JP6693552B2 - Heat exchanger and air conditioner including the same - Google Patents

Description

  INDUSTRIAL APPLICABILITY The present invention relates to a heat exchanger and an air conditioner provided with the heat exchanger, and in particular, a plurality of flat tubes arranged in multiple stages in a vertical step direction and having refrigerant passages formed therein, and adjacent flat tubes. And a plurality of fins that divide the space between a plurality of ventilation passages through which air flows, and a heat exchanger divided into a plurality of heat exchange paths in which flat tubes are arranged in multiple stages in the step direction, and an air conditioner including the heat exchanger. Regarding the device.

  Conventionally, as an outdoor heat exchanger that is housed in an outdoor unit of an air conditioner, a plurality of flat tubes that are arranged in multiple stages in the vertical direction and have refrigerant passages formed inside, and adjacent flat tubes. A heat exchanger having a plurality of fins that divide the tubes into a plurality of ventilation paths through which air flows may be used. As such a heat exchanger, for example, as shown in Patent Document 1 (International Publication No. 2013/161799), there is one in which flat tubes are divided into a plurality of heat exchange paths arranged in multiple stages in the step direction. ..

  The above conventional heat exchanger may be used in an air conditioner that switches between heating operation and defrosting operation. Here, when the air conditioner performs heating operation, the conventional heat exchanger is used as a refrigerant evaporator, and when the air conditioner performs defrosting operation, the conventional heat exchanger is Used as a radiator of refrigerant. Specifically, when the conventional heat exchanger is used as a refrigerant evaporator, the refrigerant in a gas-liquid two-phase state branches and flows into each heat exchange path, and is heated in each heat exchange path. , Outflow from each heat exchange path and merge. Further, when the conventional heat exchanger is used as a heat radiator of a refrigerant, the refrigerant in a gas state branches into each heat exchange path, is cooled in each heat exchange path, and is cooled from each heat exchange path. It flows out and joins.

  However, in the air conditioner that employs the conventional heat exchanger, the amount of frost in the lowermost heat exchange path tends to increase during heating operation. Therefore, during the defrosting operation, the time required to melt the frost adhering to the lowermost heat exchange path is equal to the time required to melt the frost adhered to other heat exchanging paths on the upper side of the lowermost heat exchanging path. It may take longer than the time required to remove the debris, and even after the defrosting operation, unmelted frost may remain in the bottommost heat exchange path, resulting in insufficient defrosting.

  An object of the present invention is to divide a plurality of flat tubes in which a passage for a refrigerant is formed and are arranged in multiple stages in a step direction that is an up-down direction, and a plurality of ventilation paths in which air flows between adjacent flat tubes. A heat exchanger having a plurality of fins and having a plurality of flat tubes arranged in multiple stages in the step direction is adopted in an air conditioner that switches between heating operation and defrosting operation. In this case, frost formation in the lowermost heat exchange path is suppressed to reduce unmelted residue during defrosting operation.

The heat exchanger according to the first aspect has a plurality of flat tubes that are arranged in multiple stages in a vertical step direction and that have refrigerant passages formed therein, and a plurality of air tubes that flow between adjacent flat tubes. And a plurality of fins that divide the ventilation passage of the flat tube, and the flat tube is divided into a plurality of heat exchange paths arranged in multiple stages in the step direction. Then, here, if the heat exchange path including the flat tube at the bottom of the heat exchange paths is taken as the first heat exchange path and the flow passage cross-sectional area of the passage in each heat exchange path is taken as the path effective cross-sectional area, the first heat The effective path area of the exchange path is smaller than the effective area areas of other heat exchange paths.

  First, when the conventional heat exchanger is adopted in an air conditioner that switches between heating operation (when used as a refrigerant evaporator) and defrosting operation (when used as a refrigerant radiator), The reason why the amount of frost is likely to increase in the lowermost heat exchange path during the heating operation will be described.

  In the above conventional heat exchanger, each heat exchange path is configured by connecting the same number of flat tubes having the same shape (tube length and size and number of through holes that serve as refrigerant passages) in series. .. That is, the above conventional heat exchanger is configured such that the heat exchange paths have the same effective cross-sectional area.

  In this conventional configuration, during the heating operation, the refrigerant in the liquid state easily flows into the bottommost heat exchange path including the bottommost flat tube, and the bottommost heat exchange path is maintained without the temperature of the refrigerant rising sufficiently. As a result, the amount of frost formed on the lowermost heat exchange path tends to increase. That is, in the configuration of the conventional heat exchanger, the refrigerant in the liquid state easily flows into the lowermost heat exchange path during the heating operation, and flows out of the lowermost heat exchange path without sufficiently increasing the temperature of the refrigerant. It is estimated that this is the reason why the amount of frost is likely to increase in the lowermost heat exchange path.

  Therefore, here, unlike the conventional heat exchanger, as described above, the path effective cross-sectional area of the first heat exchange path in the lowermost stage including the flat tubes in the lowermost stage is changed to the path effective cross-sections of other heat exchange paths. It is smaller than the cross-sectional area.

  When the heat exchanger having this configuration is adopted in the air conditioner that switches between the heating operation and the defrosting operation, the first heat exchange path has a small effective path area, and thus the first heat The flow resistance of the refrigerant in the exchange path can be increased. For this reason, during the heating operation, it becomes difficult for the liquid-state refrigerant to flow into the first heat exchange path, and the temperature of the refrigerant flowing through the lowermost heat exchange path easily rises, so that frost formation in the first heat exchange path is suppressed. can do. As a result, it is possible to reduce the unmelted residue in the first heat exchange path during the defrosting operation, as compared with the case where the conventional heat exchanger is adopted.

  As described above, here, by adopting the heat exchanger having the above configuration in the air conditioner that switches between the heating operation and the defrosting operation, frost formation in the lowermost heat exchange path is suppressed and removed. It is possible to reduce unmelted residue during frost operation.

A heat exchanger according to a second aspect is the heat exchanger according to the first aspect , in which a path effective sectional area of the first heat exchange path is 0.5 times or less than a path effective sectional area of another heat exchange path. Is.

  Here, as described above, since the path effective sectional area of the first heat exchange path is made sufficiently small, the flow resistance of the refrigerant in the first heat exchange path is made sufficiently large and the heat exchange path at the bottom The effect of suppressing frost formation can be enhanced.

A heat exchanger according to a third aspect is the heat exchanger according to the first or second aspect , in which the flat tube has a plurality of through holes that serve as passages, and constitutes a first heat exchange path. The size of the through-holes of the flat tubes is smaller than the size of the through-holes of the flat tubes forming the other heat exchange paths, and / or the number of the through-holes of the flat tubes forming the first heat exchange path is It is smaller than the number of through-holes in the flat tubes that form the other heat exchange paths.

  Here, as described above, the passage of the flat tube is formed by a plurality of through holes, and the size of the plurality of through holes of the flat tube forming the first heat exchange path is changed to the flat tube forming the other heat exchange path. Smaller than the size of the through-holes, or the number of the plurality of through-holes of the flat tubes forming the first heat exchange path is smaller than that of the flat tubes forming the other heat-exchange paths. As a result, the path effective sectional area of the first heat exchange path can be reduced.

Heat exchanger according to a fourth aspect, in the first to the heat exchanger according to any one of the third aspect, the number of flat tubes constituting the first heat exchange path constitutes the other heat exchange path Less than the number of flat tubes.

  If a configuration is adopted in which the number of flat tubes forming the first heat exchange path is smaller than the number of flat tubes forming the other heat exchange paths, uneven flow occurs when the refrigerant is branched to flow into each heat exchange path. It tends to occur.

  However, here, as described above, a configuration in which the path effective length of the first heat exchange path is made longer than the path effective lengths of the other heat exchange paths, or the path effective cross-sectional area of the first heat exchange path is adopted. Since the flow resistance of the refrigerant in the first heat exchange path is increased by adopting a configuration in which is smaller than the path effective cross-sectional area of the other heat exchange paths, the refrigerant is branched to each heat exchange path. It is possible to suppress the occurrence of uneven flow when flowing in.

A heat exchanger according to a fifth aspect is the heat exchanger according to any one of the first to fourth aspects, wherein the fins extend along the windward side from the leeward side in the ventilation direction in which air passes through the ventilation passage. And a plurality of notches into which flat tubes are inserted, a plurality of fin main parts sandwiched between adjacent notches, and a plurality of fin main parts continuous to the windward side of the notches in the ventilation direction. And the fin windward side extending.

  Here, as described above, the notch portion into which the flat tube is inserted in the fin is formed so as to extend along the windward side from the leeward side in the ventilation direction, and the windward side in the ventilation direction rather than the notch portion. It has a configuration in which a plurality of fin main parts sandwiched between the notch parts and fin upwinding parts that extend continuously are formed. In the heat exchanger having this configuration, the amount of frost attached to the windward upper part of the fins during the defrosting operation is likely to increase, and therefore there is a possibility that unmelted residue in the lowermost first heat exchange path will increase during the defrosting operation.

  However, here, as described above, a configuration in which the path effective length of the first heat exchange path is made longer than the path effective lengths of the other heat exchange paths, or the path effective cross-sectional area of the first heat exchange path is Since the configuration is smaller than the effective cross-sectional area of the other heat exchange paths, frost formation in the lowermost heat exchange path including frost adhering to the windward side of the fins is suppressed and defrosting operation is performed. Unmelting can be reduced.

An air conditioning apparatus according to a sixth aspect is provided with a heat exchanger according to any one of the first to fifth aspect.

Since the air conditioner is configured by adopting the heat exchanger according to any one of the first to fifth aspects, the frost formation in the lowermost heat exchange path is suppressed and the defrosting operation is performed. The unmelted residue can be reduced.

  As described above, according to the present invention, the heat exchanger having the configuration in which the path effective cross-sectional area of the first heat exchange path is smaller than the path effective cross-sectional areas of the other heat exchange paths is used for the heating operation. By adopting the air conditioner that switches between the defrosting operation and the defrosting operation, it is possible to suppress frost formation in the lowermost heat exchange path and reduce unmelted residue during the defrosting operation.

FIG. 1 is a schematic configuration diagram of an outdoor heat exchanger as a heat exchanger and an air conditioner including the same according to an embodiment of the present invention. It is an external appearance perspective view of an outdoor unit. It is a front view of an outdoor unit (illustration is shown except the refrigerant circuit components other than the outdoor heat exchanger). It is a schematic perspective view of the outdoor heat exchanger as a heat exchanger concerning 1st Embodiment. FIG. 5 is a partially enlarged perspective view of the heat exchange path of FIG. 4. It is a schematic block diagram of the outdoor heat exchanger as a heat exchanger concerning 1st Embodiment (the figure seen from the downwind side). It is a schematic block diagram of the outdoor heat exchanger as a heat exchanger concerning 1st Embodiment (the figure seen from the windward side). It is a plane sectional view of a connection header. It is a figure showing the path composition near the 1st heat exchange path of the outdoor heat exchanger as a heat exchanger concerning a 1st embodiment. It is a figure which shows the outdoor heat exchanger as a heat exchanger concerning the modification A of 1st Embodiment, Comprising: It is a figure corresponding to FIG. It is a figure which shows the outdoor heat exchanger as a heat exchanger concerning the modification B of 1st Embodiment, Comprising: It is a figure corresponding to FIG. It is a figure which shows the outdoor heat exchanger as a heat exchanger concerning the modification C of 1st Embodiment, Comprising: It is a figure corresponding to FIG. It is a figure which shows the outdoor heat exchanger as a heat exchanger concerning the modification D of 1st Embodiment, Comprising: It is a figure corresponding to FIG. It is a figure which shows the outdoor heat exchanger as a heat exchanger concerning the modification E of 1st Embodiment, Comprising: It is a figure corresponding to FIG. It is a figure which shows the outdoor heat exchanger as a heat exchanger concerning the modification F of 1st Embodiment, Comprising: It is a figure corresponding to FIG. It is a figure which shows the outdoor heat exchanger as a heat exchanger concerning the modification G of 1st Embodiment, Comprising: It is a figure corresponding to FIG. It is a schematic perspective view of the outdoor heat exchanger as a heat exchanger concerning 2nd Embodiment. It is a schematic block diagram (view from the downwind side) of the outdoor heat exchanger as a heat exchanger concerning 2nd Embodiment. It is a schematic block diagram (the figure seen from the windward side) of the outdoor heat exchanger as a heat exchanger concerning 2nd Embodiment. It is a figure showing the path composition near the 1st heat exchange path of the outdoor heat exchanger as a heat exchanger concerning a 2nd embodiment. It is a figure which shows the outdoor heat exchanger as a heat exchanger concerning the modification A of 2nd Embodiment, and is a figure corresponding to FIG.

  Hereinafter, embodiments of a heat exchanger according to the present invention and an air conditioning apparatus including the heat exchanger, and modifications thereof will be described with reference to the drawings. The specific configurations of the heat exchanger according to the present invention and the air conditioning apparatus including the heat exchanger are not limited to the following embodiments and modifications thereof, and can be changed without departing from the scope of the invention. is there.

(1) Configuration of Air Conditioning Apparatus FIG. 1 is a schematic configuration diagram of an outdoor heat exchanger 11 as a heat exchanger and an air conditioning apparatus 1 including the same according to one embodiment of the present invention.

  The air conditioning apparatus 1 is an apparatus capable of cooling and heating a room such as a building by performing a vapor compression refrigeration cycle. The air conditioner 1 mainly includes an outdoor unit 2, indoor units 3a and 3b, a liquid refrigerant communication pipe 4 and a gas refrigerant communication pipe 5 that connect the outdoor unit 2 and the indoor units 3a and 3b, and the outdoor unit 2 and The control unit 23 that controls the constituent devices of the indoor units 3a and 3b. The vapor compression type refrigerant circuit 6 of the air conditioner 1 is configured by connecting the outdoor unit 2 and the indoor units 3a and 3b through the refrigerant communication pipes 4 and 5.

  The outdoor unit 2 is installed outdoors (on the roof of the building, in the vicinity of the wall surface of the building, etc.) and constitutes a part of the refrigerant circuit 6. The outdoor unit 2 mainly includes an accumulator 7, a compressor 8, a four-way switching valve 10, an outdoor heat exchanger 11, an outdoor expansion valve 12 as an expansion mechanism, a liquid side closing valve 13, and a gas side closing valve. It has 14 and the outdoor fan 15. The respective devices and valves are connected by refrigerant pipes 16 to 22.

  The indoor units 3a and 3b are installed in a room (a living room, a space above the ceiling, etc.) and constitute a part of the refrigerant circuit 6. The indoor unit 3a mainly has an indoor expansion valve 31a, an indoor heat exchanger 32a, and an indoor fan 33a. The indoor unit 3b mainly has an indoor expansion valve 31b as an expansion mechanism, an indoor heat exchanger 32b, and an indoor fan 33b.

  The refrigerant communication pipes 4 and 5 are refrigerant pipes that are constructed locally when the air conditioner 1 is installed in an installation location such as a building. One end of the liquid refrigerant communication pipe 4 is connected to the liquid side closing valve 13 of the indoor unit 2, and the other end of the liquid refrigerant communication pipe 4 is connected to the liquid side ends of the indoor expansion valves 31a and 31b of the indoor units 3a and 3b. Has been done. One end of the gas refrigerant communication pipe 5 is connected to the gas side closing valve 14 of the indoor unit 2, and the other end of the gas refrigerant communication pipe 5 is connected to the gas side ends of the indoor heat exchangers 32a, 32b of the indoor units 3a, 3b. It is connected.

  The control unit 23 is configured by communicatively connecting a control board and the like (not shown) provided in the outdoor unit 2 and the indoor units 3a and 3b. Note that, in FIG. 1, for convenience, the illustration is shown at a position away from the outdoor unit 2 and the indoor units 3a and 3b. The control unit 23 controls the components 8, 10, 12, 15, 31a, 31b, 33a, 33b of the air conditioner 1 (here, the outdoor unit 2 and the indoor units 3a, 3b), that is, the air conditioner 1 It is designed to control the overall operation.

(2) Operation of Air Conditioner Next, the operation of the air conditioner 1 will be described with reference to FIG. In the air conditioner 1, the compressor 8, the outdoor heat exchanger 11, the outdoor expansion valve 12, the indoor expansion valves 31a and 31b, and the indoor heat exchangers 32a and 32b perform cooling operation in which refrigerant is circulated in that order; The heating operation of circulating the refrigerant in the order of the heat exchangers 32a and 32b, the indoor expansion valves 31a and 31b, the outdoor expansion valve 12, and the outdoor heat exchanger 11 is performed. Further, during the heating operation, the defrosting operation for melting the frost attached to the outdoor heat exchanger 11 is performed. Here, as in the cooling operation, the reverse cycle defrosting operation in which the refrigerant is circulated in the order of the compressor 8, the outdoor heat exchanger 11, the outdoor expansion valve 12, the indoor expansion valves 31a and 31b, and the indoor heat exchangers 32a and 32b. Is done. The cooling operation, the heating operation, and the defrosting operation are performed by the control unit 23.

  During the cooling operation, the four-way switching valve 10 is switched to the outdoor heat radiation state (the state shown by the solid line in FIG. 1). In the refrigerant circuit 6, the low-pressure gas refrigerant of the refrigeration cycle is sucked into the compressor 8, compressed to the high pressure of the refrigeration cycle, and then discharged. The high-pressure gas refrigerant discharged from the compressor 8 is sent to the outdoor heat exchanger 11 through the four-way switching valve 10. The high-pressure gas refrigerant sent to the outdoor heat exchanger 11 exchanges heat with the outdoor air supplied as a cooling source by the outdoor fan 15 to radiate heat in the outdoor heat exchanger 11 functioning as a radiator of the refrigerant. , Becomes a high-pressure liquid refrigerant. The high-pressure liquid refrigerant that radiates heat in the outdoor heat exchanger 11 is sent to the indoor expansion valves 31a and 31b through the outdoor expansion valve 12, the liquid-side closing valve 13 and the liquid refrigerant communication pipe 4. The refrigerant sent to the indoor expansion valves 31a, 31b is decompressed by the indoor expansion valves 31a, 31b to a low pressure in the refrigeration cycle, and becomes a low-pressure refrigerant in a gas-liquid two-phase state. The low-pressure gas-liquid two-phase refrigerant decompressed by the indoor expansion valves 31a, 31b is sent to the indoor heat exchangers 32a, 32b. The low-pressure gas-liquid two-phase refrigerant sent to the indoor heat exchangers 32a and 32b exchanges heat with the indoor air supplied as a heating source by the indoor fans 33a and 33b in the indoor heat exchangers 32a and 32b. Evaporate. As a result, the indoor air is cooled, and then the indoor air is supplied to cool the room. The low-pressure gas refrigerant evaporated in the indoor heat exchangers 32a and 32b is again sucked into the compressor 8 through the gas refrigerant communication pipe 5, the gas side closing valve 14, the four-way switching valve 10 and the accumulator 7.

