JP6985603B2 - Refrigerator with heat exchanger or heat exchanger - Google Patents

Description

The present disclosure relates to a heat exchanger or a refrigerating apparatus having a heat exchanger.

Conventionally, as disclosed in, for example, Patent Document 1 (International Publication WO2013 / 160952), a heat exchange section in which a plurality of flat tubes are lined up, a shunt arranged at the liquid side end, a heat exchange section, and a diversion section. A heat exchanger having a header tube arranged between the vessels is known. In the heat exchanger, a plurality of spaces are formed in the header pipe so as to line up along the direction in which the flat pipes are stacked, and the corresponding flat pipes communicate with each space. Further, each space in the header tube and the shunt are connected by a thin tube. In the heat exchanger configured in this way, a plurality of paths (refrigerant flow paths) are formed.

In the heat exchanger as described above, the flat tubes are often arranged so as to be lined up in the vertical direction in the installed state. When used as a condenser in such a case, the liquid refrigerant tends to stay in the flat pipe (pass) arranged near the bottom stage in relation to the head difference caused by the installation height of the shunt. Provided is a heat exchanger that suppresses the retention of liquid refrigerant.

The heat exchanger of the first aspect includes a heat exchange section, a first diversion section, and a plurality of second diversion sections. The heat exchange section includes a plurality of flat tubes. A plurality of flat tubes are arranged along the vertical direction in the installed state. The first diversion portion has a first pipe, a plurality of second pipes, and a main body portion. The first pipe is a pipe through which the refrigerant enters and exits. The second pipe forms a refrigerant flow path on the heat exchange portion side of the first pipe. The main body is formed with a first space inside. The first space communicates with one end of the first pipe and one end of each second pipe. The first space allows the refrigerant flowing out of one of the first pipe and the second pipe to flow into the other. The second diversion section forms a refrigerant flow path between the heat exchange section and the first diversion section. The second diversion portion is formed inside the second space. The second space communicates with one end of the corresponding flat tube. The second space communicates with the other end of the corresponding second pipe. The second space allows the refrigerant flowing out of one of the corresponding flat pipes and the second pipe to flow into the other. Three or more second spaces are lined up along the vertical direction in the installed state. The number of flat tubes communicating with the lower second space is smaller than the number of flat tubes communicating with the central second space. The central second space is the central second space in the installed state. The lower second space is a second space located below the central second space in the installed state.

In the heat exchanger of the first aspect, in the installed state, three or more second spaces are arranged along the vertical direction and are lower than the number of flat tubes communicating with the central second space (second space located in the center). The number of flat tubes communicating with the side second space (the second space located below the central second space) is smaller. This promotes the reduction of the head of the liquid refrigerant in the first space when used as a condenser. In this connection, when used as a condenser, good flow of the refrigerant is promoted in the flat multi-hole pipe (lower path) communicating with the lower second space where the liquid refrigerant tends to accumulate. .. As a result, the liquid refrigerant is suppressed from staying when used as a condenser.

The "central second space" here is arranged between the uppermost second space and the lowest second space among the plurality of second spaces arranged along the vertical direction in the installed state. It is the second space. The "central second space" includes a space located at least one-third or more from the lower end of the height dimension of the entire heat exchanger and one-third or less from the upper end in the installed state. The number of "central second spaces" is appropriately selected according to the number of second spaces.

Further, the "lower second space" here is the central second space including the second space arranged at the lowermost stage among the plurality of second spaces arranged along the vertical direction in the installed state. It is a second space arranged below the plumb bob. The number of "central second spaces" is appropriately selected according to the number of second spaces.

The second aspect heat exchanger is the first aspect heat exchanger, further comprising a third tube and at least one third diversion section. The third pipe is a refrigerant outlet pipe when the first pipe is a refrigerant inlet pipe. The third pipe is a refrigerant inlet pipe when the first pipe is a refrigerant outlet pipe. The third diversion section forms a refrigerant flow path between the second diversion section and the third pipe. The third diversion portion is formed inside the third space. The third space communicates with the other end of the corresponding flat tube. The third space communicates with the third pipe or with one end of the second flat pipe arranged in the same stage as the flat pipe. The third space is a space in which the refrigerant flowing out from the other end of the flat pipe flows into the third pipe or the second flat pipe when the first pipe is the inlet pipe of the refrigerant. The third space is a space in which the refrigerant flowing out from one end of the third pipe or the second flat pipe flows into the flat pipe when the first pipe is the outlet pipe of the refrigerant.

The heat exchanger of the third aspect is the heat exchanger of the first aspect or the second aspect, and the heat exchange unit exchanges heat between the refrigerant in the flat tube and the air flow. In the installed state, the air flow passing around the flat pipe communicating with the second space above the second space on the lower stage side than the wind speed of the air flow passing around the flat pipe communicating with the second space on the lower stage side. The wind speed is higher.

The heat exchanger of the fourth aspect is any of the heat exchangers from the first aspect to the third aspect, and the second space on the lower stage side is one-third of the total height of the heat exchange part in the installed state. It is placed at the following height positions.

The heat exchanger according to the fifth aspect is any of the heat exchangers from the first aspect to the fourth aspect, and the flat tube located at the lowermost stage in the installed state communicates with the second space on the lower stage side.

The heat exchanger according to the sixth aspect is any of the heat exchangers from the first aspect to the fifth aspect, and in the installed state, a plurality of lower second spaces are arranged along the vertical direction.

The heat exchanger according to the seventh aspect is any of the heat exchangers from the first aspect to the sixth aspect, and in the installed state, a plurality of central second spaces are arranged along the vertical direction.

The heat exchanger of the eighth viewpoint is any of the heat exchangers of the first viewpoint to the seventh viewpoint, and the first pipe has a main body portion extending downward from the first space in the installed state. One end is connected to. One end of the second pipe is connected to the main body so as to extend upward from the first space in the installed state.

The heat exchanger according to the ninth aspect is any of the heat exchangers from the first aspect to the seventh aspect, and the first tube has a main body so as to extend upward from the first space in the installed state. One end is connected to. One end of the second pipe is connected to the main body so as to extend downward from the first space in the installed state.

The refrigerating apparatus according to the tenth aspect includes a compressor and a heat exchanger according to any one of the first aspect to the ninth aspect. The compressor compresses the refrigerant.

Schematic block diagram of the air conditioning system. Perspective view of the outdoor unit. Schematic exploded view of the outdoor unit. The schematic diagram which showed the arrangement mode of the equipment arranged on the bottom frame, and the flow direction of an outdoor air flow. The schematic diagram which showed the mode of the outdoor air flow in the outdoor unit casing. Perspective view of the outdoor heat exchanger. The perspective view of the outdoor heat exchanger seen from the direction different from FIG. Schematic diagram of the outdoor heat exchanger in plan view. Schematic diagram of the heat exchange section. FIG. 8 is a partially enlarged view of an X-X line cross section in FIG. Exploded view of the first header pipe and the gas side collecting pipe. Exploded view of the second header tube. An enlarged view showing a part of the second header tube shown in FIG. An enlarged view showing a part of the second partition member to which the partition plate and the straightening vane are attached. The figure which looked at the 2nd header tube from above. The schematic diagram which enlarged the cross section of a part of the 2nd header tube. Perspective view of the folded header. Cross-sectional view of the folded header cut along the horizontal direction. An enlarged cross-sectional view of a part of the folded header cut along the vertical direction. Perspective view of the shunt. An enlarged view of the part A surrounded by the alternate long and short dash line in FIG. 20. An enlarged view schematically showing a cross section of a shunt body cut in the vertical direction. Perspective view of the shunt body and the liquid side inlet / outlet pipe. Perspective view of the shunt body. A view of the shunt body from the top. The figure which looked at the shunt body from the bottom side. An enlarged view showing the circumference of the shunt body as seen from the horizontal direction. An enlarged view showing the state of FIG. 27 as viewed from different directions. The schematic diagram which showed an example of the jig used when moving a shunt main body into a furnace. The schematic diagram which showed the positional relationship of the 1st header pipe, the gas side collecting pipe, the 2nd header pipe and a shunt in a plan view. Schematic diagram schematically showing each path of the outdoor heat exchanger seen from the windward side. Schematic diagram schematically showing each path of the outdoor heat exchanger seen from the leeward side.

Hereinafter, the outdoor heat exchanger 15 (heat exchanger) and the air conditioning system 1 (refrigerator) according to the embodiment of the present disclosure will be described. The following embodiments are specific examples and do not limit the technical scope, and can be appropriately changed within a range that does not deviate from the purpose. Also, in the following explanation, "top", "bottom", "left", "right", "front", "rear", "front", "back", "vertical direction", "horizontal direction", and "vertical direction". Unless otherwise specified, the "horizontal direction" means the direction shown in each figure, and indicates the direction in the installed state (note that the left-right and / or front-back in the following examples are appropriately reversed. May be).

The outdoor heat exchanger 15 according to the embodiment of the present disclosure is applied to the outdoor unit 10 which is the heat source unit of the air conditioning system 1.

(1) Air conditioning system 1
FIG. 1 is a schematic configuration diagram of an air conditioning system 1. The air conditioning system 1 is a system that performs air conditioning such as cooling or heating of a target space (air-conditioned space such as a living space or a storage room) by a steam compression type refrigeration cycle. The air conditioning system 1 mainly has an outdoor unit 10, a plurality of (here, two) indoor units 20, a liquid side connecting pipe LP, and a gas side connecting pipe GP.

In the air conditioning system 1, the outdoor unit 10 and each indoor unit 20 are connected to each other via the liquid side connecting pipe LP and the gas side connecting pipe GP to form a refrigerant circuit RC. In the air conditioning system 1, a refrigerating cycle is performed in which the refrigerant is compressed, cooled or condensed, depressurized, heated or evaporated, and then compressed again in the refrigerant circuit RC.

(1-1) Outdoor unit 10
The outdoor unit 10 is installed in the outdoor space. The outdoor space is a space outside the target space where air conditioning is performed, for example, an outdoor space such as the rooftop of a building, an underground space, or the like. The outdoor unit 10 is connected to each indoor unit 20 via a liquid side connecting pipe LP and a gas side connecting pipe GP, and constitutes a part of the refrigerant circuit RC (outdoor circuit RC1). The outdoor unit 10 mainly comprises a plurality of refrigerant pipes (first pipe P1-9th pipe P9), an accumulator 11, a compressor 12, an oil separator 13, and a four-way switching valve 14 as equipment constituting the outdoor circuit RC1. , An outdoor heat exchanger 15, an outdoor expansion valve 16, and the like. These devices (11-16) are connected by a refrigerant pipe.

The first pipe P1 connects the gas side connecting pipe GP and the first port of the four-way switching valve 14. The second pipe P2 connects the inlet port of the accumulator 11 and the second port of the four-way switching valve 14. The third pipe P3 connects the outlet port of the accumulator 11 and the suction port of the compressor 12. The fourth pipe P4 connects the discharge port of the compressor 12 and the inlet of the oil separator 13. The fifth pipe P5 connects the outlet of the oil separator 13 and the third port of the four-way switching valve 14. The sixth pipe P6 connects the oil return port of the oil separator 13 and the portion between both ends of the third pipe P3. The seventh pipe P7 connects the fourth port of the four-way switching valve 14 to the gas side inlet / outlet of the outdoor heat exchanger 15. The eighth pipe P8 connects the liquid side inlet / outlet of the outdoor heat exchanger 15 and one end of the outdoor expansion valve 16. The ninth pipe P9 connects the other end of the outdoor expansion valve 16 to the liquid side connecting pipe LP. It should be noted that these refrigerant pipes (P1-P9) may actually be configured by a single pipe, or may be configured by connecting a plurality of pipes via a joint or the like.

The accumulator 11 is a container that stores the refrigerant and separates gas and liquid in order to prevent the liquid refrigerant from being excessively sucked into the compressor 12.

The compressor 12 is a device that compresses the low-pressure refrigerant in the refrigeration cycle until it reaches a high pressure. In the present embodiment, the compressor 12 has a closed structure in which a positive displacement compression element such as a rotary type or a scroll type is rotationally driven by a compressor motor (not shown). The operating frequency of the compressor motor can be controlled by an inverter, whereby the capacity of the compressor 12 can be controlled. The start / stop and operating capacity of the compressor 12 are controlled by the outdoor unit control unit 19.

The oil separator 13 is a container that separates the refrigerating machine oil that is compatible with the refrigerant discharged from the compressor 12 and returns it to the compressor 12.

The four-way switching valve 14 is a flow path switching valve for switching the flow of the refrigerant in the refrigerant circuit RC.

The outdoor heat exchanger 15 is a heat exchanger that functions as a refrigerant condenser (or radiator) or an evaporator. Details of the outdoor heat exchanger 15 will be described later.

The outdoor expansion valve 16 is an electric expansion valve capable of controlling the opening degree, and reduces the pressure of the inflowing refrigerant or adjusts the flow rate according to the opening degree.

Further, the outdoor unit 10 has an outdoor fan 18 that generates an outdoor air flow AF (see FIGS. 4 and 5). The outdoor air flow AF (corresponding to the “air flow” described in the claims) is a flow of air that flows from the outside of the outdoor unit 10 into the outdoor unit 10 and passes through the outdoor heat exchanger 15. The outdoor air flow AF is a cooling source or a heating source for the refrigerant flowing through the outdoor heat exchanger 15, and exchanges heat with the refrigerant in the outdoor heat exchanger 15 when passing through the outdoor heat exchanger 15. The outdoor fan 18 includes an outdoor fan motor (not shown) and is driven in conjunction with the outdoor fan motor. The start and stop of the outdoor fan 18 is appropriately controlled by the outdoor unit control unit 19.

