JPWO2019207799A1 - Air conditioner and heat exchanger - Google Patents

Abstract

The outdoor heat exchanger (4A) includes two headers (13a) arranged substantially vertically, a plurality of heat transfer tubes (14) connecting the headers (13a) substantially horizontally, and the heat transfer tubes (14). It is provided with fins (15) for expanding the heat transfer area of the above. The header (13a) includes an inlet pipe (16a) through which the refrigerant flows into the header (13a), an outlet portion (18a) through which the refrigerant flows out into each of the plurality of heat transfer pipes 14, and an outlet portion from the inlet pipe (16a). It has a refrigerant flow path (18A) through which the refrigerant flows to (18a), and a volume occupying member (17) as a refrigerant flow path narrowing portion that narrows the refrigerant flow path (18A).

Description

The present invention relates to an air conditioner, and more particularly to an air conditioner and a heat exchanger that distribute a refrigerant to each of a plurality of heat transfer tubes connecting the headers of the heat exchanger.

In an air conditioner using a vapor compression refrigeration cycle, a heat exchanger is used for heat exchange between the refrigerant flowing inside the refrigeration cycle and the outdoor air or the indoor air. In such a heat exchanger, both ends of a large number of heat transfer tubes are connected to a cylindrical header, and an expanded heat transfer surface called a fin is fixed to the heat transfer tube between the headers by brazing or the like. The refrigerant flowing inside the heat exchanger flows into the header through the pipe, then branches into each heat transfer tube and flows down, exchanging heat with the air flowing outside, and flows down on the opposite side of the inlet. It merges at the header and flows out from the outlet pipe.

By the way, for example, when the heat exchanger is used as an evaporator, that is, for the purpose of evaporating the internal refrigerant to cool the air flowing outside, the inside of the header on the refrigerant inlet side is in a gas-liquid two-phase state, and gas and liquid Since the density difference is large, it is difficult to evenly distribute the liquid refrigerant having a heat absorbing action to each heat transfer tube. When this bias is large, in a heat transfer tube having a small distribution ratio of the liquid refrigerant, the liquid refrigerant completes evaporation at an early stage, so that much of the inside of the heat transfer tube is filled with a gas refrigerant having almost no endothermic action. It will be. That is, the heat transfer area of the heat exchanger cannot be effectively used, and the energy saving property of the device may be lowered.

As a conventional technique for solving such a problem, for example, there is one shown in FIG. 6 of Patent Document 1. In this example, a part of the internal space of the header is partitioned by a partition wall, and a plurality of through holes are provided in the partition wall to uniformly distribute the refrigerant to each heat transfer tube.

Japanese Patent Publication No. 2014-533819

However, in the one described in Patent Document 1, a part of the internal space of the header has a structure in which the liquid refrigerant tends to stay in the lower part due to the influence of gravity, especially in the low refrigerant flow rate region. There is a possibility that the liquid refrigerant will flow unevenly to the heat transfer tube on the side.

The present invention has been made to solve the above-mentioned conventional problems, and provides an air conditioner and a heat exchanger having excellent energy saving by preventing uneven distribution of the liquid refrigerant in the header in a wide refrigerant flow rate range. The purpose is to provide.

The present invention includes an outdoor unit and an indoor unit, the outdoor unit includes a compressor, a heat exchanger, an outdoor fan, and a throttle device, and the heat exchangers are arranged substantially vertically. The header is provided with two headers, a plurality of heat transfer tubes that connect the headers substantially horizontally, and fins that expand the heat transfer area of the heat transfer tubes. The header is an inlet through which a refrigerant flows into the header. It is characterized by having an outlet through which the refrigerant flows out into each of the plurality of heat transfer tubes, a refrigerant flow path through which the refrigerant flows from the inlet to the outlet, and a refrigerant flow path narrowing portion that narrows the refrigerant flow path. To do.

According to the present invention, it is possible to provide an air conditioner and a heat exchanger having excellent energy saving by preventing uneven distribution of the liquid refrigerant in the header in a wide refrigerant flow rate range.

It is a block diagram which shows the refrigerating cycle of the air conditioner of 1st Embodiment. It is a perspective view which shows the outdoor heat exchanger of the air conditioner of 1st Embodiment. The internal structure of the header of the first embodiment is shown, (a) is a vertical sectional view, and (b) is a sectional view taken along line IIIB-IIIB of (a). The volume occupying member installed in the header of the first embodiment is shown, (a) is a front view, (b) is a side view, and (c) is a plan view. The internal structure of the header of the second embodiment is shown, (a) is a vertical sectional view, and (b) is a VB-VB sectional view of (a). The internal structure of the header of the third embodiment is shown, (a) is a vertical sectional view, and (b) is a VIB-VIB sectional view of (a). A partition member installed in the header of the third embodiment is shown, (a) is a front view, (b) is a side view, and (c) is a plan view. The internal structure of the header of the 4th embodiment is shown, (a) is a vertical sectional view, and (b) is a sectional view of VIIIB-VIIIB of (a). The internal structure of the header of the fifth embodiment is shown, (a) is a vertical sectional view, and (b) is an IXB-IXB sectional view of (a). The internal structure of the header of the sixth embodiment is shown, (a) is a vertical sectional view, and (b) is an XB-XB sectional view of (a). The internal structure of the header of the seventh embodiment is shown, (a) is a vertical sectional view, and (b) is an XIB-XIB sectional view of (a). The shape of the heat transfer tube of the seventh embodiment is shown, (a) is a front view, (b) is a side view, and (c) is a plan view. The internal structure of the header of the eighth embodiment is shown, (a) is a vertical sectional view, and (b) is a sectional view of XIIIB-XIIIB of (a). A partition member installed in the header of the eighth embodiment is shown, (a) is a plan view, (b) is a front view, (c) is a rear view, and (d) is a side view. The internal structure of the header of the ninth embodiment is shown, (a) is a vertical sectional view, and (b) is an XVB-XVB sectional view of (b). The internal structure of the header of the tenth embodiment is shown, (a) is a vertical sectional view, (b) is an XVIB-XVIB sectional view of (a), and (c) is an enlarged view of a joint portion of a heat transfer tube.

Hereinafter, embodiments according to the present invention will be described with reference to the drawings. In addition, about each embodiment, the same reference numerals are given for the same configuration, and duplicate description will be omitted.
(First Embodiment)
FIG. 1 is a configuration diagram showing a refrigeration cycle of the air conditioner of the first embodiment.
As shown in FIG. 1, the air conditioner 100 includes an outdoor unit 1, an indoor unit 8, a connecting pipe 12a, and a connecting pipe 12b.

The outdoor unit 1 includes a compressor 2, a four-way valve 3, an outdoor heat exchanger 4 (4A, 4B, 4C, 4D, 4E, 4F, 4G, 4H, 4I, 4J), an outdoor fan 5, and an outdoor fan. It includes a motor 6 and a throttle device 7. The indoor unit 8 includes an indoor heat exchanger 9, an indoor fan 10, and an indoor fan motor 11.

