JP6419882B2 - Air conditioner - Google Patents

Description

  The present invention relates to an air conditioner, and more particularly, to an air conditioner that can equalize the amount of liquid refrigerant supplied to each heat transfer tube of a parallel flow heat exchanger.

  As a prior art of a parallel flow type heat exchanger used for an outdoor unit of an air conditioner, there is one described in Patent Document 1. In this patent, as disclosed in the abstract and FIGS. 1 and 2, etc., a pair of header pipes (hereinafter also referred to as “headers”) and a plurality of parallel flat shapes connected to both header pipes. Heat exchange tubes (hereinafter also referred to as “heat transfer tubes”), and parallel flow type heat exchange comprising upper and lower heat exchange regions that are vertically partitioned by a partition plate that partitions the space in the header pipe vertically A partition wall that divides the inside of the header pipe into a heat exchange tube side and an outer space, the partition wall having a refrigerant circulation hole that opens downward from a lowermost heat exchange tube in the upper heat exchange region, and a header Parallel flow type heat exchange provided with a plurality of refrigerant flow holes which are provided at appropriate intervals along the longitudinal direction of the pipe and which increase the opening area on the upper side of the upper heat exchange region. Vessel has been proposed.

Japanese Patent Laid-Open No. 2006-176615

  When using a heat exchanger as an evaporator, in order to improve the heat exchange efficiency, it is necessary to supply a substantially equal amount of liquid refrigerant to each of the plurality of heat transfer tubes. However, in a parallel flow heat exchanger in which a plurality of heat transfer tubes are connected to different heights of the inflow side header and the refrigerant is distributed to each heat transfer tube, the liquid refrigerant in the header stays in the lower part of the header due to gravity. Therefore, a large amount of gas refrigerant flows into the heat transfer tube connected to the upper portion of the header, and only a small amount of liquid refrigerant flows. As a result, liquid refrigerant evaporation in the upper heat transfer tube remains in a small amount, and heat exchange is not sufficiently performed. On the contrary, a large amount of liquid refrigerant staying at the lower part of the header flows into the heat transfer tube connected to the lower part of the header. As a result, the gas-liquid two-phase refrigerant flows out from the lower heat transfer tube before all of the liquid refrigerant evaporates.

  In other words, the dryness defined by the mass flow rate ratio of the gas refrigerant to the total mass flow rate of the liquid refrigerant and the gas refrigerant, among the heat transfer tubes arranged in layers, the upper heat transfer tube has a high dryness, This means that the lower heat transfer tube has a low dryness. And when the dryness for every heat exchanger tube varies, the problem that the heat exchange efficiency of the whole heat exchanger will fall will generate | occur | produce. In addition to this, if the liquid refrigerant in the gas-liquid two-phase refrigerant flowing out of the heat exchanger through the lower heat transfer tube flows into the compressor downstream of the heat exchanger, the compressor may be broken. .

  With respect to these problems, Patent Document 1 suppresses the unevenness of the dryness of each heat transfer tube by the configuration described in the background art section. However, with only a single opening provided at different heights of the partition walls partitioning the header pipe, the high-speed refrigerant flowing from the outer space into the heat exchange tube side space is not sufficiently diffused and decelerated. Therefore, a large amount of liquid refrigerant that could not flow into the heat exchange tube falls due to gravity and stays in the lower part of the header. As a result, the problem that the degree of dryness does not vary depending on the connection height of the heat transfer tubes has not been sufficiently solved.

  Therefore, in the present invention, the refrigerant sufficiently diffused and decelerated in the header of the parallel flow type heat exchanger is supplied to each heat transfer tube having a different connection height, thereby suppressing variation in dryness of each heat transfer tube. It aims at providing the air conditioner which improved the heat exchange efficiency.

