JP7493585B2 - Heat exchanger, heat exchanger unit and refrigeration cycle device - Google Patents

Description

The present disclosure relates to a heat exchanger, a heat exchanger unit and a refrigeration cycle device, and in particular to a structure for distributing refrigerant to multiple heat transfer tubes.

Conventionally, a heat exchanger is known that includes a plurality of heat transfer tubes arranged at intervals in the direction of gravity and a header connected to the ends of the plurality of heat transfer tubes, and exchanges heat between the refrigerant flowing inside the plurality of heat transfer tubes and the air. The heat exchanger is installed in a refrigeration cycle device such as an air conditioner to form a refrigeration cycle. In air conditioners, the diameter of the heat transfer tubes of the heat exchanger is becoming thinner in order to reduce the amount of refrigerant in the refrigerant circuit and to improve the performance of the heat exchanger. When the diameter of the heat transfer tube is made thinner, it is necessary to suppress the increase in the pressure loss of the refrigerant passing through the heat transfer tube. For this reason, the number of paths (number of branches) in the heat exchanger is increasing. In response to the increase in the number of refrigerant branches in the heat exchanger, the refrigerant distributor (header) of the heat exchanger is required to evenly distribute the two-phase gas-liquid refrigerant that flows in to each of the plurality of heat transfer tubes when the heat exchanger acts as an evaporator.

For example, a heat exchanger has been proposed that circulates the refrigerant that flows into the header within the header, making the amount of liquid refrigerant and gas phase refrigerant equal that flows into each of the heat transfer tubes arranged in the vertical direction due to gravity, even if the refrigerant is a gas-liquid two-phase refrigerant (see, for example, Patent Document 1).

Patent No. 6369650

However, in the heat exchanger disclosed in Patent Document 1, when the refrigerant flow rate is slow, such as when the refrigeration cycle device is operating at a low load, the liquid refrigerant may not rise to the top of the header due to the effects of gravity. In such cases, the heat exchanger has an issue in that a large amount of liquid refrigerant flows into the heat transfer tubes below the header, resulting in a decrease in heat exchange performance.

The present disclosure is intended to solve the above-mentioned problems, and aims to provide a heat exchanger, heat exchanger unit, and refrigeration cycle device that can suppress bias in liquid refrigerant and gas phase refrigerant flowing through multiple heat transfer tubes even when the refrigeration cycle device is operating at low load.

A heat exchanger according to the present disclosure includes a plurality of heat transfer tubes arranged in parallel in a first direction and extending in a second direction intersecting the first direction, a refrigerant distributor to which one ends of the plurality of heat transfer tubes are connected, and a refrigerant inlet tube connected to the refrigerant distributor, and is used with one end in the first direction positioned at an upper position and the other end positioned at a lower position, the refrigerant distributor is formed to extend along the first direction and includes a gas-liquid separation chamber that separates the refrigerant flowing in from the refrigerant inlet tube into a gas-phase refrigerant and a liquid-phase refrigerant, a distribution chamber to which the ends of the plurality of heat transfer tubes are connected, a partition plate that divides an internal space into the gas-liquid separation chamber and other spaces in the second direction, liquid circulation holes that communicate between the gas-liquid separation chamber and the distribution chamber and through which the liquid-phase refrigerant flows, and a liquid passage between the gas-liquid separation chamber and the distribution chamber. the gas-liquid separation chamber is located farther from the plurality of heat transfer tubes than the distribution chamber in the second direction; and the gas-liquid separation chamber is provided with a baffle plate extending from a wall surface on a side where the refrigerant inlet pipe is installed between the refrigerant inlet pipe and the liquid circulation hole toward the partition plate ; and a gas circulation pipe extending from the gas circulation hole and communicating a first space, which is a space on a side from the baffle plate where the liquid circulation hole is located, with the gas circulation hole, and the baffle plate is provided with a communication hole communicating the first space with a second space, which is the space on the side where the gas circulation hole is located.

The heat exchanger unit of the present disclosure comprises the above-mentioned heat exchanger and a blower that sends air to the heat exchanger.

The refrigeration cycle device of the present disclosure is equipped with the above-mentioned heat exchanger unit.

According to the present disclosure, the above configuration allows the gas-liquid two-phase refrigerant flowing into the heat exchanger to be separated into gas-phase refrigerant and liquid-phase refrigerant and then distributed to multiple heat transfer tubes. This makes it possible to suppress variation in the ratio of liquid-phase refrigerant to gas-phase refrigerant flowing through each of the multiple heat transfer tubes, even under conditions where the refrigerant flow velocity is slow.

1 is a refrigerant circuit diagram showing a configuration of a refrigeration cycle device 100 including a heat exchanger 6 according to a first embodiment. FIG. 2 is an exploded perspective view illustrating the structure of the heat exchanger 6 according to the first embodiment. 2 is an explanatory diagram of a cross-sectional structure of a refrigerant distributor 10 of a heat exchanger 6 according to the first embodiment. FIG. 2 is a cross-sectional view of the gas-liquid separation chamber 20. FIG. FIG. 2 is a Mollier diagram of the refrigeration cycle apparatus 100 according to the first embodiment. FIG. 11 is a refrigerant circuit diagram showing a configuration of a refrigeration cycle device 200 including a heat exchanger 206 according to a second embodiment. FIG. 11 is an exploded perspective view illustrating the structure of a heat exchanger 206 according to a second embodiment. 11 is an explanatory diagram of a cross-sectional structure of a refrigerant distributor 210 of a heat exchanger 206 according to embodiment 2. FIG. 2 is a cross-sectional view of the gas-liquid separation chamber 20. FIG. FIG. 2 is a cross-sectional view of the distribution chamber 21. 11 is an explanatory diagram showing regions through which liquid-phase refrigerant and gas-phase refrigerant flow and temperature distribution in the plurality of heat transfer tubes 30 in FIG. 10 . FIG. 13 is an explanatory diagram of a cross-sectional structure of a refrigerant distributor 310 of a heat exchanger 306 according to embodiment 3. FIG. 13 is an explanatory diagram showing regions through which liquid-phase refrigerant and gas-phase refrigerant flow and temperature distribution in the plurality of heat transfer tubes 30 in FIG. 12 . FIG. FIG. 11 is an exploded perspective view illustrating the structure of a heat exchanger 406 according to embodiment 4. 13 is an explanatory diagram of a cross-sectional structure of a refrigerant distributor 410 of a heat exchanger 406 according to embodiment 4. FIG. FIG. 13 is an exploded perspective view illustrating the structure of a heat exchanger 406a which is a modified example of the heat exchanger 406 according to the fourth embodiment. 13 is an explanatory diagram of a cross-sectional structure of a heat exchanger 506 according to embodiment 5. FIG. 13 is an explanatory diagram of a cross-sectional structure of a heat exchanger 606 according to embodiment 6. FIG.

