JP7724953B2 - Heat exchanger and air conditioner having the same - Google Patents

Description

The present disclosure relates to a heat exchanger having multiple heat transfer tubes and an air conditioning device having the same.

In conventional heat exchangers that exchange heat between air and refrigerant, refrigerant is distributed by circulating a two-phase gas-liquid refrigerant through multiple heat transfer tubes connected to a header section, which acts as a refrigerant distributor. The distribution characteristics of the liquid refrigerant flowing through each heat transfer tube vary depending on the structure of the header section, affecting heat exchange performance. For example, if the header section extends horizontally and multiple heat transfer tubes extend vertically, the refrigerant distribution characteristics change significantly depending on the quality factor (the mass ratio of gas refrigerant to liquid refrigerant) and the flow velocity of the refrigerant flowing through the header section.

When the dryness fraction of the refrigerant at the header inlet is low, i.e., when the refrigerant has a high proportion of liquid refrigerant, the refrigerant distribution characteristics improve, and the heat exchange performance of the heat exchanger increases. To reduce the dryness fraction of the refrigerant at the header inlet, a heat exchanger is known that is equipped with a gas-liquid separator upstream of the header in the refrigerant flow direction (see, for example, Patent Document 1).

Patent No. 3122578

In the case of the heat exchanger disclosed in Patent Document 1, a new gas-liquid separator must be installed as a refrigerant auxiliary device, separate from the header section.

This disclosure has been made to solve the above-mentioned problems, and provides a heat exchanger and an air conditioning device having the same that improves refrigerant distribution characteristics to multiple heat transfer tubes without the need to install a new refrigerant auxiliary device.

A heat exchanger according to the present disclosure is a heat exchanger that exchanges heat between air and a refrigerant, and includes: a plurality of heat transfer tubes, each extending in a vertical direction and arranged at intervals in a horizontal direction perpendicular to the vertical direction; a first header that connects the plurality of heat transfer tubes to ends of each of the heat transfer tubes that are opposite to the vertical direction; a second header that connects the plurality of heat transfer tubes to ends of each of the heat transfer tubes in the vertical direction; and a gas separation pipe that connects the first header to a refrigerant pipe that passes the refrigerant flowing out of the second header when the heat exchanger operates as an evaporator, wherein the first header separates the interior of the first header into a plurality of spaces including a mainstream space and a gas separation space. a partition wall having a plurality of first openings in the partition wall that communicate between the mainstream space and the gas separation space, the gas separation space being located above the mainstream space, and the gas separation space being connected to the refrigerant piping by the gas separation piping, the partition wall separating the interior of the first header into the mainstream space, the gas separation space, and a jetting space, a plurality of second openings in the partition wall that communicate between the mainstream space and the jetting space, each of the plurality of second openings being located at the boundary of the liquid surface of the refrigerant in a liquid phase flowing through the mainstream space, and being located at a position that does not overlap with a plane obtained by projecting a flow path cross section of the heat transfer tube in a direction opposite to the vertical direction .

The air conditioning apparatus of the present disclosure comprises the above-mentioned heat exchanger, a blower that supplies the air to the heat exchanger, and a housing that houses the heat exchanger and the blower.

The heat exchanger disclosed herein has a gas separation space in the first header that separates gas refrigerant from gas-liquid two-phase refrigerant. Of the gas-liquid two-phase refrigerant that flows into the first header, the gas refrigerant is separated from the mainstream space into the gas separation space, reducing the proportion of gas refrigerant in the mainstream space. As a result, the proportion of liquid refrigerant in the gas-liquid two-phase refrigerant in the mainstream space increases, allowing for more uniform refrigerant distribution from the mainstream space to multiple heat transfer tubes. As a result, refrigerant distribution characteristics can be improved without the need for a new refrigerant auxiliary unit.

1 is a refrigerant circuit diagram of an air conditioning apparatus according to Embodiment 1. FIG. 3 is a refrigerant circuit diagram showing the flow of refrigerant when the air conditioning apparatus according to the first embodiment performs cooling operation. FIG. 3 is a plan view showing one configuration example of a heat source side heat exchanger housed in a heat source side unit of the air conditioning apparatus according to Embodiment 1. FIG. FIG. 10 is a plan view showing another configuration example of a heat source side heat exchanger housed in the heat source side unit of the air conditioning apparatus according to Embodiment 1. FIG. 10 is a plan view showing another configuration example of a heat source side heat exchanger housed in the heat source side unit of the air conditioning apparatus according to Embodiment 1. 10 is a plan view showing an example of the configuration of a heat source side heat exchanger housed in another heat source side unit of the air conditioning apparatus according to Embodiment 1. FIG. FIG. 10 is a plan view showing another example of the configuration of a heat source side heat exchanger housed in another heat source side unit of the air conditioning apparatus according to Embodiment 1. FIG. 10 is a plan view showing another example of the configuration of a heat source side heat exchanger housed in another heat source side unit of the air conditioning apparatus according to Embodiment 1. FIG. 2 is a side view for explaining the configuration of the heat source side heat exchanger according to the first embodiment. 10 is a side view showing a configuration example in which heat radiation fins are provided in the heat source side heat exchanger shown in FIG. 9 . FIG. FIG. 10 is a cross-sectional view showing the structure of the line AA in FIG. 9. 12 is a schematic diagram showing an example of the internal configuration of the first header shown in FIG. 11 . FIG. 10 is a schematic diagram illustrating an example of the internal configuration of a first header of Modification 1. FIG. 10 is a schematic diagram illustrating an example of the internal configuration of a first header of Modification 2. FIG. 11 is a schematic diagram illustrating an example of the internal configuration of a first header of a third modified example. FIG. 13 is a schematic diagram showing an example of the internal configuration of a first header of Modification 4. 10 is a cross-sectional schematic view showing an example of the internal configuration of a first header of a heat source side heat exchanger according to embodiment 2. FIG. FIG. 10 is a side view for explaining the configuration of a heat source side heat exchanger according to embodiment 3. FIG. 10 is a side view for explaining the configuration of a heat source side heat exchanger according to embodiment 4. FIG. 10 is a side view for explaining the configuration of a heat source side heat exchanger according to embodiment 5. FIG. 13 is a side view for explaining the configuration of a heat source side heat exchanger according to embodiment 6. 22 is a side view of the heat source side heat exchanger shown in FIG. 21 as viewed from another direction. FIG. FIG. 11 is a refrigerant circuit diagram of an air conditioning apparatus having a heat source side heat exchanger according to a seventh embodiment. FIG. 13 is a side view for explaining the configuration of a heat source side heat exchanger according to embodiment 7.

Embodiments of the heat exchanger and air conditioning apparatus of the present disclosure will be described with reference to the drawings. Equivalent components are designated by the same reference numerals in multiple drawings, and descriptions of components that have been described once will be omitted or simplified as appropriate in subsequent embodiments. Furthermore, hatching has been omitted as appropriate in drawings illustrating cross sections to improve visibility. Furthermore, the forms of the components described in each embodiment are merely examples and are not limited to these descriptions. Furthermore, the shape, size, and arrangement of the components depicted in each drawing may be modified as appropriate within the scope of this disclosure.

In addition, some of the drawings used for explanation include arrows on three orthogonal axes (X-axis, Y-axis, and Z-axis) that define directions. The X-axis arrow indicates the width direction, and the Y-axis arrow indicates the depth direction. The direction opposite the Z-axis arrow indicates the vertical direction (direction of gravity).