  During the heating operation, the four-way switching valve 10 is switched to the outdoor evaporation state (the state shown by the broken line in FIG. 1). In the refrigerant circuit 6, the low-pressure gas refrigerant of the refrigeration cycle is sucked into the compressor 8, compressed to the high pressure of the refrigeration cycle, and then discharged. The high-pressure gas refrigerant discharged from the compressor 8 is sent to the indoor heat exchangers 32a and 32b through the four-way switching valve 10, the gas side closing valve 14 and the gas refrigerant communication pipe 5. The high-pressure gas refrigerant sent to the indoor heat exchangers 32a, 32b exchanges heat with the indoor air supplied as a cooling source by the indoor fans 33a, 33b in the indoor heat exchangers 32a, 32b to radiate heat. It becomes a high-pressure liquid refrigerant. As a result, the indoor air is heated, and thereafter, the indoor air is supplied to heat the room. The high-pressure liquid refrigerant that radiates heat in the indoor heat exchangers 32a and 32b is sent to the outdoor expansion valve 12 through the indoor expansion valves 31a and 31b, the liquid refrigerant communication pipe 4 and the liquid side closing valve 13. The refrigerant sent to the outdoor expansion valve 12 is decompressed by the outdoor expansion valve 12 to a low pressure of the refrigeration cycle, and becomes a low-pressure refrigerant in a gas-liquid two-phase state. The low-pressure gas-liquid two-phase refrigerant that has been decompressed by the outdoor expansion valve 12 is sent to the outdoor heat exchanger 11. The low-pressure gas-liquid two-phase refrigerant sent to the outdoor heat exchanger 11 exchanges heat with the outdoor air supplied as a heating source by the outdoor fan 15 in the outdoor heat exchanger 11 that functions as a refrigerant evaporator. It then evaporates to a low pressure gas refrigerant. The low-pressure refrigerant evaporated in the outdoor heat exchanger 11 is sucked into the compressor 8 again through the four-way switching valve 10 and the accumulator 7.

  During the above heating operation, when frost formation in the outdoor heat exchanger 11 is detected due to the temperature of the refrigerant in the outdoor heat exchanger 11 becoming lower than a predetermined temperature, that is, when the outdoor heat exchanger 11 is defrosted. When the condition to start is reached, the defrosting operation for melting the frost adhering to the outdoor heat exchanger 11 is performed.

  The defrosting operation is performed by switching the four-way switching valve 22 to the outdoor heat radiation state (the state shown by the solid line in FIG. 1) and causing the outdoor heat exchanger 11 to function as a heat radiator of the refrigerant, as in the cooling operation. Be seen. Thereby, the frost adhering to the outdoor heat exchanger 11 can be melted. The defrosting operation is performed outdoors until the defrosting time set in consideration of the heating operation state before defrosting elapses or when the temperature of the refrigerant in the outdoor heat exchanger 11 becomes higher than a predetermined temperature. This is performed until it is determined that the defrosting in the heat exchanger 11 is completed, and then the heating operation is resumed. The flow of the refrigerant in the refrigerant circuit 10 during the defrosting operation is the same as that in the cooling operation, and thus the description thereof is omitted here.

(3) Overall Configuration of Outdoor Unit FIG. 2 is an external perspective view of the outdoor unit 2. FIG. 3 is a front view of the outdoor unit 2 (illustrated excluding the refrigerant circuit components other than the outdoor heat exchanger 11).

  The outdoor unit 2 is a top-blowing heat exchange unit that sucks air from the side surface of the casing 40 and blows air from the top surface of the casing 40. The outdoor unit 2 mainly includes a casing 40 having a substantially rectangular parallelepiped box shape, an outdoor fan 15 as a blower, devices 7, 8, 11 such as a compressor and an outdoor heat exchanger, a four-way switching valve and an outdoor expansion valve. And a refrigerant circuit component that constitutes a part of the refrigerant circuit 6 including the valves 10, 12 to 14, the refrigerant tubes 16 to 22, and the like. In the following description, “upper”, “lower”, “left”, “right”, “front”, “rear”, “front”, and “rear” are shown in FIG. 2 unless otherwise specified. This means the direction when the outdoor unit 2 to be viewed is viewed from the front (the front left side of the drawing).

  The casing 40 mainly includes a bottom frame 42 spanning over a pair of installation legs 41 extending in the left-right direction, a column 43 extending vertically from a corner of the bottom frame 42, and a fan module 44 attached to an upper end of the column 43. And a front panel 45, and air inlets 40a, 40b, 40c for air are formed on the side surfaces (here, the rear surface and the left and right side surfaces in this case), and an air outlet 40d for the air is formed on the top surface.

  The bottom frame 42 forms the bottom surface of the casing 40, and the outdoor heat exchanger 11 is provided on the bottom frame 42. Here, the outdoor heat exchanger 11 is a heat exchanger having a substantially U shape in a plan view, which faces the back surface and the left and right side surfaces of the casing 40, and substantially forms the back surface and the left and right side surfaces of the casing 40. .. The bottom frame 42 is in contact with the lower end portion of the outdoor heat exchanger 11, and functions as a drain pan that receives drain water generated in the outdoor heat exchanger 11 during the cooling operation or the defrosting operation.

  A fan module 44 is provided on the upper side of the outdoor heat exchanger 11, and forms a front side, a rear side of the casing 40, a portion above the columns 43 on both left and right sides, and a top surface of the casing 40. .. Here, the fan module 44 is an assembly in which the outdoor fan 15 is housed in a substantially rectangular parallelepiped box whose upper and lower surfaces are open. An opening on the top surface of the fan module 44 is an outlet 40d, and an outlet grill 46 is provided at the outlet 40d. The outdoor fan 15 is arranged in the casing 40 so as to face the air outlet 40d, and is an air blower that takes air into the casing 40 through the air inlets 40a, 40b, and 40c and discharges the air through the air outlet 40d.

  The front panel 45 is bridged between the columns 43 on the front side, and forms the front surface of the casing 40.

  Refrigerant circuit components other than the outdoor fan 15 and the outdoor heat exchanger 11 (the accumulator 7 and the compressor 8 are shown in FIG. 2) are also accommodated in the casing 40. Here, the compressor 8 and the accumulator 7 are provided on the bottom frame 42.

  As described above, the outdoor unit 2 includes the casing 40 in which the air inlets 40a, 40b, 40c are formed on the side surfaces (here, the rear surface and the left and right side surfaces) and the air outlet 40d is formed on the top surface, and the casing 40. It has the outdoor fan 15 (blower) which is arrange | positioned facing the blower outlet 40d inside, and the outdoor heat exchanger 11 arrange | positioned below the outdoor fan 15 in the casing 40. In such an upper-blowing unit configuration, as shown in FIG. 3, since the outdoor heat exchanger 11 is arranged below the outdoor fan 15, the wind speed of the air passing through the outdoor heat exchanger 11 is The upper part of the outdoor heat exchanger 11 tends to be faster than the lower part of the outdoor heat exchanger 11.

(4) Outdoor heat exchanger of the first embodiment <Structure>
FIG. 4 is a schematic perspective view of the outdoor heat exchanger 11 as the heat exchanger according to the first embodiment. FIG. 5 is a partially enlarged perspective view of the heat exchange paths 60A to 60J of FIG. FIG. 6 is a schematic configuration diagram (viewed from the leeward side) of the outdoor heat exchanger 11 as the heat exchanger according to the first embodiment. FIG. 7 is a schematic configuration diagram (viewed from the windward side) of the outdoor heat exchanger 11 as the heat exchanger according to the first embodiment. FIG. 8 is a plan sectional view of the connection header 90. FIG. 9 is a diagram showing a path configuration near the first heat exchange path 60A of the outdoor heat exchanger 11 as the heat exchanger according to the first embodiment. The arrows indicating the flow of the refrigerant in FIGS. 4, 6, 7, and 9 are the flow directions of the refrigerant during the heating operation (when the outdoor heat exchanger 11 functions as the evaporator of the refrigerant).

  The outdoor heat exchanger 11 is a heat exchanger that performs heat exchange between the refrigerant and the outdoor air, and mainly includes a first header collecting pipe 70, a second header collecting pipe 80, a connecting header 90, and a plurality of flat tubes. It has 63 and a plurality of fins 64. Here, the first header collecting pipe 70, the second header collecting pipe 80, the connecting header 90, the flat pipe 63, and the fin 64 are all formed of aluminum or aluminum alloy and are joined to each other by brazing or the like. ..

  The first header collecting pipe 70 is a vertically elongated hollow tubular member having closed upper and lower ends. The first header collecting pipe 70 is erected on one end side (here, the left front end side in FIG. 4 or the left end side in FIG. 6) of the outdoor heat exchanger 11.

  The second header collecting pipe 80 is a vertically elongated hollow tubular member having closed upper and lower ends. The second header collecting pipe 80 is erected on one end side (here, the left front end side in FIG. 4 or the right end side in FIG. 7) of the outdoor heat exchanger 11. Here, the second header collecting pipe 80 is arranged on the windward side of the first header collecting pipe 70 in the air ventilation direction.

  The connection header 90 is a vertically elongated hollow tubular member having closed upper and lower ends. The second header collecting pipe 80 is erected on one end side (here, the right front end side in FIG. 4, the right end side in FIG. 6, or the left end side in FIG. 7) of the outdoor heat exchanger 11.

  The flat tube 63 is a flat multi-hole tube having a flat surface portion 63a that is a heat transfer surface and faces the vertical direction, and a passage 63b that is formed of a large number of small through holes through which the refrigerant formed therein flows. The flat tubes 63 are arranged in multiple stages in the vertical direction (step direction), and are also arranged in multiple rows (here, two rows) in the air ventilation direction (row direction). One end of the flat pipe 63 arranged on the leeward side in the air ventilation direction is connected to the first header collecting pipe 70, and the other end is connected to the connection header 90. One end of the flat pipe 63 arranged on the windward side in the air ventilation direction is connected to the second header collecting pipe 80, and the other end is connected to the connection header 90. The fin 64 divides the flat tubes 63 adjacent to each other into a plurality of ventilation paths through which air flows, and a plurality of horizontally extending elongated cutouts 64 a are formed so that the plurality of flat tubes 63 can be inserted. .. Here, the direction in which the flat portion 63a of the flat tube 63 faces is the vertical direction (step direction), and the longitudinal direction of the flat tube 63 is the horizontal direction along the side surfaces (here, both left and right side surfaces in this case) and back surface of the casing 40. Therefore, the direction in which the cutout portion 64a extends means the horizontal direction (column direction) that intersects the longitudinal direction of the flat tube 63, and substantially matches the air ventilation direction (column direction) in the casing 40. ing. The notch portion 64a is elongated in the horizontal direction (row direction) so that the flat tube 63 is inserted from the leeward side to the windward side in the ventilation direction. The shape of the notch 64 a of the fin 64 substantially matches the outer shape of the cross section of the flat tube 63. The cutouts 64a of the fins 64 are formed at predetermined intervals in the vertical direction (step direction) of the fins 64. The fins 64 include a plurality of fin main portions 64b sandwiched between notch portions 64a adjacent to each other in the up-down direction (step direction), and a plurality of fins on the windward side (column direction) of the notch portions 64a. The fin main part 64b and the fin windward part 64c which extends continuously are included. Like the flat tubes 63, the fins 64 are arranged in multiple rows (here, two rows) in the direction in which air passes through the ventilation path (ventilation direction, row direction).

  In the outdoor heat exchanger 11, the flat tubes 63 are divided into a plurality of heat exchange paths 60A to 60J arranged in multiple stages (here, 10 stages) in the vertical direction (step direction). Further, the flat tubes 63 are arranged in multiple rows (here, two rows) in the ventilation direction (row direction) in which air passes through the ventilation passages. Specifically, here, from the bottom to the top, the first heat exchange path 60A, the second heat exchange path 60B ... An exchange path 60J is formed. The first heat exchange path 60A has two stages of two rows (four in total) of the flat tubes 63 including the flat tubes 63AU and 63AD in the lowermost stage. Each of the second and third heat exchange paths 60B and 60C has 12 stages and 2 rows (24 tubes in total) of flat tubes 63. The fourth heat exchange path 60D has 11 stages and 2 rows (22 tubes in total) of the flat tubes 63. The fifth and sixth heat exchange paths 60E and 60F each have flat tubes 63 in 10 rows and 2 columns (total of 20 tubes). The seventh heat exchange path 60G has nine stages and two rows (18 in total) of the flat tubes 63. The eighth heat exchange path 60H has eight stages and two rows (16 in total) of the flat tubes 63. The ninth heat exchange path 60I has seven stages and two rows (14 tubes in total) of the flat tubes 63. The tenth heat exchange path 60J has 6 stages and 2 rows (12 in total) of flat tubes 63.

  The inner space of the first header collecting pipe 70 is vertically divided by a partition plate 71, so that communication spaces 72A to 72J corresponding to the heat exchange paths 60A to 60J are formed. Further, the first communication space 72A corresponding to the first heat exchange path 60A is further divided into upper and lower parts by the partition plate 73, so that the lower first gas side inlet / outlet space 72AL and the upper first liquid side inlet / outlet space are formed. 72 AU are formed. In the following description, the communication spaces 72B to 72J other than the first communication space 72A are referred to as gas side entrance / exit spaces 72B to 72J.

  And the 1st gas side entrance / exit space 72AL of the flat tubes 63 which constitute the 1st heat exchange path 60A is the leeward side of the column direction and the flat tube 63AD of the lowest stage (1st leeward stage heat exchange part 61AL). It communicates with one end. The first liquid side inlet / outlet space 72AU is a part of the flat tubes 63 constituting the first heat exchange path 60A, which is located above the first leeward lower stage heat exchange section 61AL of the flat tube 63 (first leeward upper stage heat exchange section 61AU). It communicates with one end. The second gas-side inlet / outlet space 72B communicates with one end of twelve of the flat tubes 63 forming the second heat exchange path 60B on the leeward side in the column direction (second leeward heat exchange section 61B). The third gas side inlet / outlet space 72C communicates with one end of twelve of the flat tubes 63 constituting the third heat exchange path 60C on the leeward side in the column direction (third leeward heat exchange section 61C). The fourth gas side inlet / outlet space 72D communicates with one end of eleven of the flat tubes 63 constituting the fourth heat exchange path 60D on the leeward side in the column direction (fourth leeward heat exchange section 61D). The fifth gas side inlet / outlet space 72E communicates with one end of ten leeward side (fifth leeward heat exchange section 61E) in the column direction of the flat tubes 63 forming the fifth heat exchange path 60E. The sixth gas side inlet / outlet space 72F communicates with one end of ten of the flat tubes 63 constituting the sixth heat exchange path 60F on the leeward side in the column direction (sixth leeward heat exchange section 61F). The seventh gas side inlet / outlet space 72G communicates with one end of nine leeward side (seventh leeward side heat exchange section 61G) in the column direction of the flat tubes 63 forming the seventh heat exchange path 60G. The eighth gas-side inlet / outlet space 72H communicates with one end of eight leeward sides (eighth leeward heat exchange section 61H) in the column direction of the flat tubes 63 forming the eighth heat exchange path 60H. The ninth gas side inlet / outlet space 72I communicates with one end of seven leeward sides of the flat tubes 63 forming the ninth heat exchange path 60I (the ninth leeward side heat exchange portion 61I) in the column direction. The tenth gas-side inlet / outlet space 72J communicates with one end of six leeward side (tenth leeward side heat exchanging portion 61J) in the column direction of the flat tubes 63 constituting the tenth heat exchange path 60J.

  The inner space of the second header collecting pipe 80 is vertically divided by a partition plate 81, so that communication spaces 82A to 82J corresponding to the heat exchange paths 60A to 60J are formed. In the following description, the first communication space 82A will be referred to as a first vertical folding space 82A, and the communication spaces 82B to 82J other than the first communication space 82A will be referred to as liquid side inlet / outlet spaces 82B to 82J.

  The lower part of the first vertical folding space 82A is located on the windward side in the column direction of the flat tubes 63 constituting the first heat exchange path 60A and is the lowest flat tube 63AU (first wind up-down side heat exchange section 62AL). ) Is connected to one end. The upper portion of the first vertical folding space 82A has an upper flat tube 63 (first windward upper stage side heat exchange section) of the first wind upper / lower stage side heat exchange section 62AL of the flat tubes 63 constituting the first heat exchange path 60A. 62 AU). The second liquid-side inlet / outlet space 82B communicates with one end of twelve of the flat tubes 63 forming the second heat exchange path 60B on the windward side in the column direction (second windward heat exchange section 62B). The third liquid-side inlet / outlet space 82C communicates with one end of 12 of the flat tubes 63 forming the third heat exchange path 60C on the windward side in the column direction (third windward heat exchange section 62C). The fourth liquid-side inlet / outlet space 82D communicates with one end of eleven of the flat tubes 63 forming the fourth heat exchange path 60D on the windward side in the column direction (fourth windward heat exchange section 62D). The fifth liquid-side inlet / outlet space 82E communicates with one end of ten of the flat tubes 63 constituting the fifth heat exchange path 60E on the windward side in the column direction (fifth windward heat exchange section 62E). The sixth liquid side inlet / outlet space 82F communicates with one end of ten of the flat tubes 63 constituting the sixth heat exchange path 60F on the windward side in the column direction (sixth windward heat exchange section 62F). The seventh liquid-side inlet / outlet space 82G communicates with one end of nine of the flat tubes 63 forming the seventh heat exchange path 60G on the windward side in the column direction (seventh windward heat exchange section 62G). The eighth liquid-side inlet / outlet space 82H communicates with one end of the eight pipes (eighth windward heat exchange section 62H) on the windward side in the column direction of the flat tubes 63 forming the eighth heat exchange path 60H. The ninth liquid-side inlet / outlet space 82I communicates with one end of seven of the flat tubes 63 forming the ninth heat exchange path 60I on the windward side in the column direction (the ninth windward-side heat exchange section 62I). The tenth liquid side inlet / outlet space 82J communicates with one end of the six pipes (tenth windward heat exchanging portion 62J) on the windward side in the column direction of the flat tubes 63 constituting the tenth heat exchange path 60J.

  The connection header 90 is divided into upper and lower internal spaces by a partition plate 91 to form communication spaces 92A to 92J corresponding to the heat exchange paths 60A to 60J. Further, the first communication space 92A corresponding to the first heat exchange path 60A is further partitioned into upper and lower parts by the partition plate 93, so that the lower first lower lateral folding space 92AL and the upper first upper lateral folding space 92AL. A space 92AU is formed. In the following description, the communication spaces 92B to 92J other than the first communication space 92A are referred to as horizontal folding spaces 92B to 92J.