Further, the outdoor unit 10 is provided with a plurality of outdoor sensors (not shown) for detecting the state (mainly pressure or temperature) of the refrigerant in the refrigerant circuit RC. The outdoor sensor is a pressure sensor or a temperature sensor such as a thermistor or a thermoelectric pair. The outdoor sensor includes, for example, a suction pressure sensor that detects the suction pressure that is the pressure of the refrigerant on the suction side of the compressor 12, and a discharge pressure sensor that detects the discharge pressure that is the pressure of the refrigerant on the discharge side of the compressor 12. And a temperature sensor for detecting the temperature of the refrigerant in the outdoor heat exchanger 15.

Further, the outdoor unit 10 has an outdoor unit control unit 19 that controls the operation and state of each device included in the outdoor unit 10. The outdoor unit control unit 19 includes a microcomputer having a CPU, a memory, and the like, and various electric components. The outdoor unit control unit 19 is electrically connected to each device (12, 14, 16, 18, etc.) included in the outdoor unit 10 and an outdoor sensor, and inputs and outputs signals to and from each other. Further, the outdoor unit control unit 19 transmits and receives control signals and the like to and from the indoor unit control unit 25 and the remote controller (not shown) of each indoor unit 20. The outdoor unit control unit 19 is housed in an electrical component box 39 (see FIGS. 3 and 4) described later.

Details of the outdoor unit 10 will be described later.

(1-2) Indoor unit 20
The indoor unit 20 is installed in a room (living room, attic space, etc.) and constitutes a part of the refrigerant circuit RC (indoor side circuit RC2). The indoor unit 20 mainly includes an indoor expansion valve 21, an indoor heat exchanger 22, and the like as equipment constituting the indoor circuit RC2.

The indoor expansion valve 21 is an electric expansion valve capable of controlling the opening degree, and reduces the pressure of the inflowing refrigerant or adjusts the flow rate according to the opening degree.

The indoor heat exchanger 22 is a heat exchanger that functions as a refrigerant evaporator or condenser (or radiator).

Further, the indoor unit 20 has an indoor fan 23 for sucking air in the target space, passing it through the indoor heat exchanger 22 to exchange heat with the refrigerant, and then sending it back to the target space. The indoor fan 23 includes an indoor fan motor which is a drive source. The indoor fan 23 generates an indoor air flow when driven. The indoor air flow is a flow of air that flows from the target space into the indoor unit 20, passes through the indoor heat exchanger 22, and is blown out to the target space. The indoor air flow is a heating source or a cooling source of the refrigerant flowing through the indoor heat exchanger 22, and when passing through the indoor heat exchanger 22, heat exchanges with the refrigerant in the indoor heat exchanger 22.

Further, the indoor unit 20 has an indoor unit control unit 25 that controls the operation / state of the equipment (21, 23, etc.) included in the indoor unit 20. The indoor unit control unit 25 includes a microprocessor including a CPU, a memory, and the like, and various electric components.

(1-3) Liquid side connecting pipe LP, gas side connecting pipe GP
The liquid side connecting pipe LP and the gas side connecting pipe GP are refrigerant connecting pipes connecting the outdoor unit 10 and each indoor unit 20, and are constructed on site. The pipe length and diameter of the liquid side connecting pipe LP and the gas side connecting pipe GP are appropriately selected according to the design specifications and the installation environment. The liquid side connecting pipe LP and the gas side connecting pipe GP may actually be composed of a single pipe or may be configured by connecting a plurality of pipes via a joint or the like. ..

(2) Flow of Refrigerant in Refrigerant Circuit RC The flow of refrigerant in the refrigerant circuit RC will be described below. In the air conditioning system 1, a forward cycle operation and a reverse cycle operation are mainly performed. The low pressure in the refrigeration cycle here is the pressure of the refrigerant sucked into the compressor 12 (suction pressure), and the high pressure in the refrigeration cycle is the pressure of the refrigerant discharged from the compressor 12 (discharge pressure).

(2-1) Refrigerant flow during normal cycle operation During normal cycle operation (operation such as cooling operation and cooling cycle defrosting operation), the four-way switching valve 14 is in the normal cycle state (of the four-way switching valve 14 in FIG. 1). It is controlled to the state shown by the solid line). When the normal cycle operation is started, the refrigerant is sucked into the compressor 12 and compressed in the outdoor circuit RC1 and then discharged. In the compressor 12, capacity control is performed according to the heat load required by the indoor unit 20 during operation. Specifically, the target value of the suction pressure is set according to the heat load required by the indoor unit 20, and the operating frequency of the compressor 12 is controlled so that the suction pressure becomes the target value. The gas refrigerant discharged from the compressor 12 flows into the outdoor heat exchanger 15.

The gas refrigerant flowing into the outdoor heat exchanger 15 exchanges heat with the outdoor air flow AF sent by the outdoor fan 18 in the outdoor heat exchanger 15, dissipates heat and condenses. The refrigerant flowing out of the outdoor heat exchanger 15 flows into the indoor circuit RC2 of the indoor unit 20 in operation via the liquid side connecting pipe LP.

The refrigerant that has flowed into the indoor circuit RC2 of the indoor unit 20 during operation flows into the indoor expansion valve 21, is depressurized to a low pressure in the refrigeration cycle according to the opening degree of the indoor expansion valve 21, and then exchanges heat in the room. It flows into the vessel 22. The refrigerant flowing into the indoor heat exchanger 22 exchanges heat with the indoor air flow sent by the indoor fan 23 and evaporates to become a gas refrigerant, which flows out from the indoor heat exchanger 22. The gas refrigerant flowing out of the indoor heat exchanger 22 flows out from the indoor circuit RC2.

The refrigerant flowing out from the indoor circuit RC2 flows into the outdoor circuit RC1 via the gas side connecting pipe GP. The refrigerant that has flowed into the outdoor circuit RC1 flows into the accumulator 11. The refrigerant flowing into the accumulator 11 is temporarily stored and then sucked into the compressor 12 again.

(2-2) Refrigerant flow during reverse cycle operation During reverse cycle operation (heating operation, etc.), the four-way switching valve 14 is controlled to the reverse cycle state (the state shown by the broken line of the four-way switching valve 14 in FIG. 1). Will be done. When the reverse cycle operation is started, the refrigerant is sucked into the compressor 12 and compressed in the outdoor circuit RC1 and then discharged. In the compressor 12, capacity control is performed according to the heat load required by the indoor unit 20 during operation. The gas refrigerant discharged from the compressor 12 flows out from the outdoor circuit RC1 and flows into the indoor circuit RC2 of the operating indoor unit 20 via the gas side connecting pipe GP.

The refrigerant that has flowed into the indoor circuit RC2 flows into the indoor heat exchanger 22 and exchanges heat with the indoor air flow sent by the indoor fan 23 to condense. The refrigerant flowing out of the indoor heat exchanger 22 flows into the indoor expansion valve 21, is depressurized or the flow rate is adjusted according to the opening degree of the indoor expansion valve 21, and then flows out from the indoor circuit RC2.

The refrigerant flowing out from the indoor circuit RC2 flows into the outdoor circuit RC1 via the liquid side connecting pipe LP. The refrigerant that has flowed into the outdoor circuit RC1 flows into the outdoor expansion valve 16, is depressurized to a low pressure in the refrigeration cycle according to the opening degree of the outdoor expansion valve 16, and then enters the liquid side inlet / outlet of the outdoor heat exchanger 15. Inflow.

The refrigerant flowing into the outdoor heat exchanger 15 evaporates by exchanging heat with the outdoor air flow AF sent by the outdoor fan 18 in the outdoor heat exchanger 15. The refrigerant flowing out from the gas side inlet / outlet of the outdoor heat exchanger 15 flows into the accumulator 11. The refrigerant flowing into the accumulator 11 is temporarily stored and then sucked into the compressor 12 again.

(3) Details of the outdoor unit 10 FIG. 2 is a perspective view of the outdoor unit 10. FIG. 3 is a schematic exploded view of the outdoor unit 10.

(3-1) Outdoor unit casing 30
The outdoor unit 10 constitutes an outer shell and has an outdoor unit casing 30 for accommodating each device (11-16, etc.). The outdoor unit casing 30 is formed into a substantially rectangular parallelepiped shape by assembling a plurality of sheet metal members. Most of the left side surface, the right side surface, and the back surface of the outdoor unit casing 30 are openings, and the openings function as intake ports 301 for sucking the outdoor air flow AF.

The outdoor unit casing 30 mainly has a pair of installation legs 31, a bottom frame 33, a plurality of (here, four) columns 35, a front panel 37, and a fan module 38.

The installation leg 31 is a sheet metal member that extends in the left-right direction and supports the bottom frame 33 from below. In the outdoor unit casing 30, the installation legs 31 are arranged near the front end and the vicinity of the rear end.

The bottom frame 33 is a sheet metal member constituting the bottom surface portion of the outdoor unit casing 30. The bottom frame 33 is arranged on a pair of installation legs 31. The bottom frame 33 has a substantially rectangular shape in a plan view.

The columns 35 extend vertically from the corners of the bottom frame 33. FIG. 2-3 shows how the columns 35 extend in the vertical direction from each of the four corners of the bottom frame 33.

The front panel 37 is a sheet metal member constituting the front portion of the outdoor unit casing 30.

The fan module 38 is attached near the upper end of each column 35. The fan module 38 constitutes a portion above the columns 35 on the front surface, the back surface, the left side surface, and the right side surface of the outdoor unit casing 30, and a top surface of the outdoor unit casing 30. The fan module 38 includes an outdoor fan 18 and a bell mouth 381. More specifically, the fan module 38 is an aggregate in which an outdoor fan 18 and a bell mouth 381 are housed in a substantially rectangular parallelepiped box body having an open upper surface and a lower surface. In the fan module 38, the outdoor fan 18 is arranged in such a posture that the rotation axis extends in the vertical direction. The upper surface portion of the fan module 38 is open and functions as an outlet 302 for blowing out the outdoor air flow AF from the outdoor unit casing 30. The outlet 302 is provided with a grid-like grill 382.

Although FIG. 2-3 shows an example in which the outdoor unit 10 has one fan module 38, the outdoor unit 10 may have a plurality of fan modules 38. For example, two fan modules 38 may be arranged side by side. In such a case, the outdoor unit 10 may have an outdoor unit casing 30 having a larger dimension than the outdoor unit 10 having one fan module 38, and may be configured to have one front panel 37 on each side. Further, in such a case, the size of the outdoor heat exchanger 15 may be increased according to the size of the outdoor unit casing 30.

(3-2) Equipment Arranged on the Bottom Frame 33 FIG. 4 is a diagram schematically showing an arrangement mode of the equipment arranged on the bottom frame 33 and the flow direction of the outdoor air flow AF. As shown in FIG. 4, various devices including an accumulator 11, a compressor 12, an oil separator 13, and an outdoor heat exchanger 15 are arranged at predetermined positions on the bottom frame 33. Further, an electrical component box 39 for accommodating the outdoor unit control unit 19 is arranged on the bottom frame 33.

The outdoor heat exchanger 15 has a heat exchange unit 40 arranged along the left side surface, the right side surface, and the back surface of the outdoor unit casing 30 (see FIG. 4). The heat exchange unit 40 has substantially the same height dimension as the intake port 301. Most of the back surface, left side surface, and right side surface of the outdoor unit casing 30 are intake ports 301, and the heat exchange portion 40 of the outdoor heat exchanger 15 is exposed from the intake port 301. In other words, it can be said that the back surface, the left side surface and the right side surface of the outdoor unit casing 30 are substantially formed by the heat exchange portion 40 of the outdoor heat exchanger 15. The outdoor heat exchanger 15 has three heat exchange units 40, and in relation to this, has left and right curved portions in a plan view (see B1, B2, and B3 shown in FIG. 8). It has a substantially U-shape that opens in the front direction.

(3-3) Flow of outdoor air flow AF in the outdoor unit casing 30 FIG. 5 is a diagram schematically showing a mode in which the outdoor air flow AF flows in the outdoor unit casing 30. As shown in FIG. 4-5, the outdoor airflow AF flows into the outdoor unit casing 30 from the intake ports 301 formed on the left side surface, the right side surface, and the back surface of the outdoor unit casing 30, and enters the outdoor unit casing 30. After passing through (heat exchange unit 40), it mainly flows from the lower side to the upper side and flows out from the air outlet 302. That is, the outdoor air flow AF flows horizontally into the outdoor unit casing 30 through the intake port 301, passes through the outdoor heat exchanger 15, and then turns upward and toward the outlet 302. It flows from the bottom to the top. Regarding the outdoor airflow AF flowing into the outdoor unit casing 30, the wind speed is higher in the space close to the outdoor fan 18 than in the lower space far from the outdoor fan 18. In this regard, for the outdoor airflow AF passing through the heat exchange section 40 of the outdoor heat exchanger 15, the portion above the air passing through the lower portion (particularly the path below the center) (particularly above the center). The wind speed is higher in the air passing through the path).

(4) Detailed Configuration of Outdoor Heat Exchanger 15 FIG. 6 is a perspective view of the outdoor heat exchanger 15. FIG. 7 is a perspective view of the outdoor heat exchanger 15 as viewed from a direction different from that of FIG. FIG. 8 is a schematic view of the outdoor heat exchanger 15 in a plan view.