Next, the operation of each element will be described by taking the case of cooling operation as an example.
In the case of cooling operation, the refrigerant flows in the direction of the solid arrow in the figure. First, the high-temperature, high-pressure gas refrigerant discharged from the compressor 2 flows to the outdoor heat exchanger 4 after passing through the four-way valve 3, and is ventilated by the outdoor fan 5 and the outdoor fan motor 6. By radiating heat to the outside air, it condenses and becomes a high-pressure liquid refrigerant. The high-pressure liquid refrigerant is decompressed by the action of the throttle device 7, becomes a low-temperature low-pressure gas-liquid two-phase refrigerant, and flows to the indoor unit 8 through the connection pipe 12a. The gas-liquid two-phase refrigerant contained in the indoor unit 8 evaporates by absorbing the heat of the indoor air in the indoor heat exchanger 9 ventilated by the indoor fan 10 and the indoor fan motor 11, and becomes a gas refrigerant. The gas refrigerant evaporated in the indoor unit returns to the outdoor unit 1 through the connecting pipe 12b, and is compressed again by the compressor 2 through the four-way valve 3.

In the case of heating operation, the refrigerant flow path is switched by the four-way valve 3, and the refrigerant flows in the direction of the broken line arrow in the figure. The high-temperature, high-pressure gas refrigerant discharged from the compressor 2 flows to the indoor unit 8 through the four-way valve 3 and the connecting pipe 12b. The refrigerant contained in the indoor unit 8 is condensed by being dissipated to the indoor air by the indoor heat exchanger 9 ventilated by the indoor fan 10 and the indoor fan motor 11, and becomes a high-pressure liquid refrigerant. The high-pressure liquid refrigerant flows to the outdoor unit 1 through the connection pipe 12a. The high-pressure liquid refrigerant that has entered the outdoor unit 1 is decompressed by the action of the throttle device 7, and becomes a low-temperature low-pressure gas-liquid two-phase refrigerant. This gas-liquid two-phase refrigerant flows to the outdoor heat exchanger 4 ventilated by the outdoor fan 5 and the outdoor fan motor 6, and evaporates by absorbing the heat of the outdoor air to become a gas refrigerant. The refrigerant that has become gas in the outdoor heat exchanger 4 passes through the four-way valve 3 and is compressed again by the compressor 2.

As described above, the directions of the refrigerant flows in the outdoor heat exchanger 4 and the indoor heat exchanger 9 are opposite in the cooling operation and the heating operation. In this embodiment, R32 is used as the refrigerant, but another Freon-based refrigerant such as R410A or a natural refrigerant such as carbon dioxide, hydrocarbon, or ammonia may be used.

Next, the details of the outdoor heat exchanger 4A (4) will be described with reference to FIGS. 2, 3, and 4. FIG. 2 is a perspective view showing an outdoor heat exchanger of the air conditioner of the first embodiment. 3A and 3B show the internal structure of the header of the first embodiment, where FIG. 3A is a vertical sectional view and FIG. 3B is a sectional view taken along line IIIB-IIIB of FIG. 3A. 4A and 4B show a volume occupying member installed in the header of the first embodiment, FIG. 4A is a front view, FIG. 4B is a side view, and FIG. 4C is a plan view. The thick solid arrow in FIGS. 2 and 3 indicates the flow of the refrigerant during the heating operation in which the outdoor heat exchanger 4A acts as an evaporator, and is from the inlet pipe 16a (inlet) on the drawing device 7 side. It shows how the refrigerant flows toward the connecting pipe 16b on the four-way valve 3 side.

As shown in FIG. 2, the outdoor heat exchanger 4A has two substantially cylindrical headers 13 (13a, 13b) arranged substantially vertically (so that the axial direction is the vertical direction), and these headers 13a, It is composed of a plurality of heat transfer tubes 14 (12 in this embodiment) that connect 13b substantially horizontally, and a large number of fins 15 that expand the heat transfer area of the heat transfer tubes 14.

The heat transfer tube 14 is made of, for example, a flat tube made of an aluminum alloy. The cross section of the flow path of each heat transfer tube 14 is formed in the same shape from one end to the other end of the heat transfer tube 14. Further, the heat transfer tubes 14 are arranged at equal intervals in the vertical direction (vertical direction). Further, each heat transfer tube 14 is arranged so that the longitudinal direction (major axis direction) faces the front-rear direction (ventilation direction).

The fin 15 is formed in a thin plate shape made of, for example, an aluminum alloy. Further, the fins 15 are laminated at intervals in the thickness direction. Further, the fins 15 are formed in a square shape (strip shape) elongated in the vertical direction.

As a method of fixing the heat transfer tube 14 to the fin 15, for example, the heat transfer tube 14 is inserted into the flat hole formed in the fin 15 so as to penetrate the heat transfer tube 14, and the heat transfer tube 14 is expanded and fixed by air pressure, or both are brazed. It can be fixed with.

The refrigerant passing through the inside of the heat transfer tube 14 can exchange heat with the air ventilated by the outdoor fan 5 (see FIG. 1). Further, an inlet pipe 16a into which the refrigerant is introduced is connected to the lower portion of the header 13a in the vertical direction. Further, an outlet pipe 16b from which the refrigerant is led out is provided at the lower portion of the header 13b in the vertical direction.

As shown in FIG. 3A, the header 13a includes a cylindrical cylinder 13s, an upper lid 13t that closes the upper end opening of the cylinder 13s, and a lower lid 13u that closes the lower opening of the cylinder 13s. , And are configured. The tubular body 13s is formed with an insertion hole 13v into which each heat transfer tube 14 is inserted and an insertion hole 13w into which the inlet tube 16a is inserted.

Further, a volume occupying member 17 is provided inside the header 13a. The volume occupying member 17 forms a region in which the refrigerant does not flow, and has a function as a refrigerant flow path narrowing portion (non-refrigerant flow path portion). By providing the volume occupying member 17 in the header 13a, the refrigerant flow path 18A in the header 13a is narrower than in the case where the volume occupying member 17 is not provided.

Further, the volume occupying member 17 is formed with holes 17a corresponding to a plurality of heat transfer tubes 14, and the heat transfer tubes 14 are inserted into the holes 17a. The hole portion 17a is formed at a position overlapping the insertion hole 13v.

The heat transfer tube 14 is configured so as not to protrude inward from the volume occupying member 17. That is, the flat surface portion 17e of the volume occupying member 17 (the wall surface forming the wall of the refrigerant flow path 18A) is configured to be substantially flush with the end surface 14s of the heat transfer tube 14. Further, the end surface 14s of the heat transfer tube 14 constitutes an outlet portion 18a (outlet) of the refrigerant flow path 18A. The end surface 14s of the heat transfer tube 14 may not protrude from the flat surface portion 17e (become a recessed position).

Further, the center height H of the inlet tube 16a is lower than the center height h of the heat transfer tube 14A (14) at the lowest position among the plurality of heat transfer tubes 14 connected to the header 13a. There is. This facilitates an upward flow with respect to the refrigerant.

Further, the volume occupying member 17 is formed so that the cross-sectional area when cut in the horizontal direction is the same from the lower end to the upper end of the header 13a. As a result, the internal space of the header 13a is narrowed by the volume occupying member 17, and has the same flow path cross section from the lower end to the upper end of the header 13a.

As shown in FIG. 3B, the cross section of the volume occupying member 17 is formed in a substantially half-moon shape. In the present embodiment, the volume occupying member 17 is formed in a solid shape, but it may be formed in a hollow shape. By forming the header 13a in a hollow shape, it is possible to suppress an increase in the weight and material cost of the header 13a.

