WO2020165973A1 - Unité intérieure de dispositif de climatisation, et dispositif de climatisation - Google Patents

Unité intérieure de dispositif de climatisation, et dispositif de climatisation Download PDF

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Publication number
WO2020165973A1
WO2020165973A1 PCT/JP2019/005095 JP2019005095W WO2020165973A1 WO 2020165973 A1 WO2020165973 A1 WO 2020165973A1 JP 2019005095 W JP2019005095 W JP 2019005095W WO 2020165973 A1 WO2020165973 A1 WO 2020165973A1
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Prior art keywords
heat transfer
heat exchanger
heat
transfer tube
indoor unit
Prior art date
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PCT/JP2019/005095
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English (en)
Japanese (ja)
Inventor
龍一 永田
真哉 東井上
昭憲 坂部
裕樹 宇賀神
中川　直紀
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2020571965A priority Critical patent/JPWO2020165973A1/ja
Priority to PCT/JP2019/005095 priority patent/WO2020165973A1/fr
Publication of WO2020165973A1 publication Critical patent/WO2020165973A1/fr

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    • 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
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
    • F24F1/0067—Indoor units, e.g. fan coil units characterised by heat exchangers by the shape of the heat exchangers or of parts thereof, e.g. of their fins
    • 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
    • F25B39/04—Condensers
    • 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

Definitions

  • the present invention relates to an air conditioner indoor unit and an air conditioner equipped with a heat exchanger for exchanging heat between air and a refrigerant.
  • the front heat exchanger located in the front of the casing is closer to the fan than the rear heat exchanger located in the rear of the casing. .. Therefore, air can pass through the front heat exchanger more easily than the rear heat exchanger (see, for example, Patent Document 1).
  • the wind speed at the central portion of the fan tends to be relatively low, and the wind speed at the blade portion of the fan tends to be relatively high. .. Therefore, the wind speed distribution of the air passing through the heat exchanger varies depending on the positional relationship with the fan.
  • the present invention has been made to solve the above problems, and an object of the present invention is to provide an air conditioner indoor unit and an air conditioner that improve heat exchange performance in a heat exchanger.
  • An indoor unit of an air conditioner according to the present invention is provided with a casing having a suction port formed in an upper part and a blow port in a lower part, and provided between a suction port and a blow port in the casing, and blows from the suction port.
  • An air blower that creates an airflow toward the outlet, and a heat exchanger provided between the air blower and the outlet in the casing are provided, and the heat exchanger includes a plurality of heat transfer tubes arranged at intervals, And a plurality of heat transfer portions including a plurality of fin portions through which a plurality of heat transfer tubes penetrate, and the plurality of heat transfer portions are the first heat transfer portion arranged on the most windward side. , And a second heat transfer section disposed on the leeward side of the first heat transfer section, and the ventilation resistance of the first heat transfer section is larger than the ventilation resistance of the second heat transfer section.
  • An air conditioner includes the indoor unit described above and an outdoor unit including a compressor, an expansion valve, and a heat source side heat exchanger, and also includes a compressor, a heat exchanger, an expansion valve, and a heat source side.
  • the heat exchanger has a refrigerant circuit formed by being connected by refrigerant pipes.
  • FIG. 3 is a schematic cross-sectional view taken along the line AA of the indoor unit of FIG. It is explanatory drawing which shows the heat exchanger and load side air blower shown in FIG. 3, and wind velocity distribution matched with this. It is a top view of the heat exchanger of FIG. It is explanatory drawing which shows a mode that air passes through the free passage area of the heat exchanger of FIG. It is a schematic sectional drawing of the heat exchanger which the indoor unit of the air conditioning apparatus which concerns on Embodiment 2 of this invention has. It is a front view of the heat exchanger of FIG.
  • FIG. It is a perspective view of the heat exchanger of FIG. It is a schematic sectional drawing of the heat exchanger which the indoor unit of the air conditioning apparatus which concerns on Embodiment 3 of this invention has. It is a front view of the heat exchanger of FIG. It is a perspective view of the heat exchanger of FIG. It is a schematic sectional drawing of the indoor unit of the air conditioning apparatus which concerns on Embodiment 4 of this invention. It is a top view of the heat exchange unit of FIG. It is explanatory drawing which shows a mode that air passes through the free passage area of the heat exchange unit of FIG. It is a schematic sectional drawing of the heat exchange unit which the indoor unit of the air conditioning apparatus which concerns on the modification 4-1 of Embodiment 4 of this invention has.
  • FIG. 1 is a schematic configuration diagram illustrating the overall configuration of an air conditioning apparatus according to Embodiment 1 of the present invention.
  • the overall configuration of the air conditioning apparatus 500 will be described with reference to FIG. 1. It should be noted that the reference numerals may be omitted when describing the contents common to the equivalent components. The same applies to each embodiment described later.
  • the air conditioner 500 has an indoor unit 100 installed indoors and an outdoor unit 200 installed outdoors.
  • the indoor unit 100 and the outdoor unit 200 are connected by a refrigerant pipe R.
  • the indoor unit 100 has a heat exchanger 10 and a blower 50.
  • the heat exchanger 10 is constituted by, for example, a fin-and-tube heat exchanger, and heat is exchanged between the indoor air and the refrigerant.
  • the blower 50 is attached to the heat exchanger 10 and sends air to the heat exchanger 10.
  • the first embodiment shows an example in which the indoor unit 100 has two blowers 50.
  • the outdoor unit 200 has a compressor 61, a four-way valve 62, an expansion valve 63, a heat source side heat exchanger 64, and a heat source side blower 70.
  • the compressor 61 is driven by, for example, an inverter and compresses the refrigerant.
  • the four-way valve 62 is connected to the discharge side of the compressor 61 and switches the flow path of the refrigerant.
  • the four-way valve 62 is switched to, for example, the flow path of the solid line in FIG. 1 during the heating operation, and is switched to the flow path of the broken line in FIG. 1 during the cooling operation and the defrosting operation.
