straight inflow section 35 of the two-way branch pipe 30 is 5 mm or more. However, since it is essential to provide a straight flow path of 10 mm or more, it is also possible that a sum of the L-shaped pipe 36 and the straight inflow section 35 is 10 mm or more.
  • Fig. 5 is a view showing a refrigerant circuit of a heat pump apparatus that uses the refrigerant distribution device according to Embodiment 1 of the present invention.
  • the heat pump apparatus 60 includes a compressor 61, a condensor 62 (heat exchanger 1), an expansion valve 63 as a depressurizing device and an evaporator 64 (heat exchanger 1).
  • the gas refrigerant ejected from the compressor 61 flows into the condensor 62, exchanges heat with air passing through the condensor 62, becomes a high pressure liquid refrigerant and flows out from the condensor 62.
  • the high pressure liquid refrigerant out of the condensor 62 is depressurized by the expansion valve 63, becomes a low pressure gas-liquid two-phase refrigerant, and flows into the evaporator 64.
  • the low pressure gas-liquid two-phase refrigerant flowing into the evaporator 64 exchanges heat with air passing through the evaporator 64, becomes a low pressure gas refrigerant, and is suctioned back into the compressor 61.
  • FIG. 1 the solid arrow indicates a flow of refrigerant in the case where the heat exchanger 1 is used as an evaporator.
  • the gas-liquid two-phase refrigerant flow out of the expansion valve 63 flows into the first distribution device 20 and becomes a spray flow.
  • the spray flow of the refrigerant is uniformly distributed to flow into the respective capillary tubes 40.
  • the refrigerant flows into the two-way branch pipes 30 and flows out while being uniformly distributed into two branched flows as described above, each of which flows into the heat transfer tube 3.
  • the refrigerant flowing into the respective heat transfer tubes 3 exchanges heat with air and becomes a gas state, and is then collected in the gas header 6.
  • the refrigerant collected in the gas header 6 is suctioned into the compressor 61.
  • Figs. 3 and 5 an operation in the case where the heat exchanger 1 is used as a condensor will be described.
  • the dotted arrow indicates a flow of refrigerant in the case where the heat exchanger 1 is used as a condensor.
  • the refrigerant flows in the direction opposite to the case of the evaporator, and the gas refrigerant flow out of the compressor 61 flows into the gas header 6.
  • the refrigerant flowing into the gas header 6 flows into the respective heat transfer tubes 3 while being uniformly distributed in the gas header 6.
  • a distributor or the like is not necessary since the refrigerant can be uniformly distributed without difficulty when the refrigerant is in a gas state, and the gas header 6 constituted by a cylindrical hollow tube is used.
  • the refrigerant flowing into the respective heat transfer tubes 3 flows through the two-way branch pipes 30, the capillary tubes 40 and the first distribution device 20 in sequence. Then, the refrigerant is collected in the first distribution device 20, and flows into the expansion valve 63.
  • Fig. 6 is a view showing a configuration example in which the refrigerant distribution device according to Embodiment 1 of the present invention is connected to a heat exchanger for an outdoor unit of an air conditioning apparatus that uses a flat tube as a heat transfer tube.
  • Fig. 7 is an enlarged perspective view seen from the backside of a connecting portion of the heat exchanger and the refrigerant distribution device of Fig. 5 .
  • shaded portions are the two-way branch pipes 30.
  • Fig. 8 is a perspective view of the flat tube of Fig. 6 .
  • the heat exchanger 100 has a configuration in which heat exchangers are arranged in three lines of an air flow direction, and includes a plurality of plate shaped fins 2 being stacked with spaces therebetween and a plurality of flat tube 3 that penetrate the plate shaped fins 2 in a stack direction and allow refrigerant to flow therein.
  • the ends of a plurality of flat tubes 3 are connected to bends 5, which are bent in a hairpin shape, and the gas header 6 in addition to the two-way branch pipes 30.
  • the flat tubes 3 are used as heat transfer tubes, the flat tubes 3 are connected to the two-way branch pipes 30 and the bends 5 via the circular tube - flat tube joints 4.
  • a path configuration in the heat exchanger 100 is constituted so that the refrigerant flows in a so-called parallel flow in which refrigerant flows while turning back from upstream to downstream with respect to an air flow direction.