In order to solve the above problems, an air conditioner of the present invention includes an outdoor heat exchanger, an indoor heat exchanger, a compressor, and an expansion valve, and any one of the heat exchangers has a cylindrical inflow side. A header, a tubular outflow side header, a plurality of heat transfer tubes connecting the two headers, and a fin that expands a heat transfer area of the heat transfer tubes, and each of the plurality of heat transfer tubes has a cross section Is a flat shape, and the heat transfer tubes are connected to both the headers in a state inclined from the horizontal, and the inside of the cylindrical inflow side header arranged vertically is divided by a partition plate arranged vertically, The first space for distributing the refrigerant to the plurality of heat transfer tubes and the second space for sending the refrigerant supplied from below to the first space are partitioned from the horizontal center. A first communication portion that is closer to one end side, and a second communication portion that is closer to the other end side than the center in the horizontal direction; Is provided in pairs across the horizontal center, said second communicating portion and the first communicating portion, and arranged at different heights in accordance with the inclination of the heat transfer tube.

  According to the air conditioner of the present invention, the refrigerant, which has been sufficiently diffused and decelerated in the header of the parallel flow heat exchanger, is supplied to each heat transfer tube, thereby suppressing the variation in the dryness of each heat transfer tube. An air conditioner with improved exchange efficiency can be provided.

  Other problems, configurations, operations, and effects of the present invention will be described in detail in the following examples.

The perspective view which shows the external appearance of a general heat exchanger. Sectional drawing of a general inflow side header and a heat exchanger tube. Sectional drawing of the inflow side header and heat exchanger tube of Example 1. FIG. Sectional drawing which looked at the partition plate and refrigerant | coolant flow field of Example 1 from upper direction. Sectional drawing which looked at the partition plate of Example 1 from the 2nd space side. Sectional drawing which looked at the partition plate of Example 2 from the 2nd space side. Sectional drawing which looked at the partition plate of Example 3 from the 2nd space side. Sectional drawing which looked at the partition plate of the modification of Example 3 from the 2nd space side. Sectional drawing which looked at the partition plate of Example 4 from the 2nd space side. Sectional drawing which looked at the partition plate of the modification of Example 4 from the 2nd space side. Sectional drawing which looked at the partition plate of the other modification of Example 4 from the 2nd space side. Sectional drawing which looked at the partition plate of Example 5 and the flow field of a refrigerant | coolant from upper direction. Sectional drawing which looked at the partition plate of Example 6 and the flow field of a refrigerant | coolant from upper direction. Sectional drawing which looked at the partition plate of Example 7 from the 2nd space side. Sectional drawing which looked at the partition plate of the modification of Example 7 from the 2nd space side. Schematic of a general air conditioner.

  First, the structure of a general air conditioner and a heat exchanger will be described using the schematic diagram of the air conditioner shown in FIG. 16 and the schematic diagram of the heat exchanger shown in FIGS. 1 and 2.

  FIG. 16 is a configuration diagram of a refrigeration cycle of the conventional air conditioner 100. In the air conditioner 100, an outdoor unit 101 and an indoor unit 108 are connected by connecting pipes 112a and 112b. The outdoor unit 101 includes a compressor 102, a four-way valve 103, an outdoor heat exchanger 104, an outdoor fan motor 105, an outdoor fan 106, and a throttle device 107, and the indoor unit 108 includes an indoor heat exchanger 109, The indoor fan motor 110 and the indoor fan 111 are provided.

  Next, the operation of each element of the air conditioner 100 will be described by taking the operation during the cooling operation as an example. During the cooling operation, the refrigerant flows in the direction of the solid line arrow in the figure. First, the high-temperature and high-pressure gas refrigerant discharged from the compressor 102 flows to the outdoor heat exchanger 104 after passing through the four-way valve 103, condenses by releasing heat to the outside air in the outdoor heat exchanger 104, It becomes a liquid refrigerant. The liquid refrigerant is depressurized by the action of the expansion device 107, becomes a low-temperature low-pressure gas-liquid two-phase state, and flows to the indoor unit 108 through the connection pipe 112a. The gas-liquid two-phase refrigerant that has entered the indoor unit 108 evaporates by absorbing the heat of the indoor air in the indoor heat exchanger 109, thereby realizing indoor cooling. The gas refrigerant evaporated in the indoor unit 108 returns to the outdoor unit 101 through the connection pipe 112b, and is compressed by the compressor 102 again through the four-way valve 103. This is the refrigeration cycle during the cooling operation.