  Each of the laterally folded spaces 92A to 92J communicates with the flat tubes 63 that form the corresponding heat exchange paths 60A to 60J. That is, the first lower lateral folding space 92AL is located on the windward side in the column direction of the flat tubes 63 constituting the first heat exchange section 60A and is the lowest flat tube 63AU (first wind upper / lower heat exchange section 62AL). ) And the other end of the flat tubes 63 constituting the first heat exchange section 60A on the leeward side in the column direction and at the bottom of the flat tubes 63AD (first leeward heat exchange section 61AL). It is in communication. The first upper lateral folding space 92AU is a flat tube 63 (first windward upper stage heat exchange portion 62AU) above the first wind upper / lower stage side heat exchange portion 62AL among the flat tubes 63 constituting the first heat exchange portion 60A. ) And the other end of the flat tube 63 (first leeward upper heat exchanger 61AU) above the first leeward lower heat exchanger 61AL of the flat tubes 63 constituting the first heat exchanger 60A. , To communicate with. The second horizontal folding space 92B includes the second heat exchange path and the other ends of the 12 tubes (second windward heat exchange section 62B) on the windward side in the column direction of the flat tubes 63 that form the second heat exchange path 60B. Among the flat tubes 63 forming the 60B, they communicate with the other ends of the 12 leeward side of the column direction (the second leeward side heat exchange section 61B). 92 C of 3rd horizontal folding | turning spaces, the other end of 12 windward side (3rd windward side heat exchange part 62C) of the flat tubes 63 which comprise 60 C of 3rd heat exchange paths, and 3rd heat exchange path. It communicates with the other end of the 12 tubes (third leeward side heat exchange section 61C) on the leeward side in the column direction of the flat tubes 63 constituting the 60C. The fourth horizontal folding space 92D includes the other ends of eleven pipes (fourth windward heat exchange section 62D) on the windward side in the column direction of the flat tubes 63 that form the fourth heat exchange path 60D, and the fourth heat exchange path. Among the flat tubes 63 constituting the 60D, the flat tubes 63 communicate with the other ends on the leeward side in the column direction (fourth leeward heat exchange section 61D). The fifth lateral folded space 92E is connected to the other ends of the ten pipes (fifth windward heat exchange section 62E) on the windward side in the column direction of the flat tubes 63 constituting the fifth heat exchange path 60E, and the fifth heat exchange path. It communicates with the other end of the ten leeward side (fifth leeward side heat exchange section 61E) in the row direction of the flat tubes 63 constituting the 60E. The sixth horizontal folding space 92F includes the other ends of the ten pipes (sixth windward heat exchanging portion 62F) on the windward side in the column direction of the flat tubes 63 constituting the sixth heat exchanging path 60F, and the sixth heat exchanging path. It communicates with the other ends of the ten leeward sides (sixth leeward side heat exchange portions 61F) in the row direction of the flat tubes 63 constituting the 60F. The seventh horizontal folding space 92G includes the other ends of the nine tubes (seventh windward heat exchange section 62G) on the windward side in the column direction of the flat tubes 63 that form the seventh heat exchange path 60G, and the seventh heat exchange path. It communicates with the other end of the nine tubes (seventh leeward heat exchange section 61G) on the leeward side in the column direction of the flat tubes 63 that form 60G. The eighth horizontal folding space 92H includes the other ends of the eight tubes (eighth windward heat exchange section 62H) on the windward side in the column direction of the flat tubes 63 that form the eighth heat exchange path 60H, and the eighth heat exchange path. Among the flat tubes 63 forming the 60H, the flat tubes 63 communicate with the other ends of the eight leeward sides in the column direction (eighth leeward heat exchange section 61H). The ninth horizontal folding space 92I includes the other ends of the seven tubes (the ninth windward side heat exchanging portion 62I) on the windward side in the column direction of the flat tubes 63 forming the ninth heat exchanging path 60I, and the ninth heat exchanging path. It communicates with the other ends of seven (9th leeward side heat exchanging parts 61I) on the leeward side in the column direction of the flat tubes 63 constituting the 60I. The tenth horizontal folding space 92J includes the other ends of the six pipes (the tenth windward heat exchange section 62I) on the windward side in the column direction of the flat tubes 63 that form the tenth heat exchange path 60J, and the tenth heat exchange path. It communicates with the other ends of the six tubes (tenth leeward side heat exchange section 61J) on the leeward side in the column direction of the flat tubes 63 constituting 60J. In addition, here, by providing the partition plates 91 and 93 so that the other ends of the flat tubes 63 adjacent to each other in the column direction communicate with each other, the horizontally folded spaces 92A to 92J are formed so that the flat tubes 63 adjacent to each other in the column direction. Are formed so that the other ends thereof communicate with each other. However, the present invention is not limited to this, and since the partition plates 91 and 93 are not provided in the same heat exchange portions 61A to 61J and 62A to 62J, the lateral folding spaces 92A to 92J are adjacent to each other in the column direction. It may be formed between the exchange parts 61A to 61J and 62A to 62J.

  Further, the refrigerant sent from the outdoor expansion valve 12 (see FIG. 1) during the heating operation is split into the first header collecting pipe 70 and the second header collecting pipe 80 and sent to each liquid side inlet / outlet space 72AU, 82B to 82J. The liquid-side flow dividing member 85 and the gas-side flow dividing member 75 that divides the refrigerant sent from the compressor 8 (see FIG. 1) during the cooling operation into the gas-side inlet / outlet spaces 72AL, 72B to 72J and sends the refrigerant are connected to each other. ..

  The liquid-side flow dividing member 85 is connected to the liquid-side refrigerant flow distributor 86 connected to the refrigerant pipe 20 (see FIG. 1), and is connected to each of the liquid-side inlet / outlet spaces 72AU, 82B to 82J. Liquid side refrigerant distribution pipes 87A to 87F. Here, each of the liquid-side refrigerant distribution pipes 87A to 87F has a capillary tube, and has a length corresponding to the distribution ratio to the heat exchange paths 60A to 60J.

  The gas-side distribution member 75 extends from the gas-side refrigerant distribution / distribution pipe 76 connected to the refrigerant pipe 19 (see FIG. 1) and the gas-side refrigerant distribution / distribution pipe 76 to the gas-side inlet / outlet spaces 72AL, 72B to 72J. The gas side refrigerant branch pipes 77A to 77J to be connected are included.

  As a result, the heat exchange paths 60B to 60J other than the first heat exchange path 60A have windward heats on the windward side in the row direction and windward heats on the leeward side of the windward heat exchange portions 62B to 62J. The leeward side heat exchange parts 61B to 61J are connected in series to the exchange parts 62B to 62J. That is, the second heat exchange path 60B includes twelve flat tubes 63 forming the second leeward heat exchange section 61B communicating with the second gas side inlet / outlet space 72B, and the windward side of the second leeward heat exchange section 61B. And the twelve flat tubes 63 forming the second windward heat exchange portion 62B that are located in the second liquid side inlet / outlet space 82B and are connected in series through the second horizontal folding space 92B. is doing. The third heat exchange path 60C is located on the windward side of the twelve flat tubes 63 forming the third leeward heat exchange section 61C communicating with the third gas side inlet / outlet space 72C and the third leeward heat exchange section 61C. The 12 flat tubes 63 forming the third windward heat exchange section 62C communicating with the third liquid side inlet / outlet space 82C are connected in series through the third horizontal folding space 92C. There is. The fourth heat exchange path 60D is located on the windward side of the eleven flat tubes 63 that form the fourth leeward heat exchange section 61D that communicates with the fourth gas side inlet / outlet space 72D, and the fourth leeward heat exchange section 61D. In addition, the eleven flat tubes 63 forming the fourth windward side heat exchange portion 62D communicating with the fourth liquid side inlet / outlet space 82D are connected in series through the fourth horizontal folding space 92D. There is. The fifth heat exchange path 60E is located on the windward side of the ten flat tubes 63 forming the fifth leeward heat exchange section 61E communicating with the fifth gas side inlet / outlet space 72E and the fifth leeward heat exchange section 61E. The ten flat tubes 63 forming the fifth windward side heat exchange section 62E communicating with the fifth liquid side inlet / outlet space 82E are connected in series through the fifth horizontal folding space 92E. There is. The sixth heat exchange path 60F is located on the windward side of the ten flat tubes 63 forming the sixth leeward heat exchange section 61F communicating with the sixth gas side inlet / outlet space 72F and the sixth leeward heat exchange section 61F. The ten flat tubes 63 forming the sixth windward heat exchange section 62F communicating with the sixth liquid side inlet / outlet space 82F are connected in series through the sixth horizontal folding space 92F. There is. The seventh heat exchange path 60G is located on the windward side of the nine flat tubes 63 forming the seventh leeward heat exchange portion 61G communicating with the seventh gas side inlet / outlet space 72G, and the windward side of the seventh leeward heat exchange portion 61G. It has a configuration in which the nine flat tubes 63 forming the seventh windward heat exchange portion 62G communicating with the seventh liquid side inlet / outlet space 82G are connected in series through the seventh horizontal folding space 92G. There is. The eighth heat exchange path 60H is located on the windward side of the eight flat tubes 63 forming the eighth leeward heat exchange section 61H communicating with the eighth gas side inlet / outlet space 72H and the eighth leeward heat exchange section 61H. The eight flat tubes 63 forming the eighth windward heat exchange section 62H communicating with the eighth liquid-side inlet / outlet space 82H are connected in series through the eighth horizontal folding space 92H. There is. The ninth heat exchange path 60I is located on the windward side of the seven flat tubes 63 forming the ninth leeward heat exchange section 61I communicating with the ninth gas side inlet / outlet space 72I and the ninth leeward heat exchange section 61I. It has a configuration in which seven flat tubes 63 forming a ninth windward heat exchange section 62I communicating with the ninth liquid side inlet / outlet space 82I are connected in series through a ninth horizontal folding space 92I. There is. The tenth heat exchange path 60J is located on the windward side of the six flat tubes 63 forming the tenth leeward heat exchange portion 61J communicating with the tenth gas side inlet / outlet space 72J and the tenth leeward heat exchange portion 61J. The six flat tubes 63 forming the tenth windward heat exchange section 62J communicating with the tenth liquid side inlet / outlet space 82J are connected in series through the tenth horizontal folding space 92J. There is. The first heat exchange path 60A is a windward side in the column direction and a first wind upper / lower stage side heat exchange section 62AL including the lowermost flat tube 63AU, and a first upper side of the first wind upper / lower stage side heat exchange section 62AL. An upwind-side heat exchange section 62AU, a first leeward-stage heat exchange section 61AL including the flat tubes 63AD on the leeward side of the upwind-side heat exchange sections 62AL and 62AU, and the first leeward-stage heat exchange. And a first leeward upper heat exchange portion 61AU on the upper side of the portion 61AL. That is, the first heat exchange path 60A includes the lowermost flat tubes 63AD forming the first leeward stage heat exchange section 61AL communicating with the first gas side inlet / outlet space 72AL and the first leeward stage heat exchange section 61AL. The lowermost flat tube 63AU that constitutes the first wind upper / lower stage heat exchange section 62AL located on the windward side, and the first windward / upper side heat exchange section located on the upper side of the first wind upper / lower stage side heat exchange section 62AL. The flat tube 63 that constitutes the 62 AU and the flat tube 63 that constitutes the first leeward upper-stage heat exchange section 61 AU that communicates with the first liquid side inlet / outlet space 72 AU are connected in series in sequence. Here, the flat tube 63AD in the lowermost stage, which constitutes the first leeward lower stage heat exchange section 61AL communicating with the first gas side inlet / outlet space 72AL, passes through the first lower lateral folding space 92AL to generate the first wind upper / lower stage side heat. It is connected in series to the flat tube 63AU at the bottom of the exchange section 62AL. The flat tube 63AU at the lowermost stage that constitutes the first wind up-and-down side heat exchange section 62AL is connected in series to the flat tube 63 that constitutes the first upwind-side heat exchange section 62AU through the first vertical folding space 82A. ing. The flat tubes 63 forming the first upwind-side heat exchange section 62AU are connected in series to the flat tubes 63 forming the first leeward-upper side heat exchange section 61AU through the first upper lateral folding space 92AU.

<Operation (refrigerant flow)>
Next, the flow of the refrigerant in the outdoor heat exchanger 11 having the above configuration will be described.

  During the cooling operation, the outdoor heat exchanger 11 functions as a radiator for the refrigerant discharged from the compressor 8 (see FIG. 1). In addition, here, the refrigerant flows in the direction opposite to the arrow indicating the flow of the refrigerant in FIGS. 4, 6, 7, and 9.

  The refrigerant discharged from the compressor 8 (see FIG. 1) is sent to the gas side flow dividing member 75 through the refrigerant pipe 19 (see FIG. 1). The refrigerant sent to the gas side distribution member 75 is branched from the gas side refrigerant distribution mother pipe 76 to each of the gas side refrigerant distribution branch pipes 77A to 77J, and each of the gas side inlet / outlet spaces 72AL and 72B of the first header collecting pipe 70. ~ 72J.

  The refrigerant sent to the gas side inlet / outlet spaces 72B to 72J other than the first gas side inlet / outlet space 72AL is diverted to the flat tubes 63 constituting the leeward side heat exchange sections 61B to 61J of the heat exchange paths 60B to 60J. .. The refrigerant sent to each flat tube 63 radiates heat by exchanging heat with the outdoor air while flowing through the passage 63b, and passes through the laterally folded spaces 92B to 92J of the connection header 90 to the heat exchange paths 60B to 60J. It is sent to the flat tubes 63 that form the windward heat exchange units 62B to 62J. The refrigerant sent to each flat pipe 63 further radiates heat by heat exchange with the outdoor air while flowing through the passage 63b, and joins in the liquid side inlet / outlet spaces 82B to 82J of the second header collecting pipe 80. That is, the refrigerant passes through the heat exchange paths 60B to 60J in the order of the leeward side heat exchange sections 61B to 61J and the leeward side heat exchange sections 62B to 62J. At this time, the refrigerant radiates heat from the superheated gas state to the saturated liquid state or the supercooled liquid state.

  The refrigerant sent to the first gas side inlet / outlet space 72AL is sent to the flat tubes 63 (the lowest flat tubes 63AD) that form the first leeward-side heat exchange section 61AL of the first heat exchange path 60A. The refrigerant sent to the flat tube 63 radiates heat by heat exchange with the outdoor air while flowing through the passage 63b, and passes through the first lower lateral folding space 92AL of the connection header 90 to generate the first heat exchange path 60A. The air is sent to the flat tubes 63 (the lowest flat tubes 63AU) that constitute the first wind upper and lower heat exchange section 62AL. The refrigerant sent to the flat pipe 63 further radiates heat by exchanging heat with the outdoor air while flowing through the passage 63b, and passes through the first vertical folded space 82A of the second header collecting pipe 80 to the first heat exchange path. It is sent to the flat tube 63 that constitutes the first upwind side heat exchange portion 62AU of 60A. The refrigerant sent to the flat tube 63 further radiates heat by heat exchange with the outdoor air while flowing through the passage 63b, and passes through the first upper lateral folding space 92AU of the connection header 90 to the first heat exchange path 60A. It is sent to the flat tube 63 that constitutes the first leeward upper heat exchanger 61AU. The refrigerant sent to the flat pipe 63 further radiates heat by heat exchange with the outdoor air while flowing through the passage 63b, and is sent to the first liquid side inlet / outlet space 72AU of the first header collecting pipe 70. That is, the refrigerant is the first leeward and lower stage side heat exchange section 61AL, the first leeward and upper stage side heat exchange section 62AL, the first leeward and upper stage side heat exchange section 62AU, the first leeward and upper stage side heat exchange section 61AU, in that order. It passes through one heat exchange path 60A. At this time, the refrigerant radiates heat from the superheated gas state to the saturated liquid state or the supercooled liquid state.

  The refrigerants sent to the liquid-side inlet / outlet spaces 72AU, 82B to 82J are sent to the liquid-side refrigerant distribution pipes 87A to 87J of the liquid-side refrigerant distribution member 85 and merge in the liquid-side refrigerant distributor 86. The refrigerant merged in the liquid-side refrigerant distributor 86 is sent to the outdoor expansion valve 12 (see FIG. 1) through the refrigerant pipe 20 (see FIG. 1).

  During the heating operation, the outdoor heat exchanger 11 functions as an evaporator for the refrigerant whose pressure has been reduced in the outdoor expansion valve 12 (see FIG. 1). Note that here, the refrigerant flows in the direction of the arrow that indicates the flow of the refrigerant in FIGS. 4, 6, 7, and 9.

  The refrigerant whose pressure has been reduced in the outdoor expansion valve 12 is sent to the liquid-side refrigerant distribution member 85 through the refrigerant pipe 20 (see FIG. 1). The refrigerant sent to the liquid-side refrigerant distribution member 85 is divided from the liquid-side refrigerant distributor 86 into the liquid-side refrigerant distribution pipes 87A to 87F, and the liquid-side inlets and outlets of the first and second header collecting pipes 70 and 80. It is sent to the spaces 72AU and 82B to 82J.

  The refrigerant sent to the liquid side inlet / outlet spaces 82B to 82J other than the first liquid side inlet / outlet space 72AU is diverted to the flat tubes 63 constituting the windward side heat exchange sections 62B to 62J of the heat exchange paths 60B to 60J. .. The refrigerant sent to each of the flat tubes 63 is heated by heat exchange with the outdoor air while flowing through the passage 63b, and passes through each of the laterally folded spaces 92B to 92J of the connection header 90 so that each of the heat exchange paths 60B to 60J. It is sent to the flat tubes 63 that constitute the leeward heat exchange units 62B to 62J. The refrigerant sent to each flat pipe 63 is further heated by heat exchange with the outdoor air while flowing through the passage 63b, and joins in the gas side inlet / outlet spaces 72B to 72J of the first header collecting pipe 70. That is, the refrigerant passes through the heat exchange paths 60B to 60J in the order of the windward side heat exchange sections 62B to 62J and the leeward side heat exchange sections 61B to 61J. At this time, the refrigerant is heated from the liquid state or the gas-liquid two-phase state to the superheated gas state by evaporating.