Further, the inlet pipe 16a at the lower end of the header 13a is inserted so as to penetrate through the insertion hole 13w formed in the tubular body 13s. Further, the tip of the inlet pipe 16a projects inward from the inner wall surface 13a1 of the tubular body 13s. Further, the axial direction of the inlet pipe 16a is the same as the axial direction of the heat transfer pipe 14.

As shown in FIGS. 4A and 4B, the volume occupying member 17 is formed with a hole 17a into which the heat transfer tube 14 (see FIG. 2) is inserted. The hole 17a is formed flat so as to follow the flat shape of the heat transfer tube 14 (see FIG. 2). Further, the holes 17a are formed at equal intervals in the vertical direction.

Further, a protrusion 17b is provided on each of the upper end surface 17m and the lower end surface 17n of the volume occupying member 17. The protrusions 17b of the upper end surface 17m and the lower end surface 17n are each formed at two locations, but may be at one location or at three or more locations, and can be changed as appropriate.

The protrusion 17b is for fixing the volume occupying member 17 to the header 13a (see FIG. 3A). That is, by fitting the protrusion 17b with the recesses (not shown) provided in the upper lid 13t (see FIG. 3A) and the lower lid 13u (see FIG. 3A) of the header 13a. The volume occupying member 17 is fixed in the header 13a.

As shown in FIG. 4C, the volume occupying member 17 includes a curved surface portion 17d formed along the inner wall surface 13a1 (see FIG. 3B) of the header 13a (see FIG. 3A) and a refrigerant. It has a flat surface portion 17e constituting one wall surface of the flow path 18A. The curved surface portion 17d and the inner wall surface 13a1 are configured to be in contact with each other on the entire surface.

Further, the protrusions 17b are formed so as to be separated from each other in a direction along the flat surface portion 17e (the width direction of the heat transfer tube 14). Further, the protrusion 17b is formed at a position where it overlaps the hole 17a in the vertical direction.

The header 13a (see FIG. 3A) and the heat transfer tube 14 (see FIG. 3A) are fixed by brazing, but in the present embodiment, the volume occupying member 17 and the header 13a are fitted. Is fixed by. Further, there is no mechanical connection such as brazing between the volume occupying member 17 and the heat transfer tube 14. That is, when the volume occupying member 17 and the heat transfer tube 14 are brazed, when the brazing material melts and flows out, the hole of the heat transfer tube 14 may be blocked, which can be prevented.

As described above, the volume occupying member 17 that narrows the refrigerant flow path 18A is installed inside the header 13a shown in FIG. 3A. Therefore, a substantially semicircular refrigerant flow path 18A having a cross-sectional area smaller than the substantially circular header cross section is formed inside the header 13a. The end surface 14s of the heat transfer tube 14 constitutes an outlet portion 18a (outlet) of the refrigerant flow path 18A.

By the way, the gas-liquid two-phase refrigerant supplied to the header 13a via the inlet pipe 16a is a refrigerant in which a gas refrigerant having a low density and a liquid refrigerant having a high density coexist. For this reason, the liquid refrigerant having a high density tends to accumulate on the lower side due to the influence of gravity and does not easily rise. However, in the outdoor heat exchanger 4A of the present embodiment, since the inlet pipe 16a is located at the lower part in the vertical direction of the header 13a, the refrigerant flow in the header 13a has an upward momentum and occupies a volume. The member 17 reduces the cross-sectional area of the flow path of the header 13a. As a result, the flow velocity of the refrigerant in the header 13a increases, and the momentum of the refrigerant makes it possible to raise the liquid refrigerant to the heat transfer tube 14 located above.

As described above, the air conditioner of the first embodiment includes the outdoor unit 1 and the indoor unit 8, and the outdoor unit 1 includes a compressor 2, an outdoor heat exchanger 4A, an outdoor fan 5, and a diaphragm. It has a device 7 (see FIG. 1). The outdoor heat exchanger 4A expands the heat transfer area of the two headers 13a and 13b arranged substantially vertically, a plurality of heat transfer tubes 14 connecting the headers 13a and 13b substantially horizontally, and the heat transfer tubes 14. The fins 15 and the like are provided (see FIG. 2). The header 13a includes an inlet pipe 16a into which the refrigerant flows into the header 13a, an outlet portion 18a in which the refrigerant flows out into each of the plurality of heat transfer tubes 14, and a refrigerant flow path 18A in which the refrigerant flows from the inlet pipe 16a to the outlet portion 18a. , A volume-occupying member 17 as a refrigerant flow path narrowing portion that narrows the refrigerant flow path 18A (see FIGS. 3 (a) and 3 (b)). As a result, the gas-liquid two-phase refrigerant flowing in from the inlet pipe 16a is evenly distributed to the respective heat transfer pipes 14. As a result, it is possible to provide an air conditioner excellent in energy saving, in which the same degree of endothermic action can be ensured in any of the heat transfer tubes 14 and the efficiency of the outdoor heat exchanger 4A as a whole is improved.

Further, in the first embodiment, the end surface 14s (see FIG. 3A) of the heat transfer tube 14 is substantially flush with the flat surface portion 17e (wall surface) of the refrigerant flow path 18A formed by the volume occupying member 17. As a result, the liquid refrigerant is more likely to flow into the heat transfer tube 14 than when the end surface 14s of the heat transfer tube 14 projects from the wall surface of the refrigerant flow path 18A.

Further, in the first embodiment, the refrigerant flow path constricted portion is composed of the volume occupying member 17 that occupies the space in the header 13a. As a result, a region in which the refrigerant does not flow can be formed, and a function as a non-refrigerant flow path portion can be provided.

In the present embodiment, in order to fix the volume occupying member 17 to the header 13a, the protrusions 17b (see FIGS. 4A to 4C) provided in the volume occupying member 17 and the corresponding headers. Although the fitting with the recess (not shown) on the 13a side has been described as an example, the present invention is not limited to such a configuration. For example, a method such as providing a groove corresponding to the shape of the volume occupying member 17 on the inner surface of the header 13a may be adopted.

Further, in the present embodiment, the case where a flat heat transfer tube having an oval cross section is used as the heat transfer tube 14 has been described as an example, but a heat transfer tube having a general circular cross section can also be used.

(Second Embodiment)
Next, the air conditioner of the second embodiment will be described with reference to FIG. 5A and 5B show the internal structure of the header of the second embodiment, where FIG. 5A is a vertical sectional view and FIG. 5B is a VB-VB sectional view of FIG. 5A. Since the configuration and operation of the refrigeration cycle are the same as those of the first embodiment, overlapping description will be omitted, and the differences from the first embodiment will be mainly described below.

As shown in FIG. 5A, the air conditioner of the second embodiment includes an outdoor heat exchanger 4B (4) instead of the outdoor heat exchanger 4A of the first embodiment. The outdoor heat exchanger 4B has a configuration in which a volume occupying member 19 is added to the outdoor heat exchanger 4A. As described above, the outdoor heat exchanger 4B includes a plurality of volume-occupying members 17 and 19.

A volume occupying member 19 is provided inside the header 13a. Like the volume occupying member 17, the volume occupying member 19 also forms a region in which the refrigerant does not flow, and has a function as a refrigerant flow path narrowing portion (non-refrigerant flow path portion).