Embodiment 1.
The configuration of an air conditioner having a heat exchanger according to Embodiment 1 will be described. Fig. 1 is a refrigerant circuit diagram of the air conditioner according to Embodiment 1. As shown in Fig. 1, the air conditioner 10 has a heat source side heat exchanger 1, a load side heat exchanger 2, a compressor 3, a throttling device 4, and a four-way valve 5. The compressor 3, the heat source side heat exchanger 1, the throttling device 4, and the load side heat exchanger 2 are connected by refrigerant piping 6 to form a refrigerant circuit 20 in which the refrigerant circulates. A gas separation piping 9 is connected to the heat source side heat exchanger 1. The throttling device 4 is, for example, an expansion valve.

The air conditioning unit 10 also has a heat source side blower 7 and a load side blower 8. The heat source side blower 7 draws in outside air and supplies it to the heat source side heat exchanger 1. The load side blower 8 draws in air from inside the target space and supplies it to the load side heat exchanger 2.

(Operation during heating operation)
The flow of the refrigerant when the air conditioner 10 is in heating operation will be described with reference to Fig. 1. The arrows in Fig. 1 indicate the direction of flow of the refrigerant.

Low-temperature, low-pressure gas refrigerant is drawn into the compressor 3 and compressed by the compressor 3, becoming high-temperature, high-pressure gas refrigerant. The high-temperature, high-pressure gas refrigerant is discharged from the compressor 3, passes through the four-way valve 5, and then flows into the load-side heat exchanger 2. The high-temperature, high-pressure gas refrigerant that flows into the load-side heat exchanger 2 exchanges heat with indoor air supplied by the load-side blower 8, releasing heat and condensing, becoming high-temperature, high-pressure liquid refrigerant, which then flows out of the load-side heat exchanger 2. The liquid refrigerant that flows out of the load-side heat exchanger 2 is expanded and decompressed by the throttle device 4, becoming low-temperature, low-pressure two-phase gas-liquid refrigerant. The low-temperature, low-pressure two-phase gas-liquid refrigerant flows into the heat-source-side heat exchanger 1. The two-phase gas-liquid refrigerant that flows into the heat-source-side heat exchanger 1 absorbs heat and evaporates by exchanging heat with outside air supplied by the heat-source-side blower 7, becoming low-temperature, low-pressure gas refrigerant. The low-temperature, low-pressure gas refrigerant flows out of the heat-source-side heat exchanger 1. The low-temperature, low-pressure gas refrigerant is again drawn into the compressor 3, and when compressed by the compressor 3, becomes high-temperature, high-pressure gas refrigerant and is discharged from the compressor 3. In this manner, the refrigerant is repeatedly circulated.

(Operation during cooling operation)
The flow of refrigerant when the air conditioning apparatus 10 is in cooling operation will be described with reference to Fig. 2. Fig. 2 is a refrigerant circuit diagram showing the flow of refrigerant when the air conditioning apparatus according to Embodiment 1 is in cooling operation. The arrows in Fig. 2 indicate the direction of refrigerant flow.

Low-temperature, low-pressure gas refrigerant is drawn into the compressor 3 and compressed by the compressor 3, becoming high-temperature, high-pressure gas refrigerant. When the high-temperature, high-pressure gas refrigerant is discharged from the compressor 3, it flows through the four-way valve 5 and then flows into the heat source-side heat exchanger 1. The high-temperature, high-pressure gas refrigerant that flows into the heat source-side heat exchanger 1 exchanges heat with outside air supplied by the heat source-side blower 7, releasing heat and condensing, becoming high-temperature, high-pressure liquid refrigerant, which then flows out of the heat source-side heat exchanger 1. The liquid refrigerant that flows out of the heat source-side heat exchanger 1 expands and decompresses through the throttle device 4, becoming low-temperature, low-pressure two-phase gas-liquid refrigerant. The low-temperature, low-pressure two-phase gas-liquid refrigerant flows into the load-side heat exchanger 2. The two-phase gas-liquid refrigerant that flows into the load-side heat exchanger 2 absorbs heat and evaporates by exchanging heat with indoor air supplied by the load-side blower 8, becoming low-temperature, low-pressure gas refrigerant. The low-temperature, low-pressure gas refrigerant flows out of the load-side heat exchanger 2. The low-temperature, low-pressure gas refrigerant is again drawn into the compressor 3, and when compressed by the compressor 3, becomes high-temperature, high-pressure gas refrigerant and is discharged from the compressor 3. In this manner, the refrigerant is repeatedly circulated.

(Operation during defrosting operation)
The flow of refrigerant when the air conditioner 10 performs a defrosting operation will be described with reference to Fig. 2. The arrows in Fig. 2 indicate the flow direction of the refrigerant.

Low-temperature, low-pressure gas refrigerant is drawn into the compressor 3 and compressed by the compressor 3, becoming high-temperature, high-pressure gas refrigerant. The high-temperature, high-pressure gas refrigerant is discharged from the compressor 3, flows through the four-way valve 5, and then flows into the heat source-side heat exchanger 1. The high-temperature, high-pressure gas refrigerant that flows into the heat source-side heat exchanger 1 exchanges heat with outside air supplied by the heat source-side blower 7 and frost adhering to the outer surface of the heat source-side heat exchanger 1, releasing heat and condensing, becoming high-temperature, high-pressure liquid refrigerant and flowing out of the heat source-side heat exchanger 1. The liquid refrigerant that flows out of the heat source-side heat exchanger 1 is expanded and decompressed by the throttle device 4, becoming low-temperature, low-pressure two-phase gas-liquid refrigerant. The low-temperature, low-pressure two-phase gas-liquid refrigerant flows into the load-side heat exchanger 2. The two-phase gas-liquid refrigerant that flows into the load-side heat exchanger 2 absorbs heat and evaporates through heat exchange with indoor air supplied by the load-side blower 8, becoming low-temperature, low-pressure gas refrigerant. The low-temperature, low-pressure gas refrigerant flows out of the load-side heat exchanger 2. The low-temperature, low-pressure gas refrigerant is again drawn into the compressor 3, and when compressed by the compressor 3, becomes high-temperature, high-pressure gas refrigerant and is discharged from the compressor 3. In this manner, the refrigerant is repeatedly circulated.

The number of heat source side heat exchangers 1 and load side heat exchangers 2 is not limited to the numbers shown in Figures 1 and 2. The number of heat source side heat exchangers 1 and load side heat exchangers 2 may be determined according to the environment in which the air conditioning device 10 is installed or the size of the target space to be air-conditioned by the air conditioning device 10.

(Configuration of heat source side heat exchanger 1)
The configuration of the heat source side heat exchanger 1 of the present embodiment 1 will be described. In the present embodiment 1, the case where the heat source side heat exchanger 1 operates as an evaporator will be described, but it may also operate as a condenser. When the heat source side heat exchanger 1 operates as a condenser, the flow direction of the refrigerant in the refrigerant circuit 20 is opposite to that when the heat source side heat exchanger 1 operates as an evaporator. Furthermore, although the heat exchanger of the present disclosure will be described as the heat source side heat exchanger 1, the configuration of the load side heat exchanger 2 may be the same as the configuration of the heat source side heat exchanger 1. Hereinafter, the heat source side heat exchanger 1 and the load side heat exchanger 2 may be collectively referred to simply as heat exchangers.

Figure 3 is a plan view showing an example configuration of a heat source side heat exchanger housed in the heat source side unit of an air conditioning apparatus according to embodiment 1. Figure 3 is a plan view of the housing 25 of the heat source side unit housing the heat source side heat exchanger 1 and the heat source side blower 7, as viewed from above. The housing 25 is a top flow type housing that, when the propeller of the heat source side blower 7 rotates, draws in air from the four sides of the housing 25 and blows it out in the opposite vertical direction. The planar shape of the housing 25 is rectangular. In Figure 3, arrows Dar indicate the direction of air flow, and arrows Drf indicate the direction of refrigerant flow.

