WO2024042575A1

WO2024042575A1 - Heat exchanger, and refrigeration cycle device

Info

Publication number: WO2024042575A1
Application number: PCT/JP2022/031523
Authority: WO
Inventors: 伸吾笠木; 哲二七種; 洋次尾中; 祐基中尾; 理人足立
Original assignee: 三菱電機株式会社
Priority date: 2022-08-22
Filing date: 2022-08-22
Publication date: 2024-02-29

Abstract

This heat exchanger comprises a first heat exchanging body including a plurality of first flat tubes disposed spaced apart from one another in a first direction and having a tube axial direction extending in a second direction intersecting the first direction, a first refrigerant distributor into which one end portion of each of the plurality of first flat tubes is inserted, and a second refrigerant distributor into which the other end of each of the first flat tubes is inserted, wherein: the first refrigerant distributor includes a first outer tube which is disposed extending in the first direction and into which said one end portion of each of the plurality of first flat tubes is inserted, a first inner tube which is disposed extending in the first direction, is arranged inside the first outer tube, and which includes a plurality of first refrigerant outflow holes arranged spaced apart from one another in the first direction, and a first dividing plate which is joined to an inner wall of the first outer tube with the first inner tube penetrating through in a plate thickness; and the second refrigerant distributor includes a second outer tube which is disposed extending in the first direction and into which said other end portion of each of the plurality of first flat tubes is inserted, a second inner tube which is disposed extending in the first direction, is arranged inside the second outer tube, and which includes a plurality of second refrigerant outflow holes arranged spaced apart from one another in the first direction, and a second dividing plate which is joined to an inner wall of the second outer tube with the second inner tube penetrating through in a plate thickness.

Description

Heat exchanger and refrigeration cycle equipment

The present disclosure relates to a heat exchanger and a refrigeration cycle device having a plurality of flat tubes.

Some conventional refrigeration cycle apparatuses having a plurality of heat exchangers are constructed from a plurality of heat exchangers, with one or more heat exchangers forming one set (for example, see Patent Document 1). In each of the plurality of sets, the heat exchanger is composed of an air heat exchanger, and includes an upper header pipe, a lower header pipe, a heat transfer tube, and fins.

During cooling operation, the sets are connected in series, and a series refrigerant flow path is formed in which the refrigerant flows in series between the sets. In the serial refrigerant flow path, the refrigerant flows from top to bottom through the heat transfer tubes of all the heat exchangers.

During heating operation, the sets are connected in parallel, and a parallel refrigerant flow path is formed in which the refrigerant flows in parallel to each set. In the parallel refrigerant flow paths, the refrigerant flows from bottom to top through the heat transfer tubes of all the heat exchangers.

Furthermore, in conventional heat exchangers, a refrigerant distributor having a double pipe structure including an inner pipe and an outer pipe is used as a lower header pipe, for example. A plurality of outer tubes are provided, and a gap is formed between adjacent outer tubes among the plurality of outer tubes. One inner tube is provided continuously for the plurality of outer tubes. A plurality of heat transfer tubes are connected to the outer tube in the tube axis direction of the outer tube, and the refrigerant flowing between the inner tube and the outer tube is distributed to the plurality of heat transfer tubes.

International Publication No. 2019/008664

Generally, when a heat exchanger functions as an evaporator, a gas-liquid two-phase refrigerant in which gas refrigerant and liquid refrigerant are mixed flows into the heat exchanger. In this case, a refrigerant distributor having a double pipe structure composed of an inner tube and an outer tube may be used as the refrigerant distributor on the inflow side of the heat exchanger. In a refrigerant distributor having a double pipe structure, a large number of refrigerant outlet holes are arranged in parallel in the inner pipe. A refrigerant distributor having a double tube structure can reduce the volume of the refrigerant distributor while evenly distributing the refrigerant to a plurality of heat transfer tubes that constitute a heat exchanger.

A refrigerant distributor with a single-pipe structure is provided on the outflow side of the heat exchanger that functions as an evaporator. The refrigerant distributor has a function of distributing refrigerant to a plurality of heat transfer tubes that constitute the heat exchanger when the heat exchanger functions as a condenser.

However, as in Patent Document 1 mentioned above, when multiple heat exchangers are installed in one outdoor unit, the connection state of the multiple heat exchangers is different from forming a series refrigerant flow path to parallel refrigerant flow paths. A distinction is made between the case where a refrigerant flow path is formed and the case where a refrigerant flow path is formed. When multiple heat exchangers installed in an outdoor unit for cooling operation function as condensers, if the multiple heat exchangers form a serial refrigerant flow path, a refrigerant is present on the upstream side of the flow path. The state of the refrigerant flowing into the heat exchanger and the heat exchanger located downstream are different. That is, the gas refrigerant flows in a single phase into the heat exchanger located on the upstream side. On the other hand, in the downstream heat exchanger, a part of the gas refrigerant condenses during heat exchange in the upstream heat exchanger, so a gas-liquid two-phase state where gas refrigerant and liquid refrigerant are mixed is generated. Refrigerant will flow in. However, in this case, the refrigerant distributor on the inflow side of the heat exchanger located downstream is a refrigerant distributor with a single-pipe structure. Therefore, in the heat exchanger located on the downstream side, the refrigerant flowing into the heat exchanger is not evenly distributed to the plurality of flat tubes that constitute the heat exchanger. In the heat exchanger located on the downstream side, the amount of refrigerant distributed is uneven depending on the position of the flat tube, so the amount of heat exchange is insufficient near the flat tube where more refrigerant is distributed, and less refrigerant is distributed. There is a problem in that the amount of heat exchanged is excessive near the flat tubes, and the heat exchange efficiency decreases.

The present disclosure has been made to solve such problems, and is one heat exchanger among a plurality of heat exchangers that function as a condenser during cooling operation, the heat exchangers being connected in series. A heat exchanger equipped with a refrigerant distributor that can evenly distribute refrigerant to a plurality of flat tubes even when disposed on the downstream side in the flow direction of the refrigerant when connected to form a series refrigerant flow path; And, the purpose is to provide a refrigeration cycle device.

The heat exchanger according to the present disclosure includes a plurality of first flat tubes arranged at intervals in a first direction and whose tube axis direction extends in a second direction intersecting the first direction. 1 heat exchanger, a first refrigerant distributor into which one end portion of the plurality of first flat tubes is inserted, and a second refrigerant distributor into which the other end portion of the plurality of first flat tubes is inserted. The first refrigerant distributor includes a first outer tube extending in the first direction and into which the one ends of the plurality of first flat tubes are inserted; a first inner tube disposed inside the first outer tube, the first inner tube having a plurality of first refrigerant outflow holes spaced apart from each other in the first direction; and the first inner tube penetrating through the plate thickness. and a first partition plate joined to the inner wall of the first outer tube, the second refrigerant distributor extending in the first direction and connecting the plurality of first flat tubes. a second outer tube into which the other end is inserted; and a plurality of outer tubes extending in the first direction, disposed inside the second outer tube, and spaced apart from each other in the first direction. A second inner pipe having two refrigerant outflow holes, and a second partition plate joined to the inner wall of the second outer pipe with the second inner pipe penetrating the plate thickness. .

A refrigeration cycle device according to the present disclosure is a refrigeration cycle device including an outdoor unit, wherein the outdoor unit includes the above heat exchanger, a second heat exchanger, and the heat exchanger and the second heat exchanger. refrigerant piping that connects the heat exchanger and the second heat exchanger; a box-shaped casing that houses the heat exchanger and the second heat exchanger; a blower that blows out the air that has passed through the heat exchanger and the second heat exchanger upward from the top surface of the housing, The containers are arranged along some or all of the four sides of the housing.

According to the heat exchanger and refrigeration cycle device according to the present disclosure, the refrigerant distributor is configured with a double pipe structure, and a plurality of refrigerant outlet holes are arranged in parallel in the inner pipe of the refrigerant distributor. Therefore, even when refrigerant flows into a heat exchanger in a gas-liquid two-phase state, the provision of the refrigerant distributor prevents the situation where the refrigerant is unevenly distributed to multiple flat tubes. It can be suppressed. In addition, by uniformly distributing the refrigerant to the plurality of flat tubes, the required amount of heat exchange becomes uniform over the entire surface of the heat exchanger, and a decrease in heat exchange efficiency can be prevented.

1 is a refrigerant circuit diagram showing the configuration of a refrigeration cycle device 100 according to Embodiment 1. FIG. FIG. 2 is a perspective view showing a connected state of outdoor heat exchanger 3 and outdoor heat exchanger 4 in refrigeration cycle device 100 according to Embodiment 1. FIG. 3 is a sectional view showing the configuration of the outdoor heat exchanger 3 shown in FIG. 2. FIG. 3 is a sectional view showing the configuration of the outdoor heat exchanger 4 shown in FIG. 2. FIG. 4 is a cross-sectional view showing the configuration of a refrigerant distributor 31 provided in the outdoor heat exchanger 3 shown in FIG. 3. FIG. 4 is a cross-sectional view showing the configuration of a refrigerant distributor 32 provided in the outdoor heat exchanger 3 shown in FIG. 3. FIG. 5 is a cross-sectional view showing the configuration of a refrigerant distributor 41 provided in the outdoor heat exchanger 4 shown in FIG. 4. FIG. 5 is a sectional view showing the configuration of a refrigerant distributor 42 provided in the outdoor heat exchanger 4 shown in FIG. 4. FIG. FIG. 2 is a perspective view showing a connected state of outdoor heat exchanger 3 and outdoor heat exchanger 4 in a heating operation state in refrigeration cycle device 100 according to Embodiment 1. FIG. FIG. 3 is a diagram schematically showing a refrigerant distribution operation in a refrigerant distributor 31 provided in the refrigeration cycle device 100 according to the first embodiment. FIG. 3 is a diagram schematically showing a refrigerant distribution operation in

refrigerant distributors

32, 41, and 42 provided in the refrigeration cycle device 100 according to the first embodiment. FIG. 3 is a diagram schematically showing the state of liquid refrigerant in a refrigerant distributor 31 provided in the refrigeration cycle device 100 according to the first embodiment. 3 is a diagram schematically showing the state of liquid refrigerant in

refrigerant distributors

32, 41, and 42 provided in refrigeration cycle device 100 according to Embodiment 1. FIG. 2 is a refrigerant circuit diagram showing the configuration of a refrigeration cycle device 100 according to a first modification of the first embodiment. FIG. 2 is a refrigerant circuit diagram showing the configuration of a refrigeration cycle device 100 according to a first modification of the first embodiment. FIG. 2 is a refrigerant circuit diagram showing the configuration of a refrigeration cycle device 100 according to a second modification of the first embodiment. FIG. FIG. 7 is a diagram showing the flow of refrigerant when the refrigeration cycle device 100 according to the second modification of the first embodiment is in a cooling operation state. The flow of refrigerant is shown when the refrigeration cycle device 100 according to the second modification of the first embodiment is in a heating operation state. FIG. 3 is a perspective view showing a connection state of an outdoor heat exchanger 3C and an outdoor heat exchanger 4C in a refrigeration cycle device 100 according to a second embodiment. FIG. 7 is a perspective view showing the appearance of an outdoor unit 101 provided in a refrigeration cycle device 100 according to a third embodiment. 7 is a plan view schematically showing an example of the configuration of an outdoor unit 101 provided in a refrigeration cycle device 100 according to Embodiment 3. FIG. FIG. 7 is a perspective view showing the appearance of an outdoor unit 101 provided in a refrigeration cycle device 100 according to a modification of the third embodiment. 7 is a plan view schematically showing an example of the configuration of an outdoor unit 101 provided in a refrigeration cycle device 100 according to Embodiment 3. FIG.

Hereinafter, embodiments of a heat exchanger and a refrigeration cycle device according to the present disclosure will be described with reference to the drawings. The present disclosure is not limited to the following embodiments, and can be variously modified without departing from the gist of the present disclosure. Furthermore, the present disclosure includes all combinations of configurations that can be combined among the configurations shown in the following embodiments and modifications thereof. Further, in each figure, the same or corresponding parts are given the same reference numerals, and the description thereof will be omitted or simplified as appropriate. Furthermore, regarding multiple devices of the same type that are distinguished by a subscript (capital letter at the end of the code), if there is no need to distinguish or specify them, the subscript may be omitted. There is. Note that in each drawing, the relative dimensional relationship, shape, etc. of each component may differ from the actual one. The shape, size, arrangement, etc. of the constituent members shown in each drawing can be changed as appropriate within the scope of the present disclosure.

In each figure, the width direction of each outdoor heat exchanger is called the X direction, the height direction is called the Z direction, and the depth direction is called the Y direction. The X direction and the Y direction are, for example, horizontal directions. The Z direction is, for example, an up-down direction, and may be a vertical direction. The X direction is the direction in which the plurality of flat tubes are stacked. The Z direction is the axial direction of the flat tube, and is the direction in which the refrigerant flows. The Y direction is the direction in which air flows. The X direction is sometimes called a "first direction" or a "third direction." The Z direction is sometimes referred to as the "second direction."