Further, the volume occupying member 19 is formed with a hole portion 19a into which the inlet pipe 16a is inserted at a position (overlapping position) facing the insertion hole 13w. The hole 19a is adapted so that the inlet pipe 16a penetrates through the hole 19a to communicate the inlet pipe 16a with the refrigerant flow path 18B.

As shown in FIG. 5B, the volume occupying member 19 has a substantially C-shaped cross section. That is, the volume occupying member 19 includes a curved surface portion 19b formed along the inner wall surface of the header 13a, a flat surface portion 19c facing the flat surface portion 17e of the volume occupying member 17, and flat surface portions 17e from both ends of the flat surface portion 19c. It has side surface portions 19d and 19d extending toward the surface, and is formed in a concave shape in cross section. The flat surface portions 19c, 19d, 19d and the flat surface portion 17e form a refrigerant flow path 18B having a rectangular cross section.

In the second embodiment, the refrigerant flow path constricted portion is configured by combining a plurality of volume-occupying members 17 and 19. As a result, when the increase in the momentum of the refrigerant is insufficient only by the volume occupying member 17, the speed of the refrigerant flow can be further increased, and the refrigerant flowing in from the inlet pipe 16a can be evenly distributed to each heat transfer pipe 14. As a result, it is possible to provide an air conditioner excellent in energy saving, which can secure the same degree of endothermic action in any of the heat transfer tubes 14 and enhance the efficiency of the outdoor heat exchanger 4B as a whole.

Further, in the second embodiment, the refrigerant flow path 18B is formed by combining the volume occupying members 17 and 19, for example, by changing the shape of the volume occupying member 19, the flow path cross section of the refrigerant flow path 18B is formed. It can be easily changed.

In the second embodiment, the cross-sectional shape of the volume occupying member 19 is substantially C-shaped (substantially U-shaped).

(Third Embodiment)
6A and 6B show the internal structure of the header of the third embodiment, FIG. 6A is a vertical sectional view, and FIG. 6B is a VIB-VIB sectional view of FIG. 6A. 7A and 7B show a partition member installed in the header of the third embodiment, FIG. 7A is a front view, FIG. 7B is a side view, and FIG. 7C is a plan view.
The air conditioner of the third embodiment includes an outdoor heat exchanger 4C instead of the outdoor heat exchanger 4A of the first embodiment.

As shown in FIGS. 6A and 6B, the outdoor heat exchanger 4C is provided with a partition member 20 inside the header 13a that divides the internal space of the header 13a into two in a direction orthogonal to the axial direction. ing. By providing the partition member 20, the internal space of the header 13a is divided into a refrigerant flow path 18A having a cross-sectional area smaller than the cross-sectional area of the header 13a and a partition space 21. The partition space 21 has a structure in which the refrigerant does not flow, and has a function as a refrigerant flow path narrowing portion (non-refrigerant flow path portion) like the volume occupying members 17 and 19 described above.

Further, the flat surface portion 20g of the partition member 20 forming the wall of the refrigerant flow path 18A is configured to be substantially flush with the end surface 14s of the heat transfer tube 14 (see FIG. 6A).

As shown in FIGS. 7 (a) and 7 (b), the partition member 20 is formed with a hole 20 a into which the heat transfer tube 14 is inserted. The hole 20a is formed flat so as to follow the flat shape of the heat transfer tube 14. Further, the holes 20a are formed at equal intervals in the vertical direction.

Further, protrusions 20b are formed on the upper end surface 20m and the lower end surface 20n of the partition member 20, respectively.

Further, a communication portion 20c penetrating in the same direction as the hole portion 20a is formed in the lower portion of the partition member 20. The communication portion 20c is formed at a position lower than the hole portion 20a at the lowest position. Further, the diameter (diameter) of the communicating portion 20c is formed to be smaller than the height of the hole portion 20a.

As shown in FIG. 7 (c), the partition member 20 is one of a plane 20d formed toward the insertion hole 13v (see FIG. 6A) and a refrigerant flow path 18A (see FIG. 6A). It has a flat surface 20e forming a wall surface and is formed in a plate shape.

The protrusion 20b is for fixing the partition member 20 to the header 13a (see FIG. 6A). The protrusion 20b is fitted with a recess (not shown) provided in the upper lid portion 13t (see FIG. 6A) and the lower lid portion 13u (see FIG. 6A) of the header 13a to partition the header 13a. The member 20 is fixed in the header 13a.

Since the partition member 20 is installed inside the header 13a in this way, a refrigerant flow path 18A having a cross-sectional area smaller than the cross section of the substantially circular header 13a is formed inside the header 13a. The end surface 14s of the heat transfer tube 14 constitutes an outlet portion 18a (outlet) of the refrigerant flow path 18A.

Further, since the partition member 20 is provided with the communication portion 20c, the pressure of the refrigerant acting on both surfaces (refrigerant flow path 18A and the partition space 21) of the partition member 20 is equalized. Therefore, there is no possibility that the partition member 20 will be deformed by the pressure of the refrigerant. Further, by providing the communication portion 20c, the pressure of the refrigerant acting on the surface of the header 13a that abuts on the refrigerant flow path 18A and the surface that abuts on the partition space 21 becomes the same, so that the pressure of the refrigerant acts on the inner surface of the cylinder of the header 13a. The pressure of the acting refrigerant becomes uniform, which is also suitable in terms of the pressure resistance of the header 13a.

By the way, when the partition member 20 is provided with the communication portion 20c, the refrigerant flowing through the refrigerant flow path 18A may pass through the communication portion 20c and flow into the space side partitioned by the partition member 20. However, as shown in FIG. 6A, by providing the communication portion 20c at the lower portion of the header 13a in the vertical direction, the inflowing refrigerant can easily return to the refrigerant flow path 18A side. As a result, it is possible to prevent the refrigerant from accumulating on the partitioned space side (partition space 21 side).

In the third embodiment configured in this way, the refrigerant flow path narrowing portion is composed of the partition space 21 formed by the partition member 20 provided in the header 13a. As a result, the refrigerant flow path 18A similar to that of the first embodiment is configured, so that the gas-liquid two-phase refrigerant supplied to the header 13a via the inlet pipe 16a is evenly distributed to each heat transfer pipe 14. As a result, it is possible to provide an air conditioner excellent in energy saving, which can secure the same degree of endothermic action in any of the heat transfer tubes 14 and enhance the efficiency of the outdoor heat exchanger 4C as a whole.

Further, since the partition member 20 itself has a smaller volume than the volume occupying member 17 shown in the first embodiment and its shape is relatively simple, the partition member 20 is lighter and cheaper in the first embodiment. The same effect as can be obtained.

Further, in the third embodiment, the partition member 20 is formed with a communication portion 20c for communicating the refrigerant flow path 18A and the partition space 21. As a result, the pressures of the refrigerant flow path 18A and the partition space 21 can be equalized, and the partition member 20 is not likely to be deformed by the pressure of the refrigerant.

Although the case where the through-hole-shaped communication portion 20c is formed in the partition member 20 has been described as an example, the present invention is not limited to such a configuration. For example, the fitting gap between the hole 20a of the partition member 20 and the heat transfer tube 14 or the fitting gap between the partition member 20 and the header 13a may be used as a communication portion.