  • the heat exchanger 100 is used as a condensor, paths are constituted so that the refrigerant flows in a so-called opposite flow in which refrigerant flows while turning back from downstream to upstream with respect to an air flow direction. Since the refrigerant is sub-cooled in the condensor, the refrigerant temperature decreases. Accordingly, the heat exchange efficiency in the case where the heat exchanger 100 is used as a condensor can be improved by constituting paths so that the refrigerant flows as an opposite flow.
  • the plate shaped fin 2 is made of aluminum, and the flat tube 3 and the plate shaped fin 2 are connected by in-furnace brazing.
  • the heat exchanger uses the heat transfer tube of a circular tube
  • the heat transfer tube and the plate shaped fin are connected by a mechanical pipe expansion method, which causes a problem that heat exchange efficiency is compromised because an air layer is present between the heat transfer tube and the plate shaped fin.
  • the flat tube 3 and the plate shaped fin 2 are connected by in-furnace brazing, heat resistance between the flat tube 3 and the plate shaped fin 2 becomes zero, thereby improving heat exchange efficiency.
  • the flat tube 3 is made of aluminum and the inside of the flat tube 3 is separated to form a plurality of passages 31 a as shown in Fig. 8 so that the refrigerant flows through the respective passages 31 a.
  • the flat tube 3 can increase the amount of refrigerant and a contact heat transfer area three times of those of the circular tube.
  • Fig. 9 is a view showing a conventional example that does not use a two-way branch pipe in a heat exchanger of three-line arrangement configuration.
  • the number of capillary tubes 40 can be reduced by combining the capillary tube 40, which is an outflow pipe of the first distribution device 20, with the two-way branch pipe 30 in the refrigerant distribution device 10.
  • the capillary tube 40 is mounted on an actual machine, installation space of the capillary tube 40 becomes compact.
  • cost can be reduced by reducing the number of the capillary tubes 40, and the actual machine can be inexpensively configured.
  • the angle ⁇ 1 between the arm 34 and the straight inflow section 35 is 90 degrees, the refrigerant two-phase flow vertically collides against the collision wall 34a, which faces the inflow section. Further, branch directions after collision are horizontal, and the refrigerant is not under the effect of gravity and can be uniformly distributed regardless of the amount of circulation. Since the straight inflow section 35 is formed by bulge-forming process, stable processing of the shape of 90 degrees can be performed for the angle ⁇ 1 .
  • the straight inflow section 35 is 10 mm or more, the refrigerant two-phase flow into the straight inflow section 35 can be allowed to vertically collide against the collision wall 34a as a stable annular flow, thereby preventing variation in refrigerant distribution and allowing for uniform distribution.
  • using the refrigerant distribution device 10 allows for uniform distribution of the two-phase flow of gas-liquid. Accordingly, specific heat exchange efficiency can be sufficiently performed in the heat exchanger 1.
  • Embodiment 2 is provided for further reducing the number of the capillary tubes 40.
  • the following description focuses on a part of Embodiment 2 that differs from Embodiment 1. Further, a modification example that is applied to the same configuration as that of Embodiment 1 is also applied to Embodiment 2.
  • Fig. 10 is a configuration diagram of the refrigerant distribution device according to Embodiment 2 of the present invention.
  • (a) is a front view
  • (b) is a cross sectional view taken along the line A-A of (a).
  • Fig. 11 is views showing a third distribution device in the refrigerant distribution device of Fig. 10 .
  • (a) is a front view of the refrigerant distribution device 10A
  • (b) is a side view of (a)
  • (c) is a bottom view of (a).
  • the refrigerant distribution device 10A of Embodiment 2 has a configuration that includes a plurality of two-way branch pipes 50 as a third distribution device in addition to the first distribution device 20 and the two-way branch pipes 30 as a second distribution device of Embodiment 1.
  • the two-way branch pipe 50 has the same structural characteristics as those of the two-way branch pipe 30 of Embodiment 1, and includes a U-bend section 51, which is formed by bending the circular tube in U-shape, and the straight inflow section 55.
  • the U-bend section 51 includes a connection 52 and two arms 53 and 54 extending from each end of the connection 52 in parallel to each other.
  • the straight inflow section 55 is formed by performing bulge-forming process on one of the two arms 53 and 54 (in this example, the arm 54) of the U-bend section 51.
