HEAT EXCHANGER, OUTDOOR UNIT WITH HEAT EXCHANGER, AND AIR CONDITIONER WITH OUTDOOR UNIT

Abstract

The heat exchanger includes a plurality of heat transfer tubes arranged at intervals in the horizontal direction, an upper header provided above the plurality of heat transfer tubes and having an upper first space into which upper ends of the plurality of heat transfer tubes are inserted, a lower header provided below the plurality of heat transfer tubes and having a lower first space into which lower ends of the plurality of heat transfer tubes are inserted, an inflow section provided at one horizontal end of the lower header and into which a refrigerant flows when the lower header functions as a condenser, an outflow section provided at the other horizontal end of the upper header or the lower header and from which the refrigerant flows out when the lower header functions as a condenser, and a partition plate that divides the interior of at least one of the upper header and the lower header into a plurality of regions in the horizontal direction, and the lower header includes a lower first region that distributes the refrigerant when the lower header functions as a condenser, and a partition plate that divides the interior of at least one of the upper header and the lower header into a plurality of regions in the horizontal direction. and a lower second region where the separated refrigerant join together, and of the lower first region and the lower second region, other than the lower first region communicating with the inlet portion, the lower first region and the lower second region have a lower second space partitioned from the lower first space, and a plurality of orifices formed along the horizontal direction connecting the lower first space and the lower second space. The upper header, when functioning as a condenser, has at least one upper first region which distributes refrigerant and an upper second region where the distributed refrigerant join together, and of the upper first region and the upper second region, only the upper second region has an upper second space partitioned from the upper first space, and a plurality of orifices formed along the horizontal direction connecting the upper first space and the upper second space.

Description

[Technical field]

[0001] The present disclosure relates to a heat exchanger having a plurality of heat transfer tubes, an outdoor unit including the heat exchanger, and an air conditioner including the outdoor unit. [Background technology]

[0002] Conventionally, there is a heat exchanger that includes a plurality of flat tubes arranged horizontally at intervals with the tube extension direction being the vertical direction, a plurality of fins connected between adjacent flat tubes and that transfer heat to the flat tubes, and headers respectively provided at the upper and lower ends of the plurality of flat tubes (see, for example, Patent Document 1).

[0003] In the heat exchanger of Patent Document 1, the interior is divided horizontally into multiple regions, and partitions are provided in the header so that the refrigerant flow is opposed (turned) in each adjacent region and the refrigerant flow in each region is counter-current to the adjacent region. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] JP 2015-230129 A Summary of the Invention [Problem to be solved by the invention]

[0005] Conventional heat exchangers such as that disclosed in Patent Document 1 have a problem in that the amount of refrigerant distributed from the distribution region of the header to each heat transfer tube is uneven, causing a decrease in heat exchange performance.

[0006] The present disclosure has been made to solve the above-mentioned problems, and aims to provide a heat exchanger that suppresses deterioration of heat exchange performance by improving refrigerant distribution performance, an outdoor unit equipped with a heat exchanger, and an air conditioning apparatus equipped with an outdoor unit. [Means for solving the problem]

[0007] A heat exchanger according to the present disclosure includes a plurality of heat transfer tubes arranged at intervals in a horizontal direction, an upper header provided on top of the plurality of heat transfer tubes and having an upper first space into which upper ends of the plurality of heat transfer tubes are inserted, a lower header provided on bottom of the plurality of heat transfer tubes and having a lower first space into which lower ends of the plurality of heat transfer tubes are inserted, an inflow section provided at one horizontal end of the lower header and into which a refrigerant flows when the lower header functions as a condenser, an outflow section provided at the other horizontal end of the upper header or the lower header and into which the refrigerant flows when the upper header functions as a condenser, and a heat exchanger that horizontally divides the interior of at least one of the upper header and the lower header into a plurality of regions. First partition plate and second partition plate And, The second partition plate has an opening that communicates with adjacent regions, The lower header, when functioning as a condenser, has at least one lower first region that distributes refrigerant and one lower second region where the distributed refrigerant joins, and of the lower first region and the lower second region, in addition to the lower first region that communicates with the inlet portion, the lower first region and the lower second region have a lower second space partitioned from the lower first space, and a plurality of orifices formed along the horizontal direction that connect the lower first space and the lower second space. The upper header, when functioning as a condenser, has at least one upper first region that distributes refrigerant and one upper second region where the distributed refrigerant joins, and of the upper first region and the upper second region, only the upper second region has an upper second space partitioned from the upper first space, and a plurality of orifices formed along the horizontal direction that connect the upper first space and the upper second space.

[0008] Also, a heat exchanger according to the present disclosure includes a plurality of heat transfer tubes arranged at intervals in a horizontal direction, an upper header provided on top of the plurality of heat transfer tubes and having an upper first space into which upper ends of the plurality of heat transfer tubes are inserted, a lower header provided on bottom of the plurality of heat transfer tubes and having a lower first space into which lower ends of the plurality of heat transfer tubes are inserted, an inflow section provided at one horizontal end of the upper header and into which a refrigerant flows when the upper header functions as a condenser, an outflow section provided at the other horizontal end of the upper header or the lower header and into which the refrigerant flows when the upper header functions as a condenser, and a heat exchanger that horizontally divides the interior of at least one of the upper header and the lower header into a plurality of regions. First partition plate and second partition plate And, The second partition plate has an opening that communicates with adjacent regions, The lower header, when functioning as a condenser, has at least one lower first region that distributes refrigerant and one lower second region where the distributed refrigerant joins, and each of the lower first region and the lower second region has a lower second space partitioned from the lower first space, and a plurality of orifices formed along the horizontal direction that connect the lower first space and the lower second space. The upper header, when functioning as a condenser, has at least one upper first region that distributes refrigerant and one upper second region where the distributed refrigerant joins, and of the upper first region and the upper second region, only the upper second region has an upper second space partitioned from the upper first space, and a plurality of orifices formed along the horizontal direction that connect the upper first space and the upper second space.

[0009] An outdoor unit according to the present disclosure includes the above-described heat exchanger.

