CN111656125A - Heat exchanger or refrigeration unit with heat exchanger - Google Patents

Abstract

Retention of liquid refrigerant is suppressed. The outdoor heat exchanger (15) has a heat exchange part (40) including a plurality of heat transfer tubes (41), a flow divider (90), and a refrigerant forming between the heat exchange part (40) and the flow divider (90) The plurality of second header inner space forming members (78) of the flow path. The flow divider (90) has an inlet and outlet pipe (91), a plurality of first thin tubes (93), and a flow divider main body (95) in which a main body inner space (SP3) is formed, and the main body inner space (SP3) is connected with the inlet and outlet pipes ( 91) is communicated with the first narrow pipe (93), and the refrigerant flows from one side to the other side. The second header inner space forming member (78) forms a second header inner space (SP1), the second header inner space (SP1), the corresponding heat transfer tubes (41) and the first thin tubes (93) communication, so that the refrigerant flows from one side to the other side. In the installed state, three or more second header inner spaces (SP1) are aligned in the vertical direction, and the number of heat transfer tubes (41) communicating with the middle-level second header inner space (SB) is more The number of heat transfer tubes (41) communicating with the lower second header inner space (SC) is small.

Description

Heat exchanger or refrigeration unit with heat exchanger

technical field

The present invention relates to a heat exchanger or a refrigeration unit having a heat exchanger.

Background technique

Conventionally, as disclosed in, for example, Patent Document 1 (International Publication No. WO 2013/160952 ), a heat exchanger is known which includes a heat exchange portion in which a plurality of flat tubes are arranged in parallel, a flow divider arranged at a liquid-side end portion, and a header disposed between the heat exchange part and the flow divider. In this heat exchanger, in the header, a plurality of spaces are formed so as to be lined up in the direction in which the flat tubes are stacked, and each space communicates with the corresponding flat tubes. In addition, each space in the header and the diverter are connected by thin tubes. In the heat exchanger thus constituted, a plurality of paths (refrigerant flow paths) are formed.

SUMMARY OF THE INVENTION

The problem to be solved by the invention

In such a heat exchanger as described above, in the installed state, the flat tubes are often arranged so as to be lined up in the vertical direction. In this case, when used as a condenser, the liquid refrigerant tends to stay in the flat tubes (paths) arranged in the vicinity of the lowermost layer in relation to the pressure head difference caused by the installation height of the flow divider. Provided is a heat exchanger that suppresses the retention of liquid refrigerant.

means of solving problems

The heat exchanger of the first aspect includes a heat exchange part, a first branching part, and a plurality of second branching parts. The heat exchange part includes a plurality of flat tubes. The plurality of flat tubes are aligned in the vertical direction in the installed state. The 1st branch part has a 1st pipe, a some 2nd pipe, and a main-body part. The first pipe is a pipe through which the refrigerant is taken in and out. The second tube forms a refrigerant flow path on the heat exchange portion side relative to the first tube. The main body portion has a first space formed therein. The first space communicates with one end of the first pipe and one end of each of the second pipes. The first space allows the refrigerant flowing out of one of the first tube and the second tube to flow into the other. The second branching portion forms a refrigerant flow path between the heat exchange portion and the first branching portion. A second space is formed inside the second branch. 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 from one of the corresponding flat tubes and the second tube to flow into the other. The three or more second spaces are arranged in the vertical direction in the installed state. The number of flat tubes communicated with the lower second space is smaller than the number of flat tubes communicated with the central second space. The center second space is the center second space in the installation state. The second space on the lower floor side is a second space below the center second space in the installation state.

In the heat exchanger according to the first aspect, in the installed state, three or more second spaces are arranged in the vertical direction, and the number of flat tubes communicated with the central second space (the second space located in the center) is equal to the number of flat tubes. In comparison, the number of the flat tubes communicating with the lower second space (the second space below the central second space) is small. Thereby, when it is used as a condenser, the fall of the head (head) of the liquid refrigerant in the 1st space is accelerated. In connection with this, when used as a condenser, a favorable flow of the refrigerant is promoted in the flat multi-hole tube (the lower path) communicating with the lower-layer side second space where the liquid refrigerant tends to stay. As a result, when used as a condenser, the liquid refrigerant is suppressed from staying.

In addition, the "central second space" here refers to the second space arranged between the second space on the uppermost floor and the second space on the lowermost floor among the plurality of second spaces arranged in the vertical direction in the installed state. space. The "central second space" includes at least a space located at a height of at least one third from the lower end of the overall height dimension of the heat exchanger and less than one third from the upper end in the installed state. The number of "central second spaces" is appropriately selected according to the number of second spaces.

In addition, the "second space on the lower floor side" here refers to the second space arranged at the lowermost floor, including the second space arranged at the lowermost floor, among the plurality of second spaces arranged in the vertical direction in the installation state, and the second space arranged at a lower position than the center. The second space below. The number of "central second spaces" is appropriately selected according to the number of second spaces.

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

Heat Exchanger of a Third Aspect In the heat exchanger of the first aspect or the second aspect, the heat exchange portion exchanges heat between the refrigerant in the flat tubes and the air flow. In the installation state, the air flow around the flat tubes communicating with the second space above the lower-level second space is compared with the wind speed of the air flow passing around the flat tubes communicating with the lower-level second space. wind speed is high.

Heat Exchanger of a Fourth Aspect In the heat exchanger of any one of the first to third viewpoints, the second space on the lower layer side is arranged at or less than one third of the height of the entire heat exchange portion in the installed state height position.

Heat Exchanger of a Fifth Aspect In the heat exchanger of any one of the first to fourth viewpoints, the flat tube located at the lowermost layer in the installed state communicates with the second space on the lower layer side.

A heat exchanger according to a sixth aspect In the heat exchanger according to any one of the first to fifth aspects, in the installed state, the plurality of lower-layer side second spaces are aligned in the vertical direction.

A heat exchanger according to a seventh aspect In the heat exchanger according to any one of the first to sixth aspects, in the installed state, the plurality of center second spaces are arranged in a vertical direction.

Heat Exchanger of Eighth Aspect In the heat exchanger of any one of the first to seventh viewpoints, 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. department. In the installed state, one end of the second pipe is connected to the main body portion so as to extend upward from the first space.

Heat Exchanger of Ninth Aspect In the heat exchanger of any one of the first to seventh viewpoints, 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. department. 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.

The refrigeration apparatus of the tenth viewpoint includes a compressor and a heat exchanger of any one of the first to ninth viewpoints. The compressor compresses the refrigerant.

Description of drawings

FIG. 1 is a schematic configuration diagram of an air conditioning system.

FIG. 2 is a perspective view of the outdoor unit.

Fig. 3 is a schematic exploded view of the outdoor unit.

FIG. 4 is a schematic diagram showing the arrangement of the devices arranged on the bottom frame and the flow direction of the outdoor air flow.

FIG. 5 is a schematic diagram showing the manner in which the flow of outdoor air flows within the outdoor unit casing.

Fig. 6 is a perspective view of the outdoor heat exchanger.

Fig. 7 is a perspective view of the outdoor heat exchanger viewed from a direction different from that of Fig. 6 .

FIG. 8 is a schematic diagram of the outdoor heat exchanger in a plan view.

FIG. 9 is a schematic diagram of a heat exchange part.

FIG. 10 is a partial enlarged view of the X-X line section in FIG. 8 .

Fig. 11 is an exploded view of the first header and the gas-side header.

Fig. 12 is an exploded view of the second header.

FIG. 13 is an enlarged view showing a part of the second header shown in FIG. 12 .

FIG. 14 is an enlarged view showing a part of the second partition member to which the partition plate and the rectifier plate are attached.

FIG. 15 is a view of the second header viewed from above.

Fig. 16 is a schematic diagram showing a partial cross section of the second header in an enlarged manner.

Fig. 17 is a perspective view of the folded header.

Fig. 18 is a cross-sectional view of the folded header taken along the horizontal direction.

19 is an enlarged cross-sectional view of a part of the turn-back header cut in the vertical direction.

Fig. 20 is a perspective view of the diverter.

FIG. 21 is an enlarged view of a portion A surrounded by a two-dot chain line in FIG. 20 .

FIG. 22 is an enlarged view schematically showing a cross section of the diverter body cut along the vertical direction.

Fig. 23 is a perspective view of the diverter body and the liquid side inlet and outlet pipes.

Figure 24 is a perspective view of the diverter body.

Fig. 25 is a view of the diverter main body viewed from the top surface side.

Fig. 26 is a view of the diverter main body viewed from the bottom surface side.

FIG. 27 is an enlarged view showing the surroundings of the diverter main body viewed from the horizontal direction.

FIG. 28 is an enlarged view showing the state of FIG. 27 viewed from a different direction.

FIG. 29 is a schematic diagram showing an example of a tool used when moving the diverter body in the furnace.

30 is a schematic diagram showing the positional relationship of the first header, the gas-side header, the second header, and the flow divider in a plan view.

Fig. 31 is a schematic diagram schematically showing each path of the outdoor heat exchanger viewed from the windward side.

32 is a schematic diagram schematically showing each path of the outdoor heat exchanger as viewed from the leeward side.

Detailed ways

Next, the outdoor heat exchanger 15 (heat exchanger) and the air conditioning system 1 (refrigeration apparatus) according to one embodiment of the present invention will be described. In addition, the following embodiment is a specific example, Comprising: It does not limit a technical scope, It can change suitably in the range which does not deviate from the summary. In addition, in the following description, unless otherwise specified, "up", "down", "left", "right", "front", "rear", "front", "rear", "up-down direction" , "left-right direction", "vertical direction", and "horizontal direction" mean the directions shown in the figures, and indicate the directions in the installed state (in addition, the left-right and/or front-rear in the following embodiments may be appropriately reversed ).

The outdoor heat exchanger 15 according to one embodiment of the present invention is applied to the outdoor unit 10 , which is a 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 (a living space or an air-conditioned space such as a storage room) by a vapor compression refrigeration cycle. The air-conditioning system 1 mainly includes an outdoor unit 10, a plurality of (two in this case) indoor units 20, and a liquid-side communication pipe LP and a gas-side communication pipe GP.

In the air-conditioning system 1, the outdoor unit 10 and each indoor unit 20 are connected via the liquid-side communication pipe LP and the gas-side communication pipe GP, thereby constituting a refrigerant circuit RC. In the air conditioning system 1, the following refrigeration cycle is performed in the refrigerant circuit RC: the refrigerant is compressed, cooled or condensed, decompressed, heated or evaporated, and then compressed again.

(1-1) Outdoor unit 10

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

The first piping P1 connects the gas-side communication piping GP and the first port of the four-way switching valve 14 . The second piping P2 connects the inlet port of the gas-liquid separator 11 and the second port of the four-way switching valve 14 . The third piping P3 connects the outlet port of the gas-liquid separator 11 and the suction port of the compressor 12 . The fourth piping P4 connects the discharge port of the compressor 12 and the inlet of the oil separator 13 . The fifth piping P5 connects the outlet of the oil separator 13 and the third port of the four-way switching valve 14 . The sixth piping P6 connects the oil return port of the oil separator 13 and a portion between both ends of the third piping P3. The seventh piping P7 connects the fourth port of the four-way switching valve 14 and the gas-side inlet and outlet of the outdoor heat exchanger 15 . The eighth piping P8 connects the liquid side inlet and 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 and the liquid-side communication pipe LP. In addition, these refrigerant pipes ( P1 - P9 ) may actually be constituted by a single pipe, or may be constituted by connecting a plurality of pipes via a joint or the like.

The gas-liquid separator 11 is a container that stores the refrigerant and performs gas-liquid separation in order to prevent the liquid refrigerant from being excessively drawn into the compressor 12 .

The compressor 12 is a device that compresses the low-pressure refrigerant in the refrigeration cycle until it becomes high pressure. In the present embodiment, the compressor 12 has a hermetic structure in which a rotary or scroll equal-volume compression element is rotationally driven by a compressor motor (not shown). The operation frequency of the compressor motor can be controlled by the inverter, and thus the capacity control of the compressor 12 can be performed. The start-stop and operation capacity of the compressor 12 are controlled by the outdoor unit control unit 19 .