The outdoor heat exchanger 15 mainly has a heat exchange unit 40, a first header pipe 50, a gas side collecting pipe 60, a second header pipe 70, a folded header 80, and a flow divider 90. There is. In the present embodiment, the heat exchange section 40, the first header pipe 50, the gas side collecting pipe 60, the second header pipe 70, the folded header 80, and the diversion device 90 are all made of aluminum or an aluminum alloy. In the outdoor heat exchanger 15, the heat exchange section 40, the first header pipe 50, the gas side collecting pipe 60, the second header pipe 70, the folded header 80, and the diversion device 90 in a temporarily assembled state are brazed in the furnace. It is assembled by brazing and joining with materials.

(4-1) Heat exchange unit 40
FIG. 9 is a schematic view of the heat exchange unit 40. FIG. 10 is a partially enlarged view of the cross section taken along line XX in FIG.

The heat exchange unit 40 is a portion where the outdoor air flow AF and the refrigerant in the outdoor heat exchanger 15 (heat transfer tube 41 described later) exchange heat. Specifically, the heat exchange unit 40 is a portion that extends in a direction intersecting the traveling direction of the outdoor air flow AF in the central portion of the outdoor heat exchanger 15, and occupies most of the outdoor heat exchanger 15. The heat exchange unit 40 mainly has three heat exchange surfaces, and has a substantially U-shaped or substantially C-shaped shape in a plan view (see FIG. 8).

In the present embodiment, the outdoor heat exchanger 15 has a plurality of (here, two) heat exchange units 40. Specifically, the outdoor heat exchanger 15 has a windward side heat exchange unit 40a and a leeward side heat exchange unit 40b as heat exchange units 40. The leeward side heat exchange unit 40a and the leeward side heat exchange unit 40b are arranged adjacent to each other along the flow direction of the outdoor air flow AF. The windward heat exchange unit 40a is a heat exchange unit 40 located on the windward side (here, the outside). The leeward heat exchange unit 40b is a heat exchange unit 40 located on the leeward side (here, inside).

Each heat exchange unit 40 mainly includes a plurality of heat transfer tubes 41 (corresponding to the "flat tube" described in the claims) through which the refrigerant flows, and a plurality of heat transfer fins 42.

The heat transfer tube 41 is a flat multi-hole tube having a plurality of refrigerant flow paths 411 formed therein. The heat transfer tube 41 is made of aluminum or an aluminum alloy. In the present embodiment, 97 heat transfer tubes 41 are arranged along the vertical direction (vertical direction) in the heat exchange unit 40 in the installed state. The heat transfer tube 41 extends along the horizontal direction and extends along the shape of the heat exchange portion 40 in a plan view. For convenience of explanation, the heat transfer tube 41 included in the leeward heat exchange section 40a is referred to as a leeward heat transfer tube 41a, and the heat transfer tube 41 included in the leeward side heat exchange section 40b is referred to as a leeward heat transfer tube 41b. One end of the windward heat transfer tube 41a is connected to the second header tube 70, and the other end is connected to the folded header 80. One end of the leeward heat transfer tube 41b is connected to the first header tube 50, and the other end is connected to the folded header 80.

The heat transfer fin 42 is a flat plate-shaped member that increases the heat transfer area between the heat transfer tube 41 and the outdoor air flow. The heat transfer fin 42 is made of aluminum or an aluminum alloy. The heat transfer fin 42 extends in the vertical direction so as to intersect the heat transfer tube 41 in the heat exchange unit 40. A plurality of notches are formed side by side in the heat transfer fin 42 in the vertical direction, and the heat transfer tube 41 is inserted into the notches.

In FIGS. 6 and 8, the alternate long and short dash arrow indicates the flow direction of the refrigerant flowing through the heat exchange section. The two-dot arrow points in both directions because the flow of refrigerant is opposite in the heating operation and the cooling operation. In the normal cycle operation, the refrigerant flows from the second header pipe 70 into the windward heat exchange section 40a (windward heat transfer tube 41a), then folds back at the folded header 80, and flows from the folded header 80 to the leeward heat exchange section. It flows into 40b (leeward heat transfer tube 41b) and flows to reach the first header tube 50. In the reverse cycle operation, the refrigerant flows from the first header pipe 50 into the leeward heat exchange section 40b (leeward heat transfer tube 41b), then folds back at the folded header 80, and flows from the folded header 80 to the leeward heat exchange section. It flows into 40a (windward heat transfer tube 41a) and flows to reach the second header tube 70.

(4-2) First header pipe 50, gas side collecting pipe 60
FIG. 11 is an exploded view of the first header pipe 50 and the gas side collecting pipe 60. The first header tube 50 is an elongated hollow tubular component having an upper end and a lower end closed and extending in the vertical direction. The first header pipe 50 is arranged on one end side of the leeward side heat exchange portion 40b. The first header pipe 50 has a leeward heat transfer tube side member 51, a first header partition member 52, a collecting pipe side member 53, a plurality of first partition plates 54, and a second partition plate 55.

The leeward heat transfer tube side member 51, the first header partition member 52, and the collecting pipe side member 53 are in a state where the first header partition member 52 is sandwiched between the leeward heat transfer tube side member 51 and the collecting pipe side member 53, respectively. They are combined and integrated so that their longitudinal directions match. In the first header tube 50, the upper end and the lower end are closed by two first partition plates 54. Further, in the first header tube 50, the second partition plate 55 is arranged near the lower end, and the inside of the first header tube 50 is divided into a first header main space S1 and a first header subspace S2. (See FIG. 32). As shown in FIG. 32, in the present embodiment, the first header main space S1 communicates with one end of 96 leeward heat transfer tubes 41b, and the first header subspace S2 is one leeward side located at the lowermost position. It communicates with one end of the heat transfer tube 41b.

The leeward heat transfer tube side member 51, the first header partition member 52, the collecting pipe side member 53, the first partition plate 54 and the second partition plate 55 are joined to each other by being brazed with a brazing material in the furnace and integrated. Will be transformed.

The leeward heat transfer tube side member 51 is a member having an arc-shaped cross section cut in a plane perpendicular to the vertical direction. The leeward heat transfer tube side member 51 is formed with a leeward heat transfer tube connection opening 511 into which the end of the heat transfer tube 41 (leeward side heat transfer tube 41b) is inserted. The number of leeward heat transfer tube connection openings 511 is the same as the number of stages of the heat transfer tube 41.

The first header partition member 52 is formed with a plurality of openings for allowing the refrigerant to flow from the leeward heat transfer tube side member 51 toward the collecting pipe side member 53 (not shown).

The collecting pipe side member 53 has an arcuate cross section cut by a plane perpendicular to the vertical direction. The collecting pipe side member 53 is formed with a plurality of openings 531 into which one end of the connecting pipe 61 is inserted. The connecting pipe 61 is a pipe that connects the first header pipe 50 and the gas side collecting pipe 60. The number of openings 531 is the same as the number of a plurality of connecting pipes 61 arranged side by side in the vertical direction. The opening 531 communicates with the first header main space S1. Further, the collecting pipe side member 53 is formed with a second thin tube connection opening 532 for connecting the second thin tube 94 (described later) of the shunt 90. The second thin tube connection opening 532 communicates with the first header subspace S2.

The gas side collecting pipe 60 (corresponding to the "third pipe" described in the claims) is a cylindrical straight pipe having a bottom. The gas side collecting pipe 60 forms a gas side inlet / outlet in the outdoor heat exchanger 15. Specifically, the gas-side collecting pipe 60 is a refrigerant inlet pipe during normal cycle operation (when the inlet / outlet pipe 91 of the shunt 90 described later is a refrigerant outlet pipe). Further, the gas side collecting pipe 60 is a refrigerant outlet pipe during reverse cycle operation (when the inlet / outlet pipe 91 described later is a refrigerant inlet pipe). The gas side collecting pipe 60 is arranged adjacent to the first header pipe 50. The first header pipe 50 and the gas side collecting pipe 60 are bound by a binding band 62. The gas side collecting pipe 60 is located between the first header pipe 50 and the seventh pipe P7 in the refrigerant circuit RC. One end of the seventh pipe P7 is connected to the gas side collecting pipe 60. The gas side collecting pipe 60 has a plurality of openings connected to the other end of the connecting pipe 61 (extending to the first header pipe 50) formed on the side surface (not shown).

The outdoor heat exchanger 15 communicates from the heat transfer tube 41 (leeward side heat transfer tube 41b) to the seventh pipe P7 through the first header pipe 50, the plurality of connection pipes 61, and the gas side collecting pipe 60.

(4-3) Second header tube 70
FIG. 12 is an exploded view of the second header tube 70. FIG. 13 is an enlarged view showing a part of the second header tube 70 shown in FIG. FIG. 14 shows an enlarged part of the second header partition member 72 to which the partition plate 74 and the straightening vane 75 are attached. FIG. 15 is a view of the second header tube 70 as viewed from above. FIG. 16 is an enlarged schematic view of a part of the second header tube 70.

The second header tube 70 is an elongated hollow tubular component having an upper end and a lower end closed and extending in the vertical direction. The second header pipe 70 is arranged on one end side of the windward heat exchange portion 40a. The second header tube 70 has an upwind heat transfer tube side member 71, a second header partition member 72, a shunt side member 73, a plurality of partition plates 74, and a plurality of rectifying plates 75. In the upwind heat transfer tube side member 71, the second header partition member 72, and the shunt side member 73, the second header partition member 72 is sandwiched between the upwind heat transfer tube side member 71 and the shunt side member 73. , They are combined and integrated so that their longitudinal directions match. In the second header tube 70, the upper end and the lower end are closed by the two partition plates 74. The upwind heat transfer tube side member 71, the second header partition member 72, the shunt side member 73, the partition plate 74 and the rectifying plate 75 are joined to each other and integrated by being brazed with a brazing material, for example, in a furnace. To.

The windward heat transfer tube side member 71 has an arcuate cross section cut in a plane perpendicular to the vertical direction. The upwind heat transfer tube side member 71 is formed with a plurality of upwind heat transfer tube connection openings 711 into which the ends of the corresponding heat transfer tubes 41 (upwind heat transfer tubes 41a) are inserted. The number of upwind heat transfer tube connection openings 711 is the same as the number of stages of the heat transfer tube 41. In the shunt side member 73, the plurality of upwind heat transfer tube connection openings 711 are arranged along the vertical direction.

The second header partition member 72 is a plate-shaped member extending along the vertical direction. In the second header partition member 72, openings for flowing the refrigerant from the windward heat transfer tube side member 71 toward the shunt side member 73 (see 72a and 72b in FIG. 16) are lined up along the vertical direction. It is formed in multiples.

The shunt side member 73 has an arcuate cross section cut by a plane perpendicular to the vertical direction. Further, the shunt side member 73 is formed with a plurality of first thin tube connection openings 73a for connecting one end of the corresponding first thin tube 93. The number of the first capillary connection openings 73a is the same as the number of the first capillary 93. In the shunt side member 73, the plurality of first thin tube connecting openings 73a are arranged along the vertical direction.

The inside of the second header tube 70 is partitioned by a plurality of partition plates 74 and divided into a plurality of spaces (10 second header internal spaces SP1 and one second header subspace Spa) (FIG. 6). 31).

As shown in FIG. 16, a plurality of corresponding heat transfer tubes 41 (windward transfer) are provided in the second header internal space SP1 formed between the two partition plates 74 in the second header tube 70. The ends of the heat pipe 41a) communicate with each other. Further, the end portion of the corresponding first thin tube 93 communicates with the second header internal space SP1. In the second header internal space SP1, the straightening vane 75 is arranged in the upper vicinity of the corresponding first thin tube 93.

The second header subspace SPa is formed near the lower end of the second header tube 70, and is located below each second header internal space SP1 (see FIG. 31). The ends of the corresponding plurality of (here, two) heat transfer tubes 41 (windward heat transfer tubes 41a) communicate with the second header subspace Spa.

In each second header internal space SP1, the second header partition member 72 is formed with a first communication opening 72a near the bottom of the upper partition plate 74 and a second communication opening 72b near the top of the straightening vane 75. Has been done. The straightening vane 75 is formed with a third communication opening 75a.

Each second header internal space SP1 allows the refrigerant flowing out of one of the corresponding heat transfer tubes 41 and the first thin tube 93 to flow into the other. Specifically, during the reverse cycle operation, the refrigerant flowing from the first thin tube 93 into the second header internal space SP1 flows upward through the small third communication opening 75a. The refrigerant flowing upward is divided into the flow paths 411 of the plurality of heat transfer tubes 41 (41a) between the straightening vane 75 and the upper partition plate 74, and flows into the flow path 411. Further, a part of the refrigerant flowing upward forms a loop-shaped flow (see the broken line arrow Ar in FIG. 16) that passes through the first communication opening 72a and then the second communication opening 72b. The refrigerant will eventually flow into the flow paths 411 of the plurality of heat transfer tubes 41 separately from the loop-shaped flow. Further, during the normal cycle operation, the refrigerant flowing from the corresponding heat transfer tube 41 into the second header internal space SP1 passes through the third communication opening 75a and the like and flows into the first thin tube 93.