[0010] An air conditioner according to the present disclosure includes the above outdoor unit. Effect of the Invention

[0011] According to the heat exchanger, outdoor unit equipped with a heat exchanger, and air conditioning apparatus equipped with an outdoor unit of the present disclosure, by configuring the upper header and lower header as described above, it is possible to improve the refrigerant distribution performance when the system is functioning in either evaporative operation or condensing operation, and to suppress a decrease in heat exchange performance. [Brief description of the drawings]

[0012] [Figure 1] FIG. 1 is a refrigerant circuit diagram showing the flow of refrigerant during heating operation of an air conditioner equipped with a heat exchanger according to embodiment 1. [Diagram 2] FIG. 1 is a refrigerant circuit diagram showing the flow of refrigerant during cooling operation of an air conditioner equipped with a heat exchanger according to embodiment 1. [Diagram 3] FIG. 3 is a front view illustrating a schematic flow of a refrigerant when the heat exchanger according to the first embodiment functions as a condenser. [Figure 4] 3 is a front view showing a schematic view of a refrigerant flow when the heat exchanger according to the first embodiment functions as an evaporator. FIG. [Diagram 5] FIG. 4 is an enlarged view of the portion indicated by the arrow A in FIG. 3. [Figure 6] FIG. 4 is an enlarged view of the portion indicated by the arrow B in FIG. 3. [Figure 7] 5 is a view of the CC cross section of FIG. 4 as viewed in the direction of the arrow. [Figure 8] 5 is a cross-sectional view taken along the line DD in FIG. 4, seen in the direction indicated by the arrows. [Figure 9] 5 is a cross-sectional view of the E-E section of FIG. 4 as viewed in the direction of the arrows. [Figure 10] 5 is a view of the FF cross section of FIG. 4 as seen in the direction of the arrow. [Figure 11] 5 is a view of a first modified example of the cross section DD of FIG. 4 as viewed in the direction of the arrows. [Figure 12] 5 is a view of a first modified example of the E-E cross section of FIG. 4 as viewed in the direction of the arrows. [Figure 13] 5 is a view of a second modified example of the cross section DD of FIG. 4 as viewed in the direction of the arrows. [Figure 14] 5 is a view of a second modified example of the E-E cross section of FIG. 4 as viewed in the direction of the arrows. [Figure 15]5 is a view of a third modified example of the cross section DD of FIG. 4 as viewed in the direction of the arrows. [Figure 16] 5 is a view of a third modified example of the E-E cross section of FIG. 4 as viewed in the direction of the arrows. [Figure 17] FIG. 4 is a front view illustrating a schematic flow of a refrigerant when the modified example of the heat exchanger according to the first embodiment functions as a condenser. [Figure 18] 5 is a front view illustrating a schematic flow of a refrigerant when the modified example of the heat exchanger according to the first embodiment functions as an evaporator. FIG. [Figure 19] FIG. 1 is a plan view showing a schematic view of the inside of an outdoor unit equipped with a heat exchanger according to a first embodiment. [Figure 20] FIG. 4 is a plan view showing a schematic view of the inside of a modified example of the outdoor unit provided with the heat exchanger according to the first embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0013] Hereinafter, an embodiment of the present disclosure will be described based on the drawings. Note that the present disclosure is not limited to the embodiments described below. In addition, the size relationship of each component in the following drawings may differ from the actual one. In addition, in the following description, terms expressing directions, such as "upper", "lower", "right", "left", "front", and "rear", are appropriately used to facilitate understanding, but these terms are for the purpose of explanation and do not limit the embodiments. In addition, in the embodiments, "upper", "lower", "right", "left", "front", and "rear" are used when the heat exchanger is viewed from the front.

[0014] Embodiment 1 <Configuration of the Air Conditioning Apparatus 100> Fig. 1 is a refrigerant circuit diagram showing the flow of refrigerant during heating operation of an air conditioner 100 equipped with a heat exchanger 30 according to embodiment 1. Fig. 2 is a refrigerant circuit diagram showing the flow of refrigerant during cooling operation of an air conditioner 100 equipped with a heat exchanger 30 according to embodiment 1. Note that the arrows in Fig. 1 indicate the flow of refrigerant during heating operation, and the arrows in Fig. 2 indicate the flow of refrigerant during cooling operation.

[0015] 1 and 2, a heat exchanger 30 according to the first embodiment is mounted on the outdoor unit 10 of an air conditioner 100 that includes an outdoor unit 10 and an indoor unit 20. The outdoor unit 10 includes a compressor 11, a flow switching device 12, a heat exchanger 30, a throttling device 13, and a fan 14. The indoor unit 20 includes an indoor heat exchanger 21 and an indoor fan 22.

[0016] The air conditioner 100 also includes a refrigerant circuit in which a compressor 11, a flow path switching device 12, a heat exchanger 30, a throttling device 13, and an indoor heat exchanger 21 are connected in sequence by refrigerant piping 50, and in which a refrigerant circulates. The air conditioner 100 is capable of both cooling and heating operation by switching the flow path switching device 12.

[0017] The compressor 11 draws in a low-temperature, low-pressure refrigerant, compresses the drawn refrigerant, and discharges a high-temperature, high-pressure refrigerant. The compressor 11 is, for example, an inverter compressor whose capacity, which is the amount of discharge per unit time, is controlled by changing the operating frequency.

[0018] The flow path switching device 12 is, for example, a four-way valve, and switches between cooling operation and heating operation by switching the direction of refrigerant flow. During heating operation, the flow path switching device 12 switches to the state shown by the solid line in Fig. 1, and the discharge side of the compressor 11 is connected to the heat exchanger 30. During cooling operation, the flow path switching device 12 switches to the state shown by the solid line in Fig. 2, and the discharge side of the compressor 11 is connected to the indoor heat exchanger 21.

[0019] The heat exchanger 30 exchanges heat between the outdoor air and the refrigerant. During cooling operation, the heat exchanger 30 functions as a condenser that releases heat from the refrigerant to the outdoor air to condense the refrigerant. During heating operation, the heat exchanger 30 functions as an evaporator that evaporates the refrigerant and cools the outdoor air with the heat of vaporization.

[0020] The expansion device 13 is, for example, an electronic expansion valve capable of adjusting the aperture, and by adjusting the aperture, the pressure of the heat exchanger 30 or the refrigerant flowing into the heat exchanger 30 is controlled. Note that, although the expansion device 13 is provided in the outdoor unit 10 in the first embodiment, it may be provided in the indoor unit 20, and the installation location is not limited.

