Patent Application
20230288145
The present invention relates to a heat exchanger.
There is a known heat exchanger that has a structure in which both ends of flat heat transfer tubes having a plurality of flow channels are inserted into and connected to each of two headers and a flow of a refrigerant is branched off and flows from one of the headers to the flat heat transfer tubes and that performs heat exchange between the refrigerant and air (Patent Literatures 1 and 2).
In an air conditioner, a refrigerant that enters a gas phase state from a gas-liquid two-phase state on the way passing through the heat exchanger that is used as an evaporator flows out in an overheated state on an outlet side. The refrigerant that is in the overheated state has a temperature difference ΔT with air that is smaller than that at the time of the gas-liquid two-phase state, so that a heat exchange amount ((=K*ΔT*A, where K denotes a coefficient of overall heat transfer and A denotes a heat transfer area) with air is consequently decreased. Furthermore, in the case where the degree of dryness of a refrigerant at an outlet of the heat exchanger falls below 1.0, an average value of the degree of dryness of the refrigerant passing through the heat exchanger is decreased, as compared to a case in which the degree of dryness of the refrigerant that has passed through the heat exchanger is 1.0. If the average value of the degree of dryness of the refrigerant passing through the heat exchanger is decreased, a flow velocity of the refrigerant is decreased, so that a heat transfer coefficient on the refrigerant side is decreased. If the heat transfer coefficient on the refrigerant side is low, the coefficient of overall heat transfer K between the refrigerant and air is decreased, and thus, the heat exchange amount between the refrigerant and the air is decreased. Accordingly, it is ideal that, when the heat exchanger is used as an evaporator, a refrigerant circulation volume is adjusted such that the degree of dryness of the refrigerant at an outlet of the heat exchanger is just 1.0.
Patent Literature 1: Japanese Laid-open Patent Publication No. 2006-266521
Patent Literature 2: Japanese Laid-open Patent Publication No. 2018-100800
In contrast, when heat exchange is performed between external air and a refrigerant by using the above described heat exchanger, a temperature difference between the air and the flow channel that is located on the upwind side of the flat heat transfer tube is large, and thus, a heat exchange amount is larger than that on the downwind side. Accordingly, when a heat exchanger is used as, for example, an evaporator, only the refrigerant flowing through the flow channel located on the upwind side of the flat heat transfer tube enters a gas phase state, and this gas phase refrigerant may become an overheated state. In contrast, in order to prevent the refrigerant flowing through the flow channel that is located on the upwind side from being evaporated and becoming an overheated state, it is conceivable to allow the refrigerant in which the degree of dryness is low to flow into the flat heat transfer tube. However, the flow channel located on the downwind side of the flat heat transfer tube has a heat exchange amount smaller than that of the flow channel that is located on the upwind side of the flat heat transfer tube. As a result, heat exchange between the air and the refrigerant flowing through the flow channel located on the downwind side of the flat heat transfer tube is insufficient, and thus, the degree of dryness of the refrigerant that has passed through the subject flow channel is lower than 1.0. In this case, as compared to an ideal case in which the refrigerant circulation volume is adjusted such that the degree of dryness of the refrigerant that has passed through the heat exchanger is just 1.0, there is a problem in that the heat exchange amount between the refrigerant and the air is decreased as a result of a decrease in the coefficient of overall heat transfer K between the refrigerant and the air.
Accordingly, the disclosed technology has been conceived in light of the circumstances described above and an object thereof is to provide a heat exchanger that improves a heat exchange amount between air and a refrigerant.
According to an aspect of an embodiment, a heat exchanger includes a plurality of flat heat transfer tubes in each of which a plurality of first flow channels and a plurality of second flow channels are formed in an interior portion of each of the plurality of flat heat transfer tubes, and a header in which an insertion space is formed, wherein the header includes a pipe penetration wall portion through which the plurality of flat heat transfer tubes pass such that the plurality of first flow channels are connected to a first space included in the insertion space and the plurality of second flow channels are connected to a second space included in the insertion space, a convex wall that divides the insertion space into the first space and the second space, and an inlet portion that supplies a refrigerant to the first space such that the refrigerant flows toward an inner wall surface of the pipe penetration wall portion that is in contact with the first space, and the convex wall is away from the pipe penetration wall portion such that a communication path through which the refrigerant flows from the first space to the second space is formed between the convex wall and the pipe penetration wall portion.
The disclosed heat exchanger is able to improve the heat exchange amount between the air and the refrigerant.