  On the other hand, during the heating operation, the refrigerant flow path is switched by the four-way valve 103, and the refrigerant flows in the direction of the broken line arrow in the figure. First, the high-temperature and high-pressure gas refrigerant discharged from the compressor 102 flows to the indoor unit 108 through the four-way valve 103 and the connection pipe 112b. The high-temperature gas refrigerant that has entered the indoor unit 108 is radiated to the indoor air by the indoor heat exchanger 109, thereby realizing indoor heating. At this time, the gas refrigerant condenses and becomes a high-pressure liquid refrigerant. Thereafter, the high-pressure liquid refrigerant flows to the outdoor unit 101 through the connection pipe 112a. The high-pressure liquid refrigerant that has entered the outdoor unit 101 is depressurized by the action of the expansion device 107, becomes a low-temperature low-pressure gas-liquid two-phase state, flows to the outdoor heat exchanger 104, and evaporates by absorbing the heat of the outdoor air. It becomes a gas refrigerant. The gas refrigerant passes through the four-way valve 103 and is compressed again by the compressor 102. This is the refrigeration cycle during heating operation.

  Thus, the direction of the refrigerant flow in the outdoor heat exchanger 104 and the indoor heat exchanger 109 is opposite between the cooling operation and the heating operation. In addition, although R32 is used as a refrigerant | coolant, you may use another refrigerant | coolants, such as R410A.

  FIG. 1 is a perspective view showing an external appearance when a general parallel flow heat exchanger is used as an evaporator. The heat exchanger shown here connects two headers 1 consisting of an inflow header on the left side in the figure for distributing the refrigerant and an outflow side header on the right side in the figure for merging the refrigerant, and the header 1. A plurality of flat heat transfer tubes 2 through which the refrigerant flows and a plurality of fins 3 brazed to the heat transfer tubes 2 to expand the heat transfer area. As shown in FIG. 1, the refrigerant flow direction and the air flow direction are orthogonal, and the refrigerant flowing in the heat transfer tube 2 and the air flowing between the heat transfer tubes 2 exchange heat through the fins 3. Thus, efficient heat exchange is realized.

  FIG. 2 is a cross-sectional view of the header 1 and the heat transfer tube 2 on the inflow side of FIG. As shown here, a plurality of heat transfer tubes 2 are stacked and inserted and connected to the header 1 at predetermined intervals in the height direction.

  When the heat exchanger is used as a condenser, the flow of the refrigerant is in the direction opposite to the arrow in FIG. 2, and the liquid refrigerant flowing into the header 1 from the heat transfer tube 2 stays in the lower part of the header 1 due to gravity. In order to discharge the liquid refrigerant from the header 1, the refrigerant inlet / outlet 4 is disposed at the lower part of the header 1.

  On the other hand, when the heat exchanger is used as an evaporator, the refrigerant flows into the header 1 from the refrigerant inlet / outlet 4 at the lower part of the header 1 and is distributed to the heat transfer tubes 2 as shown by arrows in FIG. The Since the gas-liquid two-phase refrigerant in which the gas refrigerant and the liquid refrigerant are mixed is supplied to the evaporator, the liquid refrigerant stays at the lower part of the header 1 due to the influence of gravity, and the gas refrigerant is at the upper part of the header 1. Since it rises, the gas refrigerant and the liquid refrigerant are naturally separated vertically in the header 1. As a result, a large amount of gas refrigerant flows through the heat transfer tube 2 connected to the upper portion of the header 1, and a large amount of liquid refrigerant flows through the heat transfer tube 2 connected to the lower portion of the header 1. If this situation is expressed using the dryness described above, the heat transfer tube 2 connected to the upper portion of the header 1 has a high dryness, and the heat transfer tube 2 connected to the lower portion of the header 1 has a low dryness.

  Since the evaporator exchanges heat by using the evaporation heat of the liquid refrigerant, the heat exchange efficiency is lowered in the heat transfer tube 2 in which the supply amount of the liquid refrigerant is too small. On the other hand, in the heat transfer tube 2 having too much liquid refrigerant, the refrigerant flows out before the liquid refrigerant evaporates, which may cause destruction of the compressor 102 downstream. That is, it is possible to suppress variation in the dryness of the heat transfer tubes 2 having different connection heights, and to realize the same heat exchange in any heat transfer tube, thereby improving the heat exchange efficiency of the evaporator and the air conditioner. This contributes to avoiding failure.