[0021] The fan 14 supplies outdoor air to the heat exchanger 30, and the amount of air sent to the heat exchanger 30 is adjusted by controlling the rotation speed.

[0022] The indoor heat exchanger 21 exchanges heat between the indoor air and the refrigerant. During cooling operation, the indoor heat exchanger 21 functions as an evaporator that evaporates the refrigerant and cools the outdoor air with the heat of vaporization. During heating operation, the indoor heat exchanger 21 functions as a condenser that radiates heat of the refrigerant to the outdoor air to condense the refrigerant.

[0023] The indoor fan 22 supplies indoor air to the indoor heat exchanger 21, and the amount of air sent to the indoor heat exchanger 21 is adjusted by controlling the rotation speed.

[0024] Next, the flow of refrigerant during each operation of the air conditioner 100 will be described with reference to FIGS.

[0025] <Heating operation> During heating operation, the flow path switching device 12 is switched to the state shown by the solid line in FIG. 1. Then, the high-temperature, high-pressure gas refrigerant discharged from the compressor 11 flows into the indoor heat exchanger 21 through the flow path switching device 12. The high-temperature, high-pressure gas refrigerant that flows into the indoor heat exchanger 21 exchanges heat with the indoor air taken in by the indoor fan 22 and condenses while releasing heat, heating the indoor air and becoming a low-temperature, high-pressure liquid refrigerant, which flows out of the indoor heat exchanger 21. The low-temperature, high-pressure liquid refrigerant that flows out of the indoor heat exchanger 21 is decompressed by the throttling device 13, becomes a low-temperature, low-pressure two-phase gas-liquid refrigerant, and flows into the heat exchanger 30. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the heat exchanger 30 exchanges heat with the outdoor air taken in by the fan 14, evaporates while absorbing heat, and becomes a low-temperature, low-pressure gas refrigerant, which flows out of the heat exchanger 30. The low-temperature, low-pressure gas refrigerant that flows out of the heat exchanger 30 is sucked into the compressor 11 and becomes a high-temperature, high-pressure gas refrigerant again.

[0026] <Cooling operation> During cooling operation, the flow path switching device 12 is switched to the state shown by the solid line in Fig. 2. Then, the high-temperature, high-pressure gas refrigerant discharged from the compressor 11 flows into the heat exchanger 30 through the flow path switching device 12. The high-temperature, high-pressure gas refrigerant that flows into the heat exchanger 30 exchanges heat with the outdoor air taken in by the fan 14, condenses while releasing heat, and flows out of the heat exchanger 30 as a low-temperature, high-pressure liquid refrigerant. The low-temperature, high-pressure liquid refrigerant that flows out of the heat exchanger 30 is decompressed by the throttling device 13, becomes a low-temperature, low-pressure two-phase gas-liquid refrigerant, and flows into the indoor heat exchanger 21. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the indoor heat exchanger 21 exchanges heat with the indoor air taken in by the indoor fan 22, evaporates while absorbing heat, cools the indoor air, and flows out of the indoor heat exchanger 21 as a low-temperature, low-pressure gas refrigerant. The low-temperature, low-pressure gas refrigerant that flows out of the indoor heat exchanger 21 is drawn into the compressor 11, where it becomes high-temperature, high-pressure gas refrigerant again.

[0027] <Configuration of heat exchanger 30> FIG. 3 is a front view showing a refrigerant flow when the heat exchanger 30 according to the first embodiment functions as a condenser. FIG. 4 is a front view showing a refrigerant flow when the heat exchanger 30 according to the first embodiment functions as an evaporator. FIG. 5 is an enlarged view of the A arrow portion of FIG. 3. FIG. 6 is an enlarged view of the B arrow portion of FIG. 3. FIG. 7 is a view of the CC cross section of FIG. 4 in the direction of the arrow. FIG. 8 is a view of the DD cross section of FIG. 4 in the direction of the arrow. FIG. 9 is a view of the EE cross section of FIG. 4 in the direction of the arrow. FIG. 10 is a view of the FF cross section of FIG. 4 in the direction of the arrow. The white arrows in FIG. 3 indicate the refrigerant flow when the heat exchanger 30 functions as a condenser, and the white arrows in FIG. 4 indicate the refrigerant flow when the heat exchanger 30 functions as an evaporator. The arrows in FIG. 8 and FIG. 9 indicate the refrigerant flow when the heat exchanger 30 functions as an evaporator.

[0028] As shown in Figs. 3 to 6, the heat exchanger 30 includes a plurality of heat transfer tubes 38 and a plurality of fins (not shown). The heat transfer tubes 38 are, for example, flat tubes in which a plurality of flow paths (not shown) through which the refrigerant flows are formed in a row. However, the present invention is not limited thereto, and the heat transfer tubes 38 may be circular tubes or the like. The heat transfer tubes 38 are arranged in parallel in the horizontal direction (left and right direction in Figs. 3 to 6) at intervals so that the wind generated by the fan 14 flows, and the refrigerant flows vertically in the tubes extending in the vertical direction (up and down direction in Figs. 3 to 6). The fins are connected between the adjacent heat transfer tubes 38 and transfer heat to the heat transfer tubes 38. The fins improve the efficiency of heat exchange between the air and the refrigerant, and for example, corrugated fins are used. However, the present invention is not limited thereto. Since heat exchange between the air and the refrigerant occurs on the surface of the heat transfer tubes 38, the fins may not be required.

[0029] A lower header 34 extending in the horizontal direction is provided at the lower ends of the heat transfer tubes 38. The lower ends of the heat transfer tubes 38 are directly inserted into the lower header 34. Furthermore, an upper header 35 extending in the horizontal direction is provided at the upper ends of the heat transfer tubes 38. The upper ends of the heat transfer tubes 38 are directly inserted into the upper header 35.

[0030] The lower header 34 is provided with a first pipe 36 and a second pipe 37, and the heat exchanger 30 is connected to the refrigerant circuit of the air conditioner 100 via the first pipe 36 and the second pipe 37. The first pipe 36 allows high-temperature, high-pressure gas refrigerant from the compressor 11 to flow into the heat exchanger 30 during cooling operation, and allows low-temperature, low-pressure gas refrigerant after heat exchange in the indoor heat exchanger 21 to flow out to the refrigerant circuit during heating operation. The second pipe 37 allows low-temperature, high-pressure liquid refrigerant after heat exchange in the heat exchanger 30 to flow out to the refrigerant circuit during cooling operation, and allows low-temperature, low-pressure gas-liquid two-phase refrigerant after being decompressed by the throttling device 13 to flow into the heat exchanger 30 during heating operation. Hereinafter, the first pipe 36 will also be referred to as an inlet section, and the second pipe 37 will also be referred to as an outlet section.