In the following, a heat exchanger according to embodiments disclosed in the present invention will be explained in detail with reference to accompanying drawings. Furthermore, the disclosed technology is not limited to the description below. In addition, in the description below, components that are the same as those in the embodiments are assigned the same reference numerals, and overlapping description will be omitted.
A heat exchanger 7 according to a first embodiment is provided in an air conditioning apparatus 1, as illustrated in
The four-way valve 6 is connected to the heat exchanger 7 via a refrigerant pipe 14 and is connected to the indoor unit 3 via a refrigerant pipe 15. The four-way valve 6 is switched to a direction in which the air conditioning apparatus 1 performs a cooling operation (cooling mode) or switched to a direction in which the air conditioning apparatus 1 performs a heating operation (heating mode). The four-way valve 6 performs control such that, in the case where the operation is switched to the cooling mode, the discharge pipe 12 is connected to the refrigerant pipe 14 and the refrigerant pipe 15 is connected to the intake pipe 11. The four-way valve 6 performs control such that, in the case where the operation is switched to the heating mode, the discharge pipe 12 is connected to the refrigerant pipe 15 and the refrigerant pipe 14 is connected to the intake pipe 11. The heat exchanger 7 is connected to the expansion valve 8 via a refrigerant pipe 16. The expansion valve 8 is connected to the indoor unit 3 via a refrigerant pipe 17. The indoor unit 3 includes a heat exchanger 18. The heat exchanger 18 is connected to the four-way valve 6 included in the outdoor unit 2 via the refrigerant pipe 15, and is connected to the expansion valve 8 included in the outdoor unit 2 via the refrigerant pipe 17.
Heat Exchanger 7
Each of the plurality of flat heat transfer tubes 23 is formed in a linear strip shape. The plurality of flat heat transfer tubes 23 are disposed between the header 21 and the header 22 with a predetermined gap in the up-down direction 25. A plurality of straight lines that are along the plurality of respective flat heat transfer tubes 23 are parallel with each other, are perpendicular to the up-down direction 25, are perpendicular to the straight line that is along the header 21, and are perpendicular to the straight line that is along the header 22. One end of each of the plurality of flat heat transfer tubes 23 is bonded to the header 21 and is fixed to the header 21. The other end of each of the plurality of flat heat transfer tubes 23 is bonded to the header 22 and is fixed to the header 22.
Each of the plurality of fins 24 is formed in a flat plate shape. The plurality of fins 24 are disposed so as to be along a plurality of planes that are perpendicular to the plurality of straight lines that are along the plurality of flat heat transfer tubes 23, respectively. The plurality of fins 24 are bonded to the plurality of flat heat transfer tubes 23, respectively, such that the plurality of fins 24 are thermally connected to the plurality of flat heat transfer tubes 23, and are fixed to the plurality of flat heat transfer tubes 23, respectively.
The outdoor unit 2 includes a fan that is not illustrated. The fan is disposed in the interior portion of the outdoor unit 2, and sends external air such that the external air flow through the interior portion of the outdoor unit 2.
Plurality of Flat Heat Transfer Tubes 23
A flat heat transfer tube 31 that is one of the plurality of flat heat transfer tubes 23 is formed in a strip shape that is substantially flat, as illustrated in
Header 21
The first partition member 42 is formed in a circular plate shape, is disposed in the interior portion space 49 so as to be along the plane that is perpendicular to the up-down direction 25, and is fixed to the main body portion 41 by being bonded to the cylindrical member 46. The interior portion space 49 is divided into a refrigerant inflow space 51 and an upper part space 52 as a result of the first partition member 42 being disposed in the interior portion space 49. The refrigerant inflow space 51 is sandwiched between the first partition member 42 and the lower wall member 48. The upper part space 52 is disposed on the upper side of the refrigerant inflow space 51, and is sandwiched between the first partition member 42 and the upper wall member 47. One end of the refrigerant pipe 16 is bonded to the cylindrical member 46 and fixed to the main body portion 41 such that the flow channel that is formed in the interior portion of the refrigerant pipe 16 is connected to the refrigerant inflow space 51.