Embodiment 1.
<Configuration of refrigeration cycle device 100>
FIG. 1 is a refrigerant circuit diagram showing the configuration of a refrigeration cycle device 100 according to the first embodiment. The refrigeration cycle device 100 has an outdoor unit 101 and an indoor unit 201, and a refrigeration cycle is configured by connecting the outdoor unit 101 and the indoor unit 201 with a refrigerant pipe 310. Note that the refrigerant pipe 310 includes a plurality of refrigerant pipes 300 to 308. Here, when these refrigerant pipes 300 to 308 are collectively called a refrigerant pipe 310. The outdoor unit 101 and the indoor unit 201 are connected through connection ports P1 and P2. Both the connection port P1 and the connection port P2 are configured from refrigerant piping 310. The connection port P1 is an inflow side connection port to the outdoor unit 101 in the cooling operation state of the refrigeration cycle device 100, and an outflow side connection port from the outdoor unit 101 in the heating operation state. The connection port P2 is an outflow side connection port from the outdoor unit 101 in the cooling operation state of the refrigeration cycle device 100, and an inflow side connection port to the outdoor unit 101 in the heating operation state. In the first embodiment, one outdoor unit 101 and one indoor unit 201 are installed, but the number of outdoor units 101 and the number of indoor units 201 are not limited to one. There may be a plurality of each.

In the refrigerant circuit that constitutes the refrigeration cycle device 100, a fluorocarbon refrigerant or an HFO refrigerant, for example, is sealed as a refrigerant.

Examples of fluorocarbon refrigerants include HFC (fluorinated hydrocarbon, hydrofluorocarbon) refrigerants. Examples of HFC refrigerants include difluoromethane (HFC-32, R32), pentafluoroethane (HFC-125, R125), 1,1,1-trifluoroethane (HFC-143a, R143a), 1,1, Examples include 1,2-tetrafluoroethane (HFC-134a, R134a). Further, other examples of the fluorocarbon refrigerant include a mixed refrigerant obtained by mixing the above-mentioned HFC refrigerants. Examples of mixed refrigerants include "R410A" which is a mixed refrigerant of R32 and R125, "R407C" which is a mixed refrigerant of R32, R125 and R134a, and "R404A" which is a mixed refrigerant of R125, R143a and R134a. ” etc.

Examples of the HFO (hydrofluoroolefin) refrigerant include HFO-1234yf, HFO-1234ze (E), and HFO-1234ze (Z).

The refrigerant sealed in the refrigerant circuit that constitutes the refrigeration cycle device 100 is not limited to the above example, and refrigerants used in vapor compression heat pumps can be used. Specifically, for example, CO ₂ refrigerant, HC refrigerant (eg, propane, isobutane refrigerant), ammonia refrigerant, etc. can be used as the refrigerant. Furthermore, a mixed refrigerant of a fluorocarbon refrigerant and an HFO refrigerant, such as a mixed refrigerant of R32 and HFO-1234yf, can also be used as the refrigerant.

(Outdoor unit 101)
The outdoor unit 101 includes a compressor 1, a four-way valve 2, an outdoor heat exchanger 3, an outdoor heat exchanger 4, an expansion valve 5, an expansion valve 6, a solenoid valve 7, a solenoid valve 8, two outdoor blowers 9, an accumulator 10, It also has refrigerant pipes 300 to 306 that connect these components.

The compressor 1 is a fluid machine that compresses sucked low-pressure refrigerant and discharges it as high-pressure refrigerant. The compressor 1 is configured, for example, as a rotary compressor or a scroll compressor. The compressor 1 may be configured, for example, as a compressor with a constant rotational frequency, or may be configured as a compressor equipped with an inverter and whose rotational frequency can be controlled.

The four-way valve 2 is a flow path switching device that is provided on the discharge side of the compressor 1 and switches between the refrigerant circulation direction in the cooling operation state and the refrigerant circulation direction in the heating operation state. The four connection ports 2a to 2d of the four-way valve 2 are connected to the compressor 1, the outdoor heat exchanger 3, the accumulator 10, and the connection port P1 that connects the outdoor unit 101 and the indoor unit 201. Of the four connection ports 2a to 2d of the four-way valve 2, the connection port 2a on the compressor 1 side is the connection port 2b on the outdoor heat exchanger 3 side, or the connection port 2d on the connection port P2 side of the outdoor unit 101. One of them is selected and connected. Furthermore, the connection port that is not selected among the

connection ports

2b and 2d is connected to the connection port 2c that is connected to the accumulator 10. Specifically, during the cooling operation state, the connection port 2a is connected to the connection port 2b, and the connection port 2d is connected to the connection port 2c. In the heating operation state, the connection port 2a is connected to the connection port 2d, and the connection port 2b is connected to the connection port 2c.

The outdoor heat exchanger 3 is a heat exchanger that can exchange heat between the refrigerant flowing inside and air. The outdoor heat exchanger 3 functions as a condenser during cooling operation, and functions as an evaporator during heating operation. The outdoor heat exchanger 3 is connected to the four-way valve 2 by a refrigerant pipe 300, and the refrigerant pipe 300 branches into a refrigerant pipe 301 between the outdoor heat exchanger 3 and the four-way valve 2. Refrigerant pipe 301 is connected to solenoid valve 8 . The outdoor heat exchanger 3 has

connection ports

3a and 3b connected to refrigerant piping. The connection port 3a is connected to the four-way valve 2. A connection port 3b on the opposite side that has passed through the inside from the connection port 3a is connected to the expansion valve 5 via a refrigerant pipe 302. The refrigerant pipe 302 branches into a refrigerant pipe 303 between the outdoor heat exchanger 3 and the expansion valve 5. Refrigerant pipe 303 is connected to solenoid valve 7 . When the wind generated by the outdoor blower 9 passes through the outdoor heat exchanger 3, heat is exchanged between the air passing therethrough and the refrigerant flowing therein. The outdoor blower 9 is configured as, for example, a centrifugal fan such as a sirocco fan or a turbo fan, a cross flow fan, a mixed flow fan, or a propeller fan. Note that the outdoor heat exchanger 3 corresponds to the "second heat exchanger" in the first embodiment.

The outdoor heat exchanger 4 is a heat exchanger that can exchange heat between the refrigerant flowing inside and air. The outdoor heat exchanger 4 functions as a condenser during cooling operation, and functions as an evaporator during heating operation. The outdoor heat exchanger 4 is connected to the solenoid valve 8 via a refrigerant pipe 301. The refrigerant pipe 301 branches into the above-mentioned refrigerant pipe 303 between the outdoor heat exchanger 4 and the solenoid valve 8. The outdoor heat exchanger 4 has

connection ports

4a and 4b connected to refrigerant piping. The connection port 4a is connected to the four-way valve 2 via a solenoid valve 8. A connection port 4 b on the opposite side that has passed through the inside from the connection port 4 a is connected to the expansion valve 6 via a refrigerant pipe 304 . When the wind generated by the outdoor blower 9 passes through the outdoor heat exchanger 4, heat is exchanged between the air passing therethrough and the refrigerant flowing therein. Note that the outdoor heat exchanger 4 corresponds to the "heat exchanger" in the first embodiment. The refrigerant pipe 304 provided with the expansion valve 6 merges with the refrigerant pipe 302 provided with the expansion valve 5. A confluence point between the refrigerant pipe 304 and the refrigerant pipe 302 is connected to the connection port P2. The connection port P2 serves as a connection port on the outflow side from the outdoor unit 101 in the cooling operation state and on the inflow side to the outdoor unit 101 in the heating operation state.

The expansion valve 5 and the expansion valve 6 have a function as a pressure reducing valve or an expansion valve, and reduce the pressure of the refrigerant and expand it. The expansion valve 5 and the expansion valve 6 are configured as a pressure reducing device such as a linear electronic expansion valve whose opening degree can be adjusted in multiple stages or continuously.

The solenoid valve 7 and the solenoid valve 8 have a function of opening and closing the flow path depending on whether or not a voltage is applied, and switch the flow path of the refrigerant by blocking and opening the flow of the refrigerant.

The accumulator 10 is provided in such a way that the outflow side of the accumulator 10 is connected to the suction side of the compressor 1. The accumulator 10 has a function of separating liquid refrigerant and gas refrigerant and a function of storing surplus refrigerant. The inflow side of the accumulator 10 is connected to the connection port 2c of the four-way valve 2 through a refrigerant pipe 306.

The outdoor unit 101 is provided with a control section 11. The control unit 11 controls the operations of the compressor 1 , the four-way valve 2 , the expansion valve 5 , the expansion valve 6 , the solenoid valve 7 , the solenoid valve 8 , and the two outdoor blowers 9 .

The hardware configuration of the control unit 11 will be explained. The control unit 11 is composed of a processing circuit. The processing circuitry consists of dedicated hardware or a processor. The dedicated hardware is, for example, an ASIC (Application Specific Integrated Circuit) or an FPGA (Field Programmable Gate Array). A processor executes programs stored in memory. The control section 11 has a storage section (not shown). The storage unit is composed of memory. Memory can be nonvolatile or volatile semiconductor memory such as RAM (Random Access Memory), ROM (Read Only Memory), flash memory, or EPROM (Erasable Programmable ROM), or disks such as magnetic disks, flexible disks, or optical disks. be.

(Indoor unit 201)
The indoor unit 201 includes an indoor heat exchanger 21, an indoor blower 22, an expansion valve 23, and

refrigerant pipes

307 and 308 that connect these components. The indoor unit 201 and the outdoor unit 101 constitute a refrigeration cycle. The indoor unit 201 supplies cold heat or heat from the outdoor unit 101 to a cooling load or a heating load. Note that the refrigerant load and the heating load are, for example, the indoor space in which the indoor unit 201 is installed.

The indoor heat exchanger 21 is a heat exchanger that can exchange heat between the refrigerant flowing inside and air. The indoor heat exchanger 21 functions as an evaporator during cooling operation, and functions as a condenser during heating operation. Indoor heat exchanger 21 has

connection ports

21a and 21b connected to refrigerant piping. The connection port 21a is connected to the expansion valve 23 via a refrigerant pipe 307. A connection port 21b on the opposite side that has passed inside from the connection port 21a is connected to the connection port P1 via a refrigerant pipe 308. When the wind generated by the indoor blower 22 passes through the indoor heat exchanger 21, heat is exchanged between the air passing therethrough and the refrigerant flowing therein. The indoor blower 22 is configured as, for example, a centrifugal fan such as a sirocco fan or a turbo fan, a cross flow fan, a mixed flow fan, or a propeller fan.

The expansion valve 23 has a function as a pressure reducing valve or an expansion valve, and reduces the pressure of the refrigerant to expand it. The expansion valve 23 is configured, for example, as a pressure reducing device such as a linear electronic expansion valve whose opening degree can be adjusted in multiple stages or continuously.

<Operation of refrigeration cycle device 100>
<Cooling operation status (serial refrigerant flow path)>
When the refrigeration cycle device 100 enters the cooling operation state, the control unit 11 causes the expansion valve 5 to be in the fully closed state, the solenoid valve 7 to be in the open state, the solenoid valve 8 to be in the closed state, and the expansion valve 6 to be in the fully open state. Control. Compressor 1 sucks refrigerant from accumulator 10 and compresses the refrigerant. The compressed refrigerant becomes a gas refrigerant and is discharged from the compressor 1, and flows into the outdoor heat exchanger 3 via the four-way valve 2. As a part of the gas refrigerant is condensed in the outdoor heat exchanger 3, the gas refrigerant enters a gas-liquid two-phase state of gas refrigerant and liquid refrigerant. The gas-liquid two-phase refrigerant passes through the solenoid valve 7 and flows into the outdoor heat exchanger 4 . The refrigerant condensed in the outdoor heat exchanger 4 becomes a liquid refrigerant. The liquid refrigerant passes through the expansion valve 6, flows out of the outdoor unit 101, and flows into the indoor unit 201. In the indoor unit 201, the refrigerant is depressurized by the expansion valve 23 and then evaporated in the indoor heat exchanger 21 to supply cold heat to the air. The refrigerant flows out of the indoor unit 201, flows into the outdoor unit 101, passes through the refrigerant pipe 305, and flows into the four-way valve 2. The refrigerant then flows out from the four-way valve 2, passes through the refrigerant pipe 306, and flows into the accumulator 10. Thereafter, the refrigerant is sucked into the compressor 1 again from the accumulator 10 and circulates through the refrigerant circuit. This results in a refrigerant circuit having a refrigerant flow path in which the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are connected in series.