The following describes embodiments of a heat exchanger, a heat exchanger unit, and a refrigeration cycle device. Note that the forms in the drawings are merely examples and do not limit the present disclosure. In addition, the same reference numerals in each drawing denote the same or equivalent parts, and this is common throughout the entire specification. In addition, to facilitate understanding, terms expressing directions (e.g., "up," "down," "right," "left," "front," "rear," etc.) are used as appropriate, but these notations are merely written in this way for the sake of convenience and do not limit the arrangement and orientation of the device or parts. Furthermore, the size relationships of the components in the following drawings may differ from the actual ones.

Embodiment 1.
FIG. 1 is a refrigerant circuit diagram showing the configuration of a refrigeration cycle apparatus 100 including a heat exchanger 6 according to the first embodiment. First, the refrigeration cycle apparatus 100 including a refrigerant distributor 10 will be described with reference to FIG. 1. In FIG. 1, the arrows indicate the direction of refrigerant flow in the refrigerant circuit 99 of the refrigeration cycle apparatus 100 during heating operation. The arrows shown by solid lines indicate the flow of liquid-phase refrigerant, the arrows shown by dotted lines indicate the flow of gas-phase refrigerant, and the arrows shown by dashed lines indicate the flow of two-phase gas-liquid refrigerant. In the first embodiment, an air conditioner is illustrated as the refrigeration cycle apparatus 100, but the refrigeration cycle apparatus 100 is used for refrigeration or air conditioning purposes, such as a refrigerator, a freezer, a vending machine, an air conditioner, a refrigeration apparatus, or a water heater.

The refrigeration cycle device 100 has a refrigerant circuit 99 in which a compressor 3, a flow switching device 7, an indoor heat exchanger 4, a pressure reducing device 5, and an outdoor heat exchanger 6 are connected in a ring shape via refrigerant piping. The refrigeration cycle device 100 has an outdoor unit 1 and an indoor unit 2. The outdoor unit 1 has a compressor 3, a flow switching device 7, an outdoor heat exchanger 6, a refrigerant distributor 10, and a pressure reducing device 5. The outdoor unit 1 houses an outdoor blower 6f that supplies outdoor air near the outdoor heat exchanger 6. The indoor unit 2 houses an indoor heat exchanger 4 and an indoor blower 4f that supplies air to the indoor heat exchanger 4. The outdoor unit 1 and the indoor unit 2 are connected via two extension pipes 111 and 112, which are part of the refrigerant piping. The outdoor blower 6f and the indoor blower 4f may be collectively referred to as blowers. Furthermore, a device having a heat exchanger therein, such as the outdoor unit 1 and the indoor unit 2, may be referred to as a heat exchanger unit.

The compressor 3 is a fluid machine that compresses and discharges the sucked refrigerant. The flow path switching device 7 is, for example, a four-way valve, and is a device that switches the flow path of the refrigerant between cooling operation and heating operation under the control of a control device (not shown). The indoor heat exchanger 4 is a heat exchanger that exchanges heat between the refrigerant flowing inside and the indoor air supplied by the indoor blower 4f. The indoor heat exchanger 4 functions as a condenser during heating operation and as an evaporator during cooling operation. The pressure reducing device 5 is, for example, an expansion valve, and is a device that reduces the pressure of the refrigerant. As the pressure reducing device 5, an electronic expansion valve whose opening degree is adjusted under the control of the control device can be used. The outdoor heat exchanger 6 is a heat exchanger that exchanges heat between the refrigerant flowing inside and the air supplied by the outdoor blower 6f. The outdoor heat exchanger 6 functions as an evaporator during heating operation and as a condenser during cooling operation.

The refrigerant circuit 99 of the refrigeration cycle device 100 according to the first embodiment includes a bypass flow path 9 that does not pass through a plurality of heat transfer tubes 30 (see FIG. 2) from the refrigerant distributor 10 of the outdoor heat exchanger 6. The bypass flow path 9 is provided with a flow control valve 8, and the opening degree of the flow control valve 8 is adjusted by the control device.

Figure 2 is an exploded perspective view illustrating the structure of the heat exchanger 6 according to embodiment 1. Figure 3 is an explanatory diagram of the cross-sectional structure of the refrigerant distributor 10 of the heat exchanger 6 according to embodiment 1. In embodiment 1, the outdoor heat exchanger 6 during heating operation of the refrigeration cycle device 100 is described. In the following description, the outdoor heat exchanger 6 may be simply referred to as the heat exchanger 6. Also, Figure 2 shows an x-axis, a y-axis, and a z-axis that are mutually orthogonal, which correspond in each figure.

The heat exchanger 6 includes a plurality of heat transfer tubes 30 and a refrigerant distributor 10 to which one end of the plurality of heat transfer tubes 30 is connected. The plurality of heat transfer tubes 30 are arranged in parallel in the z direction with their tube axes parallel to each other. The plurality of heat transfer tubes 30 are arranged so that their tube axes extend along the x direction. The refrigerant distributor 10 is connected to the ends of the plurality of heat transfer tubes 30 in the x direction. As shown by the arrow AF in FIG. 3, the air flows along the y direction by the blower 6f and passes between the plurality of heat transfer tubes 30. The z direction may be referred to as the first direction, the x direction as the second direction, and the y direction as the third direction. In the first embodiment, the z direction is upward in the direction of gravity. However, the z direction is not limited to being parallel to the direction of gravity, and may be inclined with respect to the direction of gravity, as long as at least one end is located above and the other end is located below.

As shown in FIG. 3, the inside of the refrigerant distributor 10 is divided into two spaces in a cross section perpendicular to the z-axis. The inside of the tubular portion 60 of the refrigerant distributor 10 is divided into two spaces in the x-direction by a partition plate 11, and the space located closer to the heat transfer tubes 30 is called the distribution chamber 21, and the space located farther from the heat transfer tubes 30 is called the gas-liquid separation chamber 20. One end 31 of the heat transfer tubes 30 is inserted into the distribution chamber 21. The gas-liquid separation chamber 20 is connected to the refrigerant inlet pipe 14, and gas-liquid two-phase refrigerant flows in from outside the heat exchanger 6 during heating operation.

