WO2021229794A1 - Unité intérieure de climatiseur et climatiseur - Google Patents

Unité intérieure de climatiseur et climatiseur Download PDF

Info

Publication number
WO2021229794A1
WO2021229794A1 PCT/JP2020/019439 JP2020019439W WO2021229794A1 WO 2021229794 A1 WO2021229794 A1 WO 2021229794A1 JP 2020019439 W JP2020019439 W JP 2020019439W WO 2021229794 A1 WO2021229794 A1 WO 2021229794A1
Authority
WO
WIPO (PCT)
Prior art keywords
refrigerant
air
indoor
heat
room
Prior art date
Application number
PCT/JP2020/019439
Other languages
English (en)
Japanese (ja)
Inventor
勇輝 水野
淳 西尾
宗史 池田
亮宗 石村
祐治 本村
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2020/019439 priority Critical patent/WO2021229794A1/fr
Priority to JP2020558561A priority patent/JP6847328B1/ja
Publication of WO2021229794A1 publication Critical patent/WO2021229794A1/fr

Links

Images

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
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0011—Indoor units, e.g. fan coil units characterised by air outlets
    • F24F1/0014—Indoor units, e.g. fan coil units characterised by air outlets having two or more outlet openings
    • 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
    • F24F1/0018—Indoor units, e.g. fan coil units characterised by fans
    • F24F1/0033—Indoor units, e.g. fan coil units characterised by fans having two or more fans
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/22—Means for preventing condensation or evacuating condensate