The oil separator 13 is a container that separates refrigerating machine oil 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 condenser (or a radiator) or an evaporator of the refrigerant. Details of the outdoor heat exchanger 15 will be described later.

The outdoor expansion valve 16 is an electric expansion valve whose opening degree can be controlled, and decompresses or adjusts the flow rate of the refrigerant flowing in according to the opening degree.

Further, the outdoor unit 10 includes 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 into the outdoor unit 10 from outside 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 of 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 .

In addition, the outdoor unit 10 is provided with a plurality of outdoor side 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 thermocouple. The outdoor side sensors include, for example, a suction pressure sensor that detects the pressure of the refrigerant on the suction side of the compressor 12 , that is, the suction pressure, a discharge pressure sensor that detects the pressure of the refrigerant on the discharge side of the compressor 12 , that is, the discharge pressure, and A temperature sensor or the like for the temperature of the refrigerant in the outdoor heat exchanger 15 .

Further, the outdoor unit 10 includes 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 including a CPU, a memory, and the like, and various electrical 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 side sensor, and performs signal input and output with each other. In addition, the outdoor unit control unit 19 transmits and receives control signals and the like with the indoor unit control unit 25 of each indoor unit 20 or a remote controller (not shown). The outdoor unit control unit 19 is housed in an electrical installation box 39 (see FIGS. 3 and 4 ) to be described later.

Details of the outdoor unit 10 will be described later.

(1-2) Indoor unit 20

The indoor unit 20 is installed indoors (a living room, a space behind a ceiling, 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 side circuit RC2.

The indoor expansion valve 21 is an electric expansion valve whose opening degree can be controlled, and decompresses or adjusts the flow rate of the refrigerant flowing in according to the opening degree.

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

In addition, the indoor unit 20 has an indoor fan 23 for sucking in the air in the target space, making it pass through the indoor heat exchanger 22 to exchange heat with the refrigerant, and then sending it to the target space again. The indoor fan 23 includes an indoor fan motor as a drive source. The indoor fan 23 generates indoor air flow when driven. The indoor air flow is a flow of air that flows into the indoor unit 20 from the target space, 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 exchanges heat with the refrigerant in the indoor heat exchanger 22 when passing through the indoor heat exchanger 22 .

Moreover, the indoor unit 20 has the indoor unit control part 25 which controls the operation/state of the equipment (21, 23, etc.) contained in the indoor unit 20. The indoor unit control unit 25 includes a microcomputer including a CPU, a memory, and the like, and various electrical components.

(1-3) Liquid side communication piping LP, gas side communication piping GP

The liquid-side communication pipe LP and the gas-side communication pipe GP are refrigerant communication pipes that connect the outdoor unit 10 and each indoor unit 20, and are constructed on site. The piping length and piping diameter of the liquid-side communication piping LP and the gas-side communication piping GP are appropriately selected according to the design specifications and the installation environment. In addition, the liquid-side communication pipe LP and the gas-side communication pipe GP may actually be constituted by a single pipe, or may be constituted by connecting a plurality of pipes via a joint or the like.

(2) Flow of the refrigerant in the refrigerant circuit RC

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

(2-1) Flow of refrigerant during normal cycle operation

During normal cycle operation (operation such as cooling operation, refrigeration cycle defrosting operation, etc.), the four-way switching valve 14 is controlled to be in the forward-circulating state (the state shown by the solid line of the four-way switching valve 14 in FIG. 1 ). When the normal cycle operation is started, the refrigerant is sucked into the compressor 12 in the outdoor-side circuit RC1, compressed, and then discharged. In the compressor 12, capacity control according to the heat load required by the indoor unit 20 in operation is performed. Specifically, the target value of the suction pressure is set according to the heat load required by the indoor unit 20, and the operation 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 that has flowed 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, and radiates heat and condenses. The refrigerant flowing out of the outdoor heat exchanger 15 flows into the indoor-side circuit RC2 of the indoor unit 20 in operation via the liquid-side communication pipe LP.

The refrigerant flowing into the indoor side circuit RC2 of the operating indoor unit 20 flows into the indoor expansion valve 21 , is decompressed according to the opening degree of the indoor expansion valve 21 until it becomes a low pressure in the refrigeration cycle, and then flows into the indoor heat exchanger 22 . The refrigerant that has flowed into the indoor heat exchanger 22 exchanges heat with the flow of indoor air sent by the indoor fan 23 and evaporates, becomes a gas refrigerant, and flows out of the indoor heat exchanger 22 . The gas refrigerant that has flowed out of the indoor heat exchanger 22 flows out of the indoor side circuit RC2.

The refrigerant flowing out of the indoor-side circuit RC2 flows into the outdoor-side circuit RC1 via the gas-side communication pipe GP. The refrigerant that has flowed into the outdoor-side circuit RC1 flows into the gas-liquid separator 11 . After the refrigerant that has flowed into the gas-liquid separator 11 temporarily stays, it is sucked into the compressor 12 again.

(2-2) Flow of Refrigerant During Reverse Cycle Operation

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

The refrigerant that has flowed into the indoor-side circuit RC2 flows into the indoor heat exchanger 22, and is condensed by exchanging heat with the flow of indoor air sent by the indoor fan 23. The refrigerant flowing out of the indoor heat exchanger 22 flows into the indoor expansion valve 21, is decompressed or adjusted in flow rate according to the opening degree of the indoor expansion valve 21, and then flows out of the indoor side circuit RC2.

The refrigerant flowing out of the indoor-side circuit RC2 flows into the outdoor-side circuit RC1 through the liquid-side communication pipe LP. The refrigerant flowing into the outdoor side circuit RC1 flows into the outdoor expansion valve 16 , is decompressed according to the opening degree of the outdoor expansion valve 16 to a low pressure in the refrigeration cycle, and then flows into the liquid side inlet and outlet of the outdoor heat exchanger 15 .

The refrigerant that has flowed into the outdoor heat exchanger 15 is evaporated 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 of the gas-side inlet and outlet of the outdoor heat exchanger 15 flows into the gas-liquid separator 11 . After the refrigerant that has flowed into the gas-liquid separator 11 temporarily stays, it is 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 has an outdoor unit casing 30 that constitutes an outer casing and accommodates each device (11-16, etc.). The outdoor unit casing 30 is formed in 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 taking in the outdoor air flow AF.

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

The mounting legs 31 are sheet metal members that extend in the left-right direction and support the bottom frame 33 from below. In the outdoor unit casing 30, attachment legs 31 are arranged in the vicinity of the front end and the vicinity of the rear end.

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

The pillars 35 extend in the vertical direction from the corner portions of the bottom frame 33 . In FIG. 2-3, the state which the support|pillar 35 extended in the vertical direction from each of four corner parts of the bottom frame 33 is shown.

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 support column 35 . The fan module 38 constitutes portions of the front, rear, left and right sides of the outdoor unit casing 30 above the pillars 35 , and the top surface of the outdoor unit casing 30 . The fan module 38 includes the outdoor fan 18 and the bell mouth 381 . More specifically, the fan module 38 is an assembly in which the outdoor fan 18 and the bell mouth 381 are accommodated in a substantially rectangular parallelepiped-shaped box whose upper and lower surfaces are open. In the fan module 38, the outdoor fan 18 is arranged in a posture in which the rotation axis extends in the vertical direction. The upper surface of the fan module 38 is partially open, and functions as an outlet 302 from which the outdoor air flow AF is blown out from the outdoor unit casing 30 . The air outlet 302 is provided with a grid-shaped grill 382 .

2-3 shows an example in which the outdoor unit 10 includes one fan module 38 , the outdoor unit 10 may include a plurality of fan modules 38 . For example, two fan modules 38 may be arranged side by side. In this case, the outdoor unit 10 may be configured to include the outdoor unit casing 30 larger in size than the outdoor unit 10 including one fan module 38 and to have one front panel 37 on each of the left and right sides. In addition, in this case, depending on the size of the outdoor unit casing 30, the size of the outdoor heat exchanger 15 may be configured to be large.

(3-2) Devices arranged on the bottom frame 33

FIG. 4 is a diagram schematically showing the arrangement of devices arranged on the bottom frame 33 and the flow direction of the outdoor air flow AF. As shown in FIG. 4 , on the bottom frame 33 , various devices including the gas-liquid separator 11 , the compressor 12 , the oil separator 13 , and the outdoor heat exchanger 15 are arranged at predetermined positions. In addition, an electrical installation box 39 in which the outdoor unit control unit 19 is accommodated is arranged on the bottom frame 33 .

The outdoor heat exchanger 15 has the heat exchange part 40 (refer FIG. 4) arrange|positioned along the left side surface, the right side surface, and the back surface of the outdoor unit casing 30. As shown in FIG. The heat exchange portion 40 has substantially the same height dimension as the intake port 301 . Most of the rear, left and right sides of the outdoor unit casing 30 are intake ports 301 from which the heat exchange portion 40 of the outdoor heat exchanger 15 is exposed. In other words, it can be said that the rear, left and right sides 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 parts 40 , and has curved portions on the left and right sides (refer to B1 , B2 , and B3 shown in FIG. 8 ) in a plan view, and has a substantially U-shaped opening in the front direction. .

(3-3) Flow of Outdoor Air Flow AF in Outdoor Unit Housing 30

FIG. 5 is a diagram schematically showing how the outdoor air flow AF flows in the outdoor unit casing 30 . As shown in FIGS. 4-5 , the outdoor air flow AF flows into the outdoor unit casing 30 from the air intake ports 301 formed on the left side, right side and back side of the outdoor unit casing 30, and passes through the outdoor heat exchanger 15 (heat exchange After part 40), it flows mainly from the lower side to the upper side, and flows out from the blower outlet 302. That is, the outdoor air flow AF flows into the outdoor unit casing 30 in the horizontal direction through the intake port 301 , passes through the outdoor heat exchanger 15 , turns upward, and flows upward toward the air outlet 302 from below. Regarding the outdoor air flow 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 space below the outdoor fan 18 away from the outdoor fan 18 . In connection therewith, with regard to the outdoor air flow AF passing through the heat exchange portion 40 of the outdoor heat exchanger 15, compared with the air passing through the lower portion (particularly the path lower than the center), the air passing through the upper portion (particularly the path lower than the center) The air in the upper path) has a higher wind speed.

(4) Detailed structure of the 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 viewed from a direction different from that in FIG. 6 . FIG. 8 is a schematic diagram of the outdoor heat exchanger 15 in a plan view.

The outdoor heat exchanger 15 mainly includes a heat exchange unit 40 , a first header 50 , a gas-side header 60 , a second header 70 , a return header 80 , and a flow divider 90 . In this embodiment, the heat exchange part 40 , the first header 50 , the gas-side header 60 , the second header 70 , the return header 80 , and the flow divider 90 are all made of aluminum or an aluminum alloy. The heat exchange part 40 , the first header 50 , the gas side header 60 , the second header 70 , the return header 80 , and the diverter 90 in the temporarily assembled state are welded and joined by solder in a furnace, thereby reducing outdoor heat. The exchanger 15 is assembled.

(4-1) Heat Exchange Unit 40

FIG. 9 is a schematic diagram of the heat exchange unit 40 . FIG. 10 is a partial enlarged view of the X-X line section in FIG. 8 .

The heat exchange part 40 is a part for exchanging heat between the outdoor air flow AF and the refrigerant in the outdoor heat exchanger 15 (heat transfer tubes 41 to be described later). Specifically, the heat exchange portion 40 is a portion extending in a direction intersecting the traveling direction of the outdoor air flow AF at the central portion of the outdoor heat exchanger 15 , and occupies most of the outdoor heat exchanger 15 . The heat exchange part 40 mainly has three heat exchange surfaces, and has a substantially U-shaped or substantially C-shaped shape in plan view (see FIG. 8 ).