  • the straight inflow section 55 of the two-way branch pipe 50 is connected to the capillary tube 40, and the two arms 53 and 54 are each connected to the straight inflow section 35 of the adjacent two-way branch pipe 30. Further, the two-way branch pipe 50 is also disposed so that the two arms 53 and 54 extend in a parallel direction as similar to the two-way branch pipe 30 of Embodiment 1.
  • the refrigerant distribution device 10A of Embodiment 2 which is configured as described above, can obtain the same effect as that of Embodiment 1 and the following effect. That is, since the two-way branch pipes 50 are disposed as a third distribution device, the number of capillary tubes 40 connected to the first distribution device 20 can be reduced to half of that of
  • the two-way branch pipe 50 serves as an inflow pipe for the refrigerant flowing out from the capillary tube 40, the same function as that of the two-way branch pipe 30 of Embodiment 1 is required. That is, the function of uniformly distributing the refrigerant out of the capillary tube 40 and allowing it to flow into the respective heat transfer tubes 3 is required. Since the two-way branch pipe 50 has the same configuration as that of the two-way branch pipe 30, the refrigerant out of the straight inflow section 35 of the two-way branch pipe 50 vertically collides against a collision wall that is a wall surface facing the straight inflow section 55 in the arm 54. Since branch directions after collision are horizontal, the refrigerant is not under the effect of gravity and can be uniformly distributed regardless of the amount of circulation.
  • Embodiment 3 is directed to a refrigerant distribution device that can adjust a distribution ratio of refrigerant.
  • the following description focuses on a part of Embodiment 3 that differs from Embodiment 1. Further, in Embodiment 3, a modification example that is applied to the same configuration as that of Embodiment 1 is also applied to Embodiment 3.
  • Fig. 12 is configuration diagrams of the second distribution device in the refrigerant distribution device according to Embodiment 3 of the present invention.
  • (a) is a front view of the second distribution device
  • (b) is a side view of (a).
  • the refrigerant distribution device of Embodiment 3 has the same configuration as that of Embodiment 1 except that a two-way branch pipe 30A is disposed instead of the two-way branch pipe 30.
  • the two-way branch pipe 30 of Embodiment 1 forms the angle ⁇ 1 of 90 degrees with respect to the straight inflow section 35 and the arm 34.
  • the two-way branch pipe 30A of Embodiment 3 has a configuration in which the angle ⁇ 1 is adjusted depending on a desired distribution ratio.
  • the angle ⁇ 1 is formed as the angle smaller than 90 degrees, the flow rate of the refrigerant flowing in the opening port A becomes larger than that of the opening port B, while when the angle ⁇ 1 is formed as the angle larger than 90 degrees, the flow rate of the refrigerant flowing in the opening port B becomes larger than that of the opening port A. Accordingly, the straight inflow section 35 that requires angle adjustment is formed by bulge-forming process as similar to Embodiment 1.
  • the angle ⁇ 1 can be reduced and the angle ⁇ 1 can be precisely formed at a predetermined angle.
  • the angle ⁇ 2 may be any angle as similar to Embodiment 1, 90 degrees is preferable in consideration of connection to the capillary tubes 40.
  • the two-way branch pipe 30A is connected to the first distribution device 20 at one end and the other end of the capillary tube 40 at the other end.
  • an air speed of an air sending fan that sends air to the heat exchanger 1 is not necessarily uniform across the entire surface of the heat exchanger 1, and air speed distribution is present.
  • Such air speed distribution or difference in the lengths of the refrigerant flow path for each of thermal paths may cause difference in thermal load of the paths. Accordingly, it is necessary that a larger amount of refrigerant flows into one of the paths connected to the opening port A and the opening port B that is, for example, having a faster air speed or a larger number of heat transfer tubes and a longer length of flow path. Therefore, the distribution ratio of refrigerant to the opening port A and the opening port B is determined based on the thermal load distribution of the paths in the heat exchanger 1, and thus the angle ⁇ 1 is determined.
  • the refrigerant flowing from the straight inflow section 35 collides against a surface facing the straight inflow section 35 with the angle ⁇ 1 and is then distributed into the arm 33 and the arm 34 while the flow rate is adjusted depending on an inclination angle ⁇ . Then, the refrigerant of distributed flow rate flows into the heat transfer tubes 3 of the heat exchanger 1 via the opening port A and the opening port B.