  • the expansion valve 63 is composed of, for example, an electronic expansion valve, and decompresses the refrigerant to expand it.
  • the heat source side heat exchanger 64 is formed of, for example, a fin-and-tube heat exchanger, and heat is exchanged between the outside air and the refrigerant.
  • the heat source side blower 70 is attached to the heat source side heat exchanger 64 and blows air to the heat source side heat exchanger 64.
  • the air conditioning apparatus 500 has the refrigerant circuit 80 formed by connecting the compressor 61, the four-way valve 62, the heat exchanger 10, the expansion valve 63, and the heat source side heat exchanger 64 by the refrigerant pipe R. There is.
  • the heat exchanger 10 functions as a condenser
  • the heat source side heat exchanger 64 functions as an evaporator
  • the heat exchanger 10 functions as an evaporator
  • the heat source side heat exchanger 64 functions as a condenser.
  • FIG. 2 is a front view of the indoor unit of FIG.
  • FIG. 3 is a schematic cross-sectional view taken along the line AA of the indoor unit of FIG.
  • FIG. 2 shows an example in which the indoor unit 100 is attached to the wall 800 in the room. 2 and 3, the front-back direction of the casing 101 corresponds to the x-axis direction, the left-right direction of the casing 101 corresponds to the y-axis direction, and the up-down direction of the casing 101 corresponds to the z-axis direction.
  • the positive x-axis direction corresponds to the front direction of the casing 101, and the negative x-axis direction corresponds to the rear direction of the casing 101.
  • the positive z-axis direction corresponds to the downward direction of the casing 101
  • the negative z-axis direction corresponds to the upward direction of the casing 101.
  • the heat transfer tube group is shown only in FIG. 3 in order to avoid complication of the drawing.
  • the indoor unit 100 has a casing 101 having a suction port 102 formed in the upper part and a blow port 103 formed in the lower part.
  • the blower 50 is provided in the casing 101 between the suction port 102 and the blowout port 103, and creates an airflow from the suction port 102 toward the blowout port 103.
  • the heat exchanger 10 is provided in the casing 101 between the blower 50 and the outlet 103. Therefore, the air sucked from the suction port 102 flows in the casing 101 and is blown out from the blowout port 103 as shown by the white arrow in FIG. 3. That is, the air sucked from the suction port 102 passes through the heat exchanger 10 substantially along the positive direction of the z-axis.
  • the z-axis positive direction is also referred to as the “ventilation direction”.
  • the heat exchanger 10 has a plurality of heat transfer parts including a plurality of heat transfer pipes arranged at intervals and a plurality of fin parts stacked at intervals and penetrating the plurality of heat transfer pipes.
  • the plurality of heat transfer parts are the first heat transfer part 11 arranged on the most windward side, and the second heat transfer part 12 arranged on the leeward side of the first heat transfer part 11. It is composed by.
  • the first heat transfer section 11 includes a plurality of heat transfer tubes 11a arranged at intervals and a plurality of fin sections 11b stacked at intervals and penetrated by the heat transfer tubes 11a.
  • the 1st heat transfer part 11 has the heat transfer tube group 11g which consists of the heat transfer tube 11a which forms a row.
  • the heat transfer tube group 11g is formed by arranging a plurality of heat transfer tubes 11a in the same direction at predetermined intervals.
  • the second heat transfer section 12 includes a plurality of heat transfer tubes 12a arranged at intervals and a plurality of fin sections 12b stacked at intervals and penetrated by the heat transfer tubes 12a. ..
  • the 2nd heat transfer part 12 has the heat transfer tube group 12g which consists of the heat transfer tube 12a which makes a line.
  • the heat transfer tube group 12g is formed by arranging a plurality of heat transfer tubes 12a in the same direction at predetermined intervals.
  • the ventilation resistance of the first heat transfer section 11 on the windward side is larger than the ventilation resistance of the second heat transfer section 12 on the leeward side.
  • the outer diameter O 1 of each heat transfer tube 11a of the first heat transfer section 11 is larger than the outer diameter O 2 of each heat transfer tube 12a of the second heat transfer section 12. ing. That is, the ratio of the outer diameter O 1 to the outer diameter O 2 (O 1 /O 2 ) is greater than 1.
  • the ratio of the outer diameter O 1 to the outer diameter O 2 i.e. the outer diameter O 2 of the outer diameter O 1 and the heat transfer tube 12a of the heat transfer tube 11a, when appropriately changed depending on the capacity zone and load conditions of the air conditioner 500 Good.
  • the fin portion 11b and the fin portion 12b are integrally formed to form one fin.
  • FIG. 4 is an explanatory diagram showing the heat exchanger and the load side blower shown in FIG. 3, and the wind speed distribution associated therewith. More specifically, FIG. 4A is a diagram showing the heat exchanger 10 and the blower 50 extracted from FIG. 3. In FIG. 4B, in the heat exchanger 10 of FIG. 4A, the position in the x-axis direction is taken as the horizontal axis, and the wind speed corresponding to the position in the x-axis direction is taken as the vertical axis.
  • a graph D 0 indicated by a broken line shows a wind velocity distribution on the assumption that the outer diameter of the heat transfer tube 11a and the outer diameter of the heat transfer tube 12a in the heat exchanger 10 are assumed to be equal to each other.
  • the graph D 1 shown by the solid line in FIG. 4B is a graph exemplifying the wind speed distribution in the heat exchanger 10 of the first embodiment.
  • the outer diameter O 1 of each heat transfer tube 11a of the first heat transfer section 11 is larger than the outer diameter O 2 of each heat transfer tube 12a of the second heat transfer section 12. Therefore, the ventilation resistance of the first heat transfer section 11 is larger than the ventilation resistance of the second heat transfer section 12. Therefore, as shown by the graph D 1 in FIG. 4B, it is possible to reduce the variation in the wind speed distribution of the air passing through the heat exchanger 10.
  • FIG. 5 is a plan view of the heat exchanger of FIG.