<Heating operation status (in case of serial refrigerant flow path)>
When the refrigeration cycle device 100 is in the heating operation state, the direction in which the refrigerant flows is opposite to that in the cooling operation state. The control unit 11 controls the expansion valve 5 to be in the fully closed state, the solenoid valve 7 to be in the open state, the solenoid valve 8 to be in the closed state, and the expansion valve 6 to be in the fully open state, as in the case of the cooling operation state. Compressor 1 sucks refrigerant from accumulator 10 and compresses the refrigerant. The compressed refrigerant becomes a gas refrigerant and is discharged from the compressor 1, flows out from the outdoor unit 101 through the four-way valve 2, and flows into the indoor unit 201. In the indoor unit 201, heat exchange is performed in the indoor heat exchanger 21, and the refrigerant is condensed. The refrigerant flows into the expansion valve 23 and is depressurized by the expansion valve 23. Thereafter, the refrigerant flows out of the indoor unit 201 and flows into the outdoor unit 101. In the outdoor unit 101, the refrigerant flows into the outdoor heat exchanger 4 via the expansion valve 6, and is evaporated by heat exchange. Thereafter, the refrigerant passes through the solenoid valve 7 and flows into the outdoor heat exchanger 3. The refrigerant that has undergone further heat exchange in the outdoor heat exchanger 3 becomes a gaseous refrigerant. The gaseous refrigerant flows into the four-way valve 2. The refrigerant then flows out from the four-way valve 2, passes through the refrigerant pipe 306, and flows into the accumulator 10. Thereafter, the refrigerant is sucked into the compressor 1 again from the accumulator 10 and circulates through the refrigerant circuit. This results in a refrigerant circuit having a refrigerant flow path in which the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are connected in series.

<Heating operation status (in case of parallel refrigerant flow path)>
In the above <Heating operation state (in case of serial refrigerant flow path)>, the case where the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are connected in series to form a serial refrigerant flow path has been explained. but not limited to. That is, depending on the operating state of the refrigeration cycle device 100, the connection of the outdoor heat exchanger 3 and the outdoor heat exchanger 4 may be configured to be able to be switched between a serial refrigerant flow path and a parallel refrigerant flow path. . In the heating operation state, a parallel refrigerant flow path may be formed in which the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are connected in parallel. This case will be described later using FIGS. 14 and 15.

<Outdoor heat exchanger 3 and outdoor heat exchanger 4>
FIG. 2 is a perspective view showing the connection state of the outdoor heat exchanger 3 and the outdoor heat exchanger 4 in the refrigeration cycle device 100 according to the first embodiment. In FIG. 2, the refrigeration cycle device 100 is shown in a cooling operation state. In FIG. 2, a refrigerant flow path in which the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are connected in series is expressed by a simple connection using refrigerant piping. In FIG. 2, solid arrows indicate the direction in which the refrigerant flows, and white arrows indicate the direction of the wind generated by the outdoor blower 9 (ie, the airflow direction). FIG. 3 is a sectional view showing the configuration of the outdoor heat exchanger 3 shown in FIG. 2. FIG. 4 is a sectional view showing the configuration of the outdoor heat exchanger 4 shown in FIG. 2. As shown in FIG.

<Configuration of outdoor heat exchanger 3>
First, the configuration of the outdoor heat exchanger 3 will be explained. As shown in FIGS. 2 and 3, the outdoor heat exchanger 3 includes a refrigerant distributor 31, a refrigerant distributor 32, a plurality of heat exchangers 33, and a folded header 34. As shown in FIG. 2, a refrigerant pipe 35 is connected to the refrigerant distributor 31, and a refrigerant pipe 36 is connected to the refrigerant distributor 32.

As shown in FIG. 3, the plurality of heat exchange bodies 33 include a heat exchange body 33A and a heat exchange body 33B. The heat exchanger 33A and the heat exchanger 33B are arranged side by side in the airflow direction and face each other. In other words, the heat exchanger 33A and the heat exchanger 33B are arranged in two layers in a direction along the direction of the wind generated by the outdoor blower 9. Hereinafter, the heat exchange body 33 disposed on the windward side will be referred to as a heat exchange body 33B, and the heat exchange body 33 disposed on the leeward side will be referred to as a heat exchange body 33A. Since the configurations of the heat exchange body 33A and the heat exchange body 33B are basically the same, they will be collectively described as the heat exchange body 33 below.

The heat exchange body 33 is composed of a plurality of flat tubes 37 and a plurality of fins 38. The plurality of flat tubes 37 are arranged side by side in the horizontal direction (namely, the X direction) at intervals from each other. Thereby, the wind generated by the outdoor blower 9 flows between adjacent flat tubes 37 in the direction of the white arrow in FIG. The tube axis direction of the plurality of flat tubes 37 is the Z direction. The refrigerant flows in the Z direction within the flat tube 37. As the refrigerant flows through the flat tube 37, heat exchange is performed between the refrigerant and the air.

The fins 38 are arranged between adjacent flat tubes 37 in the X direction. The fins 38 are joined to the side surfaces of the adjacent flat tubes 37 and conduct heat to the flat tubes 37 . Note that the fins 38 improve heat exchange efficiency between air and refrigerant, and are, for example, corrugated fins. However, the fins 38 are not limited to corrugated fins, and may be flat fins, for example. Further, since heat exchange between the air and the refrigerant is performed on the surface of the flat tube 37, the fins 38 do not necessarily need to be provided. When a plurality of heat exchangers 33 have fins 38, the same fins 38 may be shared between the plurality of heat exchangers 33.

FIG. 5 is a sectional view showing the configuration of the refrigerant distributor 31 provided in the outdoor heat exchanger 3 shown in FIG. 3. FIG. 6 is a sectional view showing the configuration of the refrigerant distributor 32 provided in the outdoor heat exchanger 3 shown in FIG.

As shown in FIG. 3, the plurality of flat tubes 37 included in the heat exchanger 33A have

tube end portions

37a and 37b at both ends in the tube axis direction. A refrigerant distributor 31 is provided below the lower tube end 37a of the tube ends 37a and 37b. The refrigerant distributor 31 is composed of an outer tube 51 and a connecting tube 52, as shown in FIG. The refrigerant distributor 31 has a single pipe structure. The outer tube 51 is composed of a circular tube, and the tube axis direction is the X direction. A plurality of flat tube insertion holes 51e are provided in the upper surface of the outer tube 51. The plurality of flat tube insertion holes 51e are arranged side by side in the X direction at intervals from each other. The plurality of flat tube insertion holes 51e are through holes that penetrate the upper surface of the outer tube 51. The tube end portion 37a of each flat tube 37 is directly inserted into the flat tube insertion hole 51e of the outer tube 51. The outer tube 51 has tube ends 51a and 51b at both ends in the X direction. Of the tube ends 51a and 51b, a closing plate 51c is provided on the tube end 51a side, and a closing plate 51d is provided on the tube end 51b side. The tube ends 51a and 51b are closed by closing

plates

51c and 51d, respectively, and are not open.

The connecting tube 52 is connected to the outer tube 51, as shown in FIG. The tube axis direction of the connecting tube 52 is the Z direction. A lower end portion 52a of the connecting tube 52 is inserted into the outer tube 51. The internal space of the connecting tube 52 and the internal space of the outer tube 51 communicate with each other. As mentioned above, the refrigerant distributor 31 is connected to the refrigerant pipe 35, as shown in FIG. Specifically, the outer pipe 51 of the refrigerant distributor 31 is connected to the refrigerant pipe 35 via the connecting pipe 52. As shown in FIG. 5, the inside of the refrigerant distributor 31 is one space composed of an internal space of the connecting pipe 52 and an internal space of the outer pipe 51. The refrigerant that has flowed into the internal space of the refrigerant distributor 31 from the refrigerant pipe 35 is directly distributed to the plurality of flat tubes 37 included in the heat exchanger 33A.

Although the outer tube 51 is shown here as a single cylinder with both ends covered with

closing plates

51c and 51d, the cross-sectional shape of the outer tube 51 does not have to be circular, and may be rectangular or rectangular. It may be oval. Further, the outer tube 51 does not need to be formed from one cylindrical component. The outer tube 51 is divided into two parts, for example, an upper half into which the flat tube 37 is inserted and an opposite (i.e., lower) half, and by joining the upper and lower parts, the outer tube 51 may be formed. The same applies to the outer tube 53, outer tube 57, and outer tube 61 described below.

A folded header 34 is provided above the tube end 37b of the flat tube 37 of the heat exchanger 33A and above the tube end 37b of the flat tube 37 of the heat exchanger 33B. In this way, the heat exchange body 33A is connected to the heat exchange body 33B via the folded header 34. The folded header 34 allows the refrigerant flowing from the plurality of flat tubes 37 of the heat exchanger 33A to flow out into the plurality of flat tubes 37 of the heat exchanger 33B, thereby controlling the flow of the refrigerant from the bottom to the top. It has the function of turning the flow downward. Specifically, the refrigerant flows from the bottom to the top in the Z direction in the plurality of flat tubes 37 included in the heat exchange body 33A. On the other hand, the refrigerant flows from above to below in the Z direction in the plurality of flat tubes 37 included in the heat exchange body 33B. In this way, the direction in which the refrigerant flows is switched by the folded header 34. Although an example is shown here in which the flat tube 37 on the leeward side and the flat tube 37 on the windward side are connected by the folded header 34, the present invention is not limited to that case. The flat tube 37 does not need to be divided into an upwind side and a leeward side, and may be composed of a single flat tube. The case where the flat tube 37 is composed of one flat tube will be described later in Embodiment 2 using FIG. 19.

As shown in FIG. 3, a refrigerant distributor 32 is provided below the lower tube ends 37a of the plurality of flat tubes 37 included in the heat exchanger 33B. As shown in FIG. 6, the refrigerant distributor 32 includes an outer pipe 53, an inner pipe 54, and a connecting pipe 56. The refrigerant distributor 32 has a double pipe structure. The outer tube 53 is composed of a circular tube, and the tube axis direction is the X direction. A plurality of flat tube insertion holes 53e are provided in the upper surface of the outer tube 53. The plurality of flat tube insertion holes 53e are arranged side by side in the X direction at intervals. The plurality of flat tube insertion holes 53e are through holes that penetrate the upper surface of the outer tube 53. The tube end portion 37a of each flat tube 37 is directly inserted into the flat tube insertion hole 53e of the outer tube 53. Of the tube ends 53a and 53b of the outer tube 53, a closing plate 53c is provided on the tube end 53a side, and a closing plate 53d is provided on the tube end 53b side. The tube ends 53a and 53b are closed by closing

plates

53c and 53d, respectively, and are not open.

The connecting pipe 56 is connected to the outer pipe 53, as shown in FIG. The tube axis direction of the connecting tube 56 is the Z direction. A lower end portion 56a of the connecting tube 56 is inserted into the outer tube 53. The internal space of the connecting tube 56 and the first internal space 53g, which is the internal space on the tube end 53a side of the outer tube 53, communicate with each other. The cross-sectional shape of the first internal space 53g is circular. As mentioned above, the refrigerant distributor 32 is connected to the refrigerant pipe 36, as shown in FIG. Specifically, the outer pipe 53 of the refrigerant distributor 32 is connected to the refrigerant pipe 36 via a connecting pipe 56.

Furthermore, the refrigerant distributor 32 has a double pipe structure, and an inner pipe 54 is arranged inside the outer pipe 53. There is a gap between the inner wall 53f of the outer tube 53 and the outer wall 54f of the inner tube 54, and the gap forms a second internal space 53h of the outer tube 53. The cross-sectional shape of the second internal space 53h is donut-shaped (that is, annular). The inner tube 54 includes a plurality of refrigerant outlet holes 54c arranged in parallel on the side surface. The inner tube 54 is joined to the outer tube 53 via a partition plate 55. The partition plate 55 is arranged between the first internal space 53g of the outer tube 53 and the closing plate 53d. The partition plate 55 divides the first internal space 53g and the second internal space 53h. A through hole 55a is formed in the center of the partition plate 55. Of the tube ends 54a and 54b of the inner tube 54, the tube end 54a is fitted into the through hole 55a. The tube end portion 54a opens toward the first internal space 53g. Therefore, the first internal space 53g and the internal space of the inner tube 54 are in communication with each other. Further, the tube end portion 54b of the inner tube 54 is joined to the closing plate 53d, and is in a closed state. The outer peripheral portion of the partition plate 55 is joined to the inner wall 53f of the outer tube 53. The partition plate 55 is joined to the inner wall 53f of the outer tube 53 and the outer wall 54f of the inner tube 54, as described above. Therefore, the refrigerant flowing inside the refrigerant distributor 32 flows between the first internal space 53g on the side of the pipe end 53a to which the connecting pipe 56 is connected and the closing plate 53d on the side of the opposite pipe end 53b. It is possible to pass between them only via the interior space of the inner tube 54.