In the present embodiment, in the second header pipe 70, 14 second header internal spaces SP1 are formed along the vertical direction. Here, in the second header pipe 70, each second header internal space SP1 is a part of the upwind heat transfer tube side member 71, a part of the second header partition member 72, a part of the shunt side member 73, and It is formed by being surrounded by a pair of partition plates 74. Therefore, a part of the upwind heat transfer tube side member 71 forming the first second header internal space SP1, a second header partition member 72, a part of the shunt side member 73, and a pair of partition plates 74 are combined. It can also be interpreted as the second header internal space forming member 78 (corresponding to the "second shunt portion" described in the claims). According to this interpretation, the second header tube 70 can be interpreted as a member composed of a plurality of second header internal space forming members 78 forming the second header internal space SP1. In particular, it can be interpreted that a plurality of second header internal space forming members 78 are lined up along the vertical direction in the installed state (see FIG. 31).

In such an interpretation, each second header internal space forming member 78 is made of aluminum or an aluminum alloy. Further, each second header internal space forming member 78 has a second header internal space SP1 formed therein. Further, each second header internal space forming member 78 forms a refrigerant flow path between the windward heat exchange portion 40a and the shunt 90. Further, each second header internal space forming member 78 is formed with a first thin tube connection opening 73a for connecting one end of the corresponding first thin tube 93. Further, each second header internal space forming member 78 is formed with an upwind heat transfer tube connection opening 711 for connecting one end of the corresponding heat transfer tube 41. As shown in FIG. 16, in the present embodiment, in the second header internal space SP1, the height position of the first thin tube connection opening 73a in the installed state is the windward heat transfer tube connection opening 711 (wind) located at the lowermost position. It is arranged below the height position of the upper heat transfer tube 41a).

In the following description, the second header internal space SP1 located in the upper part of the second header tube 70 is referred to as "upper second header internal space SA", and the second header internal space located in the center of the second header tube 70. SP1 is referred to as "middle second header internal space SB", and the second header internal space SP1 located below the second header tube 70 is referred to as "lower second header internal space SC" (see FIG. 31).

Here, the upper second header internal space SA is inside the second header located above the middle second header internal space SB among the plurality of second header internal spaces SP1 arranged along the vertical direction in the installed state. It is a space SP1 and includes the uppermost second header internal space SP1. Specifically, in the present embodiment, each second header internal space SP1 from the first to the fourth counting from the top (that is, each second header internal space SP1 located above the two-dot chain line L4 in FIG. 31). Corresponds to the upper second header internal space SA.

Here, the middle second header internal space SB (corresponding to the “central second space” described in the scope of the patent claim) is the largest of the plurality of second header internal spaces SP1 arranged along the vertical direction in the installed state. This is the second header internal space SP1 arranged between the upper second header internal space SP1 and the lowermost second header internal space SP1. More specifically, the middle second header internal space SB is located at least one-third or more from the lower end and one-third or less from the upper end of the total height dimension of the outdoor heat exchanger 15. The second header internal space SP1 is included. Specifically, in the present embodiment, each second header internal space SP1 from the fifth to the eighth counting from the top (that is, each second header located between the two-dot chain line L4 and the two-dot chain line L8 in FIG. 31). The internal space SP1) corresponds to the middle second header internal space SB.

Here, the lower second header internal space SC (corresponding to the "lower side second space" described in the scope of the patent claim) is among the plurality of second header internal spaces SP1 arranged along the vertical direction in the installed state. It is the second header internal space SP1 located below the middle second header internal space SB, and includes the lowermost second header internal space SP1. In the present embodiment, each of the second header internal spaces SP1 from the ninth to the thirteenth counting from the top (that is, each second header internal space SP1 located below the two-dot chain line L8 in FIG. 31) is the lower second. Corresponds to the header internal space SC.

(4-4) Wrapped header 80
FIG. 17 is a perspective view of the folded header 80. FIG. 18 is a cross-sectional view of the folded header 80 cut along the horizontal direction. FIG. 19 is an enlarged cross-sectional view of a part of the folded header 80 cut along the vertical direction.

The folded header 80 is an elongated hollow tubular member whose upper and lower ends are closed and extends in the vertical direction. The folded header 80 is arranged on the other end side of the windward side heat exchange portion 40a and the leeward side heat exchange portion 40b.

The folded header 80 is formed with a plurality of windward openings 81 (the same number as the windward heat transfer tubes 41a) into which the other ends of the windward heat transfer tubes 41a are inserted. Further, the folded header 80 is formed with a plurality of leeward side openings 82 into which the other end of the leeward side heat transfer tube 41b is inserted (the same number as the leeward side heat transfer tube 41b). The leeward side opening 81 and the leeward side opening 82 are adjacent to each other along the direction in which the leeward side heat exchange portion 40a and the leeward side heat exchange portion 40b are adjacent to each other. In the folded header 80, the plurality of leeward openings 81 and the plurality of leeward openings 82 are arranged so as to be arranged in the vertical direction.

A plurality of folded spaces SP2 are formed in the folded header 80 to allow the refrigerant flowing out from one of the adjacent windward heat transfer tubes 41a and the leeward heat transfer pipe 41b to flow into the other. The folded space SP2 (corresponding to the "third space" described in the claims) is a space for the refrigerant that has passed through one of the windward heat transfer tube 41a and the leeward heat transfer tube 41b to return to the other (FIG. 18). See broken arrow Ar). More specifically, in the folded space SP2, the refrigerant flowing out from the end of the leeward heat transfer pipe 41b flows into the leeward heat transfer pipe 41a during normal cycle operation (when the gas side collecting pipe 60 is the inlet pipe of the refrigerant). It is a space to let you. Further, the folding space SP2 is a space in which the refrigerant flowing out from the end of the windward heat transfer pipe 41a flows into the leeward heat transfer pipe 41b during the reverse cycle operation (when the gas side collecting pipe 60 is the outlet pipe of the refrigerant). be.

In each folding space SP2, a pair of windward side openings 81 and leeward side openings 82 are arranged. That is, in the folded space SP2, one of the windward heat transfer tubes 41a and the corresponding leeward heat transfer tube 41b communicate with each other. In particular, in the present embodiment, the pair of windward heat transfer tubes 41a and the leeward heat transfer tubes 41b arranged in the same stage communicate with each other in the folded space SP2. The number of folding spaces SP2 formed in the folding header 80 is the same as the number of pairs of the windward opening 81 and the leeward opening 82.

The plurality of folded spaces SP2 are configured by providing a plurality of top portions 85, bottom portions 86, and side portions 87 in the folded header 80 (see FIG. 19). That is, the top portion 85, the bottom portion 86, and the side portion 87 forming one folded space SP2 can be interpreted together as the folded space forming member 88. According to this interpretation, the folded header 80 can be interpreted as a member composed of a plurality of folded space forming members 88 forming the folded space SP2. In particular, it can be interpreted that a plurality of folded space forming members 88 are arranged in the vertical direction (in the installed state).

In such an interpretation, each folded space forming member 88 (corresponding to the "third diversion portion" described in the claims) has a folded space SP2 formed therein. Further, each folded space forming member 88 includes a gas side inlet / outlet of the refrigerant of the outdoor heat exchanger 15 (gas side collecting pipe 60 in this embodiment) and each second header internal space SP1 (each second header internal space forming member). It forms a refrigerant flow path between 78).

(4-5) Shunt 90 (corresponding to the "first shunt" described in the claims)
FIG. 20 is a perspective view of the shunt 90. FIG. 21 is an enlarged view of the portion A surrounded by the alternate long and short dash line in FIG. 20.

The shunt 90 is a member arranged at the liquid side inlet / outlet (that is, between the second header pipe 70 and the eighth pipe P8) in the outdoor heat exchanger 15. The shunt 90 causes the refrigerant flowing out from one of the second header pipe 70 and the eighth pipe P8 to flow into the other. Specifically, the shunt 90 is a mechanism that divides the refrigerant flowing out from the eighth pipe P8 and sends it to the plurality of second header internal spaces SP1 during the reverse cycle operation. Further, the shunt 90 is also a mechanism for collecting the refrigerant sent from each second header internal space SP1 and sending it to the eighth pipe P8 during the normal cycle operation. The shunt 90 is mainly located between the second header pipe 70 and the eighth pipe P8 in the refrigerant circuit RC.

The shunt 90 mainly includes an inlet / outlet pipe 91, a plurality of (13 in this case) first thin pipes 93 extending to the second header pipe 70, a second thin pipe 94 extending to the first header pipe 50, and a shunt main body 95. And have. The entrance / exit pipe 91, the first thin pipe 93, the second thin pipe 94, and the shunt main body 95 are made of aluminum or an aluminum alloy. The shunt 90 is configured by brazing and joining the inlet / outlet pipe 91 in a temporarily assembled state, the first thin pipe 93, the second thin pipe 94, and the shunt main body 95 in a furnace.

FIG. 22 is an enlarged view schematically showing a cross section of the shunt main body 95 cut in the vertical direction. FIG. 23 is a perspective view of the shunt main body 95 and the inlet / outlet pipe 91.

The entrance / exit pipe 91 (corresponding to the "first pipe" described in the claims) is a cylindrical pipe having one end and the other end open. One end of the inlet / outlet pipe 91 is connected to the shunt main body 95, and the other end is connected to the eighth pipe P8. The inlet / outlet pipe 91 is a pipe through which the refrigerant passing through the outdoor heat exchanger 15 enters and exits, and is a pipe forming the liquid side inlet / outlet of the outdoor heat exchanger 15. In particular, the inlet / outlet pipe 91 forms a flow path for allowing the refrigerant flowing out from one of the shunt main body 95 and the eighth pipe P8 to flow into the other. The inlet / outlet pipe 91 is located between the shunt main body 95 and the eighth pipe P8 in the refrigerant circuit RC. The entrance / exit pipe 91 is curved between one end and the other end, and has a substantially J-shape or a substantially U-shape (see FIG. 23).

The first thin tube 93 (corresponding to the "second tube" described in the claims) is a cylindrical pipe with one end and the other end open. The diameter of the first thin tube 93 is smaller than that of the entrance / exit tube 91. One end of the first thin tube 93 is connected to the shunt main body 95. The first thin tube 93 has a one-to-one correspondence with any of the second header internal space SP1 (second header internal space forming member 78), and the first thin tube is arranged in the corresponding second header internal space SP1. The other end is connected to the connection opening 73a. The first thin tube 93 forms a flow path for allowing the refrigerant flowing out from one of the shunt main body 95 and the second header internal space SP1 to flow into the other. The first thin tube 93 is located between the shunt main body 95 and the corresponding second header internal space SP1 in the refrigerant circuit RC. That is, the first thin tube 93 forms a refrigerant flow path on the windward side heat exchange portion 40a side of the inlet / outlet pipe 91.

The second thin tube 94 is a cylindrical pipe with one end and the other end open. The diameter of the second thin tube 94 is smaller than that of the inlet / outlet tube 91. One end of the second thin tube 94 is connected to the shunt main body 95. The other end of the second thin tube 94 is connected to the second thin tube connection opening 532 arranged in the first header subspace S2. The second thin tube 94 forms a flow path for allowing the refrigerant flowing out from one of the shunt main body 95 and the first header subspace S2 to flow into the other. The second thin tube 94 is located between the shunt main body 95 and the first header subspace S2 in the refrigerant circuit RC.

FIG. 24 is a perspective view of the shunt main body 95. FIG. 25 is a view of the shunt main body 95 as viewed from the top surface side. FIG. 26 is a view of the shunt main body 95 as viewed from the bottom surface side.

The shunt main body 95 (corresponding to the “main body portion” described in the claims) is a substantially cylindrical member in which the main body internal space SP3 is formed inside. The main body internal space SP3 is a space that communicates with the inlet / outlet pipe 91 and one end of each first thin tube 93, and allows the refrigerant flowing out from the inlet / outlet pipe 91 to flow (divide) into each first thin tube 93. Further, the main body internal space SP3 is also a space for collecting the refrigerant flowing out from each first thin tube 93 and flowing it into the inlet / outlet pipe 91.

The shunt main body 95 has a top surface 951 facing upward and a bottom surface 952 facing downward in the installed state. The shunt main body 95 is formed with a first opening 95a on the top surface 951 for inserting the entrance / exit pipe 91. In the present embodiment, the first opening 95a is arranged in the central portion of the top surface 951.

The bottom surface 952 of the shunt main body 95 is formed with a plurality of second openings 95b (14 in this case) for inserting the first thin tube 93 or the second thin tube 94. Each second opening 95b has a one-to-one correspondence with any of the first tubules 93 and the second tubule 94, and the corresponding tubules are inserted. In the present embodiment, the plurality of second openings 95b are arranged in an annular shape at intervals on the bottom surface 952. The first opening 95a and each second opening 95b individually communicate with the main body internal space SP3 (see FIG. 22).

FIG. 27 is an enlarged view showing the circumference of the shunt main body 95 as seen from the horizontal direction. FIG. 28 is an enlarged view showing the state of FIG. 27 as viewed from different directions.

In the shunt 90, the inlet / outlet pipe 91 extends upward from the top surface of the shunt main body 95 (see FIG. 27). In other words, the inlet / outlet pipe 91 is connected to the shunt main body 95 so as to extend upward from the main body internal space SP3 in the installed state (see FIG. 22).