  • the number of capillary tubes 40 can be reduced as similar to Embodiment 1, and a refrigerant distribution device that can adjust a distribution ratio of refrigerant can be provided.
  • Embodiment 4 is also directed to a refrigerant distribution device that can adjust a distribution ratio of refrigerant as similar to Embodiment 3.
  • the following description focuses on a part of Embodiment 4 that differs from Embodiment 1. Further, a modification example that is applied to the same configuration as that of Embodiment 1 in Embodiment 3 is also applied to Embodiment 4.
  • Fig. 13 is configuration diagrams of the second distribution device in the refrigerant distribution device according to Embodiment 4 of the present invention.
  • (A) shows a configuration example of the two-way branch pipe 30B in which the distribution ratio at the opening port B is larger than that at the opening port A
  • (B) shows a configuration example of the two-way branch pipe 30B in which the distribution ratio at the opening port A is larger than that at the opening port B.
  • (a) is a front view of the two-way branch pipe 30B
  • (b) is a side view of (a).
  • Fig. 14 is an enlarged view of an essential part of Fig. 13(A) .
  • the refrigerant distribution device of Embodiment 4 has the same configuration as that of Embodiment 1 except that the two-way branch pipe 30B is disposed instead of the two-way branch pipe 30.
  • the two-way branch pipe 30B has an inwardly depressed recess 37 at a position adjacent to the collision wall 34a.
  • the remaining is the same as Embodiment 1 including the facts that the straight inflow section 35 is formed by bulge-forming process and that the angle ⁇ 2 can be any angle.
  • the recess 37 is formed at a position close to the opening port A with respect to the collision wall 34a in a tube axis direction of the U-bend section 31 as shown in Fig. 13(A) .
  • the recess 37 is formed at a position close to the opening port B with respect to the collision wall 34a in a tube axis direction of the U-bend section 31 as shown in Fig. 13(B) .
  • the recess 37 is not formed on the collision wall 34a, which faces the straight inflow section 35. Since the recess 37 is formed by using a press or punch, forming the recess 37 on the collision wall 34a may deform the straight inflow section 35. Accordingly, the two-way branch pipe 30B can be manufactured in a stable manner while preventing disadvantage of deformation by not providing the recess 37 on the collision wall 34a, which faces the straight inflow section 35.
  • the number of capillary tubes 40 can be reduced as similar to Embodiment 1, and a refrigerant distribution device that can adjust a distribution ratio of refrigerant can be provided.
  • the first distribution device 20 is described as a distributor in the above Embodiments 1 to 4, the invention is not limited thereto, and the first distribution device 20 may be a header 70 as shown in Fig. 15 . In that case, the same effect can be obtained.
  • the heat exchanger described in the above Embodiments and an air conditioning apparatus that uses the heat exchanger can achieve the above effects with any refrigerating machine oil such as mineral oil, alkylbenzene oil, ester oil, ether oil, and fluorine oil regardless of whether the refrigerant dissolves in the oil or not.
  • refrigerating machine oil such as mineral oil, alkylbenzene oil, ester oil, ether oil, and fluorine oil
  • Embodiments 1 to 4 are described as separate Embodiments, combination of Embodiments can be used as appropriate when Embodiments can be combined.
  • the two-way branch pipe 30 of Embodiment 2 shown in Fig. 10 can be replaced with the two-way branch pipe 30A of Embodiment 3 by combining Embodiment 2 and Embodiment 3.
  • the present invention can be used for a heat exchanger of a heat pump apparatus that is required to improve heat exchange efficiency and performance.
  • heat exchanger 1 heat exchanger 2 plate shaped fin 3 heat transfer tube (flat tube) 4 circular tube-flat tube joint 5 bend 6 gas header 10 refrigerant distribution device 10A refrigerant distribution device 20 first distribution device 30 two-way branch pipe (second distribution device) 30A two-way branch pipe (second distribution device) 30B two-way branch pipe (second distribution device) 31 U-bend section 31 a passage 32 connection 33 arm 34 arm 34a collision wall 35 straight inflow section 36 L-shaped pipe 37 recess 40 capillary tube 50 two-way branch pipe (third distribution device) 51 U-bend section 52 connection 53 arm 54 arm 55 straight inflow section 60 heat pump apparatus 61 compressor 62 condensor 63 expansion valve 64 evaporator 70 header 100 heat exchanger