[0031] The heat transfer tubes 38, the fins, the lower header 34, and the upper header 35 are all made of aluminum, for example, and are joined together by brazing.

[0032] As shown in Figs. 3 to 6, in the heat exchanger 30 according to the first embodiment, a first partition plate 41 and a second partition plate 42 are provided inside the lower header 34 to divide the interior into a plurality of regions in the horizontal direction. Similarly, a first partition plate 41 and a second partition plate 42 are provided inside the upper header 35 to divide the interior into a plurality of regions in the horizontal direction. These first partition plate 41 and second partition plate 42 are provided to divide the interior of the heat exchanger 30 into a plurality of regions in the horizontal direction, and a flow path is formed in each region. The first partition plate 41 is provided to separate adjacent regions, to make the refrigerant flow opposite (turn) in each adjacent region, and to make the refrigerant flow opposite the adjacent region in each region. A recess 41a is formed on both sides or one side of the first partition plate 41 in the horizontal direction. In addition, the second partition plate 42 has an opening 42a that communicates the adjacent regions, and is provided so that the refrigerant flows between the adjacent regions.

[0033] In the first embodiment, two first partition plates 41 are provided in the lower header 34, and one is provided in the upper header 35. Also, one second partition plate 42 is provided in the lower header 34, and two are provided in the upper header 35. Note that the number of first partition plates 41 and second partition plates 42 is not limited to the above, and it is sufficient that at least one is provided in at least one of the lower header 34 and the upper header 35. Note that, hereinafter, the first partition plate 41 and the second partition plate 42 are collectively referred to as partition plate.

[0034] The lower header 34 is partitioned into four regions by the first partition plate 41 and the second partition plate 42, with the lower first regions RL1 and the lower second regions RL2 being formed alternately. The upper header 35 is partitioned into four regions by the first partition plate 41 and the second partition plate 42, with the upper first regions RU1 and the upper second regions RU2 being formed alternately.

[0035] The lower first region RL1 is a region where the refrigerant that has flowed in is distributed to the multiple heat transfer tubes 38 when the heat exchanger 30 functions as a condenser, and is a region where the refrigerant distributed to the multiple heat transfer tubes 38 in the upper second region RU2 joins when the heat exchanger 30 functions as an evaporator. The lower second region RL2 is a region where the refrigerant distributed to the multiple heat transfer tubes 38 in the upper first region RU1 joins when the heat exchanger 30 functions as a condenser, and is a region where the refrigerant is distributed to the multiple heat transfer tubes 38 when the heat exchanger 30 functions as an evaporator. The upper first region RU1 is a region where the refrigerant that has flowed in is distributed to the multiple heat transfer tubes 38 when the heat exchanger 30 functions as a condenser, and is a region where the refrigerant distributed to the multiple heat transfer tubes 38 in the lower second region RL2 joins when the heat exchanger 30 functions as an evaporator. The upper second region RU2 is a region where the refrigerant distributed to the multiple heat transfer tubes 38 in the lower first region RL1 joins together when the heat exchanger 30 functions as a condenser, and is a region that distributes the refrigerant to the multiple heat transfer tubes 38 when the heat exchanger 30 functions as an evaporator.

[0036] As described above, the lower header 34 and the upper header 35 are partitioned into four regions by the first partition plate 41 and the second partition plate 42, but this is not limiting. However, by partitioning the lower header 34 and the upper header 35 into at least three or more regions, the impact of deterioration of the refrigerant distribution performance can be reduced.

[0037] As shown in Figs. 7 and 8, the lower header 34 extends in the horizontal direction (perpendicular to the paper surface of Figs. 7 and 8), has a lower first space SL1 formed therein through which the refrigerant flows, and has a cylindrical outer wall portion 34a in which a plurality of connection ports (not shown) into which the lower ends of the heat transfer tubes 38 are inserted are formed at intervals in the horizontal direction. Here, the lower ends of the heat transfer tubes 38 are inserted into the lower first space SL1. The lower header 34 also has a cylindrical inner wall portion 44 provided in a hollow portion inside the outer wall portion 34a, extends in the horizontal direction, has a circular lower second space SL2 formed therein through which the refrigerant flows, and has a plurality of orifices 45 formed at intervals in the horizontal direction to communicate the lower first space SL1 and the lower second space SL2, which are separated from each other. One horizontal end of the inner wall portion 44 is inserted into the recess 41a of the first partition plate 41, and the other end is inserted into the opening 42a of the second partition plate 42, and is supported by the first partition plate 41 and the second partition plate 42.

[0038] Similarly, as shown in Fig. 9 and Fig. 10, the upper header 35 extends in the horizontal direction (the direction perpendicular to the paper surface of Fig. 9 and Fig. 10), has an upper first space SU1 formed therein through which the refrigerant flows, and has a cylindrical outer wall portion 35a in which a plurality of connection ports (not shown) into which the upper ends of the heat transfer tubes 38 are inserted are formed at intervals in the horizontal direction. Here, the upper ends of the heat transfer tubes 38 are inserted into the upper first space SU1. The upper header 35 also has a cylindrical inner wall portion 44 provided in a hollow portion inside the outer wall portion 35a, extends in the horizontal direction, has a circular upper second space SU2 formed therein through which the refrigerant flows, and has a plurality of orifices 45 formed at intervals in the horizontal direction to communicate between the upper first space SU1 and the upper second space SU2, which are partitioned from each other. As shown in Figures 5 and 6, one horizontal end of this inner wall portion 44 is inserted into the recess 41a of the first partition plate 41 and the other end is inserted into the opening 42a of the second partition plate 42, and is supported by the first partition plate 41 and the second partition plate 42.

[0039] 3, in the lower header 34, of the lower first region RL1 and the lower second region RL2, a lower second space SL2 and a plurality of orifices 45 are provided in only the lower first region RL1 that communicates with the first piping 36. In the upper header 35, of the upper first region RU1 and the upper second region RU2, an upper second space SU2 and a plurality of orifices 45 are provided only in the upper second region RU2.

