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WO2019215825A1 - Échangeur de chaleur, procédé de fabrication de section de communication, unité intérieure, unité extérieure et climatiseur - Google Patents

Échangeur de chaleur, procédé de fabrication de section de communication, unité intérieure, unité extérieure et climatiseur Download PDF

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Publication number
WO2019215825A1
WO2019215825A1 PCT/JP2018/017872 JP2018017872W WO2019215825A1 WO 2019215825 A1 WO2019215825 A1 WO 2019215825A1 JP 2018017872 W JP2018017872 W JP 2018017872W WO 2019215825 A1 WO2019215825 A1 WO 2019215825A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
communication
heat exchanger
gas
longitudinal direction
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.)
Ceased
Application number
PCT/JP2018/017872
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English (en)
Japanese (ja)
Inventor
佐々木　重幸
禎夫 関谷
遠藤　剛
高藤　亮一
法福　守
大木　長斗司
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.)
Hitachi Johnson Controls Air Conditioning Inc
Original Assignee
Hitachi Johnson Controls Air Conditioning Inc
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 Hitachi Johnson Controls Air Conditioning Inc filed Critical Hitachi Johnson Controls Air Conditioning Inc
Priority to PCT/JP2018/017872 priority Critical patent/WO2019215825A1/fr
Priority to JP2020517666A priority patent/JP6913826B2/ja
Publication of WO2019215825A1 publication Critical patent/WO2019215825A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators
    • 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

Definitions

  • the present invention relates to a heat exchanger, a method for manufacturing a communication part, an indoor unit, an outdoor unit, and an air conditioner.
  • Patent Document 1 In the outdoor heat exchanger, one end of each flat tube is connected to the first header collecting pipe.
  • the lower space of the first header collecting pipe includes an upper horizontal partition plate and a lower horizontal partition plate.
  • the vertical partition plate divides the chamber into three communication chambers and a single mixing chamber, which are arranged in a vertical direction, and a plurality of flat tubes are connected to each communication chamber.
  • the mixing chamber is connected to the first communication chamber via the communication through hole of the lower horizontal partition plate, and the vertical partition plate (through the communication through hole). It communicates with the second communication chamber and communicates with the third communication chamber via the communication through hole of the upper lateral partition plate ”(see summary).
  • Patent Document 1 intends equalizing the dryness of the refrigerant
  • Patent Document 1 does not disclose any technique for improving the heat exchange efficiency of the heat exchanger by changing the supply amount of the refrigerant with a flat tube. Then, this invention makes it a subject to change the supply amount of a refrigerant
  • a heat exchanger includes a pair of headers, a plurality of headers arranged in the longitudinal direction of the header, and heat transfer tubes each having both ends connected to the headers, A plurality of fins connected to each heat transfer tube and arranged in the longitudinal direction of the heat transfer tube, and an inflow side header serving as a refrigerant inflow side from the outside of the pair of headers is an inlet of the refrigerant
  • a plurality of gas-liquid mixing sections into which a gas-liquid two-phase refrigerant flows and a plurality of the inflow-side headers are partitioned in the longitudinal direction, and the gas-liquid mixing section is also partitioned into one or continuous
  • the header inner space connected to the plurality of heat transfer tubes arranged in parallel to each other, the plurality of communication tubes communicating the different header inner space and the gas-liquid mixing unit, and the gas-liquid mixing unit. Is provided in each communication pipe Via a communicating pipe having an opening for guiding the refriger
  • the heat exchange efficiency of the heat exchanger can be improved by changing the amount of refrigerant supplied by the heat transfer tube.
  • FIG. 1B is a cross-sectional view taken along line AA in FIG. 1A. It is the front view which arranged and illustrated two communicating pipes of the heat exchanger which concerns on Example 1 of this invention. It is the front view which arranged and illustrated two communicating pipes in other examples of the heat exchanger concerning Example 1 of the present invention. It is the front view which arranged and illustrated two communicating pipes in other examples of the heat exchanger concerning Example 1 of the present invention. 1 is a system diagram of an air conditioner according to Embodiment 1 of the present invention. It is the perspective view which permeate
  • FIG. 7A It is a cross-sectional view of the indoor unit of the air conditioner according to the first embodiment of the present invention. It is the front view which arranged and illustrated two communicating pipes of the heat exchanger which concerns on Example 2 of this invention. It is the front view which arranged and illustrated two communicating pipes in other examples of the heat exchanger concerning Example 2 of the present invention. It is the front view which arranged and illustrated two communicating pipes in other examples of the heat exchanger concerning Example 2 of the present invention. It is a longitudinal cross-sectional view of the gas-liquid mixing part part in the inflow side header of the heat exchanger which concerns on Example 3 of this invention. It is BB sectional drawing of FIG. 7A. FIG. 7B is another example of the BB cross-sectional view of FIG. 7A. It is a longitudinal cross-sectional view of the gas-liquid mixing part in the inflow side header of the heat exchanger which concerns on Example 3 of this invention, and the part of the upper part.
  • FIG. 1A is a plan view of a heat exchanger 1 according to Embodiment 1 of the present invention. Since the heat exchanger 1 has a certain length in the left-right direction in FIG. 1A, a part of the left-right longitudinal direction is notched.
  • the heat exchanger 1 includes a pair of inflow side headers 3a and outflow side headers (headers) 3b.
  • the inflow side header 3a serves as an inlet for the refrigerant from the outside
  • the outflow side header 3b serves as an outlet for the refrigerant to the outside.