The heat source side heat exchanger 1 shown in Figure 3 has a first heat exchanger 35a and a second heat exchanger 35b. As shown in Figure 3, the heat source side blower 7 is arranged in the center of the housing 25, and the first heat exchanger 35a and the second heat exchanger 35b are arranged along the side of the housing 25. When viewed vertically, the first heat exchanger 35a and the second heat exchanger 35b each have an L-shaped bending region 110 along the corner where the two side surfaces of the housing 25 meet.

Figure 4 is a plan view showing another example configuration of a heat source side heat exchanger housed in the heat source side unit of the air conditioning apparatus according to embodiment 1. In Figure 4, arrows Dar indicate the direction of air flow, and arrows Drf indicate the direction of refrigerant flow. The heat source side heat exchanger 1 shown in Figure 4 has a first heat exchanger 36a and a second heat exchanger 36b. Each of the first heat exchanger 36a and the second heat exchanger 36b has multiple rows of heat exchangers arranged in the direction of air flow.

The first heat exchanger 36a includes a first row of heat exchangers 131a, a second row of heat exchangers 132a, and a connecting pipe 27a connecting the first row of heat exchangers 131a and the second row of heat exchangers 132a. The first row of heat exchangers 131a are arranged on the upwind side, and the second row of heat exchangers 132a are arranged on the downwind side. Each of the first row of heat exchangers 131a and the second row of heat exchangers 132a has a bending region 110 that is bent in an L shape along the corner of the housing 25.

The second heat exchanger 36b includes a first row of heat exchangers 131b, a second row of heat exchangers 132b, and a connecting pipe 27b connecting the first row of heat exchangers 131b and the second row of heat exchangers 132b. The first row of heat exchangers 131b are arranged on the upwind side, and the second row of heat exchangers 132b are arranged on the downwind side. Each of the first row of heat exchangers 131b and the second row of heat exchangers 132b has an L-shaped bending region 110 that is bent along the corner of the housing 25.

Figure 5 is a plan view showing another example configuration of a heat source side heat exchanger housed in the heat source side unit of the air conditioning apparatus according to embodiment 1. In Figure 5, arrows Dar indicate the direction of air flow, and arrows Drf indicate the direction of refrigerant flow. The heat source side heat exchanger 1 shown in Figure 5 has a first heat exchanger 37a and a second heat exchanger 37b. Each of the first heat exchanger 37a and the second heat exchanger 37b has multiple rows of heat exchangers arranged in the direction of air flow.

The first heat exchanger 37a has a first row of heat exchangers 131a and a second row of heat exchangers 132a, but does not have the connecting piping 27a shown in FIG. 4. The first row of heat exchangers 131a are arranged on the upwind side, and the second row of heat exchangers 132a are arranged on the downwind side. Each of the first row of heat exchangers 131a and the second row of heat exchangers 132a has a bending region 110 that is bent in an L shape along the corner of the housing 25.

The second heat exchanger 36b has a first row of heat exchangers 131b and a second row of heat exchangers 132b, but does not have the connecting piping 27b shown in FIG. 4. The first row of heat exchangers 131b are arranged on the upwind side, and the second row of heat exchangers 132b are arranged on the downwind side. Each of the first row of heat exchangers 131b and the second row of heat exchangers 132b has a bending region 110 that is bent in an L-shape along the corner of the housing 25.

As mentioned above, Figures 4 and 5 show a case where multiple heat exchangers are arranged in the direction of air flow in the housing 25 of the heat source side unit.

Next, the heat source side heat exchanger 1 in this embodiment 1 will be described in the case where it is housed in a housing different from the housing 25 shown in Figures 3 to 5. Figure 6 is a plan view showing an example configuration of a heat source side heat exchanger housed in another heat source side unit of an air conditioning apparatus according to embodiment 1.

Figure 6 is a plan view of the housing 26 of the heat source side unit, which houses the compressor 3, heat source side heat exchanger 1, and heat source side blower 7, as seen from above. The housing 26 is a side flow type housing that, when the propeller of the heat source side blower 7 rotates, draws in air from two of the four sides of the housing 25 and blows the drawn-in air out from one side. The planar shape of the housing 26 is rectangular. In Figure 6, arrows Dar indicate the direction of air flow, and arrows Drf indicate the direction of refrigerant flow.

As shown in Figure 6, the heat source side blower 7 is arranged along one of the four sides of the housing 26, and the heat source side heat exchanger 1 is arranged along two sides of the housing 26. The heat source side heat exchanger 1 has a bending region 110 that is bent in an L shape along a corner of the housing 26.

Figure 7 is a plan view showing another example configuration of a heat source side heat exchanger housed in another heat source side unit of an air conditioning apparatus according to embodiment 1. In Figure 7, arrow Dar indicates the direction of air flow, and arrow Drf indicates the direction of refrigerant flow.

The heat source side heat exchanger 1 shown in Figure 7 has a first heat exchanger 37a and a second heat exchanger 37b arranged in the direction of air flow, and a connecting pipe 28 connecting the first heat exchanger 37a and the second heat exchanger 37b. The first heat exchanger 37a is arranged on the upwind side, and the second heat exchanger 37b is arranged on the downwind side. Each of the first heat exchanger 37a and the second heat exchanger 37b has a bending region 110 bent in an L shape along the corner of the housing 26.

Figure 8 is a plan view showing another example configuration of a heat source side heat exchanger housed in another heat source side unit of an air conditioning apparatus according to embodiment 1. In Figure 8, arrow Dar indicates the direction of air flow, and arrow Drf indicates the direction of refrigerant flow.

The heat source side heat exchanger 1 shown in Figure 8 has a first heat exchanger 37a and a second heat exchanger 37b arranged in the direction of air flow, but does not have the connecting piping 28 shown in Figure 7. The first heat exchanger 37a is arranged on the upwind side, and the second heat exchanger 37b is arranged on the downwind side. Each of the first heat exchanger 37a and the second heat exchanger 37b has a bending region 110 that is bent in an L shape along the corner of the housing 26.

As mentioned above, Figures 7 and 8 show a case in which multiple heat exchangers are arranged in the direction of air flow in the housing 26 of the heat source side unit.

With reference to Figures 3 to 8, examples of the configuration of a heat source side heat exchanger 1 having a bending region 110 bent in an L-shape with respect to the horizontal direction have been described, but the number of bending regions 110 formed is not limited to those shown in Figures 3 to 8. Two or more bending regions 110 may be provided in the heat source side heat exchanger 1. The heat source side heat exchanger 1 may not have a bending region 110. Also, for example, Figure 3 shows a configuration in which two heat exchangers, each with one bending region 110, are arranged within the housing 25, but the number of bending regions 110 and the arrangement of the bending regions 110 may be changed, and the number of heat exchangers and the arrangement of the heat exchangers may also be changed.

Next, the configuration of the heat source side heat exchanger 1 and the flow of refrigerant in this embodiment 1 will be described in detail. Figure 9 is a side view for explaining the configuration of the heat source side heat exchanger according to embodiment 1. In Figure 9, the arrow Drf indicates the direction of refrigerant flow. The heat source side heat exchanger 1 has a plurality of heat transfer tubes 11, each extending in the vertical direction and arranged at intervals in a horizontal direction perpendicular to the vertical direction, a first header 12, and a second header 13.

The first header 12 is connected to the ends of each of the multiple heat transfer tubes 11 in the opposite vertical direction (the direction of the Z-axis arrow). The second header 13 is connected to the ends of each of the multiple heat transfer tubes 11 in the vertical direction (the direction opposite to the Z-axis arrow). In this embodiment 1, the first header 12 serves to distribute the refrigerant flowing in from the expansion device 4 to the multiple heat transfer tubes 11. The second header 13 serves to merge the refrigerant flowing through the multiple heat transfer tubes 11. In this embodiment 1, the heat transfer tubes 11 are described as flat tubes, but they may also be circular tubes.