Definitions

  • the present disclosure relates to an indoor unit of an air conditioner and an air conditioner using a refrigerant whose temperature rises during endothermic process.
  • Patent Document 1 discloses an indoor unit of an air conditioner using a non-azeotropic mixed refrigerant, which has a heat exchanger including a plurality of refrigerant flow passages extending in the vertical direction.
  • the non-azeotropic mixed refrigerant flows from the bottom to the top in the heat exchanger during the cooling operation. Therefore, the temperature of the refrigerant in the lower part of the heat exchanger is lower than the temperature of the refrigerant in the upper part of the heat exchanger.
  • dew condensation is more likely to occur in the lower part than in the upper part.
  • the lower part of the heat exchanger which is more prone to condensation, often has a smaller air flow velocity than the upper part. Therefore, dew splashing of the condensed moisture in the lower part of the heat exchanger is suppressed.
  • Each extension direction of the plurality of refrigerant flow passages is orthogonal to the longitudinal direction of the air outlet, and the plurality of refrigerant flow passages are arranged in parallel with each other.
  • the longitudinal direction of the outlet is horizontal. Therefore, temperature unevenness in the horizontal direction of the air blown out from the indoor unit is suppressed. Further, in the indoor unit, the air in the upper part of the heat exchanger flows to the lower part and mixes with the air in the lower part of the heat exchanger, so that the temperature unevenness of the air blown out from the indoor unit in the vertical direction also occurs. It is suppressed.
  • the relative humidity in the room often increases due to the decrease in the saturated moisture content of the air due to the decrease in the temperature in the room during the cooling operation.
  • the air conditioner needs to keep the temperature of the refrigerant in the heat exchanger below the dew point temperature of the air in the room and cause dew condensation on the surface of the heat exchanger to dehumidify. ..
  • the air volume of the blower in the indoor unit is large, dew condensation of dew condensation water may occur.
  • the heat absorption amount of the heat exchanger becomes small, and the cooling capacity of the air conditioner decreases.
  • the indoor unit disclosed in Patent Document 1 has a structure in which water condensed on the heat exchanger does not easily fly off.
  • the refrigerant flows in the heat exchanger in the vertical direction.
  • a heat exchanger in which a refrigerant flows in the vertical direction may have a problem that the drainage property of condensed water becomes low when a heat transfer fin is attached to the air side.
  • a heat exchanger with low drainage has a reduced heat transfer performance and is less likely to generate new condensed water on the surface. Therefore, the cooling capacity and the dehumidifying capacity may not be fully exhibited.
  • the present disclosure has been made to solve the above-mentioned problems, and an indoor unit of an air conditioner and an air conditioner capable of suppressing an increase in relative humidity in the room while maintaining a cooling capacity.
  • the purpose is to provide.
  • the indoor unit of the air conditioner according to the present disclosure includes an indoor heat exchanger that exchanges heat between the indoor air and the refrigerant, and the indoor heat exchanger that sends the indoor air to the indoor heat exchanger and exchanges heat with the refrigerant.
  • a blower mechanism for sending the air into the room is provided, and the indoor heat exchangers have a plurality of heat transfer tubes in parallel with each other and in which the refrigerant is circulated in the horizontal direction to exchange heat with the air. Have.
  • the air conditioner according to the present disclosure is an outdoor unit that exchanges heat between the refrigerant and the outdoor air in a refrigerant circuit that circulates the refrigerant, and heat exchange between the refrigerant and the indoor air. It has an indoor unit that air-conditions the room, and the indoor unit has an indoor heat exchanger that exchanges heat between the indoor air and the refrigerant, and the indoor heat exchanger that exchanges heat between the indoor air and the indoor heat exchanger.
  • the room heat exchanger is provided with a blower mechanism for sending and sending the air after heat exchange with the refrigerant into the room, and the indoor heat exchangers are parallel to each other and the heat exchanger is circulated in the horizontal direction to flow the refrigerant. It has a plurality of heat transfer tubes that exchange heat with the air.
  • the air conditioner according to the present disclosure includes an indoor unit that exchanges heat between the first refrigerant and the air in the room to air-condition the room in a first refrigerant circuit that circulates the first refrigerant, and a second indoor unit.
  • the outdoor unit that exchanges heat between the second refrigerant and the outdoor air, and the first refrigerant included in the first refrigerant circuit and the second refrigerant circuit. It has an intermediate heat exchanger that exchanges heat with the second refrigerant
  • the indoor unit includes an indoor heat exchanger that exchanges heat between the air in the room and the first refrigerant, and the room.
  • the indoor heat exchangers are arranged in parallel with each other and include a ventilation mechanism that sends the air of the room to the indoor heat exchanger and sends the air after heat exchange with the first refrigerant into the room. It has a plurality of heat transfer tubes that allow the first refrigerant to flow in the horizontal direction and exchange heat with the air.
  • a plurality of heat transfer tubes in the indoor heat exchanger circulate the refrigerant in the horizontal direction to exchange heat between the refrigerant and air. This improves the drainage property of the condensed water on the surface of the heat transfer tube through which the refrigerant flows. As a result, it is possible to suppress a decrease in the heat transfer performance of the heat transfer tube, and it is possible to suppress a decrease in the occurrence of dew condensation in the heat transfer tube. Therefore, the indoor unit and the air conditioner can suppress an increase in relative humidity in the room while maintaining the cooling capacity.
  • FIG. It is a schematic diagram which illustrates the inside of the indoor unit of the air conditioner which concerns on Embodiment 1.
  • FIG. It is a figure which illustrates the temperature distribution of the refrigerant in the heat transfer tube in Embodiment 1 and the distribution of the air volume by an indoor blower in the horizontal direction.
  • FIG. It is a schematic diagram which illustrates the 2nd internal structure of the room heat exchanger in Embodiment 1.
  • FIG. It is a schematic diagram which illustrates the 3rd internal structure of the indoor heat exchanger in Embodiment 1.
  • FIG. It is a schematic diagram which illustrates the internal structure of an indoor unit.
  • FIG. 1 It is a schematic diagram which illustrates the structure of an indoor unit and the flow of wind in an indoor unit 100. It is a schematic diagram which illustrates the flow of the wind in an indoor unit and a duct. It is a schematic diagram which illustrates the internal structure of the indoor unit which concerns on modification 1 in Embodiment 1. FIG. It is a schematic diagram which illustrates the appearance of the indoor unit which concerns on modification 1 in Embodiment 1. FIG. It is a schematic diagram which illustrates the inside of the indoor unit which concerns on modification 2 in Embodiment 1. FIG. It is a schematic diagram which illustrates the appearance of the indoor unit which concerns on modification 2 in Embodiment 1. FIG.
  • FIG. 1 It is a figure which illustrates the temperature distribution of the refrigerant in the heat transfer tube in the modification 2 of Embodiment 1 and the distribution of the air volume in the horizontal direction by an indoor blower. It is a schematic diagram which illustrates the appearance of the indoor unit which concerns on modification 3 in Embodiment 1.
  • FIG. It is a schematic diagram which illustrates the air-conditioning apparatus which concerns on Embodiment 2.
  • FIG. It is a schematic diagram which shows the flow of the refrigerant at the time of a heating operation in the indoor heat exchanger illustrated in FIG.
  • FIG. 1 is a schematic diagram illustrating the inside of an indoor unit of the air conditioner according to the first embodiment.
  • the indoor unit 100 according to the first embodiment air-conditions the room by exchanging heat between the refrigerant circulated inside and the air in the room which is the space to be air-conditioned, and sending out the air after the heat exchange into the room.
  • the indoor unit 100 may be a ceiling-embedded indoor unit, a wall-mounted indoor unit, or a ceiling-suspended indoor unit.
  • the indoor unit 100 includes one or more indoor blowers 1, an indoor heat exchanger 2, a refrigerant temperature sensor 3, an air temperature sensor 4, a humidity sensor 5, and a control unit 6.
  • FIG. 1 shows an example in which the indoor unit 100 includes two indoor blowers 1, but the number of indoor blowers 1 included in the indoor unit 100 is not limited to two and may be one. However, it may be three or more. Hereinafter, a case where the number of indoor blowers 1 included in the indoor unit 100 is two will be described.
  • the indoor blower 1 includes, for example, a blower fan 10 such as a propeller fan or a sirocco fan, and a drive source such as a fan motor 11 for driving the blower fan 10 (see FIG. 6).
  • the shape of the blower fan 10 is not particularly limited.
  • the blower fan 10 and the fan motor 11 will be described later.
  • the indoor blower 1 guides the indoor air to the indoor heat exchanger 2 in the indoor unit 100, and sends out the air after the heat exchange in the indoor heat exchanger 2 into the room.
  • the indoor heat exchanger 2 exchanges heat between the air taken into the indoor unit 100 by the indoor blower 1 and the refrigerant.
  • the refrigerant absorbs heat from the indoor air. Further, when the indoor unit 100 is performing the heating operation, the refrigerant dissipates heat to the indoor air.
  • the indoor heat exchanger 2 has a plurality of heat transfer tubes 20.
  • Each of the plurality of heat transfer tubes 20 circulates a refrigerant inside.
  • Each heat transfer tube 20 serves as a flow path for the refrigerant.
  • the air taken into the interior of the indoor unit 100 by the indoor blower 1 exchanges heat with the refrigerant flowing through the plurality of heat transfer tubes 20.
  • the plurality of heat transfer tubes 20 in the first embodiment are arranged so as to be parallel to each other, and each of them is arranged so that the refrigerant flows in the same direction in the horizontal direction.
  • solid arrows indicate the direction and direction of refrigerant flow
  • white arrows indicate the direction and direction of wind.
  • the refrigerant temperature sensor 3 detects the temperature of the refrigerant in the heat transfer tube 20.
  • the refrigerant temperature sensor 3 is provided in the heat transfer tube 20 at at least one of the inlet and outlet of the refrigerant. In the first embodiment, the refrigerant temperature sensor 3 is provided at least at the inlet of the liquid refrigerant.