  • the inflow side header 3a and the outflow side header 3b may be simply referred to as headers.
  • the inflow side header 3a and the outflow side header 3b are both long cylindrical members.
  • the inflow side header 3a is shown by the longitudinal cross section, and the outflow side header 3b has shown only the outer surface.
  • Inflow side header 3a and outflow side header 3b are generally arranged at a position where the lower end side (the gas-liquid mixing portion 41 side described later) is lower than the upper end side in FIG. is not.
  • the heat transfer tube 19 is a flat heat transfer tube that is made of a metal member such as aluminum and is flat in the longitudinal direction and is arranged in the longitudinal direction of the headers 3a and 3b.
  • the step pitch is Pd in the example of FIG. 1A.
  • the longitudinal direction of the heat transfer tube 19 is substantially perpendicular to the longitudinal direction of the headers 3a and 3b.
  • Each heat transfer tube 19 is connected to each header 3a, 3b at both ends, and the refrigerant flows in from the inflow side header 3a and flows in the direction of arrow a in FIG. 1A. And the refrigerant
  • a route through which the refrigerant flows out from the outflow side header 3b is not shown, the route can be connected to the outflow side header 3b in various forms.
  • the fin 2 is made of a thin plate-like metal member such as aluminum, and expands the heat transfer area of each heat transfer tube 19.
  • the fins 2 are connected to the heat transfer tubes 19, and a plurality of the fins 2 are arranged at regular intervals in the longitudinal direction of the heat transfer tubes 19, for example.
  • the fin pitch in that case is Pf as shown in FIG. 1A.
  • the fin 2 is joined to the heat transfer tube 19 by brazing so as to be able to transfer heat.
  • a plurality of holes for inserting the heat transfer tubes 19 are formed in advance at a step pitch Pd.
  • the heat transfer tube 19 is formed, for example, by a plurality of multi-hole flow paths (not shown) in a flat cross section by extrusion.
  • the fin 2 is provided with a plurality of cuts at equal intervals on the side end in the longitudinal direction, and each heat transfer tube 19 is inserted into the cut, or a plurality of through holes arranged in the longitudinal direction are formed in each fin 2,
  • the heat transfer tube 19 can be inserted into the through-hole to be formed integrally with the heat transfer tube 19 ⁇ .
  • each heat transfer tube 19 is inserted into the hole of the header 3 and, further, the fin 2 is attached to the heat transfer tube 19 in a temporarily assembled state in the furnace.
  • the heat exchanger 1 may be manufactured by batch brazing, or the heat exchanger 1 may be manufactured by brazing partially with a torch.
  • the joining of the heat transfer tube 19 and the fin 2 is a method in which the heat transfer tube 19 is brought into close contact with the heat transfer tube 19 by pressurizing the inside of the multi-hole flow path with a liquid pressure or a gas pressure instead of the above-described brazing. May be taken.
  • corrugated (corrugated) fins may be inserted between the heat transfer tubes 19.
  • the lower end side of the inflow side header 3a in FIG. 1A is partitioned by a partition plate 31a.
  • the space above the partition plate 31a of the inflow side header 3a is partitioned into, for example, equal intervals by a plurality of partition plates 31b in the example of FIG. 1A. That is, the inside of the inflow side header 3a is divided into, for example, five sections by the partition plates 31a and 31b.
  • the space below the inflow side header 3a partitioned by the partition plate 31a is partitioned by the partition plate 31b above the partition plate 31a, which is the gas-liquid mixing unit 41, and above the inflow side header 3a.
  • the two spaces constitute header inner spaces 32 to 35.
  • the gas-liquid mixing part 41 can be implemented variously in which position of the longitudinal direction of the inflow side header 3a the gas-liquid mixing part 41 is brought.
  • the gas-liquid mixing part 41 may be arranged at an intermediate position in the longitudinal direction of the inflow-side header 3a, and the header inner spaces 32 to 35 may be distributed above and below.
  • Each of the header inner spaces 32 to 35 is connected to one or a plurality of continuously arranged heat transfer tubes 19 (four continuously arranged in the example of FIG. 1A).
  • the number of the heat transfer tubes 19 connected to each of the header inner spaces 32 to 35 may be different.
  • An inlet pipe 36 serving as a refrigerant inlet is connected to the lower side of the gas-liquid mixing unit 41.
  • a gas-liquid two-phase refrigerant L flows from the inlet pipe 36 from the outside.
  • Reference numeral 42 indicates a gas-liquid interface of the refrigerant L.
  • the gas-liquid mixing unit 41 and the header inner spaces 32 to 35 are connected by communication pipes 5a to 5d, respectively.
  • the communication pipes 5a to 5d are simply illustrated and described as the communication pipe 5. That is, the communication pipes 5a to 5d pass through the partition plate 31a. Further, three of the communication pipes 5a to 5d also penetrate one or a plurality of partition plates 31b.
  • the communication pipes 5a to 5d are joined to and supported by the through holes of the partition plates 31a and 31b.
  • the joints between the communication pipes 5a to 5d and the partition plates 31a and 31b are sealed so that the refrigerant L does not leak between the adjacent header inner spaces 32 to 35 or between the header inner space 35 and the gas-liquid mixing portion 41. .
  • FIG. 1A only schematically shows that the plurality of communication pipes 5 communicate with different header inner spaces 32 to 35, and does not show the arrangement of the communication pipes 5 accurately. Absent.