  • FIG. 6 is an explanatory diagram showing how air passes through the free passage area of the heat exchanger of FIG.
  • a gap is formed between the adjacent heat transfer tubes 11a and 12a in plan view.
  • the distance between the heat transfer tube 11a and the heat transfer tube 12a arranged along the positive x-axis is defined as a width S
  • the distance between the heat transfer tube 12a and the heat transfer tube 11a arranged along the positive x-axis is defined as The width is T.
  • the width S and the width T may be different or the same.
  • each space having the width S and each space having the width T along the y-axis direction of the heat exchanger 10 are free passage regions through which the air sent from the blower 50 can freely pass.
  • the free passage area is an area where the air flowing into the heat exchanger 10 along the vertical direction passes through the heat exchanger 10 without contacting the heat transfer tubes.
  • the first heat transfer portion 11 prevents the passage of air sent from the blower 50 through the heat transfer tube 11a having an outer diameter of O 1.
  • the second heat transfer portion 12 prevents the passage of air sent from the blower 50 through the heat transfer tube 12a having an outer diameter of O 2.
  • the ventilation resistance of the first heat transfer section 11 arranged on the most windward side is the first heat transfer section 11 arranged on the leeward side of the first heat transfer section 11. 2 It is larger than the ventilation resistance of the heat transfer section 12. That is, in the heat exchanger 10, the outer diameter O 1 of each heat transfer tube 11 a of the first heat transfer section 11 is larger than the outer diameter O 2 of each heat transfer tube 12 a of the second heat transfer section 12. Therefore, the pressure loss of the air due to the heat transfer tube group 11g becomes larger than the pressure loss of the air due to the heat transfer tube group 12g, so that the variation in the wind speed distribution of the air passing through the heat exchanger 10 can be alleviated. The heat exchange performance of the heat exchanger 10 can be improved.
  • the first heat transfer unit 11 may include a plurality of rows of heat transfer tube groups 11g
  • the second heat transfer unit 12 may include a plurality of rows of heat transfer tube groups 12g. That is, at least one of the first heat transfer section 11 and the second heat transfer section 12 may include a plurality of rows of heat transfer tube groups.
  • the heat exchanger 10 includes one heat transfer tube group 11g of the first heat transfer section 11 and two heat transfer tube group 12g of the second heat transfer section 12, and the like.
  • the number may be smaller than the number of rows of the heat transfer tube group 12g.
  • the heat exchanger 10 includes two heat transfer tube groups 11g of the first heat transfer section 11 and one heat transfer tube group 12g of the second heat transfer section 12 such that the heat transfer tube group 11g is arranged in a row.
  • the number may be greater than the number of rows of the heat transfer tube group 12g.
  • the ventilation resistance of the heat exchanger 10 can be adjusted according to the structure of the indoor unit 100, the characteristics of the actuators such as the blower 50, and the like, so that the wind velocity distribution of the air passing through the heat exchanger 10 can be adjusted. It is possible to more accurately alleviate the variation.
  • the number of heat transfer tubes configuring each heat transfer tube group is not limited to the example of each drawing, and can be appropriately changed according to the capacity band and load conditions of the air conditioner 500. ..
  • the ventilation resistance of the heat exchanger 10 may be adjusted by combining the number of heat transfer tubes forming each heat transfer tube group and the change of the ratio of the outer diameter O 1 to the outer diameter O 2 .
  • changing the ratio of the outer diameter O 1 to the outer diameter O 2 can be performed by changing at least one of the outer diameter O 2 of the outer diameter O 1 and the heat exchanger tube 12a of the heat transfer tube 11a. The same applies to each embodiment described later.
  • the respective numbers of the fin portions 11b and the fin portions 12b are not limited to the examples of FIGS. 2 and 5, and can be appropriately changed according to the size of the heat exchanger 10 and the like.
  • 2 to 6 show an example in which the vertical width of the fin portion 11b and the vertical width of the fin portion 12b are equal, but the present invention is not limited to this.
  • the vertical width of the fin portion 11b may be longer than the vertical width of the fin portion 12b, or may be shorter than the vertical width of the fin portion 12b.
  • FIGS. 2 to 6 show examples in which the thickness of the fin portion 11b in the left-right direction is equal to the thickness of the fin portion 12b in the left-right direction, the present invention is not limited to this.
  • the thickness of the fin portion 11b in the left-right direction may be greater than the thickness of the fin portion 12b in the left-right direction, or may be thinner than the thickness of the fin portion 112b in the left-right direction.
  • FIG. 7 is a schematic sectional drawing of the heat exchanger which the indoor unit of the air conditioning apparatus which concerns on Embodiment 2 of this invention has.
  • FIG. 8 is a front view of the heat exchanger of FIG. 7.
  • FIG. 9 is a perspective view of the heat exchanger of FIG. 7.
  • the configuration of the air conditioner according to the second embodiment is the same as the example of FIGS. 1 to 3 used in the first embodiment described above.
  • the configuration of the heat exchanger 110 according to the second embodiment will be described with reference to FIGS. 7 to 9.
  • the same components as those in the first embodiment are designated by the same reference numerals and the description thereof is omitted.
  • the heat exchanger 110 includes a first heat transfer section 111 including a plurality of heat transfer tubes 111a arranged at intervals and a plurality of fin sections 111b stacked at intervals and penetrated by the heat transfer tubes 111a. have.
  • the first heat transfer section 111 has a heat transfer tube group 111g made up of rows of heat transfer tubes 111a.
  • the heat exchanger 110 includes a plurality of heat transfer tubes 112a arranged at intervals and a plurality of fin portions 112b stacked at intervals and penetrating the plurality of heat transfer tubes 112a. It has a section 112.
  • the second heat transfer section 112 has a heat transfer tube group 112g formed of rows of heat transfer tubes 112a.
  • the ventilation resistance of the first heat transfer section 111 on the windward side is larger than the ventilation resistance of the second heat transfer section 112 on the leeward side.