<Configuration of outdoor heat exchanger 4>
Next, the configuration of the outdoor heat exchanger 4 will be explained. As shown in FIGS. 2 and 4, the outdoor heat exchanger 4 includes a refrigerant distributor 41, a refrigerant distributor 42, a plurality of heat exchangers 43, and a folded header 44. As shown in FIG. 2, a refrigerant pipe 36 is connected to the refrigerant distributor 41, and a refrigerant pipe 45 is connected to the refrigerant distributor 42.

As shown in FIG. 4, the plurality of heat exchange bodies 43 include a heat exchange body 43A and a heat exchange body 43B. The heat exchange body 43A and the heat exchange body 43B are arranged side by side in the airflow direction and face each other. In other words, the heat exchanger 43A and the heat exchanger 43B are arranged in two layers in a direction along the direction of the wind generated by the outdoor blower 9. Hereinafter, the heat exchange body 43 disposed on the windward side will be referred to as a heat exchange body 43B, and the heat exchange body 43 disposed on the leeward side will be referred to as a heat exchange body 43A. Since the configurations of the heat exchange body 43A and the heat exchange body 43B are basically the same, they will be collectively described as the heat exchange body 43 below.

The heat exchange body 43 is composed of a plurality of flat tubes 47 and a plurality of fins 48. The plurality of flat tubes 47 are arranged in parallel in the horizontal direction (that is, in the X direction) at intervals from each other. Thereby, the wind generated by the outdoor blower 9 flows between adjacent flat tubes 47 in the direction of the white arrow in FIG. The tube axis direction of the plurality of flat tubes 47 is the Z direction. The refrigerant flows in the Z direction within the flat tube 47. As the refrigerant flows through the flat tube 47, heat exchange is performed between the refrigerant and the air.

The fins 48 are arranged between adjacent flat tubes 47 in the X direction. The fins 48 are joined to the side surfaces of the adjacent flat tubes 47 and conduct heat to the flat tubes 47 . Note that the fins 48 improve the heat exchange efficiency between the air and the refrigerant, and for example, corrugated fins are used. However, the fins 48 are not limited to corrugated fins, and may be flat fins, for example. Furthermore, since heat exchange between the air and the refrigerant is performed on the surface of the flat tube 47, the fins 48 do not necessarily need to be provided. When a plurality of heat exchangers 43 have fins 48, the same fins 48 may be shared between the plurality of heat exchangers 43.

FIG. 7 is a sectional view showing the configuration of the refrigerant distributor 41 provided in the outdoor heat exchanger 4 shown in FIG. 4. FIG. 8 is a sectional view showing the configuration of the refrigerant distributor 42 provided in the outdoor heat exchanger 4 shown in FIG. 4.

As shown in FIG. 4, a refrigerant distributor 41 is provided below the lower tube end 47a of the tube ends 47a and 47b of the plurality of flat tubes 47 included in the heat exchanger 43A. The refrigerant distributor 41 is composed of an outer pipe 57, an inner pipe 58, and a connecting pipe 60, as shown in FIG. The refrigerant distributor 41 has a double pipe structure. The outer tube 57 is composed of a circular tube, and the tube axis direction is the X direction. A plurality of flat tube insertion holes 57e are provided in the upper surface of the outer tube 57. The plurality of flat tube insertion holes 57e are arranged side by side in the X direction at intervals from each other. The plurality of flat tube insertion holes 57e are through holes that penetrate the upper surface of the outer tube 57. The tube end portion 47a of each flat tube 47 is directly inserted into the flat tube insertion hole 57e of the outer tube 57. Of the tube ends 57a and 57b of the outer tube 57, a closing plate 57c is provided on the tube end 57a side, and a closing plate 57d is provided on the tube end 57b side. The tube ends 57a and 57b are closed by closing

plates

57c and 57d, respectively, and are not open.

The connecting tube 60 is connected to the outer tube 57, as shown in FIG. The tube axis direction of the connecting tube 60 is the Z direction. A lower end 60a of the connecting tube 60 is inserted into the outer tube 57. The internal space of the connecting tube 60 and the first internal space 57g, which is the internal space on the tube end 57a side of the outer tube 57, communicate with each other. The cross-sectional shape of the first internal space 57g is circular. As described above, the refrigerant distributor 41 is connected to the refrigerant pipe 36, as shown in FIG. Specifically, the outer pipe 57 of the refrigerant distributor 41 is connected to the refrigerant pipe 36 via the connecting pipe 60.

Further, the refrigerant distributor 41 has a double pipe structure, and an inner pipe 58 is arranged inside the outer pipe 57. There is a gap between the inner wall 57f of the outer tube 57 and the outer wall 58f of the inner tube 58, and the gap forms a second internal space 57h of the outer tube 57. The cross-sectional shape of the second internal space 57h is donut-shaped (that is, annular). The inner tube 58 includes a plurality of refrigerant outlet holes 58c arranged in parallel on the side surface. The inner diameter of the coolant outlet hole 58c may be the same as or different from the inner diameter of the coolant outlet hole 54c shown in FIG. 6 and the inner diameter of the coolant outlet hole 62c shown in FIG. 8. The inner tube 58 is joined to the outer tube 57 via a partition plate 59. The partition plate 59 is arranged between the first internal space 57g of the outer tube 57 and the closing plate 57d. The partition plate 59 divides the first internal space 57g and the second internal space 57h. A through hole 59a is formed in the center of the partition plate 59. Of the tube ends 58a and 58b of the inner tube 58, the tube end 58a is fitted into the through hole 59a. The tube end portion 58a opens toward the first internal space 57g. Therefore, the first internal space 57g and the internal space of the inner tube 58 are in communication with each other. Further, the tube end portion 58b of the inner tube 58 is joined to the closing plate 57d, and is in a closed state. The outer peripheral portion of the partition plate 59 is joined to the inner wall 57f of the outer tube 57. The partition plate 59 is joined to the inner wall 57f of the outer tube 57 and the outer wall 58f of the inner tube 58, as described above. Therefore, the refrigerant flowing inside the refrigerant distributor 41 flows between the first internal space 57g on the side of the pipe end 57a to which the connecting pipe 60 is connected and the closing plate 57d on the side of the opposite pipe end 58b. It is possible to pass between them only via the interior space of the inner tube 58.

A folded header 44 is provided above the upper tube end 47b of the flat tube 47 of the heat exchanger 43A and above the upper tube end 47b of the flat tube 47 of the heat exchanger 43B. In this way, the heat exchange body 43A is connected to the heat exchange body 43B via the folded header 44. The folded header 44 allows the refrigerant flowing from the plurality of flat tubes 47 of the heat exchanger 43A to flow out into the plurality of flat tubes 47 of the heat exchanger 43B, thereby controlling the flow of the refrigerant from the bottom to the top. It has the function of turning the flow downward. Specifically, the refrigerant flows from the bottom to the top in the Z direction in the plurality of flat tubes 47 included in the heat exchange body 43A. On the other hand, the refrigerant flows from above to below in the Z direction in the plurality of flat tubes 47 included in the heat exchange body 43B. In this way, the direction in which the refrigerant flows is switched by the folded header 44. Although an example is shown here in which the flat tube 47 on the leeward side and the flat tube 47 on the windward side are connected by the folded header 44, the present invention is not limited to that case. The flat tube 47 does not need to be divided into an upwind side and a leeward side, and may be composed of a single flat tube. The case where the flat tube 47 is composed of one flat tube will be described later in Embodiment 2 using FIG. 19.

As shown in FIG. 4, a refrigerant distributor 42 is provided below the lower tube end 47a of the tube ends 47a and 47b of the plurality of flat tubes 47 included in the heat exchanger 43B. The refrigerant distributor 42 is composed of an outer pipe 61, an inner pipe 62, and a connecting pipe 64, as shown in FIG. The refrigerant distributor 42 has a double pipe structure. The outer tube 61 is composed of a circular tube, and the tube axis direction is the X direction. A plurality of flat tube insertion holes 61e are provided in the upper surface of the outer tube 61. The plurality of flat tube insertion holes 61e are arranged side by side in the X direction at intervals from each other. The plurality of flat tube insertion holes 61e are through holes that penetrate the upper surface of the outer tube 61. The tube end portion 47a of each flat tube 47 is directly inserted into the flat tube insertion hole 61e of the outer tube 61. Of the tube ends 61a and 61b of the outer tube 61, a closing plate 61c is provided on the tube end 61a side, and a closing plate 61d is provided on the tube end 61b side. The tube ends 61a and 61b are closed by closing

plates

61c and 61d, respectively, and are not open.

The connecting tube 64 is connected to the outer tube 61, as shown in FIG. The tube axis direction of the connecting tube 64 is the Z direction. A lower end 64a of the connecting tube 64 is inserted into the outer tube 61. The internal space of the connecting tube 64 and the first internal space 61g, which is the internal space on the tube end 61a side of the outer tube 61, communicate with each other. The cross-sectional shape of the first internal space 61g is circular. As described above, the refrigerant distributor 42 is connected to the refrigerant pipe 45, as shown in FIG. Specifically, the outer pipe 61 of the refrigerant distributor 42 is connected to the refrigerant pipe 45 via the connecting pipe 64.

Furthermore, the refrigerant distributor 42 has a double pipe structure, and an inner pipe 62 is arranged inside the outer pipe 61. There is a gap between the inner wall 61f of the outer tube 61 and the outer wall 62f of the inner tube 62, and the gap forms a second internal space 61h of the outer tube 61. The cross-sectional shape of the second internal space 61h is donut-shaped (that is, annular). The inner tube 62 includes a plurality of refrigerant outlet holes 62c arranged in parallel on the side surface. The inner tube 62 is joined to the outer tube 61 via a partition plate 63. The partition plate 63 is arranged between the first internal space 61g of the outer tube 61 and the closing plate 61d. The partition plate 63 divides the first internal space 61g and the second internal space 61h. A through hole 63a is formed in the center of the partition plate 63. Of the tube ends 62a and 62b of the inner tube 62, the tube end 62a is fitted into the through hole 63a. The tube end portion 62a opens toward the first internal space 61g. Therefore, the first internal space 61g and the internal space of the inner tube 62 are in communication with each other. Further, the tube end portion 62b of the inner tube 62 is joined to the closing plate 61d, and is in a closed state. The outer peripheral portion of the partition plate 63 is joined to the inner wall 61f of the outer tube 61. The partition plate 63 is joined to the inner wall 61f of the outer tube 61 and the outer wall 62f of the inner tube 62, as described above. Therefore, the refrigerant flowing inside the refrigerant distributor 42 flows between the first internal space 61g on the side of the pipe end 61a to which the connecting pipe 64 is connected and the closing plate 61d on the side of the opposite pipe end 61b. It is possible to pass between them only through the interior space of the inner tube 62.

In this way, the configurations of the

refrigerant distributors

41 and 42 are similar to the refrigerant distributor 32 shown in FIG. It consists of

tubes

60 and 64. A refrigerant pipe 36 is connected to the refrigerant distributor 41 via a connecting pipe 60, and a refrigerant pipe 45 is connected to the refrigerant distributor 42 via a connecting pipe 64.

Note that the outdoor heat exchanger 4 is sometimes called a "heat exchanger". The heat exchange body 43 is sometimes referred to as a "first heat exchange body." The flat tube 47 is sometimes called a "first flat tube." Further, the flat tube 47 connected to the refrigerant distributor 41 is sometimes referred to as a "first flat tube on the leeward side", and the flat tube 47 connected to the refrigerant distributor 42 is sometimes referred to as a "first flat tube on the windward side". Sometimes. Refrigerant distributor 41 may be referred to as a "first refrigerant distributor," and refrigerant distributor 42 may be referred to as a "second refrigerant distributor." Further, the outer tube 57 is referred to as a "first outer tube," the inner tube 58 is referred to as a "first inner tube," the refrigerant outlet hole 58c is referred to as a "first refrigerant outlet hole," and the partition plate 59 is referred to as a "first partition plate." There is. Further, the outer tube 61 is referred to as a "second outer tube," the inner tube 62 is referred to as a "second inner tube," the refrigerant outlet hole 62c is referred to as a "second refrigerant outlet hole," and the partition plate 63 is referred to as a "second partition plate." There is. Further, the wrap header 44 is sometimes referred to as a "first wrap header." Furthermore, the tube end 47a of the flat tube 47 inserted into the refrigerant distributor 41 is sometimes referred to as "one end of the first flat tube", and the tube end 47a of the flat tube 47 inserted into the refrigerant distributor 42 is referred to as "one end of the first flat tube". is sometimes referred to as "the other end of the first flat tube."