  • inlet refers to the inlet of the refrigerant in the indoor heat exchanger 2 or the inlet of the refrigerant in the heat transfer tube 20 unless otherwise specified.
  • outlet refers to the outlet of the refrigerant in the indoor heat exchanger 2 or the outlet of the refrigerant in the heat transfer tube 20 unless otherwise specified.
  • the air temperature sensor 4 and the humidity sensor 5 are provided at an air suction port (not shown) formed in the indoor unit 100.
  • the air temperature sensor 4 detects the temperature of the air in the room.
  • the humidity sensor 5 detects the humidity in the room.
  • the control unit 6 acquires the detection result from the refrigerant temperature sensor 3, the air temperature sensor 4, and the humidity sensor 5. Then, the control unit 6 controls the indoor blower 1 to blow air based on the detection result.
  • a mechanism for taking air from the room into the room unit 100 and sending the air after heat exchange with the refrigerant in the room heat exchanger 2 into the room will also be referred to as a ventilation mechanism.
  • the control unit 6 and the indoor blower 1 are included in the blower mechanism.
  • the relative humidity in the room increases due to the decrease in the saturated moisture content of the air due to the decrease in the temperature in the room.
  • the temperature of the refrigerant in the indoor heat exchanger 2 is set to be equal to or lower than the dew point temperature of air, the following problems occur.
  • the air volume of the indoor blower 1 is large, dew splashing of condensed water may occur.
  • the air volume of the indoor blower 1 is small, the heat absorption amount of the indoor heat exchanger 2 becomes small, and the cooling capacity may decrease.
  • the indoor unit 100 has the configuration and functions described in detail below, and performs the operations described below. Unless otherwise specified, the configuration, function, operation, and the like of the indoor unit 100 during the cooling operation will be described below.
  • the temperature of the refrigerant in the first embodiment rises due to endothermic process. Therefore, during the cooling operation, the temperature of the refrigerant on the inlet side is lower than the temperature of the refrigerant on the outlet side. Since the refrigerant flows horizontally in the heat transfer tube 20 and absorbs heat, temperature unevenness of the refrigerant occurs in the horizontal direction. That is, the temperature of the refrigerant increases in the horizontal direction from the inlet to the outlet.
  • the heat transfer tube 20 is divided into a region where the temperature of the refrigerant is low and a region where the temperature of the refrigerant is high, the region where the temperature of the refrigerant is low is the first region, and the region where the temperature is high is the second region.
  • One of the two indoor blowers 1 sends the indoor air to the first region.
  • the other sends the air in the room to the second region.
  • the indoor blower 1 that blows air to the first region will be referred to as the first indoor blower 1A
  • the indoor blower 1 that blows air to the second region will be referred to as the second indoor blower 1B.
  • FIG. 2 is a diagram illustrating the temperature distribution of the refrigerant in the heat transfer tube in the first embodiment and the horizontal distribution of the air volume by the indoor blower.
  • the solid line graph in FIG. 2 illustrates the temperature distribution of the refrigerant in the heat transfer tube 20.
  • the temperature of the refrigerant in the first region is lower than the temperature of the refrigerant in the second region.
  • the control unit 6 causes the indoor unit 100 to perform a dehumidifying operation in the first region and a cooling operation in the second region. It is assumed that the temperature of the refrigerant in the first region is equal to or lower than the dew point temperature of the air in the room, and the temperature of the refrigerant in the second region is higher than the dew point temperature.
  • the control unit 6 controls at least one of the first indoor blower 1A and the second indoor blower 1B so that the air volume by the first indoor blower 1A is smaller than the air volume by the second indoor blower 1B.
  • the control unit 6 controls the first indoor blower 1A so that the flow rate of the air that exchanges heat with the refrigerant in the first region is equal to or less than the predetermined first limit flow rate.
  • the first limited flow rate corresponds to the maximum flow rate of the air flowing into the indoor heat exchanger 2 that does not cause dew splash when dew condensation occurs in the indoor heat exchanger 2.
  • the fan motor 11 in the first indoor blower 1A reduces the rotation speed according to the instruction from the control unit 6. As a result, the blower fan 10 (see FIG. 6) in the first indoor blower 1A blows air with a small air volume at which the condensed water does not fly.
  • the control unit 6 controls the second indoor blower 1B so that the flow rate of the air that exchanges heat with the refrigerant in the second region becomes equal to or higher than the predetermined second limit flow rate.
  • the second limited flow rate is determined based on the cooling capacity or the heating capacity desired by the user.
  • the second limit flow rate corresponds to, for example, the lowest flow rate of air that can achieve the cooling capacity or heating capacity desired by the user.
  • the fan motor 11 in the second indoor blower 1B increases the rotation speed according to the instruction from the control unit 6. As a result, the blower fan 10 in the second indoor blower 1B blows air at a volume sufficiently large to satisfy the cooling capacity or the heating capacity desired by the user.
  • the white arrow in FIG. 1 indicates a larger air volume as the width increases.
  • the air volume from the first indoor blower 1A blowing into the first region is shown as small, and the air volume from the second indoor blower 1B blowing into the second region is shown as large.
  • the broken line graph in FIG. 2 shows the distribution of the air volume in the horizontal direction by the indoor blower 1. As the graph shows, the air volume to the second region is larger than the air volume to the first region.
  • FIG. 3 is a schematic diagram illustrating the first internal structure of the indoor heat exchanger according to the first embodiment.
  • FIG. 4 is a schematic diagram illustrating the second internal structure of the indoor heat exchanger according to the first embodiment.
  • FIG. 5 is a schematic diagram illustrating the third internal structure of the indoor heat exchanger according to the first embodiment.
  • the indoor heat exchanger 2 further includes a plurality of heat transfer promoting fins 21, a liquid header 22, and a gas header 23 in addition to the plurality of heat transfer tubes 20.
  • a plurality of heat transfer promoting fins 21 are provided for improving the efficiency of heat exchange between air and the refrigerant. Since the direction in which the refrigerant flows in the heat transfer tube 20 is the horizontal direction, the plurality of heat transfer promoting fins 21 are arranged in parallel in the horizontal direction.
  • the black arrows in FIGS. 3 to 5 indicate the direction and direction in which the refrigerant flows, and the white arrows indicate the direction and direction in which the air flows. Therefore, in FIGS. 3 to 5, the x direction is the horizontal direction. Then, either the y direction or the z direction is the vertical direction.
  • the dew condensation water falls downward in the y direction or the z direction, which is the vertical direction.
  • the width of the heat transfer promoting fins 21 on the plane orthogonal to the vertical direction is small.
  • the width of the heat transfer promoting fins 21 in the xy plane is small.
  • the width of the heat transfer promoting fins 21 in the zx plane is small.
  • the liquid header 22 distributes the liquid refrigerant to each heat transfer tube 20 during the cooling operation.
  • the gas header 23 the gas refrigerants from the heat transfer tubes 20 merge.
  • the inlet of the liquid refrigerant in the liquid header 22 and the outlet of the gas refrigerant in the gas header 23 are in the indoor heat exchanger 2. They are arranged diagonally. When the inlet and the outlet are not arranged diagonally in the indoor heat exchanger 2, the flow rate of the refrigerant is concentrated on the shortest heat transfer tube 20 between the inlet and the outlet. There is a risk that it will end up.
  • FIGS. 3 to 5 it is assumed that the x direction and the y direction are the horizontal direction and the z direction is the vertical direction.
  • the refrigerant flowing into the indoor heat exchanger 2 shown in FIG. 3 is distributed in the z direction in the liquid header 22.
  • Some of the refrigerant distributed in the z direction flows through the heat transfer tube 20 in the negative direction in the x direction, and the remaining refrigerant flows in the positive direction in the y direction.
  • the refrigerant flowing in the positive direction in the y direction is distributed in the y direction, flows into the heat transfer tube 20, and flows in the heat transfer tube 20 in the negative direction in the x direction.
  • the refrigerants flowing through the heat transfer tubes 20 merge in the horizontal direction and then merge in the vertical direction in the gas header 23.
  • the refrigerant flowing into the indoor heat exchanger 2 shown in FIG. 4 is distributed into a refrigerant flowing in the positive direction in the y direction and a refrigerant flowing in the positive direction in the z direction.
  • the refrigerant flowing in the positive direction in the y direction is further distributed in the y direction, and each of the distributed refrigerants flows in the positive direction in the z direction.
  • the refrigerant flowing in the positive direction in the z direction is further distributed in the z direction, flows into the heat transfer tube 20, and flows in the negative direction in the x direction.
  • the refrigerant flowing through the heat transfer tube 20 merges in the z direction and further merges in the horizontal direction.
  • the direction of the refrigerant flowing through the liquid header 22 is opposite to the direction of the refrigerant flowing through the liquid header 22 in the indoor heat exchanger 2 shown in FIG.
  • the flow direction and direction of the refrigerant in FIG. 5 are the same as those in FIG. 3 except for the liquid header 22. In this way, space can be saved by making the direction in which the refrigerant flows in either the liquid header 22 or the gas header 23 opposite to the direction in which the refrigerant flows in the other.
  • 3 to 5 show an example in which the indoor heat exchanger 2 distributes the liquid refrigerant by the liquid header 22, but in order to further improve the distributability of the liquid refrigerant, the indoor heat exchanger 2 has a liquid header.
  • a distributor may be used instead of 22.
  • FIG. 6 is a schematic diagram illustrating the internal structure of the indoor unit.