  In the general header 1 shown in FIG. 2, in addition to not having means for suppressing the variation in dryness, the flow direction of the refrigerant flowing in from the refrigerant inlet / outlet 4 (from the bottom to the top in the figure) Direction) and the flow direction in the heat transfer tubes 2 (the direction from the left to the right in the figure) are orthogonal to each other, and it is difficult for the refrigerant to flow into the heat transfer tubes 2. It becomes.

  Below, the Example of this invention is described as a structure which solves this problem.

  First, the air conditioner of Example 1 is demonstrated using FIGS. 3-5. In addition, description is abbreviate | omitted about the point which is common in the general air conditioner demonstrated in FIG. 16, FIG. 1, FIG.

  FIG. 3 is a cross-sectional view of the header 1 and the heat transfer tube on the inflow side of the present embodiment. As shown here, in the present embodiment, the inside of the substantially cylindrical header 1 arranged vertically is distributed to the heat transfer tube 2 by the partition plate 10 that is long in the height direction. The space 1a (the right side space of the partition plate 10) and the second space 1b (the left space of the partition plate 10) having a small volume for sending the refrigerant supplied from below to the first space 1a are partitioned. Thus, by partitioning the inside of the header 1 by the partition plate 10, the flow area of the second space 1b in which the refrigerant rises is reduced, and the flow rate of the refrigerant is increased, so that the liquid in the gas-liquid two-phase refrigerant is increased. The refrigerant can be transported to the upper end of the header 1. Further, the partition plate 10 is provided with a plurality of communication holes for moving the refrigerant from the second space 1b to the first space 1a at predetermined intervals in the height direction, and the plurality of heat transfer tubes 2 having different connection heights. The refrigerant can be supplied to the vicinity of each.

  Various methods can be considered as a method of manufacturing the header 1 shown in FIG. 3. For example, a plurality of heat transfer tubes 2 are provided on a substantially cylindrical header 1 in which a heat transfer tube insertion hole and a partition plate insertion hole are opened. The manufacturing method which inserts the partition plate 10 and integrates them by brazing them in a furnace is mentioned.

  Next, the flow field of the refrigerant inside the substantially cylindrical header 1 will be described using the cross-sectional view of FIG. 4 is a cross-sectional view taken along the AA plane of FIG. 3 including the communication portion. As shown here, the partition plate 10 is closer to one end side so as to sandwich the center in the horizontal direction (width direction). A first communication part 20 and a second communication part 21 approaching the other end are provided in pairs. The refrigerant 50 that has moved from the narrow second space 1b to the wide first space 1a via these communicating portions is decelerated in the first space 1a as the flow path area increases. Further, the refrigerant 50 that has passed through each communication portion flows along the inner wall surface of the first space 1a, collides at the facing position of the partition plate 10 at the right end in the figure, and changes the flow direction to the partition plate 10 side. While decelerating, it diffuses evenly in the first space 1a.

  FIG. 5 is a cross-sectional view of the partition plate 10 installed in the header 1 as viewed from the second space 1b side. As shown here, by arranging the first communication part 20 and the second communication part 21 in a substantially line symmetrical manner so as to sandwich the center line of the partition plate 10, the wall surface of the header 1 described in FIG. Along the flow.

  Moreover, since the 1st communication part 20 and the 2nd communication part 21 are provided between the connection height of the heat exchanger tube 2 immediately above and the connection height of the heat transfer pipe 2 directly below, the comparison which flowed out the communication part The high-speed refrigerant does not flow into the heat transfer tube 2 as it is, and is sufficiently decelerated and diffused by the long path shown in part in FIG. 4, that is, at any height in the first space 1a. In addition, after becoming a substantially homogeneous gas-liquid two-phase refrigerant, the refrigerant flows into the heat transfer tube 2. In FIG. 5, the first series communication portion 20 and the second communication portion 21 are arranged approximately in the middle of the upper and lower heat transfer tubes 2, but depending on the dryness and flow rate of the refrigerant flowing into the header 1, The first communication part 20 and the second communication part 21 may be arranged so as to be biased toward the heat transfer tube 2 side.