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

Each heat exchange part 40 mainly includes a plurality of heat transfer tubes 41 (corresponding to "flat tubes" 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 porous tube in which a plurality of refrigerant flow paths 411 are formed. The heat transfer tube 41 is made of aluminum or aluminum alloy. In the present embodiment, in the installed state, in the heat exchange unit 40, 97 heat transfer tubes 41 are arranged in parallel in the up-down direction (vertical direction). The heat transfer tube 41 extends in the horizontal direction, and extends along the shape of the heat exchange portion 40 in plan view. For convenience of description, the heat transfer tubes 41 included in the windward side heat exchange portion 40a are referred to as upwind side heat transfer tubes 41a, and the heat transfer tubes 41 included in the downwind side heat exchange portion 40b are referred to as leeward side heat transfer tubes 41b. One end of the windward side heat transfer pipe 41 a is connected to the second header 70 , and the other end is connected to the folded header 80 . One end of the leeward side heat transfer pipe 41 b is connected to the first header 50 , and the other end is connected to the folded header 80 .

The heat transfer fins 42 are flat plate-shaped members that increase the heat transfer area between the heat transfer tubes 41 and the flow of outdoor air. The heat transfer fins 42 are made of aluminum or aluminum alloy. The heat transfer fins 42 extend in the vertical direction in the heat exchange portion 40 so as to intersect the heat transfer tubes 41 . A plurality of notches are formed in the heat transfer fins 42 in parallel in the up-down direction, and the heat transfer tubes 41 are inserted into the notches.

In FIGS. 6 and 8 , the double-dot chain arrows show the flow direction of the refrigerant flowing in the heat exchange portion. The two-dot chain arrows are directed in both directions because the flow of the refrigerant is reversed in the heating operation and the cooling operation. In the normal cycle operation, after the refrigerant flows from the second header 70 into the windward side heat exchange part 40a (upwind side heat transfer tube 41a ), it is turned back by the turn-back header 80 and flows from the turn-back header 80 into the leeward side heat exchange part The portion 40b (the leeward side heat transfer tube 41b ) flows and reaches the first header 50 . In the reverse cycle operation, the refrigerant flows from the first header 50 into the leeward side heat exchange portion 40b (the leeward side heat transfer tube 41b ), and then turns back at the turn-back header 80 and flows from the turn-back header 80 into the windward side heat exchange portion The part 40a (upwind side heat transfer tube 41a) flows and reaches the second header 70.

(4-2) First header 50, gas side header 60

FIG. 11 is an exploded view of the first header 50 and the gas-side header 60 . The first header 50 is an elongated hollow cylindrical member extending in the vertical direction with the upper end and the lower end closed. The 1st header 50 is arrange|positioned at one end side of the leeward side heat exchange part 40b. The first header 50 includes a leeward heat transfer tube side member 51 , a first header partition member 52 , a header side member 53 , a plurality of first partition plates 54 and a second partition plate 55 .

The downwind heat transfer tube side member 51, the first header partition member 52, and the manifold side member 53 are separated from each other in a state where the first header partition member 52 is sandwiched between the downwind heat transfer tube side member 51 and the manifold side member 53. Ways to be consistent in the length direction are combined and integrated. In the first header 50 , the upper end and the lower end are closed by two first partition plates 54 . In addition, in the first header 50, the second partition plate 55 is arranged near the lower end, and the inside of the first header 50 is divided into a first header main space S1 and a first header auxiliary space S2 (see FIG. 32 ). ). As shown in FIG. 32 , in the present embodiment, the first header main space S1 communicates with one end of the 96 leeward side heat transfer tubes 41b, and the first header auxiliary space S2 communicates with one leeward side heat transfer tube located at the bottom. One end of the pipe 41b is communicated.

The downwind heat transfer tube side member 51 , the first header partition member 52 , the header side member 53 , the first partition plate 54 and the second partition plate 55 are welded with solder in a furnace to be joined and integrated with each other. change.

The downwind heat transfer tube-side member 51 is a member having an arc-shaped cross-section cut along 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 (the leeward side heat transfer tube 41b) is inserted. The number of the downwind heat transfer pipe connection openings 511 is the same as the number of layers of the heat transfer pipes 41 .

The first header partition member 52 has a plurality of openings (not shown) through which the refrigerant flows from the leeward heat transfer tube side member 51 to the header side member 53 .

The cross section of the manifold side member 53 cut along a plane perpendicular to the vertical direction is arc-shaped. A plurality of openings 531 into which one end of the connection pipe 61 is inserted are formed in the manifold-side member 53 . The connection pipe 61 is a pipe connected to the first header 50 and the gas-side header 60 . The number of the openings 531 is the same as the number of the plurality of connecting pipes 61 arranged side by side in the up-down direction. The opening 531 communicates with the first header main space S1. Further, the manifold-side member 53 is formed with a second capillary connection opening 532 for connecting a second capillary tube 94 (described later) of the flow divider 90 . The second capillary connection opening 532 communicates with the first header auxiliary space S2.

The gas side collecting pipe 60 (corresponding to the "third pipe" described in the claims) is a bottomed cylindrical straight pipe. The gas-side manifold 60 forms a gas-side inlet and outlet in the outdoor heat exchanger 15 . Specifically, the gas-side collecting pipe 60 is an inlet pipe of the refrigerant during normal circulation operation (when the inlet and outlet pipes 91 of the flow divider 90 to be described later are outlet pipes of the refrigerant). In addition, the gas-side collecting pipe 60 is an outlet pipe of the refrigerant during the reverse cycle operation (when the inlet and outlet pipes 91 described later are inlet pipes of the refrigerant). The gas-side manifold 60 is arranged adjacent to the first manifold 50 . The first header 50 and the gas-side header 60 are bound by a binding tape 62 . The gas-side header 60 is located between the first header 50 and the seventh pipe P7 in the refrigerant circuit RC. One end of the seventh pipe P7 is connected to the gas-side manifold 60 . The gas-side header 60 is formed with a plurality of openings (not shown) on the side surface for connecting the other end of the connection pipe 61 (extended to the first header 50 ).

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

(4-3) Second header 70

FIG. 12 is an exploded view of the second header 70 . FIG. 13 is an enlarged view showing a part of the second header 70 shown in FIG. 12 . FIG. 14 shows an enlarged view of a part of the second header partition member 72 to which the partition plate 74 and the baffle plate 75 are attached. FIG. 15 is a view of the second header 70 viewed from above. FIG. 16 is an enlarged schematic view of a part of the cross section of the second header 70 .

The second header 70 is an elongated hollow cylindrical member extending in the vertical direction with the upper end and the lower end closed. The second header 70 is arranged on one end side of the windward side heat exchange portion 40a. The second header 70 includes an upwind heat transfer tube side member 71 , a second header partition member 72 , a flow divider side member 73 , a plurality of partition plates 74 , and a plurality of rectifier plates 75 . The upwind heat transfer tube side member 71 , the second header partition member 72 and the manifold side member 73 are separated from each other in a state where the second header partition member 72 is sandwiched between the upwind heat transfer tube side member 71 and the manifold side member 73 . are combined and integrated in a consistent manner in the length direction. In the second header 70 , the upper end and the lower end are closed by two partition plates 74 . The upwind heat transfer tube side member 71 , the second header partition member 72 , the diverter side member 73 , the partition plate 74 , and the rectifier plate 75 are welded with solder in a furnace, for example, to be joined and integrated with each other.

The cross section of the upwind heat transfer tube side member 71 cut along a plane perpendicular to the vertical direction is arc-shaped. A plurality of upwind heat transfer tube connection openings 711 into which the ends of the corresponding heat transfer tubes 41 (upwind side heat transfer tubes 41 a ) are inserted are formed in the upwind heat transfer tube side member 71 . The number of the connection openings 711 of the upwind heat transfer tubes is the same as the number of layers of the heat transfer tubes 41 . In the diverter-side member 73 , the plurality of upstream heat transfer tube connection openings 711 are aligned in the vertical direction.

The second header partition member 72 is a plate-shaped member extending in the vertical direction. In the second header partition member 72, a plurality of openings for allowing the refrigerant to flow from the upwind heat transfer tube side member 71 to the flow divider side member 73 are formed in parallel in the vertical direction (see 72a in FIG. 16 ). , 72b).

The cross section of the diverter-side member 73 cut along a plane perpendicular to the vertical direction is arc-shaped. In addition, a plurality of first thin tube connection openings 73 a are formed in the diverter-side member 73 , and these first thin tube connection openings 73 a are used to connect one end of the corresponding first thin tube 93 . The number of the first thin tube connection openings 73 a is the same as the number of the first thin tube 93 . In the diverter-side member 73, the plurality of first thin tube connection openings 73a are aligned in the vertical direction.

The inside of the second header 70 is partitioned by a plurality of partition plates 74 and divided into a plurality of spaces (10 second header inner spaces SP1 and one second header auxiliary space SPa) (see FIG. 31 ).

As shown in FIG. 16 , the second header inner space SP1 formed between the two partition plates 74 in the second header 70 and the ends of the corresponding plurality of heat transfer tubes 41 (upwind side heat transfer tubes 41 a ) Connected. In addition, the second header inner space SP1 communicates with the end portion of the corresponding first thin tube 93 . In the second header inner space SP1 , the rectifying plate 75 is arranged in the vicinity of the upper side of the corresponding first thin tubes 93 .

The 2nd header auxiliary space SPa is formed in the lower end vicinity of the 2nd header 70, and is located in the position below each 2nd header inner space SP1 (refer FIG. 31). The second header auxiliary space SPa communicates with the ends of the corresponding plurality of (two in this case) heat transfer tubes 41 (upwind side heat transfer tubes 41a).

In each second header inner space SP1, in the second header partition member 72, a first communication opening 72a is formed in the vicinity of the lower part of the upper partition plate 74, and a second communication opening 72a is formed in the vicinity of the upper part of the rectifying plate 75. Communication opening 72b. A third communication opening 75 a is formed in the rectifying plate 75 .

Each of the second header inner spaces SP1 allows the refrigerant that has flowed out from one of the corresponding heat transfer tubes 41 and the first thin tubes 93 to flow into the other. Specifically, during the reverse cycle operation, the refrigerant that has flowed into the second header internal space SP1 from the first narrow tubes 93 flows upward through the small third communication opening 75a. The refrigerant that has flowed upward is divided into flow paths 411 of the plurality of heat transfer tubes 41 ( 41 a ) located between the rectifying plate 75 and the upper partition plate 74 . Moreover, a part of the refrigerant|coolant which flows upward forms the annular flow which passes through the 2nd communication opening 72b after the 1st communication opening 72a (refer the dotted line arrow Ar of FIG. 16). This refrigerant is finally divided from the annular flow and flows into the flow paths 411 of the plurality of heat transfer tubes 41 . In addition, during the normal cycle operation, the refrigerant that has flowed into the second header inner space SP1 from the corresponding heat transfer tubes 41 flows into the first narrow tubes 93 through the third communication openings 75a and the like.

In the present embodiment, 14 second header inner spaces SP1 are formed along the vertical direction in the second header 70 . Here, in the second header 70, each second header inner space SP1 is divided by a part of the upwind heat transfer tube side member 71, a part of the second header partition member 72, a part of the splitter side member 73, and a pair of The partition plate 74 is surrounded and formed. Therefore, a part of the upwind heat transfer tube side member 71 , the second header partition member 72 , a part of the splitter side member 73 , and the pair of partition plates 74 that form one second header inner space SP1 can also be collectively interpreted as The second header inner space forming member 78 (corresponding to the "second branching portion" described in the claims). From this explanation, the second header 70 can also be interpreted as a member configured by assembling a plurality of second header inner space forming members 78 that form the second header inner space SP1. In particular, it can be interpreted that a plurality of the second header inner space forming members 78 are arranged in parallel in the vertical direction in the installed state (see FIG. 31 ).