Although not shown in Figure 9, the heat source side heat exchanger 1 is provided with heat dissipation fins for dissipating heat from the refrigerant through the heat transfer tubes 11. Figure 10 is a side view showing an example configuration when heat dissipation fins are provided in the heat source side heat exchanger shown in Figure 9. As shown in Figure 10, corrugated fins 19 are provided between adjacent heat transfer tubes 11 at intervals in the multiple heat transfer tubes 11. The heat dissipation fins are not limited to corrugated fins 19 and may be plate fins. The heat source side heat exchanger 1 does not necessarily have to be provided with heat dissipation fins.

Furthermore, with reference to Figure 9, an example configuration has been described in which the first header 12 functions as a distribution header, the second header 13 functions as a merging header, and a combination of a distribution header and a merging header forms one set, but the combination and positional relationship of each header is not limited to this example configuration. As will be described later, the second header 13 may also function as a distribution header. Furthermore, each of the first header 12 and the second header 13 may be a combination of a distribution header and a merging header.

Next, the flow of refrigerant in the heat source-side heat exchanger 1 will be described with reference to Figures 1 and 9. When the heat source-side heat exchanger 1 operates as an evaporator, the gas-liquid two-phase refrigerant that flows into the first header 12 from the inlet 22 first flows into the mainstream space 15. Of the gas-liquid two-phase refrigerant that flows into the mainstream space 15, a portion of the gas refrigerant flows into the gas separation space 16 through the first opening 31. The gas refrigerant that flows into the gas separation space 16 flows via the gas separation piping 9 to the refrigerant piping 6 connected to the outlet 23 of the second header 13. Meanwhile, of the gas-liquid two-phase refrigerant that flows into the mainstream space 15, the refrigerant that does not flow into the gas separation space 16 is distributed to the multiple heat transfer tubes 11. The refrigerant distributed to the multiple heat transfer tubes 11 has a high proportion of liquid phase because some of the gas refrigerant has flowed into the gas separation space 16. The gas-liquid two-phase refrigerant distributed to the plurality of heat transfer tubes 11 exchanges heat with the air to evaporate, and flows through each heat transfer tube 11 while gasifying, and then flows into the second header 13. The gas refrigerant that has joined in the second header 13 flows out from the second header 13 to the refrigerant pipe 6 via the outlet 23.

Figure 11 is a schematic cross-sectional view showing the structure of the A-A line portion in Figure 9. For ease of explanation, Figure 11 illustrates a heat transfer tube 11 positioned in the X-axis direction shown in Figure 9 rather than the A-A line portion. The arrow Drf in Figure 11 indicates the direction of refrigerant flow. The first header 12 has an internal space divided into a mainstream space 15 and a gas separation space 16 by a plate-shaped partition wall 17. The gas separation space 16 is positioned above the mainstream space 15 in the Z-axis direction. The partition wall 17 is provided with a plurality of first openings 31 spaced apart in the X-axis direction, connecting the mainstream space 15 and the gas separation space 16. When the heat source side heat exchanger 1 operates as an evaporator, the plurality of first openings 31 are formed at a position higher than the liquid level of the liquid-phase refrigerant flowing through the mainstream space 15. This is to suppress the inflow of liquid refrigerant from the gas-liquid two-phase refrigerant flowing through the main space 15 into the gas separation space 16, and to facilitate separation of gas refrigerant from the gas-liquid two-phase refrigerant into the gas separation space 16.

In the heat source side heat exchanger 1, the gas-liquid two-phase refrigerant that flows into the first header 12 is affected by gravity, with the liquid refrigerant flowing mainly through the lower part of the mainstream space 15 and the gas refrigerant flowing mainly through the upper part of the mainstream space 15. As a result, the gas refrigerant passes through the first opening 31 from the mainstream space 15 and is separated into the gas separation space 16, reducing the proportion of gas in the mainstream space 15.

Note that the configuration example shown in Figure 11 shows a case where the cross-sectional area of the mainstream space 15 is larger than the cross-sectional area of the gas separation space 16, but the relationship in size between these cross-sectional areas is not limited to the configuration shown in Figure 11. The cross-sectional area of the gas separation space 16 may be larger than the cross-sectional area of the mainstream space 15, or the cross-sectional areas of the gas separation space 16 and the mainstream space 15 may be equal.

Figure 12 is a schematic diagram showing an example of the internal configuration of the first header shown in Figure 11. Figure 12 shows the shape and position of the first openings 31, and the positional relationship between the first openings 31 and the heat transfer tubes 11. Figure 12 is a view of the first header 12 viewed from above. As shown in Figure 12, the first openings 31 are arranged alternately with the heat transfer tubes 11. The relationship between the positions of the first openings 31 and the heat transfer tubes 11 is not limited to the configuration shown in Figure 12. Below, modified examples of the positional relationship between the first openings 31 and the heat transfer tubes 11 are described.

(Variation 1)
Fig. 13 is a schematic diagram showing an example of the internal configuration of the first header of Modification 1. As shown in Fig. 13 , the first openings 31 may be arranged to overlap the positions of the heat transfer tubes 11.

(Variation 2)
Fig. 14 is a schematic diagram showing an example of the internal configuration of the first header of Modification 2. As shown in Fig. 14 , the number of first openings 31 may be less than the number of heat transfer tubes 11. Furthermore, the configuration is not limited to that shown in Fig. 14 , and the number of first openings 31 may be more than the number of heat transfer tubes 11.

(Variation 3)
Fig. 15 is a schematic diagram showing an example of the internal configuration of the first header of Modification 3. As shown in Fig. 15, the positions of the multiple first openings 31 may be biased to one side of the first header 12. In the configuration example shown in Fig. 15, the multiple first openings 31 are located in the opposite direction of the X-axis arrow from the halfway position of the first header 12 on the X-axis.

(Variation 4)
Fig. 16 is a schematic diagram showing an example of the internal configuration of the first header of Modification 4. As shown in Fig. 16 , the first openings 31 may have a flat shape that is longer in the X-axis direction than the spacing between the heat transfer tubes 11.

Note that Figures 12 to 16 illustrate examples in which the shape of the first opening 31 is circular and flat, but the shape of the first opening 31 is not limited to the shapes shown in Figures 12 to 16. The shape of the first opening 31 may be rectangular or polygonal, or may be a shape formed by a closed curve.

Here, we will explain the case where the heat source side heat exchanger 1 shown in Figure 9 is applied to the configuration shown in Figures 3 to 5. First, we will explain the case where the heat source side heat exchanger 1 shown in Figure 9 is applied to the configuration shown in Figure 3. In this case, the first heat exchanger 35a and the second heat exchanger 35b shown in Figure 3 each have a configuration similar to the heat source side heat exchanger 1 shown in Figure 9.

Next, we will explain the case where the heat source-side heat exchanger 1 shown in Figure 9 is applied to the configuration shown in Figure 4. In this case, for example, the first row heat exchanger 131a and the second row heat exchanger 132a shown in Figure 4 each have a configuration similar to the heat source-side heat exchanger 1 shown in Figure 9. The first header 12 of the first row heat exchanger 131a and the first header 12 of the second row heat exchanger 132a are connected via a connecting pipe 27. This connecting pipe 27 is referred to as the first connecting pipe. Furthermore, multiple second headers are connected via connecting pipes. The second header 13 of the first row heat exchanger 131a and the second header 13 of the second row heat exchanger 132a are connected via a connecting pipe 27. This connecting pipe 27 is referred to as the second connecting pipe. Each of the two first headers 12 connected via the first connecting pipe has a main flow space 15 and a gas separation space 16.