Additionally, the outdoor heat exchanger 3 is sometimes called a "second heat exchanger". The heat exchange body 33 is sometimes referred to as a "second heat exchange body." The flat tube 37 is sometimes called a "second flat tube." Further, the flat tube 37 connected to the refrigerant distributor 31 is sometimes referred to as a "second flat tube on the leeward side", and the flat tube 37 connected to the refrigerant distributor 32 is sometimes referred to as a "second flat tube on the windward side". Sometimes. The refrigerant distributor 31 is sometimes called a "third refrigerant distributor," and the refrigerant distributor 32 is sometimes called a "fourth refrigerant distributor." Further, the outer tube 51 is sometimes referred to as a "third outer tube." The outer pipe 53 is sometimes called a "fourth outer pipe," the inner pipe 54 is sometimes called a "fourth inner pipe," the refrigerant outlet hole 54c is sometimes called a "fourth refrigerant outlet hole," and the partition plate 55 is sometimes called a "fourth partition plate." . Further, the wrap header 34 is sometimes referred to as a "second wrap header." Further, the tube end 37a of the flat tube 37 inserted into the refrigerant distributor 31 is sometimes referred to as "one end of the second flat tube", and the tube end 37a of the flat tube 37 inserted into the refrigerant distributor 32 is sometimes referred to as "one end of the second flat tube". is sometimes referred to as "the other end of the second flat tube".

<Flow of refrigerant in outdoor heat exchanger 3 and outdoor heat exchanger 4>
Next, the flow of refrigerant in the outdoor heat exchanger 3 and the outdoor heat exchanger 4 will be explained.

<Refrigerant flow during cooling operation>
First, the flow of refrigerant in the cooling operation state will be explained. As described above, FIG. 2 is a perspective view showing the connection state between the outdoor heat exchanger 3 and the outdoor heat exchanger 4 in the cooling operation state and the flow of refrigerant. As shown in FIG. 2, among the four connection pipes provided in the outdoor heat exchanger 3 and the outdoor heat exchanger 4, that is, the connection pipe 52, the connection pipe 56, the connection pipe 60, and the connection pipe 64, the connection pipe 56 and The pipe 60 is connected to the refrigerant pipe 36 . The refrigerant flowing from the refrigerant pipe 35 connected to the connecting pipe 52 is partially condensed in the outdoor heat exchanger 3 to become a gas-liquid two-phase state, and flows out into the refrigerant pipe 36 . Thereafter, the refrigerant flows into the outdoor heat exchanger 4 in a gas-liquid two-phase state. In the outdoor heat exchanger 4, the refrigerant first flows into the refrigerant distributor 41. The refrigerant distributor 41 has a double pipe structure, and the inner pipe 58 thereof has a large number of refrigerant outlet holes 58c arranged in parallel. The refrigerant that has flowed into the refrigerant distributor 41 flows out from the refrigerant outlet hole 58c into the second internal space 57h when passing through the interior of the inner tube 58. Thereafter, it is distributed to each flat tube 47 from the second internal space 57h. In this way, by providing the refrigerant outlet hole 58c in the inner tube 58, the refrigerant is evenly distributed to each flat tube 47 of the heat exchanger 43A. The refrigerant condensed inside the heat exchanger 43A and the heat exchanger 43B flows out into the refrigerant pipe 45 through the refrigerant distributor 42.

As described above, the refrigerant distributor 41 on the inflow side of the outdoor heat exchanger 4 located on the downstream side among the plurality of outdoor heat exchangers 3 and outdoor heat exchangers 4 forming serial refrigerant flow paths during cooling operation. has a double tube structure. The inner pipe 58 of the refrigerant distributor 41 has a large number of refrigerant outlet holes 58c arranged in parallel. Thereby, in the outdoor heat exchanger 4 located on the downstream side, it is possible to improve the uniformity of distribution of the gas-liquid two-phase refrigerant to the heat exchanger 43A.

Specifically, in the refrigerant distributor 41, the refrigerant flows into the first internal space 57g of the outer tube 57 via the connecting pipe 60. Thereafter, the refrigerant once enters the inner tube 58 from the first inner space 57g, and flows out from the inner tube 58's many juxtaposed refrigerant outlet holes 58c to the second inner space 57h of the outer tube 57. do. At this time, in the outer tube 57, the second internal space 57h is separated from the first internal space 57g by a partition plate 59. Therefore, the refrigerant that has flowed into the second internal space 57h of the outer tube 57 does not flow into the first internal space 57g, but instead passes through the flat tube insertion holes 57e into the plurality of flat tubes connected to the outer tube 57. It flows out into pipe 47.

Here, the refrigerant distribution operation in the single-pipe structure and the double-pipe structure will be explained. FIG. 10 is a diagram schematically showing a refrigerant distribution operation in the refrigerant distributor 31 provided in the refrigeration cycle device 100 according to the first embodiment. FIG. 11 is a diagram schematically showing a refrigerant distribution operation in the

refrigerant distributors

32, 41, and 42 provided in the refrigeration cycle device 100 according to the first embodiment. In addition, in FIG. 10 and FIG. 11, in order to make it easy to understand, the case where the

refrigerant outflow holes

54c, 58c, and 62c are opened directly downward is illustrated.

As shown in FIG. 10, in the case of a single-pipe structure, the refrigerant flows in from one location (i.e., the connecting pipe 52) and flows out from multiple locations (i.e., the flat tube insertion hole 51e). Therefore, there is a strong tendency for a large amount of the refrigerant to flow out from the flat tube insertion hole 51e located close to the connecting tube 52.

On the other hand, as shown in FIG. 11, in the case of a double-pipe structure, the refrigerant flows from multiple locations (i.e., refrigerant outlet holes 54c, 58c, 62c of the

inner pipes

54, 58, 62) to the

outer pipes

53, 57, 61 and flows out from multiple locations (ie, flat

tube insertion holes

53e, 57e, and 61e). Therefore, even if the outflow from the

inner tubes

54, 58, 62 is uneven, the uniformity of refrigerant distribution is improved compared to the case where the

inner tubes

54, 58, 62 are not provided.

FIG. 12 is a diagram schematically showing the state of liquid refrigerant in the refrigerant distributor 31 provided in the refrigeration cycle device 100 according to the first embodiment. FIG. 13 is a diagram schematically showing the state of liquid refrigerant in the

refrigerant distributors

32, 41, and 42 provided in the refrigeration cycle device 100 according to the first embodiment. In addition, in FIG. 12 and FIG. 13, in order to make it easy to understand, the case where the

refrigerant outflow holes

54c, 58c, and 62c are opened directly downward is illustrated.

12 and 13 show a case where gas-liquid two-phase refrigerant flows into the

refrigerant distributors

31, 32, 41, and 42. In the case of a single-pipe structure, as shown in FIG. 12, liquid refrigerant may accumulate under the outer tube 51, reducing the amount of refrigerant circulating in the refrigerant circuit. On the other hand, in the case of a double pipe structure, as shown in FIG. 13, the refrigerant is spouted from a plurality of refrigerant outlet holes 54c, 58c, and 62c provided in the

inner pipes

54, 58, and 62. This disturbs the liquid refrigerant staying inside the

outer tubes

53, 57, and 61, so that it is possible to suppress the liquid refrigerant from staying below the outer tube 51. As a result, the amount of liquid refrigerant remaining in the outer tube 51 is reduced, so that the refrigerant can be efficiently circulated within the refrigerant circuit.

Note that although the examples in FIGS. 12 and 13 show the case of separate flows in which the gas refrigerant and the liquid refrigerant flow separately, the way the refrigerant flows is not limited to the examples in FIGS. 12 and 13. Another example of the flow of the refrigerant inside the

refrigerant distributors

31, 32, 41, 42 is, for example, an annular flow. When the refrigerant flows in an annular flow, the liquid refrigerant is annular and the annular liquid refrigerant flow covers the gas refrigerant.

The refrigerant that flows out from the refrigerant outlet holes 54c, 58c, and 62c provided in the

inner tubes

54, 58, and 62 is mainly a gas refrigerant or a liquid refrigerant. Which refrigerant mainly flows out from the refrigerant outlet holes 54c, 58c, and 62c varies depending on the state of the refrigerant flowing inside the

inner pipes

54, 58, and 62, and the arrangement and position of the refrigerant outlet holes 54c, 58c, and 62c. do. For example, when the refrigerant flows in an annular flow, the liquid refrigerant covers the

refrigerant outflow holes

54c, 58c, and 62c, so that the liquid refrigerant mainly flows out from the

refrigerant outflow holes

54c, 58c, and 62c. On the other hand, when the refrigerant flows as a separated flow, the determination is made depending on whether the refrigerant outlet holes 54c, 58c, and 62c open upward or downward. That is, in the case of separated flows, when the

refrigerant outflow holes

54c, 58c, and 62c are open upward, the gas refrigerant mainly flows out from the

refrigerant outflow holes

54c, 58c, and 62c. In the case of separated flow, when the

refrigerant outflow holes

54c, 58c, and 62c open downward, liquid refrigerant mainly flows out from the

refrigerant outflow holes

54c, 58c, and 62c. Also, depending on whether the position of each

refrigerant outlet hole

54c, 58c, 62c is on the inlet side or the back side of the

inner pipe

54, 58, 62, the refrigerant flowing out from each

refrigerant outlet hole

54c, 58c, 62c may be gas refrigerant. The liquid refrigerant changes. Even in the case of an annular flow, the liquid refrigerant mainly flows out closer to the inlet side of the

inner pipes

54, 58, 62. If more liquid refrigerant flows out, the degree of dryness of the refrigerant will change, so gas refrigerant becomes the main flow toward the back of the

inner pipes

54, 58, and 62. When the liquid refrigerant decreases to such an extent that the annular flow cannot be maintained, the gas refrigerant mainly flows out from the refrigerant outlet holes 54c, 58c, and 62c.

<Refrigerant flow during heating operation>
Next, the flow of refrigerant in the heating operation state will be explained. FIG. 9 is a perspective view showing the connection state of the outdoor heat exchanger 3 and the outdoor heat exchanger 4 in the heating operation state in the refrigeration cycle device 100 according to the first embodiment. In FIG. 9, the refrigerant flow path connecting the outdoor heat exchanger 3 and the outdoor heat exchanger 4 is expressed by a simple connection using refrigerant piping. In FIG. 9, solid arrows indicate the direction in which the refrigerant flows, and white arrows indicate the direction of the wind generated by the outdoor blower 9.

As can be seen by comparing FIG. 2 and FIG. 9, the direction in which the refrigerant flows in the heating operation state is opposite to that in the cooling operation. In the heating operation state, refrigerant flows into the outdoor heat exchanger 3 and the outdoor heat exchanger 4 through the refrigerant distributor 32 and the refrigerant distributor 42 . Both the refrigerant distributor 32 and the refrigerant distributor 42 are refrigerant distributors having a double pipe structure.

In the refrigerant distributor 32, the refrigerant flows into the first internal space 53g of the outer tube 53 via the connecting pipe 56. Thereafter, the refrigerant once enters the inner tube 54 from the first inner space 53g, and flows out from the inner tube 54's many juxtaposed refrigerant outlet holes 54c to the second inner space 53h of the outer tube 53. do. At this time, in the outer tube 53, the second internal space 53h is separated from the first internal space 53g by a partition plate 55. Therefore, the refrigerant that has flowed into the second internal space 53h of the outer tube 53 does not flow into the first internal space 53g, but instead passes through the flat tube insertion holes 53e into the plurality of flat tubes connected to the outer tube 53. It flows out into pipe 37.

In the refrigerant distributor 42, the refrigerant flows into the first internal space 61g of the outer tube 61 via the connecting pipe 64. Thereafter, the refrigerant once enters the inner tube 62 from the first inner space 61g, and flows out from the inner tube 62's many juxtaposed refrigerant outlet holes 62c to the second inner space 61h of the outer tube 61. do. At this time, in the outer tube 61, the second internal space 61h is separated from the first internal space 61g by a partition plate 63. Therefore, the refrigerant that has flowed into the second internal space 61h of the outer tube 61 does not flow into the first internal space 61g, but instead passes through the flat tube insertion holes 53e into the plurality of flat tubes connected to the outer tube 61. It flows out into pipe 47.

When the refrigerant flows out from the outdoor heat exchanger 3 and the outdoor heat exchanger 4 during the heating operation state, it passes through the refrigerant distributor 31 and the refrigerant distributor 41. While the refrigerant distributor 31 is a refrigerant distributor having a single pipe structure, the refrigerant distributor 41 is a refrigerant distributor having a double pipe structure. The refrigerant flowing into the refrigerant distributor 31 from the flat tube 37 passes through the inside of the outer tube 51 and flows out via the connecting tube 52. On the other hand, the refrigerant that has flowed into the refrigerant distributor 41 from the flat tube 47 first flows into the second internal space 61h of the outer tube 57, and then flows into the inner tube 58 from the refrigerant outlet hole 58c. Then, the refrigerant passes through the inside of the inner tube 58 and flows out from the inner tube 58 into the first internal space 57g partitioned by the partition plate 59. The refrigerant flows out of the refrigerant distributor 41 from the first internal space 57g via the connecting pipe 60.