  • the interval P 1 between the fin portions 111b of the first heat transfer portion 111 arranged on the windward side is equal to the fin portion 112b of the second heat transfer portion 112 on the leeward side. It is smaller than the interval P 2 between them. That is, the ratio of the interval P 1 to the interval P 2 (P 1 /P 2 ) is a value smaller than 1.
  • the interval P 1 and the interval P 2 the ratio of spacing P 1 relative spacing P 2 is set to be about 0.83 to 0.92.
  • the ratio of the distance P 1 relative spacing P 2, that is, the distance P 1 and spacing P 2 can be appropriately changed depending on the capacity zone and load conditions of the air conditioning apparatus 500.
  • the fin portion 111b and the fin portion 112b are formed as separate bodies.
  • the area of the fin portion 111b is larger than the area of the fin portion 112b in plan view, so that the ventilation resistance of the first heat transfer portion 111 is larger than the ventilation resistance of the second heat transfer portion 112. Become. Therefore, similarly to the graph D 1 illustrated in FIG. 4B, it is possible to reduce the variation in the wind speed distribution of the air passing through the heat exchanger 110.
  • the ventilation resistance of the first heat transfer section 111 arranged on the most windward side is set to the lee side of the first heat transfer section 111. 2 It is larger than the ventilation resistance of the heat transfer section 112. That is, in the heat exchanger 110, the distance between the fin portions 111b of the first heat transfer portion 111 is smaller than the distance between the fin portions 112b of the second heat transfer portion 112. Therefore, the pressure loss of the air due to the plurality of fins 111b becomes larger than the pressure loss of the air due to the plurality of fins 112b, so that the variation in the wind velocity distribution of the air passing through the heat exchanger 110 can be reduced. Therefore, the heat exchange performance can be improved.
  • the vertical width of the fin portion 111b and the vertical width of the fin portion 112b are equal, but the present invention is not limited to this.
  • the vertical width of the fin portion 111b may be longer than the vertical width of the fin portion 112b, or may be shorter than the vertical width of the fin portion 112b.
  • the ventilation resistance of the heat exchanger 110 is adjusted by changing the vertical widths of the fin portions 111b and the fin portions 112b according to the characteristics of the actuators such as the blower 50 and the structure of the indoor unit 100. Therefore, the variation in the wind speed distribution of the air passing through the heat exchanger 10 can be alleviated more accurately.
  • the first heat transfer section 111 includes the row of heat transfer tube groups 111g and the second heat transfer section 112 includes the row of the heat transfer tube groups 112g has been exemplified, but the present invention is not limited to this. Not done.
  • the first heat transfer section 111 may include a plurality of heat transfer tube groups 111g
  • the second heat transfer section 112 may include a plurality of heat transfer tube groups 112g. That is, at least one of the first heat transfer section 111 and the second heat transfer section 112 may include a plurality of heat transfer tube groups.
  • the number of rows of each heat transfer tube group may be adjusted according to the vertical widths of the fin portions 111b and the fin portions 112b.
  • the horizontal thickness of the fin portion 111b and the horizontal thickness of the fin portion 112b are equal, but the present invention is not limited to this.
  • the horizontal thickness of the fin portion 111b may be larger than the horizontal thickness of the fin portion 112b, or may be smaller than the horizontal thickness of the fin portion 112b.
  • the numbers of the fin portions 111b and the fin portions 112b are not limited to the examples of FIGS. 8 and 9, and can be appropriately changed according to the size of the heat exchanger 110 and the like. Further, the respective number of changes of the fin portion 111b and the fin part 112b, by combining the change in the ratio between the interval P 1 relative spacing P 2, may adjust the air flow resistance of the heat exchanger 110.
  • FIG. 10 is a schematic sectional drawing of the heat exchanger which the indoor unit of the air conditioning apparatus which concerns on Embodiment 3 of this invention has.
  • 11 is a front view of the heat exchanger of FIG.
  • FIG. 12 is a perspective view of the heat exchanger of FIG.
  • the configuration of the air conditioner according to the third embodiment is the same as the example of FIGS. 1 to 3 used in the above-described first embodiment.
  • the configuration of the heat exchanger 210 according to the third embodiment will be described with reference to FIGS. 10 to 12.
  • the same members as those in the first and second embodiments are designated by the same reference numerals and the description thereof will be omitted.
  • the heat exchanger 210 includes a first heat transfer section 211 including a plurality of heat transfer tubes 11a arranged at intervals and a plurality of fin sections 111b stacked at intervals and penetrated by the heat transfer tubes 11a. have.
  • the 1st heat transfer part 211 has the heat transfer tube group 11g which comprises the heat transfer tube 11a which forms a row.
  • the heat exchanger 210 includes a second heat transfer tube including a plurality of heat transfer tubes 12a arranged at intervals and a plurality of fin portions 112b stacked at intervals and penetrating the plurality of heat transfer tubes 12a. It has a part 212.
  • the second heat transfer section 212 has a heat transfer tube group 12g including the heat transfer tubes 12a forming a row.
  • the fin portion 111b and the fin portion 112b are formed as separate bodies.
  • the ventilation resistance of the first heat transfer section 211 on the windward side is larger than the ventilation resistance of the second heat transfer section 212 on the leeward side. That is, in the heat exchanger 210, the outer diameter O 1 of each heat transfer tube 11a of the first heat transfer section 211 is larger than the outer diameter O 2 of each heat transfer tube 12a of the second heat transfer section 212. Further, in the heat exchanger 210, the distance P 1 between the fin portions 111b of the first heat transfer portion 211 arranged on the windward side is equal to the distance P 1 between the fin portions 112b of the second heat transfer portion 212 on the leeward side. It is smaller than 2 .
  • the ratio of outer diameter O 1 to outer diameter O 2 of heat exchanger 210 is smaller than the ratio of outer diameter O 1 to outer diameter O 2 of heat exchanger 10 in the first embodiment.