[0040] FIG. 11 is a view of a first modified example of the DD cross section of FIG. 4 as viewed in the direction of the arrows. FIG. 12 is a view of a first modified example of the EE cross section of FIG. 4 as viewed in the direction of the arrows. FIG. 13 is a view of a second modified example of the DD cross section of FIG. 4 as viewed in the direction of the arrows. FIG. 14 is a view of a second modified example of the EE cross section of FIG. 4 as viewed in the direction of the arrows. FIG. 15 is a view of a third modified example of the DD cross section of FIG. 4 as viewed in the direction of the arrows. FIG. 16 is a view of a third modified example of the EE cross section of FIG. 4 as viewed in the direction of the arrows. The arrows in FIG. 11 to FIG. 16 indicate the flow of refrigerant when the heat exchanger 30 functions as an evaporator.

[0041] The structures of the lower header 34 and the upper header 35 are not limited to the above, and may be, for example, the structures shown in Figs. 11 to 16. As shown in Fig. 11, the lower header 34 extends in the horizontal direction, and includes a cylindrical outer wall portion 34a in which a lower first space SL1 through which a refrigerant flows is formed, and in which a plurality of connection ports (not shown) into which the lower ends of the heat transfer tubes 38 are inserted are formed at intervals in the horizontal direction. Here, the lower ends of the heat transfer tubes 38 are inserted into the lower first space SL1. The lower header 34 includes two plate-like members 46 that extend in the horizontal direction and in the depth direction (left and right direction in Fig. 11) to be connected to the inner wall of the outer wall portion 34a, and have central portions 46a in the depth direction that are semicircular on opposite sides to form a circular lower second space SL2. A plurality of orifices 45 that communicate the lower first space SL1 and the lower second space SL2 are formed at intervals in the horizontal direction in the central portions 46a. Similarly, as shown in Fig. 12, the upper header 35 extends in the horizontal direction, and has a cylindrical outer wall portion 35a in which an upper first space SU1 through which the refrigerant flows is formed, and in which a plurality of connection ports (not shown) into which the upper ends of the heat transfer tubes 38 are inserted are formed at intervals in the horizontal direction. Here, the upper ends of the heat transfer tubes 38 are inserted into the upper first space SU1. The upper header 35 also has two plate-like members 46 that extend in the horizontal direction and in the depth direction (left and right direction in Fig. 12) to be connected to the inner wall of the outer wall portion 35a, and have central portions 46a in the depth direction that are semicircular on opposite sides to form a circular upper second space SU2. A plurality of orifices 45 that communicate the upper first space SU1 and the upper second space SU2 are formed at intervals in the horizontal direction in the central portions 46a.

[0042] As shown in Fig. 13, the lower header 34 extends in the horizontal direction, and includes a cylindrical outer wall portion 34a in which a lower first space SL1 through which the refrigerant flows is formed, and in which a plurality of connection ports (not shown) into which the lower ends of the heat transfer tubes 38 are inserted are formed at intervals in the horizontal direction. Here, the lower ends of the heat transfer tubes 38 are inserted into the lower first space SL1. The lower header 34 includes two plate-like members 46 that extend in the horizontal direction and in the depth direction (left and right direction in Fig. 13) to be connected to the inner wall of the outer wall portion 34a, and have central portions 46a in the depth direction that are semicircular on opposite sides to form a circular lower second space SL2. A plurality of orifices 45 that communicate the lower first space SL1 and the lower second space SL2 are formed at intervals in the horizontal direction in the central portions 46a. Furthermore, a plurality of communication holes 46b are formed at intervals in the horizontal direction on both sides of the center portion 46a of the two plate-like members 46 in the depth direction. In FIG. 13, the lower first space SL1 of the lower header 34 is separated into two spaces, upper and lower, by the two plate-like members 46, but the two spaces, upper and lower, can be communicated by the communication holes 46b formed in the two plate-like members 46, so that the space in the lower header 34 where the refrigerant does not flow can be reduced. Similarly, as shown in FIG. 14, the upper header 35 has a cylindrical outer wall portion 35a that extends in the horizontal direction, has an upper first space SU1 formed therein through which the refrigerant flows, and has a plurality of connection ports (not shown) formed at intervals in the horizontal direction, into which the upper ends of the heat transfer tubes 38 are inserted. Here, the upper ends of the heat transfer tubes 38 are inserted into the upper first space SU1. The upper header 35 extends horizontally and in the depth direction (left and right direction in FIG. 14) to be connected to the inner wall of the outer wall portion 35a, and includes two plate-like members 46 whose depth direction central portions 46a are semicircular on opposite sides to form a circular upper second space SU2. A plurality of orifices 45 that communicate the upper first space SU1 and the upper second space SU2 are formed at intervals in the horizontal direction in the central portions 46a. Furthermore, a plurality of communication holes 46b are formed at intervals in the horizontal direction on both sides in the depth direction of the central portions 46a of the two plate-like members 46.In FIG. 14, the upper first space SU1 of the upper header 35 is separated into two spaces, upper and lower, by the two plate-shaped members 46. However, the two spaces, upper and lower, can be connected by the communication holes 46b formed in the two plate-shaped members 46, thereby reducing the space within the upper header 35 where the refrigerant does not flow.