  The refrigerant sent to the first liquid side inlet / outlet space 72AU is sent to the flat tube 63 that constitutes the first leeward upper heat exchange section 61AU of the first heat exchange path 60A. The refrigerant sent to the flat tube 63 is heated by heat exchange with the outdoor air while flowing through the passage 63b, passes through the first upper lateral folding space 92AU of the connection header 90, and then passes through the first heat exchange path 60A. The air is sent to the flat tube 63 that constitutes the 1st windward upper side heat exchange portion 62AU. The refrigerant sent to the flat tube 63 is further heated by heat exchange with the outdoor air while flowing through the passage 63b, and passes through the first vertical folding space 82A of the second header collecting tube 80 to the first heat exchange path. It is sent to the flat tubes 63 (the bottom flat tubes 63AU) that form the first wind upper and lower heat exchangers 62AL of 60A. The refrigerant sent to the flat tube 63 is further heated by heat exchange with the outdoor air while flowing through the passage 63b, and passes through the first lower lateral folding space 92AL of the connection header 90 to the first heat exchange path 60A. Is sent to the flat tubes 63 (the lowest flat tubes 63AD) forming the first leeward lower heat exchange section 61AL. The refrigerant sent to the flat pipe 63 is further heated by heat exchange with the outdoor air while flowing through the passage 63b, and sent to the first gas side inlet / outlet space 72AL of the first header collecting pipe 70. That is, the refrigerant is the first leeward heat exchanger 61AU, the first leeward heat exchanger 62AU, the first leeward heat exchanger 62AL, and the first leeward heat exchanger 61AL in this order. It passes through one heat exchange path 60A. At this time, the refrigerant is heated from the liquid state or the gas-liquid two-phase state to the superheated gas state by evaporating.

  The refrigerant sent to each of the gas-side inlet / outlet spaces 72AL, 72B to 72J is sent to the gas-side refrigerant branch pipes 77A to 77J of the gas-side refrigerant branch member 75 and joins in the gas-side refrigerant branch pipe 76. The refrigerants that have merged in the gas-side refrigerant distribution mother pipe 76 are sent to the suction side of the compressor 8 (see FIG. 1) through the refrigerant pipe 19 (see FIG. 1).

  During the defrosting operation, the outdoor heat exchanger 11 functions as a radiator for the refrigerant discharged from the compressor 8 (see FIG. 1), as in the cooling operation. The flow of the refrigerant in the outdoor heat exchanger 11 during the defrosting operation is the same as that during the cooling operation, and thus the description thereof is omitted here. However, unlike the cooling operation, during the defrosting operation, the refrigerant mainly radiates heat while melting the frost adhering to the heat exchange paths 60A to 60J.

<Features>
The outdoor heat exchanger 11 (heat exchanger) of this embodiment and the air conditioning apparatus 1 including the same have the following features.

-A-
As described above, the heat exchanger 11 of the present embodiment includes a plurality of flat tubes 63 arranged vertically and having passages for the refrigerant formed therein, and a plurality of air tubes flowing between the adjacent flat tubes 63. It has a plurality of fins 64 which divide into a ventilation path. The flat tube 63 is divided into a plurality (here, 10) of heat exchange paths 60A to 60J arranged in multiple stages in the step direction. When the length of the passage 63b from one end to the other end of the flow of the refrigerant in each of the heat exchange paths 60A to 60J is defined as the path effective lengths LA to LJ, the first heat including the flat tubes 63AU and 63AD in the lowermost stage. The effective path length LA of the exchange path 60A is longer than the effective path lengths LB to LJ of the other heat exchange paths 60B to 60J. Specifically, each of the second to tenth heat exchange paths 60B to 60J is from each liquid side inlet / outlet space 82B to 82J as one end of the refrigerant flow to each gas side inlet / outlet space 72B from the other end of the refrigerant flow. Up to 72J, the flat tubes 63 forming the windward side heat exchange sections 62B to 62J and the flat tube 63 forming the leeward side heat exchange sections 61B to 61J are connected in series. Therefore, the path effective lengths LB to LJ of the respective second to tenth heat exchange paths 60B to 60J are the passages 63b of the flat tubes 63 constituting the respective windward side heat exchange portions 62B to 62J, and the respective leeward side heat exchanges. It is the length obtained by adding the passages 63b of the flat tubes 63 constituting the portions 61B to 61J (the length of the passages 63b for two flat tubes). The first heat exchange path 60A is located between the first liquid side inlet / outlet space 72AU as one end of the refrigerant flow and the first gas side inlet / outlet space 72AL as the other end of the refrigerant flow between the first leeward upper stage side. A flat tube 63 that constitutes the heat exchange section 61AU, a flat tube 63 that constitutes the first upwind side heat exchange section 62AU, and a lowermost flat tube 63AU that constitutes the first wind up and down side heat exchange section 62AL. , And the flat tube 63AD in the lowermost stage that constitutes the first leeward lower heat exchanger 61AL are connected in series. Therefore, the path effective length LA of the first heat exchange path 60A is the passage 63b of the flat tube 63 that constitutes the first leeward upper heat exchange section 61AU, and the flat tube that constitutes the first leeward upper heat exchange section 62AU. A passage 63b of 63, a passage 63b of the lowermost flat tube 63AU constituting the first wind up-down side heat exchange section 62AL, and a passage of the lowermost flat tube 63AD constituting the first downwind stage heat exchange section 61AL. It is the length obtained by adding 63b (the length of the passage 63b for four flat tubes). As described above, the effective path length LA of the first heat exchange path 60A is longer than the effective path lengths LB to LJ of the other heat exchange paths 60B to 60J.

  On the other hand, in the conventional heat exchanger, each heat exchange path is connected in series by the same number of flat tubes having the same shape (tube length and size and number of through holes that serve as refrigerant passages). It is configured. That is, the above conventional heat exchanger is configured such that the heat exchange paths have the same effective path length. When such a conventional heat exchanger is used in an air conditioner that switches between heating operation (when used as a refrigerant evaporator) and defrosting operation (when used as a refrigerant radiator). During the heating operation, the amount of frost on the lowermost heat exchange path tends to increase. First, the cause will be described.

  In this conventional configuration, during the heating operation, the refrigerant in the liquid state easily flows into the bottommost heat exchange path including the bottommost flat tube, and the bottommost heat exchange path is maintained without the temperature of the refrigerant rising sufficiently. As a result, the amount of frost formed on the lowermost heat exchange path tends to increase. That is, in the configuration of the conventional heat exchanger, the refrigerant in the liquid state easily flows into the lowermost heat exchange path during the heating operation, and flows out of the lowermost heat exchange path without sufficiently increasing the temperature of the refrigerant. It is presumed that this is the reason why the amount of frost in the lowermost heat exchange path tends to increase.

  Therefore, here, unlike the conventional heat exchanger, as described above, the effective path length LA of the first heat exchange path 60A in the lowermost stage including the flat tubes 63AU and 63AD in the lowermost stage is changed to other heat exchange paths. It is set longer than the effective path lengths LB to LJ of 60B to 60J.

  When the heat exchanger 11 having this configuration is adopted in the air conditioner 1 that switches between the heating operation and the defrosting operation, the effective path length LA of the first heat exchange path 60A becomes longer, The flow resistance of the refrigerant in the first heat exchange path 60A can be increased. For this reason, it becomes difficult for the liquid-state refrigerant to flow into the first heat exchange path 60A during the heating operation, and the temperature of the refrigerant flowing through the lowermost heat exchange path 60A easily rises. Frost can be suppressed. Moreover, here, since the heat transfer area in the first heat exchange path 60A can be increased by increasing the path effective length LA of the first heat exchange path 60A, the refrigerant flowing through the heat exchange path 60A in the lowermost stage. It is possible to accelerate the rise in temperature. As a result, it is possible to reduce the unmelted residue in the first heat exchange path 60A during the defrosting operation, as compared with the case where the conventional heat exchanger is adopted.

  Thus, here, by adopting the heat exchanger 11 having the above-described configuration in the air conditioning apparatus 1 that switches between the heating operation and the defrosting operation, frost formation in the lowermost heat exchange path 60A is suppressed. As a result, it is possible to reduce unmelted residue during the defrosting operation.

-B-
Further, in the heat exchanger 11 of the present embodiment, as described above, the effective path length LA of the first heat exchange path 60A is set to be twice the effective path lengths LB to LJ of the other heat exchange paths 60B to 60J. Therefore, the effective path length LA of the first heat exchange path 60A is sufficiently long. Therefore, the flow resistance and heat transfer area of the refrigerant in the first heat exchange path 60A can be sufficiently increased, and the effect of suppressing frost formation in the lowermost heat exchange path 60A can be enhanced. ..

  The effective path length LA of the first heat exchange path 60A is not limited to twice the effective path lengths LB to LJ of the other heat exchange paths 60B to 60J. For example, by increasing the number of heat exchange parts (flat tubes) forming the first heat exchange path 60A to the upper stage side and connecting them in series, the path effective length LA of the first heat exchange path 60A is equivalent to that of six flat tubes. For example, the length of the passage 63b may be set to be twice the effective path lengths LB to LJ of the other heat exchange paths 60B to 60J.

-C-
In addition, in the heat exchanger 11 of the present embodiment, as described above, the first heat exchange path 60A includes the first lower heat exchangers 62AL and 61AL including the lowermost flat tubes 63AU and 63AD, and the first lower heat exchanger. The upper side heat exchangers 62AL and 61AL have first upper stage heat exchangers 62AU and 61AU connected in series to the first lower stage heat exchangers 62AL and 61AL. In particular, here, the flat tubes 63 are arranged in multiple rows (two rows) in the row direction that is the ventilation direction in which air passes through the ventilation passages. Each of the heat exchange paths 60B to 60J other than the first heat exchange path 60A includes a windward side heat exchange section 62B to 62J on the windward side in the column direction and a windward side heat exchange section on the leeward side of the windward side heat exchange sections 62B to 62J. 62B-62J and the leeward side heat exchange parts 61B-61J connected in series. The first heat exchange path 60A is a windward side in the column direction and a first wind upper / lower stage side heat exchange section 62AL including the lowermost flat tube 63AU, and a first upper side of the first wind upper / lower stage side heat exchange section 62AL. An upwind-side heat exchange section 62AU, a first leeward-stage heat exchange section 61AL including the flat tubes 63AD on the leeward side of the upwind-side heat exchange sections 62AL and 62AU, and the first leeward-stage heat exchange. And a first leeward upper heat exchange portion 61AU on the upper side of the portion 61AL. Then, the first wind up-down side heat exchange section 62AL, the first upwind upside heat exchange section 62AU, the first downwind downside heat exchange section 61AL, and the first downwind upside heat exchange section 61AU are connected in series. There is.

  Therefore, here, the path effective length LA of the first heat exchange path 60A is made longer than the path effective lengths LB to LJ of the other heat exchange paths 60B to 60J that do not have a series connection of the upper side and the lower side. be able to. In particular, here, the heat exchange paths 60B to 60J other than the first heat exchange path 60A are configured such that the windward side heat exchange sections 62B to 62J and the leeward side heat exchange sections 61B to 61J are connected in series, and The first heat up / down side heat exchange section 62AL, the first upwind / upper side heat exchange section 62AU, the first downwind / lower side heat exchange section 61AL, and the first downwind / upper side heat exchange section 61AU are connected in series to the 1 heat exchange path 60A. With the connected configuration, the effective path length LA of the first heat exchange path 60A can be increased.

-D-
Further, in the heat exchanger 11 of the present embodiment, as described above, each heat exchange path 60A to 60J has the plurality of heat exchange portions 61A to 61J, 62A to 62J connected in series, and The number (4) of the heat exchanging parts 61AL, 61AU, 62AL, 61AU constituting one heat exchanging path 61A is the same as the number of heat exchanging parts 61B to 61J, 62B to 62J constituting the other heat exchanging paths 60B to 60J ( 2 for each pass). Therefore, the path effective length LA of the first heat exchange path 60A can be made longer than the path effective lengths LB to LJ of the other heat exchange paths 60B to 60J.

-E-
In addition, in the heat exchanger 11 of the present embodiment, when used as a radiator of the refrigerant, the first lower stage of the first lower stage heat exchange units 62AL, 61AL and the first upper stage heat exchange units 62AU, 61AU is used. The first leeward side heat exchange section 61AL, which is one of the side heat exchange sections, is configured to be an inlet of the first heat exchange path 60A. In particular, here, when used as a heat radiator for the refrigerant, the first wind upper / lower stage side heat exchange section 62AL, the first windward / upper stage side heat exchange section 62AU, the first leeward / lower stage side heat exchange section 61AL, and Of the first leeward upper heat exchanger 61AU, the first leeward heat exchanger 61AL is configured to be an inlet of the first heat exchange path 60A.

  As described above, when the first heat exchange path 60A is configured such that the first upper heat exchange units 62AL and 61AL and the first lower heat exchange units 62AU and 61AU are connected in series, the heating operation to the defrosting operation. When switched to, the liquid-state refrigerant easily accumulates in the first lower heat exchange units 62AU, 61AU including the lowermost flat tubes 63AU, 63AD.

  Therefore, here, as described above, when the heat exchanger 11 is used as a heat radiator for the refrigerant, the first lower heat exchange units 62AL, 61AL and the first upper heat exchanger constituting the first heat exchange path 60A are formed. Of the heat exchange units 62AU and 61AU, the first leeward lower heat exchange unit 61AL, which is one of the first lower heat exchange units including the lowermost flat tube (here, the lowermost flat tube 63AD), It is configured to be the inlet of the 1 heat exchange path 60A.

  Then, during the defrosting operation, when the refrigerant in the gas state is caused to flow into the first heat exchange path 60A, the refrigerant in the gas state is the first lower heat exchange section (here, the first leeward lower heat exchange section 61AL). Will flow into. That is, here, in the defrosting operation, the first lower-stage heat exchange section including the lowermost flat tubes (here, the first leeward lower-stage heat exchange section 61AL including the lowermost flat tubes 63AD) flows through the refrigerant. Will be located on the upstream side of. Therefore, here, of the first lower-stage heat exchange units 62AL and 61AL and the first upper-stage heat exchange units 62AU and 61AU that form the first heat exchange path 60A, the first lower-stage side including the lowermost flat tube is included. The refrigerant in the gas state is caused to flow into the heat exchange section (here, the first leeward lower side heat exchange section 61AL including the lowermost flat tube 63AD), and the lowermost first lower side heat exchange section (here, It is possible to positively heat and evaporate the liquid-state refrigerant that accumulates in the first leeward lower stage side heat exchange section 61AL) to elevate the temperature of the lowermost first heat exchange path 60A. As a result, here, the unmelted residue in the first heat exchange path 60A during the defrosting operation can be further reduced.

-F-
Further, in the heat exchanger 11 of the present embodiment, as described above, when the heat exchange paths 60B to 60J other than the first heat exchange path 60A are used as the refrigerant evaporator, the second header collecting pipe 80 is used. The liquid side inlet / outlet spaces 82B to 82J, the windward side heat exchange parts 62B to 62J, the lateral folded spaces 92B to 92J formed in the connection header 90, the leeward side heat exchange parts 62B to 62J, and the first header collecting pipe 70. The refrigerant is configured to flow in the order of the gas side inlet / outlet spaces 72B to 72J formed in. Further, when the first heat exchange path 60A is used as a refrigerant evaporator, a first liquid side inlet / outlet space 72AU formed in the first header collecting pipe 70, a first leeward upper heat exchange portion 61AU, and a connection. The first upper horizontal folding space 92AU formed in the header 90, the first windward upper heat exchange portion 62AU, the first vertical folding space 82A formed in the second header collecting pipe 80, the first wind upper heat exchanger. The portion 62AL, the first lower lateral folding space 92AL formed in the connection header 90, the first leeward lower heat exchange portion 61AL, and the first gas side inlet / outlet space 72AL formed in the first header collecting pipe 70 are sequentially cooled by the refrigerant. It is designed to flow.

  Then, as described above, since the inlets and outlets on the gas refrigerant side of the heat exchange paths 60A to 60J are all arranged on the leeward heat exchangers 61AL and 61B to 61J, the gas side inlet and outlet spaces 72AL, All of 72B to 72J can be collectively formed in the first header collecting pipe 70.

  Further, here, as described above, since the folding directions in the connection header 90 of the heat exchange paths 60A to 60J are all lateral directions, the internal space of the connection header 90 is simply divided into upper and lower stages. Can be configured.

  In addition, here, as described above, when the heat exchanger 11 is used as an evaporator for the refrigerant, the first heat exchange sections 61AU, 62AU, 62AL, 61AL that configure the first heat exchange path 60A in the lowermost stage. Of the second heat exchange section 61B, the first lower heat exchange section 62AL, 61AL located upstream of the flow of the refrigerant constitutes the second heat exchange path 60B on the upper side of the first heat exchange path 60A, It is located away from 62B. Therefore, it is possible to suppress heat loss between the first heat exchange path 60A and the second heat exchange path 60B, and thus it is difficult to prevent the temperature of the refrigerant flowing through the lowermost heat exchange path 60A from increasing. , Can contribute to the suppression of frost formation in the first heat exchange path 60A.

-G-
Further, in the heat exchanger 11 of the present embodiment, as described above, the number of the flat tubes 63 forming the first heat exchange path 60A is greater than the number of the flat tubes 63 forming the other heat exchange paths 60B to 60J. Is also less.

  Here, if the number of the flat tubes 63 forming the first heat exchange path 60A is smaller than the number of the flat tubes 63 forming the other heat exchange paths 60B to 60J, the refrigerant is branched and each heat exchange is performed. When flowing into the paths 60A to 60J, a drift is likely to occur.

  However, here, as described above, by adopting a configuration in which the path effective length LA of the first heat exchange path 60A is made longer than the path effective lengths LB to LJ of the other heat exchange paths 60B to 60J, Since the flow resistance of the refrigerant in the first heat exchange path 60A is increased, it is possible to suppress the occurrence of uneven flow when the refrigerant is branched and flowed into the heat exchange paths 60A to 60J.

  Further, here, the number of the flat tubes 63 forming each of the second heat exchange paths 60B to 60J excluding the first heat exchange path 60A corresponds to a portion where the wind speed of air obtained by the outdoor fan 15 (blower) is high. The number of the flat tubes 63 of the heat exchanging section is larger than the number of the flat tubes 63 of the heat exchanging section corresponding to the portion where the wind speed of the air obtained by the outdoor fan 15 (blower) is slow. This is because in a heat exchanger that exchanges heat between the refrigerant and air, the heat exchange efficiency is higher in the portion where the wind velocity of air is higher, and the heat exchange efficiency is lower in the portion where the wind velocity of air is slower. Specifically, the wind speed of the air is higher than that of the tenth heat exchange section 60J than the number of the flat tubes 63 (total of 12 tubes in 6 rows and 2 lines) forming the 10th heat exchange path 60J having the highest air speed. The number of the flat tubes 63 forming the slower ninth heat exchange path 60I is larger (14 tubes in 7 stages and 2 rows in total). That is, the lower heat exchange path having the slower air velocity, The number of the flat tubes 63 constituting the above is increased.

  Therefore, here, for most of the heat exchanger 11 (heat exchange paths 60B to 60J other than the first heat exchange path 60A in the lowermost stage), the heat exchange path is lower in the lower heat exchange path. By increasing the number of the flat tubes 63 forming the path, the relationship between the wind speed distribution and the heat exchange efficiency is adapted. In addition, regarding the lowermost first heat exchange path 60A including the lowermost flat tubes 63AU and 63AD, in consideration of the amount of frost formation and the unmelted residue, the path effective length LA is set to be long while other heat Unlike the exchange paths 60B to 60J, the number of flat tubes 63 is reduced.