The second partition member 43 is formed in a substantially rectangular plate shape. The second partition member 43 is disposed in the upper part space 52, and is fixed to the main body portion 41 by being bonded to the cylindrical member 46 and the upper wall member 47. The plane that is along the second partition member 43 is parallel to the up-down direction 25, and is perpendicular to each of the plurality of straight lines that are along the plurality of respective flat heat transfer tubes 23. The upper part space 52 is divided into an insertion space 53 and a circulation space 54 as a result of the second partition member 43 being disposed in the upper part space 52. The plurality of flat heat transfer tubes 23 pass through a pipe penetration wall portion 68 that is in contact with the insertion space 53 and that is included in the cylindrical member 46 such that the end portions of the plurality of flat heat transfer tubes 23 are disposed in the insertion space 53 (see
The third partition member 44 is formed in a substantially rectangular plate shape. The third partition member 44 is disposed in the circulation space 54 so as to be along the plane that is perpendicular to the flow direction 26, and is fixed to the main body portion 41 by being bonded to both of the cylindrical member 46 and the second partition member 43. The circulation space 54 is divided into a first circulation path 56 and a second circulation path 57 as a result of the third partition member 44 being disposed in the circulation space 54. The first circulation path 56 is disposed at a position closer to the downstream side of the flow direction 26 than the second circulation path 57. An upper side communication path 58 is formed in the vicinity of the upper part of the third partition member 44, as a result of an upper end of the third partition member 44 being away from the upper wall member 47. The upper side communication path 58 communicates the upper part of the first circulation path 56 and the upper part of the second circulation path 57. A lower communication path 59 is formed in the vicinity of the lower part of the third partition member 44, as a result of the lower end of the third partition member 44 being away from the first partition member 42. The lower communication path 59 communicates the lower part of the second circulation path 57 and the lower part of the first circulation path 56.
A refrigerant inlet port 60 is formed in the first partition member 42. The refrigerant inlet port 60 is formed at a portion that is in contact with the first circulation path 56 formed in the circulation space 54 in the first partition member 42 and communicates the refrigerant inflow space 51 and the first circulation path 56.
The convex wall 45 is formed in a strip shape. The convex wall 45 is disposed in the insertion space 53 so as to be along the plane that is perpendicular to the flow direction 26, and is fixed to the main body portion 41 by being bonded to the second partition member 43.
An upwind side inner wall surface 64 and a downwind side inner wall surface 65 (inner wall surface) are formed at the pipe penetration wall portion 68 formed in the cylindrical member 46. The upwind side inner wall surface 64 faces the upwind side insertion space 61. The downwind side inner wall surface 65 faces the downwind side insertion space 62. The pipe penetration wall portion 68 is gently bent such that a step is not formed at a boundary between the upwind side inner wall surface 64 and the downwind side inner wall surface 65, that is, the upwind side inner wall surface 64 and the downwind side inner wall surface 65 are smoothly connected. A plurality of refrigerant inlet ports 67 (inlet portion) are formed in the second partition member 43. The plurality of refrigerant inlet ports 67 communicates the first circulation path 56 and the downwind side insertion space 62.
Heating Operation
The air conditioning apparatus 1 performs a heating operation as a result of the four-way valve 6 is switched to the heating mode. The compressor 5 compresses a low pressure gas phase refrigerant that has been supplied from the four-way valve 6, and then, supplies a high pressure gas phase refrigerant that has been generated as a result of the low pressure gas phase refrigerant being compressed to the four-way valve 6 (see
The heat exchanger 7 supplies, to the refrigerant inflow space 51, the gas-liquid two-phase refrigerant that has been supplied from the expansion valve 8 (see
The gas-liquid two-phase refrigerant that is present in the first circulation path 56 is supplied to the downwind side insertion space 62 formed in the insertion space 53 via each of the plurality of refrigerant inlet ports 67 formed in the second partition member 43. The gas-liquid two-phase refrigerant supplied to the downwind side insertion space 62 becomes a jet stream as a result of passing through the plurality of refrigerant inlet ports 67, flows toward the downwind side inner wall surface 65 of the cylindrical member 46, comes into collision with the downwind side inner wall surface 65. A large amount of liquid refrigerant out of the gas-liquid two-phase refrigerant that has come into collision with the upwind side inner wall surface 64 adheres to the downwind side inner wall surface 65, and the large amount of the gas refrigerant flows into the plurality of downwind side flow channels 35. That is, the gas-liquid two-phase refrigerant is separated into a liquid refrigerant and a gas refrigerant. As a result of the liquid refrigerant adhered to the downwind side inner wall surface 65 being pushed by the gas-liquid two-phase refrigerant that flows from the plurality of refrigerant inlet ports 67 toward the upwind side inner wall surface 64, the liquid refrigerant moves along the pipe penetration wall portion 68 of the cylindrical member 46, and is supplied to the upwind side insertion space 61 via the communication path 63. The flow of the gas refrigerant into the upwind side insertion space 61 is blocked by the convex wall 45. As a result, a proportion of the liquid refrigerant in the gas-liquid two-phase refrigerant that is present in the upwind side insertion space 61 is larger than a proportion of the liquid refrigerant in the gas-liquid two-phase refrigerant that is present in the downwind side insertion space 62. Furthermore, the gas-liquid two-phase refrigerant exhibits a substantially similar behavior as a case in which the up-down direction 25 is parallel to the vertical direction even when the up-down direction 25 at the time of installation is slightly inclined with respect to the vertical direction, and a proportion of the liquid refrigerant that is present in the upwind side insertion space 61 is larger than a proportion of the liquid refrigerant that is present in the downwind side insertion space 62.