With reference to Figure 4, we have described a configuration in which two headers are connected via a connecting pipe 27, but the heat source side heat exchanger 1 shown in Figure 9 may be bent like the first heat exchanger 36a shown in Figure 4 without providing the connecting pipe 27a. Even with this configuration, multiple heat exchangers are arranged at intervals in the direction of air flow. In this case, the first header 12 of the upwind heat exchanger and the first header 12 of the downwind heat exchanger share the gas separation space 16.

Next, we will explain the case where the heat source side heat exchanger 1 shown in Figure 9 is applied to the configuration shown in Figure 5. In this case, for example, the first row heat exchanger 131a and the second row heat exchanger 132a shown in Figure 5 each have a configuration similar to the heat source side heat exchanger 1 shown in Figure 9. Note that when the heat source side heat exchanger 1 shown in Figure 9 is applied to the configurations shown in Figures 6 to 8, the configuration is the same as when it is applied to the configurations shown in Figures 3 to 5, so a detailed description thereof will be omitted.

The heat source-side heat exchanger 1 of this embodiment 1 includes a plurality of heat transfer tubes 11, each extending vertically and spaced apart in a horizontal direction perpendicular to the vertical direction, a first header 12 connected to each of the heat transfer tubes 11 at their ends opposite the vertical direction, a second header 13 connected to each of the heat transfer tubes 11 at their ends in the vertical direction, and a gas separation pipe 9. The gas separation pipe 9 connects the first header 12 to a refrigerant pipe 6 through which refrigerant flows out of the second header 13 when the heat source-side heat exchanger 1 operates as an evaporator. The first header 12 has a partition wall 17 that separates the interior of the first header 12 into a plurality of spaces, including a mainstream space 15 and a gas separation space 16. The partition wall 17 has a plurality of first openings 31 that connect the mainstream space 15 and the gas separation space 16. The gas separation space 16 is disposed above the main flow space 15. The gas separation space 16 and the refrigerant pipe 6 through which the refrigerant flows out from the second header 13 are connected by a gas separation pipe 9.

According to the first embodiment, the first header 12 of the heat source-side heat exchanger 1 is provided with a gas separation space 16 that separates gas refrigerant from two-phase gas-liquid refrigerant. Of the two-phase gas-liquid refrigerant that flows into the first header 12, the gas refrigerant is separated from the mainstream space 15 to the gas separation space 16, reducing the proportion of gas refrigerant in the mainstream space 15. As a result, the proportion of liquid refrigerant in the two-phase gas-liquid refrigerant in the mainstream space 15 increases, allowing for more uniform refrigerant distribution from the mainstream space 15 to the multiple heat transfer tubes 11. As a result, the refrigerant distribution characteristics are improved without the need for a new refrigerant auxiliary device, thereby improving the heat exchange performance of the heat exchanger. In the first embodiment, the refrigerant distribution characteristics can be improved by providing a mechanism for controlling the dryness of the two-phase gas-liquid refrigerant in a horizontally extending header-type refrigerant distributor, as described above.

In addition, the flow rate of gas refrigerant flowing through the multiple heat transfer tubes 11 and the second header 13 can be reduced. This reduces refrigerant pressure loss that occurs inside the multiple heat transfer tubes 11 and the second header 13, improving heat exchanger performance. In particular, when the air conditioning unit 10 is operated under operating conditions with a high proportion of gas refrigerant, this prevents deterioration of refrigerant distribution to the multiple heat transfer tubes 11 and reduces refrigerant pressure loss.

Embodiment 2.
In the second embodiment, the internal configuration of the first header 12 is different from that described in the first embodiment. In the second embodiment, the same components as those described in the first embodiment or components corresponding to those described in the first embodiment are denoted by the same reference numerals, and detailed description thereof will be omitted.

The configuration of the heat exchanger of embodiment 2 will now be described. Figure 17 is a cross-sectional schematic diagram showing an example of the internal configuration of the first header of the heat source side heat exchanger according to embodiment 2. Figure 17 shows the structure of the A-A line portion shown in Figure 9, but for ease of explanation, the figure shows the heat transfer tube 11 that is positioned in the X-axis direction shown in Figure 9 rather than the A-A line portion. The arrow Drf shown in Figure 17 indicates the direction in which the refrigerant flows.

In this second embodiment, the first header 12 has a configuration in which the internal space of the first header 12 is separated by a partition wall 17 into a gas separation space 16, a mainstream space 15, and an ejection space 18. The partition wall 17 has a plurality of first openings 31 and a plurality of second openings 32 formed therein. The plurality of first openings 31 connect the mainstream space 15 and the gas separation space 16. The plurality of second openings 32 connect the mainstream space 15 and the ejection space 18.

It is desirable that each of the multiple second openings 32 is not located in the direction of the Z-axis arrow of the heat transfer tube 11. In other words, each of the multiple second openings 32 is located at a position that does not overlap with a plane obtained by projecting the flow path cross section of the heat transfer tube 11 in the opposite vertical direction (the direction of the Z-axis arrow). This is to prevent the refrigerant ejected from the mainstream space 15 into the ejection space 18 through the second openings 32 from flowing directly into the heat transfer tube 11. It is also desirable that each of the multiple second openings 32 is located at the boundary of the liquid surface of the liquid-phase refrigerant flowing through the mainstream space 15. This is to prevent the proportion of gas refrigerant flowing into the ejection space 18 from becoming too high.

Note that while Figure 17 shows a configuration in which two main flow spaces 15 are provided in the first header 12, the number of main flow spaces 15 is not limited to two. The number of main flow spaces 15 may be one, or three or more. Also, while Figure 17 shows a configuration in which each of the two second openings 32 is formed to face inward, they may be formed to face in the direction of the Y-axis arrow or the direction opposite to the Y-axis arrow.

In the heat source side heat exchanger 1 of this embodiment 2, the refrigerant flow rate ejected from the main flow space 15 to the ejection space 18 can be made uniform. As a result, the amount of refrigerant distributed to the multiple heat transfer tubes 11 can be made more uniform. This can further improve heat exchanger performance. In addition, the amount of gas refrigerant flowing through the multiple heat transfer tubes 11 and the second header 13 can be reduced. As a result, the refrigerant pressure loss occurring within the multiple heat transfer tubes 11 and the second header 13 can be reduced, and heat exchanger performance can be improved.

Embodiment 3.
In the third embodiment, the first header 12 and the second header 13 each have the functions of a distribution header and a merging header. In the third embodiment, the same components as those described in the first embodiment or components corresponding to those described in the first embodiment are denoted by the same reference numerals, and detailed descriptions thereof will be omitted.

The configuration of the heat exchanger of embodiment 3 will be described. Figure 18 is a side view for explaining the configuration of the heat source side heat exchanger of embodiment 3. The arrow Drf shown in Figure 18 indicates the direction in which the refrigerant flows.

The heat source side heat exchanger 1a has a first header 12a, a second header 13a, and a plurality of heat transfer tubes 11. The first header 12a has an upper confluence header 41a and an upper distribution header 42a. When the heat source side heat exchanger 1a operates as an evaporator, the upper confluence header 41a confluences refrigerant flowing through some of the plurality of heat transfer tubes 11. The upper distribution header 42a distributes the refrigerant that has confluenced into the upper confluence header 41a to the remaining heat transfer tubes 11 of the plurality of heat transfer tubes 11, excluding some of the heat transfer tubes 11.