[0043] As shown in FIG. 15, the lower header 34 extends horizontally, and includes a cylindrical outer wall portion 34a in which a lower first space SL1 is formed in which a refrigerant flows, and in which a plurality of connection ports (not shown) into which the lower ends of the heat transfer tubes 38 are inserted are formed at intervals in the horizontal direction. Here, the lower ends of the heat transfer tubes 38 are inserted into the lower first space SL1. The surface of the outer wall portion 34a opposite to the surface in which the connection ports are formed has a central portion 34b in the depth direction (left and right direction in FIG. 15) formed in a semicircular shape that is recessed inward. The lower header 34 includes a single plate-like member 46 extending horizontally and connected to the outer wall portion 34a so as to cover the central portion 34b of the outer wall portion 34a from the outside, and a central portion 46a in the depth direction formed in a semicircular shape opposite to the central portion 34b of the outer wall portion 34a to form a circular lower second space SL2. A plurality of orifices 45 that communicate the lower first space SL1 and the lower second space SL2 are formed at intervals in the horizontal direction in the central portion 34b of the outer wall portion 34a. Similarly, as shown in Fig. 16, the upper header 35 has a cylindrical outer wall portion 35a that extends in the horizontal direction, has an upper first space SU1 formed therein through which the refrigerant flows, and has a plurality of connection ports (not shown) formed at intervals in the horizontal direction into which the upper ends of the heat transfer tubes 38 are inserted. Here, the upper ends of the heat transfer tubes 38 are inserted into the upper first space SU1. On the surface of the outer wall portion 35a opposite to the surface on which the connection ports are formed, the central portion 35b in the depth direction (left and right direction in Fig. 16) is semicircular so as to be recessed inward. The upper header 35 includes a plate-like member 46 that extends horizontally, is connected to the outer wall portion 35a so as to cover the central portion 35b of the outer wall portion 35a from the outside, and has a central portion 46a in the depth direction that is semicircular on the opposite side to the central portion 35b of the outer wall portion 35a to form a circular upper second space SU2. A plurality of orifices 45 that communicate between the upper first space SU1 and the upper second space SU2 are formed at intervals in the horizontal direction in the central portion 35b of the outer wall portion 35a.

[0044] In the first embodiment and its first to third modifications, the upper second space SU2 and the lower second space SL2 are each formed into a single circular shape as shown in Fig. 8, Fig. 9, and Fig. 11 to Fig. 16, but are not limited thereto and may be separated into a plurality of spaces or may have another shape. In addition, in the case of the structure shown in Fig. 11 to Fig. 16, the inner wall portion 44 is not provided and there is no need to support the end of the inner wall portion 44, so that the recess 41a does not need to be formed in the first partition plate 41 and the second partition plate 42 does not need to be provided.

[0045] As shown in Fig. 3 and Fig. 4, when the heat exchanger 30 functions as a condenser, in the region of the plurality of heat transfer tubes 38 where the refrigerant is an ascending flow, the density of the refrigerant increases while ascending in each heat transfer tube 38, and the refrigerant is further made difficult to ascend due to gravity, resulting in a decrease in condensation performance. Therefore, by providing a plurality of orifices 45 in the region of the lower header 34 where the ascending flow originates (distribution origin), the distribution of the gas-liquid two-phase refrigerant is made uniform (the distribution performance is improved), and the condensation performance is improved (the condensation performance is not decreased). However, since the gas refrigerant flowing in from the first pipe 36 is single-phase, the condensation performance is not decreased even if the plurality of orifices 45 are not provided. Therefore, when the first pipe 36 is provided in the lower header 34, the cost can be reduced by not providing the orifice 45 in the region communicating with the first pipe 36 even in the region of the lower header 34 where the ascending flow originates (distribution origin), and further, the flow resistance increased by providing the orifice 45 can be suppressed, thereby suppressing the decrease in heat exchange performance. Furthermore, when the heat exchanger 30 functions as a condenser, in the region of the multiple heat transfer tubes 38 that forms a downward flow, the refrigerant becomes more likely to descend because the density of the refrigerant increases as it descends within each heat transfer tube 38. Therefore, even if multiple orifices 45 are not provided in the region that is the source (distribution source) of the downward flow of the upper header 35, a decrease in condensation performance does not occur. Thus, by not providing multiple orifices 45 in the region that is the source (distribution source) of the downward flow of the upper header 35, costs can be reduced, and further, by suppressing the flow resistance that increases by providing multiple orifices 45, a decrease in heat exchange performance can be suppressed.

[0046] On the other hand, when the heat exchanger 30 functions as an evaporator, in the region of the plurality of heat transfer tubes 38 that is the upward flow, the density of the refrigerant decreases as it rises in each heat transfer tube 38, but the refrigerant is difficult to rise due to gravity, and the condensation performance decreases. Therefore, by providing the orifice 45 in the region that is the source (distribution source) of the upward flow of the lower header 34, the distribution of the gas-liquid two-phase refrigerant is made uniform (the distribution performance is improved), so the evaporation performance is improved (the evaporation performance does not decrease), and the deterioration of the heat exchange performance can be suppressed. Also, when the heat exchanger 30 functions as an evaporator, in the region of the plurality of heat transfer tubes 38 that is the downward flow, the refrigerant is difficult to fall in each heat transfer tube 38, so the density of the refrigerant decreases as it descends, and the condensation performance decreases. Therefore, by providing the plurality of orifices 45 in the region that is the source (distribution source) of the downward flow of the upper header 35, the distribution of the gas-liquid two-phase refrigerant is made uniform (the distribution performance is improved), so the evaporation performance is improved (the evaporation performance does not decrease), and the deterioration of the heat exchange performance can be suppressed.

[0047] For the above reasons, when the first piping 36 is provided in the lower header 34, as shown in Fig. 3, the lower header 34 has a lower second space SL2 and a plurality of orifices 45 in addition to the lower first region RL1 that communicates with the first piping 36, out of the lower first region RL1 and the lower second region RL2. Moreover, the upper header 35 has an upper second space SU2 and a plurality of orifices 45 only in the upper second region RU2, out of the upper first region RU1 and the upper second region RU2.

[0048] Fig. 17 is a front view showing a refrigerant flow when the modified heat exchanger 30 according to the first embodiment functions as a condenser. Fig. 18 is a front view showing a refrigerant flow when the modified heat exchanger 30 according to the first embodiment functions as an evaporator. The white arrows in Fig. 17 indicate the refrigerant flow when the heat exchanger 30 functions as a condenser, and the white arrows in Fig. 18 indicate the refrigerant flow when the heat exchanger 30 functions as an evaporator.

[0049] In the first embodiment, the first pipe 36 and the second pipe 37 are each provided in the lower header 34, but the present invention is not limited thereto. As shown in FIG. 17 and FIG. 18, the first pipe 36 and the second pipe 37 may each be provided in the upper header 35, or, although not shown, the first pipe 36 may be provided in the lower header 34 and the second pipe 37 may be provided in the upper header 35, or the first pipe 36 may be provided in the upper header 35 and the second pipe 37 may be provided in the lower header 34. That is, the first pipe 36 and the second pipe 37 may be provided in either the lower header 34 or the upper header 35. However, when the inside of the heat exchanger 30 is divided into an odd number of regions, the first pipe 36 and the second pipe 37 are provided in different headers, the lower header 34 and the upper header 35. Furthermore, when the inside of the heat exchanger 30 is divided into an even number of regions, the first pipe 36 and the second pipe 37 are provided in the same header, either the lower header 34 or the upper header 35, respectively.