The cylindrical portion 60 is formed by combining the outer casing members 12 and 13, which are formed by bending and processing a plate material into a semi-cylindrical shape. The outer casing member 12 located on the side farther from the heat transfer tubes 30 has a gas circulation hole 15 at the end in the z direction, to which the gas circulation tube 15a is connected, and the refrigerant inlet tube 14 is connected to the center in the z direction. The outer casing member 13 located on the side closer to the heat transfer tubes 30 has a plurality of slits into which the ends 31 of the heat transfer tubes 30 are inserted. Both ends of the cylindrical portion 60 in the z direction are blocked by end members 25 and 26, which are semicircular plate-shaped members. In the first embodiment, the refrigerant distributor 10 has a cylindrical shape as shown in Figs. 2 and 3, but is not limited to this. For example, the refrigerant distributor 10 may be a rectangular box.

The partition plate 11 has a liquid flow hole 16 at the end opposite the z-direction. The liquid flow hole 16 connects the lower part of the gas-liquid separation chamber 20 with the lower part of the distribution chamber 21. A gas flow hole 15 is provided at the upper part of the gas-liquid separation chamber 20, and a gas flow pipe 15a leading to the outside of the heat exchanger 6 is connected to the gas flow pipe 15a. The gas flow pipe 15a is connected to the bypass flow path 9 shown in FIG. 1.

Figure 4 is a cross-sectional view of the gas-liquid separation chamber 20. Figure 4 corresponds to the cross section of the A-A portion of Figure 3. The circles shown in Figure 4 are schematic representations of the positions of the refrigerant inlet pipe 14, the gas flow hole 15, and the liquid flow hole 16 connected to the gas-liquid separation chamber 20. During heating operation, gas-liquid two-phase refrigerant flows into the gas-liquid separation chamber 20 from the refrigerant inlet pipe 14. The liquid phase refrigerant 92, which has a higher density among the gas-liquid two-phase refrigerant, is influenced by gravity and accumulates unevenly at the lower part of the gas-liquid separation chamber 20. On the other hand, the gas phase refrigerant 91, which has a lower density among the gas-liquid two-phase refrigerant, moves to the upper part of the gas-liquid separation chamber 20. Then, as shown in Figure 4, the gas phase refrigerant 91 accumulates at the upper part and the liquid phase refrigerant 92 accumulates at the lower part, and the gas-liquid two-phase refrigerant is separated into the gas phase refrigerant 91 and the liquid phase refrigerant 92.

Since a gas flow hole 15 is provided at the top of the gas-liquid separation chamber 20, the gas-phase refrigerant 91 flows from the gas flow hole 15 through the gas flow pipe 15a into the bypass flow path 9 of the refrigerant circuit 99. Therefore, the gas-phase refrigerant 91 of the gas-liquid two-phase refrigerant that has flowed into the refrigerant distributor 10 flows into the bypass flow path 9.

On the other hand, since the lower part of the gas-liquid separation chamber 20 is provided with a liquid flow hole 16 that communicates with the distribution chamber 21, the liquid-phase refrigerant 92 flows into the distribution chamber 21 through the liquid flow hole 16. Therefore, the liquid-phase refrigerant 92 flows into the distribution chamber 21. However, when the heating operation of the refrigeration cycle device 100 starts, etc., there may be cases where a two-phase gas-liquid refrigerant flows through the distribution chamber 21.

Only liquid phase refrigerant 92 flows into the distribution chamber 21. Therefore, in the first embodiment, only liquid phase refrigerant 92 flows through the multiple heat transfer tubes 30. Therefore, the liquid phase refrigerant 92 flows evenly through the multiple heat transfer tubes 30 located at the top and the bottom in the direction of gravity. Therefore, when the heat exchanger 6 functions as an evaporator, gas phase refrigerant that does not contribute to the evaporation of the refrigerant does not flow through the heat transfer tubes 30.

5 is a Mollier diagram of the refrigeration cycle device 100 according to the first embodiment. In FIG. 5, the solid line is a diagram of a refrigeration cycle device as a comparative example, and is a diagram in the case where the gas-liquid two-phase refrigerant is passed through the evaporator as it is. Also, the dotted line in FIG. 5 is a Mollier diagram of the refrigerant circulating in the refrigeration cycle device 100 according to the first embodiment. In the refrigeration cycle device 100 according to the first embodiment, the gas-liquid two-phase refrigerant decompressed by the decompression device 5 to the state of point D in FIG. 1 and FIG. 5 flows into the heat exchanger 6 and is separated in the gas-liquid separation chamber 20. The liquid phase refrigerant 92 separated in the gas-liquid separation chamber 20 and flowing into the distribution chamber 21 is in the state of point D2. Thereafter, the liquid phase refrigerant 92 flows into a plurality of heat transfer tubes 30, evaporates, and becomes the state of point A2. In the refrigeration cycle device of the comparative example shown by the solid line in FIG. 5, the refrigerant that has passed through the evaporator changes from point D to point A. At this time, the gas-liquid two-phase refrigerant passes through the heat transfer tubes 30 and changes to a gas-phase refrigerant, but the pressure drops due to pressure loss when passing through the heat transfer tubes 30. On the other hand, in the refrigeration cycle device 100 according to the first embodiment, the refrigerant passing through the heat transfer tubes 30 is a liquid-phase refrigerant 92 indicated by point D2 in Fig. 5. Then, the gas-phase refrigerant 91 passes through the bypass passage 9 and merges with the gas-phase refrigerant that has passed through the heat exchanger 6, which is an evaporator. That is, the gas-phase refrigerant 91 that has passed through the bypass passage 9, which is in the state of point E2 in Fig. 5, and the gas-phase refrigerant that has evaporated after passing through the heat transfer tubes 30, which is in the state of point E3 in Fig. 5, merge to reach the state of point A2 in Fig. 5, and is sucked into the compressor 3. The refrigeration cycle apparatus 100 according to the first embodiment can reduce the pressure loss of the refrigerant by separating the refrigerant into a gas phase refrigerant and a liquid phase refrigerant in the refrigerant distributor 10 of the heat exchanger 6 serving as an evaporator, flowing only the liquid phase refrigerant through the heat transfer tubes 30 of the heat exchanger 6, and bypassing the gas phase refrigerant to the bypass flow path 9. Furthermore, by flowing only the liquid phase refrigerant through the heat transfer tubes 30, it becomes easier to ensure a temperature difference between the air and the liquid phase refrigerant, and the latent heat of the liquid phase refrigerant can be efficiently utilized, thereby improving the heat exchange performance of the heat exchanger 6.