During heating operation, the outdoor heat exchanger 3 and the outdoor heat exchanger 4 function as an evaporator. As described above, the refrigerant distributor 41 provided on the outflow side of the outdoor heat exchanger 4 is configured with a double pipe, and has a large number of refrigerant outflow holes 58c arranged in parallel in the inner pipe 58. There is. Therefore, compared to the case where a refrigerant distributor 41 with a single-pipe structure is used as the refrigerant distributor 41, in the case of a refrigerant distributor 41 with a double-pipe structure, the pressure loss in the refrigerant flow path becomes higher, and the pressure loss of the compressor 1 increases. The pressure on the suction side decreases. This causes a problem in that the required amount of work of the compressor 1 increases and the performance of the refrigeration cycle device decreases.

In order to deal with the above problem, the specifications of the refrigerant distributor 41 and the refrigerant distributor 42 included in the outdoor heat exchanger 4 are set such that the uniformity of refrigerant distribution in the cooling operation state and the uniformity of refrigerant distribution in the outdoor heat exchanger 4 in the heating operation state are determined. It is desirable to determine the balance by taking into account the pressure loss that occurs. In other words, part or all of the specifications in the refrigerant distributor 41 are the same as those in the refrigerant distributor 42 so that pressure loss can be suppressed in the heating operation state while ensuring uniformity of the refrigerant in the cooling operation state. Some or all of them may be designed differently.

Candidates for specifications of the refrigerant distributor 41 and the refrigerant distributor 42 to be changed here include the following items.
- Diameter of refrigerant outlet holes 58c and 62c (i.e. hole diameter)
- Arrangement interval of refrigerant outlet holes 58c and 62c - Arrangement position of refrigerant outlet holes 58c and 62c - Number of refrigerant outlet holes 58c and 62c - Diameter (inner diameter or outer diameter) of

inner pipes

58 and 62
- Diameter of outer tubes 57 and 61 (inner diameter or outer diameter)

When changing the specifications of the refrigerant distributor 41 and the refrigerant distributor 42, it is desirable to make decisions as appropriate based on data from simulations, prototype experiments, etc. Specifically, by increasing the diameter or number of the refrigerant outlet holes 58c and 62c, an increase in pressure loss can be suppressed and the refrigerant distribution characteristics change. In accordance with the changed characteristics, the spacing or position of the refrigerant outlet holes 58c and 62c is changed to suppress deterioration in uniformity of distribution during cooling operation. Furthermore, increasing the diameters of the inner tube 58 and the inner tube 62 and the diameters of the outer tube 57 and the outer tube 61 contributes to suppressing pressure loss. In this way, the specifications of the refrigerant distributor 41 and the refrigerant distributor 42 are convenient specifications considering the balance between the uniformity of refrigerant distribution in the cooling operation state and the pressure loss in the heating operation state. It is desirable to make adjustments accordingly.

In this way, the specifications of the refrigerant distributor 41 and the specifications of the refrigerant distributor 42 are related to the uniformity of refrigerant distribution when the

outdoor heat exchangers

3 and 4 function as condensers, and the conditions regarding the uniformity of refrigerant distribution when the

outdoor heat exchangers

3 and 4 function as condensers. It is determined based on the pressure loss that occurs when 4 functions as an evaporator.

Further, part or all of the specifications of the

refrigerant distributor

41 or 42 may be designed to be different from part or all of the specifications of the refrigerant distributor 32 of the outdoor heat exchanger 3. In that case, for example, the refrigerant distributor 41 and the refrigerant distributor 42 are arranged so that the total pressure loss of the refrigerant distributor 41 and the refrigerant distributor 42 is smaller than that of the refrigerant distributor 32 that the outdoor heat exchanger 3 has. The above specifications may be changed.

In this way, by adjusting the specifications of the refrigerant distributor 41 and the refrigerant distributor 42, the effect of improving the uniformity of refrigerant distribution to the heat exchangers 43A and 43B during cooling operation described above is greatly impaired. Without this, it is possible to suppress the increase in pressure loss during heating described in the previous section.

As described above, during heating operation, the plurality of outdoor heat exchangers 3 and outdoor heat exchangers 4 that form serial refrigerant flow paths both function as an evaporator. Therefore, the refrigerant distributor 42 on the inflow side of the outdoor heat exchanger 4 located on the upstream side and the refrigerant distributor 32 on the inflow side of the outdoor heat exchanger 3 located on the downstream side have a double pipe structure. There is. The inner pipe 62 of the refrigerant distributor 42 and the inner pipe 54 of the refrigerant distributor 32 each have a large number of refrigerant outflow holes 62c and refrigerant outflow holes 54c arranged in parallel. As a result, in the outdoor heat exchanger 4 located on the upstream side and the outdoor heat exchanger 3 located on the downstream side, the refrigerant in the gas-liquid two-phase state is evenly distributed to the heat exchanger 43B and the heat exchanger 33B. can improve sex.

<Modification 1>
In the above description, a case has been described in which the outdoor heat exchanger 3 and the outdoor heat exchanger 4 form a serial refrigerant flow path in both the cooling operation and the heating operation. However, it is not limited to that case. The circuit is configured such that the two

outdoor heat exchangers

3 and 4 can be switched between a series refrigerant flow path and a parallel refrigerant flow path depending on the operating state, forming a serial refrigerant flow path during cooling operation and forming a serial refrigerant flow path during heating operation. Parallel refrigerant flow paths may be formed.

FIG. 14 is a refrigerant circuit diagram showing the configuration of refrigeration cycle device 100 according to Modification 1 of Embodiment 1. FIG. 14 shows the flow of refrigerant when the refrigeration cycle device 100 according to Modification Example 1 is in a cooling operation state. FIG. 15 is a refrigerant circuit diagram showing the configuration of refrigeration cycle device 100 according to Modification 1 of Embodiment 1. FIG. 15 shows the flow of refrigerant when the refrigeration cycle device 100 according to Modification 1 is in a heating operation state.

<Cooling operation status (in case of serial refrigerant flow path)>
In Modification 1, when the refrigeration cycle device 100 is in the cooling operation state, as shown in FIG. 14, the flow of the refrigerant is the same as in the cooling operation state described above using FIG. Therefore, the explanation thereof will be omitted here. In this manner, in the first modification, during the cooling operation state, the outdoor heat exchanger 3 and the outdoor heat exchanger 4 form a series refrigerant flow path, as in the first embodiment.

<Heating operation status (in case of parallel refrigerant flow path)>
In Modification 1, when the refrigeration cycle device 100 enters the heating operation state, as shown in FIG. 15, the outdoor heat exchanger 3 and the outdoor heat exchanger 4 form a parallel refrigerant flow path connected in parallel. In that case, the control unit 11 controls the

expansion valves

5 and 6 to be in the open state, the solenoid valve 7 to be in the closed state, and the solenoid valve 8 to be in the open state. Compressor 1 sucks refrigerant from accumulator 10 and compresses the refrigerant. The compressed refrigerant becomes a gas refrigerant and is discharged from the compressor 1, flows out from the outdoor unit 101 via the four-way valve 2 and the refrigerant pipe 305, and flows into the indoor unit 201. In the indoor unit 201, the refrigerant is condensed in the indoor heat exchanger 21 and supplies heat to the air. The refrigerant then flows into the outdoor unit 101 after flowing out of the indoor unit 201. In the outdoor unit 101, the refrigerant branches into a refrigerant pipe 302 and a refrigerant pipe 304, and flows into the expansion valve 5 and the expansion valve 6, respectively. The refrigerant that has been depressurized and expanded by the

expansion valves

5 and 6 flows into the outdoor heat exchanger 3 and the outdoor heat exchanger 4, respectively, and evaporates. The refrigerant flowing out from the outdoor heat exchanger 4 passes through the electromagnetic valve 8 and joins with the refrigerant flowing out from the outdoor heat exchanger 3. Thereafter, the combined refrigerant flows into the accumulator 10 via the four-way valve 2 and the refrigerant pipe 306. It is sucked into the compressor 1 again from the accumulator 10 and circulates through the refrigerant circuit. This results in a refrigerant circuit having a refrigerant flow path in which the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are connected in parallel.

In the case of Modification 1, the two

outdoor heat exchangers

3 and 4 are connected in parallel during heating operation. Therefore, even if outdoor heat exchangers with similar specifications are used as the two

outdoor heat exchangers

3 and 4, due to the difference in pressure loss due to the difference in the

refrigerant distributors

32 and 42, the two

outdoor heat exchangers

3 and 4 There is a possibility that the distribution of refrigerant to 4 may be biased. In that case, the uniformity of distribution to the

outdoor heat exchangers

3 and 4 can be improved by adjusting the opening degrees of the

expansion valves

5 and 6 by the control unit 11. Specifically, among the

expansion valves

5 and 6, the opening degree of the

expansion valve

5 or 6 on the side where more refrigerant flows is reduced, and the opening degree of the

expansion valve

5 or 6 on the side where refrigerant is less likely to flow is reduced. Increase the opening.

<Modification 2>
By the way, in the above description of Embodiment 1, the case where the number of outdoor heat exchangers is two was described, but even if the number of outdoor heat exchangers is three or more, the structure of Embodiment 1 can be applied. is applicable. Specifically, when n outdoor heat exchangers can form a series refrigerant flow path by controlling the refrigerant circuit, the outdoor heat exchanger 3 and the upstream outdoor heat exchanger when functioning as a condenser are Using a similar configuration, a configuration similar to that of the outdoor heat exchanger 4 is used for the outdoor heat exchanger on the downstream side. It goes without saying that this provides the same effects as in the first embodiment. Here, n is a natural number of 3 or more. Furthermore, the first embodiment is a case where n=2. Therefore, to summarize the first embodiment and its modifications, n is a natural number of 2 or more.

FIG. 16 is a refrigerant circuit diagram showing the configuration of a refrigeration cycle device 100 according to a second modification of the first embodiment. FIG. 17 is a diagram showing the flow of refrigerant when the refrigeration cycle device 100 according to the second modification of the first embodiment is in a cooling operation state. FIG. 18 shows the flow of refrigerant when the refrigeration cycle device 100 according to the second modification of the first embodiment is in a heating operation state.

The difference between the configuration in FIG. 16 and the configuration in FIG. 1 is that in FIG. 16, two

outdoor heat exchangers

3A and 3B are provided instead of the outdoor heat exchanger 3 in FIG. Two

outdoor heat exchangers

3A and 3B are connected in parallel. Both

outdoor heat exchangers

3A and 3B have the same configuration as outdoor heat exchanger 3 in FIG. 1. Since the other configurations are the same as those in FIG. 1, their explanation will be omitted here.

<Flow of refrigerant in outdoor heat exchanger 3 and outdoor heat exchanger 4>
Next, the flow of refrigerant in the outdoor heat exchanger 3 and the outdoor heat exchanger 4 in Modification 2 will be described.

<Refrigerant flow during cooling operation>
First, the flow of refrigerant in the cooling operation state will be explained. In Modification 2,

outdoor heat exchangers

3A and 3B serve as upstream outdoor heat exchangers, and outdoor heat exchanger 4 serves as a downstream outdoor heat exchanger. As shown in FIG. 3, the refrigerant distributor 31 of the

outdoor heat exchangers

3A and 3B has a single pipe structure, and the refrigerant distributor 32 of the

outdoor heat exchangers

3A and 3B has a double pipe structure.

In modification example 2, when the refrigeration cycle device 100 enters the cooling operation state, as shown in FIG. form. However, the outdoor heat exchanger 3A and the outdoor heat exchanger 3B are connected in parallel. In this case, the control unit 11 controls the expansion valve 5 to be in a fully closed state, the solenoid valve 7 to be in an open state, the solenoid valve 8 to be in a closed state, and the expansion valve 6 to be in a fully open state.

Then, as shown in FIG. 17, the gas refrigerant discharged from the compressor 1 flows into the refrigerant distributor 31 of the

outdoor heat exchangers

3A and 3B. The gas refrigerant exchanges heat with air in the

outdoor heat exchangers

3A and 3B, and a part of the gas refrigerant condenses to become a gas-liquid two-phase state. The gas-liquid two-phase refrigerant flowing out from the outdoor heat exchanger 3A and the gas-liquid two-phase refrigerant flowing out from the outdoor heat exchanger 3B join on the upstream side of the solenoid valve 7. The combined refrigerant then flows into the refrigerant distributor 41 of the outdoor heat exchanger 4 via the solenoid valve 7. As described using FIG. 7, the refrigerant distributor 41 has a double pipe structure, and the inner pipe 58 has a large number of refrigerant outlet holes 58c arranged in parallel. The refrigerant that has flowed into the refrigerant distributor 41 flows out from the refrigerant outlet hole 58c into the second internal space 57h when passing through the interior of the inner tube 58. In this way, by providing the refrigerant outlet hole 58c in the inner tube 58, the refrigerant is evenly distributed to each flat tube 47 of the heat exchanger 43A. The refrigerant condensed inside the heat exchanger 43A and the heat exchanger 43B flows out into the refrigerant pipe 45 through the refrigerant distributor 42. The refrigerant that has flowed out of the outdoor heat exchanger 4 flows into the indoor heat exchanger 21. In the indoor heat exchanger 21, the refrigerant exchanges heat with air and evaporates. Thereafter, the refrigerant flows out of the indoor unit 201 and flows into the outdoor unit 101. In the outdoor unit 101, the refrigerant flows into the accumulator 10 via the four-way valve 2 and the refrigerant pipe 306. It is sucked into the compressor 1 again from the accumulator 10 and circulates through the refrigerant circuit.