The second header 13a has a lower distribution header 44a and a lower confluence header 43a. When the heat source side heat exchanger 1a operates as an evaporator, the lower distribution header 44a distributes the refrigerant flowing in from the inlet 22 to some of the heat transfer tubes 11. The lower confluence header 43a confluences the refrigerant flowing through the remaining heat transfer tubes 11 from the upper distribution header 42a. In the second header 13a, a partition 24 is provided between the lower distribution header 44a and the lower confluence header 43a. In the first header 12a, the upper confluence header 41a and the upper distribution header 42a share the gas separation space 16.

The flow of refrigerant in the heat source side heat exchanger 1a of this embodiment 3 will be described. The refrigerant flows into the lower distribution header 44a of the second header 13a, evaporates and gasifies, flows through some of the heat transfer tubes 11, and flows into the upper merging header 41a. The gas-liquid two-phase refrigerant that flows into the upper merging header 41a flows into the adjacent upper distribution header 42a. Because the upper merging header 41a and the upper distribution header 42a share a common gas separation space 16, the gas refrigerant is separated from the gas-liquid two-phase refrigerant in the shared gas separation space 16.

In the heat source-side heat exchanger 1a of this third embodiment, the gas refrigerant in the gas-liquid two-phase state that flows into the first header 12a is separated from the mainstream space 15 to the gas separation space 16, reducing the proportion of gas refrigerant in the mainstream space 15. This increases the proportion of liquid refrigerant in the gas-liquid two-phase refrigerant in the mainstream space 15, allowing for more uniform refrigerant distribution from the mainstream space 15 to the multiple heat transfer tubes 11. This improves heat exchanger performance. Furthermore, the flow rate of gas refrigerant flowing through the remaining heat transfer tubes 11 and the lower merging header 43a can be reduced. This reduces refrigerant pressure loss in the remaining heat transfer tubes 11 and the lower merging header 43a, improving heat exchanger performance. In particular, the gas refrigerant is separated within the upper merging header 41a, and the flow rate of gas refrigerant is reduced as the refrigerant flows into the upper distribution header 42a adjacent to the upper merging header 41a, further reducing refrigerant pressure loss.

Embodiment 4.
In the fourth embodiment, the first header 12 and the second header 13 each have the functions of a distribution header and a merging header, but have a different configuration from that of the third embodiment. In the fourth embodiment, the same components as those described in the first to third embodiments or components corresponding to those described in the first to third embodiments are denoted by the same reference numerals, and detailed description thereof will be omitted.

The configuration of the heat exchanger of embodiment 4 will be described. Figure 19 is a side view for explaining the configuration of the heat source side heat exchanger according to embodiment 4. The arrow Drf shown in Figure 19 indicates the direction in which the refrigerant flows.

The heat source side heat exchanger 1b has a first header 12b, a second header 13b, and a plurality of heat transfer tubes 11. The first header 12b has an upper confluence header 41b and an upper distribution header 42b. When the heat source side heat exchanger 1b operates as an evaporator, the upper confluence header 41b confluences refrigerant flowing through some of the plurality of heat transfer tubes 11. The upper distribution header 42b distributes the refrigerant that has confluenced into the upper confluence header 41b to the remaining heat transfer tubes 11 of the plurality of heat transfer tubes 11, excluding some of the heat transfer tubes 11.

The second header 13b has a lower distribution header 44b and a lower confluence header 43b. When the heat source side heat exchanger 1b operates as an evaporator, the lower distribution header 44b distributes the refrigerant flowing in from the inlet 22 to some of the heat transfer tubes 11. The lower confluence header 43b confluences the refrigerant flowing through the remaining heat transfer tubes 11 from the upper distribution header 42b. The upper confluence header 41b has a gas separation space 16 and a mainstream space 15, while the upper distribution header 42b only has a mainstream space 15. The flow path cross-sectional area of the mainstream space 15 of the upper distribution header 42b is smaller than the flow path cross-sectional area of the mainstream space 15 of the upper confluence header 41b.

In the heat source side heat exchanger 1b of this fourth embodiment, the refrigerant flow velocity, which is reduced by the separation of gas refrigerant in the upper confluence header 41b, can be increased in the upper distribution header 42b adjacent to the upper confluence header 41b. This prevents deterioration of refrigerant distribution characteristics in the upper distribution header 42b caused by a decrease in flow velocity. Furthermore, the mass of the components constituting the first header 12b can be reduced, improving the cost performance of the heat source side heat exchanger 1b.

Embodiment 5.
In the fifth embodiment, the first header 12 and the second header 13 each have the functions of a distribution header and a merging header, but have a different configuration from those of the third and fourth embodiments. In the fifth embodiment, the same components as those described in the first to fourth embodiments or components corresponding to those described in the first to fourth embodiments are denoted by the same reference numerals, and detailed description thereof will be omitted.

The configuration of the heat exchanger of this embodiment 5 is explained. Figure 20 is a side view for explaining the configuration of the heat source side heat exchanger of embodiment 5. The arrow Drf shown in Figure 20 indicates the direction in which the refrigerant flows.

The heat source side heat exchanger 1c has a first header 12c, a second header 13c, and a plurality of heat transfer tubes 11. The first header 12c has an upper confluence header 41c and an upper distribution header 42c. When the heat source side heat exchanger 1c operates as an evaporator, the upper confluence header 41c confluences refrigerant flowing through some of the heat transfer tubes 11. The upper distribution header 42c distributes the refrigerant that has merged into the upper confluence header 41c to the remaining heat transfer tubes 11, excluding some of the heat transfer tubes 11. In the first header 12c, the upper confluence header 41c and the upper distribution header 42c share the main flow space 15. In the first header 12c, a partition 24 is provided between the refrigerant inlet and the upper confluence header 41c.

The second header 13c has a lower distribution header 44c and a lower confluence header 43c. When the heat source side heat exchanger 1c operates as an evaporator, the lower distribution header 44c distributes the incoming refrigerant to some of the heat transfer tubes 11. The lower confluence header 43c confluences the refrigerant flowing through the remaining heat transfer tubes 11 from the upper distribution header 42c. In the second header 13c, a partition 24 is provided between the lower distribution header 44c and the lower confluence header 43c.

The heat source side heat exchanger 1c has one or more bending regions 110 shown in Figures 3 to 8. In Figure 20, the heat exchange portion consisting of the upper distribution header 42c, the lower merging header 43c, and two or more heat transfer tubes 11 connected to the upper distribution header 42c and the lower merging header 43c is located in the bending region 110. In the heat source side heat exchanger 1c, the upper merging header 41c, which is located upstream of the bending region 110 in the refrigerant flow direction, has a gas separation space 16 and a mainstream space 15.

The flow of refrigerant in the heat source side heat exchanger 1c of this embodiment 5 will be explained. The refrigerant flows from the lower distribution header 44c into the upper merging header 41c, which is located upstream of the bending region 110, and a portion of the gas refrigerant is separated into the gas separation space 16 in the upper merging header 41c. The refrigerant with a high proportion of liquid refrigerant then flows into the upper distribution header 42c, where the bending region 110 is located, and then branches off to two or more heat transfer tubes 11.

Conventionally, when a refrigerant with a high proportion of gas refrigerant flows into the bending region 110, centrifugal force is generated in the refrigerant in the bending region 110, causing uneven refrigerant distribution and degrading heat exchanger performance. In contrast, in the heat source side heat exchanger 1c of this embodiment 5, a refrigerant with a low proportion of gas refrigerant flows into the upper distribution header 42c located in the bending region 110, preventing deterioration of refrigerant distribution to the multiple heat transfer tubes 11. This prevents deterioration of heat exchanger performance due to the bending region 110.

Embodiment 6.
The heat exchanger of the sixth embodiment has a plurality of heat exchangers arranged at intervals in the air flow direction. In the sixth embodiment, the same components as those described in the first to fifth embodiments or components corresponding to those described in the first to fifth embodiments are denoted by the same reference numerals, and detailed description thereof will be omitted.