  • each direction in the xyz direction corresponds to each direction in the xyz direction in FIGS. 3 to 5. Therefore, in FIG. 6, the x direction corresponds to the horizontal direction. Further, in FIG. 6, it is assumed that the y direction is the horizontal direction and the z direction is the vertical direction. Further, the positive and negative directions in each direction correspond to the positive and negative directions in each direction in FIGS. 3 to 5. Also in FIG. 6, similarly to FIGS. 3 to 5, the heat transfer tube 20 in the indoor heat exchanger 2 is assumed to be along the x direction. In FIG. 6, the refrigerant flows inside the indoor heat exchanger 2 in the positive direction in the x direction.
  • the first indoor blower 1A and the second indoor blower 1B included in the indoor unit 100 are arranged in the x direction, face the indoor heat exchanger 2, and blow air in the negative direction in the y direction.
  • the first indoor blower 1A blows air to the first region on the upstream side of the refrigerant in the indoor heat exchanger 2.
  • the second indoor blower 1B blows air to the second region on the downstream side of the refrigerant in the indoor heat exchanger 2.
  • Each indoor blower 1 includes a blower fan 10 and a fan motor 11.
  • the positional relationship between the blower fan 10 and the fan motor 11 shown in FIG. 6 is an example, and is not limited to this.
  • the fan motor 11 is arranged at a positive position in the y direction with respect to the blower fan 10. You may be.
  • the drain pan 8 is arranged at the lower portion of the indoor heat exchanger 2 in the z direction.
  • FIG. 7 is a schematic diagram illustrating the structure of the indoor unit and the flow of wind in the indoor unit 100.
  • the duct 9 is connected to the ceiling-embedded indoor unit 100.
  • the duct 9 is formed with a first opening 90 for allowing the wind from the indoor unit 100 to flow in and a second opening 91 for allowing the wind to flow out into the room.
  • the second opening 91 faces the floor surface in the room.
  • the white arrows in FIG. 7 indicate the direction and direction of the wind from each indoor blower 1.
  • the width of the white arrow indicates the magnitude of the air volume, and it is assumed that the larger the width, the larger the air volume.
  • the air volume from the first indoor blower 1A is smaller than the air volume from the second indoor blower 1B.
  • the temperature of the wind blown from the first indoor blower 1A is lower than the temperature of the wind blown from the second indoor blower 1B. Therefore, the air flowing from the indoor unit 100 to the duct 9 has uneven temperature and uneven air volume.
  • FIG. 8 is a schematic diagram illustrating the flow of wind between the indoor unit and the duct.
  • the y direction in FIG. 8 corresponds to the y direction in FIG. 7, and the z direction in FIG. 8 corresponds to the z direction in FIG. 7.
  • the direction and direction in which the wind flows are indicated by white arrows.
  • the wind from the indoor blower 1 blows into the room through the duct 9.
  • each air sent out by the first indoor blower 1A and the second indoor blower 1B mixes with each other and flows out into the room. As a result, the temperature unevenness and the air volume unevenness of the wind blown into the room are reduced.
  • FIG. 9 is a schematic diagram illustrating the internal structure of the indoor unit according to the first modification of the first embodiment.
  • the x-direction in FIGS. 9 corresponds to the x-direction which is the horizontal direction in FIGS. 3 to 7
  • the z-direction in FIG. 9 corresponds to the z-direction which is the vertical direction in FIGS. 3 to 8. do.
  • the indoor heat exchanger 2 is arranged at the lower portion in the vertical direction with respect to the indoor blower 1. In FIG.
  • the two indoor blowers 1 are arranged in the x direction and blow in the z direction.
  • the air from the first indoor blower 1A is sent to the first region on the upstream side of the refrigerant in the indoor heat exchanger 2, and the air from the second indoor blower 1B is sent to the second region on the downstream side.
  • the first region is used for dehumidifying purposes and the second region is used for cooling purposes. Therefore, the control unit 6 controls the air volume of the first indoor blower 1A to be small so that dew skipping does not occur, and controls the air volume of the second indoor blower 1B to be large enough to maintain the cooling capacity.
  • a drain pan 8 (not shown) is installed at least in the lower portion of the first region in the vertical direction.
  • Each indoor blower 1 includes a blower fan 10 and a fan motor 11 as described above.
  • the shape of the blower fan 10 is not particularly limited.
  • FIG. 10 is a schematic diagram illustrating the appearance of the indoor unit according to the modified example 1 in the first embodiment.
  • the x-direction in FIG. 10 is assumed to correspond to the x-direction which is the horizontal direction in FIG.
  • the y direction in FIG. 10 is assumed to correspond to the y direction in the horizontal direction in FIGS. 3 to 8.
  • the z direction in FIG. 10 is assumed to correspond to the z direction which is the vertical direction in FIG. Also in FIG. 10, it is assumed that the refrigerant flows in the x direction in the indoor heat exchanger 2 in the positive direction.
  • the bottom surface of the indoor unit 100 which is the lowermost surface in the vertical direction and faces the floor surface of the room, is referred to as a bottom surface 101.
  • the bottom surface 101 is formed with an outlet 102, which is an opening for blowing air from the indoor unit 100 into the room.
  • the outlet 102 of the indoor unit 100 is provided with a flap 103 for changing the opening degree of the outlet 102 to adjust the air volume from the outlet 102 and the angle of the wind from the vertical direction.
  • the flap 103 adjusts the opening degree of the outlet 102 by opening and closing under the control of the control unit 6.
  • the blower mechanism in the first modification includes the air outlet 102 and the flap 103 together with the indoor blower 1 and the control unit 6.
  • the wind from the indoor unit 100 is sent out into the room in a direction and an air volume according to the angle of the flap 103.
  • the white arrow 12A in FIG. 10 indicates the direction and direction of the air sent out by the first indoor blower 1A in FIG. 9, and the white arrow 12B in FIG. 10 indicates the direction and direction of the second indoor blower 1B in FIG. Indicates the direction and direction of the air sent out by.
  • the wider the width of the white arrow the larger the air volume.
  • the air volume from the first indoor blower 1A is smaller than the air volume from the second indoor blower 1B.
  • the indoor unit 100 internally mixes the air that has exchanged heat with the refrigerant in the first region and the air that has exchanged heat with the refrigerant in the second region, and causes the air to flow out into the room. It may be connected to a duct such as the duct 9.
  • the duct corresponds to the wall-mounted indoor unit 100. As the indoor unit 100 blows air through the duct in this way, the temperature unevenness and the air volume unevenness of the air from the indoor unit 100 are reduced.
  • FIG. 11 is a schematic diagram illustrating the inside of the indoor unit according to the second modification in the first embodiment.
  • FIG. 12 is a schematic diagram illustrating the appearance of the indoor unit according to the modified example 2 in the first embodiment.
  • FIG. 13 is a diagram illustrating the temperature distribution of the refrigerant in the heat transfer tube and the distribution of the air volume in the horizontal direction by the indoor blower in the second modification of the first embodiment.
  • the components included in the indoor unit 100 according to the modification 2 shown in FIG. 11 are the same as the components included in the indoor unit 100 described with reference to FIG. 1 except for the following points. The description of similar components will be omitted.
  • the indoor unit 100 according to the second modification in the first embodiment includes at least one indoor blower 1.
  • FIG. 11 shows an example in which the indoor unit 100 includes one indoor blower 1, but the number of indoor blowers 1 included in the indoor unit 100 is not limited to one, and may be two or more. You may.
  • the second modification a case where the number of indoor blowers 1 included in the indoor unit 100 is one will be described.
  • the solid arrows in FIG. 11 indicate the direction and direction in which the refrigerant flows. The direction corresponds to the x direction in FIGS. 3 to 5.
  • FIG. 12 shows the appearance of the indoor unit 100 according to the modified example 2 in the case of the wall-mounted type.
  • the x-direction in FIG. 12 is assumed to correspond to the x-direction which is the horizontal direction in FIG.
  • the y direction in FIG. 12 is assumed to correspond to the y direction which is the horizontal direction in FIG.
  • the z-direction in FIG. 12 is assumed to correspond to the z-direction which is the vertical direction in FIG.
  • the refrigerant flows in the x direction in the indoor heat exchanger 2 in the positive direction as described above.
  • the temperature of the refrigerant rises when it absorbs heat, as described above. Therefore, the temperature of the refrigerant in the first region on the upstream side of the indoor heat exchanger 2 is lower than the temperature of the refrigerant in the second region on the downstream side.
  • a plurality of outlets 102 are formed on the bottom surface 101 of the indoor unit 100 according to the second modification.
  • the plurality of outlets 102 are arranged side by side in the x direction.
  • FIG. 12 shows an example in which two outlets 102 are formed on the bottom surface 101, but three or more outlets 102 may be formed.
  • two two outlets 102 are formed on the bottom surface 101 will be described.
  • Air that has exchanged heat with the refrigerant in the first region is blown out from one of the two outlets 102, and air that has exchanged heat with the refrigerant in the second region is blown out from the other.
  • the outlet 102 for allowing the air that has exchanged heat with the refrigerant in the first region to flow out into the room will be referred to as the first outlet 102A
  • the air that has exchanged heat with the refrigerant in the second region will be referred to as the indoor outlet 102A.
  • the outlet 102 for flowing out is referred to as a second outlet 102B.
  • the first outlet 102A and the second outlet 102B may communicate with each other to form one outlet 102.
  • the first flap 103A for adjusting the air volume from the first outlet 102A and the angle of the wind from the vertical direction by changing the opening degree of the first outlet 102A to the first outlet 102A.
  • the second flap 103B for adjusting the air volume from the second outlet 102B and the angle of the wind from the vertical direction by changing the opening degree of the second outlet 102B to the second outlet 102B.
  • the first flap 103A and the second flap 103B are opened and closed by the control from the control unit 6.
  • the blower mechanism in the second modification includes the first outlet 102A, the second outlet 102B, the first flap 103A, and the second flap 103B together with the indoor blower 1 and the control unit 6.
  • the wind from the indoor unit 100 is sent out into the room in the direction and air volume according to the angle of the flap 103.
  • the control unit 6 controls at least one of the first flap 103A and the second flap 103B so that the opening degree of the first outlet 102A is smaller than the opening degree of the second outlet 102B.