  As described above, in the air conditioner of this embodiment, the inside of the header 1 of the evaporator is divided into a narrow space where the refrigerant is raised at a high speed and a wide space where the refrigerant is decelerated and then distributed to the heat transfer tubes 2. By partitioning and providing a pair of communicating portions at different heights of the partition plate 10 that partitions both spaces, the gas-liquid two-phase refrigerant accelerated in the second space 1b is sufficiently decelerated and diffused in the first space 1a. Since the gas-liquid two-phase refrigerant that has become low-speed and substantially homogeneous can be supplied to each of the plurality of heat transfer tubes 2 in an appropriate amount, variation in the dryness of each heat transfer tube 2 is suppressed, Heat exchange efficiency can be improved.

  In this embodiment, the partition plate 10 is a rectangular flat plate. However, the first space 1a and the second space 1b are formed, and the first communication portion 20 and the second communication portion 21 through which the refrigerant passes are provided. If possible, the partition plate 10 may be composed of a member whose thickness is partially changed or a member composed of a curved surface, a plurality of members combined, or a partition plate integrally molded with the header 1 It may be 10.

  Further, in this embodiment, as shown in FIG. 3, the partition plate 10 is arranged vertically (parallel to the direction of gravity). However, when the refrigerant flow rate and the dryness of each heat transfer tube 2 are to be changed intentionally, Depending on the refrigerant flow rate, the partition plate 10 may be tilted from the vertical position. 4 and 5, the first communication part 20 and the second communication part 21 are arranged in line symmetry. However, if the refrigerant flow field illustrated in FIG. 4 can be formed, a pair of communication parts is provided. It is not always necessary to provide the line target. In FIG. 3, a pair of two-hole communication portions including the first communication portion 20 and the second communication portion 21 are shown, but three or more communication portions may be provided at the same height. Furthermore, although the shape of the heat transfer tube 2 is flat in FIG. 5, it may be a round tube or a flat multi-hole tube.

  Next, the air conditioner of Example 2 is demonstrated using FIG. In addition, duplication description is abbreviate | omitted about the point which is common in Example 1. FIG.

  FIG. 6 is a cross-sectional view of the partition plate 10 according to the second embodiment when viewed from the second space 1b side, and the first series communication portion 20 and the second communication portion 21 are disposed at the end of the partition plate 10 in the horizontal direction. In addition, the heat transfer tube 2 is disposed outside the width. By arranging the first communication part 20 and the second communication part 21 in this way, the refrigerant flowing into the first space 1a from the second space 1b is further more than the refrigerant flow field shown in FIG. Since it flows in a state along the wall surface, the loss at the first communication part 20 and the second communication part 21 can be further reduced. Moreover, when it is set as the manufacturing method which fixes the partition plate 10 to the header 1 by brazing, since a brazing area can be reduced, it becomes possible to manufacture a heat exchanger more easily.

  In addition, you may use the structure demonstrated here in combination with Example 1, For example, it is also possible to arrange | position only the 1st communicating part 20 in the edge part in the horizontal direction of the partition plate 10. For example, as shown in FIG.

  Next, the air conditioner of Example 3 will be described with reference to FIG. In addition, the description which overlaps with the above-mentioned Example is abbreviate | omitted.

  FIG. 7 is a cross-sectional view of the partition plate 10 according to the third embodiment as viewed from the second space 1b side. In order to obtain the effect of the present invention, as shown in FIG. 4, a pair of refrigerant flow fields that flow along the inner surface of the first space 1 a may be generated. There is no need to provide a separate communication part. Therefore, in the present embodiment, a laterally long hole 22 as shown in FIG. 7 is provided as the communicating portion, and the refrigerant flow field shown in FIG. 4 can be formed by the refrigerant flowing out from both ends thereof.

  In FIG. 7, the shape of the horizontally long hole 22 is a rectangle, but it may be an ellipse. Further, the dimensions of only the portions that become the first communication portion 20 and the second communication portion 21 may be enlarged or reduced more than the width of the laterally long hole 22 in the short direction.

  FIG. 8 is a cross-sectional view of the partition plate 10 according to a modification of the third embodiment when viewed from the second space 1b side. Thus, by expanding the horizontally long hole 22 to the wall surface of the header 1, the same effect as the effect shown in the second embodiment can be obtained.

  Next, the air conditioner of Example 4 is demonstrated using FIG. In addition, the description which overlaps with the above-mentioned Example is abbreviate | omitted.