  • FIG. 1B is a cross-sectional view taken along line AA of FIG. 1A.
  • FIG. 2A is a front view illustrating two communication pipes 5a and 5c arranged side by side. In FIG. 2A, the communication pipes 5b and 5d are not shown. Moreover, although the communication pipes 5a and 5c in FIG. 2A are actually different in length, in FIG. 2A, the same length is shown for convenience (the same applies hereinafter).
  • the communication pipes 5a to 5d located in the gas-liquid mixing part 41 are respectively provided with openings 5a1 to 5d1 on the side parts.
  • Each of the openings 5a1 to 5d1 serves as an inlet to each of the communication pipes 5a to 5d that guides the refrigerant L in the gas-liquid mixing unit 41 to each of the header inner spaces 32 to 35 via the communication pipes 5a to 5d. .
  • the gas refrigerant in the gas-liquid mixing unit 41 is sucked into the openings 5a1 to 5d1, and the liquid refrigerant in the gas-liquid mixing unit 41 is also sucked into the openings 5a1 to 5d1.
  • the areas of the openings 5a1 to 5d1 include different ones among the communication pipes 5a to 5d. That is, the openings 5a1 to 5d1 in FIG. 2A are through holes provided in the same number in each of the communication pipes 5a to 5d. The same number of through-holes are formed in the communication pipes 5a to 5d in the longitudinal direction. In each of the communication pipes 5a to 5d, the first through hole from the top has the same center in each of the communication pipes 5a to 5d, and the second through hole from the top has the center in each of the communication pipes 5a to 5d. They are the same height, and so on.
  • the through holes in the same order counted from the top or the bottom are located at the same height in each of the communication pipes 5a to 5d.
  • the difference between the openings 5a1 to 5d1 is that the sizes of the through holes are different depending on the communication pipes 5a to 5d.
  • the amount of the refrigerant L that flows in per unit time can be changed in each of the communication pipes 5a to 5d.
  • the size of the through hole, which is the opening 5a1 of the communication pipe 5a is maximized (diameter size G5a), and the amount of the refrigerant L flowing in per unit time is set to the communication pipes 5a to 5d. It is the largest among them. Further, the size of the through-hole which is the opening 5c1 of the communication pipe 5c is minimized (diameter size G5c), and the amount of the refrigerant L flowing in per unit time is minimized among the communication pipes 5a to 5d.
  • the size of the through holes which are the openings 5b1 and 5d1 of the communication pipes 5b and 5d, is set to an intermediate size thereof (diameter sizes G5b and G5d), and the amount of the refrigerant L flowing in per unit time is communicated.
  • An intermediate value is set in the tubes 5a to 5d.
  • the example of FIG. 2A shows an example in which each through hole is a round hole
  • the shape of the through hole can be various shapes such as a square shape and a triangular shape.
  • the openings 5a1 to 5d1 are all directed toward the central axis of the gas-liquid mixing unit 41 that is cylindrical in the example of FIG. 1B. As a result, the opening 5d1 of the communication pipe 5d faces away from the refrigerant inflow direction from the inlet pipe 36.
  • FIG. 2B is a front view illustrating two communication pipes 5a and 5c in another example. Also in FIG. 2B, illustration of the communication pipes 5b and 5d is omitted.
  • the example of FIG. 2B is different from the example of FIG. 2A in that the openings 5a1 to 5d1 of the communication pipes 5a to 5d are long holes in the longitudinal direction of the communication pipes 5a to 5d.
  • FIG. 2C is a front view illustrating two communication pipes 5a and 5c which are modifications of FIG. 2B side by side. Also in FIG. 2C, the communication pipes 5b and 5d are not shown. FIG. 2C differs from FIG. 2B in that a stopper 53 is fitted into the lower end portion of each communication pipe 5a-5d, which is a tubular member, and the lower end parts of the respective communication pipes 5a-5d are closed. . That is, in the example of FIG. 2B, the lower ends of the communication pipes 5a to 5d are open, but in the example of FIG. 2C, the refrigerant is distributed by flowing the refrigerant L only from the openings 5a1 to 5d1. . In the example of FIG.
  • each opening is merely an example (the same applies to each of the following embodiments). Which opening is widened and which opening is narrowed vary depending on the model of the air conditioner 100 and other conditions.
  • FIG. 3 is a system diagram showing the overall configuration of the air conditioner 100 to which the heat exchanger 1 is applied.
  • the air conditioner 100 includes a compressor 8, a four-way valve 9, an indoor heat exchanger (first heat exchanger) 101, an expansion valve 103, an outdoor heat exchanger (second heat exchanger) 106, and the like. Are connected by a pipe 121.
  • the indoor heat exchanger 101 and the indoor fan 102 are provided in the indoor unit 108.
  • the compressor 8, the four-way valve 9, the expansion valve 103, the outdoor heat exchanger 106, and the outdoor fan 107 are provided in the outdoor unit 105.
  • the expansion valve 103 may be provided in the indoor unit 108 or in both the indoor unit 108 and the outdoor unit 105.
  • the compressor 8 is a device that compresses a low-temperature and low-pressure gas refrigerant by driving a compressor motor (not shown) and discharges it as a high-temperature and high-pressure gas refrigerant.
  • the four-way valve 9 is a valve that switches the flow path of the refrigerant according to the operation mode of the air conditioner 100.