A part of the liquid refrigerant that is present in the insertion space 53 descends the insertion space 53 caused by gravity, and is retained in the lower part of the insertion space 53. The liquid refrigerant retained in the lower part of the insertion space 53 is supplied to the lower part of the second circulation path 57 via the lower communication path 55. The liquid refrigerant supplied to the lower part of the second circulation path 57 is supplied to the lower part of the first circulation path 56 via the lower communication path 59. The liquid refrigerant supplied to the lower part of the first circulation path 56 is pushed up by the gas-liquid two-phase refrigerant that is supplied to the first circulation path 56 via the refrigerant inlet port 60 and ascends the first circulation path 56 together with the gas-liquid two-phase refrigerant that ascends the first circulation path 56. That is, the gas-liquid two-phase refrigerant supplied to the circulation space 54 at the time of the heating operation ascends the first circulation path 56, and circulates through the circulation space 54 as a result of the gas-liquid two-phase refrigerant descending the second circulation path 57.
The gas-liquid two-phase refrigerant that is present in the upwind side insertion space 61 flows into the plurality of upwind side flow channels 34 formed in the plurality of flat heat transfer tubes 23, respectively, and flows through the plurality of upwind side flow channels 34. The gas-liquid two-phase refrigerant that is present in the downwind side insertion space 62 flows into the plurality of downwind side flow channels 35 formed in the plurality of flat heat transfer tubes 23 and flows through the plurality of downwind side flow channels 35. The gas-liquid two-phase refrigerant flowing through the plurality of upwind side flow channels 34 and the plurality of downwind side flow channels 35 absorbs heat as a result of performing heat exchange with the air flowing outside the plurality of flat heat transfer tubes 23, and changes its state to the low pressure gas phase refrigerant that is in an overheated state. That is, the heat exchanger 7 functions as an evaporator, performs heat exchange between the gas-liquid two-phase refrigerant supplied from the expansion valve 8 and the outside air, and supplies, to the four-way valve 6, the low pressure gas phase refrigerant that is in the overheated state and that has been generated as a result of the gas-liquid two-phase refrigerant absorbing heat. The four-way valve 6 supplies the low pressure gas phase refrigerant supplied from the heat exchanger 7 to the compressor 5.
The mass flow rate of the gas-liquid two-phase refrigerant flowing through the plurality of upwind side flow channels 34 formed in the plurality of flat heat transfer tubes 23 is higher than the mass flow rate of the gas-liquid two-phase refrigerant flowing through the plurality of downwind side flow channels 35 because a proportion of the liquid refrigerant that is present in the upwind side insertion space 61 is higher than a proportion of the liquid refrigerant that is present in the downwind side insertion space 62. The air that is subjected to heat exchange with the refrigerant flowing through the plurality of downwind side flow channels 35 is the air that has been subjected to heat exchange with the refrigerant that flows through the plurality of upwind side flow channels 34. As a result, a temperature difference between the refrigerant flowing through the plurality of upwind side flow channels 34 and the air is larger than a temperature difference between the refrigerant flowing through the plurality of downwind side flow channels 35 and the air. As a result, an amount of heat transferred from the air to the gas-liquid two-phase refrigerant flowing through the plurality of upwind side flow channels 34 is greater than an amount of heat transferred from the air to the gas-liquid two-phase refrigerant flowing through the plurality of downwind side flow channels 35. That is, a relatively large amount heat is transferred to a relatively large amount of gas-liquid two-phase refrigerant flowing through the plurality of upwind side flow channels 34, and a relatively small amount of heat is transferred to a relatively small amount of gas-liquid two-phase refrigerant flowing through the plurality of downwind side flow channels 35. As a result, the heat exchanger 7 is able to make the degree of dryness of the refrigerant that has passed through the plurality of upwind side flow channels 34 and the plurality of downwind side flow channels 35 formed in the plurality of flat heat transfer tubes 23 uniform. As a result, when the heat exchanger 7 is used as an evaporator, it is possible to allow the degree of dryness of the refrigerant that has passed through the heat exchanger 7 and that is present on the outlet side of the heat exchanger 7 to be about 1.0, which is an ideal state.