  FIG. 9 is a cross-sectional view of the partition plate 10 according to the fourth embodiment as viewed from the second space 1b side. In FIG. 9, the refrigerant flowing into the first space 1 a from the second space 1 b in the height direction is formed by making the first communication portion 20 and the second communication portion 21 into a vertically long hole that is long in the height direction of the header 1. To be easily diffused.

  FIG. 10 is a cross-sectional view of the partition plate 10 according to a modification of the fourth embodiment when viewed from the second space 1b side. In FIG. 9, the height of the vertically long holes is made smaller than the interval between the heat transfer tubes 2, but in FIG. 10, the height of the vertically long holes is made larger than the interval between the heat transfer tubes 2. For example, if the height of the vertically long hole is equal to the height of the partition plate 10, when the partition plate 10 is fixed to the header 1 by brazing, the brazed portion is only a surface in contact with the upper and lower wall surfaces of the header 1, and manufacturing is easy. Become.

  FIG. 11 is a cross-sectional view of the partition plate 10 according to another modification of the fourth embodiment when viewed from the second space 1b side. As shown here, it is good also as a communicating part which combined the horizontally long hole 22 of the modification of Example 3, and the vertically long hole of Example 4. FIG. According to this configuration, an evaporator having both the action of the horizontally long hole 22 and the action of the vertically long hole can be obtained.

  Next, the air conditioner of Example 5 is demonstrated using FIG. In addition, the description which overlaps with the above-mentioned Example is abbreviate | omitted.

  FIG. 12 is a cross-sectional view of the partition plate and the refrigerant flow field of Example 5 as viewed from above. As shown here, in this embodiment, compared with FIG. 4 of the first embodiment, the flow area of the second space 1b is further narrowed, and at the same time, the flow area of the first space 1a is further increased. The partition plate 11 is installed to further accelerate the flow rate of the refrigerant 50 flowing through the second space 1b and further decelerate the flow rate of the refrigerant 50 flowing out to the first space 1a.

  In FIG. 12, the flat plate is curved. However, when it is desired to reduce only the flow area of the first space 1a according to the dryness and flow rate of the refrigerant flowing into the header 1, the second space 1b is used. It is also possible to partially increase the thickness of the partition plate 11 so as to reduce only the flow path area.

  Next, the air conditioner of Example 6 will be described with reference to FIG. In addition, the description which overlaps with the above-mentioned Example is abbreviate | omitted.

  FIG. 13: is sectional drawing which looked at the partition plate and refrigerant | coolant flow field of Example 6 from upper direction. As shown here, in the present embodiment, the second space 1b is divided into a space 1c and a space 1d by the partition plate 12 arranged in a substantially L shape. The gas-liquid two-phase refrigerant supplied to the header 1 is separated in advance into a gas refrigerant 51 and a liquid refrigerant 52 at the lower part of the header 1, and the gas refrigerant 51 can be supplied separately to the space 1c and the liquid refrigerant 52 to the space 1d. It is like that. And the gas refrigerant | coolant 51 which passed the 1st communication part 20, and the liquid refrigerant | coolant 52 which passed the 2nd communication part 21 are mixed by desired ratio in the 1st space 1a. At this time, the mixing ratio of the gas refrigerant 51 and the liquid refrigerant 52 can be adjusted by changing the flow path area of the space 1c and the space 1d or the opening area of the first communication part 20 and the second communication part 21, The dryness of the refrigerant in one space 1a can be adjusted.

  In addition, in FIG. 13, although the example which divides | segments the 2nd space 1b into two spaces was shown by comprising the partition plate 12 by two flat plates, according to the number and shape of the space to divide | segment, The plate thickness of 12 may be partially changed, and the partition plate 12 may be formed of a desired curved surface.

  Next, the air conditioner of Example 7 is demonstrated using FIG. In addition, the description which overlaps with the above-mentioned Example is abbreviate | omitted.

  FIG. 14 is a cross-sectional view of the partition plate 10 according to the seventh embodiment when viewed from the second space 1b side. As shown here, in the present embodiment, the flat heat transfer tube 2 is connected to the header 1 while being inclined from the horizontal, and the first communication portion 20 and the second communication portion 21 are connected to each other. By disposing the straight lines so as to be substantially parallel to the inclination of the heat transfer tube 2, the refrigerant flowing out from the connecting portion can easily flow into the heat transfer tubes 2 connected in an inclined manner.