Further, in the shunt 90, each first thin tube 93 once extends downward from the bottom surface of the shunt main body 95 (see FIGS. 27 and 28). In other words, each first capillary tube 93 is connected to the shunt main body 95 so as to extend downward from the main body internal space SP3 in the installed state. Specifically, each first capillary tube 93 extends downward from the main body internal space SP3 and then curves, and extends upward toward the corresponding second header internal space SP1. More specifically, in the present embodiment, more than half (nine in this case) of the first thin tubes 93 of each first thin tube 93 extend downward from the main body internal space SP3 and then swell downward. It is an upward curved pipe 93a (see FIGS. 27 and 28) that curves and changes the extending direction in the upward direction and extends along the upward direction while being adjacent to the shunt main body 95 at intervals. That is, the upper curved pipe 93a has at least two curved portions (a curved portion that folds upward from the lower part and a curved portion that extends upward and then curves toward the second header internal space SP1).

In addition, most of the upward curved pipes 93a (here, eight) are curved toward the center of the shunt main body 95 and extend in the upward direction while being adjacent to the inlet / outlet pipe 91 at intervals (FIG. FIG. 27, see FIG. 28). That is, the upper curved pipe 93a further has one curved portion (curved portion curved toward the center of the shunt main body 95).

In the present embodiment, the upper curved pipe 93a is arranged at intervals in the circumferential direction of the shunt main body 95 and the inlet / outlet pipe 91 in a plan view in the installed state. In other words, in the shunt 90, the shunt main body 95 and the inlet / outlet pipe 91 extending upward from the top surface side are connected to the bottom surface side and are curved and extend upward. It can be interpreted that it is surrounded by).

However, the shunt main body 95 has an outer surface portion not surrounded by the first thin tube 93, and the outer surface portion corresponds to a jig used when moving into the furnace when assembling the shunt 90. It functions as a contacting contact portion 953. That is, the shunt main body 95 is moved into the furnace while being supported by a jig 100 as shown in FIG. 29, for example, with the inlet / outlet pipe 91, the plurality of first thin pipes 93, and the second thin pipe 94 inserted. To. Therefore, a part of the shunt main body 95 (that is, a part corresponding to the contact portion 953) is not adjacent to the first thin tube 93 in order to secure a receiving surface supported by the jig 100. That is, the shunt main body 95 has a contact portion 953 that abuts on the jig.

In the shunt 90, during normal cycle operation, the refrigerant flowing out from each second header internal space SP1 flows into the corresponding first thin tube 93, passes through the first thin tube 93, and passes through the first thin tube 93 to form the shunt main body 95 (main body internal space SP3). ). The refrigerant that has flowed into the main body internal space SP3 flows through the inlet / outlet pipe 91 and flows out to the eighth pipe P8.

Further, during the reverse cycle operation, the refrigerant flowing out from the eighth pipe P8 passes through the inlet / outlet pipe 91 and flows into the shunt main body 95 (main body internal space SP3). The refrigerant that has flowed into the main body internal space SP3 is separated and flows through the plurality of first thin tubes 93 and flows into any of the second header internal spaces SP1.

(5) Positional relationship of each part in the outdoor heat exchanger 15 FIG. 30 is a schematic view showing the positional relationship of the first header pipe 50, the gas side collecting pipe 60, the second header pipe 70, and the shunt 90 in a plan view. Is. In the outdoor heat exchanger 15, the first header pipe 50, the gas side collecting pipe 60, the second header pipe 70, and the shunt 90 are densely arranged near one end of the outdoor heat exchanger 15 as shown in FIG. Has been done. In particular, the second header pipe 70 (second header internal space forming member 78) and the shunt 90 are arranged close to each other in the vicinity of one end of the windward heat exchange portion 40a. The linear distance D1 between the second header tube 70 (second header internal space forming member 78) and the shunt 90 in a plan view is appropriately set according to the design specifications and the installation environment, but in the present embodiment, it is made compact. From the viewpoint, it is set to 100 mm or less.

(6) Manufacturing Method of Outdoor Heat Exchanger 15 The outdoor heat exchanger 15 is configured by brazing and joining each part with a brazing material in a furnace. In this respect, the outdoor heat exchanger 15 is greatly curved at three points in a plan view, and the bent portions B1, B2, and B3 are formed (see FIG. 8). On the other hand, since the size of the furnace in which brazing is performed is fixed, the heat exchange portion 40 is brazed in the furnace in a flat state before the bent portions B1, B2 and B3 are formed. The bent portions B1, B2, and B3 are configured by using a predetermined roll jig and pressing jig after brazing in the furnace.

(7) Path Configuration in Outdoor Heat Exchanger 15 In the outdoor heat exchanger 15 configured as described above, a plurality of paths are configured. Here, the "pass" includes the first thin tube 93 of the shunt 90, the second header internal space SP1 (second header internal space forming member 78), and one or more corresponding heat transfer tubes 41 (41a and 41b). , The turn-back space SP2, and the passage of the refrigerant.

FIG. 31 is a schematic view schematically showing each path of the outdoor heat exchanger 15 as seen from the windward side. FIG. 32 is a schematic view schematically showing each path of the outdoor heat exchanger 15 as seen from the leeward side. As shown in FIGS. 31 and 32, in the outdoor heat exchanger 15, the first pass RP1 to the thirteenth pass RP13 are configured.

The first pass RP1 is the path located at the highest position in the installed state. In FIGS. 31 and 32, the first pass RP1 is a pass located above the two-dot chain line L1. The first pass RP1 includes three windward heat transfer tubes 41a and a leeward heat transfer tube 41b. The first path RP1 is a path including the second header internal space SP1 (that is, the uppermost upper second header internal space SA) located above the alternate long and short dash line L1.

The second pass RP2 is the second pass from the top in the installed state. In FIGS. 31 and 32, the second pass RP2 is a path located between the two-dot chain line L1 and the two-dot chain line L2. The second pass RP2 includes four windward heat transfer tubes 41a and a leeward heat transfer tube 41b. The second pass RP2 is a path including the second header internal space SP1 (that is, the second upper second header internal space SA located between the two-dot chain line L1 and the two-dot chain line L2).

The third pass RP3 is the third pass from the top in the installed state. In FIGS. 31 and 32, the third pass RP3 is a path located between the two-dot chain line L2 and the two-dot chain line L3. The third pass RP3 includes eight windward heat transfer tubes 41a and leeward heat transfer tubes 41b. The third pass RP3 is a path including the second header internal space SP1 (that is, the third upper upper second header internal space SA) located between the two-dot chain line L2 and the two-dot chain line L3.

The fourth pass RP4 is the fourth pass from the top in the installed state. In FIGS. 31 and 32, the fourth pass RP4 is a path located between the two-dot chain line L3 and the two-dot chain line L4. The fourth pass RP4 includes nine windward heat transfer tubes 41a and leeward heat transfer tubes 41b. The fourth pass RP4 is a path including the second header internal space SP1 (that is, the fourth upper second header internal space SA from the top) located between the two-dot chain line L3 and the two-dot chain line L4.

The fifth pass RP5 is the fifth pass from the top in the installed state. In FIGS. 31 and 32, the fifth pass RP5 is a path located between the two-dot chain line L4 and the two-dot chain line L5. The fifth pass RP5 includes 10 windward heat transfer tubes 41a and leeward heat transfer tubes 41b. The fifth path RP5 is a path including the second header internal space SP1 (that is, the uppermost middle second header internal space SB) located between the two-dot chain line L4 and the two-dot chain line L5.

The sixth pass RP6 is the sixth pass from the top in the installed state. In FIGS. 31 and 32, the sixth pass RP6 is a path located between the two-dot chain line L5 and the two-dot chain line L6. The sixth pass RP6 includes 11 windward heat transfer tubes 41a and leeward heat transfer tubes 41b. The sixth path RP6 is a path including the second header internal space SP1 (that is, the second middle stage second header internal space SB located between the two-dot chain line L5 and the two-dot chain line L6).

The seventh pass RP7 is the seventh pass from the top in the installed state. In FIGS. 31 and 32, the seventh pass RP7 is a pass located between the two-dot chain line L6 and the two-dot chain line L7. The seventh pass RP7 includes twelve windward heat transfer tubes 41a and leeward heat transfer tubes 41b. The seventh path RP7 is a path including the second header internal space SP1 (that is, the third middle stage second header internal space SB located between the two-dot chain line L6 and the two-dot chain line L7).

The eighth pass RP8 is the eighth pass from the top in the installed state. In FIGS. 31 and 32, the eighth pass RP8 is a path located between the two-dot chain line L7 and the two-dot chain line L8. The eighth pass RP8 includes twelve windward heat transfer tubes 41a and leeward heat transfer tubes 41b. The eighth path RP8 is a path including the second header internal space SP1 (that is, the fourth middle stage second header internal space SB from the top) located between the two-dot chain line L7 and the two-dot chain line L8.

The ninth pass RP9 is the ninth pass from the top in the installed state. In FIGS. 31 and 32, the ninth pass RP9 is a path located between the two-dot chain line L8 and the two-dot chain line L9. The ninth pass RP9 includes seven windward heat transfer tubes 41a and a leeward heat transfer tube 41b. The ninth pass RP9 is a path including the second header internal space SP1 (that is, the uppermost lower second header internal space SC) located between the two-dot chain line L8 and the two-dot chain line L9.

The tenth pass RP10 is the tenth pass from the top in the installed state. In FIGS. 31 and 32, the tenth pass RP10 is a pass located between the two-dot chain line L9 and the two-dot chain line L10. The tenth pass RP10 includes six windward heat transfer tubes 41a and a leeward heat transfer tube 41b. The tenth pass RP10 is a path including the second header internal space SP1 (that is, the second lower second header internal space SC located between the two-dot chain line L9 and the two-dot chain line L10).

The eleventh pass RP11 is the eleventh path from the top in the installed state. In FIGS. 31 and 32, the eleventh pass RP11 is a path located between the two-dot chain line L10 and the two-dot chain line L11. The eleventh pass RP11 includes six windward heat transfer tubes 41a and a leeward heat transfer tube 41b. The eleventh path RP11 is a path including the second header internal space SP1 (that is, the third lower second header internal space SC from the top) located between the two-dot chain line L10 and the two-dot chain line L11.

The twelfth pass RP12 is the twelfth pass from the top in the installed state. In FIGS. 31 and 32, the twelfth pass RP12 is a path located between the two-dot chain line L11 and the two-dot chain line L12. The twelfth pass RP12 includes four windward heat transfer tubes 41a and a leeward heat transfer tube 41b. The twelfth path RP12 is a path including the second header internal space SP1 (that is, the fourth lower second header internal space SC from the top) located between the two-dot chain line L11 and the two-dot chain line L12.

The thirteenth pass RP13 is the thirteenth (bottom) path from the top in the installed state. In FIGS. 31 and 32, the thirteenth pass RP13 is a path located between the two-dot chain line L12 and the two-dot chain line L13. The thirteenth pass RP13 includes five windward heat transfer tubes 41a and a leeward heat transfer tube 41b. The thirteenth pass RP13 is a pass including the second header internal space SP1 (that is, the fifth and sixth lower second header internal space SC located between the two-dot chain line L12 and the one-dot chain line A1). The thirteenth pass RP13 is further divided into an upper thirteenth pass RP13a and a lower thirteenth pass RP13b.

The upper thirteenth pass RP13a is located above the alternate long and short dash line A1 (FIGS. 31 and 32). The upper 13-pass RP13a is composed of a first thin tube 93, a lowermost second header internal space SP1, three windward heat transfer tubes 41a, a folded space SP2, and three leeward heat transfer tubes 41b.

The lower thirteenth pass RP13b is located below the alternate long and short dash line A1 (FIGS. 31 and 32). The lower 13th pass RP13b has a second thin tube 94, a space (S1, S2) in the first header tube 50, two leeward heat transfer tubes 41b counting from the bottom, a folded space SP2, and two counting from the bottom. It is composed of the windward heat transfer tube 41a and the second header subspace Spa.

The thirteenth path RP13 configured in this way has a longer flow path length than the other paths.

Each path (RP1-RP13) configured as described above divides in one of the first header main space S1 and the main body internal space SP3, and merges in the other. In other words, in the outdoor heat exchanger 15, each path is configured in parallel. That is, as a general rule, the refrigerant that has passed through any of the paths (RP1-RP13) flows out of the outdoor heat exchanger 15 without flowing into the other paths. From this point of view, the outdoor heat exchanger 15 is different from the heat exchanger in which the refrigerant that has passed through one of the paths returns to the other path.

Here, as described above, for the outdoor airflow AF passing through the heat exchange section 40 of the outdoor heat exchanger 15, the portion above the air passing through the lower portion (particularly the path below the center) (particularly from the center). The wind speed is higher for the air passing through the upper path). Therefore, among the paths, the path arranged at the upper part has a higher wind speed of the passing air flow than the path passing through the lower part. For example, the air passing through the path including the middle second header internal space SB (here, RP5-RP8) rather than the wind speed of the air flow passing through the path including the lower second header internal space SC (here, RP9-RP13). The wind speed of the flow is higher. Further, the air passing through the path including the upper second header internal space SA (here, RP1-RP4) is higher than the wind speed of the air flow passing through the path including the middle second header internal space SB (here, RP5-RP8). The wind speed of the flow is higher.

(8) Flow of Refrigerant in Outdoor Heat Exchanger 15 In the outdoor heat exchanger 15, the refrigerant flows in the following modes.

(8-1) During normal cycle operation The refrigerant flowing into the outdoor heat exchanger 15 during normal cycle operation flows while exchanging heat with the outdoor air flow AF. However, during the cooling cycle defrosting operation, the refrigerant flowing into the outdoor heat exchanger 15 flows while exchanging heat with the adhering frost.