In this explanation, each second header inner space forming member 78 is made of aluminum or an aluminum alloy. Further, each second header inner space forming member 78 has a second header inner space SP1 formed therein. Further, each second header inner space forming member 78 forms a refrigerant flow path between the windward side heat exchange portion 40 a and the flow divider 90 . Moreover, the 1st thin tube connection opening 73a for connecting one end of the corresponding 1st thin tube 93 is formed in each 2nd header inner space forming member 78. Further, each second header inner space forming member 78 is formed with an upstream 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 inner space SP1, the height position of the first thin tube connection opening 73a in the installed state is arranged at the lowermost upstream heat transfer tube connection opening 711 (for Below the height position of the opening in which the windward side heat transfer tube 41a is inserted).

In the following description, the second header inner space SP1 located at the upper part of the second header 70 will be referred to as the "upper second header inner space SA", and the second header located in the center of the second header 70 will be referred to as the "upper second header inner space SA". The inner space SP1 is referred to as a "middle second header inner space SB", and the second header inner space SP1 located at the lower part of the second header 70 is referred to as a "lower second header inner space SC" (see FIG. 31).

The upper layer second header inner space SA here is the second header above the middle layer second header inner space SB among the plurality of second header inner spaces SP1 arranged in the vertical direction in the installed state The inner space SP1 includes the uppermost second header inner space SP1. Specifically, in the present embodiment, each of the first to fourth second header inner spaces SP1 from the top (that is, each of the second headers located above the two-dot chain line L4 in FIG. 31 ) The pipe interior space SP1) corresponds to the upper-stage second header interior space SA.

Here, the middle-level second header inner space SB (corresponding to the "central second space" described in the claims) is arranged in a plurality of second header inner spaces SP1 arranged in the vertical direction in the installed state. The second header inner space SP1 between the uppermost second header inner space SP1 and the lowermost second header inner space SP1. More specifically, the middle-level second header inner space SB includes at least a second set located at a height of at least one third from the lower end of the overall height dimension of the outdoor heat exchanger 15 and less than one third from the upper end. Tube interior space SP1. Specifically, in the present embodiment, the fifth to eighth second header inner spaces SP1 from the top (that is, each of the second header inner spaces SP1 located between the two-dot chain line L4 and the two-dot chain line L8 in FIG. 31 ) The second header inner space SP1) corresponds to the middle layer second header inner space SB.

Here, the lower second header inner space SC (corresponding to the "lower second space on the lower layer side" described in the claims) is one of the plurality of second header inner spaces SP1 arranged in the vertical direction in the installed state. The second header inner space SP1 below the second header inner space SB in the middle layer includes the second header inner space SP1 in the lowermost layer. In the present embodiment, the ninth to thirteenth second header inner spaces SP1 from the top (that is, the respective second header inner spaces SP1 located below the two-dot chain line L8 in FIG. 31 ) ) corresponds to the inner space SC of the lower second header.

(4-4) Return 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 in the vertical direction.

The folded-back header 80 is an elongated hollow cylindrical member extending in the up-down direction whose upper and lower ends are closed. The folded-back headers 80 are arranged on the other end sides of the windward side heat exchange portion 40a and the leeward side heat exchange portion 40b.

The turn-back 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. In addition, a plurality of leeward side openings 82 (the same number as the leeward side heat transfer tubes 41b) into which the other ends of the leeward side heat transfer tubes 41b are inserted are formed in the folded header 80 . The windward side opening 81 and the leeward side opening 82 are adjacent to each other along the direction in which the windward side heat exchange portion 40a and the leeward side heat exchange portion 40b are adjacent. In the turn-back header 80 , the plurality of windward openings 81 and the plurality of leeward openings 82 are arranged in parallel in the up-down direction, respectively.

A plurality of folded spaces SP2 are formed in the folded header 80, and the folded spaces SP2 allow the refrigerant flowing out from one of the adjacent windward side heat transfer tubes 41a and leeward side heat transfer tubes 41b to flow into the other. The turning space SP2 (corresponding to the "third space" described in the claims) is a space for turning back the refrigerant passing through one of the windward side heat transfer tube 41a and the leeward side heat transfer tube 41b to the other (see Dotted arrow Ar) in FIG. 18 . More specifically, in the normal circulation operation (in the case where the gas-side manifold 60 is an inlet pipe of the refrigerant), the turning space SP2 allows the refrigerant flowing out from the end of the leeward side heat transfer pipe 41b to flow into the upstream side heat transfer. space for the tube 41a. In addition, during the reverse cycle operation (in the case where the gas-side manifold 60 is the outlet pipe of the refrigerant), the turning space SP2 is for allowing the refrigerant flowing out from the end of the windward side heat transfer pipe 41a to flow into the leeward side heat transfer pipe 41b space.

A pair of windward side openings 81 and leeward side openings 82 are arranged in each turn-back space SP2. That is, in the turn-back space SP2, any one of the windward side heat transfer tubes 41a communicates with the corresponding leeward side heat transfer tube 41b. In particular, in this embodiment, a pair of windward side heat transfer tubes 41a and leeward side heat transfer tubes 41b arranged on the same floor communicate with each other in the turning space SP2. The number of the turn-back spaces SP2 formed in the turn-back header 80 is the same number as the number of pairs of the windward side openings 81 and the leeward side openings 82 .

Further, the plurality of folded spaces SP2 are configured by providing a plurality of tops 85, bottoms 86, and side portions 87 in the folded header 80 (see FIG. 19). That is, the top part 85 , the bottom part 86 , and the side part 87 forming one turn-back space SP2 can be collectively interpreted as the turn-back space forming member 88 . From this explanation, the folded-back header 80 can also be interpreted as a member configured by assembling a plurality of folded-space forming members 88 that form the folded-back space SP2. In particular, it can be interpreted that there are a plurality of turned-back space forming members 88 (in the installed state) in parallel in the vertical direction.

In this explanation, each folded space forming member 88 (corresponding to the "third branch" described in the claims) forms the folded space SP2 inside. In addition, each turn-back space forming member 88 forms a gas-side inlet/outlet of the refrigerant of the outdoor heat exchanger 15 (the gas-side header 60 in this embodiment) and each second header inner space SP1 (inside each second header) The space forms a refrigerant flow path between the members 78).

(4-5) Diverter 90 (corresponding to "first diverter" described in the claims)

FIG. 20 is a perspective view of the diverter 90 . FIG. 21 is an enlarged view of a portion A surrounded by a two-dot chain line in FIG. 20 .

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

The flow divider 90 mainly includes the inlet and outlet pipes 91 , a plurality of (thirteen here) first thin tubes 93 extending toward the second header 70 , second thin tubes 94 extending toward the first header 50 , and a flow divider body 95 . The inlet/outlet pipe 91, the first thin pipe 93, the second thin pipe 94, and the diverter body 95 are made of aluminum or an aluminum alloy. The inlet and outlet pipes 91 in the temporarily assembled state, each of the first thin pipes 93 , the second thin pipes 94 , and the diverter main body 95 are welded and joined by solder in a furnace, thereby configuring the diverter 90 .

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

The inlet/outlet pipe 91 (corresponding to the "first pipe" described in the claims) is a cylindrical pipe whose one end and the other end are open. One end of the inlet/outlet pipe 91 is connected to the diverter main body 95, and the other end is connected to the eighth piping P8. The inlet/outlet pipe 91 is a pipe through which the refrigerant passing through the outdoor heat exchanger 15 is taken in and out, and is a pipe that forms an inlet/outlet on the liquid side of the outdoor heat exchanger 15 . In particular, the inlet/outlet pipe 91 forms a flow path for the refrigerant flowing out from one of the flow divider main body 95 and the eighth piping P8 to flow into the other. The inlet/outlet pipe 91 is located between the flow divider main body 95 and the eighth piping P8 in the refrigerant circuit RC. The inlet/outlet pipe 91 is bent from one end to the other end, and has a substantially J-shape or a substantially U-shape (see FIG. 23 ).

The first thin pipe 93 (corresponding to the "second pipe" described in the claims) is a cylindrical pipe whose one end and the other end are open. The diameter of the first thin tube 93 is smaller than the diameter of the inlet and outlet pipes 91 . One end of the first thin tube 93 is connected to the diverter body 95 . The first thin tubes 93 correspond one-to-one with any one of the second header inner spaces SP1 (second header inner space forming members 78 ), and the other end corresponds to the first thin tubes arranged in the corresponding second header inner space SP1 The pipe connection opening 73a is connected. The first thin tube 93 forms a flow path for the refrigerant flowing out from one of the flow divider main body 95 and the second header internal space SP1 to flow into the other. The first thin tubes 93 are located between the flow divider main body 95 and the corresponding second header inner 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 part 40a side rather than the inlet and outlet pipes 91 .

The second thin pipe 94 is a cylindrical pipe whose one end and the other end are open. The diameter of the second thin tube 94 is smaller than the diameter of the inlet and outlet pipes 91 . One end of the second thin tube 94 is connected to the diverter 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 auxiliary space S2. The second thin tube 94 forms a flow path for the refrigerant flowing out from one of the flow divider main body 95 and the first header auxiliary space S2 to flow into the other. The second thin tube 94 is located between the flow divider main body 95 and the first header auxiliary space S2 in the refrigerant circuit RC.

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

The diverter 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. The main body interior space SP3 is a space that communicates with the inlet and outlet pipes 91 and one end of each of the first thin tubes 93 , and allows the refrigerant flowing out of the inlet and outlet pipes 91 to flow into (distribute into) each of the first thin tubes 93 . In addition, the main body interior space SP3 is also a space in which the refrigerant flowing out from each of the first narrow tubes 93 is collected and allowed to flow into the inlet and outlet pipes 91 .

The diverter body 95 has a top surface 951 facing upward and a bottom surface 952 facing downward in an installed state. The diverter main body 95 is formed with a first opening 95 a on the top surface 951 for inserting the inlet and outlet pipes 91 . In the present embodiment, the first opening 95 a is arranged in the center portion of the top surface 951 .

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

FIG. 27 is an enlarged view showing the surroundings of the diverter main body 95 viewed from the horizontal direction. FIG. 28 is an enlarged view showing the state of FIG. 27 viewed from a different direction.

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

In addition, in the diverter 90, each of the first thin tubes 93 temporarily extends downward from the bottom surface of the diverter body 95 (see FIGS. 27 and 28 ). In other words, each of the first thin tubes 9 is connected to the diverter main body 95 so as to extend in the downward direction from the main body internal space SP3 in the installed state. Specifically, each first thin tube 93 extends in the downward direction from the main body inner space SP3 and then bends, and extends in the upper direction toward the corresponding second header inner space SP1. More specifically, in the present embodiment, more than half (here, nine) of the first thin tubes 93 of the first thin tubes 93 are upwardly curved tubes 93a which follow the downward direction from the main body internal space SP3 After extending, it is bent so as to bulge downward, the extending direction is changed to the upward direction, and it is adjacent to the diverter main body 95 at intervals and extends in the upward direction (see FIGS. 27 and 28 ). That is, the upper curved pipe 93a has at least two curved portions (a curved portion turned upward from below, and a curved portion extended upward and curved toward the second header inner space SP1).

Further, most of the upper curved pipes 93a (here, eight pipes) are bent toward the center of the diverter body 95, and are adjacent to the inlet and outlet pipes 91 at intervals and extend in the upward direction (see FIGS. 27 and 28 ). . That is, the upper curved pipe 93a also has a curved portion (a curved portion curved toward the center of the diverter main body 95).

In the present embodiment, the upper curved pipes 93a are arranged at intervals in the circumferential direction of the flow divider main body 95 and the inlet and outlet pipes 91 in a plan view in the installed state. In other words, it can be explained that in the flow divider 90, the flow divider main body 95 and the inlet/outlet pipe 91 extending upward from the top surface side are surrounded by a plurality of first thin tubes 93 ( The upper curved tube 93a) surrounds.