  • the flow rate of the air that has exchanged heat with the refrigerant in the first region into the room is smaller than the flow rate of the air that has exchanged heat with the refrigerant in the second region into the room.
  • the control unit 6 controls the first flap 103A so that the flow rate of the air that has exchanged heat with the refrigerant in the first region into the room is equal to or less than the above-mentioned first limit flow rate.
  • the first flap 103A adjusts the opening degree of the first outlet 102A to an opening degree equal to or lower than the first opening degree in response to an instruction from the control unit 6.
  • the first opening degree is an opening degree in which the flow rate of the air that has exchanged heat with the refrigerant in the first region into the room becomes the first limiting flow rate. In this way, the indoor unit 100 suppresses dew splashing into the room in the first region by reducing the flow rate of the air that has exchanged heat with the refrigerant in the first region into the room.
  • the control unit 6 controls the second flap 103B so that the flow rate of the air that has exchanged heat with the refrigerant in the second region into the room becomes equal to or higher than the above-mentioned second limit flow rate.
  • the second flap 103B adjusts the opening degree of the second outlet 102B to an opening degree equal to or higher than the second opening degree in response to an instruction from the control unit 6.
  • the second opening degree is an opening degree in which the flow rate of the air that has exchanged heat with the refrigerant in the second region into the room becomes the second limiting flow rate.
  • the indoor unit 100 aims to maintain the cooling capacity desired by the user by increasing the flow rate of the air that has exchanged heat with the refrigerant in the second region into the room.
  • the white arrows 13A shown in FIGS. 11 and 12 indicate the direction and direction in which the air heat-exchanged with the refrigerant in the first region flows
  • the white arrows 13B indicate the direction and direction in which the air heat-exchanged with the refrigerant in the second region flows. Indicates the flow direction and direction. Similar to the above, the wider the width of the white arrow, the larger the air volume.
  • the solid line graph in FIG. 13 exemplifies the temperature distribution of the refrigerant in the heat transfer tube 20 that circulates the refrigerant in the horizontal direction.
  • the broken line graph illustrates the air volume from the indoor unit 100 in the horizontal direction.
  • the temperature of the refrigerant in the first region of the heat transfer tube 20 is lower than the temperature of the refrigerant in the second region.
  • the control unit 6 in the second modification of the first embodiment controls at least one of the first flap 103A and the second flap 103B, and changes the opening degree of the first outlet 102A to the opening degree of the second outlet 102B. Make it smaller than.
  • the indoor unit 100 also maintains the cooling capacity while suppressing dew splash.
  • the indoor unit 100 may include a plurality of indoor blowers 1.
  • the indoor unit 100 may include the first indoor blower 1A and the second indoor blower 1B as described above.
  • the indoor unit 100 can realize higher cooling performance and can further suppress dew flying when dew condensation water is generated.
  • the indoor unit 100 according to the second modification is like the duct 9 described above, in which the air that has exchanged heat with the refrigerant in the first region and the air that has exchanged heat with the refrigerant in the second region are internally mixed and discharged into the room. It may be connected to a duct.
  • the duct corresponds to the wall-mounted indoor unit 100. As the indoor unit 100 blows air through the duct in this way, the temperature unevenness and the air volume unevenness of the air from the indoor unit 100 are reduced.
  • FIG. 14 is a schematic diagram illustrating the appearance of the indoor unit according to the modified example 3 in the first embodiment.
  • the x-direction in FIG. 14 corresponds to the x-direction which is the horizontal direction in FIGS. 10 and 12 and the like.
  • the y direction in FIG. 14 corresponds to the y direction in the horizontal direction in FIGS.
  • the z-direction in FIG. 14 corresponds to the z-direction which is the vertical direction in FIGS. 10 and 12 and the like.
  • FIG. 14 similarly to the above, it is assumed that the refrigerant flows in the x direction in the indoor heat exchanger 2 in the positive direction. It is assumed that the temperature of the refrigerant rises when it absorbs heat, similar to the above-mentioned one. Therefore, the temperature of the refrigerant on the upstream side of the indoor heat exchanger 2 is lower than the temperature of the refrigerant on the downstream side.
  • a plurality of outlets 102 are formed on one surface of the indoor unit 100, which is orthogonal to the horizontal direction. In addition, this one side is referred to as a side surface below. It is assumed that the number of outlets 102 in the modified example 3 is two as in the modified example 2.
  • the two outlets 102 are arranged side by side in the x direction.
  • One of the two outlets 102 is the first outlet 102A for allowing the air that has exchanged heat with the refrigerant in the first region to flow out into the room, and the other is the air that has exchanged heat with the refrigerant in the second region.
  • It is a second outlet 102B for flowing out into the room.
  • the first outlet 102A and the second outlet 102B may communicate with each other to form one outlet 102.
  • the first outlet 102A is provided with the opening degree of the first outlet 102A to be changed to obtain the air volume from the first outlet 102A and the angle of the wind from the vertical direction.
  • a first flap 103A for adjustment is provided.
  • the opening degree of the second outlet 102B is changed to adjust the air volume from the second outlet 102B and the angle of the wind from the vertical direction.
  • a flap 103B is provided.
  • the opening / closing operation of the first flap 103A and the second flap 103B is controlled by the control unit 6.
  • the ventilation mechanism in the modification 3 includes the first outlet 102A, the second outlet 102B, the first flap 103A, and the second flap 103B together with the indoor blower 1 and the control unit 6. included.
  • control unit 6 has at least one of the first flap 103A and the second flap 103B so that the opening degree of the first outlet 102A is smaller than the opening degree of the second outlet 102B. Control one. As a result, the flow rate of the air that has exchanged heat with the refrigerant in the first region into the room is smaller than the flow rate of the air that has exchanged heat with the refrigerant in the second region into the room.
  • the control unit 6 controls the first flap 103A so that the flow rate of the air that has exchanged heat with the refrigerant in the first region into the room is equal to or less than the above-mentioned first limit flow rate.
  • the indoor unit 100 suppresses dew splashing into the room in the first region by reducing the flow rate of the air that has exchanged heat with the refrigerant in the first region into the room.
  • the control unit 6 controls the second flap 103B so that the flow rate of the air that has exchanged heat with the refrigerant in the second region into the room becomes equal to or higher than the above-mentioned second limit flow rate.
  • the indoor unit 100 maintains the cooling capacity desired by the user by increasing the flow rate of the air that has exchanged heat with the refrigerant in the second region into the room.
  • the white arrow 14A in FIG. 14 indicates the direction and direction in which the air that has exchanged heat with the refrigerant in the first region flows.
  • the white arrow 14B indicates the direction and direction in which the air that has exchanged heat with the refrigerant in the second region flows. Similar to the above, the wider the width of the white arrow, the larger the air volume.
  • the indoor unit 100 internally mixes the air that has exchanged heat with the refrigerant in the first region and the air that has exchanged heat with the refrigerant in the second region, and causes the air to flow out into the room. It may be connected to the duct 9. As the indoor unit 100 blows air through the duct 9 in this way, the temperature unevenness and the air volume unevenness of the air from the indoor unit 100 are reduced.
  • the first region is used for dehumidification.
  • the humidity detected by the humidity sensor 5 is lower than a predetermined threshold value, the occurrence of dew condensation may be reduced even if the temperature of the refrigerant in the first region is equal to or lower than the dew point temperature of air. be. In this case, the above-mentioned process for suppressing dew splash becomes unnecessary. Therefore, when the humidity detected by the humidity sensor 5 is equal to or less than the threshold value, the control unit 6 performs an air blowing process for realizing the cooling capacity instead of the above process for suppressing dew splash.
  • the blower 1A may be controlled.
  • the flow rate of the air heat-exchanged with the refrigerant in the first region realizes the cooling capacity.
  • the first flap 103A may be controlled so as to have a flow rate for the above.
  • the indoor unit 100 according to the first embodiment includes an indoor heat exchanger 2 and a ventilation mechanism.
  • the indoor heat exchanger 2 exchanges heat between the indoor air and the refrigerant.
  • the blower mechanism sends the indoor air to the indoor heat exchanger 2 and sends out the air after heat exchange with the refrigerant into the room.
  • the indoor heat exchanger 2 has a plurality of heat transfer tubes 20.
  • the plurality of heat transfer tubes 20 are parallel to each other and allow the refrigerant to flow in the horizontal direction to exchange heat with the air.
  • the indoor unit 100 according to the first embodiment can suppress an increase in relative humidity in the room while maintaining the cooling capacity.
  • the indoor heat exchanger 2 in the first embodiment circulates the refrigerant in the same direction in a plurality of heat transfer tubes 20.
  • the region where the temperature of the refrigerant in each of the plurality of heat transfer tubes 20 is low becomes a region common to the plurality of heat transfer tubes 20 in the horizontal direction.
  • the region where the temperature of the refrigerant in each of the plurality of heat transfer tubes 20 is high becomes a region common to the plurality of heat transfer tubes 20 in the horizontal direction.
  • the blower mechanism measures the flow rate of air that exchanges heat with the refrigerant in the first region where the temperature of the refrigerant is low among the first region and the second region in each of the plurality of heat transfer tubes 20, and the second region where the temperature of the refrigerant is high. It should be smaller than the flow rate of the air that exchanges heat with the refrigerant in. As a result, the indoor unit 100 according to the first embodiment can suppress dew flying during dehumidification while maintaining the cooling capacity.
  • the blower mechanism in the first embodiment sets the flow rate of the air that exchanges heat with the refrigerant in the first region to a predetermined first limit flow rate or less.