[0050] 17, when the first piping 36 is provided in the upper header 35, the lower header 34 has a lower second space SL2 and a plurality of orifices 45 in both the lower first region RL1 and the lower second region RL2. Moreover, the upper header 35 has an upper second space SU2 and a plurality of orifices 45 only in the upper second region RU2 out of the upper first region RU1 and the upper second region RU2.

[0051] Fig. 19 is a plan view showing typically the inside of the outdoor unit 10 including the heat exchanger 30 according to embodiment 1. Fig. 20 is a plan view showing typically the inside of a modified example of the outdoor unit 10 including the heat exchanger 30 according to embodiment 1. Note that the white arrows in Fig. 19 and Fig. 20 indicate the flow of air, and the black arrows indicate the flow of refrigerant when the heat exchanger 30 functions as a condenser.

[0052] As shown in FIG. 19, the outdoor unit 10 includes two heat exchangers 30 inside a rectangular housing 15. These two heat exchangers 30 are U-shaped in plan view along three of the four side surfaces of the housing 15, arranged in two rows, and connected to each other by inter-row connection pipes 60. In the first embodiment, the heat exchangers 30 are arranged in two rows, but this is not limited thereto, and one row or three or more rows may be used. Also, as shown in FIG. 20, the heat exchangers 30 are L-shaped in plan view along two of the four side surfaces of the housing 15, arranged in two rows, and connected to each other by inter-row connection pipes 60 may be arranged inside the housing 15 so as to be symmetrical with respect to a line connecting two opposing corners of the housing 15.

[0053] As described above, the heat exchanger 30 according to the first embodiment includes a plurality of heat transfer tubes 38 arranged at intervals in the horizontal direction, an upper header 35 provided above the plurality of heat transfer tubes 38 and having an upper first space SU1 into which the upper ends of the plurality of heat transfer tubes 38 are inserted, a lower header 34 provided below the plurality of heat transfer tubes 38 and having a lower first space SL1 into which the lower ends of the plurality of heat transfer tubes 38 are inserted, an inflow portion provided at one horizontal end of the lower header 34 and into which the refrigerant flows when the lower header 34 functions as a condenser, an outflow portion provided at the other horizontal end of the upper header 35 or the lower header 34 and from which the refrigerant flows out when the lower header 34 functions as a condenser, and a partition plate that divides the interior of at least one of the upper header 35 and the lower header 34 into a plurality of regions in the horizontal direction. The lower header 34 distributes the refrigerant when it functions as a condenser, and a lower first region RL1 that distributes the distributed refrigerant. The upper header 35 has at least one upper first region RU1 which distributes the refrigerant and one upper second region RU2 where the distributed refrigerant join, and of the lower first region RL1 and the lower second region RL2, in addition to the lower first region RL1 which communicates with the inlet portion, has a lower second space SL2 partitioned from the lower first space SL1, and a plurality of orifices 45 formed along the horizontal direction which connect the lower first space SL1 and the lower second space SL2. When functioning as a condenser, the upper header 35 has at least one upper first region RU1 which distributes the refrigerant and an upper second region RU2 where the distributed refrigerant join, and of the upper first region RU1 and the upper second region RU2, only the upper second region RU2 has an upper second space SU2 partitioned from the upper first space SU1, and a plurality of orifices 45 formed along the horizontal direction which connect the upper first space SU1 and the upper second space SU2.

[0054] Moreover, the heat exchanger 30 according to the first embodiment includes a plurality of heat transfer tubes 38 arranged at intervals in the horizontal direction, an upper header 35 provided above the plurality of heat transfer tubes 38 and having an upper first space SU1 into which upper ends of the plurality of heat transfer tubes 38 are inserted, a lower header 34 provided below the plurality of heat transfer tubes 38 and having a lower first space SL1 into which lower ends of the plurality of heat transfer tubes 38 are inserted, an inflow portion provided at one horizontal end of the upper header 35 and into which a refrigerant flows when the upper header 35 functions as a condenser, an outflow portion provided at the other horizontal end of the upper header 35 or the lower header 34 and from which the refrigerant flows out when the upper header 35 functions as a condenser, and a partition plate that divides the interior of at least one of the upper header 35 and the lower header 34 into a plurality of regions in the horizontal direction. The lower header 34 has a lower first region RL that distributes the refrigerant when it functions as a condenser. The upper header 35 has at least one upper first region RU1 which distributes the refrigerant and one upper second region RU2 where the distributed refrigerant join, and of the upper first region RU1 and the upper second region RL2, each of them has a lower second space SL2 partitioned from the lower first space SL1, and a plurality of orifices 45 formed along the horizontal direction that connect the lower first space SL1 and the lower second space SL2. When functioning as a condenser, the upper header 35 has at least one upper first region RU1 which distributes the refrigerant and an upper second region RU2 where the distributed refrigerant join, and of the upper first region RU1 and the upper second region RU2, only the upper second region RU2 has an upper second space SU2 partitioned from the upper first space SU1, and a plurality of orifices 45 formed along the horizontal direction that connect the upper first space SU1 and the upper second space SU2.

[0055] According to the heat exchanger 30 of embodiment 1, by configuring the upper header 35 and the lower header 34 as described above, the refrigerant distribution performance can be improved whether the heat exchanger 30 is functioning in evaporation mode or condensation mode, and a decrease in heat exchange performance can be suppressed.

[0056] Specifically, when the heat exchanger 30 functions as a condenser, the distribution of the two-phase refrigerant is made uniform (the distribution performance is improved) by providing multiple orifices 45 in the lower first region RL1, which is the region that is the source (distribution source) of the upward flow of the lower header 34, and therefore the condensation performance is improved (the condensation performance is not deteriorated). However, since the gas refrigerant flowing in from the first pipe 36 is single-phase, the condensation performance is not deteriorated even if multiple orifices 45 are not provided. Therefore, when the first pipe 36 is provided in the lower header 34, the cost can be reduced by not providing the orifices 45 in the region that communicates with the first pipe 36 even in the lower first region RL1, which is the region that is the source (distribution source) of the upward flow of the lower header 34, and further, the deterioration of the heat exchange performance can be suppressed by suppressing the flow resistance that increases by providing the orifices 45. In addition, when the heat exchanger 30 functions as a condenser, costs can be reduced by not providing multiple orifices 45 in the upper first region RU1, which is the region that is the source (distribution source) of the downward flow of the upper header 35.Furthermore, by suppressing the increased flow resistance that would be caused by providing multiple orifices 45, a decrease in heat exchange performance can be suppressed.