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP13873009.8A 2013-01-22 2013-01-22 Distributeur de réfrigérant et dispositif de pompe à chaleur utilisant le distributeur de réfrigérant Withdrawn EP2955464A4 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/051146 WO2014115240A1 (fr) 2013-01-22 2013-01-22 Distributeur de réfrigérant et dispositif de pompe à chaleur utilisant le distributeur de réfrigérant

Publications (2)

Publication Number Publication Date
EP2955464A1 true EP2955464A1 (fr) 2015-12-16
EP2955464A4 EP2955464A4 (fr) 2016-11-09

Family

ID=51227057

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13873009.8A Withdrawn EP2955464A4 (fr) 2013-01-22 2013-01-22 Distributeur de réfrigérant et dispositif de pompe à chaleur utilisant le distributeur de réfrigérant

Country Status (4)

Country Link
US (1) US20150362222A1 (fr)
EP (1) EP2955464A4 (fr)
JP (1) JP6278904B2 (fr)
WO (1) WO2014115240A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3594591A4 (fr) * 2017-03-09 2020-03-11 Mitsubishi Electric Corporation Échangeur de chaleur et climatiseur

Families Citing this family (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6207624B2 (ja) * 2013-10-29 2017-10-04 三菱電機株式会社 熱交換器、及び、空気調和装置
US20160290691A1 (en) * 2013-11-14 2016-10-06 Nec Corporation Piping structure, cooling device including the same, and method for transporting refrigerant vapor
JP6329786B2 (ja) * 2014-03-13 2018-05-23 新晃工業株式会社 空調機の熱交換器
US10161652B2 (en) * 2014-04-04 2018-12-25 Mitsubishi Electric Corporation Air-conditioning apparatus
JP2016014504A (ja) * 2014-07-02 2016-01-28 三菱電機株式会社 熱交換器及びそれを備えた冷凍サイクル装置
US10156387B2 (en) * 2014-12-18 2018-12-18 Lg Electronics Inc. Outdoor device for an air conditioner
KR101694614B1 (ko) * 2014-12-18 2017-01-09 엘지전자 주식회사 공기 조화기
CN108291755B (zh) * 2015-12-01 2020-07-31 三菱电机株式会社 制冷循环装置
WO2018000662A1 (fr) * 2016-06-28 2018-01-04 海信科龙电器股份有限公司 Dérivation de réfrigérant et équipement de réfrigération
WO2018047330A1 (fr) * 2016-09-12 2018-03-15 三菱電機株式会社 Climatiseur
US10502468B2 (en) * 2016-10-05 2019-12-10 Johnson Controls Technology Company Parallel capillary expansion tube systems and methods
US11098927B2 (en) * 2016-12-21 2021-08-24 Mitsubishi Electric Corporation Distributor, heat exchanger and refrigeration cycle apparatus
DE102017109065B4 (de) * 2017-04-27 2019-06-06 Miele & Cie. Kg Verbindungssystem zur gas- und fluiddichten Verbindung eines Verflüssigers einer Wärmepumpe mit einem Verdampfer der Wärmepumpe
CN107279448B (zh) * 2017-06-28 2022-12-27 中绅科技(广东)有限公司 双节流预冷保鲜冰淇淋机冷控装置及冷控方法及冰淇淋机
CN110095008A (zh) * 2018-01-27 2019-08-06 浙江盾安热工科技有限公司 一种换热器转接装置
US11656013B2 (en) 2018-06-05 2023-05-23 Mitsubishi Electric Corporation Distributor and refrigeration cycle apparatus