  • the indoor unit 100 according to the first embodiment can more reliably suppress dew flying during dehumidification.
  • the first limited flow rate in the first embodiment is the maximum flow rate at a flow rate that does not cause dew splashing when dew condensation occurs in the indoor heat exchanger 2.
  • the indoor unit 100 according to the first embodiment can more reliably suppress dew flying during dehumidification.
  • the indoor unit 100 further includes a humidity sensor 5 for detecting the humidity in the room.
  • the ventilation mechanism sets the flow rate of the air that exchanges heat with the refrigerant in the first region to the first limit flow rate or less. Therefore, the ventilation mechanism performs a process for suppressing dew splash when the humidity in the room is high and dew condensation is likely to occur.
  • the indoor unit 100 performs the dehumidification treatment at the timing when dehumidification is necessary, and does not perform the dehumidification treatment at the timing when it is not necessary, and the operation efficiency is improved.
  • the blower mechanism in the first embodiment sets the flow rate of the air that exchanges heat with the refrigerant in the second region to a predetermined second limit flow rate or higher.
  • the indoor unit 100 according to the first embodiment can maintain the cooling capacity or the heating capacity.
  • the second limited flow rate in the first embodiment is determined based on the cooling capacity or the heating capacity desired by the user. As a result, the indoor unit 100 according to the first embodiment can maintain the cooling capacity or the heating capacity.
  • the blower mechanism in the first embodiment includes a first room blower 1A, a second room blower 1B, and a control unit 6.
  • the first indoor blower 1A sends the indoor air to the first region, and also blows the air after heat exchange with the refrigerant in the first region into the room.
  • the second indoor blower 1B sends the indoor air to the second region, and also blows the air after heat exchange with the refrigerant in the second region into the room.
  • the control unit 6 controls the first indoor blower 1A and the second indoor blower 1B.
  • the control unit 6 controls at least one of the first room blower 1A and the second room blower 1B so that the air volume by the first room blower 1A is smaller than the air volume by the second room blower 1B.
  • the indoor unit 100 can blow the air that has exchanged heat with the refrigerant in the first region into the room with a smaller air volume than the air that has exchanged heat with the refrigerant in the second region. Therefore, the indoor unit 100 can achieve both suppression of dew splash and maintenance of cooling capacity.
  • the blowing mechanism in the first embodiment further includes a first outlet 102A, a second outlet 102B, a first flap 103A, and a second flap 103B.
  • the first outlet 102A is an opening through which air that has exchanged heat with the refrigerant in the first region blows out.
  • the second outlet 102B is an opening through which air that has exchanged heat with the refrigerant in the second region blows out.
  • the first flap 103A adjusts the opening degree of the first outlet 102A.
  • the second flap 103B adjusts the opening degree of the second outlet 102B.
  • the control unit 6 controls at least one of the first flap 103A and the second flap 103B so that the opening degree of the first outlet 102A is smaller than the opening degree of the second outlet 102B.
  • the indoor unit 100 can blow the air heat-exchanged with the refrigerant in the first region into the room with a smaller air volume, and also blow the air heat-exchanged with the refrigerant in the second region into the room with a larger air volume. can do. Therefore, the indoor unit 100 can further suppress dew splash and further maintain or improve the cooling capacity.
  • the blower mechanism in the first embodiment includes an indoor blower 1, a first outlet 102A, a second outlet 102B, a first flap 103A, a second flap 103B, and a control unit 6.
  • the indoor blower 1 sends the indoor air to the indoor heat exchanger 2, and also blows the air that has been heat-exchanged with the refrigerant in the indoor heat exchanger 2 into the room.
  • the first outlet 102A is an opening through which air that has exchanged heat with the refrigerant in the first region blows out.
  • the second outlet 102B is an opening through which air that has exchanged heat with the refrigerant in the second region blows out.
  • the first flap 103A adjusts the opening degree of the first outlet 102A.
  • the second flap 103B adjusts the opening degree of the second outlet 102B.
  • the control unit 6 controls the indoor blower 1, the first flap 103A, and the second flap 103B.
  • the control unit 6 controls at least one of the first flap 103A and the second flap 103B so that the opening degree of the first outlet 102A is smaller than the opening degree of the second outlet 102B.
  • the indoor unit 100 can blow the air that has exchanged heat with the refrigerant in the first region into the room with a smaller air volume than the air that has exchanged heat with the refrigerant in the second region. Therefore, the indoor unit 100 can achieve both suppression of dew splash and maintenance of cooling capacity.
  • the indoor unit 100 is connected to a duct 9 that internally mixes the air that has exchanged heat with the refrigerant in the first region and the air that has exchanged heat with the refrigerant in the second region. There is. Thereby, the indoor unit 100 can reduce the temperature unevenness and the air volume unevenness of the air blown out from the indoor unit 100.
  • the refrigerant in the first embodiment is a non-azeotropic mixed refrigerant.
  • a first region where the temperature of the refrigerant is low and a second region where the temperature of the refrigerant is high are formed. Therefore, the indoor unit 100 can perform the dehumidifying operation using the first region and the cooling operation using the second region. Therefore, during the cooling operation, the indoor unit 100 can be dehumidified while maintaining the cooling capacity. Therefore, it becomes possible to suppress an increase in the relative humidity in the room during the cooling operation.
  • the refrigerant in the first embodiment is water.
  • a first region where the temperature of the refrigerant is low and a second region where the temperature of the refrigerant is high are formed. Therefore, the indoor unit 100 can perform the dehumidifying operation using the first region and the cooling operation using the second region. Therefore, during the cooling operation, the indoor unit 100 can be dehumidified while maintaining the cooling capacity. Therefore, it becomes possible to suppress an increase in the relative humidity in the room during the cooling operation.
  • FIG. 15 is a schematic diagram illustrating the air conditioner according to the second embodiment.
  • the air conditioner 300 according to the second embodiment has an indoor unit 100 and an outdoor unit 200 according to the first embodiment.
  • the indoor unit 100 and the outdoor unit 200 are connected to form a refrigerant circuit 301.
  • the air conditioner 300 circulates the non-azeotropic mixed refrigerant in the refrigerant circuit 301.
  • FIG. 15 illustrates an indoor unit 100 including a first indoor blower 1A and a second indoor blower 1B, but the number of indoor blowers 1 in the indoor unit 100 is three even if it is one. It may be the above.
  • the indoor unit 100 has a plurality of outlets 102 and a plurality of outlets 102, for example, as in the modified example 2 or the modified example 3 in the first embodiment. It is provided with a flap 103.
  • the non-azeotropic mixed refrigerant is a refrigerant whose temperature changes during the phase change.
  • the temperature of the non-azeotropic mixed refrigerant rises while exchanging heat with air in the evaporation process in the heat exchanger.
  • the heat exchanger is a general term for the indoor heat exchanger 2 described above and the outdoor heat exchanger 203 described later.
  • a temperature gradient is generated such that the refrigerant on the outlet side of the heat exchanger has a higher temperature than the refrigerant on the inlet side.
  • the temperature of the refrigerant flowing into the heat exchanger drops while exchanging heat with air.
  • a temperature gradient is generated so that the refrigerant on the outlet side of the heat exchanger has a lower temperature than the refrigerant on the inlet side.
  • the non-azeotropic mixed refrigerant include R407C, but R407C produces a temperature gradient of 6 [° C.] or more when the temperature of the saturated gas is 5 [° C.].
  • the outdoor unit 200 includes a compressor 201, a flow path switching device 202, an outdoor heat exchanger 203, an outdoor blower 204, and a flow rate adjusting valve 205.
  • the compressor 201, the flow path switching device 202, the outdoor heat exchanger 203, and the flow rate adjusting valve 205 are sequentially connected by a refrigerant pipe.
  • the compressor 201 compresses the refrigerant sucked from the suction side and discharges it from the discharge side as a high-temperature and high-pressure gas refrigerant.
  • the flow path switching device 202 includes, for example, a four-way valve, and switches the direction of the flow path of the refrigerant. Switching between cooling and heating is performed by switching the flow path of the refrigerant by the flow path switching device 202.
  • the solid line portion in the flow path switching device 202 shows the flow path of the refrigerant during the cooling operation. Further, the broken line portion indicates the flow path of the refrigerant during the heating operation.
  • the arrow shown by the solid line in FIG. 15 indicates the direction in which the refrigerant flows during the cooling operation, and the arrow indicated by the broken line indicates the direction in which the refrigerant flows during the heating operation.
  • the outdoor heat exchanger 203 exchanges heat between the refrigerant and the outdoor air.
  • the outdoor heat exchanger 203 functions as a refrigerant condenser during the cooling operation and as a refrigerant evaporator during the heating operation.
  • the outdoor blower 204 includes a blower fan driven by a drive source such as a fan motor, guides the outdoor air to the outdoor heat exchanger 203 in the outdoor unit 200, and sends out the air after heat exchange with the refrigerant to the outside.
  • the flow rate adjusting valve 205 is also called an expansion valve, and adjusts the flow rate of the refrigerant circulating between the outdoor unit 200 and the indoor unit 100 by changing the opening degree, or adjusts the flow rate of the refrigerant compressed by the compressor 201. Reduce the pressure.
  • the opening degree of the flow rate adjusting valve 205 according to the second embodiment is adjusted according to the operating condition of the indoor unit 100.
  • the flow of the refrigerant during the cooling operation will be described below.
  • the refrigerant flowing out of the compressor 201 flows into the outdoor heat exchanger 203 via the flow path switching device 202, exchanges heat with the outdoor air in the outdoor heat exchanger 203, and condenses.
  • the refrigerant condensed in the outdoor heat exchanger 203 is depressurized by the flow rate adjusting valve 205 and flows out to the indoor unit 100.