Further, in order to fix the partition member 20 to the header 13a, the protrusion 20b provided on the partition member 20 and the corresponding recess on the header 13a side (not shown) are fitted as an example. However, it is not limited to such a configuration. For example, a method such as providing a groove corresponding to the shape of the partition member 20 may be provided on the inner surface of the header 13a.

(Fourth Embodiment)
FIG. 8 shows the internal structure of the header of the fourth embodiment, (a) is a vertical sectional view, and (b) is a sectional view of VIIIB-VIIIB of (a).
The air conditioner of the fourth embodiment includes an outdoor heat exchanger 4D instead of the outdoor heat exchanger 4C of the third embodiment.

As shown in FIG. 8A, the outdoor heat exchanger 4D has a configuration in which the partition member 22 is added to the third embodiment. The partition member 22 is formed with a hole 22a through which the inlet pipe 16a penetrates and a communication portion 22b that communicates both sides of the partition member 22. Although the communication portion 22b is formed above the hole 22a, it may be formed below the hole 22a.

As shown in FIG. 8B, by providing the partition member 22 in the header 13a, the internal space of the header 13a becomes the refrigerant flow path 18B having a cross-sectional area smaller than the cross-sectional area of the header 13a and the partition space 23. Divided. The partition space 23 has a structure in which the refrigerant does not flow, and has a function as a refrigerant flow path narrowing portion (non-refrigerant flow path portion) like the partition space 21 described above.

In the fourth embodiment, the refrigerant flow path narrowing portion is composed of a plurality of partition members 20 and 22. As a result, when the increase in the momentum of the refrigerant by the partition member 20 alone is insufficient, the speed of the refrigerant flow can be further increased, and the refrigerant flowing in from the inlet pipe 16a can be evenly distributed to each heat transfer pipe 14. As a result, it is possible to provide an air conditioner excellent in energy saving, which can secure the same degree of endothermic action in any of the heat transfer tubes 14 and enhance the efficiency of the outdoor heat exchanger 4D as a whole.

In the present embodiment, the case where the partition member 22 is provided with the communication portion 22b in order to equalize the pressure between the refrigerant flow path 18B and the partition space 23 has been described as an example. Not limited. For example, the fitting gap between the partition member 22 and the inlet pipe 16a or the fitting gap between the partition member 22 and the header 13a may be used as a communication portion.

(Fifth Embodiment)
9A and 9B show the internal structure of the header of the fifth embodiment, where FIG. 9A is a vertical sectional view and FIG. 9B is a sectional view taken along line IXB-IXB of FIG. 9A.
The air conditioner of the fifth embodiment includes an outdoor heat exchanger 4E instead of the outdoor heat exchanger 4C of the third embodiment.

As shown in FIG. 9A, the outdoor heat exchanger 4E includes a partition member 24 in place of the partition member 20. A hole 24a into which the heat transfer tube 14 is inserted is formed in the partition member 24. Further, the partition member 24 is formed with a communication portion 24c having the same function as the communication portion 20c (see FIG. 8A) below the hole portion 24a at the lowest position.

As shown in FIG. 9B, the partition member 24 is formed in a substantially concave shape in a cross-sectional view. That is, the partition member 24 extends from both ends of the flat surface portion 24b into which the hole portion 24a (see FIG. 9A) into which the heat transfer tube 14 is inserted is formed and toward the inlet tube 16a side. It has two bent portions 24d and 24d.

Further, the tips of the bent portions 24d and 24d are in contact with the inner wall surface 13a1 of the header 13a (circular tubular body 13s). As a result, the refrigerant flow path 18C surrounded by the flat surface portion 24b, the bent portions 24d, 24d, and the inner wall surface 13a1 is formed. The refrigerant flow path 18C is formed so as to diverge from the inlet pipe 16a toward the heat transfer pipe 14.

Further, the end surface 14s of the heat transfer tube 14 (see FIG. 9A) is configured to be substantially on the same plane as the flat surface portion 24e (the wall surface forming the refrigerant flow path 18C) of the partition member 24. As a result, the refrigerant can easily enter the heat transfer tube 14 as compared with the case where the heat transfer tube 14 protrudes from the flat surface portion 24e.

In the fifth embodiment, the cross-sectional area of the refrigerant flow path 18C can be made smaller than that of the refrigerant flow path 18A of the third embodiment, the speed of the refrigerant flow can be further increased, and the refrigerant flowing in from the inlet pipe 16a can be further increased. It can be distributed evenly to the heat transfer tube 14. As a result, it is possible to provide an air conditioner excellent in energy saving, which can secure the same degree of endothermic action in any of the heat transfer tubes 14 and enhance the efficiency of the outdoor heat exchanger 4E as a whole.

Further, in the fifth embodiment, since the partition member 24 can be composed of a single component, the work of attaching the partition member 24 to the header 13a can be performed more easily than in the case of a plurality of partition members.

Further, in the fifth embodiment, by adjusting the length L of the bent portion 24d (see FIG. 9B), the contact position of the tip of the bent portion 24d with respect to the inner wall surface 13a1 of the header 13a changes, so that the refrigerant is used. The cross-sectional area of the flow path 18C can be easily adjusted. That is, the cross-sectional area of the refrigerant flow path 18C can be narrowed by increasing the length L of the bent portion 24d, and the cross-sectional area of the refrigerant flow path 18C can be widened by shortening the length L.

(Sixth Embodiment)
10A and 10B show the internal structure of the header of the sixth embodiment, where FIG. 10A is a vertical sectional view and FIG. 10B is a sectional view taken along line XB-XB of FIG.
The air conditioner of the sixth embodiment includes an outdoor heat exchanger 4F instead of the outdoor heat exchanger 4D of the fourth embodiment.

As shown in FIG. 10A, the outdoor heat exchanger 4F includes partition members 24 and 25 in place of the partition members 20 and 22. The partition member 24 is formed with a hole 24a into which the heat transfer tube 14 is inserted.

The partition member 25 is formed with a hole 25a into which the inlet pipe 16a is inserted. Further, the partition member 25 is formed with a communication portion 25b having the same function as the communication portion 22b of the fourth embodiment (see FIG. 8A) above the hole portion 25a. The communication portion 25b may be formed below the hole portion 25a.

As shown in FIG. 10B, the partition member 24 is formed in a substantially concave shape in a cross-sectional view, as in the fifth embodiment, and has a flat surface portion 24b and bent portions 24d and 24d. Further, the partition member 24 is arranged so that the inlet pipe 16a side opens.

The partition member 25 is formed in a flat plate shape in a cross-sectional view, and is arranged so as to close the opening of the partition member 24.

By configuring the partition members 24 and 25 in this way, the refrigerant flow path 18D surrounded by the partition members 24 and 25 is formed in the header 13a. Further, the end surface 14s of the heat transfer tube 14 (see FIG. 10A) is configured to be substantially on the same plane as the flat surface portion 24e (the wall surface forming the refrigerant flow path 18D) of the partition member 24.

In the sixth embodiment, when the increase in the momentum of the refrigerant by the partition member 24 alone is insufficient, the speed of the refrigerant flow is further increased, and the refrigerant flowing in from the inlet pipe 16a is evenly distributed to the heat transfer pipes 14. it can. As a result, it is possible to provide an air conditioner excellent in energy saving, which can secure the same degree of endothermic action in any of the heat transfer tubes 14 and enhance the efficiency of the outdoor heat exchanger 4F as a whole.