Embodiment 2.
The refrigeration cycle apparatus 200 according to the second embodiment is obtained by deleting the bypass passage 9 from the refrigerant circuit 99 of the refrigeration cycle apparatus 100 according to the first embodiment and by changing the structure of the heat exchanger 6. The refrigeration cycle apparatus 200 according to the second embodiment will be described mainly with respect to the changes from the first embodiment. Regarding the components of the refrigeration cycle apparatus 200 according to the second embodiment, those having the same functions in each drawing are indicated by the same reference numerals as those in the drawings used in the description of the first embodiment.

6 is a refrigerant circuit diagram showing the configuration of a refrigeration cycle apparatus 200 including a heat exchanger 206 according to embodiment 2. The refrigerant circuit 299 of the refrigeration cycle apparatus 200 according to embodiment 2 is different from the refrigerant circuit 99 according to embodiment 1 in that the bypass flow path 9 that runs from the refrigerant distributor 10 of the outdoor heat exchanger 6 of the outdoor unit 1 to the flow path switching device 7 without passing through multiple heat transfer tubes 30 is eliminated.

Figure 7 is an exploded perspective view illustrating the structure of the heat exchanger 206 according to the second embodiment. Figure 8 is an explanatory diagram of the cross-sectional structure of the refrigerant distributor 210 of the heat exchanger 206 according to the second embodiment. The heat exchanger 206 according to the second embodiment does not have a gas circulation hole 15 and a gas circulation pipe 15a leading from the gas-liquid separation chamber 20 of the refrigerant distributor 210 to the outside of the heat exchanger 206. Instead, a gas circulation hole 215 communicating with the distribution chamber 21 is provided at the upper part of the gas-liquid separation chamber 20 in the z direction. Also, as in the first embodiment, a liquid circulation hole 16 communicating with the distribution chamber 21 is provided at the lower part of the gas-liquid separation chamber 20 in the z direction.

As shown in Fig. 8, the distribution chamber 21 according to the second embodiment is divided into two spaces in the y direction by a dividing plate 217. That is, the distribution chamber 21 has a first distribution chamber 221 on the windward side and a second distribution chamber 222 on the leeward side. In Fig. 8, the blower 6f is configured to send air in the y direction. The first distribution chamber 221 and the second distribution chamber 222 are divided by the dividing plate 217 formed in a comb-tooth shape according to the arrangement of the multiple heat transfer tubes 30.

The first distribution chamber 221 is connected to the gas-liquid separation chamber 20 via the liquid flow hole 16. The liquid flow hole 16 is formed at the bottom of the gas-liquid separation chamber 20 in the direction of gravity, and thus causes the liquid phase refrigerant 92 that accumulates at the bottom of the gas-liquid separation chamber 20 to flow into the first distribution chamber 221.

The second distribution chamber 222 is connected to the gas-liquid separation chamber 20 via the gas flow hole 215. The gas flow hole 215 is formed at the upper part of the gas-liquid separation chamber 20 in the direction of gravity, and therefore allows the gas phase refrigerant 91 that accumulates at the upper part of the gas-liquid separation chamber 20 to flow into the second distribution chamber 222.

Figure 9 is a cross-sectional view of the gas-liquid separation chamber 20. Figure 9 shows a cross section perpendicular to the x-axis, and shows a cross section of part A-A in Figure 8. In the gas-liquid separation chamber 20, the two-phase gas-liquid refrigerant flowing in from the refrigerant inlet pipe 14 is separated by the effect of gravity, as in embodiment 1.

Since a gas flow hole 215 is provided at the top of the gas-liquid separation chamber 20, the gas phase refrigerant 91 flows from the gas flow hole 215 into the second distribution chamber 222 of the distribution chamber 21. Therefore, only the gas phase refrigerant 91 exists in the second distribution chamber 222.

Meanwhile, since a liquid flow hole 16 communicating with the distribution chamber 21 is provided at the bottom of the gas-liquid separation chamber 20, the liquid phase refrigerant 92 flows into the first distribution chamber 221 of the distribution chamber 21 through the liquid flow hole 16. Therefore, only the liquid phase refrigerant 92 is present in the first distribution chamber 221. In this way, the heat exchanger 206 according to embodiment 2 separates the gas-liquid two-phase refrigerant. The liquid flow hole 16 and the gas flow hole 215 are designed to be of appropriate size according to the expected refrigerant flow rate.

Figure 10 is a cross-sectional view of the distribution chamber 21. Figure 10 shows a cross section perpendicular to the x-axis, and shows a cross section of part B-B in Figure 8. As shown in Figure 10, the multiple heat transfer tubes 30 are inserted into both the first distribution chamber 221 and the second distribution chamber 222 of the distribution chamber 21. The refrigerant flow section 32 (see Figure 11) inside the multiple heat transfer tubes 30 is partially connected to the first distribution chamber 221 and partially connected to the second distribution chamber 222 at the end face 33 (see Figure 11).

11 is an explanatory diagram showing the regions through which the liquid-phase refrigerant and gas-phase refrigerant flow in the multiple heat transfer tubes 30 of FIG. 10 and the temperature distribution. In the heat exchanger 206 according to the second embodiment, the liquid-phase refrigerant flows in the refrigerant flow section 32 in the region L on the windward side of the multiple heat transfer tubes 30. Also, the gas-phase refrigerant flows in the refrigerant flow section 32 in the region G on the leeward side of the multiple heat transfer tubes 30. In the second embodiment, it is desirable to set the region L through which the liquid-phase refrigerant flows into the multiple heat transfer tubes 30 larger than the region G through which the gas-phase refrigerant flows into the multiple heat transfer tubes 30.

When air flows between the heat transfer tubes 30 of the heat exchanger 206, which is an evaporator, the refrigerant temperature is almost constant in the upwind region L. On the other hand, the temperature of the air exchanging heat with the refrigerant drops as it passes through region L due to the latent heat of the liquid refrigerant. The refrigerant passing through region L evaporates due to the sensible heat from the air and changes to gas-phase refrigerant. Also, in the downwind region L, the temperature of the gas-phase refrigerant increases the further it is from region L where the liquid-phase refrigerant flows. This is because the temperature increases in the parts far from region L due to sensible heat exchange with the air passing through region G, and in the regions close to region L, it is affected by the latent heat of the liquid-phase refrigerant in region L.

In the heat exchanger 206 of embodiment 2, liquid refrigerant flows in the region L on the windward side of the multiple heat transfer tubes 30, making it easier to maintain a temperature difference between the air and the refrigerant, thereby improving the heat transfer performance of the heat exchanger 206.