The configuration of the heat exchanger of this embodiment 6 will be described. Figure 21 is a side view for explaining the configuration of the heat source side heat exchanger according to embodiment 6. Figure 22 is a side view of the heat source side heat exchanger shown in Figure 21 when viewed from a different direction. Arrows Drf shown in Figures 21 and 22 indicate the direction in which the refrigerant flows. Arrows Dar shown in Figure 22 indicate the direction in which air flows.

The heat source side heat exchanger 1d has a heat exchanger consisting of a first header 12-1, multiple heat transfer tubes 11, and a second header 13-1, and a heat exchanger consisting of a first header 12-2, multiple heat transfer tubes 11, and a second header 13-2. These multiple heat exchangers are arranged at intervals in the direction of air flow, as shown in Figure 22.

The heat source side heat exchanger 1d has a connection header 14 to which the first headers 12-1 and 12-2 are connected and integrally formed. The second header 13-1 functions as a distribution header that distributes the refrigerant to the multiple heat transfer tubes 11. The second header 13-2 functions as a confluence header that confluences the refrigerant that has flowed from the connection header 14 through the multiple heat transfer tubes 11. The connection header 14 has a mainstream space 15 and a gas separation space 16.

In the heat source side heat exchanger 1d of this sixth embodiment, the proportion of gas refrigerant in the refrigerant that has become high can be reduced in the connection header 14. This allows for uniform refrigerant distribution to the multiple heat transfer tubes 11 located downstream of the connection header 14, improving heat exchanger performance. Furthermore, the flow rate of gas refrigerant flowing through the second header 13-2 and the multiple heat transfer tubes 11 connected to the second header 13-2 can be reduced. This reduces refrigerant pressure loss that occurs inside the second header 13-2 and the multiple heat transfer tubes 11 connected to the second header 13-2, improving heat exchanger performance.

Embodiment 7.
The seventh embodiment is configured to adjust the flow rate of the gas refrigerant flowing out from the gas separation space 16 of the first header 12. In the seventh embodiment, the same components as those described in the first to sixth embodiments or components corresponding to those described in the first to sixth embodiments are denoted by the same reference numerals, and detailed description thereof will be omitted.

The configuration of the heat exchanger of embodiment 7 will be described. Figure 23 is a refrigerant circuit diagram of an air conditioning system having a heat source side heat exchanger according to embodiment 7. Figure 24 is a side view for explaining the configuration of the heat source side heat exchanger according to embodiment 7. The arrow Drf shown in Figure 24 indicates the direction in which the refrigerant flows.

The heat source side heat exchanger 1e of this embodiment 7 has a gas separation throttle device 21 provided in the gas separation pipe 9. The gas separation throttle device 21 is, for example, a thermal expansion valve. The gas separation throttle device 21 adjusts the flow rate of the refrigerant in the gas phase.

The gas refrigerant separated from the gas-liquid two-phase refrigerant passes through the gas separation throttle device 21 and then flows into the refrigerant pipe 6 at the outlet 23 of the second header 13. The gas separation throttle device 21 adjusts the flow rate of the separated gas refrigerant by its opening degree. For example, when the heat source side heat exchanger 1e operates as a condenser, the gas separation throttle device 21 is closed, but when the heat source side heat exchanger 1e operates as an evaporator, the gas separation throttle device 21 is open. Furthermore, when the proportion of gas refrigerant is high during heating operation of the air conditioning unit 10a, the amount of gas refrigerant separated can be adjusted by increasing the opening degree of the gas separation throttle device 21.

In the heat source side heat exchanger 1e of this embodiment 7, when operating as an evaporator, the flow rate of the separated gas can be adjusted according to the dryness of the refrigerant flowing into the heat source side heat exchanger 1e. This allows for uniform refrigerant distribution over a wider range of operating conditions, further improving heat exchanger performance.

Note that the above-mentioned embodiments 1 to 7 are examples for explaining the heat exchanger and air conditioning device of the present disclosure, and two or more of embodiments 1 to 7 may be combined to solve the problem.

1, 1a to 1e Heat source side heat exchanger, 2 Load side heat exchanger, 3 Compressor, 4 Throttle device, 5 Four-way valve, 6 Refrigerant piping, 7 Heat source side blower, 8 Load side blower, 9 Gas separation piping, 10, 10a Air conditioning device, 11 Heat transfer tube, 12, 12-1, 12-2, 12a to 12c First header, 13, 13-1, 13-2, 13a to 13c Second header, 14 Connection header, 15 Main flow space, 16 Gas separation space, 17 Partition wall, 18 Jet space, 19 Corrugated fin, 20 Refrigerant circuit, 21 Gas separation throttle device, 22 Inlet, 23 Outlet, 24 Partition, 25, 26 Housing, 27, 27a, 27b, 28 Connection piping, 31 First opening, 32 Second openings, 35a-37a First heat exchangers, 35b-37b Second heat exchangers, 41a-41c Upper converging headers, 42a-42c Upper distribution headers, 43a-43c Lower converging headers, 44a-44c Lower distribution headers, 110 Bending regions, 131a, 131b First row heat exchangers, 132a, 132b Second row heat exchangers, Dar, Drf Arrows.

Claims (13)