  • the ratio of the distance P 1 relative spacing P 2 of the heat exchanger 210 is greater than the ratio of the distance P 1 relative spacing P 2 of the heat exchanger 110 in the second embodiment.
  • Other configurations and alternative configurations of the heat exchanger 210 are similar to those of the heat exchanger 10 of the first embodiment and the heat exchanger 110 of the second embodiment.
  • the ventilation resistance of the first heat transfer section 211 on the most windward side is larger than the ventilation resistance of the second heat transfer section 212. That is, the outer diameter O 1 of each heat transfer tube 11a of the first heat transfer section 211 is larger than the outer diameter O 2 of each heat transfer tube 12a of the second heat transfer section 212.
  • the distance between the fin portions 11b of the first heat transfer portion 211 is smaller than the distance between the fin portions 12b of the second heat transfer portion 212. Therefore, the pressure loss of the air due to the first heat transfer section 211 becomes larger than the pressure loss of the air due to the second heat transfer section 212, so that the variation in the wind speed distribution in the heat exchanger 210 can be alleviated.
  • the heat exchange performance can be improved.
  • FIG. 13 is a schematic sectional drawing of the indoor unit of the air conditioning apparatus which concerns on Embodiment 4 of this invention.
  • FIG. 14 is a plan view of the heat exchange unit shown in FIG.
  • FIG. 15 is explanatory drawing which shows a mode that air passes through the free passage area of the heat exchange unit of FIG.
  • the configuration of the air conditioner according to the fourth embodiment is the same as the example of FIGS. 1 and 2 used in the above-described first embodiment. That is, the air conditioning apparatus 500 according to Embodiment 4 has the refrigerant circuit 80 formed by connecting the compressor 61, the heat exchange unit 310V, the expansion valve 63, and the heat source side heat exchanger 64 by the refrigerant pipe R. doing.
  • FIGS. 13 to 15 The configuration of the heat exchange unit 310V according to the fourth embodiment will be described with reference to FIGS. 13 to 15.
  • the same members as those in the first to third embodiments are designated by the same reference numerals and the description thereof will be omitted.
  • one reference numeral is partially omitted for the constituent members that overlap between the first heat exchanger 10A and the second heat exchanger 10B.
  • the heat exchange unit 310V includes a first heat exchanger 10A provided on the front side in the casing 101 and a second heat exchanger 10B provided on the rear side in the casing 101. That is, the second heat exchanger 10B is arranged rearward of the first heat exchanger 10A.
  • the first heat exchanger 10A and the second heat exchanger 10B are configured similarly to the heat exchanger 10 of the first embodiment described above.
  • the first heat exchanger 10A and the second heat exchanger 10B are arranged in a V-shape in cross section so that the distance between the surfaces facing each other becomes shorter from the windward side toward the leeward side. That is, the distance between the inner surface 31A of the first heat exchanger 10A and the inner surface 31B of the second heat exchanger 10B becomes shorter from the windward side toward the leeward side.
  • the inner surface 31A and the inner surface 31B are imaginary surfaces that combine the end surfaces of the plurality of fin portions 11b and the gaps between the fin portions 11b.
  • a gap having a width U 1 is formed between the two rear heat transfer tubes 11a in a plan view, and between the two front heat transfer tubes 12a.
  • a gap having a width U 2 is formed.
  • a gap having a width U 1 is formed between the two front heat transfer tubes 11a and a width U 2 having a width U 2 between the two rear heat transfer tubes 12a in a plan view.
  • a gap is formed. That is, in the indoor unit 100 of the fourth embodiment, the air sent from the blower 50 has a space of width U 1 along the y-axis direction of the first heat exchanger 10A, as indicated by the white arrow in FIG.
  • the space of width U 2 can be freely passed. That is, the space of the width U 1 and the space of the width U 2 along the y-axis direction of the first heat exchanger 10A are free passage areas through which the air sent from the blower 50 can freely pass. Further, in the indoor unit 100 according to the fourth embodiment, the air blown from the blower 50 has a space with a width U 1 along the y-axis direction of the second heat exchanger 10B as indicated by a white arrow in FIG.
  • the space of width U 2 can be freely passed. That is, the space having the width U 1 and the space having the width U 2 along the y-axis direction of the second heat exchanger 10B are free passage areas through which the air sent from the blower 50 can freely pass.
  • the adjacent heat transfer tube groups have at least one heat transfer tube of one heat transfer tube group and the heat transfer tube group of the other heat transfer tube group of one of the other heat transfer tube group in plan view. Or it overlaps with the heat transfer tube of 2. That is, in each of the first heat exchanger 10A and the second heat exchanger 10B, at least one heat transfer tube of one heat transfer tube group and one or two heat transfer tubes of the other heat transfer tube group are both seen in a plan view. They are arranged so as to overlap with each other and form a predetermined inclination angle with respect to the ventilation direction.
  • a part of the uppermost heat transfer tube 11a of the heat transfer tube group 11g corresponds to the lower two heat transfer tubes 12a of the heat transfer tube group 12g. It overlaps with a part.
  • a part of the second heat transfer tube 11a from the top of the heat transfer tube group 11g overlaps with a part of the lowermost heat transfer tube 12a of the heat transfer tube group 12g.
  • a part of the lowermost heat transfer tube 12a of the heat transfer tube group 12g overlaps a part of the upper two heat transfer tubes 11a of the heat transfer tube group 11g.
  • a part of the second heat transfer tube 12a from the bottom of the heat transfer tube group 12g overlaps with a part of the uppermost heat transfer tube 11a of the heat transfer tube group 11g in a plan view. ..
  • a part of the uppermost heat transfer tube 11a of the heat transfer tube group 11g overlaps a part of the lower two heat transfer tubes 12a of the heat transfer tube group 12g. ..
  • a part of the second heat transfer tube 11a from the top of the heat transfer tube group 11g overlaps with a part of the lowermost heat transfer tube 12a of the heat transfer tube group 12g.