  • the expansion valve 103 is a valve that decompresses the refrigerant condensed in the “condenser” (one of the outdoor heat exchanger 106 and the indoor heat exchanger 101 according to the type of air conditioning operation). The refrigerant decompressed in the expansion valve 103 is guided to an “evaporator” (the other of the outdoor heat exchanger 106 and the indoor heat exchanger 101 according to the type of air conditioning operation).
  • the heat exchanger 1 is applied to the indoor heat exchanger 101.
  • the indoor heat exchanger 101 is a heat exchanger that performs heat exchange between the refrigerant flowing through the heat transfer tube 19 and the indoor air (air in the air-conditioning target space) sent from the indoor fan 102.
  • the indoor fan 102 is a fan that sends indoor air into the indoor heat exchanger 101, and is installed in the vicinity of the indoor heat exchanger 101.
  • the heat exchanger 1 is applied to the outdoor heat exchanger 106.
  • the outdoor heat exchanger 106 is a heat exchanger that exchanges heat between the refrigerant flowing through the heat transfer tube 19 and outdoor air sent from the indoor fan 102.
  • the outdoor fan 107 is a fan that sends outdoor air to the outdoor heat exchanger 106, and is installed in the vicinity of the outdoor heat exchanger 106.
  • the heat exchanger 1 may be used for only one of the indoor heat exchanger 101 and the outdoor heat exchanger 106, and the other may be a heat exchanger having another configuration.
  • the refrigeration cycle of the heat pump type air conditioner 100 will be described taking heating operation as an example.
  • the flow of the refrigerant during the heating operation is indicated by a solid arrow 60.
  • the compressor 8 is a device that compresses a gas refrigerant, and the refrigerant that has reached a high temperature and a high pressure in the compressor 8 is led to the indoor heat exchanger 101 (condenser) in the indoor unit 108 via the four-way valve 9. It is burned.
  • coolant which flows through the inside of the heat exchanger tube 19 (FIG. 1A) of the indoor heat exchanger 101 radiates heat to the indoor air supplied from the indoor fan 102, so that the room is warmed.
  • the heat-deprived gas refrigerant is gradually liquefied, and from the outlet of the indoor heat exchanger 101, the supercooled liquid refrigerant having a temperature lower by about several degrees C. than the saturation temperature flows out.
  • the liquid refrigerant flowing out of the indoor unit 108 becomes a gas-liquid two-phase refrigerant in a low temperature / low pressure state by an expansion action when passing through the expansion valve 103.
  • This low-temperature, low-pressure gas-liquid two-phase refrigerant is guided to the outdoor heat exchanger 106 (evaporator) in the outdoor unit 105.
  • the refrigerant is gasified and returned to the compressor 8 in a state where the degree of superheat is increased by about several degrees Celsius.
  • the heating operation of the air conditioner 100 is realized by the series of refrigeration cycles described above.
  • the flow of the refrigerant during the cooling operation is indicated by a broken line arrow 61.
  • the four-way valve 9 is switched to form a refrigeration cycle in which the refrigerant circulates in the direction of the broken line arrow 61.
  • the indoor heat exchanger 101 acts as an evaporator
  • the outdoor heat exchanger 106 acts as a condenser.
  • the cooling operation of the air conditioner 100 is realized.
  • FIG. 4 is a perspective view illustrating the interior of the outdoor unit 105. 4 and 5, the heat transfer tube 19 and the like are not specifically illustrated (see FIG. 1A and the like for the heat transfer tube 19 and the like).
  • the outdoor air is taken into the outdoor unit 105 by driving the outdoor fan 107, and this outdoor air passes through the outdoor heat exchanger 106 (heat exchanger 1), so that heat exchange between the refrigerant L and the outdoor air is achieved.
  • the amount of outside air that passes through per unit time is not uniform in each heat transfer tube 19 in which the horizontal direction is the length direction and many pipes are arranged in the vertical direction.
  • the flow rate V2 of the outside air flowing in at an intermediate height of the outdoor unit 105 is the fastest, and then the flow rate V1 of the outdoor air flowing into the upper part of the outdoor unit 105 is fast and flows into the lower part of the outdoor unit 105.
  • the flow rate V3 of the outside air is the slowest. That is, “V2> V1> V3”.
  • the sizes of the openings 5b1 and 5d1 of the communication pipes 5a to 5d corresponding to the header inner spaces 32 to 35 to which the heat transfer pipes 19 are connected are set to the flow velocity V1 to Change according to V3.
  • the opening of the communication pipe 5 connected to the header inner space corresponding to the heat transfer pipe 19 through which the outside air passes at the flow velocity V2 has a relatively large area.
  • the opening of the communication pipe 5 connected to the header inner space corresponding to the heat transfer pipe 19 through which the outside air passes at the flow velocity V3 has a relatively narrow area.
  • the openings 5a1 to 5d1 of the communication pipes 5a to 5d have a large area, the pressure loss of the part decreases, so that a large amount of gas refrigerant flows through the communication pipes.
  • the outdoor heat exchanger 106 heat exchanger 1
  • the liquid refrigerant that plays a role acts on the flow of the gas refrigerant, and flows in a large amount of the communication pipe through which the gas refrigerant flows. Therefore, it is possible to adjust the distribution amount of the liquid refrigerant by changing the opening areas of the openings 5a1 to 5d1 with each other, and also to adjust the distribution amount of the liquid refrigerant flowing into the header inner spaces 32 to 35.
  • FIG. 5 is a cross-sectional view of the indoor unit 108.