-H-
Further, in the heat exchanger 11 of the present embodiment, as described above, the fins 64 extend along the windward side from the leeward side in the ventilation direction in which air passes through the ventilation passages, and the flat tubes 63 are inserted therein. Notch portion 64a, a plurality of fin main portions 64b sandwiched between adjacent notch portions 64a, and fins extending continuously with the plurality of fin main portions 64b on the windward side of the notch portion 64a in the ventilation direction. And the windward side 64c.

  In the heat exchanger 11 having such a fin configuration, since the amount of frost adhering to the fin windward side 64c tends to increase during the defrosting operation, unmelted residue in the lowermost first heat exchange path 60A may occur during the defrosting operation. May increase.

  However, here, as described above, since the path effective length LA of the first heat exchange path 60A is longer than the path effective lengths LB to LJ of the other heat exchange paths 60B to 60J, the fins are used. It is possible to suppress frost formation in the lowermost heat exchange path 60A including frost adhering to the windward side 64c and reduce unmelted residue during the defrosting operation.

<Modification>
-A-
In the outdoor heat exchanger 11 (heat exchanger) of the above-described embodiment, when the first heat exchange path 60A is used as an evaporator of the refrigerant, the first leeward heat exchanger 61AU and the first leeward heat exchanger. The side heat exchange section 62AU, the first wind upper / lower stage side heat exchange section 62AL, and the first leeward lower stage side heat exchange section 61AL are connected in series so that the refrigerant flows in that order (see FIGS. 4 to 9). ). However, the connection configuration of the first heat exchange units 61AU, 61AL, 62AU, 62AL is not limited to this.

  For example, as shown in FIG. 10, when the first heat exchange path 60A is used as a refrigerant evaporator, the first upwind-side heat exchange section 62AU, the first leeward-upstream side heat exchange section 61AU, The configuration may be such that the first leeward lower heat exchanger 61AL and the first leeward upper heat exchanger 62AL are connected in series so that the refrigerant flows in that order. When used as a radiator for the refrigerant, the flow of the refrigerant is reversed.

  Here, as in the above-described embodiment, the effective path length LA of the first heat exchange path 60A is longer than the effective path lengths LB to LJ of the other heat exchange paths 60B to 60J. It is possible to suppress frost formation at 60A and reduce unmelted residue during defrosting operation.

  In addition, here, when used as a radiator of the refrigerant, the first wind upper / lower stage side heat exchange portion 62AL becomes the inlet of the first heat exchange path 60A, and thus, during the defrosting operation as in the above embodiment. By positively heating and evaporating the liquid state refrigerant accumulated in the first wind upper / lower stage side heat exchange portion 62AL, the temperature of the lowermost first heat exchange path 60A can be rapidly raised. The unmelted residue in the heat exchange path 60A can be further reduced. Moreover, the first wind upper / lower stage side heat exchange portion 62AL is located on the windward side in the row direction. Here, each of the heat exchange paths 60A to 60J is located on the windward side in the column direction, and the windward side heat exchange sections 62A to 62J (for the first heat exchange path 60A, the first wind upper and lower stage heat exchange sections 62AL and 1 leeward upper heat exchanger 62AU) and leeward heat exchangers 61A to 61J located on the leeward side in the column direction (for the first heat exchange path 60A, the first leeward heat exchanger 61AL and the first leeward heat exchanger 61AL). And the leeward side heat exchange section 61AU), the amount of frost attached to the upwind side heat exchange sections 62A to 62J tends to increase during the heating operation. Therefore, during the defrosting operation, unmelted residue may increase in the lowermost first heat exchange path 60A (particularly, the first wind upper / lower stage heat exchange section 62AL and the first windward / upper side heat exchange section 61AL). . However, here, as described above, when the heat exchanger 11 is used as a radiator of the refrigerant, the first wind up-and-down stage side heat exchange section 62AL located on the windward side in the column direction is connected to the first heat exchange path. It is configured to be the entrance of 60A. Therefore, during the defrosting operation, when the refrigerant in the gas state is made to flow into the first heat exchange path 60A, the refrigerant in the gas state will flow into the first wind upper / lower stage side heat exchange section 62AL. That is, here, during the defrosting operation, the first wind upper / lower stage side heat exchange portion 62AL located on the windward side in the column direction is located on the upstream side of the flow of the refrigerant. Therefore, here, the first wind up / down side heat exchange section 62AL, the first upwind / upper side heat exchange section 62AU, the first leeward / downstream side heat exchange section 61AL and the first leeward forming the first heat exchange path 60A. The first wind up-and-down stage side located on the windward side in the column direction is caused to flow the refrigerant in the gas state into the first wind up-and-down stage side heat exchange unit 62AL located on the windward side in the column direction of the upper-stage heat exchange unit 61AU. The frost attached to the heat exchange section 62AL can be positively heated and melted. As a result, here, the unmelted residue in the first heat exchange path 60A during the defrosting operation can be further reduced.

  Further, here, unlike the above embodiment, the first liquid side inlet / outlet space 72AU is formed in the second header collecting pipe 80 to communicate with the first upwind side heat exchange portion 62AU, and the first gas side inlet / outlet is formed. The space 72AL is formed in the second header collecting pipe 80 so as to communicate with the first wind upper / lower stage side heat exchange portion 62AL. In addition, the first vertical folding space 82A is formed in the first header collecting pipe 70 in order to communicate between the first leeward lower heat exchange section 61AL and the first leeward upper heat exchange section 61AU. Then, here, since the inlets and outlets on the liquid refrigerant side of the heat exchange paths 60A to 60J are arranged in the heat exchangers 62AU and 62B to 62J on the windward side, respectively, the liquid side inlet and outlet spaces 72AU and 82B to 82J are all arranged. , The second header collecting pipe 80 can be collectively formed. Further, here, as in the above-described embodiment, since the folding directions of the heat exchange paths 60A to 60J in the connecting header 90 are all lateral directions, it is easy to simply divide the internal space of the connecting header 90 into upper and lower stages. It can be constructed according to the structure. Further, here, similarly to the above-described embodiment, when the heat exchanger 11 is used as an evaporator of the refrigerant, the first heat exchange sections 61AU, 62AU, 62AL that configure the first heat exchange path 60A in the lowermost stage. , 61AL, the second lower heat exchange section 62AL, 61AL located on the downstream side of the flow of the refrigerant constitutes the second heat exchange path 60B on the upper side of the first heat exchange path 60A. It is arranged apart from 61B and 62B. Therefore, it is possible to suppress heat loss between the first heat exchange path 60A and the second heat exchange path 60B, and thus it is difficult to prevent the temperature of the refrigerant flowing through the lowermost heat exchange path 60A from increasing. , Can contribute to the suppression of frost formation in the first heat exchange path 60A.

-B-
In the outdoor heat exchanger 11 (heat exchanger) of the above-described embodiment, when the first heat exchange path 60A is used as an evaporator of the refrigerant, the first leeward heat exchanger 61AU and the first leeward heat exchanger. The side heat exchange section 62AU, the first wind upper / lower stage side heat exchange section 62AL, and the first leeward lower stage side heat exchange section 61AL are connected in series so that the refrigerant flows in that order (see FIGS. 4 to 9). ). However, the connection configuration of the first heat exchange units 61AU, 61AL, 62AU, 62AL is not limited to this.

  For example, as shown in FIG. 11, when the first heat exchange path 60A is used as a refrigerant evaporator, a first leeward lower stage heat exchange section 61AL, a first wind upper and lower stage heat exchange section 62AL, The configuration may be such that the first upstream windward heat exchange section 62AU and the first downstream windward heat exchange portion 61AU are connected in series so that the refrigerant flows in that order. When used as a radiator for the refrigerant, the flow of the refrigerant is reversed.

  Here, as in the above-described embodiment, the effective path length LA of the first heat exchange path 60A is longer than the effective path lengths LB to LJ of the other heat exchange paths 60B to 60J. It is possible to suppress frost formation at 60A and reduce unmelted residue during defrosting operation.

  Further, here, the first liquid side inlet / outlet space 72AU and the first gas side inlet / outlet space 72AL are formed in the first header collecting pipe 70 as in the above-described embodiment, but the upper and lower positions of both inlet and outlet spaces are opposite. Become. That is, the first liquid side inlet / outlet space 72AU communicates with the first leeward lower heat exchanger 61AL, and the first gas side inlet / outlet space 72AL communicates with the first leeward upper heat exchanger 61AU. Then, here, as in the above-described embodiment, all the inlets and outlets on the gas refrigerant side of the heat exchange paths 60A to 60J are arranged on the leeward side heat exchange portions 61AL and 61B to 61J, so that the gas side inlet / outlet space 72AL. , 72B to 72J can be collectively formed in the first header collecting pipe 70. Moreover, unlike the above embodiment, the first liquid side inlet / outlet space 72AU is not arranged between the first gas side inlet / outlet space 72AL and the second gas side inlet / outlet space 72B in the vertical direction, Since it is arranged below 72AL, the structure of the first header collecting pipe 70 can be simplified and the length of the first header collecting pipe 70 can be shortened. Further, here, as in the above-described embodiment, since the folding directions of the heat exchange paths 60A to 60J in the connecting header 90 are all lateral directions, it is easy to simply divide the internal space of the connecting header 90 into upper and lower stages. It can be constructed according to the structure.

-C-
In the outdoor heat exchanger 11 (heat exchanger) of the above-described embodiment, when the first heat exchange path 60A is used as an evaporator of the refrigerant, the first leeward heat exchanger 61AU and the first leeward heat exchanger. The side heat exchange section 62AU, the first wind upper / lower stage side heat exchange section 62AL, and the first leeward lower stage side heat exchange section 61AL are connected in series so that the refrigerant flows in that order (see FIGS. 4 to 9). ). However, the connection configuration of the first heat exchange units 61AU, 61AL, 62AU, 62AL is not limited to this.

  For example, as shown in FIG. 12, when the first heat exchange path 60A is used as a refrigerant evaporator, the first wind upper / lower stage side heat exchange section 62AL, the first leeward / lower stage side heat exchange section 61AL, The configuration may be such that the first leeward upper heat exchange portion 61AU and the first leeward upper heat exchange portion 62AU are connected in series so that the refrigerant flows in this order. When used as a radiator for the refrigerant, the flow of the refrigerant is reversed.

  Here, as in the above-described embodiment, the effective path length LA of the first heat exchange path 60A is longer than the effective path lengths LB to LJ of the other heat exchange paths 60B to 60J. It is possible to suppress frost formation at 60A and reduce unmelted residue during defrosting operation.

  Further, here, when the heat exchanger 11 is used as a radiator of the refrigerant, the first upwind-side heat exchange portion 62AU located on the windward side in the row direction becomes the inlet of the first heat exchange path 60A. Is configured as follows. Therefore, during the defrosting operation, when the refrigerant in the gas state is made to flow into the first heat exchange path 60A, the refrigerant in the gas state will flow into the first windward upper heat exchanger 62AU. That is, here, during the defrosting operation, similarly to the modification A, the first wind up-and-down stage side heat exchange section 62AL located on the windward side in the column direction is located on the upstream side of the flow of the refrigerant. Therefore, here, the first wind up / down side heat exchange section 62AL, the first upwind / upper side heat exchange section 62AU, the first leeward / downstream side heat exchange section 61AL and the first leeward forming the first heat exchange path 60A. A first upwind side of the upper heat exchange portion 61AU, which is in a gas state, flows into the first upwind side heat exchange portion 62AU located on the windward side in the column direction, and is located on the windward side in the column direction. The frost attached to the heat exchange unit 62AU can be positively heated and melted. As a result, here, the unmelted residue in the first heat exchange path 60A during the defrosting operation can be further reduced.

  Further, here, the first liquid side inlet / outlet space 72AU and the first gas side inlet / outlet space 72AL are formed in the second header collecting pipe 80 similarly to the modification A (see FIG. 10). The top and bottom positions of are opposite. That is, the first liquid side inlet / outlet space 72AU communicates with the first wind upper / lower stage side heat exchange section 62AL, and the first gas side inlet / outlet space 72AL communicates with the first windward upper stage side heat exchange section 62AU. Then, here, as in the case of the modified example A, since the inlets and outlets on the liquid refrigerant side of the heat exchange paths 60A to 60J are all arranged on the heat exchangers 62AL and 62B to 62J on the windward side, the liquid side inlet and outlet spaces are provided. All of 72 AU and 82B to 82J can be collectively formed in the second header collecting pipe 80. Moreover, unlike the modification A, the first gas side inlet / outlet space 72AL is not arranged vertically between the first liquid side inlet / outlet space 72AU and the second liquid side inlet / outlet space 82B, and the first liquid side inlet / outlet Since it is arranged below the space 72AU, the structure of the second header collecting pipe 80 can be simplified, and the length of the second header collecting pipe 80 can be shortened. Further, here, as in the above-described embodiment, since the folding directions of the heat exchange paths 60A to 60J in the connecting header 90 are all lateral directions, it is easy to simply divide the internal space of the connecting header 90 into upper and lower stages. It can be constructed according to the structure.

-D-
In the outdoor heat exchanger 11 (heat exchanger) of the above-described embodiment, when the first heat exchange path 60A is used as an evaporator of the refrigerant, the first leeward heat exchanger 61AU and the first leeward heat exchanger. The side heat exchange section 62AU, the first wind upper / lower stage side heat exchange section 62AL, and the first leeward lower stage side heat exchange section 61AL are connected in series so that the refrigerant flows in that order (see FIGS. 4 to 9). ). However, the connection configuration of the first heat exchange units 61AU, 61AL, 62AU, 62AL is not limited to this.

  For example, as shown in FIG. 13, when the first heat exchange path 60A is used as a refrigerant evaporator, the first leeward upper heat exchanger 61AU, the first leeward heat exchanger 61AL, and the first leeward heat exchanger 61AL, The configuration may be such that the windward-upper-stage heat exchange portion 62AL and the first windward-upper-stage heat exchange portion 62AU are connected in series so that the refrigerant flows in this order. When used as a radiator for the refrigerant, the flow of the refrigerant is reversed. Further, in the above-described embodiment, the partition plate 93 that partitions the first communication space 92A corresponding to the first heat exchange path 60A of the connection header 90 is provided so as to partition the first communication space 92A into upper and lower parts. However, here, the vertical folding connection between the first leeward upper heat exchanger 61AU and the first leeward heat exchanger 61AL, and the first leeward heat exchanger 62AL and the first leeward. Since a vertical folded connection with the upper heat exchange section 62AU is required, a partition plate 93 (not shown) is provided so as to partition the first communication space 92A into the windward side and the leeward side. .. Further, in the above-described embodiment, the first communication space 82A corresponding to the first heat exchange path 60A of the second header collecting pipe 80 is the first vertical folding space, but here, the first communicating space 70A of the first header collecting pipe 70 is formed. Similar to the partition plate 73 that partitions the first communication space 72A into upper and lower parts, a partition plate (not shown) that partitions the first communication space 82A into upper and lower parts is provided. Further, here, since a horizontal turn-back connection is required between the first leeward heat exchanger 61AL and the first leeward heat exchanger 62AL, the first communication space of the first header collecting pipe 70 is required. A communication pipe (not shown) for communicating between 72A and the second communication space 82A of the second header collecting pipe 80 is provided.

  Here, as in the above-described embodiment, the effective path length LA of the first heat exchange path 60A is longer than the effective path lengths LB to LJ of the other heat exchange paths 60B to 60J. It is possible to suppress frost formation at 60A and reduce unmelted residue during defrosting operation.

  Further, here, when the heat exchanger 11 is used as an evaporator of the refrigerant, the air flow and the refrigerant flow in the first heat exchange path 60A are configured to have a counterflow relationship as a whole. There is. Therefore, during the heating operation, heat exchange between the air and the refrigerant flowing through the first heat exchange path 60A is promoted, and the temperature of the refrigerant flowing through the first heat exchange path 60A at the lowermost stage easily rises. The effect of suppressing frost formation in the heat exchange path 60A can be enhanced.

  In addition, here, when the heat exchanger 11 is used as a radiator of the refrigerant, the first upwind-side heat exchange portion 62AU located on the windward side in the column direction is set to the first as in the case of the modification C. It is configured to be the inlet of the heat exchange path 60A. Therefore, during the defrosting operation, when the refrigerant in the gas state is made to flow into the first heat exchange path 60A, the refrigerant in the gas state will flow into the first windward upper heat exchanger 62AU. That is, here, during the defrosting operation, the first upwind-side heat exchange portion 62AU located on the windward side in the row direction is located on the upstream side of the flow of the refrigerant, as in the modification C. Therefore, here, the first wind up / down side heat exchange section 62AL, the first upwind / upper side heat exchange section 62AU, the first leeward / downstream side heat exchange section 61AL and the first leeward forming the first heat exchange path 60A. A first upwind side of the upper heat exchange portion 61AU, which is in a gas state, flows into the first upwind side heat exchange portion 62AU located on the windward side in the column direction, and is located on the windward side in the column direction. The frost attached to the heat exchange unit 62AU can be positively heated and melted. As a result, here, the unmelted residue in the first heat exchange path 60A during the defrosting operation can be further reduced.

-E-
In the outdoor heat exchanger 11 (heat exchanger) of the above-described embodiment, when the first heat exchange path 60A is used as an evaporator of the refrigerant, the first leeward heat exchanger 61AU and the first leeward heat exchanger. The side heat exchange section 62AU, the first wind upper / lower stage side heat exchange section 62AL, and the first leeward lower stage side heat exchange section 61AL are connected in series so that the refrigerant flows in that order (see FIGS. 4 to 9). ). However, the connection configuration of the first heat exchange units 61AU, 61AL, 62AU, 62AL is not limited to this.

  For example, as shown in FIG. 14, when the first heat exchange path 60A is used as a refrigerant evaporator, the first wind up / down stage side heat exchange unit 62AL, the first windward / upper stage side heat exchange unit 62AU, The first leeward upper heat exchanger 61AU and the first leeward heat exchanger 61AL may be connected in series so that the refrigerant flows in that order. When used as a radiator for the refrigerant, the flow of the refrigerant is reversed. Further, here, similarly to the modification D, a partition plate 93 (not shown) is provided so as to partition the first communication space 92A into the windward side and the leeward side, and partitions the first communication space 82A vertically. A partition plate (not shown) is provided, and a communication pipe (not shown) for communicating between the first communication space 72A of the first header collecting pipe 70 and the second communication space 82A of the second header collecting pipe 80 is provided. Will be provided.