The heat exchanger 206 according to the second embodiment separates the gas-liquid two-phase refrigerant into the first distribution chamber 221 and the second distribution chamber 222, and then flows the liquid phase refrigerant and the gas phase refrigerant in separate regions of the multiple heat transfer tubes 30. Therefore, the refrigerant flowing through each of the multiple heat transfer tubes 30 has a reduced variation in the ratio of gas phase refrigerant to liquid phase refrigerant. Therefore, the heat exchanger 206 can exhibit the desired heat exchange performance.

Embodiment 3.
In the refrigeration cycle apparatus 300 according to the third embodiment, the positions of the first distribution chamber 221 and the second distribution chamber 222 of the heat exchanger 206 according to the second embodiment are reversed. In the refrigeration cycle apparatus 300 according to the third embodiment, changes from the second embodiment will be mainly described. In the drawings, the components of the refrigeration cycle apparatus 300 according to the third embodiment that have the same functions are denoted by the same reference numerals as those in the drawings used in the description of the first and second embodiments.

Figure 12 is an explanatory diagram of the cross-sectional structure of the refrigerant distributor 310 of the heat exchanger 306 according to embodiment 3. In the refrigerant distributor 310 of the heat exchanger 306, the positional relationship between the first distribution chamber 221 and the second distribution chamber 222 is swapped in the y direction. That is, in the heat exchanger 306, the second distribution chamber 222 is arranged on the windward side, and the first distribution chamber 221 is arranged on the leeward side.

13 is an explanatory diagram showing the regions through which the liquid-phase refrigerant and gas-phase refrigerant flow in the multiple heat transfer tubes 30 of FIG. 12, and the temperature distribution. In the heat exchanger 306 according to the third embodiment, a region G through which the gas-phase refrigerant flows is arranged on the windward side of the multiple heat transfer tubes 30, and a region L through which the liquid-phase refrigerant flows is arranged on the leeward side. In the third embodiment as well, it is desirable to set the region L through which the liquid-phase refrigerant flows into the multiple heat transfer tubes 30 larger than the region G through which the gas-phase refrigerant flows into the multiple heat transfer tubes 30.

When air flows between the heat transfer tubes 30 of the heat exchanger 306, which is an evaporator, the refrigerant temperature in the windward region G is higher the further away from the region L. This is because the gas phase refrigerant flowing in the region G exchanges sensible heat with the air of high temperature passing through the region G. Therefore, since the temperature in the region G is relatively high, the occurrence of frost can be suppressed in the windward region of the heat transfer tubes 30, which is most likely to cause frost, when performing heating operation under low outdoor air temperature conditions. As a result, the heat exchanger 306 can exhibit the desired heat exchange performance because the flow of air is not obstructed by frost. Also, as in the second embodiment, the refrigerant flowing through each of the heat transfer tubes 30 has a suppressed variation in the ratio of gas phase refrigerant to liquid phase refrigerant. Therefore, the heat exchanger 306 can exhibit the desired heat exchange performance.

Embodiment 4.
The refrigeration cycle apparatus 400 according to the fourth embodiment is obtained by modifying the structure of the heat exchanger 206 according to the second embodiment. The refrigeration cycle apparatus 400 according to the fourth embodiment will be described mainly with respect to the changes made to the second embodiment. Regarding the components of the refrigeration cycle apparatus 400 according to the fourth embodiment, those components having the same functions in each drawing are indicated by the same reference numerals as those in the drawings used in the description of the first to third embodiments.

Figure 14 is an exploded perspective view illustrating the structure of the heat exchanger 406 according to the fourth embodiment. Figure 15 is an explanatory diagram of the cross-sectional structure of the refrigerant distributor 410 of the heat exchanger 406 according to the fourth embodiment. The refrigerant distributor 410 of the heat exchanger 406 according to the fourth embodiment is similar to the heat exchangers 6, 206, and 306 in the first to third embodiments in that it separates the gas-liquid two-phase refrigerant flowing in from the refrigerant inlet pipe 14 into a gas-phase refrigerant and a liquid-phase refrigerant in the gas-liquid separation chamber 20. However, the refrigerant distributor 410 of the heat exchanger 406 according to the fourth embodiment has a distribution chamber 421 to which a plurality of heat transfer tubes 30 are connected, which is divided into a plurality of chambers in the z direction by a partition member 42. In addition, between the gas-liquid separation chamber 20 and the distribution chamber 421, there is a liquid chamber 427 into which only the liquid-phase refrigerant flows, and a gas chamber 428 into which only the gas-phase refrigerant flows.

As shown in FIG. 14, a gas flow hole 415a is provided at the top of the gas-liquid separation chamber 20, i.e., at the top of the partition plate 411, and a liquid flow hole 416a is provided at the bottom. The gas chamber 428 is connected to the gas-liquid separation chamber 20 via the gas flow hole 415a, so only gas phase refrigerant flows in. The liquid chamber 427 is connected to the gas-liquid separation chamber 20 via the liquid flow hole 416a, so only liquid phase refrigerant flows in. The liquid chamber 427 and the gas chamber 428 are separated by a partition plate 417, and each is an independent space. The liquid chamber 427 and the gas chamber 428 are separated from the distribution chamber 421 by a partition plate 418.

The liquid chamber 427 is provided in the partition plate 418, and has a liquid circulation hole 416b communicating with the distribution chamber 421. The gas chamber 428 has a gas circulation hole 415b communicating with the distribution chamber 421. In the fourth embodiment, the distribution chamber 421 into which the heat transfer tubes 30 are inserted is divided into a plurality of junctions 421a, 421b, 421c, and 421d in the z direction. The liquid circulation hole 416b and the gas circulation hole 415b are provided corresponding to the plurality of junctions 421a, 421b, 421c, and 421d, respectively. Therefore, the liquid phase refrigerant in the liquid chamber 427 and the gas phase refrigerant in the gas chamber 428 flow into each of the plurality of junctions 421a, 421b, 421c, and 421d without bias. The gas phase refrigerant and liquid phase refrigerant flowing into the multiple junctions 421a, 421b, 421c, and 421d are mixed and flow into the multiple heat transfer tubes 30. Since the separated gas phase refrigerant and liquid phase refrigerant flow into the multiple junctions 421a, 421b, 421c, and 421d from separate paths, the variation in the ratio of the gas phase refrigerant to the liquid phase refrigerant is suppressed.