  • the indoor heat exchanger 101 includes three indoor heat exchangers 101a to 101c (all of which are heat exchangers 1).
  • the indoor fan 102 is cylindrical and has a longitudinal direction perpendicular to the paper surface of FIG.
  • the indoor heat exchangers 101a to 101c are also arranged so that the longitudinal direction thereof is along the longitudinal direction of the indoor fan 102, and the indoor fans 102 are covered by the three indoor heat exchangers 101a to 101c.
  • the indoor air is taken from outside the indoor heat exchangers 101a to 101c and passed through the indoor heat exchangers 101a to 101c, and the air is passed through the outlet 110 as indicated by an arrow c. To blow out.
  • the flow rates of the indoor air flowing through the heat transfer tubes 19 are different as in the example of FIG.
  • the indoor heat exchangers 101b and 101c since the heat transfer tube 19 on the side close to the inlet pipe 36 is close to the indoor fan 102, the flow rate of indoor air is relatively high, and the heat transfer pipe 19 on the side far from the inlet pipe 36 is indoors. Since it is far from the fan 102, it can be considered that the flow rate of the indoor air is relatively slow.
  • the indoor heat exchangers 101b and 101c may become an obstacle in the vicinity of the indoor heat exchangers 101b and 101c, and the flow rate of indoor air may be relatively slow.
  • the indoor heat exchangers 101b and 101c do not get in the way and the flow rate of the indoor air can be relatively high.
  • a relatively large amount of refrigerant L is supplied to the heat transfer tubes 19 that are considered to have a large amount of air per unit time to pass (a heat load is partially large).
  • a relatively small amount of refrigerant L can be supplied to the heat transfer tube 19, which is considered to have a small amount of air per unit time to pass (the heat load is partially small).
  • the gas-liquid mixing part 41 is arranged at one end (lower end) of the inflow side header 3a, and the header internal spaces 32 to 35 are arranged on the other end side (upper side).
  • the gas-liquid interface 42 is at a substantially constant water level as a whole when viewed at a certain moment. Therefore, the refrigerant L supplied from the gas-liquid mixing unit 4 to the header inner spaces 32 to 35 can make the gas refrigerant and the liquid refrigerant substantially uniform.
  • the gas-liquid interface 42 reaches the openings 5a1 to 5d1 that are the third through holes from the top to the openings 5a1 to 5d1 that are the second through holes from the top.
  • the flow rate of the refrigerant L flowing into the communication pipes 5a to 5d changes suddenly.
  • the gas-liquid interface 42 when the gas-liquid interface 42 is at an intermediate position between the openings 5a1 to 5d1 that are the third through holes from the top and the openings 5a1 to 5d1 that are the second through-holes from the top, the gas-liquid interface 42 is The flow rate of the refrigerant L does not change when it is in the openings 5a1 to 5d1, which are the third through holes. At this time, the flow rate of the refrigerant L flowing into the communication pipes 5a to 5d when the gas-liquid interface 42 is in the openings 5a1 to 5d1, which are the third through holes from the top, is obtained. These relationships occur in all through holes that are adjacent to each other in the vertical direction. That is, in the example of FIG.
  • the amount of refrigerant L sucked into the communication pipes 5a to 5d from the openings 5a1 to 5d1 generated by the upper and lower sides of the gas-liquid interface 42 (the same applies to the distribution amounts of gas refrigerant and liquid refrigerant). Can be changed to
  • the openings 5a1 to 5d1 are long holes whose longitudinal direction is the longitudinal direction of the communication pipes 5a to 5d. Therefore, the amount of refrigerant L sucked into the communication pipes 5a to 5d from the openings 5a1 to 5d1 varies even if the gas-liquid interface 42 is slightly up and down. That is, in the example of FIG. 2B, the amount of refrigerant L sucked into the communication pipes 5a to 5d from the openings 5a1 to 5d1 generated by the upper and lower sides of the gas-liquid interface 42 (the distribution amount of gas refrigerant and liquid refrigerant is the same) is stepless. Can be changed. In the example of FIG.
  • the inlet of the refrigerant L to the communication pipes 5a to 5d can be limited to the openings 5a1 to 5d1. Further, as shown in FIG. 1B, since the opening 5d1 faces away from the flow path into which the refrigerant L flows in the inlet pipe 36, the excessive flow of the refrigerant L only into the opening 5d1 can be suppressed. it can.
  • FIG. 6A is a front view illustrating two communication pipes 5a and 5c in the second embodiment side by side.
  • members and the like common to the first embodiment are denoted by the same reference numerals as those in the first embodiment, and detailed description thereof is omitted.
  • the second embodiment is technically different from the first embodiment in the configuration of the openings 5a1 to 5d1. That is, in the example of FIG. 2A, the areas of the openings 5a1 to 5d1 are changed by changing the areas (diameter sizes) of the through holes which are the openings 5a1 to 5d1. On the other hand, in the example of FIG. 6A, the areas (diameter size) of the through holes which are the openings 5a1 to 5d1 are the same, and the areas of the openings 5a1 to 5d1 are changed by changing the number of through holes. ing.
  • the through hole on the most gas phase refrigerant side (uppermost part) in the gas-liquid mixing part 41 is at the same height in the longitudinal direction of the inflow side header 3a. That is, the communication pipe with relatively few through holes has a region where no through hole is provided on the lower side of the communication pipe, like the communication pipe 5c in FIG. 6A. That is, the number of through holes is different on the liquid refrigerant side (lower side) in the gas-liquid mixing unit 41.