(7th Embodiment)
11A and 11B show the internal structure of the header of the seventh embodiment, where FIG. 11A is a vertical sectional view and FIG. 11B is a sectional view taken along line XIB-XIB of FIG. 12A and 12B show the shape of the heat transfer tube of the seventh embodiment, where FIG. 12A is a front view, FIG. 12B is a side view, and FIG. 12C is a plan view.
The air conditioner of the seventh embodiment includes an outdoor heat exchanger 4G instead of the outdoor heat exchanger 4D of the fourth embodiment.

As shown in FIG. 11A, the outdoor heat exchanger 4G includes a heat transfer tube 14A instead of the heat transfer tube 14. The heat transfer tube 14A is provided with a protrusion 14a at the end of the heat transfer tube 14. The protrusion 14a is formed so as to extend from the end surface 14s of the heat transfer tube 14A toward the partition member 22. By contacting the partition member 22 with the protrusion 14a, the insertion depth of the heat transfer tube 14A into the header 13a is defined, facilitating the positioning of the heat transfer tube 14A with respect to the header 13a.

As shown in FIG. 11B, the protrusion 14a extends from the center of the heat transfer tube 14A in the width direction toward the partition member 22. Further, the tip of the protrusion 14a is abutted against the partition member 22.

As shown in FIG. 12A, the heat transfer tube 14A is a flat tube having an oval cross section. Further, the outer surface of the heat transfer tube 14A has an upper surface and a lower surface formed in a plane shape, and both ends in the width direction are formed in a semicircular shape.

Further, in the heat transfer tube 14A, partition wall portions 14d are formed inside the flat tube at intervals in the flat direction (width direction), and a plurality of (four in the present embodiment) minute flow paths 14b (flow paths). Is formed. The partition wall portion 14d is continuously formed from the end portion on the header 13a (see FIG. 11A) side to the end portion on the header 13b (see FIG. 2) side.

As shown in FIGS. 12B and 12C, an inflow portion 14c is formed in the heat transfer tube 14A. The protrusion 14a has a structure extending in the pipe axis direction from the inflow surface of the inflow portion 14c. Further, the protrusion 14a is formed by removing a part of the flat tube. In the seventh embodiment, it is a pin-shaped structure including a partition wall portion 14d forming the microchannel 14b.

As a result, the strength of the protrusion 14a is secured. Further, since the shape of the protrusion 14a when viewed from the pipe axis direction is formed in an H shape, the bending strength of the protrusion 14a is enhanced. Further, since the protrusion 14a does not form a flow path inside the protrusion 14a, even if the end portion of the protrusion 14a is abutted against another component (partition member 22), the flow path is blocked. It is not configured.

In the seventh embodiment, the same effect as that of the fourth embodiment can be realized in a structure that is easier to assemble. That is, it is possible to provide an air conditioner having excellent energy saving properties.

In the seventh embodiment, the improvement of the assembling property with respect to the fourth embodiment has been described as an example, but it may be applied to any of the first to sixth embodiments. ..

(8th Embodiment)
FIG. 13 shows the internal structure of the header of the eighth embodiment, (a) is a vertical sectional view, and (b) is a sectional view of XIIIB-XIIIB of (a). 14A and 14B show a partition member installed in the header of the eighth embodiment, FIG. 14A is a plan view, FIG. 14B is a front view, FIG. 14C is a rear view, and FIG. 14D is a side view.
The air conditioner of the eighth embodiment is an outdoor heat exchanger 4H instead of the outdoor heat exchanger 4D of the fourth embodiment.

As shown in FIGS. 13 (a) and 13 (b), the outdoor heat exchanger 4H includes a partition member 26 in place of the flat plate-shaped partition member 22 (see FIG. 8). The partition member 26 has a flat plate-shaped flat surface portion 26a formed in a substantially T shape in a cross-sectional view and formed parallel to the partition member 20, and a projecting portion 26b extending from the flat surface portion 26a toward the partition member 20. ,have. The protrusion 26b is located at the center of the flat surface portion 26a in the width direction, and the tip of the protrusion 26b is in contact with the partition member 20.

In this way, the protruding portion 26b of the partition member 26 is in contact with the heat transfer tube 14A. As a result, the insertion depth of the heat transfer tube 14A into the header 13a is defined, and the positioning of the heat transfer tube 14A with respect to the header 13a is facilitated.

As shown in FIG. 14A, the partition member 26 is formed in a substantially T shape, and has a flat surface portion 26a arranged in parallel with the partition member 20 and a protruding portion protruding in a direction orthogonal to the flat surface portion 26a. It has 26b and.

As shown in FIGS. 14 (b) and 14 (c), the flat surface portion 26a extends in the vertical direction (vertical direction) and is formed in a rectangular shape. Further, a plurality of protrusions 26c are formed on the upper end surface 26m and the lower end surface 26n of the flat surface portion 26a, respectively. The protrusion 26c is fitted with a recess (not shown) provided in the upper end lid portion 13t and the lower end lid portion 13u (see FIG. 13A) of the header 13a to form a partition member 26 with respect to the header 13a. Can be fixed.

Further, a hole 26d into which the inlet pipe 16a is inserted is formed at the lower end of the partition member 26. Further, the flat surface portion 26a is formed with a communication portion 26e for communicating the refrigerant flow path 18E (see FIG. 13B) and the partition space 21 (see FIG. 13A) to equalize the pressure. Has been done. The communication portion 26e is formed at a position smaller and lower than the hole portion 26d.

As shown in FIG. 14 (d), the protrusion 26b is formed with a notch 26f at a position facing the hole 26d. As a result, one refrigerant flow path 18E1 (see FIG. 13 (b)) partitioned by the protrusion 26b can communicate with the other refrigerant flow path 18E2 (see FIG. 13 (b)), and the refrigerant flow path can be communicated with each other. The pressure in each space of 18E can be made uniform.

In the eighth embodiment, the same effect as that of the fourth embodiment can be realized in a structure that is easier to assemble. That is, it is possible to provide an air conditioner having excellent energy saving properties.

Further, in the eighth embodiment, the refrigerant flow path 18E is divided into the refrigerant flow paths 18E1 and 18E2 by the protruding portion (veneer portion) 26b. As a result, when the increase in the momentum of the refrigerant by the partition members 20 and 22 is insufficient, the speed of the refrigerant flow can be further increased, and the refrigerant flowing in from the inlet pipe 16a can be evenly distributed to the heat transfer pipes 14. As a result, it is possible to provide an air conditioner excellent in energy saving, which can secure the same degree of endothermic action in any of the heat transfer tubes 14 and enhance the efficiency of the outdoor heat exchanger 4H as a whole.

Further, in the eighth embodiment, by forming the notch 26f in the partition member 26, the pressure can be made uniform between the refrigerant flow path 18E1 and the refrigerant flow path 18E2, and the partition member 26 can control the pressure of the refrigerant. There is no risk of deformation.