In addition, when the multiple heat transfer tubes 30 are flat multi-hole tubes, if the gas phase refrigerant and the liquid phase refrigerant flow separately for each refrigerant flow path, a temperature difference occurs between the gas phase refrigerant and the liquid phase refrigerant. Then, heat exchange occurs between the gas phase refrigerant and the liquid phase refrigerant, and the amount of heat exchange between the air and the refrigerant passing through the heat exchanger may decrease. In the fourth embodiment, the gas phase refrigerant and the liquid phase refrigerant flow into the multiple junctions 421a, 421b, 421c, and 421d in the same ratio and merge. As a result, a refrigerant mixed with the gas phase refrigerant and the liquid phase refrigerant can flow into each of the multiple heat transfer tubes 30, suppressing heat exchange between the gas phase refrigerant and the liquid phase refrigerant and promoting heat exchange between the air and the refrigerant. In addition, as in the first to third embodiments, the heat exchanger 406 separates the gas-liquid two-phase refrigerant into the gas phase refrigerant and the liquid phase refrigerant, and then merges them at the multiple junctions 421a, 421b, 421c, and 421d that are divided. As a result, the variation in the ratio of gas phase refrigerant to liquid phase refrigerant flowing into each of the multiple junctions 421a, 421b, 421c, and 421d is reduced, and the variation in the ratio of gas phase refrigerant to liquid phase refrigerant flowing into each of the multiple heat transfer tubes 30 is also reduced.

(Modification)
16 is an exploded perspective view illustrating the structure of a heat exchanger 406a which is a modification of the heat exchanger 406 according to the fourth embodiment. The heat exchanger 406 creates spaces for refrigerant separation and merging by dividing the refrigerant distributor 410 into three spaces in the x direction using two partition plates 411 and 418. In contrast, the heat exchanger 406a according to the modification creates spaces for refrigerant separation and merging by stacking plate materials 451 and 454 and providing holes or elongated holes such as gas circulation holes 415 and liquid circulation holes 416 in each of the plate materials.

Specifically, the liquid chamber 427 and the gas chamber 428 are formed by providing two long holes 452, whose major axes extend in the z direction, in parallel in the y direction in a single plate material 451. The central portion 453 of the plate material 451 between the two long holes 452 corresponds to the dividing plate 417. One of the two long holes 452 communicates with the gas-liquid separation chamber 20 via the gas circulation hole 415, and the other communicates with the gas-liquid separation chamber 20 via the liquid circulation hole 416.

The multiple distribution chambers 421 of the heat exchanger 406a according to the modified example are formed by providing multiple long holes 455 with their major axes extending in the y direction in parallel in the z direction in the plate material 454. The multiple long holes 455 are formed corresponding to each of the multiple heat transfer tubes 30. Each of the multiple long holes 455 is connected to both the long hole 452 that is the liquid chamber 427 and the long hole 452 that is the gas chamber 428. As a result, the liquid phase refrigerant from the liquid chamber 427 and the gas phase refrigerant from the gas chamber 428 merge in each of the multiple long holes 455 that are the multiple distribution chambers 421. Note that the multiple long holes 455 correspond to each of the multiple heat transfer tubes 30, but are not limited to this form. For example, one distribution chamber 421 may be connected to two or more heat transfer tubes 30.

The refrigerant distributor 410a of the heat exchanger 406a according to the modified example is formed by stacking members of a simple shape, such as plate materials 451 and 454, which are simply holes provided in the members. Therefore, the heat exchanger 406a can be manufactured inexpensively with a small number of parts. In addition, since the refrigerant distributor 410a of the heat exchanger 406a is formed by stacking members such as plate materials 451 and 454, the thickness dimension in the x direction is reduced, and the area of the heat transfer section in which the multiple heat transfer tubes 30 are installed can be increased accordingly.

Embodiment 5.
The refrigeration cycle apparatus 500 according to the fifth embodiment is obtained by modifying the structure of the heat exchanger 206 according to the second embodiment. The refrigeration cycle apparatus 500 according to the fifth embodiment will be described mainly with respect to the changes made to the second embodiment. Regarding the components of the refrigeration cycle apparatus 500 according to the fifth embodiment, those components having the same functions in each drawing are indicated by the same reference numerals as those in the drawings used in the description of the first to fourth embodiments.

Figure 17 is an explanatory diagram of the cross-sectional structure of the heat exchanger 506 according to embodiment 5. Figure 17 shows a cross section along the xz axis. The refrigerant distributor 510 of the heat exchanger 506 according to embodiment 5 is provided with a liquid refrigerant capture structure 570 in the gas-liquid separation chamber 20. The liquid refrigerant capture structure 570 is, for example, a mesh filter, and the mesh size and material can be set appropriately. The liquid refrigerant capture structure 570 is located between the refrigerant inlet pipe 514 and the gas flow hole 15 in the z direction, and is arranged to divide the gas-liquid separation chamber 20 in the z direction.

The refrigerant inlet pipe 514 is inserted into the gas-liquid separation chamber 20 at an incline in the z-reverse direction. Therefore, the gas-liquid two-phase refrigerant flowing in from the refrigerant inlet pipe 514 moves in the z-reverse direction. In the process, the gas-liquid two-phase refrigerant is influenced by gravity, and the liquid phase refrigerant is biased and accumulates in the lower part of the gas-liquid separation chamber 20. In addition, the gas phase refrigerant and the liquid phase refrigerant in the form of fine particles are biased to the upper part of the gas-liquid separation chamber 20. A gas circulation hole 15 is installed in the upper part of the gas-liquid separation chamber 20, and the separated gas phase refrigerant flows into the second distribution chamber 222 of the distribution chamber 21. At this time, the liquid phase refrigerant floating in the form of fine particles together with the gas phase refrigerant may also flow into the second distribution chamber 222. The refrigerant distributor 510 of the heat exchanger 506 according to embodiment 5 is provided with a distribution chamber 21 consisting of a first distribution chamber 221 and a second distribution chamber 222, similar to the refrigerant distributor 210 of the heat exchanger 206 according to embodiment 2.

The liquid refrigerant capture structure 570 is structured to allow gas phase refrigerant to pass through. By providing the liquid refrigerant capture structure 570 to the heat exchanger 506, the liquid phase refrigerant that moves to the upper part of the gas-liquid separation chamber 20 together with the gas phase refrigerant adheres to the liquid refrigerant capture structure 570 and falls in the direction of gravity as droplets. As a result, the heat exchanger 506 according to the fifth embodiment promotes separation of the gas phase refrigerant and the liquid phase refrigerant.