JP6641542B1 (ja) * 2019-03-05 2020-02-05 三菱電機株式会社 熱交換器及び冷凍サイクル装置
JP7137092B2 (ja) * 2021-01-22 2022-09-14 ダイキン工業株式会社 熱交換器
JP6956297B1 (ja) * 2021-08-03 2021-11-02 日立ジョンソンコントロールズ空調株式会社 空気調和機及び熱交換器
CN113932488A (zh) * 2021-09-19 2022-01-14 青岛海尔空调器有限总公司 换热器、制冷循环系统、空调器
WO2023152789A1 (fr) * 2022-02-08 2023-08-17 三菱電機株式会社 Échangeur de chaleur
WO2023188386A1 (fr) * 2022-03-31 2023-10-05 三菱電機株式会社 Échangeur de chaleur et climatiseur

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS45677Y1 (fr) * 1963-07-12 1970-01-12
US3350905A (en) * 1963-12-21 1967-11-07 Agency Ind Science Techn Liquid pressure bulge forming apparatus
US4089368A (en) * 1976-12-22 1978-05-16 Carrier Corporation Flow divider for evaporator coil
JPS5613692U (fr) * 1979-07-06 1981-02-05
US4483156A (en) * 1984-04-27 1984-11-20 The Trane Company Bi-directional variable subcooler for heat pumps
JPH03195874A (ja) * 1989-12-26 1991-08-27 Matsushita Refrig Co Ltd 分流器
JP3606732B2 (ja) * 1997-07-04 2005-01-05 ユニオン空調工業株式会社 冷媒管用分岐継手
JPH11159917A (ja) * 1997-11-28 1999-06-15 Goh Shoji Co Inc 冷媒分流器とその製造方法
JPH11230637A (ja) * 1998-02-16 1999-08-27 Mitsubishi Heavy Ind Ltd 空気調和機
JP2001263863A (ja) * 2000-03-24 2001-09-26 Matsushita Electric Ind Co Ltd 空気調和機
JP3842999B2 (ja) * 2001-11-15 2006-11-08 三洋電機株式会社 熱交換器の冷媒分流装置及びそれを用いた空気調和装置
JP4205885B2 (ja) * 2002-03-20 2009-01-07 東芝キヤリア株式会社 熱交換器
US7174919B2 (en) * 2003-10-20 2007-02-13 Metaldyne Company, Llc Flow redirection member and method of manufacture
JP2006097987A (ja) * 2004-09-29 2006-04-13 Daikin Ind Ltd 三方分岐管及びこれを用いたフィンチューブ型熱交換器
JP2008121984A (ja) 2006-11-13 2008-05-29 Matsushita Electric Ind Co Ltd 熱交換器ユニット
US7597137B2 (en) * 2007-02-28 2009-10-06 Colmac Coil Manufacturing, Inc. Heat exchanger system
JP4982401B2 (ja) * 2008-02-06 2012-07-25 日立アプライアンス株式会社 空気調和機の室外機
ES2722223T3 (es) * 2009-06-19 2019-08-08 Daikin Ind Ltd Unidad de aire acondicionado montada en el techo
JP2011144968A (ja) * 2010-01-13 2011-07-28 Toshiba Carrier Corp 冷凍サイクル装置
JP4715963B1 (ja) * 2010-02-15 2011-07-06 ダイキン工業株式会社 空気調和機用熱交換器
CN203349584U (zh) * 2010-04-28 2013-12-18 大金工业株式会社 热交换装置及其使用的连接管
US20120145246A1 (en) * 2010-12-13 2012-06-14 Heatcraft Refrigeration Products Llc System and method for distribution of refrigerant to a plurality of heat exchanger evaporator coil circuits
JP5171983B2 (ja) * 2011-04-15 2013-03-27 三菱電機株式会社 熱交換器及び冷凍サイクル装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3594591A4 (fr) * 2017-03-09 2020-03-11 Mitsubishi Electric Corporation Échangeur de chaleur et climatiseur
US11112149B2 (en) 2017-03-09 2021-09-07 Mitsubishi Electric Corporation Heat exchanger and air-conditioning apparatus