  • the length from the uppermost through hole to the lowermost through hole is long with the length of A2 in the communication pipe 5a, whereas the length of A1 in the communication pipe 5c. It is shorter.
  • FIG. 6B is a front view illustrating two communication pipes 5a and 5c side by side in another example.
  • the second embodiment is technically different from the first embodiment with respect to FIG. 6B in the configuration of the openings 5a1 to 5d1. That is, in the example of FIG. 2B, the area of the openings 5a1 to 5d1 is changed by changing the width of the long holes which are the openings 5a1 to 5d1.
  • the areas of the openings 5a1 to 5d1 are changed by changing the length of the long holes which are the openings 5a1 to 5d1.
  • the length of the long hole is B2 and long in the communication pipe 5a, whereas it is B1 and short in the communication pipe 5c.
  • one end of the longest gas-phase refrigerant side (uppermost) long hole in the gas-liquid mixing unit 41 is at the same position in the longitudinal direction of the inflow side header 3a. That is, the communication pipe having a relatively short long hole has a region where no long hole is provided on the lower side of the communication pipe, like the communication pipe 5c in FIG. 6B. That is, the position of the other end of the long hole is different on the liquid-phase refrigerant side (lower side) in the gas-liquid mixing unit 41.
  • FIG. 6C is an example in which the plug 53 is provided in the example of FIG. 6B as in the example of FIG. 2C. In the example of FIG. 6A, the stopper 53 may be provided.
  • the communication pipes 5a to 5d in FIG. 6B it is sufficient to form long holes of the same width regardless of the length, and it is not necessary to change the width of the long holes between the communication pipes 5a to 5d.
  • the manufacture of the tubes 5a to 5d is easy.
  • the width of the long hole is changed as shown in FIG. 2B, whereas the length of the long hole is changed in FIG. 6B, so that there is a large difference in the area of the openings 5a1 to 5d1 between the communication pipes 5a to 5d. Becomes easy. Therefore, it is effective when there is a large difference in the inflow amount of the refrigerant L between the communication pipes 5a to 5d.
  • the heights of the uppermost through holes or long holes of the openings 5a1 to 5d1, which are a plurality of through holes or long holes, are aligned. That is, the number of through holes is reduced or the length of the long holes is reduced on the lower end side of the communication pipes 5a to 5d. Therefore, even if the gas-liquid interface 42 rises, the openings 5a1 to 5d1 for sucking the gas refrigerant do not narrow.
  • the gas refrigerant can be sufficiently sucked regardless of the fluctuation of the gas-liquid interface 42, and therefore, the suction of the liquid refrigerant sucked into the openings 5a1 to 5d1 by the momentum of the gas refrigerant does not deteriorate.
  • FIG. 7A is a vertical cross-sectional view of the gas-liquid mixing portion 41 portion of the inflow side header 3a.
  • FIG. 7B is a cross-sectional view taken along the line BB in FIG. 7A of the communication part 50 provided in the gas-liquid mixing part 41.
  • the same reference numerals as those in the first embodiment are used for members and the like common to the first embodiment, and detailed description thereof is omitted.
  • the third embodiment is different from the first embodiment in that a single communication portion 50 is provided instead of the portion where the openings 5a1 to 5d1 of the communication pipes 5a to 5d in the inflow side header 3a are provided. It is.
  • the communication part 50 is a cylindrical member and is provided in the gas-liquid mixing part 41 of the inflow side header 3a.
  • the communication part 50 is connected to the communication pipes 5a to 5d in the gas-liquid mixing part 41, and openings 5a1 to 5d1 are formed in the single communication part 50 in place of the communication pipes 5a to 5d.
  • the communication part (communication part main body) 50 is a space provided vertically in the longitudinal direction of the inflow header 3a, and a cylindrical mixing chamber into which the gas-liquid two-phase refrigerant L flows. 51 is provided.
  • a plurality of refrigerant communication paths 52a to 52d in this example are provided so as to surround the mixing chamber 51.
  • the refrigerant communication paths 52a to 52d are, for example, cylindrical spaces penetrating vertically in the longitudinal direction of the inflow side header 3a, and upper ends thereof are connected to the communication pipes 5a to 5d, respectively.
  • the diameter size of each of the refrigerant communication paths 52 a to 52 d is smaller than the diameter size of the mixing chamber 51.
  • the communication part (communication part main body) 50 connects the refrigerant communication paths 52a to 52d and the mixing chamber 51, and the connection paths 53a to 53d allow the refrigerant to flow from the mixing chamber 51 to the refrigerant communication paths 52a to 52d. Is provided.
  • the connection paths 53 a to 53 d also penetrate from the top to the bottom of the communication portion (communication portion main body) 50. Each of the connection paths 53a to 53d is narrower than the diameter size of the refrigerant communication paths 52a to 52d to which the connection paths 53a to 53d are connected.
  • the partition plate 31a closes the gap between the mixing chamber 51, the connection paths 53a to 53d, the communication part 50, and the gas-liquid mixing part 41, and from other than the refrigerant communication paths 52a to 52d. Prevents the refrigerant L from flowing on the side opposite to the gas-liquid mixing part 41 of the inflow side header 3a.
  • the upper end of the gap between the mixing chamber 51, the connection paths 53a to 53d, the communication portion 50 and the gas-liquid mixing portion 41 is closed using a predetermined member or material. May be.