Embodiment 6.
The refrigeration cycle apparatus 600 according to the sixth embodiment is obtained by modifying the structure of the heat exchanger 206 according to the second embodiment. The refrigeration cycle apparatus 600 according to the sixth embodiment will be described mainly with respect to the changes made to the second embodiment. Regarding the components of the refrigeration cycle apparatus 600 according to the sixth embodiment, those components having the same functions in each drawing are indicated by the same reference numerals as those in the drawings used in the description of the first to fifth embodiments.

Figure 18 is an explanatory diagram of the cross-sectional structure of the heat exchanger 606 according to the sixth embodiment. Figure 18 shows a cross section along the xz axis. The refrigerant distributor 610 of the heat exchanger 606 according to the sixth embodiment is provided with a baffle plate 670 in the gas-liquid separation chamber 20. The baffle plate 670 is disposed below the portion where the refrigerant inlet pipe 614 is inserted, and extends from the wall surface where the refrigerant inlet pipe 614 is installed toward the partition plate 11. The baffle plate 670 has a communication hole 671 that communicates the upper and lower parts of the gas-liquid separation chamber 20 at the portion on the partition plate 11 side. The baffle plate 670 is inclined in the z-reverse direction toward the partition plate 11 side, and is formed so that the gas-liquid two-phase refrigerant flowing in from the refrigerant inlet pipe 614, which is also inclined in the z-reverse direction, flows along it. In the sixth embodiment, the baffle plate 670 and the refrigerant inlet pipe 614 are formed so as to be parallel to each other, but this is not limited to this. For example, the refrigerant inflow pipe 614 may be inclined in the z-reverse direction more than the baffle plate 670 so that the gas-liquid two-phase refrigerant flowing in from the refrigerant inflow pipe 614 hits the baffle plate 670. When the gas-liquid two-phase refrigerant hits the baffle plate 670, the liquid phase refrigerant contained in the gas-liquid two-phase refrigerant adheres to the surface of the baffle plate 670 and flows downward through the communication holes 671. This promotes gas-liquid separation of the refrigerant in the gas-liquid separation chamber 20.

The gas-liquid separation chamber 20 is divided into two spaces in the z direction by the baffle plate 670, and in FIG. 18, the space below the baffle plate 670 is called the first space 620a, and the space above is called the second space 620b. A gas circulation pipe 615a is connected to the gas circulation hole 615 provided in the second space 620b, which is the space at the top of the gas-liquid separation chamber 20. The tip 615b of the gas circulation pipe 615a is located in the second space 620b, which is the space below the baffle plate 670. The gas circulation pipe 615a is configured to send the gas phase refrigerant from the upper part of the space below the baffle plate 670 to the second distribution chamber 222. By being configured in this way, the liquid phase refrigerant flows downward by adhering to the baffle plate 670 and the partition plate 11, and the gas phase refrigerant flows into the gas circulation pipe 615a. Therefore, gas-liquid separation of the refrigerant in the gas-liquid separation chamber 20 is performed efficiently.

The present disclosure is not limited to the configurations described above. For example, the heat exchangers 6, 206, 306, 406, 506, and 606 according to the first to sixth embodiments may be configured by stacking plate materials in some structures, like the heat exchanger 406a. The heat exchangers 6, 206, 306, 406, 506, and 606 may be applied not only to the outdoor unit 1 but also to the indoor unit 2. Furthermore, the present disclosure may be configured by combining each embodiment. For example, the liquid refrigerant capture structure 570 of the fifth embodiment may be applied to the first, third, fourth, or sixth embodiment. The structure of the baffle plate 670 of the sixth embodiment may be applied to the first, third, fourth, or fifth embodiment.

1 outdoor unit, 2 indoor unit, 3 compressor, 4 indoor heat exchanger, 4f indoor blower, 5 pressure reducing device, 6 (outdoor) heat exchanger, 6f outdoor blower, 7 flow path switching device, 8 flow control valve, 9 bypass flow path, 10 refrigerant distributor, 11 partition plate, 12 outer casing member, 13 outer casing member, 14 refrigerant inlet pipe, 15 gas flow hole, 15a gas flow pipe, 16 liquid flow hole, 20 gas-liquid separation chamber, 21 distribution chamber, 25 end member, 30 heat transfer tube, 31 end, 32 refrigerant flow section, 33 end surface, 42 partition member, 60 tube portion, 91 gas phase refrigerant, 92 liquid phase refrigerant, 99 refrigerant circuit, 100 refrigeration cycle device, 111 extension pipe, 112 extension pipe, 200 refrigeration cycle device, 206 heat exchanger, 210 Refrigerant distributor, 215 Gas circulation hole, 217 Dividing plate, 221 First distribution chamber, 222 Second distribution chamber, 299 Refrigerant circuit, 300 Refrigeration cycle device, 306 Heat exchanger, 310 Refrigerant distributor, 400 Refrigeration cycle device, 406 Heat exchanger, 406a Heat exchanger, 410 Refrigerant distributor, 410a Refrigerant distributor, 411 Partition plate, 415 Gas circulation hole, 415a Gas circulation hole, 415b Gas circulation hole, 416 Liquid circulation hole, 416a Liquid circulation hole, 416b Liquid circulation hole, 417 Dividing plate, 421 Distribution chamber, 421a Junction, 421b Junction, 421c Junction, 427 Liquid chamber, 428 Gas chamber, 451 Plate material, 452 Long hole, 453 Center portion, 454 Plate material, 455 long hole, 500 refrigeration cycle device, 506 heat exchanger, 510 refrigerant distributor, 514 refrigerant inlet pipe, 570 liquid refrigerant capture structure, 600 refrigeration cycle device, 606 heat exchanger, 610 refrigerant distributor, 614 refrigerant inlet pipe, 615 gas circulation hole, 615a gas circulation pipe, 615b tip portion, 620a first space, 620b second space, 670 baffle plate, 671 communication hole, AF arrow, G region, L region.