(9th Embodiment)
15A and 15B show an internal structure of a header according to a ninth embodiment, where FIG. 15A is a vertical sectional view and FIG. 15B is a sectional view taken along line XVB-XVB according to FIG. Note that FIG. 15 is a cross-sectional view showing a detailed structure in the vicinity of the headers 13a and 13b of both the outdoor heat exchangers 4I.
The air conditioner of the ninth embodiment is a case where the outdoor heat exchanger 4H of the eighth embodiment is applied to a part of the header 13a.

As shown in FIG. 15A, in the outdoor heat exchanger 4I, an inlet pipe 16a and an outlet pipe 16b through which the refrigerant flows in and out of the outdoor heat exchanger 4I are provided in the header 13b on one side. The internal space of the header 13b is vertically divided by a partition plate 27. In the present embodiment, the internal space of the header 13a is divided so that the upper space Q1 contains 12 heat transfer tubes 14 and the lower space Q2 contains 3 heat transfer tubes.

Further, the internal space of the header 13a is divided into upper and lower parts by a partition plate 28 in which a through hole 28a is formed. Similar to the header 13b, the header 13a is divided into an internal space so that the upper space Q3 contains 12 heat transfer tubes 14 and the lower space Q4 contains three heat transfer tubes 14. Further, among the upper and lower divided spaces inside the header 13a, the same structure as that shown in the eighth embodiment is applied to the upper space Q3.

Further, the heat transfer tubes 14 in the space Q1 and the space Q2 are connected to the header 13b so that the tip of the heat transfer tube 14 projects from the inner wall surface of the header 13b. Further, the heat transfer tube 14 in the space Q4 is connected to the header 13a so that the tip of the heat transfer tube 14 projects from the inner wall surface of the header 13a.

As shown in FIG. 15B, the through hole 28a formed in the partition plate 28 is formed in a long hole shape and is formed so as to straddle the refrigerant flow path 18E1 and the refrigerant flow path 18E2. Further, the through hole 28a is formed at a position capable of communicating between the partition member 20 and the flat surface portion 26a, that is, the space forming the refrigerant flow paths 18E1 and 18E2.

In the outdoor heat exchanger 4I configured in this way, when the gas-liquid two-phase refrigerant flows into the header 13b from the inlet pipe 16a, the refrigerant passes through the lower three heat transfer tubes 14 and enters the space Q4 below the header 13a. The flow flows into the space Q3 above the header 13a through the through hole 28a of the partition plate 28.

Inside the space Q3 above the header 13a, the partition member 20 and the partition member 26 form a refrigerant flow path 18E having a cross-sectional area smaller than the cross section of the header 13a, so that the refrigerant flow is accelerated and the momentum thereof causes the refrigerant flow to accelerate. The liquid refrigerant rises to the upper heat transfer tube 14. Further, the end surface 14s (inflow portion) of the connected heat transfer tube 14 is substantially flush with the flat surface portion 20g of the refrigerant flow path 18E formed by the partition member 20. Therefore, the liquid refrigerant is more likely to flow into the heat transfer tube 14 than when the end surface 14s (inflow portion) of the heat transfer tube 14 protrudes from the wall surface of the refrigerant flow path 18E.

By these actions, the gas-liquid two-phase refrigerant flowing in the header 13 is evenly distributed to each heat transfer tube 14 in the upper space Q3 divided by the partition plate 28 inside the header 13a. As a result, it is possible to provide an air conditioner excellent in energy saving, which can secure the same degree of endothermic action in any of the heat transfer tubes 14 and enhance the efficiency of the outdoor heat exchanger 4I as a whole.

Further, in the ninth embodiment, the partition member 20 and the partition member 26 are used as in the eighth embodiment in order to form the refrigerant flow path 18 having a cross-sectional area smaller than the cross section of the header 13a. Not limited to. For example, the method using the volume occupying members 17, 19 as shown in the first embodiment or the second embodiment, or the partition members 20, 22, 24, as shown in the third to seventh embodiments, The method using 25 may be applied.

Further, as in the ninth embodiment, the device for forming the refrigerant flow path 18E having a cross-sectional area smaller than the cross section of the header 13a may be applied to a part of the header 13a whose region is divided by the partition plate 28. Good.

(10th Embodiment)
16A and 16B show the internal structure of the header of the tenth embodiment, FIG. 16A is a vertical sectional view, FIG. 16B is an enlarged sectional view of XVIB-XVIB of FIG. 16A, and FIG. Is. The solid arrow in FIG. 16A indicates the flow of the refrigerant during evaporation.
The air conditioner of the tenth embodiment includes an outdoor heat exchanger 4J.

As shown in FIG. 16A, the outdoor heat exchanger 4J includes a header 13 arranged substantially vertically, a plurality of heat transfer tubes 14 connecting the headers 13 substantially horizontally, and a heat transfer tube 14. It is configured to include fins 15 that expand the heat area.

The header 13 includes an outer tube 13c, an inner tube 13d, an insertion tube 13e, a partition plate 13f, an inner end cap 13h, and an outer end cap 13i.

The outer tube 13c is formed in a cylindrical shape with the upper end surface and the lower end surface open. Further, the outer tube 13c is composed of, for example, a clad tube in which the main material is made of an aluminum alloy and a brazing material is formed on the outside.

The inner tube 13d is made of, for example, an aluminum alloy, and is formed in a cylindrical shape with open upper and lower end surfaces. Further, the axial length of the inner pipe 13d is formed in the same manner as the axial length of the outer pipe 13c. Further, the inner tube 13d is inserted into the outer tube 13c in a state where the outer surface of the inner tube 13d and the inner surface of the outer tube 13c are in contact with each other. The inner tube 13d is made of, for example, a non-clad material.

The intubation tube 13e is made of a hollow or solid aluminum alloy and is formed in a columnar shape. The axial length of the intubation tube 13e is shorter than the axial length of the outer tube 13c and the inner tube 13d.

The partition plate 13f is formed in a disk shape and is provided at the center of the inner pipe 13d in the axial direction. As a result, the internal space of the header 13 is divided into upper and lower spaces Q5 and Q6. The internal space is divided into the spaces Q5 and Q6 so as to include four heat transfer tubes 14 respectively. The number of heat transfer tubes 14 is an example, and is not limited to this embodiment.

Further, the partition plate 13f is formed with a communication hole 13g penetrating in the axial direction (vertical direction, axial direction of the header 13).

The inner end cap 13h is made of, for example, an aluminum alloy, and is provided on both sides of the insertion tube 13e in the axial direction (when the insertion tube 13e is hollow).

The outer end cap 13i is made of, for example, an aluminum alloy, and closes both ends in the axial direction of the header 13. The outer end cap 13i is joined to the outer pipe 13c and the inner pipe 13d by a brazing material.

As shown in FIG. 16B, the partition plate 13f is formed with a large-diameter insertion hole 13f1 through which the insertion tube 13e is inserted. The radial center of the insertion hole 13f1 is formed so as to be offset from the radial center of the inner tube 13d to the side opposite to the heat transfer tube 14.

Further, the communication holes 13g formed in the partition plate 13f are formed at a plurality of locations. The communication holes 13g are not limited to two locations, and may be formed at three or more locations. Further, the communication hole 13g is formed at a position where it does not overlap with the heat transfer tube 14 in the axial direction. Further, the diameter of the communication hole 13g is formed to be sufficiently smaller than the diameter of the insertion hole 13f1.