However, the diverter body 95 has an outer surface portion not surrounded by the first thin tube 93 , and this outer surface portion functions as a contact portion 953 that abuts a tool used for moving in the furnace when the diverter 90 is assembled. That is, the diverter main body 95 is supported by the tool 100 shown in FIG. 29 , for example, and moves in the furnace in a state in which the inlet and outlet pipes 91 , the plurality of first thin tubes 93 and the second thin tubes 94 are inserted. Therefore, a part of the diverter main body 95 (ie, the part corresponding to the abutting part 953 ) is not adjacent to the first thin tube 93 to secure a receiving surface supported by the tool 100 . That is, the diverter main body 95 has the abutting portion 953 that abuts against the tool.

In the flow divider 90, during the normal cycle operation, the refrigerant flowing out from the respective second header internal spaces SP1 flows into the corresponding first thin tubes 93, and passes through the first thin tubes 93 to the flow divider main body 95 (the main body internal space SP3). ) flow out. The refrigerant that has flowed into the main body interior space SP3 flows through the inlet and outlet pipes 91 and flows out to the eighth piping P8.

In addition, at the time of the reverse cycle operation, the refrigerant flowing out from the eighth piping P8 passes through the inlet and outlet pipes 91 and flows into the distributor main body 95 (the main body interior space SP3 ). The refrigerant that has flowed into the main body internal space SP3 is divided and flows through the plurality of first narrow tubes 93, and then flows into any one of the second header internal spaces SP1.

(5) Positional relationship of each part in the outdoor heat exchanger 15

FIG. 30 is a schematic diagram showing the positional relationship of the first header 50 , the gas-side header 60 , the second header 70 , and the flow divider 90 in plan view. In the outdoor heat exchanger 15, as shown in FIG. In particular, the second header 70 (second header inner space forming member 78 ) and the flow divider 90 are arranged close to one end of the windward side heat exchange portion 40a. The straight-line distance D1 between the second header 70 (the second header inner space forming member 78 ) and the flow divider 90 in plan view is appropriately set according to the design specifications and the installation environment. From the viewpoint of , it is set to 100 mm or less.

(6) Manufacturing method of outdoor heat exchanger 15

The outdoor heat exchanger 15 is constituted by soldering each part in a furnace with solder. In this regard, in a plan view, the three parts of the outdoor heat exchanger 15 are greatly curved to form curved portions B1, B2, and B3 (see FIG. 8 ). On the other hand, since the size of the furnace for welding is determined, the heat exchange portion 40 is welded in the furnace in a flat state before forming the bent portions B1 , B2 , and B3 . After furnace welding, the bending parts B1 , B2 , and B3 are formed using predetermined roll tools and pressing tools.

(7) Path structure in the outdoor heat exchanger 15

In the outdoor heat exchanger 15 configured as described above, a plurality of paths are configured. The "path" here is defined by the first thin tube 93 of the flow divider 90 , the second header inner space SP1 (the second header inner space forming member 78 ), and the corresponding one or more heat transfer tubes 41 ( 41 a and 41 b ). ) and the path of the refrigerant constituted by the return space SP2.

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

The first path RP1 is the path located at the top in the installed state. In FIGS. 31 and 32 , the first path RP1 is a path located above the two-dot chain line L1. The first route RP1 includes three windward side heat transfer tubes 41a and leeward side heat transfer tubes 41b. The first route RP1 is a route including the second header inner space SP1 located above the two-dot chain line L1 (that is, the uppermost upper-layer second header inner space SA).

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

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

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

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

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

The seventh route RP7 is the seventh route from the top in the set state. In FIGS. 31 and 32, the seventh route RP7 is a route located between the two-dot chain line L6 and the two-dot chain line L7. The seventh route RP7 includes 12 windward side heat transfer tubes 41a and leeward side heat transfer tubes 41b. The seventh route RP7 is a route including the second header inner space SP1 (ie, the third middle-level second header inner space SB from the top) located between the two-dot chain line L6 and the two-dot chain line L7.

The eighth path RP8 is the eighth path from the top in the set state. In FIGS. 31 and 32 , the eighth route RP8 is a route located between the two-dot chain line L7 and the two-dot chain line L8. The eighth route RP8 includes 12 windward side heat transfer tubes 41a and leeward side heat transfer tubes 41b. The eighth route RP8 is a route including the second header inner space SP1 (ie, the fourth middle-level second header inner space SB from the top) located between the two-dot chain line L7 and the two-dot chain line L8.

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

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

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

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

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

The upper thirteenth path RP13a is located above the one-dot chain line A1 (FIG. 31, FIG. 32). The upper thirteenth path RP13a is constituted by the first thin tube 93, the lowermost second header inner space SP1, three windward side heat transfer tubes 41a, turning space SP2, and three leeward side heat transfer tubes 41b.

The lower 13th path RP13b is located below the one-dot chain line A1 (FIG. 31, FIG. 32). The lower thirteenth path RP13b is composed of the second thin tube 94, the spaces (S1, S2) in the first header 50, the two leeward side heat transfer tubes 41b from the bottom, the return space SP2, and the two from the bottom. The windward side heat transfer tubes 41a and the second header auxiliary space SPa are constituted.

The flow path length of the thirteenth path RP13 configured in this way is longer than the flow path lengths of the other paths.

The paths ( RP1 - RP13 ) configured as described above branch off in one of the first header main space S1 and the main body interior space SP3 , and merge in the other. In other words, in the outdoor heat exchanger 15, each path is configured in parallel. That is, in principle, the refrigerant that has passed through any one of the paths ( RP1 to RP13 ) flows out of the outdoor heat exchanger 15 and does not flow into the other paths. From this viewpoint, the outdoor heat exchanger 15 is different from a heat exchanger in which the refrigerant that has passed through any one of the paths is turned back to the other paths.

Here, as described above, with regard to the outdoor air flow AF passing through the heat exchange portion 40 of the outdoor heat exchanger 15, compared with the air passing through the lower portion (particularly the path below the center), the air passing through the upper portion (particularly the path lower than the center) is more The wind speed of the air in the path above the center) is high. Therefore, in each path, the wind speed of the air flow passing through the upper path is higher than that of the path passing through the lower part. For example, compared with the wind speed of the air flow passing through the path including the lower second header inner space SC (here, RP9 to RP13), the wind speed of the air passing through the path including the middle second header inner space SB (here, RP5 to RP8) The wind speed of the air flow is high. In addition, compared with the wind speed of the air flow passing through the path including the second header inner space SB in the middle layer (here, RP5-RP8), the wind speed of the air passing through the path including the upper second header inner space SA (here, RP1-RP4) The wind speed of the air flow is high.

(8) Flow of the refrigerant in the outdoor heat exchanger 15

In the outdoor heat exchanger 15, the refrigerant flows as follows.

(8-1) During forward cycle operation

The refrigerant that has flowed into the outdoor heat exchanger 15 during the normal cycle operation flows while exchanging heat with the outdoor air flow AF. However, during the defrosting operation of the refrigeration cycle, the refrigerant flowing into the outdoor heat exchanger 15 flows while exchanging heat with adhering frost.

Specifically, during the normal cycle operation, the refrigerant flows into the gas-side collecting pipe 60 from the seventh pipe P7. The refrigerant that has flowed into the gas-side header 60 flows into the first header main space S1 of the first header 50 via the plurality of connection pipes 61 . The refrigerant flowing into the first header main space S1 is divided into the leeward side heat transfer tubes 41b of the respective paths (first path RP1-thirteenth path RP13), and passes through the leeward side heat exchange portion 40b. The refrigerant that has passed through the leeward side heat exchange portion 40b reaches the turn-back header 80 (more specifically, the corresponding turn-back space SP2).

Then, the refrigerant is turned back in the turning space SP2, flows into the corresponding windward side heat transfer tubes 41a, and passes through the windward side heat exchange portion 40a. The refrigerant that has passed through the windward side heat exchange portion 40a reaches the second header 70 (more specifically, the corresponding second header inner space SP1).

In principle, the refrigerant that has flowed into the second header inner space SP1 flows into the flow divider 90 (the main body inner space SP3 ) via the corresponding first thin tubes 93 . The refrigerant that has flowed into the main body interior space SP3 from the first thin tube 93 merges with the refrigerant that has flowed out from the other first thin tubes 93 , and flows out to the eighth piping P8 through the inlet and outlet pipes 91 .

In addition, the refrigerant flowing into the first header main space S1 of the first header 50 from the gas-side header 60 flows into the leeward side heat transfer pipe 41b (ie, the leeward side) located at the lowermost part of the first header main space S1. The refrigerant in the second leeward side heat transfer tube 41b) in the side heat exchange portion 40b flows through the leeward side heat exchange portion 40b. The refrigerant that has passed through the leeward side heat exchange portion 40b is turned back in the turning space SP2, flows into the second upstream side heat transfer tube 41a from below, and flows through the upstream side heat exchange portion 40a. The refrigerant passing through the windward side heat exchange portion 40a is turned downward in the second header auxiliary space SPa, flows into the lowermost windward side heat transfer tube 41a, and flows through the windward side heat exchange portion 40a again. Then, the refrigerant that has passed through the windward side heat exchange portion 40a is folded back in the turning space SP2, flows into the lowermost leeward side heat transfer tube 41b, and flows through the leeward side heat exchange portion 40b. Then, the refrigerant that has passed through the leeward side heat exchange portion 40 b flows into the first header auxiliary space S2 , and flows into the main body interior space SP3 of the splitter main body 95 via the second thin tube 94 .

(8-2) During reverse cycle operation

The refrigerant that has flowed into the outdoor heat exchanger 15 during the reverse cycle operation flows while exchanging heat with the outdoor air flow AF. Specifically, during the reverse cycle operation, the refrigerant flows into the inlet and outlet pipes 91 from the eighth piping P8. The refrigerant that has passed through the inlet and outlet pipes 91 reaches the flow divider 90 (main body interior space SP3 ), and is divided and flows into the plurality of first thin tubes 93 and second thin tubes 94 (ie, flows into each path).

The refrigerant that has flowed into the first narrow tubes 93 from the main body interior space SP3 reaches the second header 70 (more specifically, the corresponding second header interior space SP1). The refrigerant that has flowed into the second header inner space SP1 flows into the corresponding windward side heat transfer tubes 41a, and passes through the windward side heat exchange portion 40a. The refrigerant that has passed through the windward side heat exchange portion 40a reaches the turn-back header 80 (more specifically, the corresponding turn-back space SP2). Then, the refrigerant is turned back in the turning space SP2, flows into the corresponding leeward side heat transfer tubes 41b, and passes through the leeward side heat exchange portion 40b. The refrigerant that has passed through the leeward side heat exchange portion 40b reaches the first header 50 (more specifically, the first header main space S1). The refrigerant that has flowed into the first header main space S1 reaches the gas-side header 60 via the plurality of connection pipes 61 and flows out of the outdoor heat exchanger 15 .

On the other hand, the refrigerant flowing into the second narrow tubes 94 from the main body interior space SP3 (ie, the refrigerant flowing into the lower thirteenth path RP13 b ) reaches the first header auxiliary space S2 of the first header 50 . The refrigerant that has flowed into the first header auxiliary space S2 flows into the lowermost leeward side heat transfer tube 41b, and passes through the leeward side heat exchange portion 40b. The refrigerant that has passed through the leeward side heat exchange portion 40b reaches the turn-back header 80 (more specifically, the corresponding turn-back space SP2). Then, the refrigerant turns back in the turning space SP2, flows into the lowermost windward side heat transfer tube 41a, and passes through the windward side heat exchange portion 40a. The refrigerant that has passed through the windward side heat exchange portion 40a is turned upward in the second header auxiliary space SPa, flows into the second windward side heat transfer tube 41a from the bottom of the windward side heat exchange portion 40a, and flows through the windward side again. The heat exchange part 40a. Then, the refrigerant that has passed through the windward heat exchange portion 40a is turned back in the turning space SP2, flows into the second leeward heat transfer tube 41b from below, and flows through the leeward heat exchange portion 40b. Then, the refrigerant that has passed through the leeward side heat exchange portion 40 b flows into the first header main space S1 , reaches the gas side header 60 via the connecting pipe 61 , and flows out of the outdoor heat exchanger 15 .