  • the refrigerant flowing into the indoor unit 100 exchanges heat with air in the indoor heat exchanger 2 and evaporates. Since the temperature of the non-azeotropic mixed refrigerant rises during evaporation, temperature unevenness is formed in the indoor heat exchanger 2 in which the inlet side is low temperature and the outlet side is high temperature.
  • the evaporated refrigerant flows out of the indoor unit 100 and flows into the outdoor unit 200 again. Then, the refrigerant is sucked into the compressor 201 via the flow path switching device 202.
  • the refrigerant flowing out of the compressor 201 flows out of the outdoor unit 200 via the flow path switching device 202 and flows into the indoor unit 100.
  • the refrigerant flowing into the indoor unit 100 exchanges heat with air in the indoor heat exchanger 2 and condenses.
  • the condensed refrigerant flows out of the indoor unit 100 and flows into the outdoor unit 200 again.
  • the refrigerant flowing into the outdoor unit 200 is depressurized by the flow rate adjusting valve 205, exchanges heat with air in the outdoor heat exchanger 203 to vaporize, and then is sucked into the compressor 201 via the flow path switching device 202.
  • FIG. 16 is a schematic diagram showing the flow of the refrigerant during the heating operation in the indoor heat exchanger illustrated in FIG.
  • the x-direction, y-direction, and z-direction in FIG. 16 correspond to the x-direction, y-direction, and z-direction in FIG. 3, respectively.
  • the black arrows in FIG. 16 indicate the direction and direction in which the refrigerant flows, and the white arrows indicate the direction and direction in which the air flows.
  • the direction in which the refrigerant flows in the indoor heat exchanger 2 is opposite to that during the cooling operation. Then, the inlet and outlet of the refrigerant in the indoor heat exchanger 2 are reversed from those in the cooling operation. Also in the heating operation, the temperature unevenness in the horizontal direction of the refrigerant occurs in the heat transfer tube 20 as in the cooling operation. In this case, the inlet side of the refrigerant in the heat transfer tube 20 has a high temperature, and the outlet side has a low temperature. Therefore, in the heating operation, the arrangement relationship between the heat transfer tubes 20 in the first region and the second region is the same as in the cooling operation.
  • the temperature unevenness of the refrigerant occurs in the heat transfer tube 20 even during the heating operation, the temperature unevenness in the horizontal direction also occurs in the wind blown from the indoor unit 100 during the heating operation.
  • the wind having uneven temperature is mixed inside the duct 9. Then, the unevenness of the temperature of the wind blown into the room is reduced. Since it is unlikely that dew condensation will occur in the indoor heat exchanger 2 during the heating operation, the indoor unit 100 does not have to adjust the air volume to prevent dew splashing.
  • FIG. 17 is a schematic diagram illustrating an air conditioner according to a modified example of the second embodiment.
  • the air conditioner 400 according to the modification of the second embodiment has a first refrigerant circuit 401 in which one of the two types of refrigerant circulates, and a second refrigerant circuit 402 in which the other circulates.
  • the refrigerant that circulates in the first refrigerant circuit 401 will be referred to as the first refrigerant below.
  • the refrigerant circulating in the second refrigerant circuit 402 will be referred to as a second refrigerant below.
  • the first refrigerant may be any existing refrigerant whose temperature changes in the evaporation process, but the case where it is water will be described below as an example.
  • the second refrigerant is any existing refrigerant.
  • the air conditioner 400 has an intermediate heat exchanger 403 and a pump 404 in addition to the indoor unit 100 and the outdoor unit 200.
  • the first refrigerant circuit 401 includes an indoor unit 100, an intermediate heat exchanger 403, and a pump 404.
  • the second refrigerant circuit 402 includes an outdoor unit 200 and an intermediate heat exchanger 403. Note that FIG. 17 illustrates an indoor unit 100 including the first indoor blower 1A and the second indoor blower 1B, but the number of indoor blowers 1 in the indoor unit 100 is three even if it is one. It may be the above.
  • the indoor unit 100 has a plurality of outlets 102 and a plurality of outlets 102, for example, as in the modified example 2 or the modified example 3 in the first embodiment. It is provided with a flap 103.
  • the solid arrow in FIG. 17 indicates the direction and direction of water flow in the first refrigerant circuit 401 during the cooling operation.
  • the water flowing out of the indoor unit 100 during the cooling operation flows out to the intermediate heat exchanger 403 by the pump 404.
  • the water flowing into the intermediate heat exchanger 403 exchanges heat with the second refrigerant flowing through the second refrigerant circuit 402 and dissipates heat.
  • the heat-dissipated water flows out from the intermediate heat exchanger 403 and flows into the indoor unit 100.
  • the water flowing into the indoor unit 100 exchanges heat with air in the indoor heat exchanger 2 and absorbs heat.
  • the endothermic water flows out of the indoor unit 100 and again flows out to the intermediate heat exchanger 403 by the pump 404.
  • the broken line arrow in FIG. 17 indicates the direction and direction in which the second refrigerant flows in the second refrigerant circuit 402 during the cooling operation.
  • the gaseous gas refrigerant discharged from the compressor 201 is condensed in the outdoor heat exchanger 203 via the flow path switching device 202.
  • the condensed second refrigerant is decompressed by the flow rate adjusting valve 205, flows out of the outdoor unit 200, and flows into the intermediate heat exchanger 403.
  • the second refrigerant exchanges heat with the water in the first refrigerant circuit 401 and evaporates.
  • the evaporated second refrigerant flows out from the intermediate heat exchanger 403 and flows into the outdoor unit 200 again.
  • the second refrigerant that has flowed into the outdoor unit 200 is sucked into the compressor 201 again.
  • the water circulating in the first refrigerant circuit 401 is always a liquid and does not undergo a phase change in the indoor heat exchanger 2.
  • the water flowing into the indoor heat exchanger 2 absorbs heat by heat exchange with air, and the temperature rises. Therefore, the water on the outlet side of the indoor heat exchanger 2 has a higher temperature than the water on the inlet side.
  • the direction and direction of water flow in the first refrigerant circuit 401 are opposite to those in the cooling operation.
  • the water flowing into the indoor heat exchanger 2 dissipates heat by heat exchange with air, and the temperature drops. Therefore, the water on the outlet side of the indoor heat exchanger 2 has a lower temperature than the water on the inlet side.
  • the temperature of water is uneven in the horizontal direction. Due to heat exchange with water having temperature unevenness in the horizontal direction, the temperature unevenness in the horizontal direction occurs in the wind flowing out from the indoor unit 100. As described above, for example, by using the duct 9, the temperature unevenness is caused. It will be reduced. Further, the first indoor blower 1A, which blows out the air heat-exchanged with the water in the first region into the room during the cooling operation, reduces the air volume when the humidity is higher than the threshold value according to the instruction from the control unit 6. As a result, it is possible to reduce dew splash as described above.
  • the air conditioner 300 has an outdoor unit 200 and an indoor unit 100.
  • the outdoor unit 200 exchanges heat between the refrigerant and the outdoor air in the refrigerant circuit 301 that circulates the refrigerant.
  • the indoor unit 100 exchanges heat between the refrigerant and the air in the room to air-condition the room.
  • the indoor unit 100 includes an indoor heat exchanger 2 and a ventilation mechanism.
  • the indoor heat exchanger 2 exchanges heat between the indoor air and the refrigerant.
  • the blower mechanism sends the indoor air to the indoor heat exchanger 2 and sends the air after heat exchange with the refrigerant into the room.
  • the indoor heat exchanger 2 has a plurality of heat transfer tubes 20.
  • the plurality of heat transfer tubes 20 are parallel to each other and allow the refrigerant to flow in the horizontal direction to exchange heat with the air. Since the refrigerant flows in the heat transfer tube 20 in the horizontal direction, the drainage property of the dew condensation water is improved, the heat transfer performance on the surface of the heat transfer tube 20 is improved, and new dew condensation can be generated on the surface. This promotes heat exchange between the refrigerant flowing in the heat transfer tube 20 and the air, and enhances the dehumidifying performance. Therefore, in the second embodiment, the air conditioner 300 can suppress an increase in relative humidity in the room while maintaining the cooling capacity.
  • the air conditioner 400 has an indoor unit 100, an outdoor unit 200, and an intermediate heat exchanger 403.
  • the indoor unit 100 exchanges heat between the first refrigerant and the air in the room to air-condition the room.
  • the outdoor unit 200 exchanges heat between the second refrigerant and the outdoor air in the second refrigerant circuit 402 that circulates the second refrigerant.
  • the intermediate heat exchanger 403 is included in the first refrigerant circuit 401 and the second refrigerant circuit 402, and causes heat exchange between the first refrigerant and the second refrigerant.
  • the indoor unit 100 includes an indoor heat exchanger 2 and a ventilation mechanism.
  • the indoor heat exchanger 2 exchanges heat between the indoor air and the first refrigerant.
  • the blower mechanism sends the indoor air to the indoor heat exchanger 2 and sends the air after heat exchange with the first refrigerant into the room.
  • the indoor heat exchanger 2 has a plurality of heat transfer tubes 20.
  • the plurality of heat transfer tubes 20 are parallel to each other and allow the refrigerant to flow in the horizontal direction to exchange heat with the air.
  • the plurality of heat transfer tubes 20 are parallel to each other and allow the refrigerant to flow in the horizontal direction to exchange heat with the air.
  • the air conditioner 400 according to the second embodiment can suppress an increase in relative humidity in the room while maintaining the cooling capacity.
  • 1 Indoor blower 1A 1st indoor blower, 1B 2nd indoor blower, 2 Indoor heat exchanger, 3 Refrigerant temperature sensor, 4 Air temperature sensor, 5 Humidity sensor, 6 Control unit, 8 Drain pan, 9 Duct, 10 Blower fan, 11 fan motor, 20 heat transfer tube, 21 heat transfer promotion fin, 22 liquid header, 23 gas header, 90 first opening, 91 second opening, 100 indoor unit, 101 bottom, 102 outlet, 102A first outlet, 102B 2nd outlet, 103 flap, 103A 1st flap, 103B 2nd flap, 200 outdoor unit, 201 compressor, 202 flow path switching device, 203 outdoor heat exchanger, 204 outdoor blower, 205 flow control valve, 300, 400 air conditioner, 301 refrigerant circuit, 401 first refrigerant circuit, 402 second refrigerant circuit, 403 intermediate heat exchanger, 404 pump.