  • the refrigerant communication passages 52a to 52d have the same diameter size, but the width sizes of the connection passages 53a to 53d are not uniform. That is, the connection paths 53a to 53d become the openings 5a1 to 5d1, and the diameters of the connection paths 53a to 53d are the areas of the openings 5a1 to 5d1. That is, the width W53a of the connection path 53a is the maximum, and the width W53c of the connection path 53c is the minimum.
  • the width of the connection paths 53b and 53d is an intermediate size between them.
  • the communication pipes 5a to 5d are joined to the refrigerant communication paths 52a to 52d by a predetermined means so that the refrigerant L does not leak.
  • the communication pipes 5a to 5d have the same diameter size but different lengths.
  • the communication part 50 may be supported by the communication pipes 5a to 5d, may be supported by the partition plate 31a, or may be supported by the inner peripheral surface of the gas-liquid mixing part 41.
  • a refrigerant inflow part 55 is provided between the communication part 50 and the end part (lower end part) of the inflow side header 3a.
  • the inlet pipe 36 is connected to the bottom plate 3a1 of the inflow side header 3a.
  • FIG. 8 is a longitudinal sectional view of the lower part of the inflow side header 3a showing an example in which the position of the inlet pipe 36 is changed in the example of FIG. 7A.
  • the inlet pipe 36 may be connected to a desired position on the side of the refrigerant inflow portion 55.
  • FIG. 7C is a cross-sectional view taken along the line BB in FIG. 7A showing another example of the communication portion 50.
  • the example of FIG. 7C is different from the example of FIG. 7B in that the width sizes of the connection paths 53a to 53d are all constant, and the diameter sizes of the refrigerant communication paths 52a to 52d are not uniform. That is, the diameter D52a of the refrigerant communication passage 52a is the largest, the diameter size D52c of the refrigerant communication passage 52c is the smallest, and the diameter sizes of the refrigerant communication passages 52b and 52d are intermediate sizes thereof.
  • the mixing chamber 51, the refrigerant communication paths 52a to 52d, and the connection paths 53a to 53d are all linear in the longitudinal direction of the inflow side header 3a.
  • the diameter size and shape are uniform at all positions in the longitudinal direction. Therefore, the communication part 50 can be easily manufactured by extrusion molding.
  • the gas-liquid two-phase refrigerant L flowing in from the inlet pipe 36 flows into the refrigerant inflow portion 55 from the inlet pipe 36, and further mainly flows into the mixing chamber 51. Then, the refrigerant flows into the refrigerant communication passages 52a to 52d from the mixing chamber 51 through the connection passages 53a to 53d. Then, the refrigerant flows from the refrigerant communication paths 52a to 52 to the communication pipes 5a to 5d.
  • the diameters of the refrigerant communication passages 52a to 52d are the same, but the widths of the connection passages 53a to 53d are different from each other, so that the refrigerant communication passages 52a to 52d, and thus the communication pipes.
  • the amount of the refrigerant L flowing into the units 5a to 5d per unit time can be made different from each other.
  • the diameters of the connection paths 53a to 53d are the same, but the diameters of the refrigerant communication paths 52a to 52d are different from each other, so that the refrigerant communication paths 52a to 52d and thus the communication pipes
  • the amount of the refrigerant L flowing into the units 5a to 5d per unit time can be made different from each other.
  • the width sizes of the connection paths 53a to 53d are smaller than the diameter sizes of the refrigerant communication paths 52a to 52d. Therefore, there is a possibility that the communication portion 50 can be made more compact in the example of FIG. 7B than in the example of FIG. 7C in which there is a possibility of providing a refrigerant communication passage having a considerably large diameter size.
  • connection passages 53a to 53d and the refrigerant communication passages 52a to 52d are formed from end to end in the longitudinal direction of the communication portion 50. Therefore, as in the example of FIGS. 2B and 6B, the gas-liquid interface 42
  • the amount of gas refrigerant and liquid refrigerant flowing into the respective communication pipes 5a to 5d can be adjusted steplessly according to the change in height.
  • a step of positioning each one end side of the plurality of communication pipes 5a to 5d and installing them in the gas-liquid mixing part 41 is necessary.
  • the refrigerant inflow portion 55 is provided, the inlet pipe 36 can be attached at various positions on one end portion side of the inflow side header 3a. Therefore, the freedom degree of handling of refrigerant piping can be raised.
  • the mixing chamber 51, the refrigerant communication paths 52a to 52d, and the connection paths 53a to 53d are all linear in the longitudinal direction of the inflow header 3a, and the diameter size and shape are uniform at all positions in the longitudinal direction. It is. Therefore, the communication part 50 can be easily manufactured by extrusion molding. That is, if the communicating part 50 is extrusion-molded with an extrusion molding machine, the communicating part 50 can be easily mass-produced by repeating the operation of cutting the extruded communicating part 50 in a radial direction with a predetermined length. it can.
  • this invention is not limited to an above-described Example, Various modifications are included.
  • the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described.
  • one communication pipe 5a to 5d is connected to each header inner space 32 to 35, but a plurality of communication pipes 5 are connected to a single header inner space. Also good. And you may make it change the area of the opening part for every space in a header by changing the number of the communication pipes 5 connected to the space in a header.