  FIG. 15 is a cross-sectional view of the partition plate 10 according to a modification of the seventh embodiment when viewed from the second space 1b side. As shown here, the communicating portion of the present embodiment is a horizontally long hole 22 that connects the first communicating portion 20 and the second communicating portion 21 of the seventh embodiment, and this horizontally long hole 22 is defined as the inclination of the heat transfer tube 2. By arrange | positioning in parallel, the refrigerant | coolant which flowed out from the connection part becomes easy to flow in into the heat exchanger tube 2 inclinedly connected.

  As shown in FIGS. 14 and 15, it is ideal to arrange the communication portion in parallel with the inclined heat transfer tube 2, but it is not necessarily required to be parallel. Similarly, the present embodiment can be applied even when the heat transfer tube 2 having a flat shape is not inclined or the shape of the heat transfer tube 2 is, for example, a round tube. Moreover, it is also possible to incline the 1st communicating part 20 and the 2nd communicating part 21 according to the shape of the header 1 or the flow field inside the header 1.

  The present invention is not limited to the above-described embodiments, and includes various modifications. For example, the above-described embodiments have been described in detail for easy understanding of the present invention, and are not necessarily limited to those having all the configurations described. Further, a part of the configuration of one embodiment can be replaced with the configuration of another embodiment, and the configuration of another embodiment can be added to the configuration of one embodiment. Moreover, it is possible to add, delete, and replace other configurations with respect to the configuration of each embodiment.

1 header,
1a first space,
1b second space,
1c, 1d space,
2 heat transfer tubes,
3 Fins,
4 Refrigerant entrance / exit,
10, 11, 12 partition plate,
20 First communication part,
21 Second communication part,
22 Horizontal hole,
50 refrigerant,
51 gas refrigerant,
52 liquid refrigerant,
100 air conditioner,
101 outdoor unit,
102 compressor,
103 Four-way valve,
104 outdoor heat exchanger,
105 outdoor fan motor,
106 outdoor fan,
107 aperture device,
108 indoor units,
109 indoor heat exchanger,
110 Indoor fan motor,
111 indoor fans,
112a, 112b Connection piping

Claims (7)

An air conditioner including an outdoor heat exchanger, an indoor heat exchanger, a compressor, and an expansion valve,
Any one of the heat exchangers includes a cylindrical inflow side header, a cylindrical outflow side header, a plurality of heat transfer tubes connecting the two headers, and a fin that expands a heat transfer area of the heat transfer tubes, Have
Each of the plurality of heat transfer tubes has a flat cross section.
While connecting each heat transfer tube to both headers in a state inclined from the horizontal,
The inside of the cylindrical inflow header arranged vertically is
By the partition plates arranged vertically,
A first space for distributing the refrigerant to the plurality of heat transfer tubes;
And is partitioned into a second space that sends the refrigerant supplied from below to the first space,
In the partition plate,
A first series of passages that are closer to one end than the horizontal center;
A second communicating portion that is closer to the other end side than the horizontal center, and is provided in pairs across the horizontal center ;
The air conditioner characterized in that the first communication part and the second communication part are arranged with different heights according to the inclination of the heat transfer tube . In the air conditioner according to claim 1,
The air conditioner characterized in that the first communication part and the second communication part are provided at a horizontal end of the partition plate. In the air conditioner according to claim 1 or 2,
The air conditioner, wherein the partition plate is formed with a laterally long hole connecting the first communication part and the second communication part. In the air conditioner according to claim 1,
The air conditioner, wherein the first communication part and the second communication part are vertically long holes in a height direction of the inflow side header. In the air conditioner according to claim 1,
The air conditioner characterized in that the first communication part and the second communication part are provided at a substantially intermediate height between the upper heat transfer tube and the lower heat transfer tube. In the air conditioner according to claim 1,
The air conditioner, wherein the partition plate has a convex shape that reduces a surface area of the second space on a surface of the second space. In the air conditioner according to claim 1,
The air conditioner characterized in that the second space is divided into a plurality by the surface of the partition plate on the second space side.

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