Landscapes

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

Abstract

La présente invention concerne une unité intérieure de climatiseur pourvue d'un échangeur de chaleur intérieur et d'un mécanisme de soufflage d'air. L'échangeur de chaleur intérieur (2) échange la chaleur entre un fluide frigorigène et l'air dans une pièce. Le mécanisme de soufflage d'air souffle de l'air dans la pièce vers l'échangeur de chaleur intérieur (2), et souffle vers l'extérieur, vers la pièce, l'air ayant subi un échange de chaleur avec le fluide frigorigène. L'échangeur de chaleur intérieur (2) comprend une pluralité de tuyaux de transfert de chaleur. La pluralité de tuyaux de transfert de chaleur sont disposés en parallèle les uns avec les autres et permettent au fluide frigorigène de s'écouler à travers ceux-ci dans la direction horizontale de façon à effectuer un échange de chaleur entre le fluide frigorigène et l'air.
PCT/JP2020/019439 2020-05-15 2020-05-15 Unité intérieure de climatiseur et climatiseur WO2021229794A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2020/019439 WO2021229794A1 (fr) 2020-05-15 2020-05-15 Unité intérieure de climatiseur et climatiseur
JP2020558561A JP6847328B1 (ja) 2020-05-15 2020-05-15 空気調和装置の室内ユニット、および、空気調和装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2020/019439 WO2021229794A1 (fr) 2020-05-15 2020-05-15 Unité intérieure de climatiseur et climatiseur

Publications (1)

Publication Number Publication Date
WO2021229794A1 true WO2021229794A1 (fr) 2021-11-18

Family

ID=74879231

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2020/019439 WO2021229794A1 (fr) 2020-05-15 2020-05-15 Unité intérieure de climatiseur et climatiseur

Country Status (2)

Country Link
JP (1) JP6847328B1 (fr)
WO (1) WO2021229794A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023286181A1 (fr) * 2021-07-14 2023-01-19 三菱電機株式会社 Dispositif de climatisation

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0798165A (ja) * 1993-09-30 1995-04-11 Toshiba Corp 熱交換器
JP2001082761A (ja) * 1999-09-14 2001-03-30 Mitsubishi Electric Corp 空気調和機
WO2010049999A1 (fr) * 2008-10-29 2010-05-06 三菱電機株式会社 Conditionneur d'air
WO2012017480A1 (fr) * 2010-08-04 2012-02-09 三菱電機株式会社 Unité intérieure pour climatiseur et climatiseur
JP2014145490A (ja) * 2013-01-28 2014-08-14 Sharp Corp 熱交換器及びそれを備えた空気調和機
JP2016194388A (ja) * 2015-03-31 2016-11-17 三菱重工業株式会社 空気調和システム
US20190078848A1 (en) * 2015-07-10 2019-03-14 Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. Heat exchanger

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0798165A (ja) * 1993-09-30 1995-04-11 Toshiba Corp 熱交換器
JP2001082761A (ja) * 1999-09-14 2001-03-30 Mitsubishi Electric Corp 空気調和機
WO2010049999A1 (fr) * 2008-10-29 2010-05-06 三菱電機株式会社 Conditionneur d'air
WO2012017480A1 (fr) * 2010-08-04 2012-02-09 三菱電機株式会社 Unité intérieure pour climatiseur et climatiseur
JP2014145490A (ja) * 2013-01-28 2014-08-14 Sharp Corp 熱交換器及びそれを備えた空気調和機
JP2016194388A (ja) * 2015-03-31 2016-11-17 三菱重工業株式会社 空気調和システム
US20190078848A1 (en) * 2015-07-10 2019-03-14 Sanhua (Hangzhou) Micro Channel Heat Exchanger Co., Ltd. Heat exchanger

Also Published As

Publication number Publication date
JP6847328B1 (ja) 2021-03-24
JPWO2021229794A1 (fr) 2021-11-18

Similar Documents

Publication Publication Date Title
JP5799932B2 (ja) 空気調和装置
WO2014054533A1 (fr) Dispositif de cycle de réfrigération et unité extérieure
CN106716024A (zh) 空调装置的室内机组
JP2011144996A (ja) 空調機
WO2021229794A1 (fr) Unité intérieure de climatiseur et climatiseur
WO2019171462A1 (fr) Unité intérieure et climatiseur
JP4341358B2 (ja) 空気調和装置
JP2002228187A (ja) 空冷ヒートポンプ式外気処理空調機
JP4505486B2 (ja) ヒートポンプ式空調機
JPH0719514A (ja) 空気調和装置の室内ユニット
JP2007285628A (ja) 空調調和装置
CN215951581U (zh) 空调装置
JP6745895B2 (ja) 空調システム
JP2007333378A (ja) ヒートポンプ式空調機
JP6938950B2 (ja) 空気調和システム
JP5195135B2 (ja) 空気調和機
WO2022158263A1 (fr) Unité intérieure de climatisation montée sur une paroi et dispositif de climatisation
JPWO2019116838A1 (ja) 熱交換ユニット及びこれを搭載する空気調和装置
WO2023047716A1 (fr) Échangeur de chaleur et dispositif de climatisation
WO2020195153A1 (fr) Climatiseur
JP7450807B2 (ja) 空気調和機
WO2024101103A1 (fr) Dispositif de ventilation du type à échange de chaleur
JP7129603B2 (ja) 除湿機能付き熱交換形換気装置
WO2022049879A1 (fr) Dispositif de climatisation
JP6630923B2 (ja) 空気調和機

Legal Events

Date Code Title Description
ENP Entry into the national phase

Ref document number: 2020558561

Country of ref document: JP

Kind code of ref document: A

121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 20935593

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 20935593

Country of ref document: EP

Kind code of ref document: A1