A heat exchanger that exchanges heat between air and a refrigerant,
a plurality of heat transfer tubes each extending in a vertical direction and arranged at intervals in a horizontal direction perpendicular to the vertical direction;
a first header connected to the plurality of heat transfer tubes at ends of the heat transfer tubes that are opposite in the vertical direction;
a second header connected to the plurality of heat transfer tubes at the vertical end of each of the heat transfer tubes;
a gas separation pipe connecting the first header and a refrigerant pipe through which the refrigerant flowing out of the second header passes when the heat exchanger operates as an evaporator,
the first header has a partition wall that separates the interior of the first header into a plurality of spaces including a main flow space and a gas separation space;
a plurality of first openings are provided in the partition wall, which allow the main flow space and the gas separation space to communicate with each other;
the gas separation space is disposed above the main flow space,
The gas separation space and the refrigerant pipe are connected by the gas separation pipe,
the partition wall separates the interior of the first header into the main flow space, the gas separation space, and an ejection space;
a plurality of second openings are provided in the partition wall, the second openings communicating the main flow space and the ejection space;
each of the plurality of second openings is located at a boundary of a liquid surface of the refrigerant in a liquid phase state flowing through the main space, and is provided at a position not overlapping with a plane obtained by projecting a flow path cross section of the heat transfer tube in a direction opposite to the vertical direction;
heat exchanger. the plurality of first openings are formed at a position higher than a liquid level of the refrigerant in a liquid phase state that flows through the mainstream space when the heat exchanger operates as an evaporator.
The heat exchanger of claim 1 . the first header includes an upper merging header that merges refrigerant flowing through some of the heat transfer tubes when the heat exchanger operates as the evaporator, and an upper distribution header that distributes the refrigerant that has merged into the upper merging header to the remaining heat transfer tubes of the plurality of heat transfer tubes excluding the some of the heat transfer tubes,
the second header includes a lower distribution header that distributes the refrigerant to some of the heat transfer tubes when the heat exchanger operates as the evaporator, and a lower confluence header that confluences the refrigerant flowing from the upper distribution header through the remaining heat transfer tubes,
In the second header, a partition is provided between the lower distribution header and the lower confluence header,
In the first header, the upper confluence header and the upper distribution header share the gas separation space.
3. The heat exchanger according to claim 1 or 2 . the first header includes an upper merging header that merges refrigerant flowing through some of the heat transfer tubes when the heat exchanger operates as the evaporator, and an upper distribution header that distributes the refrigerant that has merged into the upper merging header to the remaining heat transfer tubes of the plurality of heat transfer tubes excluding the some of the heat transfer tubes,
the second header includes a lower distribution header that distributes the refrigerant to some of the heat transfer tubes when the heat exchanger operates as the evaporator, and a lower confluence header that confluences the refrigerant flowing from the upper distribution header through the remaining heat transfer tubes,
the upper confluence header has a plurality of spaces including the gas separation space and the mainstream space,
the upper distribution header has only the main flow space;
a flow path cross-sectional area of the main stream space of the upper distribution header is smaller than a flow path cross-sectional area of the main stream space of the upper confluence header;
3. The heat exchanger according to claim 1 or 2 . a plurality of heat exchangers each including the first header, the plurality of heat transfer tubes, and the second header, the heat exchangers being spaced apart in the air flow direction;
a connection header to which a plurality of the first headers are connected and integrally formed,
Among the plurality of second headers, one of the second headers is a distribution header that distributes the refrigerant to the plurality of heat transfer tubes, and another of the second headers is a confluence header that confluences the refrigerant that has flowed through the plurality of heat transfer tubes from the connection header,
the connection header has a plurality of spaces including the main flow space and the gas separation space;
3. The heat exchanger according to claim 1 or 2 . a plurality of heat exchangers each including the first header, the plurality of heat transfer tubes, and the second header, the heat exchangers being spaced apart in the air flow direction;
a first connection pipe that connects the plurality of first headers together;
a second connection pipe that connects the plurality of second headers to each other,
each of the plurality of first headers has the main flow space and the gas separation space;
3. The heat exchanger according to claim 1 or 2 . each of the heat exchangers includes the first header, the plurality of heat transfer tubes, and the second header, and the heat exchangers are spaced apart in the air flow direction;
The plurality of first headers are configured to share the gas separation space.
3. The heat exchanger according to claim 1 or 2 . a gas separation throttle device that is provided in the gas separation pipe and adjusts the flow rate of the refrigerant in a gas phase state;
3. The heat exchanger according to claim 1 or 2 . A heat exchanger that exchanges heat between air and a refrigerant,
a plurality of heat transfer tubes each extending in a vertical direction and arranged at intervals in a horizontal direction perpendicular to the vertical direction;
a first header connected to the plurality of heat transfer tubes at ends of the heat transfer tubes that are opposite in the vertical direction;
a second header connected to the plurality of heat transfer tubes at the vertical end of each of the heat transfer tubes;
a gas separation pipe connecting the first header and a refrigerant pipe through which the refrigerant flowing out of the second header passes when the heat exchanger operates as an evaporator,
the first header has a partition wall that separates the interior of the first header into a plurality of spaces including a main flow space and a gas separation space;
a plurality of first openings are provided in the partition wall, which allow the main flow space and the gas separation space to communicate with each other;
the gas separation space is disposed above the main flow space,
The gas separation space and the refrigerant pipe are connected by the gas separation pipe,
the first header includes an upper merging header that merges refrigerant flowing through some of the heat transfer tubes when the heat exchanger operates as the evaporator, and an upper distribution header that distributes the refrigerant that has merged into the upper merging header to the remaining heat transfer tubes of the plurality of heat transfer tubes excluding the some of the heat transfer tubes,
the second header includes a lower distribution header that distributes the refrigerant to some of the heat transfer tubes when the heat exchanger operates as the evaporator, and a lower confluence header that confluences the refrigerant flowing from the upper distribution header through the remaining heat transfer tubes,
In the second header, a partition is provided between the lower distribution header and the lower confluence header,
In the first header, the upper confluence header and the upper distribution header share the gas separation space.
heat exchanger. A heat exchanger that exchanges heat between air and a refrigerant,
a plurality of heat transfer tubes each extending in a vertical direction and arranged at intervals in a horizontal direction perpendicular to the vertical direction;
a first header connected to the plurality of heat transfer tubes at ends of the heat transfer tubes that are opposite in the vertical direction;
a second header connected to the plurality of heat transfer tubes at the vertical end of each of the heat transfer tubes;
a gas separation pipe connecting the first header and a refrigerant pipe through which the refrigerant flowing out of the second header passes when the heat exchanger operates as an evaporator,
the first header has a partition wall that separates the interior of the first header into a plurality of spaces including a main flow space and a gas separation space;
a plurality of first openings are provided in the partition wall, which allow the main flow space and the gas separation space to communicate with each other;
the gas separation space is disposed above the main flow space,
The gas separation space and the refrigerant pipe are connected by the gas separation pipe,
the first header includes an upper merging header that merges refrigerant flowing through some of the heat transfer tubes when the heat exchanger operates as the evaporator, and an upper distribution header that distributes the refrigerant that has merged into the upper merging header to the remaining heat transfer tubes of the plurality of heat transfer tubes excluding the some of the heat transfer tubes,
the second header includes a lower distribution header that distributes the refrigerant to some of the heat transfer tubes when the heat exchanger operates as the evaporator, and a lower confluence header that confluences the refrigerant flowing from the upper distribution header through the remaining heat transfer tubes,
the upper confluence header has a plurality of spaces including the gas separation space and the mainstream space,
the upper distribution header has only the main flow space;
a flow path cross-sectional area of the main stream space of the upper distribution header is smaller than a flow path cross-sectional area of the main stream space of the upper confluence header;
heat exchanger. A heat exchanger that exchanges heat between air and a refrigerant,
a plurality of heat transfer tubes each extending in a vertical direction and arranged at intervals in a horizontal direction perpendicular to the vertical direction;
a first header connected to the plurality of heat transfer tubes at ends of the heat transfer tubes that are opposite in the vertical direction;
a second header connected to the plurality of heat transfer tubes at the vertical end of each of the heat transfer tubes;
a gas separation pipe connecting the first header and a refrigerant pipe through which the refrigerant flowing out of the second header passes when the heat exchanger operates as an evaporator;
a throttle device for gas separation that is provided in the gas separation pipe and adjusts the flow rate of the refrigerant in a gas phase state,
the first header has a partition wall that separates the interior of the first header into a plurality of spaces including a main flow space and a gas separation space;
a plurality of first openings are provided in the partition wall, which allow the main flow space and the gas separation space to communicate with each other;
the gas separation space is disposed above the main flow space,
The gas separation space and the refrigerant pipe are connected by the gas separation pipe.
heat exchanger. The heat exchanger according to claim 1 or 2 ;
a blower for supplying the air to the heat exchanger;
a housing that houses the heat exchanger and the blower;
An air conditioning device having the above. a heat exchanger for exchanging heat between the air and the refrigerant;
a blower that supplies the air to the heat exchanger;
a housing that houses the heat exchanger and the blower,
The heat exchanger comprises:
a plurality of heat transfer tubes each extending in a vertical direction and arranged at intervals in a horizontal direction perpendicular to the vertical direction;
a first header connected to the plurality of heat transfer tubes at ends of the heat transfer tubes that are opposite in the vertical direction;
a second header connected to the plurality of heat transfer tubes at the vertical end of each of the heat transfer tubes;
a gas separation pipe connecting the first header and a refrigerant pipe through which the refrigerant flowing out of the second header passes when the heat exchanger operates as an evaporator;
a bending region that is bent along a corner where two side surfaces of the housing meet when viewed in the vertical direction ,
the first header has a partition wall that separates the interior of the first header into a plurality of spaces including a main flow space and a gas separation space;
a plurality of first openings are provided in the partition wall, which allow the main flow space and the gas separation space to communicate with each other;
the gas separation space is disposed above the main flow space,
The gas separation space and the refrigerant pipe are connected by the gas separation pipe,
the gas separation space is formed upstream of the bent region in the flow direction of the refrigerant when the heat exchanger operates as the evaporator.
Air conditioning equipment.