As described above, in Modification 2, among the

outdoor heat exchangers

3A and 3B and the outdoor heat exchanger 4 that form a serial refrigerant flow path during refrigerant operation, the outdoor heat exchanger located on the downstream side The refrigerant distributor 41 on the inflow side of No. 4 has a double pipe structure. The inner pipe 58 of the refrigerant distributor 41 has a large number of refrigerant outlet holes 58c arranged in parallel. Thereby, in the outdoor heat exchanger 4 located on the downstream side, it is possible to improve the uniformity of distribution of the gas-liquid two-phase refrigerant to the heat exchanger 43A.

<Heating operation status (in case of parallel refrigerant flow path)>
In Modified Example 2, when the refrigeration cycle device 100 is in the heating operation state, as shown in FIG. form a road. In this case, the control unit 11 controls the

expansion valves

5 and 6 flows into the

outdoor heat exchangers

3A, 3B and the outdoor heat exchanger 4, respectively, and evaporates. The refrigerant flowing out from the outdoor heat exchanger 4 passes through the solenoid valve 8 and joins with the refrigerant flowing out from the

outdoor heat exchangers

3A and 3B. Thereafter, the combined refrigerant flows into the accumulator 10 via the four-way valve 2 and the refrigerant pipe 306. It is sucked into the compressor 1 again from the accumulator 10 and circulates through the refrigerant circuit. This results in a refrigerant circuit having a refrigerant flow path in which the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are connected in parallel.

<Heating operation status (in case of serial refrigerant flow path)>
In modification 2, when the refrigeration cycle device 100 enters the heating operation state, the

outdoor heat exchangers

3A, 3B and the outdoor heat exchanger 4 may be connected in series to form a series refrigerant flow path. . In this case, the flow of the refrigerant is opposite to that in the cooling operation state described above with reference to FIG. Therefore, the explanation thereof will be omitted here.

As described above, according to the first embodiment and its modifications, the following effects can be obtained.

When multiple outdoor heat exchangers are connected in series to function as condensers during cooling operation, the downstream outdoor heat exchanger will contain a mixture of gas and liquid refrigerants. Refrigerant may be introduced in a two-phase state. In the first embodiment, the refrigeration cycle device 100 is configured to form a refrigerant flow path such that the outdoor heat exchanger 4 is located on the downstream side and the outdoor heat exchanger 3 is located on the upstream side during cooling operation. There is. The refrigerant distributor 41 of the outdoor heat exchanger 4 disposed on the downstream side has a double pipe structure, and the inner pipe 58 is formed with a plurality of refrigerant outlet holes 58c. Therefore, when the refrigerant flows into the outdoor heat exchanger 4 in a gas-liquid two-phase state, the refrigerant is biased toward the plurality of flat tubes 47 of the outdoor heat exchanger 4 due to the function of the refrigerant distributor 41. The situation in which it is distributed can be controlled. By evenly distributing the refrigerant to the plurality of flat tubes 47, the required amount of heat exchange becomes uniform over the entire surface of the heat exchange body 43 included in the outdoor heat exchanger 4, and a decrease in heat exchange efficiency is prevented. be able to.

Specifically, the outdoor heat exchanger 4 includes a refrigerant distributor 41 and a refrigerant distributor 42. Both

refrigerant distributors

41 and 42 have a double-pipe structure composed of an outer tube and an inner tube. Further, the

inner tubes

58 and 62 are formed with refrigerant outlet holes 58c and 62c through which the refrigerant flows out from the inner tube into the outer tube. A flat tube 47 is inserted into the

outer tubes

57 and 61. Therefore, even when the gas-liquid two-phase refrigerant flows into the

refrigerant distributor

41 or 42, the refrigerant is evenly distributed to all the flat tubes 47.

Even when a plurality of

outdoor heat exchangers

3 and 4 functioning as condensers are connected to form a serial refrigerant flow path, the gas-liquid two-phase refrigerant flowing into the outdoor heat exchanger 4 located on the downstream side is distributed evenly. can be distributed to.

Since the refrigerant distributor 31 provided in the outdoor heat exchanger 3 has a single-pipe structure, pressure loss can be kept small during both cooling and heating operations.

Embodiment 2.
FIG. 19 is a perspective view showing the connection state of the outdoor heat exchanger 3C and the outdoor heat exchanger 4C in the refrigeration cycle device 100 according to the second embodiment. The configuration of refrigeration cycle device 100 according to the second embodiment is basically the same as the configuration of refrigeration cycle device 100 according to the first embodiment. The difference from the first embodiment is that in the second embodiment,

outdoor heat exchangers

3C and 4C are provided in place of the

outdoor heat exchangers

3 and 4 of the first embodiment, respectively. Since the other configurations are the same as those in Embodiment 1, the description thereof will be omitted here.

In the first embodiment described above, as shown in FIGS. 3 and 4, the heat exchange body 33 constituting the outdoor heat exchanger 3 and the heat exchange body 43 constituting the outdoor heat exchanger 4 are Two layers are arranged in the direction along the direction of the wind generated by the blower 9. On the other hand, in Embodiment 2, as shown in FIG. One layer is arranged in the direction along the direction of the wind generated by the outdoor blower 9.

In FIG. 19, the refrigerant flow path in which the outdoor heat exchanger 3C and the outdoor heat exchanger 4C are connected in series is expressed by a simple connection using refrigerant piping. The white arrow indicates the direction of the wind generated by the outdoor blower 9. Also, the arrows written near the

refrigerant pipes

35A, 36A, and 45A represent the flow of refrigerant, with solid arrows representing the flow of refrigerant during cooling operation, and dashed arrows representing refrigerant flow during heating operation. It represents the flow of

<Configuration of outdoor heat exchanger 3C>
First, the configuration of the outdoor heat exchanger 3C will be explained. As shown in FIG. 19, the outdoor heat exchanger 3C includes a refrigerant distributor 31, a refrigerant distributor 32, and a heat exchanger 33. The heat exchanger 33 is composed of a plurality of flat tubes 37 and a plurality of fins 38. The configuration of the heat exchanger 33 is the same as described in Embodiment 1, so a description thereof will be omitted here. In the second embodiment, a refrigerant distributor 31 having a single-pipe structure is provided above the heat exchanger 33, and a refrigerant distributor 32 having a double-pipe structure is provided below the heat exchanger 33. The configurations of the refrigerant distributor 31 and the refrigerant distributor 32 are as described in Embodiment 1, so the description thereof will be omitted here. As shown in FIG. 19, a refrigerant pipe 35A is connected to the refrigerant distributor 31 via a connecting pipe 52, and a refrigerant pipe 36A is connected to the refrigerant distributor 32 via a connecting pipe 56.

<Configuration of outdoor heat exchanger 4C>
Next, the configuration of the outdoor heat exchanger 4C will be explained. As shown in FIG. 19, the outdoor heat exchanger 4C includes a refrigerant distributor 41, a refrigerant distributor 42, and a heat exchanger 43. The heat exchanger 43 is composed of a plurality of flat tubes 47 and a plurality of fins 48. The configuration of the heat exchanger 43 is the same as described in Embodiment 1, so a description thereof will be omitted here. In the second embodiment, a refrigerant distributor 41 with a double tube structure is provided above the heat exchanger 43, and a refrigerant distributor 42 with a double tube structure is provided below the heat exchanger 43. . The configurations of the refrigerant distributor 41 and the refrigerant distributor 42 are as described in Embodiment 1, so the description thereof will be omitted here. As shown in FIG. 19, a refrigerant pipe 36A is connected to the refrigerant distributor 41 via a connecting pipe 60, and a refrigerant pipe 45A is connected to the refrigerant distributor 42 via a connecting pipe 64.

Note that the outdoor heat exchanger 4C is sometimes called a "heat exchanger". The heat exchange body 43 is sometimes referred to as a "first heat exchange body." The flat tube 47 is sometimes called a "first flat tube." Refrigerant distributor 41 may be referred to as a "first refrigerant distributor," and refrigerant distributor 42 may be referred to as a "second refrigerant distributor." Further, the outer tube 57 is sometimes called a "first outer tube," the inner tube 58 is sometimes called a "first inner tube," and the partition plate 59 is sometimes called a "first partition plate." Further, the outer tube 61 is sometimes called a "second outer tube," the inner tube 62 is sometimes called a "second inner tube," and the partition plate 63 is sometimes called a "second partition plate." Further, the tube end 47c of the flat tube 47 inserted into the refrigerant distributor 41 is sometimes referred to as "one end of the first flat tube", and the tube end 47d of the flat tube 47 inserted into the refrigerant distributor 42 is referred to as "one end of the first flat tube". is sometimes referred to as "the other end of the first flat tube".

Additionally, the outdoor heat exchanger 3C is sometimes referred to as a "second heat exchanger". Heat exchange body 33 is sometimes referred to as a "second heat exchange body." The flat tube 37 is sometimes called a "second flat tube." The refrigerant distributor 31 is sometimes called a "third refrigerant distributor," and the refrigerant distributor 32 is sometimes called a "fourth refrigerant distributor." Further, the outer tube 51 is sometimes referred to as a "third outer tube." The outer tube 53 is sometimes called a "fourth outer tube," the inner tube 54 is sometimes called a "fourth inner tube," and the partition plate 55 is sometimes called a "fourth partition plate." Further, the tube end 37c of the flat tube 37 inserted into the refrigerant distributor 31 is sometimes referred to as "one end of the second flat tube", and the tube end 37d of the flat tube 37 inserted into the refrigerant distributor 32 is referred to as "one end of the second flat tube". is sometimes referred to as "the other end of the second flat tube".

<Refrigerant flow during cooling operation>
First, the flow of refrigerant in the cooling operation state will be explained. As shown in FIG. 19, gas refrigerant discharged from the compressor 1 (see FIG. 1) flows into the refrigerant distributor 31 from the refrigerant pipe 35A via the connecting pipe 52. The inflowing refrigerant is partially condensed in the outdoor heat exchanger 3 to become a gas-liquid two-phase state, and flows out to the refrigerant pipe 36A via the refrigerant distributor 32. Thereafter, the refrigerant flows into the outdoor heat exchanger 4 in a gas-liquid two-phase state. In the outdoor heat exchanger 4, the refrigerant first flows into the refrigerant distributor 41 via the connecting pipe 60. The refrigerant distributor 41 has a double pipe structure, and the inner pipe 58 thereof has a large number of refrigerant outlet holes 58c arranged in parallel. When the refrigerant that has flowed into the refrigerant distributor 41 passes through the interior of the inner tube 58, it flows out from the refrigerant outlet hole 58c into the second internal space 57h of the outer tube 57. In this way, by providing the refrigerant outlet hole 58c in the inner tube 58, the refrigerant is evenly distributed to each flat tube 47 of the heat exchanger 43A. The refrigerant condensed inside the heat exchanger 43 flows out from the refrigerant distributor 42 to the refrigerant pipe 45A via the connecting pipe 64.

As described above, the refrigerant distributor 41 on the inflow side of the outdoor heat exchanger 4C located on the downstream side among the plurality of outdoor heat exchangers 3C and the outdoor heat exchanger 4C forming a serial refrigerant flow path during refrigerant operation. has a double tube structure. The inner pipe 58 of the refrigerant distributor 41 has a large number of refrigerant outlet holes 58c arranged in parallel. Thereby, in the outdoor heat exchanger 4C located on the downstream side, it is possible to improve the uniformity of distribution of the gas-liquid two-phase refrigerant to the heat exchanger 43.

<Refrigerant flow during heating operation>
Next, the flow of refrigerant in the heating operation state will be explained. As can be seen by comparing the solid line arrow and the broken line arrow in FIG. 19, the direction in which the refrigerant flows in the heating operation state is opposite to that in the cooling operation state. In the heating operation state, the refrigerant flows into the outdoor heat exchanger 3C and the outdoor heat exchanger 4C through the refrigerant distributor 32 and the refrigerant distributor 42. Both the refrigerant distributor 32 and the refrigerant distributor 42 are refrigerant distributors having a double pipe structure.