  Here, as in the above-described embodiment, the effective path length LA of the first heat exchange path 60A is longer than the effective path lengths LB to LJ of the other heat exchange paths 60B to 60J. It is possible to suppress frost formation at 60A and reduce unmelted residue during defrosting operation.

  In addition, here, when used as a radiator of the refrigerant, the first leeward-side heat exchange section 61AL serves as the inlet of the first heat exchange path 60A, and therefore, as in the above embodiment, during the defrosting operation, By positively heating and evaporating the liquid-state refrigerant that accumulates in the first wind upper / lower stage side heat exchange section 62AL, the temperature of the lowermost first heat exchange path 60A can be quickly raised, and the first heat It is possible to further reduce the unmelted portion in the exchange path 60A.

  Further, here, since the inlets and outlets on the gas refrigerant side of the heat exchange paths 60A to 60J are arranged in the leeward side heat exchange sections 61AL and 61B to 61J, respectively, the gas side inlet and outlet spaces 72AL and 72B to 72J are all provided. , The first header collecting pipe 70 can be collectively formed. Further, here, since the inlets and outlets on the liquid refrigerant side of the heat exchange paths 60A to 60J are arranged in the heat exchangers 62AL and 62B to 62J on the windward side, respectively, the liquid side inlet and outlet spaces 82AL and 82B to 82J are all provided. , The second header collecting pipe 80 can be collectively formed.

-F-
In the outdoor heat exchanger 11 (heat exchanger) of the above-described embodiment, when the first heat exchange path 60A is used as an evaporator of the refrigerant, the first leeward heat exchanger 61AU and the first leeward heat exchanger. The side heat exchange section 62AU, the first wind upper / lower stage side heat exchange section 62AL, and the first leeward lower stage side heat exchange section 61AL are connected in series so that the refrigerant flows in that order (see FIGS. 4 to 9). ). However, the connection configuration of the first heat exchange units 61AU, 61AL, 62AU, 62AL is not limited to this.

  For example, as shown in FIG. 15, when the first heat exchange path 60A is used as a refrigerant evaporator, the first windward upper heat exchanger 62AU, the first wind upper heat exchanger 62AL, The first leeward lower heat exchanger 61AL and the first leeward upper heat exchanger 61AU may be connected in series so that the refrigerant flows in that order. When used as a radiator for the refrigerant, the flow of the refrigerant is reversed. Further, here, similarly to the modification D, a partition plate 93 (not shown) is provided so as to partition the first communication space 92A into the windward side and the leeward side, and partitions the first communication space 82A vertically. A partition plate (not shown) is provided, and a communication pipe (not shown) for communicating between the first communication space 72A of the first header collecting pipe 70 and the second communication space 82A of the second header collecting pipe 80 is provided. Will be provided.

  Here, as in the above-described embodiment, the effective path length LA of the first heat exchange path 60A is longer than the effective path lengths LB to LJ of the other heat exchange paths 60B to 60J. It is possible to suppress frost formation at 60A and reduce unmelted residue during defrosting operation.

  Further, here, since the inlets and outlets on the gas refrigerant side of the heat exchange paths 60A to 60J are arranged in the leeward side heat exchange portions 61AU and 61B to 61J, respectively, the gas side inlet and outlet spaces 72AL and 72B to 72J are both provided. , The first header collecting pipe 70 can be collectively formed. Further, here, since the inlets and outlets on the liquid refrigerant side of the heat exchange paths 60A to 60J are all arranged in the heat exchangers 62AU and 62B to 62J on the windward side, all the liquid side inlet and outlet spaces 82AL and 82B to 82J are provided. , The second header collecting pipe 80 can be collectively formed.

-G-
In the outdoor heat exchanger 11 (heat exchanger) of the above-described embodiment, when the first heat exchange path 60A is used as an evaporator of the refrigerant, the first leeward heat exchanger 61AU and the first leeward heat exchanger. The side heat exchange section 62AU, the first wind upper / lower stage side heat exchange section 62AL, and the first leeward lower stage side heat exchange section 61AL are connected in series so that the refrigerant flows in that order (see FIGS. 4 to 9). ). However, the connection configuration of the first heat exchange units 61AU, 61AL, 62AU, 62AL is not limited to this.

  For example, as shown in FIG. 16, when the first heat exchange path 60A is used as a refrigerant evaporator, the first leeward lower heat exchanger 61AL, the first leeward heat exchanger 61AU, and the first leeward heat exchanger 61AU, The upstream windward side heat exchange section 62AU and the first upstream windward side heat exchange section 62AL may be connected in series so that the refrigerant flows in that order. When used as a radiator for the refrigerant, the flow of the refrigerant is reversed. Further, here, similarly to the modification D, a partition plate 93 (not shown) is provided so as to partition the first communication space 92A into the windward side and the leeward side, and partitions the first communication space 82A vertically. A partition plate (not shown) is provided, and a communication pipe (not shown) for communicating between the first communication space 72A of the first header collecting pipe 70 and the second communication space 82A of the second header collecting pipe 80 is provided. Will be provided.

  Here, as in the above-described embodiment, the effective path length LA of the first heat exchange path 60A is longer than the effective path lengths LB to LJ of the other heat exchange paths 60B to 60J. It is possible to suppress frost formation at 60A and reduce unmelted residue during defrosting operation.

  Further, here, when the heat exchanger 11 is used as an evaporator of the refrigerant, the air flow and the refrigerant flow in the first heat exchange path 60A are configured to have a counterflow relationship as a whole. There is. Therefore, during the heating operation, heat exchange between the air and the refrigerant flowing through the first heat exchange path 60A is promoted, and the temperature of the refrigerant flowing through the first heat exchange path 60A at the lowermost stage easily rises. The effect of suppressing frost formation in the heat exchange path 60A can be enhanced.

  In addition, here, when used as a radiator of the refrigerant, the first wind upper / lower stage side heat exchange portion 62AL becomes the inlet of the first heat exchange path 60A, and thus, during the defrosting operation as in the above embodiment. By positively heating and evaporating the liquid state refrigerant accumulated in the first wind upper / lower stage side heat exchange portion 62AL, the temperature of the lowermost first heat exchange path 60A can be rapidly raised. The unmelted residue in the heat exchange path 60A can be further reduced. Moreover, the first wind upper / lower stage side heat exchange portion 62AL is located on the windward side in the row direction. Therefore, during the defrosting operation, when the refrigerant in the gas state is made to flow into the first heat exchange path 60A, the refrigerant in the gas state will flow into the first wind upper / lower stage side heat exchange section 62AL. That is, here, during the defrosting operation, similarly to the modification A, the first wind up-and-down stage side heat exchange section 62AL located on the windward side in the column direction is located on the upstream side of the flow of the refrigerant. Therefore, here, the first wind up / down side heat exchange section 62AL, the first upwind / upper side heat exchange section 62AU, the first leeward / downstream side heat exchange section 61AL and the first leeward forming the first heat exchange path 60A. The first wind up-and-down stage side located on the windward side in the column direction is caused to flow the refrigerant in the gas state into the first wind up-and-down stage side heat exchange unit 62AL located on the windward side in the column direction of the upper-stage heat exchange unit 61AU. The frost attached to the heat exchange section 62AL can be positively heated and melted. As a result, here, the unmelted residue in the first heat exchange path 60A during the defrosting operation can be further reduced.

-H-
In the outdoor heat exchanger 11 (heat exchanger) of the above-described embodiment and its modifications, the number of the flat tubes 63 forming the first heat exchange path is two rows and two stages including the flat tubes 63AU and 63AD in the lowest stage (total). 4), and these four flat tubes 63 constitute the heat exchange parts 61AU, 61AL, 62AU, 62AL, respectively, and the four heat exchange parts are connected in series, but the present invention is not limited to this. Not something. For example, the number of the flat tubes 63 forming the first heat exchange path is two rows and four stages (total 8 tubes) including the flat tubes 63AU and 63AD at the lowest stage, and each of these eight flat tubes 63 is two. The heat exchange units 61AU, 61AL, 62AU, 62AL may be configured, and the four heat exchange units may be connected in series.

  Further, in the heat exchanger 11 of the above-described embodiment and its modified example, the number of rows of the heat exchange sections forming the heat exchange path is two, but it is not limited to this. For example, the number of rows of the heat exchange sections constituting the heat exchange path is one row, and the first heat exchange path 60A has a plurality of stages of flat tubes 63 and is folded back and forth a plurality of times to be connected in series, thereby The heat exchange paths 60B to 60J may be configured to have a longer effective path length.

  As described above, in the heat exchanger 11 of the above-described embodiment and its modifications, the number of stages of heat exchange paths (10 stages), the number of rows of heat exchange sections (2 rows), the number of flat tubes 63 (87), and Although the number and the like of the flat tubes 63 forming the heat exchange paths 60A to 60J are specified, these numbers are merely examples, and the number is not limited to these numbers.

(5) Outdoor heat exchanger of the second embodiment <Structure>
FIG. 17 is a schematic perspective view of the outdoor heat exchanger 11 as the heat exchanger according to the second embodiment. FIG. 18 is a schematic configuration diagram (viewed from the leeward side) of the outdoor heat exchanger 11 as the heat exchanger according to the second embodiment. FIG. 19 is a schematic configuration diagram (viewed from the windward side) of the outdoor heat exchanger 11 as the heat exchanger according to the second embodiment. FIG. 20 is a diagram showing a path configuration in the vicinity of the first heat exchange path 60A of the outdoor heat exchanger 11 as the heat exchanger according to the second embodiment. The arrows indicating the flow of the refrigerant in FIGS. 17 to 20 are the flow directions of the refrigerant during the heating operation (when the outdoor heat exchanger 11 functions as the evaporator of the refrigerant).

  The outdoor heat exchanger 11 is a heat exchanger that performs heat exchange between the refrigerant and the outdoor air, and mainly includes a first header collecting pipe 70, a second header collecting pipe 80, a connecting header 90, and a plurality of flat tubes. It has 63 and a plurality of fins 64. Here, the first header collecting pipe 70, the second header collecting pipe 80, the connecting header 90, the flat pipe 63, and the fin 64 are all formed of aluminum or aluminum alloy and are joined to each other by brazing or the like. ..

  The first header collecting pipe 70 is a vertically elongated hollow tubular member having closed upper and lower ends. The first header collecting pipe 70 is erected on one end side (here, the left front end side in FIG. 17 or the left end side in FIG. 18) of the outdoor heat exchanger 11.

  The second header collecting pipe 80 is a vertically elongated hollow tubular member having closed upper and lower ends. The second header collecting pipe 80 is erected on one end side (here, the left front end side in FIG. 17 or the right end side in FIG. 19) of the outdoor heat exchanger 11. Here, the second header collecting pipe 80 is arranged on the windward side of the first header collecting pipe 70 in the air ventilation direction.

  The connection header 90 is a vertically elongated hollow tubular member having closed upper and lower ends. The second header collecting pipe 80 is erected on one end side of the outdoor heat exchanger 11 (here, the right front end side in FIG. 17, the right end side in FIG. 18, or the left end side in FIG. 19).

  The flat tube 63 is a flat multi-hole tube having a flat surface portion 63a that is a heat transfer surface and faces the vertical direction, and a passage 63b that is formed of a large number of small through holes through which the refrigerant formed therein flows. The flat tubes 63 are arranged in multiple stages in the vertical direction (step direction), and are also arranged in multiple rows (here, two rows) in the air ventilation direction (row direction). One end of the flat pipe 63 arranged on the leeward side in the air ventilation direction is connected to the first header collecting pipe 70, and the other end is connected to the connection header 90. One end of the flat pipe 63 arranged on the windward side in the air ventilation direction is connected to the second header collecting pipe 80, and the other end is connected to the connection header 90. The fin 64 divides the flat tubes 63 adjacent to each other into a plurality of ventilation paths through which air flows, and a plurality of horizontally extending elongated cutouts 64 a are formed so that the plurality of flat tubes 63 can be inserted. .. Here, the direction in which the flat portion 63a of the flat tube 63 faces is the vertical direction (step direction), and the longitudinal direction of the flat tube 63 is the horizontal direction along the side surfaces (here, both left and right side surfaces in this case) and back surface of the casing 40. Therefore, the direction in which the cutout portion 64a extends means the horizontal direction (column direction) that intersects the longitudinal direction of the flat tube 63, and substantially matches the air ventilation direction (column direction) in the casing 40. ing. The notch portion 64a is elongated in the horizontal direction (row direction) so that the flat tube 63 is inserted from the leeward side to the windward side in the ventilation direction. The shape of the notch 64 a of the fin 64 substantially matches the outer shape of the cross section of the flat tube 63. The cutouts 64a of the fins 64 are formed at predetermined intervals in the vertical direction (step direction) of the fins 64. The fins 64 include a plurality of fin main portions 64b sandwiched between notch portions 64a adjacent to each other in the up-down direction (step direction), and a plurality of fins on the windward side (column direction) of the notch portions 64a. The fin main part 64b and the fin windward part 64c which extends continuously are included. Like the flat tubes 63, the fins 64 are arranged in multiple rows (here, two rows) in the direction in which air passes through the ventilation path (ventilation direction, row direction).

  In the outdoor heat exchanger 11, the flat tubes 63 are divided into a plurality of heat exchange paths 60A to 60J arranged in multiple stages (here, 10 stages) in the vertical direction (step direction). Further, the flat tubes 63 are arranged in multiple rows (here, two rows) in the ventilation direction (row direction) in which air passes through the ventilation passages. Specifically, here, from the bottom to the top, the first heat exchange path 60A, the second heat exchange path 60B ... An exchange path 60J is formed. The first heat exchange path 60A has two stages of two rows (four in total) of the flat tubes 63 including the flat tubes 63AU and 63AD in the lowermost stage. Each of the second and third heat exchange paths 60B and 60C has 12 stages and 2 rows (24 tubes in total) of flat tubes 63. The fourth heat exchange path 60D has 11 stages and 2 rows (22 tubes in total) of the flat tubes 63. The fifth and sixth heat exchange paths 60E and 60F each have flat tubes 63 in 10 rows and 2 columns (total of 20 tubes). The seventh heat exchange path 60G has nine stages and two rows (18 in total) of the flat tubes 63. The eighth heat exchange path 60H has eight stages and two rows (16 in total) of the flat tubes 63. The ninth heat exchange path 60I has seven stages and two rows (14 tubes in total) of the flat tubes 63. The tenth heat exchange path 60J has 6 stages and 2 rows (12 in total) of flat tubes 63.

  The inner space of the first header collecting pipe 70 is vertically divided by a partition plate 71, so that communication spaces 72A to 72J corresponding to the heat exchange paths 60A to 60J are formed. In the following description, the communication spaces 72A to 72J are referred to as gas side entrance / exit spaces 72A to 72J.

  The first gas-side inlet / outlet space 72A includes two flat tubes 63 that form the first heat exchange path 60A and include the flat tubes 63AD on the leeward side in the column direction and at the bottom (first leeward-side heat exchange section). 61A) communicates with one end. The second gas-side inlet / outlet space 72B communicates with one end of twelve of the flat tubes 63 forming the second heat exchange path 60B on the leeward side in the column direction (second leeward heat exchange section 61B). The third gas side inlet / outlet space 72C communicates with one end of twelve of the flat tubes 63 constituting the third heat exchange path 60C on the leeward side in the column direction (third leeward heat exchange section 61C). The fourth gas side inlet / outlet space 72D communicates with one end of eleven of the flat tubes 63 constituting the fourth heat exchange path 60D on the leeward side in the column direction (fourth leeward heat exchange section 61D). The fifth gas side inlet / outlet space 72E communicates with one end of ten leeward side (fifth leeward heat exchange section 61E) in the column direction of the flat tubes 63 forming the fifth heat exchange path 60E. The sixth gas side inlet / outlet space 72F communicates with one end of ten of the flat tubes 63 constituting the sixth heat exchange path 60F on the leeward side in the column direction (sixth leeward heat exchange section 61F). The seventh gas side inlet / outlet space 72G communicates with one end of nine leeward side (seventh leeward side heat exchange section 61G) in the column direction of the flat tubes 63 forming the seventh heat exchange path 60G. The eighth gas-side inlet / outlet space 72H communicates with one end of eight leeward sides (eighth leeward heat exchange section 61H) in the column direction of the flat tubes 63 forming the eighth heat exchange path 60H. The ninth gas side inlet / outlet space 72I communicates with one end of seven leeward sides of the flat tubes 63 forming the ninth heat exchange path 60I (the ninth leeward side heat exchange portion 61I) in the column direction. The tenth gas-side inlet / outlet space 72J communicates with one end of six leeward side (tenth leeward side heat exchanging portion 61J) in the column direction of the flat tubes 63 constituting the tenth heat exchange path 60J.

  The inner space of the second header collecting pipe 80 is vertically divided by a partition plate 81, so that communication spaces 82A to 82J corresponding to the heat exchange paths 60A to 60J are formed. In the following description, the communication spaces 82A to 82J will be referred to as liquid-side inlet / outlet spaces 82A to 82J.

  Then, the first liquid-side inlet / outlet space 82A includes two flat tubes 63 constituting the first heat exchange path 60A, which include the flat tubes 63AU on the windward side in the column direction and at the bottom (first windward side heat exchange section). 62A) communicates with one end. The second liquid-side inlet / outlet space 82B communicates with one end of twelve of the flat tubes 63 forming the second heat exchange path 60B on the windward side in the column direction (second windward heat exchange section 62B). The third liquid-side inlet / outlet space 82C communicates with one end of 12 of the flat tubes 63 forming the third heat exchange path 60C on the windward side in the column direction (third windward heat exchange section 62C). The fourth liquid-side inlet / outlet space 82D communicates with one end of eleven of the flat tubes 63 forming the fourth heat exchange path 60D on the windward side in the column direction (fourth windward heat exchange section 62D). The fifth liquid-side inlet / outlet space 82E communicates with one end of ten of the flat tubes 63 constituting the fifth heat exchange path 60E on the windward side in the column direction (fifth windward heat exchange section 62E). The sixth liquid side inlet / outlet space 82F communicates with one end of ten of the flat tubes 63 constituting the sixth heat exchange path 60F on the windward side in the column direction (sixth windward heat exchange section 62F). The seventh liquid-side inlet / outlet space 82G communicates with one end of nine of the flat tubes 63 forming the seventh heat exchange path 60G on the windward side in the column direction (seventh windward heat exchange section 62G). The eighth liquid-side inlet / outlet space 82H communicates with one end of the eight pipes (eighth windward heat exchange section 62H) on the windward side in the column direction of the flat tubes 63 forming the eighth heat exchange path 60H. The ninth liquid-side inlet / outlet space 82I communicates with one end of seven of the flat tubes 63 forming the ninth heat exchange path 60I on the windward side in the column direction (the ninth windward-side heat exchange section 62I). The tenth liquid side inlet / outlet space 82J communicates with one end of the six pipes (tenth windward heat exchanging portion 62J) on the windward side in the column direction of the flat tubes 63 constituting the tenth heat exchange path 60J.