Specifically, during the normal cycle operation, the refrigerant flows from the seventh pipe P7 into the gas side collecting pipe 60. The refrigerant that has flowed into the gas-side collecting pipe 60 flows into the first header main space S1 of the first header pipe 50 via the plurality of connecting pipes 61. The refrigerant flowing into the first header main space S1 is separated, flows into the leeward heat transfer tube 41b of each pass (first pass RP1-13th pass RP13), and passes through the leeward heat exchange section 40b. The refrigerant that has passed through the leeward heat exchange section 40b reaches the folding header 80 (more specifically, the corresponding folding space SP2).

After that, the refrigerant turns back in the folded space SP2, flows into the corresponding windward heat transfer tube 41a, and passes through the windward heat exchange section 40a. The refrigerant that has passed through the windward heat exchange section 40a reaches the second header pipe 70 (more specifically, the corresponding second header internal space SP1).

As a general rule, the refrigerant that has flowed into the second header internal space SP1 flows into the shunt 90 (main body internal space SP3) via the corresponding first thin tube 93. The refrigerant flowing into the main body internal space SP3 from the first thin tube 93 merges with the refrigerant flowing out from the other first thin tube 93, passes through the inlet / outlet pipe 91, and flows out to the eighth pipe P8.

Of the refrigerant that has flowed from the gas side collecting pipe 60 into the first header main space S1 of the first header pipe 50, the leeward heat transfer tube 41b (that is, the leeward heat exchange) located at the lowermost part of the first header main space S1. The refrigerant that has flowed into the leeward side heat transfer tube 41b), which is the second from the bottom in the part 40b, flows through the leeward side heat exchange part 40b. The refrigerant that has passed through the leeward heat exchange section 40b folds back in the turn-back space SP2, flows into the second windward heat transfer tube 41a from the bottom, and flows through the leeward heat exchange section 40a. The refrigerant that has passed through the windward heat exchange section 40a folds downward in the second header subspace SPA, flows into the lower windward heat transfer tube 41a, and flows through the windward heat exchange section 40a again. After that, the refrigerant that has passed through the leeward heat exchange section 40a folds back in the folded space SP2, flows into the lowermost leeward heat transfer tube 41b, and flows through the leeward heat exchange section 40b. After that, the refrigerant that has passed through the leeward heat exchange section 40b flows into the first header subspace S2, passes through the second thin tube 94, and flows into the main body internal space SP3 of the shunt main body 95.

(8-2) During reverse cycle operation The refrigerant flowing into the outdoor heat exchanger 15 during reverse cycle operation flows while exchanging heat with the outdoor air flow AF. Specifically, during the reverse cycle operation, the refrigerant flows from the eighth pipe P8 into the inlet / outlet pipe 91. The refrigerant that has passed through the inlet / outlet pipe 91 reaches the shunt 90 (main body internal space SP3), and separately flows into the plurality of first thin tubes 93 and the second thin tubes 94 (that is, flows into each path).

The refrigerant flowing into the first thin tube 93 from the main body internal space SP3 reaches the second header pipe 70 (more specifically, the corresponding second header internal space SP1). The refrigerant that has flowed into the second header internal space SP1 flows into the corresponding windward heat transfer tube 41a and passes through the windward heat exchange section 40a. The refrigerant that has passed through the windward heat exchange section 40a reaches the folding header 80 (more specifically, the corresponding folding space SP2). After that, the refrigerant turns back in the folded space SP2, flows into the corresponding leeward heat transfer tube 41b, and passes through the leeward heat exchange section 40b. The refrigerant that has passed through the leeward heat exchange section 40b reaches the first header pipe 50 (more specifically, the first header main space S1). The refrigerant flowing into the first header main space S1 reaches the gas side collecting pipe 60 via the plurality of connecting pipes 61, and flows out from the outdoor heat exchanger 15.

On the other hand, the refrigerant flowing into the second thin tube 94 from the main body internal space SP3 (that is, the refrigerant flowing into the lower 13th pass RP13b) reaches the first header subspace S2 of the first header tube 50. The refrigerant that has flowed into the first header subspace S2 flows into the lowermost leeward heat transfer tube 41b and passes through the leeward heat exchange section 40b. The refrigerant that has passed through the leeward heat exchange section 40b reaches the folding header 80 (more specifically, the corresponding folding space SP2). After that, the refrigerant turns back in the folded space SP2, flows into the lower windward heat transfer tube 41a, and passes through the windward heat exchange section 40a. The refrigerant that has passed through the windward heat exchange section 40a is folded upward in the second header subspace Spa and flows into the windward heat transfer tube 41a, which is the second from the bottom of the windward heat exchange section 40a, and flows into the windward heat exchange section 40a again. Flow. After that, the refrigerant that has passed through the leeward heat exchange section 40a folds back in the leeward space SP2, flows into the leeward heat transfer tube 41b, which is the second from the bottom, and flows through the leeward heat exchange section 40b. After that, the refrigerant that has passed through the leeward side heat exchange section 40b flows into the first header main space S1, reaches the gas side collecting pipe 60 via the connecting pipe 61, and flows out from the outdoor heat exchanger 15.

(9) Functions of Outdoor Heat Exchanger 15 The outdoor heat exchanger 15 configured as described above has the following functions.

(9-1) Performance improvement promotion function (A)
In the shunt main body 95, the height of the communication portion of the main body internal space SP3 with the first thin tube 93 (height of the outlet surface of the first thin tube 93) h2 (see FIG. 27) is a reference of the head. When the head difference becomes larger than the pressure of the refrigerant flowing through the heat transfer tube 41, the flow of the refrigerant is obstructed. In particular, with respect to the heat transfer tube 41 arranged at the lower part of the heat exchange unit 40, the circulation amount of the refrigerant is reduced due to the influence of the head, and the refrigerant tends to stay.

Here, in the outdoor heat exchanger 15, the flat tube is used as the heat transfer tube 41. Then, the outdoor heat exchanger 15 uses a header (more specifically, a plurality of second header internal spaces SP1 in the second header pipe 70) to divert the refrigerant to each path, so that so-called header diversion is performed. It is configured in. Further, a plurality of heat transfer tubes 41 are included in each path (RP1-RP10), and the current is diverted to each heat transfer tube 41 in the second header internal space SP1. In particular, in the outdoor heat exchanger 15, a loop-shaped flow of the refrigerant is formed in the second header internal space SP1 with respect to the diversion to each heat transfer tube 41.

In the outdoor heat exchanger 15 configured as described above, a drift may occur with respect to the refrigerant flowing into each heat transfer tube 41 in the second header internal space SP1 in relation to the head difference during the reverse cycle operation. That is, of the heat transfer tubes 41 connected to the second header internal space SP1, the liquid refrigerant is more likely to flow in the lower heat transfer tube 41, and the gas refrigerant is more likely to flow in the upper heat transfer tube 41. That is, in one pass, a pressure loss difference is likely to occur with respect to a plurality of heat transfer tubes 41 located above and below. In relation to this, particularly during the cooling cycle defrost operation, in each pass, the lower heat transfer tube 41, which is easily affected by the liquid head, tends to retain the refrigerant, and the hot gas is not supplied and undissolved residue is likely to occur.

In this respect, in the heat exchanger that does not perform header shunting, the number of paths and the number of heat transfer tubes have a one-to-one relationship, and when functioning as a condenser, the refrigerant flowing through the heat transfer tubes of the lowest path If a pressure difference larger than that of the liquid head of the shunt is secured, the stagnation of the refrigerant is suppressed. On the other hand, in a heat exchanger that performs header diversion such as the outdoor heat exchanger 15, the circulation amount is different for each pass, and when it functions as a condenser, it is most affected by the liquid head and the circulation amount tends to be small. With respect to the refrigerant flowing through the heat transfer tube 41 in the lowermost stage, it is necessary to ensure a pressure difference superior to that of the liquid head.

In the outdoor heat exchanger 15, the height position of the shunt main body 95 in the installed state is lower than before. In the present embodiment, the height position of the shunt main body 95 is suppressed so that the height h1 (see FIG. 27) of the bottom surface 952 from the upper surface of the bottom frame 33 is 43 mm (within 100 mm).

This makes it possible to reduce the head difference caused by the installation height of the shunt main body 95 when the outdoor heat exchanger 15 is used as a condenser. In this connection, the pressure difference over the liquid head with respect to the liquid refrigerant flowing in the heat transfer tube 41 (for example, the heat transfer tube 41 included in the 9th pass RP9 to the 13th pass RP13) arranged in the lower part of the heat exchange unit 40 is higher than that of the liquid head. It is secured and easy to flow, and performance improvement is promoted. In particular, during the cooling cycle defrosting operation, the retention of the liquid refrigerant is suppressed and the defrosting is promoted. Therefore, the undissolved residue of frost is suppressed and the reliability is excellent.

(B)
Further, in the outdoor heat exchanger 15, 13 paths are formed so as to be arranged along the vertical direction. That is, in the outdoor heat exchanger 15, three or more second header internal spaces SP1 are arranged along the vertical direction in the installed state. Then, in each of the second header internal spaces SP1, a predetermined number of heat transfer tubes 41 communicate with each other.

Specifically, three heat transfer tubes 41 communicate with the upper second header internal space SA of the first pass RP1. Four heat transfer tubes 41 communicate with the upper second header internal space SA of the second pass RP2. Eight heat transfer tubes 41 communicate with the upper second header internal space SA of the third pass RP3. Nine heat transfer tubes 41 communicate with the upper second header internal space SA of the fourth pass RP4.

Further, 10 heat transfer tubes 41 communicate with each other in the middle second header internal space SB of the fifth pass RP5. Eleven heat transfer tubes 41 communicate with the inner space SB of the middle second header of the sixth pass RP6. Twelve heat transfer tubes 41 communicate with the inner space SB of the middle second header of the seventh pass RP7. Twelve heat transfer tubes 41 communicate with the inner space SB of the middle second header of the eighth pass RP8.

Further, seven heat transfer tubes 41 communicate with the lower second header internal space SC of the ninth pass RP9. Six heat transfer tubes 41 communicate with the lower second header internal space SC of the tenth pass RP10. Six heat transfer tubes 41 communicate with the lower second header internal space SC of the eleventh pass RP11. Four heat transfer tubes 41 communicate with the lower second header internal space SC of the twelfth pass RP12. Three heat transfer tubes 41 communicate with the lower second header internal space SC of the thirteenth pass RP13 (upper thirteenth pass RP13a). That is, in the present embodiment, the number of heat transfer tubes 41 communicating with the lower second header internal space SC is 7 or less.

In the outdoor heat exchanger 15 configured in such an embodiment, the number of heat transfer tubes 41 communicating with the lower second space of one is larger than the number of heat transfer tubes 41 communicating with the second header internal space SB of the middle stage. Is less. This promotes the reduction of the head of the liquid refrigerant in the shunt main body 95 (main body internal space SP3) when used as a condenser. In this connection, when used as a condenser, the heat transfer tube 41 (that is, the 9th pass RP9 to the 13th pass RP13 arranged at the lower part) communicating with the lower second header internal space SC where the liquid refrigerant tends to accumulate is RP13. ), The refrigerant is apt to flow well, and the performance improvement is promoted. In particular, during the cooling cycle defrosting operation, the retention of the liquid refrigerant is suppressed and the defrosting is promoted. Therefore, the undissolved residue of frost is suppressed and the reliability is excellent.

(9-2) Assemblability improvement function In the outdoor heat exchanger 15, the flow divider main body 95 has a large number (10, that is, 6 or more in this case) as the inlet / outlet pipe 91 extends upward from the main body internal space SP3. The first capillary tube 93 is installed so as to extend downward from the main body internal space SP3. In this respect, in relation to the fact that the shunt main body 95 is installed in such a manner, when the shunt main body 95 and the first thin tube 93 are manually brazed and joined, the workability is significantly reduced and the assembleability is improved. It is assumed that it is not good. In the outdoor heat exchanger 15, since the shunt main body 95 and the plurality of first thin tubes 93 are made of aluminum or an aluminum alloy, both can be joined by brazing in the furnace to form the shunt 90. It has become. In this regard, the improvement of assemblability is promoted.

(9-3) Compactification Improvement Function The outdoor heat exchanger 15 is being promoted to be compact. That is, in the shunt 90, each first thin tube 93 extends downward from the main body internal space SP3, then curves, and extends upward toward the corresponding second header internal space SP1. .. More specifically, in the present embodiment, more than half (nine in this case) of the first thin tubes 93 of each first thin tube 93 extend downward from the main body internal space SP3 and then swell downward. It is an upward curved pipe 93a (see FIGS. 27 and 28) that curves and changes the extending direction in the upward direction and extends along the upward direction while being adjacent to the shunt main body 95 at intervals. In addition, most of the upward curved pipes 93a (here, eight) are curved toward the center of the shunt main body 95 and extend in the upward direction while being adjacent to the inlet / outlet pipe 91 at intervals (FIG. FIG. 27, see FIG. 28). That is, in a plan view in the installed state, more than half of the first thin tubes 93 are arranged at intervals in the circumferential direction of the shunt main body 95 and the inlet / outlet tube 91. In other words, in the shunt 90, the shunt main body 95 and the inlet / outlet pipe 91 extending upward from the top surface side are connected to the bottom surface side and are curved and extend upward. ) Surrounds the surrounding area.