Also Published As

Publication number Publication date
EP2955464A4 (fr) 2016-11-09
US20150362222A1 (en) 2015-12-17
JP6278904B2 (ja) 2018-02-14
JPWO2014115240A1 (ja) 2017-01-19
WO2014115240A1 (fr) 2014-07-31

Similar Documents

Publication Publication Date Title
EP2955464A1 (fr) Distributeur de réfrigérant et dispositif de pompe à chaleur utilisant le distributeur de réfrigérant
US10571205B2 (en) Stacking-type header, heat exchanger, and air-conditioning apparatus
US9976820B2 (en) Stacking-type header, heat exchanger, and air-conditioning apparatus
US9651317B2 (en) Heat exchanger and air conditioner
US10107570B2 (en) Stacking-type header, heat exchanger, and air-conditioning apparatus
US10088247B2 (en) Stacking-type header, heat exchanger, and air-conditioning apparatus
EP2853843A1 (fr) Distributeur de fluide réfrigérant, et échangeur de chaleur équipé d'un distributeur de fluide réfrigérant
US20160169595A1 (en) Stacking-type header, heat exchanger, and air-conditioning apparatus
EP3037773A1 (fr) Échangeur de chaleur, climatiseur, dispositif de cycle de réfrigération, et procédé de fabrication d'un échangeur de chaleur
EP3290851B1 (fr) Collecteur stratifié, échangeur de chaleur et climatiseur
EP2851641A1 (fr) Échangeur de chaleur, unité intérieure, et dispositif de cycle de réfrigération
US10041710B2 (en) Heat exchanger and air conditioner
CN113574342A (zh) 热交换器及制冷循环装置
WO2016121119A1 (fr) Échangeur de chaleur et dispositif à cycle de réfrigération
JP6656368B2 (ja) フィンチューブ型熱交換器、および、このフィンチューブ型熱交換器を備えたヒートポンプ装置
JP2016148480A (ja) 熱交換器
JP6766980B1 (ja) 熱交換器及び熱交換器を搭載した空気調和装置
JP2020165578A (ja) 熱交換器分流器
WO2023199466A1 (fr) Échangeur de chaleur et dispositif de climatisation l'incluant
WO2022215164A1 (fr) Échangeur de chaleur et climatiseur
CN111587350B (zh) 热交换器、室外单元及制冷循环装置
KR20130000896U (ko) 냉매의 유동 패턴을 균일하게 하기 위한 증발기
KR101336372B1 (ko) 냉매 시스템

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20150624

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20161007

RIC1 Information provided on ipc code assigned before grant

Ipc: F28F 9/26 20060101ALI20160930BHEP

Ipc: F25B 39/02 20060101ALI20160930BHEP

Ipc: F28D 1/047 20060101ALI20160930BHEP

Ipc: F25B 41/00 20060101AFI20160930BHEP

Ipc: F25B 13/00 20060101ALI20160930BHEP

Ipc: F28F 9/22 20060101ALI20160930BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20200305

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20230801