  The connection header 90 is divided into upper and lower internal spaces by a partition plate 91 to form communication spaces 92A to 92J corresponding to the heat exchange paths 60A to 60J. In the following description, the communication spaces 92A to 92J are laterally folded spaces 92A to 92J.

  Each of the laterally folded spaces 92A to 92J communicates with the flat tubes 63 that form the corresponding heat exchange paths 60A to 60J. That is, the first horizontal folded space 92A includes two flat tubes 63 constituting the first heat exchange path 60A, which include the flat tubes 63AU at the windward side in the column direction and at the bottom (first windward side heat exchange section 62A). ) And the other end of the two (first leeward side heat exchanging portion 61A) including the flattened tubes 63AD which are on the leeward side in the column direction and which are the lowest stage of the flattened tubes 63 forming the first heat exchange path 60A. And, it communicates with. The second horizontal folding space 92B includes the second heat exchange path and the other ends of the 12 tubes (second windward heat exchange section 62B) on the windward side in the column direction of the flat tubes 63 that form the second heat exchange path 60B. Among the flat tubes 63 forming the 60B, they communicate with the other ends of the 12 leeward side of the column direction (the second leeward side heat exchange section 61B). 92 C of 3rd horizontal folding | turning spaces, the other end of 12 windward side (3rd windward side heat exchange part 62C) of the flat tubes 63 which comprise 60 C of 3rd heat exchange paths, and 3rd heat exchange path. It communicates with the other end of the 12 tubes (third leeward side heat exchange section 61C) on the leeward side in the column direction of the flat tubes 63 constituting the 60C. The fourth horizontal folding space 92D includes the other ends of eleven pipes (fourth windward heat exchange section 62D) on the windward side in the column direction of the flat tubes 63 that form the fourth heat exchange path 60D, and the fourth heat exchange path. Among the flat tubes 63 constituting the 60D, the flat tubes 63 communicate with the other ends on the leeward side in the column direction (fourth leeward heat exchange section 61D). The fifth lateral folded space 92E is connected to the other ends of the ten pipes (fifth windward heat exchange section 62E) on the windward side in the column direction of the flat tubes 63 constituting the fifth heat exchange path 60E, and the fifth heat exchange path. It communicates with the other end of the ten leeward side (fifth leeward side heat exchange section 61E) in the row direction of the flat tubes 63 constituting the 60E. The sixth horizontal folding space 92F includes the other ends of the ten pipes (sixth windward heat exchanging portion 62F) on the windward side in the column direction of the flat tubes 63 constituting the sixth heat exchanging path 60F, and the sixth heat exchanging path. It communicates with the other ends of the ten leeward sides (sixth leeward side heat exchange portions 61F) in the row direction of the flat tubes 63 constituting the 60F. The seventh horizontal folding space 92G includes the other ends of the nine tubes (seventh windward heat exchange section 62G) on the windward side in the column direction of the flat tubes 63 that form the seventh heat exchange path 60G, and the seventh heat exchange path. It communicates with the other end of the nine tubes (seventh leeward heat exchange section 61G) on the leeward side in the column direction of the flat tubes 63 that form 60G. The eighth horizontal folding space 92H includes the other ends of the eight tubes (eighth windward heat exchange section 62H) on the windward side in the column direction of the flat tubes 63 that form the eighth heat exchange path 60H, and the eighth heat exchange path. Among the flat tubes 63 forming the 60H, the flat tubes 63 communicate with the other ends of the eight leeward sides in the column direction (eighth leeward heat exchange section 61H). The ninth horizontal folding space 92I includes the other ends of the seven tubes (the ninth windward side heat exchanging portion 62I) on the windward side in the column direction of the flat tubes 63 forming the ninth heat exchanging path 60I, and the ninth heat exchanging path. It communicates with the other ends of seven (9th leeward side heat exchanging parts 61I) on the leeward side in the column direction of the flat tubes 63 constituting the 60I. The tenth horizontal folding space 92J includes the other ends of the six pipes (the tenth windward heat exchange section 62I) on the windward side in the column direction of the flat tubes 63 that form the tenth heat exchange path 60J, and the tenth heat exchange path. It communicates with the other ends of the six tubes (tenth leeward side heat exchange section 61J) on the leeward side in the column direction of the flat tubes 63 constituting 60J. Here, by providing the partition plate 91 so that the other ends of the flat tubes 63 adjacent to each other in the row direction communicate with each other, the lateral folding spaces 92A to 92J are different from each other of the flat tubes 63 adjacent to each other in the row direction. It is formed so that the ends communicate with each other. However, the present invention is not limited to this, and since the partition plate 91 is not provided in the same heat exchange section 61A to 61J, 62A to 62J, the lateral folding spaces 92A to 92J are adjacent to each other in the column direction. It may be formed between 61A to 61J and 62A to 62J.

  Further, to the first header collecting pipe 70 and the second header collecting pipe 80, the liquid side which divides the refrigerant sent from the outdoor expansion valve 12 (see FIG. 1) during the heating operation into the respective liquid side inlet / outlet spaces 82A to 82J and sends the liquid side. The flow dividing member 85 and the gas side flow dividing member 75 that divides the refrigerant sent from the compressor 8 (see FIG. 1) during the cooling operation into the gas side inlet / outlet spaces 72A to 72J and sends the refrigerant are connected to each other.

  The liquid-side flow dividing member 85 is connected to the refrigerant pipe 20 (see FIG. 1), and the liquid-side refrigerant flow distributor 86 is a liquid that extends from the liquid-side refrigerant flow distributor 86 and is connected to each of the liquid-side inlet / outlet spaces 82A to 82J. Side refrigerant distribution pipes 87A to 87F. Here, each of the liquid-side refrigerant distribution pipes 87A to 87F has a capillary tube, and has a length corresponding to the distribution ratio to the heat exchange paths 60A to 60J.

  The gas-side distribution member 75 extends from the gas-side refrigerant distribution pipe 76 connected to the refrigerant pipe 19 (see FIG. 1), and is connected to each of the gas-side inlet / outlet spaces 72A to 72J. Gas side refrigerant branch pipes 77A to 77J.

  Thereby, the heat exchange paths 60A to 60J are arranged in series with the windward side heat exchange sections 62A to 62J on the windward side in the column direction and the windward side heat exchange sections 62A to 62J on the leeward side of the windward side heat exchange sections 62A to 62J. The leeward side heat exchange parts 61A to 61J are connected. That is, the first heat exchange path 60A includes the two flat tubes 63 including the flat tubes 63AD in the lowermost stage that constitute the first leeward heat exchange section 61A that communicates with the first gas side inlet / outlet space 72A, and the first leeward. Two flat tubes 63 including a lowermost flat tube 63AU constituting a first windward heat exchange section 62A located on the windward side of the side heat exchange section 61A and communicating with the first liquid side inlet / outlet space 82A, Are connected in series through the first lateral folding space 92A. The second heat exchange path 60B is located on the windward side of the twelve flat tubes 63 forming the second leeward heat exchange section 61B communicating with the second gas side inlet / outlet space 72B, and on the windward side of the second leeward heat exchange section 61B. The 12 flat tubes 63 forming the second windward side heat exchange section 62B communicating with the second liquid side inlet / outlet space 82B are connected in series through the second horizontal folding space 92B. There is. The third heat exchange path 60C is located on the windward side of the twelve flat tubes 63 forming the third leeward heat exchange section 61C communicating with the third gas side inlet / outlet space 72C and the third leeward heat exchange section 61C. The 12 flat tubes 63 forming the third windward heat exchange section 62C communicating with the third liquid side inlet / outlet space 82C are connected in series through the third horizontal folding space 92C. There is. The fourth heat exchange path 60D is located on the windward side of the eleven flat tubes 63 that form the fourth leeward heat exchange section 61D that communicates with the fourth gas side inlet / outlet space 72D, and the fourth leeward heat exchange section 61D. In addition, the eleven flat tubes 63 forming the fourth windward side heat exchange portion 62D communicating with the fourth liquid side inlet / outlet space 82D are connected in series through the fourth horizontal folding space 92D. There is. The fifth heat exchange path 60E is located on the windward side of the ten flat tubes 63 forming the fifth leeward heat exchange section 61E communicating with the fifth gas side inlet / outlet space 72E and the fifth leeward heat exchange section 61E. The ten flat tubes 63 forming the fifth windward side heat exchange section 62E communicating with the fifth liquid side inlet / outlet space 82E are connected in series through the fifth horizontal folding space 92E. There is. The sixth heat exchange path 60F is located on the windward side of the ten flat tubes 63 forming the sixth leeward heat exchange section 61F communicating with the sixth gas side inlet / outlet space 72F and the sixth leeward heat exchange section 61F. The ten flat tubes 63 forming the sixth windward heat exchange section 62F communicating with the sixth liquid side inlet / outlet space 82F are connected in series through the sixth horizontal folding space 92F. There is. The seventh heat exchange path 60G is located on the windward side of the nine flat tubes 63 forming the seventh leeward heat exchange portion 61G communicating with the seventh gas side inlet / outlet space 72G, and the windward side of the seventh leeward heat exchange portion 61G. It has a configuration in which the nine flat tubes 63 forming the seventh windward heat exchange portion 62G communicating with the seventh liquid side inlet / outlet space 82G are connected in series through the seventh horizontal folding space 92G. There is. The eighth heat exchange path 60H is located on the windward side of the eight flat tubes 63 forming the eighth leeward heat exchange section 61H communicating with the eighth gas side inlet / outlet space 72H and the eighth leeward heat exchange section 61H. The eight flat tubes 63 forming the eighth windward heat exchange section 62H communicating with the eighth liquid-side inlet / outlet space 82H are connected in series through the eighth horizontal folding space 92H. There is. The ninth heat exchange path 60I is located on the windward side of the seven flat tubes 63 forming the ninth leeward heat exchange section 61I communicating with the ninth gas side inlet / outlet space 72I and the ninth leeward heat exchange section 61I. It has a configuration in which seven flat tubes 63 forming a ninth windward heat exchange section 62I communicating with the ninth liquid side inlet / outlet space 82I are connected in series through a ninth horizontal folding space 92I. There is. The tenth heat exchange path 60J is located on the windward side of the six flat tubes 63 forming the tenth leeward heat exchange portion 61J communicating with the tenth gas side inlet / outlet space 72J and the tenth leeward heat exchange portion 61J. The six flat tubes 63 forming the tenth windward heat exchange section 62J communicating with the tenth liquid side inlet / outlet space 82J are connected in series through the tenth horizontal folding space 92J. There is.

  Then, here, as shown in FIG. 20, the number of the through holes (here, three) that become the refrigerant passages 63bA of the four flat tubes 63 forming the first heat exchange path 60A is different from that of the other heat. The number is smaller than the number (here, seven) of through holes that serve as the refrigerant passages 63b of the flat tubes 63 that form the exchange paths 60B to 60J. In addition, here, the size (diameter or flow passage cross-sectional area) of each through-hole 63bA of the flat tubes forming the first heat exchange path 60A is the same as that of the flat tubes forming the other heat exchange paths 60B to 60D. It is the same as the size of each through hole 63b.

<Operation (refrigerant flow)>
Next, the flow of the refrigerant in the outdoor heat exchanger 11 having the above configuration will be described.

  During the cooling operation, the outdoor heat exchanger 11 functions as a radiator for the refrigerant discharged from the compressor 8 (see FIG. 1). Note that here, the refrigerant flows in the direction opposite to the arrow indicating the flow of the refrigerant in FIGS. 17 to 20.

  The refrigerant discharged from the compressor 8 (see FIG. 1) is sent to the gas side flow dividing member 75 through the refrigerant pipe 19 (see FIG. 1). The refrigerant sent to the gas side distribution member 75 is branched from the gas side refrigerant distribution mother pipe 76 to each of the gas side refrigerant distribution branch pipes 77A to 77J, and each of the gas side inlet / outlet spaces 72AL and 72B of the first header collecting pipe 70. ~ 72J.

  The refrigerant sent to the gas side inlet / outlet spaces 72A to 72J is divided into the flat tubes 63 that form the leeward side heat exchange sections 61A to 61J of the heat exchange paths 60A to 60J. The refrigerant sent to each flat tube 63 radiates heat by heat exchange with the outdoor air while flowing through the passage 63b, and passes through the laterally folded spaces 92A to 92J of the connection header 90 to the heat exchange paths 60A to 60J. It is sent to the flat tubes 63 that constitute the windward side heat exchange units 62A to 62J. The refrigerant sent to each flat tube 63 further radiates heat by heat exchange with the outdoor air while flowing through the passage 63b, and joins in the liquid side inlet / outlet spaces 82A to 82J of the second header collecting tube 80. That is, the refrigerant passes through the heat exchange paths 60A to 60J in the order of the leeward side heat exchange sections 61A to 61J and the leeward side heat exchange sections 62A to 62J. At this time, the refrigerant radiates heat from the superheated gas state to the saturated liquid state or the supercooled liquid state.

  The refrigerant sent to each of the liquid-side inlet / outlet spaces 82A to 82J is sent to the liquid-side refrigerant distribution pipes 87A to 87J of the liquid-side refrigerant distribution member 85 and merges in the liquid-side refrigerant distributor 86. The refrigerant merged in the liquid-side refrigerant distributor 86 is sent to the outdoor expansion valve 12 (see FIG. 1) through the refrigerant pipe 20 (see FIG. 1).

  During the heating operation, the outdoor heat exchanger 11 functions as an evaporator for the refrigerant whose pressure has been reduced in the outdoor expansion valve 12 (see FIG. 1). Note that here, the refrigerant flows in the direction of the arrow indicating the flow of the refrigerant in FIGS. 17 to 20.

  The refrigerant whose pressure has been reduced in the outdoor expansion valve 12 is sent to the liquid-side refrigerant distribution member 85 through the refrigerant pipe 20 (see FIG. 1). The refrigerant sent to the liquid-side refrigerant distribution member 85 is divided from the liquid-side refrigerant distributor 86 into the liquid-side refrigerant distribution pipes 87A to 87F, and the liquid-side inlets and outlets of the first and second header collecting pipes 70 and 80. It is sent to the spaces 82A to 82J.

  The refrigerant sent to the liquid-side inlet / outlet spaces 82A to 82J is diverted to the flat tubes 63 that constitute the windward heat exchange sections 62A to 62J of the heat exchange paths 60A to 60J. The refrigerant sent to each of the flat tubes 63 is heated by heat exchange with the outdoor air while flowing through the passage 63b, and passes through each of the laterally folded spaces 92A to 92J of the connection header 90 to form the heat exchange paths 60A to 60J. It is sent to the flat tubes 63 that constitute the leeward heat exchange sections 62A to 62J. The refrigerant sent to each flat pipe 63 is further heated by heat exchange with the outdoor air while flowing through the passage 63b, and joins in the gas side inlet / outlet spaces 72A to 72J of the first header collecting pipe 70. That is, the refrigerant passes through the heat exchange paths 60A to 60J in the order of the windward side heat exchange sections 62A to 62J and the leeward side heat exchange sections 61A to 61J. At this time, the refrigerant is heated from the liquid state or the gas-liquid two-phase state to the superheated gas state by evaporating.

  The refrigerant sent to each of the gas side inlet / outlet spaces 72A to 72J is sent to the gas side refrigerant distribution branch pipes 77A to 77J of the gas side refrigerant distribution member 75 and joins at the gas side refrigerant distribution mother pipe 76. The refrigerants that have merged in the gas-side refrigerant distribution mother pipe 76 are sent to the suction side of the compressor 8 (see FIG. 1) through the refrigerant pipe 19 (see FIG. 1).

  During the defrosting operation, the outdoor heat exchanger 11 functions as a radiator for the refrigerant discharged from the compressor 8 (see FIG. 1), as in the cooling operation. The flow of the refrigerant in the outdoor heat exchanger 11 during the defrosting operation is the same as that during the cooling operation, and thus the description thereof is omitted here. However, unlike the cooling operation, during the defrosting operation, the refrigerant mainly radiates heat while melting the frost adhering to the heat exchange paths 60A to 60J.

<Features>
The outdoor heat exchanger 11 (heat exchanger) of this embodiment and the air conditioning apparatus 1 including the same have the following features.

-A-
As described above, the heat exchanger 11 of the present embodiment includes a plurality of flat tubes 63 arranged vertically and having passages for the refrigerant formed therein, and a plurality of air tubes flowing between the adjacent flat tubes 63. It has a plurality of fins 64 which divide into a ventilation path. The flat tube 63 is divided into a plurality (here, 10) of heat exchange paths 60A to 60J arranged in multiple stages in the step direction. And let the flow path cross-sectional area of the passage 63b in each heat exchange path 60A-60J be path effective cross-sectional area SA-SJ, the path effective cross-sectional area SA of the 1st heat exchange path 60A is other heat exchange paths 60B-60J. Is smaller than the pass effective sectional areas SB to SJ. Specifically, each of the second to tenth heat exchange paths 60B to 60J is configured by a flat tube 63 having seven through holes that serve as refrigerant passages 63b. Therefore, the pass effective cross-sectional areas SB to SJ of the respective second to tenth heat exchange paths 60B to 60J are the flow passage cross-sectional areas of the seven through holes that become the refrigerant passages 63b, and one per through hole. When the flow passage cross-sectional area is s, the path effective cross-sectional areas SB to SJ are 7 × s. The first heat exchange path 60A is configured by a flat tube 63 (including the flat tubes 63AU and 63AD at the lowest stage) having three through holes that serve as the refrigerant passages 63bA. Therefore, the path effective cross-sectional area SA of the first heat exchange path 60A is the flow-path cross-sectional area of the three through-holes that form the refrigerant passage 63b, and the flow-path cross-sectional area per one through-hole is s. , The effective path area SA is 3 × s. As described above, the pass effective sectional area SA of the first heat exchange path 60A is smaller than the pass effective sectional areas SB to SJ of the other heat exchange paths 60B to 60J.

  On the other hand, in the conventional heat exchanger, each heat exchange path is connected in series by the same number of flat tubes having the same shape (tube length and size and number of through holes that serve as refrigerant passages). It is configured. That is, the above conventional heat exchanger is configured such that the heat exchange paths have the same effective cross-sectional area. When such a conventional heat exchanger is used in an air conditioner that switches between heating operation (when used as a refrigerant evaporator) and defrosting operation (when used as a refrigerant radiator). During the heating operation, the amount of frost on the lowermost heat exchange path tends to increase. First, the cause will be described.