  • the air conditioner 100 may be implemented as a cooling or heating dedicated air conditioner that does not include the four-way valve 9. Furthermore, you may apply the heat exchanger 1 to another refrigeration cycle apparatus, for example, a natural refrigerant heat pump water heater. Further, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. Moreover, it is also possible to add, delete, and replace other configurations for a part of the configuration of each embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Other Air-Conditioning Systems (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

Un collecteur côté entrée (3a) sur le côté d'entrée d'un fluide frigorigène à partir de l'extérieur comprend : une section de mélange gaz-liquide (41) qui est pourvue d'un tuyau d'entrée (36) pour permettre au fluide frigorigène (L) de s'écouler depuis l'extérieur et dans lequel s'écoule le fluide frigorigène à deux phases gaz-liquide; une pluralité d'espaces internes de collecteur (32) à (35) qui est fournie par séparation du collecteur entrée (3a) dans la direction longitudinale de celle-ci, séparée de la section de mélange gaz-liquide (41), et reliée à un ou à une pluralité de tubes de transfert de chaleur (19) disposées en continu et en parallèle; une pluralité de tuyaux de communication (5) qui communiquent des espaces internes de collecteur différents respectifs (32) à (35) avec la section de mélange gaz-liquide (41); et des ouvertures disposées chacune au niveau du tuyau de communication respectif (5) situé dans la section de mélange gaz-liquide (41) et l'introduction du fluide frigorigène dans la section de mélange gaz-liquide vers l'espace interne de collecteur respectif (32) à (35) par l'intermédiaire du tuyau de communication respectif (5), les ouvertures comprenant des ouvertures ayant des diamètres d'ouverture mutuellement différents parmi la pluralité de tuyaux de communication (5).
PCT/JP2018/017872 2018-05-09 2018-05-09 Échangeur de chaleur, procédé de fabrication de section de communication, unité intérieure, unité extérieure et climatiseur Ceased WO2019215825A1 (fr)

Priority Applications (2)

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PCT/JP2018/017872 WO2019215825A1 (fr) 2018-05-09 2018-05-09 Échangeur de chaleur, procédé de fabrication de section de communication, unité intérieure, unité extérieure et climatiseur
JP2020517666A JP6913826B2 (ja) 2018-05-09 2018-05-09 熱交換器、連通部の製造方法、室内機、室外機及び空気調和機

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PCT/JP2018/017872 WO2019215825A1 (fr) 2018-05-09 2018-05-09 Échangeur de chaleur, procédé de fabrication de section de communication, unité intérieure, unité extérieure et climatiseur

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JPWO2021186766A1 (fr) * 2020-03-19 2021-09-23
JP7142806B1 (ja) * 2021-10-15 2022-09-27 三菱電機株式会社 分配器、熱交換器およびヒートポンプ装置

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JPH04302964A (ja) * 1991-03-29 1992-10-26 Daikin Ind Ltd 冷媒分流器
JPH04316785A (ja) * 1990-01-29 1992-11-09 Mitsubishi Electric Corp 分配器
JPH09166368A (ja) * 1995-12-14 1997-06-24 Sanden Corp 熱交換器
JPH09264693A (ja) * 1996-03-29 1997-10-07 Sanden Corp 分配装置を備えた熱交換器
WO2015027783A1 (fr) * 2013-08-30 2015-03-05 杭州三花研究院有限公司 Échangeur thermique à micro-canal et son procédé de fabrication
JP2015203506A (ja) * 2014-04-11 2015-11-16 パナソニックＩｐマネジメント株式会社 熱交換器
WO2016060064A1 (fr) * 2014-10-16 2016-04-21 ダイキン工業株式会社 Répartiteur de débit de fluide frigorigène
WO2016135935A1 (fr) * 2015-02-27 2016-09-01 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド Appareil d'échange de chaleur et conditionneur d'air l'utilisant
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JPH04316785A (ja) * 1990-01-29 1992-11-09 Mitsubishi Electric Corp 分配器
JPH04302964A (ja) * 1991-03-29 1992-10-26 Daikin Ind Ltd 冷媒分流器
JPH09166368A (ja) * 1995-12-14 1997-06-24 Sanden Corp 熱交換器
JPH09264693A (ja) * 1996-03-29 1997-10-07 Sanden Corp 分配装置を備えた熱交換器
US20160298887A1 (en) * 2013-08-12 2016-10-13 Carrier Corporation Heat exchanger and flow distributor
WO2015027783A1 (fr) * 2013-08-30 2015-03-05 杭州三花研究院有限公司 Échangeur thermique à micro-canal et son procédé de fabrication
JP2015203506A (ja) * 2014-04-11 2015-11-16 パナソニックＩｐマネジメント株式会社 熱交換器
WO2016060064A1 (fr) * 2014-10-16 2016-04-21 ダイキン工業株式会社 Répartiteur de débit de fluide frigorigène
WO2016135935A1 (fr) * 2015-02-27 2016-09-01 ジョンソンコントロールズ ヒタチ エア コンディショニング テクノロジー（ホンコン）リミテッド Appareil d'échange de chaleur et conditionneur d'air l'utilisant

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JPWO2021186766A1 (fr) * 2020-03-19 2021-09-23
JP7471392B2 (ja) 2020-03-19 2024-04-19 三菱電機株式会社 熱交換器用ヘッダ、熱交換器、熱交換器用ヘッダの製造方法、及び熱交換器の製造方法
JP7142806B1 (ja) * 2021-10-15 2022-09-27 三菱電機株式会社 分配器、熱交換器およびヒートポンプ装置

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