By configuring the shunt 90 in such an embodiment, the distance between the shunt main body 95 and the first thin tube 93, the distance between the inlet / outlet pipe 91 and each first thin tube 93, and / or the distance between each first thin tube 93 can be reduced. It is possible to do. That is, it is possible to arrange each part in close proximity while ensuring clearance. This promotes the compactification of the shunt 90, which is expected to be arranged in a narrow space. As a result, the outdoor heat exchanger 15 is being made more compact.

(10) Features (10-1)
Conventionally, a heat exchanger including a plurality of flat tubes in which flat tubes are lined up in the vertical direction in an installed state, a diversion device arranged at the liquid side end, and a header arranged between the heat exchange section and the diversion device. Heat exchangers with tubes are known. In the heat exchanger, a plurality of spaces are formed in the header pipe so as to line up along the direction in which the flat pipes are stacked, and the corresponding flat pipes communicate with each space. Further, each space in the header and the shunt are connected by a thin tube, and a plurality of paths (refrigerant flow paths) are formed. When such a heat exchanger is used as a condenser, the liquid refrigerant tends to stay in the flat tube (pass) arranged near the bottom stage in relation to the head difference caused by the installation height of the shunt.

In the outdoor heat exchanger 15 according to the present embodiment, in the installed state, three or more second header internal spaces SP1 are arranged along the vertical direction, and the middle second header internal space SB (second header internal space located in the center) is arranged. The number of heat transfer tubes 41 communicating with the lower second header internal space SC (second header internal space SP1 located below the middle second header internal space SB) is larger than the number of heat transfer tubes 41 communicating with SP1). few. This promotes the reduction of the head of the liquid refrigerant in the shunt main body 95 (main body internal space SP3) when used as a condenser. In this connection, when used as a condenser, the heat transfer tube 41 (that is, the 9th pass RP9 to the 13th pass RP13 arranged at the lower part) communicating with the lower second header internal space SC where the liquid refrigerant tends to accumulate is RP13. ), The refrigerant is apt to flow well, and the performance improvement is promoted. In particular, during the cooling cycle defrosting operation, the retention of the liquid refrigerant is suppressed and the defrosting is promoted. Therefore, the undissolved residue of frost is suppressed and the reliability is excellent.

(10-2)
In the outdoor heat exchanger 15 according to the above embodiment, the folded space forming member 88 (third diversion portion) forms a refrigerant flow path between the second header internal space forming member 78 and the gas side collecting pipe 60. The folded space SP2 (third space) is formed inside. The folded space SP2 communicates with the other end of the corresponding heat transfer tube (one of the windward side heat transfer tube 41a and the leeward side heat transfer tube 41b), and the second heat transfer tube (windward side) arranged in the same stage as the heat transfer tube 41. It communicates with one end of the heat transfer tube 41a and the other end of the leeward heat transfer tube 41b).

As a result, each path (RP1-RP13) is configured in parallel. That is, as a general rule, the refrigerant that has passed through any of the paths (RP1-RP13) flows out of the outdoor heat exchanger 15 without flowing into the other paths.

(10-3)
In the outdoor heat exchanger 15 according to the above embodiment, in the installed state, the wind speed of the outdoor air flow AF passing around the heat transfer tube 41 communicating with the lower second header internal space SC is higher than the wind speed of the lower second header internal space SC. The wind speed of the outdoor air flow AF passing around the heat transfer tube 41 communicating with the upper second header internal space SP1 is higher. That is, the performance improvement of the outdoor heat exchanger 15 arranged in the outdoor unit 10 in which the outdoor airflow AF is sucked from the side and blown upward is promoted.

(10-4)
In the outdoor heat exchanger 15 according to the above embodiment, the lower second header internal space SC is arranged at a height position of 1/3 or less of the total height of the heat exchange unit 40 in the installed state, and the lower stage is concerned. The refrigerant easily flows well in the heat transfer tube 41 (that is, the heat transfer tube 41 in which the liquid refrigerant tends to accumulate when used as a condenser) communicating with the second header internal space SC, and the performance improvement is promoted. ing.

(10-5)
In the outdoor heat exchanger 15 according to the above embodiment, the heat transfer tube 41 located at the lowermost stage in the installed state communicates with the lower second header internal space SC, and is used as the heat transfer tube 41 (that is, as a condenser). In particular, in the heat transfer tube 41) in which the liquid refrigerant tends to accumulate, the refrigerant tends to flow well, and the performance improvement is promoted.

(10-6)
In the outdoor heat exchanger 15 according to the above embodiment, in the installed state, a plurality of lower second header internal space SCs are arranged along the vertical direction, and the heat transfer tube 41 communicating with each lower second header internal space SC ( That is, when used as a condenser, the refrigerant tends to flow well, especially in the heat transfer tube 41) where the liquid refrigerant tends to accumulate.

(10-7)
In the outdoor heat exchanger 15 according to the above embodiment, in the installed state, a plurality of middle-stage second header internal space SBs are arranged along the vertical direction. In relation to this, in the heat transfer tube 41 communicating with the lower second header internal space SC, the liquid refrigerant tends to accumulate particularly when used as a condenser. In the above embodiment, the refrigerant is also in the heat transfer tube 41. Is easy to flow well.

(10-8)
In the outdoor heat exchanger 15 according to the above embodiment, one end of the inlet / outlet pipe 91 is connected to the shunt main body 95 so as to extend upward from the main body internal space SP3 in the installed state. One end of the first thin tube 93 is connected to the shunt main body 95 so as to extend downward from the main body internal space SP3 in the installed state.

This makes it possible to lower the height position of the shunt main body 95 of the shunt 90 in the installed state. As a result, when the heat transfer tubes 41 are installed so as to be arranged along the vertical direction and used as a condenser, it is possible to reduce the head difference caused by the installation height of the shunt. Therefore, when used as a condenser, the retention of the liquid refrigerant is particularly suppressed even in the heat transfer tube 41 (pass) arranged near the lowermost stage where the liquid refrigerant tends to stay. Therefore, the performance improvement is particularly promoted, and the decrease in reliability is particularly suppressed during the normal cycle operation (cooling operation and cooling cycle defrosting operation).

(10-9)
In the air conditioning system 1 according to the above embodiment, performance improvement is promoted in relation to the function of the outdoor heat exchanger 15.

(11) Modification Example The above embodiment can be appropriately modified as shown in the following modification examples. In addition, each modification may be applied in combination with another modification as long as there is no contradiction.

(11-1) Modification 1
In the above embodiment, in the shunt main body 95, a plurality of second openings 95b to which one end of the first thin tube 93 is connected are formed on the bottom surface 952 facing downward in the installed state. From the viewpoint of connecting the first shunt 93 to the shunt main body 95 so as to extend downward from the main body internal space SP3 in the installed state, the shunt 90 is preferably configured in such an embodiment. However, the configuration of the shunt 90 is not necessarily limited to this, as long as the first tubule 93 is connected to the shunt main body 95 so as to extend downward from the main body internal space SP3 in the installed state. It can be changed. For example, in the shunt main body 95, a part or all of the plurality of second openings 95b may be formed on the side surface facing sideways in the installed state.

(11-2) Modification 2
In the above embodiment, in the shunt main body 95, a first opening 95a to which one end of the inlet / outlet pipe 91 is connected is formed on the top surface 951 facing upward in the installed state. From the viewpoint of connecting the inlet / outlet pipe 91 to the shunt main body 95 so as to extend upward from the main body internal space SP3 in the installed state, the shunt 90 is preferably configured in such an embodiment. However, the configuration of the shunt 90 is not necessarily limited to this, and is appropriately changed as long as it is connected to the shunt main body 95 so that the inlet / outlet pipe 91 extends upward from the main body internal space SP3 in the installed state. Is possible. For example, in the shunt main body 95, the first opening 95a may be formed on the side surface facing sideways in the installed state.

Further, in the shunt main body 95, a first opening 95a to which one end of the inlet / outlet pipe 91 is connected may be formed on the bottom surface 952 facing downward in the installed state. In such a case, in the shunt main body 95, a first opening 95a to which one end of the first thin tube 93 is connected may be formed on the top surface 951 facing upward in the installed state. In that example, one end is connected to the shunt main body 95 so that the inlet / outlet pipe 91 extends downward from the main body internal space SP3 in the installed state, and a plurality of first thin tubes 93 are connected from the main body internal space SP3 in the installed state. One end is connected to the shunt main body 95 so as to extend in the upward direction, but the action and effect described in the above "10-1" can be realized in the same manner as in the above embodiment.

(11-3) Modification 3
In the above embodiment, the first thin tube 93 has a one-to-one correspondence with the second header internal space SP1 and is connected to the corresponding second header internal space SP1. However, the correspondence between the first thin tube 93 and the second header internal space SP1 can be appropriately changed according to the design specifications and the installation environment as long as there is no contradiction. For example, each first thin tube 93 may correspond to any second header internal space SP1 in a one-to-many, many-to-one, or many-to-many manner.

Further, the number of the first thin tubes 93 included in the shunt 90 is not necessarily limited to that in the above embodiment, and can be appropriately changed according to the design specifications and the installation environment. That is, the shunt 90 may have 11 or more first thin tubes 93, or may have less than 10 first thin tubes 93.

(11-4) Modification 4
In the outdoor heat exchanger 15 according to the above embodiment, the second header internal space forming member 78 is the windward heat transfer tube connection opening 711 connected to one end of the corresponding heat transfer tube 41, and the corresponding first thin tube 93. A first thin tube connection opening 73a connected to the end is formed, and the height position of the first thin tube connection opening 73a is the height of the windward heat transfer tube connection opening 711 located at the lowermost position in the installed state. It was below the position. From the viewpoint of suppressing the retention of the liquid refrigerant in each pass when used as a condenser, the outdoor heat exchanger 15 is preferably configured in such an embodiment. However, in the second header internal space forming member 78, the height position of the first thin tube connection opening 73a does not necessarily have to be equal to or lower than the height position of the windward heat transfer tube connection opening 711 located at the lowermost position.

(11-5) Modification 5
Although not particularly described in the above embodiment, regarding the height position of the shunt main body 95 in the installed state, the height h2 of the communicating portion with the first thin tube 93 of the main body internal space SP3 is located at the lowermost position. It may be set so as to be located below the height position of the upper end of the second header internal space SP1. This further suppresses the retention of the liquid refrigerant in each pass when used as a condenser.

(11-6) Modification 6
In the above embodiment, it can be interpreted that a plurality of second header internal space forming members 78 (“second shunting portion” described in the claims) forming the second header internal space SP1 are assembled together. The second header tube 70 of the above was arranged between the heat exchange unit 40 and the shunt 90.
However, in the outdoor heat exchanger 15, the member forming the space corresponding to the second header internal space SP1 (that is, the member corresponding to the second header internal space forming member 78) is arranged other than the second header pipe 70. May be done.

For example, one or more members (for example, a header pipe or the like) forming at least one space corresponding to the second header internal space SP1 between the heat exchange unit 40 and the flow divider 90 replaces the second header pipe 70. It may be arranged together with the second header tube 70. In such a case, the member corresponds to the "second diversion portion" described in the claims.

Further, for example, between the heat exchange unit 40 and the shunt 90, the shunt mechanism for shunting the refrigerant to any / all of the plurality of paths (RP1-RP13) replaces the second header pipe 70 / the second header. It may be arranged together with the tube 70.

(11-7) Modification 7
In the above embodiment, 10 passes are formed in the outdoor heat exchanger 15. However, the number of paths formed in the outdoor heat exchanger 15 can be appropriately changed according to the design specifications and the installation environment. For example, in the outdoor heat exchanger 15, 11 or more paths may be formed, or less than 10 paths may be formed. Further, the number of the second header internal space SP1 and the number of the first thin tubes 93 formed in the second header tube 70 may be appropriately changed according to the number of paths.

(11-8) Modification 8
The mode of forming the path in the above embodiment can be changed as appropriate. For example, the number of heat transfer tubes 41 included in each path can be individually and appropriately changed as long as it does not contradict the idea described in (10-1) above. Further, for example, the number of the upper second header internal space SA formed in the outdoor heat exchanger 15, the number of the middle second header internal space SB, and the number of the lower second header internal space SC are appropriately changed. Is possible. For example, the number of upper second header internal spaces SA in the outdoor heat exchanger 15 is not limited to 4, and may be 1 or more and 3 or less, or may be 5 or more. Further, the number of the middle stage second header internal space SBs in the outdoor heat exchanger 15 is not limited to 4, and may be 1 or more and 3 or less, or may be 5 or more. Further, the number of the lower second header internal space SCs in the outdoor heat exchanger 15 is not limited to 5, and may be 1 or more and 4 or less, or 6 or more.

(11-9) Modification 9
In the above embodiment, the thirteenth pass RP13 is formed so as to include the upper thirteenth pass RP13a and the lower thirteenth pass RP13b. However, the thirteenth pass RP13 does not necessarily have to be formed in such an embodiment, and the lower thirteenth pass RP13b may be omitted in the thirteenth pass RP13. In such a case, the first header subspace S2, the second header subspace SPA, the second thin tube 94, and the like may be omitted.