[0057] On the other hand, when the heat exchanger 30 functions as an evaporator, the orifice 45 is provided in the lower second region RL2, which is the region that is the source (distribution source) of the upward flow of the lower header 34, to uniformize the distribution of the two-phase refrigerant (improve the distribution performance), thereby improving the evaporation performance (no decrease in evaporation performance occurs), and suppressing the decrease in heat exchange performance. Also, when the heat exchanger 30 functions as an evaporator, the orifice 45 is provided in the upper second region RU2, which is the region that is the source (distribution source) of the downward flow of the upper header 35, to uniformize the distribution of the two-phase refrigerant (improve the distribution performance), thereby improving the evaporation performance (no decrease in evaporation performance occurs), and suppressing the decrease in heat exchange performance.

[0058] In the heat exchanger 30 according to the first embodiment, the lower header 34 has three or more lower first regions RL1 and lower second regions RL2 in total.

[0059] According to the heat exchanger 30 of the first embodiment, by providing the lower header 34 with a total of three or more lower first regions RL1 and lower second regions RL2, it is possible to reduce the impact of deterioration of the refrigerant distribution performance.

[0060] Moreover, the outdoor unit 10 according to the first embodiment is provided with the above-mentioned heat exchanger 30.

[0061] According to the heat exchanger 30 according to the first embodiment, the same effects as those of the heat exchanger 30 described above can be obtained.

[0062] Moreover, the air-conditioning apparatus 100 according to the first embodiment is equipped with the outdoor unit 10 described above.

[0063] According to the air conditioning apparatus 100 according to the first embodiment, the same effects as those of the heat exchanger 30 described above can be obtained. [Explanation of symbols]

[0064] 10 outdoor unit, 11 compressor, 12 flow path switching device, 13 throttling device, 14 fan, 15 housing, 20 indoor unit, 21 indoor heat exchanger, 22 indoor fan, 30 heat exchanger, 34 lower header, 34a outer wall portion, 34b central portion, 35 upper header, 35a outer wall portion, 35b central portion, 36 first piping, 37 second piping, 38 heat transfer tube, 41 first partition plate, 41a recess, 42 second partition plate, 42a opening, 44 inner wall portion, 45 orifice, 46 plate-shaped member, 46a central portion, 46b communication hole, 50 refrigerant piping, 60 inter-row connection piping, 100 air conditioning device, RL1 lower first region, RL2 lower second region, RU1 upper first region, RU2 upper second region, SL1 Lower first space, SL2 lower second space, SU1 upper first space, SU2 upper second space.

Claims

1. A plurality of heat transfer tubes arranged at intervals in a horizontal direction; an upper header provided on an upper portion of the plurality of heat transfer tubes and having an upper first space into which upper ends of the plurality of heat transfer tubes are inserted; a lower header provided at a lower portion of the plurality of heat transfer tubes and having a lower first space into which lower ends of the plurality of heat transfer tubes are inserted; an inlet portion provided at one end of the lower header in a horizontal direction, into which a refrigerant flows when the lower header functions as a condenser; an outlet portion provided at the other end of the upper header or the lower header in the horizontal direction, from which a refrigerant flows out when the header functions as a condenser; a first partition plate and a second partition plate that divide an interior of at least one of the upper header and the lower header into a plurality of regions in a horizontal direction; The second partition plate has an opening that communicates with adjacent regions, The lower header is When functioning as a condenser, The cooling system includes at least one lower first region that distributes a refrigerant and one lower second region where the distributed refrigerant joins together, and among the lower first region and the lower second region, other than the lower first region that communicates with the inlet portion, A lower second space separated from the lower first space; a plurality of orifices formed along a horizontal direction and communicating the lower first space with the lower second space; The upper header is When functioning as a condenser, The cooling system has at least one upper first region that distributes a refrigerant and one upper second region where the distributed refrigerant joins together, and of the upper first region and the upper second region, only the upper second region is an upper second space partitioned from the upper first space; and a plurality of orifices formed along a horizontal direction to communicate the upper first space with the upper second space. heat exchanger.

2. A plurality of heat transfer tubes arranged at intervals in a horizontal direction; an upper header provided on an upper portion of the plurality of heat transfer tubes and having an upper first space into which upper ends of the plurality of heat transfer tubes are inserted; a lower header provided at a lower portion of the plurality of heat transfer tubes and having a lower first space into which lower ends of the plurality of heat transfer tubes are inserted; an inlet portion provided at one end of the upper header in a horizontal direction, into which a refrigerant flows when the upper header functions as a condenser; an outlet portion provided at the other end of the upper header or the lower header in the horizontal direction, from which a refrigerant flows out when the header functions as a condenser; a first partition plate and a second partition plate that divide an interior of at least one of the upper header and the lower header into a plurality of regions in a horizontal direction; The second partition plate has an opening that communicates with adjacent regions, The lower header is When functioning as a condenser, The cooling system has at least one lower first region that distributes a refrigerant and one lower second region where the distributed refrigerant joins together, and each of the lower first region and the lower second region has: A lower second space separated from the lower first space; a plurality of orifices formed along a horizontal direction and communicating the lower first space with the lower second space; The upper header is When functioning as a condenser, The cooling system has at least one upper first region that distributes a refrigerant and one upper second region where the distributed refrigerant joins together, and of the upper first region and the upper second region, only the upper second region is an upper second space partitioned from the upper first space; and a plurality of orifices formed along a horizontal direction to communicate the upper first space with the upper second space. heat exchanger.

3. The lower header is The lower first region and the lower second region are three or more in total.

3. A heat exchanger according to claim 1 or 2.

4. A heat exchanger according to claim 1 or 2 is provided. outdoor unit.

5. The outdoor unit according to claim 4 is provided Air conditioning equipment.

Images