  • a part of the lowermost heat transfer tube 12a of the heat transfer tube group 12g overlaps with a part of the upper two heat transfer tubes 11a of the heat transfer tube group 11g.
  • the outer diameter O 2 of the heat transfer tube 12a is smaller than the outer diameter O 1 of the heat transfer tube 11a. Therefore, in the first heat exchanger 10A and the second heat exchanger 10B, the entire heat transfer tubes 12a of the heat transfer tube group 12g may be the heat transfer tubes depending on the inclination angle with respect to the ventilation direction and the arrangement of the heat transfer tubes 11a and the heat transfer tubes 12a. It will overlap with a part of the heat transfer tube 11a of the group 11g.
  • the ventilation resistance of the first heat transfer section 11 arranged on the most windward side is the first heat transfer section 11 arranged on the leeward side of the first heat transfer section 11. 2 It is larger than the ventilation resistance of the heat transfer section 12. That is, in the heat exchange unit 310V, the outer diameter O 1 of each heat transfer tube 11a of the first heat transfer section 11 is larger than the outer diameter O 2 of each heat transfer tube 12a of the second heat transfer section 12. Therefore, since the pressure loss of air due to the heat transfer tube group 11g becomes larger than the pressure loss of air due to the heat transfer tube group 11g, it is possible to mitigate the variation in the wind speed distribution of the air passing through the heat exchange unit 310V. The heat exchange performance can be improved.
  • the heat exchangers are arranged such that the heat transfer tube groups are parallel to each other in the left-right direction as in the above-described first to third embodiments, as shown in FIGS.
  • the free passage regions exist at regular intervals between the heat transfer tubes of one heat transfer tube group and the heat transfer tubes of the other heat transfer tube group.
  • adjacent heat transfer tube groups in each of the first heat exchanger 10A and the second heat exchanger 10B, adjacent heat transfer tube groups have at least one heat transfer tube of one heat transfer tube group in a plan view, It overlaps with one or two heat transfer tubes of the other heat transfer tube group.
  • the free passage area is smaller than that in the case where the heat exchanger is arranged as in the first to third embodiments, so that the heat exchanger flows into the heat exchanger. Since the air easily contacts the heat transfer tube, the heat exchange performance can be further enhanced.
  • the push-in type indoor unit 100 has the heat exchange unit 310V in which the first heat exchanger 10A and the second heat exchanger 10B are arranged in a V shape in cross section. .. Therefore, the ventilation resistance of the heat exchange unit 310V is smaller than that of the heat exchange unit having an inverted V-shape in cross section. Therefore, according to the indoor unit 100, the air can be efficiently passed through the heat exchange unit 310V, so that the heat exchange efficiency can be improved.
  • the width U 1 and width U 2 of the gap formed in the first heat exchanger 10A may be equal to the width U 1 and width U 2 of the gap formed in the second heat exchanger 10B. , May be different.
  • the inclination angle of the first heat exchanger 10A with respect to the ventilation direction and the inclination angle of the second heat exchanger 10B with respect to the ventilation direction may be the same or different. The same applies to each heat exchanger of the fifth embodiment described later.
  • FIGS. 13 to 15 show examples in which the first heat exchanger 10A and the second heat exchanger 10B are configured in the same manner as the heat exchanger 10 of the first embodiment, the present invention is not limited to this.
  • the first heat exchanger 10A and the second heat exchanger 10B may be configured in the same manner as the heat exchanger 110 in the second embodiment, or may be configured in the same manner as the heat exchanger 210 in the third embodiment. Good.
  • FIG. 16 is a schematic cross-sectional view of a heat exchange unit included in the indoor unit of the air-conditioning apparatus according to Modification 4-1 of Embodiment 4 of the present invention.
  • the air conditioning apparatus 500 in the present modification 4-1 has a refrigerant circuit 80 formed by connecting a compressor 61, a heat exchange unit 410V, an expansion valve 63, and a heat source side heat exchanger 64 by a refrigerant pipe R. ing.
  • the heat exchange unit 410V has a first heat exchanger 410A provided on the front side inside the casing 101 and a second heat exchanger 410B provided on the rear side inside the casing 101.
  • the first heat exchanger 410A and the second heat exchanger 410B are arranged such that the distance between the surfaces facing each other becomes shorter from the windward side toward the leeward side.
  • Each of the first heat exchanger 410A and the second heat exchanger 410B has, as two heat transfer portions, a sub heat exchanger 411 including at least one heat transfer tube group 411g and a main heat exchange including a plurality of heat transfer tube groups 412g. And a container 412.
  • the sub heat exchanger 411 has one heat transfer tube group 411g
  • the main heat exchanger 412 has two heat transfer tube groups 412g.
  • the sub heat exchanger 411 is arranged on the windward side of the main heat exchanger 412.
  • the sub heat exchanger 411 includes a plurality of heat transfer tubes 11a that are arranged at intervals, and a plurality of fin portions 411b that are stacked at intervals and that penetrate the plurality of heat transfer tubes 11a.
  • the sub heat exchanger 411 has a heat transfer tube group 411g including the heat transfer tubes 11a forming a row.
  • the main heat exchanger 412 is arranged on the leeward side of the sub heat exchanger 411.
  • the main heat exchanger 412 has a plurality of heat transfer tubes 12a arranged at intervals, and a plurality of fin portions 412b that are laminated at intervals and penetrate through the plurality of heat transfer tubes 12a.
  • the main heat exchanger 412 has a heat transfer tube group 412g composed of rows of heat transfer tubes 12a.
  • the area of the surface of the fin portion 411b through which the heat transfer tube 11a penetrates is smaller than the area of the surface of the fin portion 412b through which the heat transfer tube 12a penetrates.
  • the outer diameter O 1 of each heat transfer tube 11a of the sub heat exchanger 411 is equal to each heat transfer tube of the main heat exchanger 412. It is larger than the outer diameter O 2 of 12a.
  • the space between the fin portions 411b of the windward side sub-heat exchanger 411 is the same as in the third embodiment. It may be smaller than the distance between the fin portions 412b of the main heat exchanger 412 on the side.