(11-10) Modification 10
The arrangement position of each part of the outdoor heat exchanger 15 in the above embodiment may be changed as appropriate. For example, in the above embodiment, the first header pipe 50, the gas side collecting pipe 60, the second header pipe 70 and the diversion device 90 are arranged in the vicinity of one end of the heat exchange section 40, and the folded header 80 is the heat exchange section 40. Although it was arranged near the other end, the first header pipe 50, the gas side collecting pipe 60, the second header pipe 70 and the diversion device 90 were arranged near the other end of the heat exchange section 40, and the folded header 80 was the heat exchange section. It may be arranged near one end of 40. Further, for example, the arrangement positions of the windward side heat exchange unit 40a and the leeward side heat exchange unit 40b may be exchanged. That is, the leeward heat exchange portion 40a may be arranged on the leeward side (or inside), and the leeward heat exchange portion 40b may be arranged on the leeward side (or outside).

(11-11) Modification 11
The gas side collecting pipe 60 in the above embodiment may be omitted as appropriate. In such a case, for example, the seventh pipe P7 may be connected to the first header pipe 50. In this case, the first header tube 50 corresponds to the "third tube" described in the claims.

(11-12) Modification 12
In the above embodiment, the outdoor heat exchanger 15 has two heat exchange units 40 (windward side heat exchange unit 40a and leeward side heat exchange unit 40b). However, the configuration mode of the outdoor heat exchanger 15 is not necessarily limited to such a mode, and can be appropriately changed. For example, the outdoor heat exchanger 15 may have three or more heat exchange units 40. In such a case, the heat exchange units 40 may be arranged along the flow direction of the outdoor air flow AF, or may be arranged in another manner.

Further, for example, the outdoor heat exchanger 15 may be configured to have only a single heat exchanger 40. In such a case, the folded header 80 may be omitted and the first header tube 50 may be connected to the end of the windward heat transfer tube 41a. In such an example, the space in the first header tube 50 may be partitioned for each path (in that case, each partitioned space corresponds to the "third space" described in the claims, and the first Each portion forming each space of the header tube 50 corresponds to a "third diversion portion").

(11-13) Modification 13
In the above embodiment, the outdoor heat exchanger 15 is configured to have a substantially U-shape or a substantially C-shape in a plan view. That is, the outdoor heat exchanger 15 is configured such that the heat exchange unit 40 has three surfaces that mainly intersect with each other in the flow direction of the outdoor air flow AF. However, the configuration mode of the outdoor heat exchanger 15 is not necessarily limited to such a mode, and can be appropriately changed.

For example, the outdoor heat exchanger 15 may be configured to have a substantially L-shape or a substantially V-shape in a plan view. That is, the outdoor heat exchanger 15 may be configured so that the heat exchange unit 40 has two surfaces intersecting with each other in the flow direction of the outdoor air flow AF.

Further, for example, the outdoor heat exchanger 15 may be configured to have a substantially I shape in a plan view. That is, the outdoor heat exchanger 15 may be configured such that the heat exchange unit 40 has a single surface that intersects the flow direction of the outdoor air flow AF.

Further, for example, the outdoor heat exchanger 15 may be configured so that the heat exchange unit 40 has four or more surfaces intersecting with each other in the flow direction of the outdoor air flow AF.

(11-14) Modification 14
In the above embodiment, a plurality of flow paths 411 are formed in the heat transfer tube 41. However, the present invention is not limited to this, and a flat tube having a single flow path 411 formed may be used as the heat transfer tube 41.

(11-15) Modification 15
In the above embodiment, the heat exchange unit 40 includes 97 heat transfer tubes 41. However, the number of heat transfer tubes 41 included in the heat exchange unit 40 can be appropriately changed, and may be 98 or more, or less than 97.

(11-16) Modification 16
In the above embodiment, the case where each part included in the outdoor heat exchanger 15 is made of aluminum or an aluminum alloy has been described. However, not all of the parts included in the outdoor heat exchanger 15 need to be made of aluminum or an aluminum alloy. For example, any portion may be composed of another metal (for example, a material such as steel) or another material (for example, a resin or the like).

(11-17) Modification 17
In the above embodiment, the outdoor heat exchanger 15 is configured such that the linear distance D1 between the shunt 90 and the second header internal space forming member 78 in a plan view is 100 mm or less in the installed state. From the viewpoint of improving compactness, it is preferable to set D1 to a small value. However, the value is not necessarily limited to this, and the value of the linear distance D1 between the shunt 90 and the second header internal space forming member 78 in a plan view can be appropriately changed.

(11-18) Modification 18
In the outdoor heat exchanger 15 according to the above embodiment, the plurality of second openings 95b are arranged in an annular shape at intervals. With respect to a heat exchanger having a shunt 90 in which a large number of first thin tubes 93 extend downward from the shunt main body 95, from the viewpoint of concentrating a large number of first thin tubes 93 while ensuring a clearance between adjacent first thin tubes 93. According to this, it is preferable that the plurality of second openings 95b are arranged in such an embodiment. However, the arrangement mode of the second opening 95b is not necessarily limited to this, and can be changed as appropriate.

(11-19) Modification 19
In the outdoor heat exchanger 15 according to the above embodiment, more than half of the first thin tubes 93 out of the plurality of first thin tubes 93 extend downward from the main body internal space SP3 and then bend and shunt in the installed state. It was an upward curved pipe 93a that was adjacent to the vessel body 95 and extended in the upward direction. In this respect, the number of the upper curved pipes 93a is not necessarily limited to that in the above embodiment, and can be changed as appropriate. That is, the number of the upper curved pipes 93a included in the shunt 90 may be 9 or more or less than 8.

(11-20) Modification 20
In the outdoor heat exchanger 15 according to the above embodiment, in the installed state, the upper curved pipe 93a extends in the upward direction adjacent to the shunt main body 95, then curves again and extends toward the inlet / outlet pipe 91. Further curved and extends along the upward direction adjacent to the inlet / outlet pipe 91. In this respect, the configuration of the upper curved pipe 93a is not necessarily limited to that of the above embodiment, and can be appropriately changed according to the design specifications and the installation environment.

(11-21) Modification 21
In the outdoor heat exchanger 15 according to the above embodiment, a plurality of upward curved pipes 93a are arranged at intervals in the circumferential direction of the entrance / exit pipe 91 in a plan view in the installed state. From the viewpoint of making the shunt 90 compact, it is preferable that a plurality of upward curved pipes 93a are arranged in such an embodiment. However, the configuration of the upper curved pipe 93a is not necessarily limited to that of the above embodiment, and can be appropriately changed according to the design specifications and the installation environment.

(11-22) Modification 22
In addition, the formation mode (position, shape, size, etc.) of each part of the outdoor heat exchanger 15 in the above embodiment is not necessarily limited to the mode in the above embodiment, and the idea described in the above (10-1). As long as there is no contradiction, it can be changed as appropriate according to the design specifications.

(11-23) Modification 23
The configuration of the refrigerant circuit RC in the above embodiment can be appropriately changed according to the design specifications and the installation environment. For example, instead of a part of the equipment included in the refrigerant circuit RC / the equipment included in the refrigerant circuit RC may include equipment not shown in FIG. Further, for example, a part of the equipment included in the refrigerant circuit RC (for example, the accumulator 11 or the like) may be omitted as long as it does not cause any trouble.

(11-24) Modification 24
In the above embodiment, the outdoor heat exchanger 15 is applied to the outdoor unit 10 in which the air flow flows in from the side and flows out upward. However, the outdoor heat exchanger 15 may be applied to other units. For example, the outdoor heat exchanger 15 may be applied to a trunk type outdoor unit 10 in which an air flow flows in from the side and flows out to the front side. Further, for example, the outdoor heat exchanger 15 may be applied as the indoor heat exchanger 22 in the indoor unit 20.

(11-25) Modification 25
In the above embodiment, the case where the outdoor heat exchanger 15 is applied to the air conditioning system 1 has been described. However, the outdoor heat exchanger 15 can also be applied to other refrigerating devices (hot water supply devices, heat pump chillers, etc.).

(12)
Although the embodiments have been described above, it will be understood that various modifications of the embodiments and details are possible without departing from the spirit and scope described in the claims.

The present disclosure is available for heat exchangers, or air conditioning indoor units with heat exchangers.

1: Air conditioning system (refrigerator)
10: Outdoor unit 12: Compressor 15: Outdoor heat exchanger (heat exchanger)
18: Outdoor fan 20: Indoor unit 30: Outdoor unit casing 40: Heat exchange unit 40a: Upwind heat exchange unit 40b: Downwind side heat exchange unit 41: Heat transfer tube (flat tube)
41a: Upwind heat transfer tube 41b: Downwind side heat transfer tube 42: Heat transfer fin 50: First header tube 51: Downwind heat transfer tube side member 52: First header partition member 53: Collective tube side member 54: First partition plate 55 : 2nd partition plate 60: Gas side collecting pipe (3rd pipe)
61: Connection pipe 62: Bundling band 70: Second header pipe 71: Upwind heat transfer tube side member 72: Second header partition member 72a: First communication opening 72b: Second communication opening 73: Shunt side member 73a: First 1 Thin tube connection openings 74, 74a: Partition plate 75: Straightening plate 75a: Third communication opening 78: Second header internal space forming member (second shunt portion)
80: Folded header 81: Upwind opening 82: Downwind opening 88: Folded space forming member (third diversion part)
90: Shunt (1st shunt)
91: Doorway pipe (first pipe)
93: 1st thin tube (2nd tube)
93a: Upper curved tube 94: Second thin tube 95: Shunt body (main body)
95a: 1st opening 95b: 2nd opening 100: Jig 411: Flow path 511: Downwind heat transfer tube connection opening 711: Upwind heat transfer tube connection opening 951: Top surface 952: Bottom surface 953: Contact AF: Outdoor air flow P1-P9: 1st pipe-9th pipe RC: Refrigerant circuit RP1-RP13: 1st pass-13th pass RP13a: Upper 13th pass RP13b: Lower 13th pass S1: 1st header main space S2: 1st Header subspace SA: Upper second header internal space SB: Central second header internal space (central second space)
SC: Lower second header internal space (lower second space)
SPa: Second header subspace SP1: Second header internal space (second space)
SP2: Folding space (third space)
SP3: Main body internal space (first space)

International Publication WO2013 / 160952

Claims (10)

A heat exchange unit (40) including a plurality of flat tubes (41) arranged along the vertical direction in the installed state, and
A first pipe (91) through which refrigerant enters and exits, a plurality of second pipes (93) forming a refrigerant flow path on the heat exchange portion side of the first pipe, one end of the first pipe, and each of the first pipes. A first having a main body portion (95) formed inside a first space (SP3) that communicates with one end of two pipes and allows a refrigerant flowing out from one of the first pipe and the second pipe to flow into the other. Divided flow section (90) and
The flat tube and the corresponding flat tube that form a refrigerant flow path between the heat exchange section and the first diversion section, communicate with one end of the corresponding flat tube, and communicate with the other end of each corresponding second tube. A plurality of second diversion portions (78) having a second space (SP1) in which the refrigerant flowing out from one of the second pipes flows into the other,
Equipped with
In the installed state, three or more of the second spaces are arranged along the vertical direction, and the number of the flat tubes communicating with the central second space (SB), which is the central second space, is larger than the number of the central second spaces. The number of the flat tubes communicating with the lower second space (SC), which is the second space located below, is smaller.
Heat exchanger (15). A third pipe (60), which is a refrigerant outlet pipe when the first pipe is a refrigerant inlet pipe, and a refrigerant inlet pipe when the first pipe is a refrigerant outlet pipe,
At least one third diversion flow in which a refrigerant flow path is formed between the second diversion portion and the third pipe, and a third space (SP2) communicating with the other end of the corresponding flat pipe is formed inside. Part (88) and
Further prepare
The third space is
Communicate with one end of the third pipe or the second flat pipe arranged in the same stage as the flat pipe,
When the first pipe is an inlet pipe for the refrigerant, it is a space for flowing the refrigerant flowing out from the other end of the flat pipe into the third pipe or the second flat pipe.
When the first pipe is an outlet pipe for the refrigerant, it is a space for flowing the refrigerant flowing out from one end of the third pipe or the second flat pipe into the flat pipe.
The heat exchanger (15) according to claim 1. The heat exchange unit exchanges heat between the refrigerant in the flat tube and the air flow (AF).
In the installed state, the circumference of the flat pipe communicating with the second space above the lower second space with respect to the wind speed of the air flow passing around the flat pipe communicating with the lower second space. The wind speed of the air flow passing through is higher,
The heat exchanger (15) according to claim 1 or 2. The lower second space is arranged at a height position of 1/3 or less of the total height of the heat exchange unit in the installed state.
The heat exchanger (15) according to any one of claims 1 to 3. The flat tube located at the lowest stage in the installed state communicates with the second space on the lower stage side.
The heat exchanger (15) according to any one of claims 1 to 4. In the installed state, a plurality of the lower second spaces are lined up along the vertical direction.
The heat exchanger (15) according to any one of claims 1 to 5. In the installed state, a plurality of the central second spaces are lined up along the vertical direction.
The heat exchanger (15) according to any one of claims 1 to 6. One end of the first pipe is connected to the main body so as to extend downward from the first space in the installed state.
One end of the second pipe is connected to the main body so as to extend upward from the first space in the installed state.
The heat exchanger (15) according to any one of claims 1 to 7. One end of the first pipe is connected to the main body so as to extend upward from the first space in the installed state.
One end of the second pipe is connected to the main body portion so as to extend downward from the first space in the installed state.
The heat exchanger (15) according to any one of claims 1 to 7. A compressor (12) that compresses the refrigerant,
The heat exchanger (15) according to any one of claims 1 to 9, and the heat exchanger (15).
To prepare
Refrigerator (1).

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