As shown in FIG. 16C, in the method of manufacturing the header 13, the inner tube 13d is inserted into the outer tube 13c, and then the burring process is performed. As a result, the outer tube 13c is formed with a burring portion 13v1 into which the heat transfer tube 14 is inserted. A notch hole 13d1 is formed in advance in the inner pipe 13d so that the burring portion 13v1 does not come into contact with the inner pipe 13d.

Then, the partition plate 13f is inserted and fixed through a notch (not shown) formed on the side surface of the outer pipe 13c and the inner pipe 13d. Then, the insertion tube 13e to which the inner end cap 13h is attached is inserted into the insertion hole 13f1 of the partition plate 13f. Then, the outer end cap 13i is attached and fixed via the brazing material. Then, the heat transfer tube 14 is inserted into the burring portion 13v1 through the insertion hole 13v, and the outer tube 13c and the heat transfer tube 14 are joined via a brazing material.

In the tenth embodiment configured in this way, when the gas-liquid two-phase refrigerant flows into the header 13 from the heat transfer tube 14 of the lower space Q6, the refrigerant passes through the lower four heat transfer tubes 14 to the header 13. The flow flows into the space Q5 above the header 13 through the communication hole 13g of the partition plate 13f.

Inside the space Q5 above the header 13, the inner pipe 13d and the insertion pipe 13e form a refrigerant flow path 18F having a cross-sectional area smaller than the cross section of the header 13, so that the refrigerant flow is accelerated and the momentum causes the refrigerant flow to accelerate. The liquid refrigerant rises to the upper heat transfer tube 14.

The gas-liquid two-phase refrigerant flowing in the header 13 is evenly distributed to each heat transfer tube 14 connected to the upper space Q5 divided by the partition plate 13f inside the header 13. As a result, it is possible to provide an air conditioner excellent in energy saving, which can secure the same degree of endothermic action in any of the heat transfer tubes 14 and enhance the efficiency of the outdoor heat exchanger 4J as a whole.

In the present embodiment, the header 13 is composed of an outer pipe 13c, an inner pipe 13d, an insertion pipe 13e, a partition plate 13f, an inner end cap 13h, and an outer end cap 13i, but the inner pipe depends on the flow rate condition of the refrigerant. The 13d and the inner end cap 13h may be omitted.

The present invention is not limited to the above-described embodiment, and includes various modifications. For example, although the cross-sectional shape of the header 13 of each of the above-described embodiments is substantially circular, the present invention may be applied to a header having a cross-sectional shape other than the substantially circular shape such as an elliptical shape or a square shape.

Further, in the first embodiment, the case where the refrigerant flow path 18A is configured with the same flow path cross section from the lower end to the upper end of the header 13a has been described as an example. However, the present invention is not limited to such a configuration, and the flow path cross-sectional area may be narrowed on the lower side and widened toward the upper side.

1 Outdoor unit 2 Compressor 3 Four-way valve 4,4A, 4B, 4C, 4D, 4E, 4F, 4G, 4H, 4I, 4J Outdoor heat exchanger (heat exchanger)
5 Outdoor fan 6 Outdoor fan motor 7 Squeezing device 8 Indoor unit 9 Indoor heat exchanger 10 Indoor fan 11 Indoor fan motor 12 Connection piping 13, 13a, 13b Header 13c Outer pipe 13d Inner pipe 13e Insert pipe 13f Partition plate 13f1 Insertion hole 13g Communication hole 14, 14A Heat transfer tube 14a Projection 14b Micro flow path (flow path)
14d partition wall 14s end face 15 fin 16a inlet pipe (entrance)
16b Outlet pipe 17, 19 Volume occupying member (refrigerant flow path constriction)
18, 18A, 18B, 18C, 18D, 18E, 18F Refrigerant flow path 18a Outlet (outlet)
20, 22, 24, 25, 26 Partition member 20c, 22b, 24c, 25b, 26e Communication part 21, 23 Partition space (refrigerant flow path constriction part)
26b Protruding parts 27,28 Partition plate

Claims (15)

Equipped with an outdoor unit and an indoor unit,
The outdoor unit includes a compressor, a heat exchanger, an outdoor fan, and a throttle device.
The heat exchanger includes two headers arranged substantially vertically, a plurality of heat transfer tubes connecting the headers substantially horizontally, and fins for expanding the heat transfer area of the heat transfer tubes.
The header narrows the inlet through which the refrigerant flows into the header, the outlet through which the refrigerant flows out into each of the plurality of heat transfer tubes, the refrigerant flow path through which the refrigerant flows from the inlet to the outlet, and the refrigerant flow path. An air conditioner characterized by having a refrigerant flow path constricted portion. In the air conditioner according to claim 1,
The refrigerant flow path constricted portion is an air conditioner characterized in that the wall surface forming the wall of the refrigerant flow path is configured to be substantially flush with the end surface of the heat transfer tube. In the air conditioner according to claim 1 or 2.
An air conditioner characterized in that the refrigerant flow path constricted portion is composed of a volume occupying member that occupies at least the space in the header. In the air conditioner according to claim 3,
An air conditioner characterized in that the number of the volume occupying members is a plurality. In the air conditioner according to claim 1 or 2.
An air conditioner characterized in that the refrigerant flow path constricted portion is composed of at least a partition space formed by a partition member provided in the header. In the air conditioner according to claim 5,
The partition member is an air conditioner having a communicating portion for communicating the refrigerant flow path and the partition space. In the air conditioner according to claim 6,
An air conditioner characterized in that the communication portion is provided at a lower portion in the vertical direction of the header. In the air conditioner according to claim 5,
An air conditioner characterized by having a plurality of partition members. In the air conditioner according to claim 1,
The heat transfer tube has a protrusion formed at the end of the heat transfer tube.
An air conditioner characterized in that the amount of the heat transfer tube inserted into the header is defined by the protrusion coming into contact with another member. In the air conditioner according to claim 9,
The heat transfer tube is a flat tube divided into a plurality of flow paths by a partition wall portion.
An air conditioner characterized in that the protrusion is composed of the partition wall. In the air conditioner according to claim 8,
At least one of the plurality of partition members includes a protrusion protruding from a flat surface portion.
An air conditioner characterized in that the amount of the heat transfer tube inserted into the header is defined by the contact of the heat transfer tube with the protruding portion. In the air conditioner according to claim 1,
The header has a partition plate that divides the refrigerant flow path into upper and lower parts.
An air conditioner characterized in that the partition plate is formed with a communication hole for communicating the upper and lower spaces and an insertion hole through which the narrowed portion of the refrigerant flow path is inserted. In the air conditioner according to claim 12,
The header is an air conditioner characterized in that it is configured by inserting an inner pipe into an outer pipe. In the air conditioner according to claim 1,
An air conditioner characterized in that the central height of the inlet is lower than the central height of the heat transfer tube at the lowest position. Two headers arranged almost vertically,
A plurality of heat transfer tubes that connect the headers substantially horizontally, and
A fin that expands the heat transfer area of the heat transfer tube is provided.
The header includes an inlet through which the refrigerant flows into the header, an outlet through which the refrigerant flows out into each of the plurality of heat transfer tubes, a refrigerant flow path through which the refrigerant flows from the inlet to the outlet, and the refrigerant flow path. A heat exchanger characterized by having a narrowed refrigerant flow path and a narrowed portion.

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