Claims (11)

A plurality of heat transfer tubes arranged in parallel in a first direction and extending in a second direction intersecting the first direction;
a refrigerant distributor to which one ends of the plurality of heat transfer tubes are connected;
a refrigerant inlet pipe connected to the refrigerant distributor, the refrigerant inlet pipe being used with one end in the first direction positioned at an upper position and the other end positioned at a lower position,
The refrigerant distributor comprises:
The insulating film is formed to extend along the first direction,
a gas-liquid separation chamber that separates the refrigerant flowing in from the refrigerant inlet pipe into a gas phase refrigerant and a liquid phase refrigerant;
a distribution chamber to which the ends of the plurality of heat transfer tubes are connected;
a partition plate that divides the internal space into the gas-liquid separation chamber and other spaces in the second direction;
a liquid flow hole that communicates the gas-liquid separation chamber with the distribution chamber and through which the liquid phase refrigerant flows;
a gas circulation hole that communicates the gas-liquid separation chamber with the distribution chamber, is shifted upward in the first direction with respect to the liquid circulation hole, and through which the gas-phase refrigerant flows;
The refrigerant inlet pipe is
a gas passage hole and a liquid passage hole,
The gas-liquid separation chamber is
In the second direction, the heat transfer tube is located farther from the distribution chamber ,
a baffle plate extending from a wall surface on a side where the refrigerant inlet pipe is installed between the refrigerant inlet pipe and the liquid circulation hole toward the partition plate;
a gas circulation pipe extending from the gas circulation hole and communicating the gas circulation hole with a first space, which is a space on the side of the baffle plate on which the liquid circulation hole is disposed;
The baffle plate is
a communication hole that communicates the first space with a second space, which is the space on the side where the gas circulation holes are arranged. A plurality of heat transfer tubes arranged in parallel in a first direction and extending in a second direction intersecting the first direction;
a refrigerant distributor to which one ends of the plurality of heat transfer tubes are connected;
a refrigerant inlet pipe connected to the refrigerant distributor, the heat exchanger being used with one end in the first direction positioned at an upper position and the other end positioned at a lower position,
The refrigerant distributor comprises:
The insulating film is formed to extend along the first direction,
a gas-liquid separation chamber that separates the refrigerant flowing in from the refrigerant inlet pipe into a gas phase refrigerant and a liquid phase refrigerant;
a distribution chamber to which the ends of the plurality of heat transfer tubes are connected;
a partition plate that divides the internal space into the gas-liquid separation chamber and other spaces in the second direction;
a liquid flow hole that communicates the gas-liquid separation chamber with the distribution chamber and through which the liquid phase refrigerant flows;
a gas circulation hole that communicates the gas-liquid separation chamber with the distribution chamber, is shifted upward in the first direction with respect to the liquid circulation hole, and through which the gas-phase refrigerant flows;
The gas-liquid separation chamber is
In the second direction, the heat transfer tube is located farther from the distribution chamber,
The distribution chamber comprises:
a first distribution chamber and a second distribution chamber divided in a third direction intersecting a plane parallel to the first direction and the second direction,
The first distribution chamber is
The liquid passage hole communicates with the gas-liquid separation chamber,
The second distribution chamber is
a heat exchanger communicating with the gas-liquid separation chamber through the gas communication hole. A plurality of heat transfer tubes arranged in parallel in a first direction and extending in a second direction intersecting the first direction;
a refrigerant distributor to which one ends of the plurality of heat transfer tubes are connected;
a refrigerant inlet pipe connected to the refrigerant distributor, the heat exchanger being used with one end in the first direction positioned at an upper position and the other end positioned at a lower position,
The refrigerant distributor comprises:
The insulating film is formed to extend along the first direction,
a gas-liquid separation chamber that separates the refrigerant flowing in from the refrigerant inlet pipe into a gas phase refrigerant and a liquid phase refrigerant;
a distribution chamber to which the ends of the plurality of heat transfer tubes are connected;
a partition plate that divides the internal space into the gas-liquid separation chamber and other spaces in the second direction;
a liquid flow hole that communicates the gas-liquid separation chamber with the distribution chamber and through which the liquid phase refrigerant flows;
a gas circulation hole that communicates the gas-liquid separation chamber with the distribution chamber, is shifted upward in the first direction with respect to the liquid circulation hole, and through which the gas-phase refrigerant flows;
The gas-liquid separation chamber is
In the second direction, the heat transfer tube is located farther from the distribution chamber,
Further comprising a gas chamber and a liquid chamber disposed between the distribution chamber and the gas-liquid separation chamber,
The gas chamber comprises:
The gas-liquid separation chamber communicates with the gas-liquid separation chamber through the gas flow hole,
The liquid chamber is
The liquid passage hole is connected to the gas-liquid separation chamber,
Each of the gas chamber and the liquid chamber is
A heat exchanger in communication with the distribution chamber. The distribution chamber comprises:
The heat exchanger according to claim 3 , wherein the heat exchanger is divided into a plurality of junctions in the first direction. A plurality of heat transfer tubes arranged in parallel in a first direction and extending in a second direction intersecting the first direction;
a refrigerant distributor to which one ends of the plurality of heat transfer tubes are connected;
a refrigerant inlet pipe connected to the refrigerant distributor, the heat exchanger being used with one end in the first direction positioned at an upper position and the other end positioned at a lower position,
The refrigerant distributor comprises:
The insulating film is formed to extend along the first direction,
a gas-liquid separation chamber that separates the refrigerant flowing in from the refrigerant inlet pipe into a gas phase refrigerant and a liquid phase refrigerant;
a distribution chamber to which the ends of the plurality of heat transfer tubes are connected;
a partition plate that divides the internal space into the gas-liquid separation chamber and other spaces in the second direction;
a liquid flow hole that communicates the gas-liquid separation chamber with the distribution chamber and through which the liquid phase refrigerant flows;
a gas circulation hole that communicates the gas-liquid separation chamber with the distribution chamber, is shifted upward in the first direction with respect to the liquid circulation hole, and through which the gas-phase refrigerant flows;
The gas-liquid separation chamber is
In the second direction, the heat transfer tube is located farther from the distribution chamber,
The refrigerant distributor comprises:
A heat exchanger formed by stacking a plurality of plate-like members. The gas-liquid separation chamber is
The heat exchanger according to claim 2 , further comprising a liquid refrigerant trapping structure that traps liquid refrigerant between the gas circulation hole and the refrigerant inlet pipe. A heat exchanger according to any one of claims 1 to 6 ,
A blower that blows air to the heat exchanger. The heat exchanger includes:
The heat exchanger unit according to claim 7 , wherein the first direction is oriented in a direction of gravity. A heat exchanger according to claim 3 or claim 4 ;
A blower that blows air to the heat exchanger,
The gas chamber comprises:
A heat exchanger unit located on the windward side of the liquid chamber. A heat exchanger according to claim 3 or claim 4 ;
A blower that blows air to the heat exchanger,
The gas chamber comprises:
A heat exchanger unit located on the downwind side of the liquid chamber. A refrigeration cycle device comprising the heat exchanger unit according to any one of claims 7 to 10 .

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