(9) Function of the 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 diverter main body 95, the height (the height of the outlet surface of the first thin tube 93) h2 (refer to FIG. 27 ) of the communicating portion of the main body interior space SP3 communicating with the first thin tube 93 is the reference of the pressure head. When the pressure head difference is larger than the pressure of the refrigerant flowing through the heat transfer tubes 41, the flow of the refrigerant is hindered. In particular, with regard to the heat transfer tubes 41 arranged at the lower part of the heat exchange part 40, the circulation amount of the refrigerant decreases due to the influence of the pressure head, and the refrigerant tends to stay.

Here, in the outdoor heat exchanger 15 , flat tubes are used as the heat transfer tubes 41 . Furthermore, the outdoor heat exchanger 15 is configured so that the refrigerant is distributed to each path using a header (more specifically, the plurality of second header internal spaces SP1 in the second header 70 ), that is, so-called header distribution. . In addition, each path ( RP1 - RP10 ) includes a plurality of heat transfer tubes 41 , and the flow is branched toward each heat transfer tube 41 in the second header inner space SP1 . In particular, in the outdoor heat exchanger 15, an annular flow of the refrigerant is formed in the second header inner space SP1 with respect to the branch flow toward each of the heat transfer tubes 41.

In the outdoor heat exchanger 15 having such a configuration, during the reverse cycle operation, the refrigerant flowing into each of the heat transfer tubes 41 in the second header inner space SP1 may be biased in relation to the pressure head difference. That is, in each of the heat transfer tubes 41 connected to the one second header inner space SP1, the lower the heat transfer tubes 41, the easier it is for the liquid refrigerant to flow, and the more the upper heat transfer tubes 41 are, the easier it is to flow. gas refrigerant. That is, within one path, a difference in pressure loss tends to occur between the plurality of heat transfer tubes 41 located at the upper and lower positions. In connection with this, especially during the defrosting operation of the refrigeration cycle, in each path, the lower heat transfer tube 41 easily affected by the liquid head tends to retain the refrigerant, and the hot gas is not supplied and tends to remain there.

In this regard, in a heat exchanger that does not perform header branching, the number of paths and the number of heat transfer tubes are in a one-to-one relationship, and when functioning as a condenser, the heat transfer through the path flowing through the lowermost layer is in a one-to-one relationship. Refrigerant retention can be suppressed if the pressure difference of the refrigerant in the pipe is higher than that of the liquid head of the flow divider. On the other hand, in a heat exchanger that is divided into headers like the outdoor heat exchanger 15, the circulation amount differs for each path, and when functioning as a condenser, the flow is most easily affected by the liquid head and The refrigerant in the lowermost heat transfer tube 41 whose circulation amount is likely to be reduced needs to secure a pressure difference stronger than the liquid head.

In the outdoor heat exchanger 15, the height position of the flow divider main body 95 in the installed state is lower than in the past. In the present embodiment, the height position of the diverter body 95 is controlled so that the height h1 (refer to FIG. 27 ) of the bottom surface 952 from the upper surface of the bottom frame 33 is 43 mm (within 100 mm).

Thereby, in the case where the outdoor heat exchanger 15 is used as a condenser, it is possible to reduce the pressure head difference caused by the installation height of the flow divider main body 95 . In connection with this, the liquid refrigerant flowing through the heat transfer tubes 41 (for example, the heat transfer tubes 41 included in the ninth path RP9 to the thirteenth path RP13 ) arranged in the lower part of the heat exchange unit 40 is ensured to have a pressure stronger than that of the liquid. The pressure difference of the head makes it easy to flow, which promotes the performance improvement. In particular, during the defrosting operation of the refrigeration cycle, the accumulation of liquid refrigerant is suppressed and defrosting is accelerated. Therefore, the residue of frost is suppressed, and it is excellent in reliability.

(B)

In addition, in the outdoor heat exchanger 15, thirteen paths are formed side by side in the vertical direction. That is, in the outdoor heat exchanger 15, the three or more second header inner spaces SP1 are arranged side by side in the vertical direction in the installed state. Then, a predetermined number of heat transfer tubes 41 communicate with each of the second header inner spaces SP1.

Specifically, the three heat transfer tubes 41 communicate with the upper second header inner space SA of the first path RP1. The four heat transfer tubes 41 communicate with the upper second header inner space SA of the second path RP2. The eight heat transfer tubes 41 communicate with the upper second header inner space SA of the third path RP3. The nine heat transfer tubes 41 communicate with the upper second header inner space SA of the fourth path RP4.

In addition, the ten heat transfer tubes 41 communicate with the intermediate second header inner space SB of the fifth path RP5. The eleven heat transfer tubes 41 communicate with the intermediate second header inner space SB of the sixth path RP6. The 12 heat transfer tubes 41 communicate with the inner space SB of the second header in the middle stage of the seventh path RP7. The 12 heat transfer tubes 41 communicate with the inner space SB of the second header in the middle stage of the eighth path RP8.

In addition, the seven heat transfer tubes 41 communicate with the lower second header inner space SC of the ninth path RP9. The six heat transfer tubes 41 communicate with the lower second header inner space SC of the tenth path RP10. The six heat transfer tubes 41 communicate with the lower second header inner space SC of the eleventh path RP11. The four heat transfer tubes 41 communicate with the lower second header inner space SC of the twelfth path RP12. The three heat transfer tubes 41 communicate with the lower second header inner space SC of the thirteenth path RP13 (upper thirteenth path RP13a). That is, in the present embodiment, the number of the heat transfer tubes 41 communicating with the lower second header inner space SC is seven or less.

In the outdoor heat exchanger 15 configured in this way, the number of heat transfer tubes 41 communicating with one lower-stage second space is greater than the number of heat transfer tubes 41 communicating with one middle-stage second header inner space SB. Less in quantity. Thereby, when used as a condenser, the reduction of the pressure head of the liquid refrigerant in the flow divider main body 95 (main body internal space SP3) is accelerated|stimulated. In connection therewith, when used as a condenser, the heat transfer tubes 41 (that is, the ninth paths RP9-thirteenth paths arranged in the lower part) communicate with the lower second header inner space SC where the liquid refrigerant tends to stay. In the route RP13), the refrigerant easily flows well, and the performance improvement is promoted. In particular, during the defrosting operation of the refrigeration cycle, the accumulation of liquid refrigerant is suppressed and defrosting is accelerated. Therefore, the residue of frost is suppressed, and it is excellent in reliability.

(9-2) Assemblability improvement function

In the outdoor heat exchanger 15, the flow divider main body 95 is provided so that the inlet and outlet pipes 91 extend upward from the main body interior space SP3, and a plurality of (10, that is, six or more) first thin pipes 93 extend from the main body interior space SP3 in the upward direction. The main body inner space SP3 extends in the downward direction. In this regard, in connection with the arrangement of the diverter body 95 in this manner, when the diverter body 95 and the first narrow tube 93 are manually welded and joined, the workability is remarkably lowered, and the assembly performance is expected to be poor. In the outdoor heat exchanger 15, the diverter main body 95 and the plurality of first thin tubes 93 are made of aluminum or an aluminum alloy, and thereby, the diverter 90 can be configured by joining the two by furnace welding. In connection therewith, the assemblability improvement is promoted.

(9-3) Compactness improving function

In the outdoor heat exchanger 15, compactness is promoted. That is, in the flow divider 90, each first thin tube 93 extends in the downward direction from the main body inner space SP3 and then bends, and extends in the upper direction toward the corresponding second header inner space SP1. More specifically, in the present embodiment, more than half (here, nine) of the first thin tubes 93 of the first thin tubes 93 are upwardly curved tubes 93a which follow the downward direction from the main body internal space SP3 After extending, it is bent so as to bulge downward, the extending direction is changed to the upward direction, and it is adjacent to the diverter main body 95 at intervals and extends in the upward direction (see FIGS. 27 and 28 ). Further, most of the upper curved pipes 93a (here, eight pipes) are bent toward the center of the diverter body 95, and are adjacent to the inlet and outlet pipes 91 at intervals and extend in the upward direction (see FIGS. 27 and 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 flow divider main body 95 and the inlet and outlet tubes 91 . In other words, in the diverter 90, the diverter main body 95 and the inlet/outlet pipe 91 extending upward from the top surface side are surrounded by a plurality of first thin tubes 93 (the upper curved tube 93a) that are connected to the bottom surface side and are bent to extend upward. ) surrounded.

By configuring the flow divider 90 in this way, the distance between the flow divider main body 95 and the first thin tubes 93 , the distance between the inlet and outlet pipes 91 and each of the first thin tubes 93 , and/or the distance between each of the first thin tubes 93 can be reduced. distance between. That is, it is possible to arrange each part close to each other while securing a gap. Thereby, compactness of the flow divider 90 which is supposed to be arranged in a narrow space is promoted. Furthermore, the compactness of the outdoor heat exchanger 15 is promoted.

(10) Features

(10-1)

Conventionally, there is known a heat exchanger including: a heat exchange unit including a plurality of flat tubes in which the flat tubes are arranged in a vertical direction in an installed state; a flow divider arranged at a liquid-side end; and The header is arranged between the heat exchange part and the flow divider. In this heat exchanger, in the header, a plurality of spaces are formed so as to be lined up in the direction in which the flat tubes are stacked, and each space communicates with the corresponding flat tubes. In addition, each space in the header and the flow divider are connected by thin tubes to form a plurality of paths (refrigerant flow paths). When such a heat exchanger is used as a condenser, the liquid refrigerant tends to stay in the flat tubes (paths) arranged in the vicinity of the lowermost layer in relation to the pressure head difference caused by the installation height of the flow divider.

In the outdoor heat exchanger 15 of the present embodiment, in the installed state, three or more second header inner spaces SP1 are arranged in the vertical direction, following the middle-level second header inner space SB (the second header inner space SB located in the center). The number of the heat transfer tubes 41 communicating with the lower second header inner space SC (the second header inner space SP1 below the middle layer second header inner space SB) is compared with the number of the heat transfer tubes 41 communicating with the lower second header inner space SB. The number of heat transfer tubes 41 is small. Thereby, when used as a condenser, the reduction of the pressure head of the liquid refrigerant in the flow divider main body 95 (main body internal space SP3) is accelerated|stimulated. In connection with this, when used as a condenser, the heat transfer tubes 41 (that is, the ninth paths RP9-thirteenth paths arranged in the lower part) communicate with the lower second header inner space SC, which tends to accumulate liquid refrigerant. In the route RP13), the refrigerant easily flows well, and the performance improvement is promoted. In particular, during the defrosting operation of the refrigeration cycle, the accumulation of liquid refrigerant is suppressed and defrosting is accelerated. Therefore, the residue of frost is suppressed, and reliability is excellent.

(10-2)

In the outdoor heat exchanger 15 of the above-described embodiment, the folded space forming member 88 (the third branching portion) forms a refrigerant flow path between the second header inner space forming member 78 and the gas-side manifold 60, and is formed inside There is a return space SP2 (third space). The turn-back space SP2 communicates with the other end of the corresponding heat transfer pipe (one of the windward side heat transfer pipe 41 a and the leeward side heat transfer pipe 41 b ), and also communicates with the second heat transfer pipe arranged on the same layer as the heat transfer pipe 41 One end of (the other of the windward side heat transfer pipe 41a and the leeward side heat transfer pipe 41b) is communicated with each other.

Thereby, each path ( RP1 - RP13 ) is configured in parallel. That is, in principle, the refrigerant that has passed through any one of the paths ( RP1 to RP13 ) flows out of the outdoor heat exchanger 15 and does not flow into the other paths.