  • the heat transfer tube 11a is arranged so that the outer diameter O 1 and the outer diameter O 2 become equal to each other, as in the second embodiment.
  • the heat transfer tube 12a may be configured.
  • the fins forming each of the two or more heat transfer parts have the same shape, but the present invention is not limited to this, and as in the example of FIG.
  • the shapes of the fin portions forming each may be different from each other.
  • the configuration of the present modification 4-1 can be applied to the configurations of the above-described second and third embodiments. That is, in the heat exchanger 110, the first heat transfer section 111 may be a sub heat exchanger including at least one heat transfer tube group 111g, and the second heat transfer section 112 includes a plurality of heat transfer tube groups 112g. It may be the main heat exchanger.
  • the first heat transfer section 211 may be a sub heat exchanger including at least one heat transfer tube group 11g, and the second heat transfer section 212 includes a plurality of heat transfer tube groups 12g. It may be the main heat exchanger.
  • FIG. 17 is a schematic sectional drawing of the indoor unit of the air conditioning apparatus which concerns on Embodiment 5 of this invention.
  • FIG. 18 is a plan view of the heat exchange unit shown in FIG.
  • the configuration of the air conditioner in the fifth embodiment is the same as the example of FIGS. 1 and 2 used in the above-described first embodiment. That is, the air conditioning apparatus 500 according to Embodiment 5 has the refrigerant circuit 80 formed by connecting the compressor 61, the heat exchange unit 510W, the expansion valve 63, and the heat source side heat exchanger 64 by the refrigerant pipe R. doing.
  • FIG. 17 illustrates the state where the indoor unit 100 is attached to the wall 800 in the room.
  • the configuration of the heat exchange unit 510W of the fifth embodiment will be described with reference to FIGS. 17 and 18.
  • the same reference numerals are used for the same components as those of the first to fourth embodiments, and the description and some of the reference numerals are omitted.
  • the heat exchange unit 510W of the fifth embodiment includes a first heat exchanger 510A, a second heat exchanger 510B, a third heat exchanger 510C, and a fourth heat exchanger, which are arranged in order from the front to the rear in the casing 101. It has a container 510D.
  • the first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchanger 510D are configured similarly to the heat exchanger 210 of the third embodiment.
  • the positional relationship between the first heat exchanger 510A and the second heat exchanger 510B and the positional relationship between the third heat exchanger 510C and the fourth heat exchanger 510D are respectively the first heat exchanger in the fourth embodiment.
  • the positional relationship between 10A and the second heat exchanger 10B is the same.
  • the 2nd heat exchanger 510B and the 3rd heat exchanger 510C are arrange
  • the heat exchange unit 510W is formed in a W-shape in cross section as a whole by the first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchanger 510D. ..
  • the adjacent heat transfer tube group is a plane.
  • at least one heat transfer tube of one heat transfer tube group overlaps with one or two heat transfer tubes of the other heat transfer tube group.
  • the inclination angle of each of the first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchanger 510D with respect to the vertical direction is the size of the casing 101, The size is appropriately changed according to the size.
  • the first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchanger 510D are all of the first heat transfer section 211.
  • the outer diameter O 1 of the heat transfer tube 11 a is larger than the outer diameter O 2 of each heat transfer tube 12 a of the second heat transfer section 212.
  • the first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchanger 510D of the fifth embodiment are similar to the heat exchanger 10 of the first embodiment. It may be configured, and may be configured similarly to the heat exchanger 110 of the second embodiment.
  • the ventilation resistance of the first heat transfer section 211 arranged on the most windward side is set to the lee side of the first heat transfer section 211. 2 It is larger than the ventilation resistance of the heat transfer section 212. Therefore, the pressure loss of the air due to the heat transfer tube group 11g becomes larger than the pressure loss of the air due to the heat transfer tube group 11g, so that the variation in the wind speed distribution of the air passing through the heat exchange unit 510W can be alleviated. The heat exchange performance can be improved.
  • heat exchange unit 510W in each of the first heat exchanger 510A, the second heat exchanger 510B, the third heat exchanger 510C, and the fourth heat exchanger 510D, adjacent heat transfer tube groups are seen in a plan view. At least one heat transfer tube of one heat transfer tube group overlaps with one or two heat transfer tubes of the other heat transfer tube group. According to the heat exchange unit 510W in which the heat exchangers are arranged in this way, the free passage area can be reduced as compared with the case where the heat exchangers are arranged parallel to the left-right direction. Therefore, the air flowing into each heat exchanger is likely to come into contact with the heat transfer tubes, so that the heat exchange performance can be further enhanced.
  • FIG. 19 is a schematic cross-sectional view of a heat exchange unit included in the indoor unit of the air-conditioning apparatus according to Modification 5-1 of Embodiment 5 of the present invention.
  • the air conditioning apparatus 500 in the present modification 5-1 has a refrigerant circuit 80 formed by connecting a compressor 61, a heat exchange unit 610W, an expansion valve 63, and a heat source side heat exchanger 64 by a refrigerant pipe R. ing.
  • the heat exchange unit 610W has a first heat exchanger 610A, a second heat exchanger 610B, a third heat exchanger 610C, and a fourth heat exchanger 610D, which are arranged in order from the front to the rear in the casing 101. There is.
  • the 1st heat exchanger 610A, the 2nd heat exchanger 610B, the 3rd heat exchanger 610C, and the 4th heat exchanger 610D are the 1st heat exchanger 410A and the 2nd heat exchanger 410B of the modification 4-1. It is similarly configured.
  • the positional relationship between the first heat exchanger 610A and the second heat exchanger 610B and the positional relationship between the third heat exchanger 610C and the fourth heat exchanger 610D are respectively the first heat exchange in the modification 4-1.
  • the positional relationship between the vessel 410A and the second heat exchanger 410B is the same.