As described above, in the heating operation state, the plurality of outdoor heat exchangers 3C and the outdoor heat exchanger 4C, which form serial refrigerant flow paths, both function as an evaporator. Therefore, the refrigerant distributor 42 on the inflow side of the outdoor heat exchanger 4C located on the upstream side and the refrigerant distributor 32 on the inflow side of the outdoor heat exchanger 3C located on the downstream side have a double pipe structure. There is. The inner pipe 62 of the refrigerant distributor 42 and the inner pipe 54 of the refrigerant distributor 32 each have a large number of refrigerant outflow holes 62c and refrigerant outflow holes 54c arranged in parallel. As a result, in the outdoor heat exchanger 4C located on the upstream side and the outdoor heat exchanger 3C located on the downstream side, the refrigerant in the gas-liquid two-phase state is uniformly distributed to the heat exchanger 43 and the heat exchanger 33. can improve sex.

As described above, in the second embodiment as well, the refrigerant distributor 41 of the outdoor heat exchanger 4C on the downstream side during cooling operation is configured with a double pipe structure, so that the same structure as in the first embodiment is achieved. Effects can be obtained.

Embodiment 3.
FIG. 20 is a perspective view showing the external appearance of the outdoor unit 101 provided in the refrigeration cycle device 100 according to the third embodiment. FIG. 21 is a plan view schematically showing an example of the configuration of the outdoor unit 101 provided in the refrigeration cycle device 100 according to the third embodiment.

As shown in FIGS. 20 and 21, the outdoor unit 101 includes

outdoor heat exchangers

3 and 4,

refrigerant pipes

35, 36, 45 (see FIG. 2) connecting the

outdoor heat exchangers

3 and 4, and a housing. 101a, and an outdoor blower 9.

The housing 101a has a box shape, as shown in FIG. 20. As shown in FIG. 21,

outdoor heat exchangers

3 and 4 are housed inside the housing 101a. Although not shown in FIG. 21, inside the housing 101a are the compressor 1, the four-way valve 2, the

expansion valves

5 and 6, the

solenoid valves

7 and 8, and the control unit 11 shown in FIG. A control box (not shown) containing a control board constituting the controller is further housed. Furthermore, an outdoor blower 9 is arranged in the upper part 101b of the housing 101a. When the outdoor blower 9 is driven to rotate, air flows as shown by the white arrows in FIG. 20 are generated. The air is sucked into the housing 101a from at least two of the four sides of the housing 101a. Further, after passing through the

outdoor heat exchangers

3 and 4, the air is blown upward from an air outlet provided in the upper part 101b of the housing 101a.

In the example of FIG. 21(a), the outdoor heat exchanger 3 and the outdoor heat exchanger 4 each have a rectangular shape in plan view. In the example of FIG. 21(a), the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are arranged to face each other. Moreover, in the example of FIG. 21(a), the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are arranged along a part of the side surface of the housing 101a. That is, the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are arranged along two of the four side surfaces of the housing 101a.

In the example of FIG. 21(b), the outdoor heat exchanger 3 and the outdoor heat exchanger 4 each have an L-shape in plan view. In the example of FIG. 21(b), the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are arranged at point-symmetrical positions. Moreover, in the example of FIG. 21(b), the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are arranged along the entire side surface of the housing 101a. That is, the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are arranged along the four side surfaces of the housing 101a.

The example in FIG. 21(c) shows a case where there are three outdoor heat exchangers, as in the second modification of the first embodiment shown in FIGS. 16 to 18. In the example of FIG. 21(c), the

outdoor heat exchangers

3A, 3B, and 4 are arranged in a U-shape when viewed from above. In the example of FIG. 21(c), the

outdoor heat exchangers

3A, 3B, and 4 are arranged along part of the side surface of the housing 101a. That is, the

outdoor heat exchangers

3A, 3B, and 4 are arranged along three side surfaces of the housing 101a.

<Modified example>
FIG. 22 is a perspective view showing the appearance of an outdoor unit 101 provided in a refrigeration cycle device 100 according to a modification of the third embodiment. FIG. 23 is a plan view schematically showing an example of the configuration of the outdoor unit 101 provided in the refrigeration cycle device 100 according to the third embodiment.

In the example of FIG. 21, one outdoor blower 9 is arranged at the upper part 101b of the housing 101a. However, it is not limited to this case. The number of outdoor blowers 9 may be one as shown in FIG. 21, or two as shown in FIG. 1 in the first embodiment. FIG. 22 shows a case where two outdoor blowers 9 are provided in the upper part 101b of the housing 101a.

In the example of FIG. 23, the outdoor heat exchanger 3 and the outdoor heat exchanger 4 each have an L-shape in plan view. In the example of FIG. 23, the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are arranged in line-symmetrical positions. Moreover, in the example of FIG. 23, the outdoor heat exchanger 3 and the outdoor heat exchanger 4 are arranged along three side surfaces among the four side surfaces of the housing 101a.

1 Compressor, 2 Four-way valve, 2a connection port, 2b connection port, 2c connection port, 2d connection port, 3 outdoor heat exchanger, 3A outdoor heat exchanger, 3B outdoor heat exchanger, 3C outdoor heat exchanger, 3a connection Port, 3b connection port, 4 outdoor heat exchanger, 4C outdoor heat exchanger, 4a connection port, 4b connection port, 5 expansion valve, 6 expansion valve, 7 solenoid valve, 8 solenoid valve, 9 outdoor blower, 10 accumulator, 11 Control unit, 21 indoor heat exchanger, 21a connection port, 21b connection port, 22 indoor blower, 23 expansion valve, 31 refrigerant distributor, 32 refrigerant distributor, 33 heat exchange body, 33A heat exchange body, 33B heat exchange body, 34 Folded header, 35 Refrigerant pipe, 35A Refrigerant pipe, 36 Refrigerant pipe, 36A Refrigerant pipe, 37 Flat tube, 37a Pipe end, 37b Pipe end, 37c Pipe end, 37d Pipe end, 38 Fin, 41 Refrigerant distribution 42 Refrigerant distributor, 43 Heat exchanger, 43A Heat exchanger, 43B Heat exchanger, 44 Folded header, 45 Refrigerant piping, 45A Refrigerant piping, 47 Flat tube, 47a Pipe end, 47b Pipe end, 47c Pipe End, 47d Tube end, 48 Fin, 51 Outer tube, 51a Tube end, 51b Tube end, 51c Closing plate, 51d Closing plate, 51e Flat tube insertion hole, 52 Connecting tube, 52a Lower end, 53 Outer tube , 53a tube end, 53b tube end, 53c closing plate, 53d closing plate, 53e flat tube insertion hole, 53f inner wall, 53g first internal space, 53h second internal space, 54 inner tube, 54a tube end , 54b pipe end, 54c refrigerant outflow hole, 54f outer wall, 55 partition plate, 55a through hole, 56 connecting pipe, 56a lower end, 57 outer pipe, 57a pipe end, 57b pipe end, 57c closing plate, 57d closing Plate, 57e flat tube insertion hole, 57f inner wall, 57g first internal space, 57h second internal space, 58 inner tube, 58a tube end, 58b tube end, 58c refrigerant outflow hole, 58f outer wall, 59 partition plate , 59a through hole, 60 connecting tube, 60a lower end, 61 outer tube, 61a tube end, 61b tube end, 61c closing plate, 61d closing plate, 61e flat tube insertion hole, 61f inner wall, 61g first internal space , 61h second internal space, 62 inner tube, 62a tube end, 62b tube end, 62c refrigerant outflow hole, 62f outer wall, 63 partition plate, 63a through hole, 64 connecting tube, 100 refrigeration cycle device, 101 outdoor unit , 101a housing, 101b upper part, 201 indoor unit, 300 refrigerant piping, 301 refrigerant piping, 302 refrigerant piping, 303 refrigerant piping, 304 refrigerant piping, 305 refrigerant piping, 306 refrigerant piping, 307 refrigerant piping, 308 refrigerant piping, 31 0 Refrigerant Piping, P1 connection port, P2 connection port.

Claims

a first heat exchange body having a plurality of first flat tubes arranged at intervals in a first direction and whose tube axis direction extends in a second direction intersecting the first direction;
a first refrigerant distributor into which one end portions of the plurality of first flat tubes are inserted;
a second refrigerant distributor into which the other end portions of the plurality of first flat tubes are inserted;
Equipped with
The first refrigerant distributor includes:
a first outer tube extending in the first direction and into which the one end portions of the plurality of first flat tubes are inserted;
a first inner tube extending in the first direction, disposed inside the first outer tube, and having a plurality of first refrigerant outlet holes spaced apart from each other in the first direction;
a first partition plate joined to the inner wall of the first outer tube with the first inner tube penetrating through the plate thickness;
has
The second refrigerant distributor includes:
a second outer tube extending in the first direction and into which the other end portions of the plurality of first flat tubes are inserted;
a second inner tube extending in the first direction, disposed inside the second outer tube, and having a plurality of second refrigerant outlet holes spaced apart from each other in the first direction;
a second partition plate joined to the inner wall of the second outer tube with the second inner tube penetrating through the plate thickness;
has,
Heat exchanger.
When the heat exchanger functions as a condenser,
The refrigerant flows into the one end of the first flat tube from the first refrigerant distributor, flows inside the first flat tube, and flows from the other end of the first flat tube into the second refrigerant distributor. leaks into
The heat exchanger according to claim 1.
The refrigerant flowing from the first refrigerant distributor into the one end of the first flat tube is in a gas-liquid two-phase state.
The heat exchanger according to claim 2.
Some or all of the specifications of the first refrigerant distributor are different from some or all of the specifications of the second refrigerant distributor,
The specifications of the first refrigerant distributor and the specifications of the second refrigerant distributor are based on the distribution of the refrigerant in the first refrigerant distributor and the second refrigerant distributor when the heat exchanger functions as a condenser. Determined based on the state regarding uniformity and the pressure loss occurring in the first refrigerant distributor and the second refrigerant distributor when the heat exchanger functions as an evaporator.
The heat exchanger according to any one of claims 1 to 3.
The first flat tube is
a leeward-side first flat tube that is disposed on the leeward side in the direction of air flow and has the one end portion of the first flat tube;
a windward-side first flat tube that is disposed on the windward side in the air flow direction and has the other end of the first flat tube;
including;
An end opposite to the one end of the first flat tube on the leeward side and an end opposite to the other end of the first flat tube on the windward side are connected via a first folded header. ing,
The heat exchanger according to any one of claims 1 to 4.
When the heat exchanger functions as a condenser, the heat exchanger is connected in series to a second heat exchanger that functions as a condenser,
The second heat exchanger is arranged upstream of the heat exchanger in the direction in which the refrigerant flows.
The heat exchanger according to any one of claims 1 to 5.
The second heat exchanger is
a second heat exchanger having a plurality of second flat tubes arranged at intervals in a third direction and whose tube axis direction extends in the second direction intersecting the third direction;
a third refrigerant distributor into which one end portion of the plurality of second flat tubes is inserted;
a fourth refrigerant distributor into which the other end portions of the plurality of second flat tubes are inserted;
Equipped with
The third refrigerant distributor is
a third outer tube extending in the third direction and into which the one ends of the plurality of second flat tubes are inserted;
The fourth refrigerant distributor is
a fourth outer tube extending in the third direction and into which the other end portions of the plurality of second flat tubes are inserted;
a fourth inner pipe extending in the third direction, disposed inside the fourth outer pipe, and having a plurality of fourth refrigerant outlet holes spaced apart from each other in the third direction;
a fourth partition plate joined to the inner wall of the fourth outer tube with the fourth inner tube penetrating through the plate thickness;
has,
The heat exchanger according to claim 6.
When the second heat exchanger functions as a condenser,
The refrigerant flows from the third refrigerant distributor into the one end of the second flat tube, flows inside the second flat tube, and flows from the other end of the second flat tube into the fourth refrigerant distributor. leaks into
The heat exchanger according to claim 7.
The refrigerant flowing from the third refrigerant distributor into the one end of the second flat tube is in a gas state.
The heat exchanger according to claim 8.
The second flat tube is
a second leeward flat tube that is disposed on the leeward side in the direction of air flow and has the one end of the second flat tube;
a second windward flat tube that is disposed on the windward side in the air flow direction and has the other end of the second flat tube;
including;
An end opposite to the one end of the second flat tube on the leeward side and an end opposite to the other end of the second flat tube on the windward side are connected via a second folded header. ing,
The heat exchanger according to any one of claims 7 to 9.
A refrigeration cycle device equipped with an outdoor unit,
The outdoor unit is
The heat exchanger according to any one of claims 1 to 5,
The second heat exchanger according to any one of claims 6 to 10,
refrigerant piping connecting the heat exchanger and the second heat exchanger;
a box-shaped casing that houses the heat exchanger and the second heat exchanger therein;
an air blower that is disposed at the top of the casing, forms an air flow by rotationally driving, and blows the air that has passed through the heat exchanger and the second heat exchanger upward from the top surface of the casing; and,
Equipped with
the heat exchanger and the second heat exchanger are arranged along some or all of the four sides of the housing;
Refrigeration cycle equipment.