(10-3)

In the outdoor heat exchanger 15 of the above-described embodiment, in the installed state, the wind speed of the outdoor air flow AF passing through the periphery of the heat transfer tubes 41 communicating with the lower second header inner space SC is higher than that of the lower stage. The wind speed of the outdoor air flow AF around the heat transfer tubes 41 connected to the second header inner space SP1 above the second header inner space SC is large. That is, regarding the outdoor heat exchanger 15 arranged in the outdoor unit 10 which draws in the outdoor air flow AF from the side and blows it upward, the performance improvement is promoted.

(10-4)

In the outdoor heat exchanger 15 according to the above-described embodiment, the lower second header inner space SC is arranged at a height position equal to or less than one third of the height of the entire heat exchange portion 40 in the installed state, and is located at the same height as the lower second header. In the heat transfer tubes 41 communicating with the header inner space SC (ie, the heat transfer tubes 41 having a tendency to retain liquid refrigerant in particular when used as a condenser), the refrigerant flows easily and favorably, thereby promoting performance improvement.

(10-5)

In the outdoor heat exchanger 15 of the above-described embodiment, the heat transfer tubes 41 located in the lowermost layer in the installed state communicate with the lower second header inner space SC, and when the heat transfer tubes 41 (that is, used as condensers) are particularly In the heat transfer tube 41) in which the liquid refrigerant tends to stay, the refrigerant easily flows well, and the performance improvement is promoted.

(10-6)

In the outdoor heat exchanger 15 of the above-described embodiment, in the installed state, the plurality of lower-layer second header inner spaces SC are aligned in the vertical direction, and the heat transfer tubes communicate with each lower-layer second header inner space SC 41 (that is, the heat transfer tube 41 which, when used as a condenser, has a tendency to retain liquid refrigerant in particular), the refrigerant easily flows well.

(10-7)

In the outdoor heat exchanger 15 of the above-described embodiment, in the installed state, the plurality of middle-stage second header inner spaces SB are aligned in the vertical direction. In connection with this, in the heat transfer tube 41 communicating with the lower second header inner space SC, the liquid refrigerant is particularly likely to stay when used as a condenser. However, in the above-described embodiment, the heat transfer tube In 41, the refrigerant flows easily and well.

(10-8)

In the outdoor heat exchanger 15 of the above-described embodiment, one end of the inlet/outlet pipe 91 is connected to the flow divider main body 95 so as to extend upward from the main body interior space SP3 in the installed state. One end of the first thin tube 93 is connected to the diverter main body 95 so as to extend in the downward direction from the main body internal space SP3 in the installed state.

Thereby, the height position of the diverter main body 95 of the diverter 90 in the installed state can be lowered. As a result, in the case where the heat transfer tubes 41 are arranged in parallel in the vertical direction, when used as a condenser, the pressure head difference caused by the installation height of the flow divider can be reduced. Thereby, even in the heat transfer tube 41 (path) arranged in the vicinity of the lowermost layer in which the liquid refrigerant tends to accumulate when used as a condenser, the accumulation of the liquid refrigerant is particularly suppressed. Therefore, the performance improvement is particularly promoted, and the reduction in reliability especially during normal cycle operation (cooling operation or refrigeration cycle defrosting operation) is suppressed.

(10-9)

In the air conditioning system 1 of the above-described embodiment, performance improvement is promoted in association with the function of the outdoor heat exchanger 15 .

(11) Modifications

The above-described embodiment can be appropriately modified as shown in the following modified examples. In addition, each modification can be applied in combination with other modification in the range which does not cause a contradiction.

(11-1) Modification 1

In the above-described embodiment, the diverter body 95 has a plurality of second openings 95b formed on the bottom surface 952 facing downward in the installed state, and the plurality of second openings 95b are connected to one end of the first thin tube 93 . From the viewpoint of connecting the first thin tube 93 to the flow divider main body 95 so as to extend downward from the main body interior space SP3 in the installed state, the flow divider 90 is preferably configured in this manner. However, the configuration of the diverter 90 is not necessarily limited to this, and the first thin tube 93 may be appropriately changed as long as it is connected to the diverter main body 95 so as to extend downward from the main body interior space SP3 in the installed state. For example, in the diverter body 95, a part or all of the plurality of second openings 95b may be formed on the side surface facing the side in the installed state.

(11-2) Modification 2

In the above-described embodiment, in the diverter body 95 , the top surface 951 facing upward in the installed state is formed with the first opening 95 a , and the first opening 95 a is connected to one end of the inlet and outlet pipes 91 . From the viewpoint of connecting the inlet/outlet pipe 91 to the flow divider main body 95 so as to extend upward from the main body interior space SP3 in the installed state, the flow divider 90 is preferably configured in this manner. However, the configuration of the flow divider 90 is not necessarily limited to this, and can be appropriately changed as long as the inlet and outlet pipes 91 are connected to the flow divider main body 95 so as to extend upward from the main body interior space SP3 in the installed state. For example, in the diverter body 95, the first opening 95a may be formed on the side surface facing the side in the installed state.

In addition, in the diverter body 95 , in the installed state, the bottom surface 952 facing downward may be formed with a first opening 95 a that is connected to one end of the inlet/outlet pipe 91 . In this case, the diverter body 95 may have a first opening 95a formed on the ceiling surface 951 facing upward in the installed state, and the first opening 95a may be connected to one end of the first thin tube 93 . In this example, one end of the inlet/outlet pipe 91 is connected to the flow divider main body 95 so as to extend downward from the main body internal space SP3 in the installed state, and the plurality of first thin tubes 93 are connected to the main body internal space from the main body internal space in the installed state. One end of the SP3 is connected to the shunt main body 95 so as to extend in the upward direction, but the effects described in the above-mentioned "10-1" can be achieved in the same manner as in the above-mentioned embodiment.

(11-3) Modification 3

In the above-described embodiment, the first thin tubes 93 correspond to the second header inner spaces SP1 one-to-one, and are connected to the corresponding second header inner spaces SP1. However, the correspondence relationship between the first thin tubes 93 and the second header inner space SP1 can be appropriately changed according to the design specifications and the installation environment as long as there is no conflict. For example, each of the first thin tubes 93 may correspond to any one of the second header inner spaces SP1 in a one-to-many, many-to-one, or many-to-many correspondence.

In addition, the number of the first thin tubes 93 included in the flow divider 90 is not necessarily limited to the number of the above-described embodiment, and can be appropriately changed according to design specifications and installation environments. That is, the diverter 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 of the above-described embodiment, the second header inner space forming member 78 is formed with the upstream heat transfer tube connection opening 711 connected to one end of the corresponding heat transfer tube 41 and the corresponding first thin tube, respectively. The first thin tube connection opening 73a connected to the other end of 93 has a height position of the first thin tube connection opening 73a below the height position of the lowermost upstream heat transfer tube connection opening 711 in the installed state. The outdoor heat exchanger 15 is preferably configured in this manner from the viewpoint of suppressing the accumulation of the liquid refrigerant in each path when used as a condenser. However, in the second header inner space forming member 78, the height position of the first thin tube connection opening 73a does not necessarily have to be lower than the height position of the lowermost upstream heat transfer tube connection opening 711.

(11-5) Modification 5

Although not particularly described in the above-mentioned embodiment, the height position of the diverter main body 95 in the installed state may be set such that the height h2 of the communicating portion of the main body interior space SP3 communicating with the first narrow tube 93 is the highest. Below the height position of the upper end of the lower 2nd header inner space SP1. Thereby, it is further suppressed that the liquid refrigerant stays in each path when used as a condenser.

(11-6) Modification 6

In the above-described embodiment, it can be interpreted as a single unit composed of a plurality of second header inner space forming members 78 (corresponding to the "second branch" described in the claims) that form the second header inner space SP1. The second header 70 is arranged between the heat exchange unit 40 and the flow divider 90 .

However, in the outdoor heat exchanger 15, a member that forms a space corresponding to the second header inner space SP1 (that is, a member corresponding to the second header inner space forming member 78) may be arranged other than the second header 70 .

For example, one or more members (for example, a header, etc.) that form at least one space corresponding to the second header internal space SP1 may be arranged in the heat exchange part 40 instead of or together with the second header 70 . and shunt 90. In this case, the member corresponds to the "second diverter" described in the claims.

In addition, for example, a branching mechanism for branching the refrigerant to any one/all of the plurality of paths ( RP1 to RP13 ) may be arranged in the heat exchange part 40 and the branch instead of the second header 70 or together with the second header 70 . between 90.

(11-7) Modification 7

In the above-described embodiment, ten paths 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 design specifications and installation environments. For example, in the outdoor heat exchanger 15, 11 or more paths may be formed, or less than 10 paths may be formed. In addition, the number of the second header inner spaces SP1 and the number of the first thin tubes 93 formed in the second header 70 may be appropriately changed according to the number of paths.

(11-8) Modification 8

The form of the path in the above-described embodiment can be appropriately changed. For example, the number of the heat transfer tubes 41 included in each path can be appropriately changed independently as long as it does not contradict the idea described in (10-1) above. In addition, for example, the number of upper second header inner spaces SA, the number of middle layer second header inner spaces SB, and the number of lower second header inner spaces SC formed in the outdoor heat exchanger 15 can be appropriately changed, respectively. For example, the number of the upper second header inner spaces SA in the outdoor heat exchanger 15 is not limited to four, and may be one or more and three or less, or five or more. In addition, the number of the middle-stage second header inner spaces SB in the outdoor heat exchanger 15 is not limited to four, and may be one or more and three or less, or may be five or more. In addition, the number of the lower second header inner spaces SC in the outdoor heat exchanger 15 is not limited to five, and may be one or more and four or less, or may be six or more.

(11-9) Modification 9

In the above-described embodiment, the thirteenth route RP13 is formed to include the upper thirteenth route RP13a and the lower thirteenth route RP13b. However, the thirteenth route RP13 need not necessarily be formed in this way, and the lower thirteenth route RP13b may be omitted in the thirteenth route RP13. In this case, the first auxiliary header space S2, the second auxiliary header space SPa, the second narrow tubes 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-described embodiment may be appropriately changed. For example, in the above-described embodiment, the first header 50 , the gas-side header 60 , the second header 70 , and the diverter 90 are arranged in the vicinity of one end of the heat exchange portion 40 , and the folded header 80 is arranged in the heat exchange portion. However, the first header 50, the gas side header 60, the second header 70, and the diverter 90 may be arranged near the other end of the heat exchange part 40, and the return header 80 may be arranged in the vicinity of the other end of the heat exchange part 40. Near one end of the exchange unit 40 . In addition, for example, the arrangement positions of the windward side heat exchange portion 40a and the leeward side heat exchange portion 40b may be exchanged. That is, the windward side heat exchange part 40a may be arranged on the leeward side (or the inner side), and the leeward side heat exchange part 40b may be arranged on the windward side (or the outer side).

(11-11) Modification 11

The gas-side manifold 60 in the above-described embodiment may be appropriately omitted. In this case, for example, the seventh piping P7 may be connected to the first header 50 . In addition, in this case, the first header 50 corresponds to the "third pipe" described in the claims.

(11-12) Modification 12

In the said embodiment, the outdoor heat exchanger 15 has the two heat exchange parts 40 (the windward side heat exchange part 40a and the leeward side heat exchange part 40b). However, the configuration of the outdoor heat exchanger 15 is not necessarily limited to this, and can be appropriately changed. For example, the outdoor heat exchanger 15 may have three or more heat exchange parts 40 . In this case, the heat exchange parts 40 may be arranged in the flow direction of the outdoor air flow AF, or may be arranged in other ways.

In addition, for example, the outdoor heat exchanger 15 may be configured to include only a single heat exchange part 40 . In this case, the return header 80 may be omitted, and the first header 50 may be connected to the ends of the windward side heat transfer tubes 41a. In this example, the space in the first header 50 may be divided for each path (in this case, each divided space corresponds to the "third space" described in the claims, and the first header is formed Each part of each space of 50 corresponds to a "third diverter").