  • the 2nd heat exchanger 610B and the 3rd heat exchanger 610C are arrange
  • the first heat exchanger 610A, the second heat exchanger 610B, the third heat exchanger 610C, and the fourth heat exchanger 610D are all of the heat transfer tubes 11a of the sub heat exchanger 411.
  • the outer diameter O 1 is larger than the outer diameter O 2 of each heat transfer tube 12 a of the main heat exchanger 412.
  • the first heat exchanger 610A, the second heat exchanger 610B, the third heat exchanger 610C, and the fourth heat exchanger 610D of the present modification 5-1 are the windward side sub-elements as in the third embodiment.
  • the distance between the fin portions 411b of the heat exchanger 411 may be smaller than the distance between the fin portions 412b of the leeward main heat exchanger 412.
  • the first heat exchanger 410A and the second heat exchanger 410B of the present modification 5-1 are configured such that the outer diameter O 1 and the outer diameter O 2 are the same as in the second embodiment. Good.
  • the above embodiments are preferred specific examples of the indoor unit of the air conditioning apparatus and the air conditioning apparatus, and the technical scope of the present invention is not limited to these aspects.
  • the outer diameter of the heat transfer tube forming each heat transfer part may be gradually reduced from the windward side to the leeward side.
  • the heat exchanger has three or more heat transfer parts and the fin parts of each heat transfer part are formed separately, the space between the fin parts forming each heat transfer part is from the leeward side. It may be gradually reduced toward the windward side.
  • the pipe having a circular cross section is exemplified as the pipe constituting the heat exchanger, but the pipe constituting the heat exchanger is not limited to this, and the flat pipe and the elliptical pipe in cross section Etc., various pipes may be included. Further, the space between the fin portions in each heat transfer tube does not have to be constant, and the space between the fin portions may change depending on the position.
  • the present invention is not limited to this, and instead of the four-way valve 62, a two-way valve and a three-way valve are used. You may use the structure etc. which were combined.
  • the air conditioner 500 may be configured with the refrigerant circuit 80 without providing the flow path switching means such as the four-way valve 62, and may be specialized for the cooling operation or the heating operation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Filters, Heat-Exchange Apparatuses, And Housings Of Air-Conditioning Units (AREA)

Abstract

La présente invention concerne une unité intérieure d'un dispositif de climatisation, l'unité intérieure comprenant : un boîtier dans lequel une ouverture d'admission est formée dans une partie supérieure et une ouverture de soufflage est formée dans une partie inférieure ; une soufflante qui crée un flux d'air orienté à partir de l'ouverture d'admission vers l'ouverture de soufflage ; et un échangeur de chaleur disposé dans le boîtier entre la soufflante et l'ouverture de soufflage. L'échangeur de chaleur comprend : une pluralité de tubes de transfert de chaleur agencés avec des espaces formés entre ceux-ci ; et une pluralité de parties ailette qui sont disposées en couches avec des espaces formés entre celles-ci, la pluralité de tubes de transfert de chaleur passant à travers la pluralité de parties ailette. La pluralité de tubes de transfert de chaleur comprend une première partie de transfert de chaleur disposée sur le côté le plus éloigné face au vent et une seconde partie de transfert de chaleur disposée sur le côté dans le sens du vent de la première partie de transfert de chaleur. La résistance au tirage de la première partie de transfert de chaleur est supérieure à la résistance au tirage de la seconde partie de transfert de chaleur
PCT/JP2019/005095 2019-02-13 2019-02-13 Unité intérieure de dispositif de climatisation, et dispositif de climatisation WO2020165973A1 (fr)

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JP2020571965A JPWO2020165973A1 (ja) 2019-02-13 2019-02-13 空気調和装置の室内機及び空気調和装置
PCT/JP2019/005095 WO2020165973A1 (fr) 2019-02-13 2019-02-13 Unité intérieure de dispositif de climatisation, et dispositif de climatisation

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JP2000329486A (ja) * 1999-05-17 2000-11-30 Matsushita Electric Ind Co Ltd フィン付き熱交換器
JP2001304605A (ja) * 2000-04-21 2001-10-31 Hitachi Ltd 空気調和機
JP2001336786A (ja) * 2000-05-26 2001-12-07 Hitachi Ltd 空気調和機用室外機
JP2002372266A (ja) * 2001-06-12 2002-12-26 Nippon Sheet Glass Co Ltd ファンフィルタ装置
JP2008039278A (ja) * 2006-08-04 2008-02-21 Sharp Corp 熱交換器および空気調和機の室内機
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JP3757680B2 (ja) * 1999-05-27 2006-03-22 松下電器産業株式会社 空気調和機
JP2008121950A (ja) * 2006-11-10 2008-05-29 Matsushita Electric Ind Co Ltd フィン付き熱交換器
JP2010216718A (ja) * 2009-03-17 2010-09-30 Panasonic Corp フィン付き熱交換器
JP5935167B2 (ja) * 2012-07-20 2016-06-15 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 空気調和機
JP2016200338A (ja) * 2015-04-13 2016-12-01 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 空気調和機

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JPH10292925A (ja) * 1997-02-19 1998-11-04 Daikin Ind Ltd 送風ユニット
JP2000329486A (ja) * 1999-05-17 2000-11-30 Matsushita Electric Ind Co Ltd フィン付き熱交換器
JP2001304605A (ja) * 2000-04-21 2001-10-31 Hitachi Ltd 空気調和機
JP2001336786A (ja) * 2000-05-26 2001-12-07 Hitachi Ltd 空気調和機用室外機
JP2002372266A (ja) * 2001-06-12 2002-12-26 Nippon Sheet Glass Co Ltd ファンフィルタ装置
JP2008039278A (ja) * 2006-08-04 2008-02-21 Sharp Corp 熱交換器および空気調和機の室内機
JP2008281214A (ja) * 2007-05-08 2008-11-20 Hitachi Appliances Inc 空気調和機
WO2017068725A1 (fr) * 2015-10-23 2017-04-27 三菱電機株式会社 Unité intérieure pour climatiseur

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