  In this conventional configuration, during the heating operation, the refrigerant in the liquid state easily flows into the bottommost heat exchange path including the bottommost flat tube, and the bottommost heat exchange path is maintained without the temperature of the refrigerant rising sufficiently. As a result, the amount of frost formed on the lowermost heat exchange path tends to increase. That is, in the configuration of the conventional heat exchanger, the refrigerant in the liquid state easily flows into the lowermost heat exchange path during the heating operation, and flows out of the lowermost heat exchange path without sufficiently increasing the temperature of the refrigerant. It is presumed that this is the reason why the amount of frost in the lowermost heat exchange path tends to increase.

  Therefore, here, unlike the conventional heat exchanger, as described above, the path effective sectional area SA of the first heat exchange path 60A in the lowermost stage including the flat tubes 63AU and 63AD in the lowermost stage is changed to another heat exchanger. The paths 60B to 60J are made smaller than the path effective sectional areas SB to SJ.

  When the heat exchanger 11 having this configuration is adopted in the air conditioning apparatus 1 that switches between the heating operation and the defrosting operation, the effective path sectional area SA of the first heat exchange path 60A decreases. The flow resistance of the refrigerant in the first heat exchange path 60A can be increased. For this reason, it becomes difficult for the liquid-state refrigerant to flow into the first heat exchange path 60A during the heating operation, and the temperature of the refrigerant flowing through the lowermost heat exchange path 60A easily rises. Frost can be suppressed. As a result, it is possible to reduce the unmelted residue in the first heat exchange path 60A during the defrosting operation, as compared with the case where the conventional heat exchanger is adopted.

  Thus, here, by adopting the heat exchanger 11 having the above-described configuration in the air conditioning apparatus 1 that switches between the heating operation and the defrosting operation, frost formation in the lowermost heat exchange path 60A is suppressed. As a result, it is possible to reduce unmelted residue during the defrosting operation.

  In addition, here, the path effective cross-sectional area SA of the lowermost first heat exchange path 60A including the lowermost flat tubes 63AU and 63AD is set to be smaller than the path effective cross-sectional areas SB to SJ of the other heat exchange paths 60B to 60J. In order to obtain a reduced structure, the flat tubes 63 forming the first heat exchange path 60A are formed so that the number of through holes is smaller than that of the flat tubes 63 forming the other heat exchange paths 60B to 60J. Although a flat tube is used, it is not limited to this. For example, for all the heat exchange paths 60A to 60J, flat tubes 63 having the same shape (tube length and size and number of through holes that serve as refrigerant passages) are used, and the first and second header collecting tubes are used. The first heat exchange paths 60A are formed by forming portions in the first inlet / outlet spaces 72A, 82A of 70, 80 that block some of the through holes 63bA of the flat tubes 63 that form the first heat exchange path 60A. The number of holes 63bA may be reduced.

-B-
In the heat exchanger 11 of the present embodiment, as described above, the pass effective area SA of the first heat exchange path 60A is 0.4 times the pass effective area SB of the other heat exchange paths 60B to 60J. Therefore, the effective path area SA of the first heat exchange path 60A is sufficiently small. The flow resistance of the refrigerant in the first heat exchange path 60A can be made sufficiently large to enhance the effect of suppressing frost formation in the lowermost heat exchange path 60A.

  The pass effective sectional area SA of the first heat exchange pass 60A is not limited to 0.4 times the pass effective sectional areas SB to SJ of the other heat exchange passes 60B to 60J. However, in order to sufficiently obtain the effect of increasing the flow resistance of the refrigerant, the path effective cross-sectional area SA of the first heat exchange path 60A is set to 0.% of the path effective cross-sectional areas SB to SJ of the other heat exchange paths 60B to 60J. It is preferably 5 times or less.

-C-
Further, in the heat exchanger 11 of the present embodiment, as described above, the number of the flat tubes 63 forming the first heat exchange path 60A is greater than the number of the flat tubes 63 forming the other heat exchange paths 60B to 60J. Is also less.

  Here, if the number of the flat tubes 63 forming the first heat exchange path 60A is smaller than the number of the flat tubes 63 forming the other heat exchange paths 60B to 60J, the refrigerant is branched and each heat exchange is performed. When flowing into the paths 60A to 60J, a drift is likely to occur.

  However, here, as described above, by adopting a configuration in which the path effective sectional area SA of the first heat exchange path 60A is made smaller than the path effective sectional areas SB to SJ of the other heat exchange paths 60B to 60J. Since the flow resistance of the refrigerant in the first heat exchange path 60A is increased, it is possible to suppress the occurrence of uneven flow when the refrigerant is branched and flowed into the heat exchange paths 60A to 60J.

  Further, here, the number of the flat tubes 63 forming each of the second heat exchange paths 60B to 60J excluding the first heat exchange path 60A corresponds to a portion where the wind speed of air obtained by the outdoor fan 15 (blower) is high. The number of the flat tubes 63 of the heat exchanging section is larger than the number of the flat tubes 63 of the heat exchanging section corresponding to the portion where the wind speed of the air obtained by the outdoor fan 15 (blower) is slow. This is because in a heat exchanger that exchanges heat between the refrigerant and air, the heat exchange efficiency is higher in the portion where the wind velocity of air is higher, and the heat exchange efficiency is lower in the portion where the wind velocity of air is slower. Specifically, the wind speed of the air is higher than that of the tenth heat exchange section 60J than the number of the flat tubes 63 (total of 12 tubes in 6 rows and 2 lines) forming the 10th heat exchange path 60J having the highest air speed. The number of the flat tubes 63 forming the slower ninth heat exchange path 60I is larger (14 tubes in 7 stages and 2 rows in total). That is, the lower heat exchange path having the slower air velocity, The number of the flat tubes 63 constituting the above is increased.

  Therefore, here, for most of the heat exchanger 11 (heat exchange paths 60B to 60J other than the first heat exchange path 60A in the lowermost stage), the heat exchange path is lower in the lower heat exchange path. By increasing the number of the flat tubes 63 forming the path, the relationship between the wind speed distribution and the heat exchange efficiency is adapted. Moreover, regarding the lowermost first heat exchange path 60A including the lowermost flat tubes 63AU and 63AD, in consideration of the amount of frost and unmelted residue, the path effective sectional area SA is set to be small, and Unlike the heat exchange paths 60B to 60J, the number of flat tubes 63 is reduced.

-D-
Further, in the heat exchanger 11 of the present embodiment, as described above, the fins 64 extend along the windward side from the leeward side in the ventilation direction in which air passes through the ventilation passages, and the flat tubes 63 are inserted therein. Notch portion 64a, a plurality of fin main portions 64b sandwiched between adjacent notch portions 64a, and fins extending continuously with the plurality of fin main portions 64b on the windward side of the notch portion 64a in the ventilation direction. And the windward side 64c.

  In the heat exchanger 11 having such a fin configuration, since the amount of frost adhering to the fin windward side 64c tends to increase during the defrosting operation, unmelted residue in the lowermost first heat exchange path 60A may occur during the defrosting operation. May increase.

  However, here, as described above, since the path effective sectional area SA of the first heat exchange path 60A is made longer than the path effective sectional areas SB to SJ of the other heat exchange paths 60B to 60J. It is possible to suppress frost formation in the lowermost heat exchange path 60A including frost adhering to the fin windward side 64c and reduce unmelted residue during defrosting operation.

<Modification>
-A-
In the outdoor heat exchanger 11 (heat exchanger) of the above-described embodiment, the path effective cross-sectional area SA of the lowermost first heat exchange path 60A including the lowermost flat tubes 63AU and 63AD is set to the other heat exchange paths 60B to. In order to obtain a configuration in which the pass effective sectional areas SB to SJ of 60J are made smaller, the number of through holes 63bA of the flat tube 63 constituting the first heat exchange path 60A is set to the other heat exchange paths 60B to 60J. The number is smaller than the number of through holes 63b of the flat tube 63 (see FIGS. 17 to 20). However, the path effective sectional area SA of the lowermost first heat exchange path 60A including the lowermost flat tubes 63AU and 63AD is made smaller than the effective path sectional areas SB to SJ of the other heat exchange paths 60B to 60J. Is not limited to this.

  For example, as shown in FIG. 21, the size of the through hole 63bA of the flat tube 63 that constitutes the first heat exchange path 60A is larger than the size of the through hole 63b of the flat tube 63 that constitutes the other heat exchange paths 60B to 60J. Also, by making it smaller, the path effective sectional area SA of the first heat exchange path 60A at the lowermost stage is made smaller than the path effective sectional areas SB to SJ of the other heat exchange paths 60B to 60J. Good.

  Here, as in the above-described embodiment, since the path effective cross-sectional area SA of the first heat exchange path 60A is smaller than the path effective cross-sectional areas SB to SJ of the other heat exchange paths 60B to 60J, the heat of the bottom stage is reduced. Frost formation on the replacement path 60A can be suppressed to reduce unmelted residue during defrosting operation.

  Also in this case, in order to sufficiently increase the flow resistance of the refrigerant in the first heat exchange path 60A, the path effective sectional area SA of the first heat exchange path 60A is set to the paths of the other heat exchange paths 60B to 60J. It is preferable to make the effective area SB to SJ 0.5 times or less. If the configuration uses a flat tube having a square through hole as shown in FIG. 21, for example, the size of the square through hole 63bA of the flat tube 63 forming the first heat exchange path 60A (vertical length or The horizontal length is set to 0.7 times or less of the size (vertical length or horizontal length) of the rectangular through hole 63b forming the other heat exchange paths 60B to 60J, so that the flow passage cross-sectional area is set to 0.5 times or less. do it.

-B-
In the outdoor heat exchanger 11 (heat exchanger) of the above-described embodiment, the path effective cross-sectional area SA of the lowermost first heat exchange path 60A including the lowermost flat tubes 63AU and 63AD is set to the other heat exchange paths 60B to. In order to obtain a configuration in which the pass effective sectional areas SB to SJ of 60J are made smaller, the number of through holes 63bA of the flat tube 63 constituting the first heat exchange path 60A is set to the other heat exchange paths 60B to 60J. The number is smaller than the number of through holes 63b of the flat tube 63. In the outdoor heat exchanger 11 (heat exchanger) of Modification A, the path effective cross-sectional area SA of the lowermost first heat exchange path 60A including the lowermost flat tubes 63AU and 63AD is changed to another heat exchanger. In order to obtain a configuration in which the pass effective cross-sectional areas SB to SJ of the paths 60B to 60J are made smaller, the size of the through hole 63bA of the flat tube 63 constituting the first heat exchange path 60A is set to be different from that of the other heat exchange paths 60B to 60J. The size is smaller than the size of the through hole 63b of the flat tube 63 constituting the.

  However, the path effective sectional area SA of the lowermost first heat exchange path 60A including the lowermost flat tubes 63AU and 63AD is made smaller than the effective path sectional areas SB to SJ of the other heat exchange paths 60B to 60J. The method of obtaining is not limited to any one of the above, and both may be applied at the same time. That is, the number of the through holes 63bA of the flat tubes 63 forming the first heat exchange path 60A is made smaller than the number of the through holes 63b of the flat tubes 63 forming the other heat exchange paths 60B to 60J. The size of the through hole 63bA of the flat tube 63 forming the heat exchange path 60A may be smaller than the size of the through hole 63b of the flat tube 63 forming the other heat exchange paths 60B to 60J.

  Here, as in the above-described embodiment, since the path effective cross-sectional area SA of the first heat exchange path 60A is smaller than the path effective cross-sectional areas SB to SJ of the other heat exchange paths 60B to 60J, the heat of the bottom stage is reduced. Frost formation on the replacement path 60A can be suppressed to reduce unmelted residue during defrosting operation.

-C-
In the outdoor heat exchanger 11 (heat exchanger) of the above-described embodiment and its modifications, the number of the flat tubes 63 forming the first heat exchange path is two rows and two stages including the flat tubes 63AU and 63AD in the lowest stage (total). 4) but is not limited to this. For example, the number of the flat tubes 63 constituting the first heat exchange path is two rows and one step (total of two tubes) including only the flat tubes 63AU and 63AD in the lowest stage, and each of these two flat tubes 63 is provided. The heat exchanging portions 61A and 62A may be configured, or the two flat tubes 63AU and 63AD that form the first heat exchanging path may include three flat tubes 63AU and 63AD in three rows (three rows in total). The heat exchangers 61A and 62A may be configured by three of each of the six flat tubes 63.

  Further, in the heat exchanger 11 of the above-described embodiment and its modified example, the number of rows of the heat exchange sections forming the heat exchange path is two, but it is not limited to this. For example, assuming that the number of rows of the heat exchanging portions constituting the heat exchanging path is one, and the path effective cross-sectional area SA of the first heat exchanging path 60A depends on the size and number of the through holes 63b and 63bA. It may be configured so as to be smaller than the path effective sectional areas SB to SJ of 60J.

  As described above, in the heat exchanger 11 of the above-described embodiment and its modifications, the number of stages of heat exchange paths (10 stages), the number of rows of heat exchange sections (2 rows), the number of flat tubes 63 (87), and Although the number and the like of the flat tubes 63 forming the heat exchange paths 60A to 60J are specified, these numbers are merely examples, and the number is not limited to these numbers.

(6) Outdoor Heat Exchanger of Other Embodiments In the outdoor heat exchanger 11 (heat exchanger) of the first embodiment and its modification, defrosting is performed by suppressing frost formation in the lowermost heat exchange path 60A. In order to reduce the unmelting residue during operation, the path effective length LA of the first heat exchange path 60A in the lowermost stage including the flat tubes 63AU and 63AD in the lowermost step is changed to the path effective length LB of the other heat exchange paths 60B to 60J. It is longer than LJ. In addition, in the heat exchanger 11 of the second embodiment and its modification, in order to suppress frost formation in the heat exchange path 60A in the lowermost stage and reduce unmelted residue during the defrosting operation, the flat tube 63AU in the lowermost stage is used. , 63AD, the effective path area SA of the lowermost first heat exchange path 60A is made smaller than the effective path areas SB to SJ of the other heat exchange paths 60B to 60J.

  However, the method for suppressing the frost formation in the lowermost heat exchange path 60A and reducing the unmelted residue during the defrosting operation is not limited to one of the above, and both may be applied at the same time. .. That is, the path effective length LA of the lowermost first heat exchange path 60A including the lowermost flat tubes 63AU and 63AD is made longer than the path effective lengths LB to LJ of the other heat exchange paths 60B to 60J, and The path effective cross-sectional area SA of the lowermost first heat exchange path 60A including the lower flat tubes 63AU and 63AD may be smaller than the path effective cross-sectional areas SB to SJ of the other heat exchange paths 60B to 60J.

  Also here, similarly to the first and second embodiments, it is possible to suppress frost formation in the lowermost heat exchange path 60A and reduce unmelted residue during the defrosting operation.

  The present invention provides a plurality of flat tubes that are arranged in multiple stages in a step direction that is an up-and-down direction and have a plurality of passages for the refrigerant formed therein, and a plurality of air passages between which adjacent flat tubes flow. It is widely applicable to a heat exchanger having a plurality of fins and a flat tube divided into a plurality of heat exchange paths arranged in multiple stages in the step direction.

60A-60J Heat exchange path 61A-61J, 62A-62J Heat exchange part 61AL 1st leeward lower stage side heat exchange part 61AU 1st leeward upper stage side heat exchange part 62AL 1st wind upper and lower stage side heat exchange part 62AU 1st windward upper stage Side heat exchange section 63, 63AU, 63AD Flat tube 63b, 63bA Refrigerant passage, through hole 64 Fin 64a Cutout section 64b Fin main section 64c Fin windward

International Publication No. 2013/161799

Claims (6)

A heat exchanger (11) arranged in a refrigerant circuit (6) between a gas side flow dividing member (75) for dividing the refrigerant and a liquid side dividing member (85) for dividing the refrigerant,
A plurality of flat tubes (63) that are arranged in multiple stages in the vertical direction and that have a refrigerant passage (63b) formed therein;
A plurality of fins (64) partitioning between the adjacent flat tubes into a plurality of air passages through which air flows;
A first header collecting pipe (70) to which the gas side refrigerant branch pipes (77A to 77J) extending from the gas side branch member (75) and the plurality of flat pipes (63) are connected,
A second header collecting pipe (80), to which the plurality of liquid-side refrigerant distribution pipes (87A to 87J) extending from the liquid-side distribution member (85) and the plurality of flat pipes (63) are connected,
Equipped with
The flat tube is divided into a plurality of heat exchange paths (60A to 60J) arranged in multiple stages in the step direction,
A partition plate (81) is arranged inside the second header collecting pipe (80),
The partition plate (81) partitions the internal space of the second header collecting pipe (80) to form a plurality of spaces (82A to 82J) corresponding to the plurality of heat exchange paths (60A to 60J),
The plurality of spaces (82A to 82J) partitioned by the partition plate (81) and the plurality of flat tubes (63) forming the plurality of heat exchange paths (60A to 60J) communicate with each other. ,
In the heat exchange path (60A-60J),
The gas side refrigerant branch pipes (77A to 77J) connected to the first header collecting pipe (70), the flat pipe (63), and the second header collecting pipe (80). To the liquid side refrigerant distribution pipe (87A to 87J),
Or
The gas connected to the first header collecting pipe (70) from the liquid-side refrigerant distribution pipes (87A to 87J) connected to the second header collecting pipe (80) through the flat pipe (63). To the side refrigerant branch pipe (77A to 77J),
The refrigerant flows,
Of the heat exchange paths, the heat exchange path including the flat tubes (63AU, 63AD) at the lowermost stage is defined as the first heat exchange path (60A), and the flow passage cross-sectional area of each of the heat exchange paths is effectively cut. In terms of area, the path effective cross-sectional area of the first heat exchange path is smaller than the path effective cross-sectional area of the other heat exchange paths (60B to 60J).
Heat exchanger (11). The path effective cross-sectional area of the first heat exchange path is 0.5 times or less than the path effective cross-sectional area of the other heat exchange paths,
The heat exchanger according to claim 1. The flat tube has a plurality of through holes to be the passage,
The size of the through holes (63bA) of the flat tubes that configure the first heat exchange path is smaller than the size of the through holes (63b) of the flat tubes that configure the other heat exchange paths,
And / or
The number of the through holes (63bA) of the flat tubes forming the first heat exchange path is smaller than the number of the through holes (63b) of the flat tubes forming the other heat exchange paths,
The heat exchanger according to claim 1 or 2. The number of the flat tubes forming the first heat exchange path is smaller than the number of the flat tubes forming the other heat exchange paths,
The heat exchanger according to claim 1. The fins extend from the leeward side in the ventilation direction in which the air passes through the ventilation path along the windward side, and a plurality of notch portions (64a) into which the flat tubes are inserted and the notch portions adjacent to each other. A plurality of fin main parts (64b) sandwiched between the fins; and a fin windward part (64c) continuously extending to the plurality of fin main parts on the windward side of the cutout part in the ventilation direction. ing,
The heat exchanger according to any one of claims 1 to 4.   An air conditioner (1) comprising the heat exchanger according to any one of claims 1 to 5.

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