(11-13) Modification 13

In the above-described 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 portion 40 mainly has three surfaces that intersect with the flow direction of the outdoor air flow AF. However, the configuration of the outdoor heat exchanger 15 is not necessarily limited to this, and can be appropriately changed.

For example, the outdoor heat exchanger 15 may be configured to be substantially L-shaped or substantially V-shaped in plan view. That is, the outdoor heat exchanger 15 may be configured such that the heat exchange portion 40 has two surfaces that intersect with the flow direction of the outdoor air flow AF.

In addition, for example, the outdoor heat exchanger 15 may be configured to be substantially I-shaped in plan view. That is, the outdoor heat exchanger 15 may be configured such that the heat exchange portion 40 has a single surface that intersects with the flow direction of the outdoor air flow AF.

In addition, for example, the outdoor heat exchanger 15 may be configured such that the heat exchange portion 40 has four or more surfaces that intersect the flow direction of the outdoor air flow AF.

(11-14) Modification 14

In the above-described embodiment, the plurality of flow paths 411 are formed in the heat transfer tube 41 . However, it is not necessarily limited to this, and a flat tube in which a single flow path 411 is formed may be used as the heat transfer tube 41 .

(11-15) Modification 15

In the above-described embodiment, the heat exchange portion 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-mentioned 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, it is not necessary that all the parts included in the outdoor heat exchanger 15 be made of aluminum or an aluminum alloy. For example, any one part may be composed of other metals (for example, materials such as steel), or may be composed of other raw materials (for example, resins, etc.).

(11-17) Modification 17

In the above-described embodiment, the outdoor heat exchanger 15 is configured such that the linear distance D1 between the flow divider 90 and the second header inner space forming member 78 in 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, it is not necessarily limited to this, and the value of the linear distance D1 in plan view between the diverter 90 and the second header inner space forming member 78 can be appropriately changed.

(11-18) Modification 18

In the outdoor heat exchanger 15 of the above-described embodiment, the plurality of second openings 95b are arranged annularly at intervals. Regarding the heat exchanger including the flow divider 90 in which the plurality of first thin tubes 93 extend downward from the flow divider main body 95 , the plurality of first thin tubes 93 are densely packed by securing the space between the adjacent first thin tubes 93 . From such a viewpoint, it is preferable to arrange the plurality of second openings 95b in this manner. However, the arrangement of the second openings 95b is not necessarily limited to this, and can be appropriately changed.

(11-19) Modification 19

In the outdoor heat exchanger 15 according to the above-described embodiment, more than half of the first thin tubes 93 among the plurality of first thin tubes 93 are upwardly bent tubes 93a that go in the downward direction from the main body interior space SP3 in the installed state After being extended, it is bent, and extends in the upward direction adjacent to the shunt main body 95 . In this regard, the number of the upper curved pipes 93a is not necessarily limited to the number in the above-described embodiment, and can be appropriately changed. That is, the number of the upper curved pipes 93a included in the diverter 90 may be nine or more or less than eight.

(11-20) Modification 20

In the outdoor heat exchanger 15 of the above-described embodiment, the upper curved pipe 93 a extends in the upward direction adjacent to the flow divider main body 95 in the installed state, is then bent again, extends toward the inlet and outlet pipes 91 , and is further bent to be connected to the inlet and outlet pipes 91 . Adjacent and extending in the upward direction. In this regard, the configuration of the upper curved pipe 93a is not necessarily limited to that in the above-described embodiment, and can be appropriately changed according to design specifications and installation environments.

(11-21) Modification 21

In the outdoor heat exchanger 15 of the above-described embodiment, in a plan view, the plurality of upper curved pipes 93a are arranged at intervals along the circumferential direction of the inlet and outlet pipes 91 in the installed state. From the viewpoint of compactness of the flow divider 90, it is preferable to arrange the plurality of upper curved pipes 93a in this manner. However, the configuration of the upper curved pipe 93a is not necessarily limited to that in the above-described embodiment, and can be appropriately changed according to design specifications and installation environments.

(11-22) Modification 22

In addition to this, the formation form (position, shape, size, etc.) of each part of the outdoor heat exchanger 15 in the above-described embodiment is not necessarily limited to the form in the above-described embodiment, as long as it does not conform to the idea described in the above (10-1). What is necessary is just to generate|occur|produce a contradiction, and it can change suitably according to a design specification etc..

(11-23) Modification 23

The configuration of the refrigerant circuit RC in the above-described embodiment can be appropriately changed according to design specifications and installation environments. For example, equipment not shown in FIG. 1 may also be included instead of a part of the equipment included in the refrigerant circuit RC/together with the equipment included in the refrigerant circuit RC. In addition, for example, as long as there is no obstacle, a part of the equipment (for example, the gas-liquid separator 11 , etc.) included in the refrigerant circuit RC may be omitted.

(11-24) Modification 24

In the above-mentioned 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 can also be applied to other units. For example, the outdoor heat exchanger 15 may be applied to a box-shaped outdoor unit 10 in which an air flow flows in from the side and flows out from the front side. In addition, for example, the outdoor heat exchanger 15 may be applied to the indoor unit 20 as the indoor heat exchanger 22 .

(11-25) Modification 25

In the above-described 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 refrigeration apparatuses (hot water supply apparatuses, heat pump coolers, etc.).

(12)

The embodiment has been described above, but it is understood that various changes in the form and details can be made without departing from the spirit and scope of the claims.

Industrial Availability

The present invention can be applied to a heat exchanger or an air conditioner indoor unit having a heat exchanger.

Label description

1: Air conditioning system (refrigeration device)

10: Outdoor unit

12: Compressor

15: Outdoor heat exchanger (heat exchanger)

18: Outdoor Fan

20: Indoor unit

30: Outdoor unit enclosure

40: Heat Exchange Section

40a: Upwind side heat exchange part

40b: Downwind side heat exchange part

41: Heat transfer tube (flat tube)

41a: Upwind side heat transfer tube

41b: Downwind side heat transfer tube

42: Heat transfer fins

50: Header 1

51: Downwind heat transfer tube side parts

52: 1st header dividing member

53: Manifold side parts

54: 1st dividing plate

55: Second partition plate

60: Gas side manifold (third pipe)

61: connecting pipe

62: Binding straps

70: Header 2

71: Upwind heat transfer tube side parts

72: 2nd header dividing member

72a: 1st communication opening

72b: Second communication opening

73: Diverter side parts

73a: 1st thin tube connection opening

74, 74a: Separator

75: Rectifier plate

75a: 3rd communication opening

78: Second header inner space forming member (second branch)

80: Foldback header

81: Windward side opening

82: Downwind side opening

88: Turning space forming member (third diverter)

90: Diverter (1st Diverter)

91: Inlet and outlet pipe (1st pipe)

93: 1st thin tube (2nd tube)

93a: Upper Bend Tube

94: 2nd thin tube

95: Diverter body (main body)

95a: 1st opening

95b: 2nd opening

100: Tools

411: Flow Path

511: Downwind heat transfer pipe connection opening

711: Upwind heat transfer pipe connection opening

951: Top Surface

952: Underside

953: Abutment

AF: Outdoor Airflow

P1-P9: 1st piping - 9th piping

RC: refrigerant circuit

RP1-RP13: Path 1 - Path 13

RP13a: 13th path on the upper side

RP13b: 13th path on the lower side

S1: 1st Header Main Space

S2: 1st Header Auxiliary Space

SA: Upper level 2nd header interior space

SB: Central 2nd header inner space (Central 2nd space)

SC: The inner space of the second header on the lower floor (the second space on the lower floor side)

SPa: 2nd Header Auxiliary Space

SP1: 2nd header inner space (2nd space)

SP2: Entrance space (3rd space)

SP3: Main body interior space (1st space)

prior art literature

Patent Literature

Patent Document 1: International Publication No. WO2013/160952

Claims (10)

1. A heat exchanger (15), the heat exchanger (15) having:

a heat exchange unit (40) including a plurality of flat tubes (41) arranged in parallel in the vertical direction in the installed state;

a1 st flow dividing portion (90) having a1 st tube (91) through which a refrigerant flows, a plurality of 2 nd tubes (93) forming refrigerant passages on the heat exchange portion side of the 1 st tube, and a body portion (95) having a1 st space (SP3) formed therein, the 1 st space (SP3) communicating with one end of the 1 st tube and one end of each of the 2 nd tubes, and allowing the refrigerant flowing out of one of the 1 st tube and the 2 nd tube to flow into the other; and

a plurality of 2 nd flow dividing portions (78), the plurality of 2 nd flow dividing portions (78) forming refrigerant flow paths between the heat exchange portion and the 1 st flow dividing portion and having a 2 nd space (SP1) formed therein, the 2 nd space (SP1) communicating with one end of the corresponding flat tube and with the other end of the corresponding each 2 nd tube, and flowing the refrigerant flowing out of one of the corresponding flat tube and the 2 nd tube into the other,

in the installed state, 3 or more of the 2 nd spaces are arranged in the vertical direction, and the number of the flat tubes communicating with the 2 nd Space (SC) on the lower layer side, which is the 2 nd space below the central 2 nd space, is smaller than the number of the flat tubes communicating with the central 2 nd Space (SB), which is the 2 nd space at the center.

2. The heat exchanger (15) of claim 1,

the heat exchanger (15) further has:

a 3 rd tube (60) which is a refrigerant outlet tube in the case where the 1 st tube is a refrigerant inlet tube, and which is a refrigerant inlet tube in the case where the 1 st tube is a refrigerant outlet tube; and

at least one 3 rd branching portion (88) which forms a refrigerant flow path between the 2 nd branching portion and the 3 rd tube and in which a 3 rd space (SP2) communicating with the other end of the corresponding flat tube is formed,

the 3 rd space communicates with one end of the 3 rd tube or a 2 nd flat tube disposed in the same layer as the flat tubes,

in a case where the 1 st tube is a refrigerant inlet tube, the 3 rd space is a space in which the refrigerant flowing out of the other end of the flat tube flows into the 3 rd tube or the 2 nd flat tube,

in the case where the 1 st tube is a refrigerant outlet tube, the 3 rd space is a space in which the refrigerant flowing out of one end of the 3 rd tube or the 2 nd flat tube flows into the flat tube.

3. The heat exchanger (15) according to claim 1 or 2,

the heat exchange portion exchanges heat between the refrigerant in the flat tubes and an Air Flow (AF),

in the installed state, the air velocity of the air flow passing around the flat tube communicating with the 2 nd space above the lower layer side 2 nd space is larger than the air velocity of the air flow passing around the flat tube communicating with the lower layer side 2 nd space.

4. A heat exchanger (15) according to any one of claims 1 to 3,

the lower-stage 2 nd space is disposed at a height position that is less than one third of the height of the entire heat exchange unit in the installed state.

5. The heat exchanger (15) according to any one of claims 1 to 4,

the flat tube positioned in the lowermost layer in the installed state communicates with the lower-layer-side No. 2 space.

6. The heat exchanger (15) according to any one of claims 1 to 5,

in the installed state, the plurality of lower-stage 2 nd spaces are arranged in parallel in the vertical direction.

7. The heat exchanger (15) according to any one of claims 1 to 6,

in the installed state, the plurality of central No. 2 spaces are arranged in the vertical direction.

8. The heat exchanger (15) according to any one of claims 1 to 7,

one end of the 1 st pipe is connected to the main body in a manner of extending from the 1 st space along a lower direction in an installation state,

the 2 nd pipe is connected at one end to the main body portion so as to extend in an upward direction from the 1 st space in an installed state.

9. The heat exchanger (15) according to any one of claims 1 to 7,

one end of the 1 st pipe is connected to the main body so as to extend in an upward direction from the 1 st space in the installed state,

the 2 nd pipe is connected to the main body portion at one end thereof in a set state so as to extend downward from the 1 st space.

10. A refrigeration device (1), the refrigeration device (1) comprising:

a compressor (12) that compresses a refrigerant; and

a heat exchanger (15) as claimed in any one of claims 1 to 9.

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