In a heat exchanger that is used in a comparative example and in which a refrigerant equally flows through the plurality of flow channels 33, after the entire of the liquid refrigerant out of the gas-liquid two-phase refrigerant flowing through the plurality of upwind side flow channels 34 has been evaporated, the gas refrigerant is overheated caused by heat being transferred from air to the evaporated gas refrigerant. In the heat exchanger used in the comparative example, furthermore, the liquid refrigerant out of the gas-liquid two-phase refrigerant flowing through the plurality of downwind side flow channels 35 is not sufficiently subjected to heat exchange with the air and is not completely evaporated. In this case, as compared to a case in which the liquid refrigerant has been completely evaporated, a heat exchange amount between the air and the refrigerant is small. In contrast, the heat exchanger 7 is able to prevent the gas refrigerant from being overheated by making the degree of dryness of the refrigerant that has passed through the plurality of upwind side flow channels 34 and the plurality of downwind side flow channels 35 formed in the plurality of flat heat transfer tubes 23 uniform. As a result, in a case in which the heat exchanger 7 is used as an evaporator, it is possible to allow the degree of dryness of the refrigerant that has passed through the heat exchanger 7 to be about 1.0, which is an ideal state.
Furthermore, in the present embodiment, the refrigerant inlet port 60 is formed at a portion that is communicated with the first circulation path 56 formed in the circulation space 54 in the first partition member 42; however, the refrigerant inlet port 60 may be formed at a portion that is in contact with the second circulation path 57. In this case, the gas-liquid two-phase refrigerant supplied to the refrigerant inflow space 51 is supplied to the lower part of the second circulation path 57 via the refrigerant inlet port 60 formed in the first partition member 42. After that, the gas-liquid two-phase refrigerant ascends the second circulation path 57, and then, descends the first circulation path 56.
Cooling Operation
The air conditioning apparatus 1 performs a cooling operation as a result of the four-way valve 6 being switched to a cooling mode. The compressor 5 compresses the low pressure gas phase refrigerant supplied from the four-way valve 6, and supplies, to the four-way valve 6, the high pressure gas phase refrigerant that has been generated as a result of the low pressure gas phase refrigerant being compressed (see
The expansion valve 8 expands the high pressure liquid phase refrigerant supplied from the heat exchanger 7, and supplies, to the heat exchanger 18, the low pressure gas-liquid two-phase refrigerant that is in a state in which the degree of humidity is high and that is generated as a result of the high pressure liquid phase refrigerant being expanded. The heat exchanger 18 functions as an evaporator, cools the air in the room by performing heat exchange between the low pressure gas-liquid two-phase refrigerant supplied from the expansion valve 8 and the air in the room, and supplies, to the four-way valve 6 included in the outdoor unit 2, the low pressure gas phase refrigerant that is in an overheated state and that is generated as a result of the low pressure gas-liquid two-phase refrigerant absorbing heat. The four-way valve 6 supplies, to the compressor 5 the low pressure gas phase refrigerant supplied from the heat exchanger 18.
In the heat exchanger 7, the plurality of flat heat transfer tubes 23 are away from the convex wall 45. As a result, the plurality of flat heat transfer tubes 23 do not interfere with the convex wall 45, so that it is possible to prevent some of the flow channels 33 formed in each of the plurality of flat heat transfer tubes 23 from being crushed, and it is possible to appropriately and reliably allow the refrigerant to flow through the plurality of flat heat transfer tubes 23.
Effects of Heat Exchanger 7 According to First Embodiment
The heat exchanger 7 according to the first embodiment includes the plurality of flat heat transfer tubes 23 and the header 21. The plurality of downwind side flow channels 35 and the plurality of upwind side flow channels 34 are formed in each of the interior portions of the plurality of flat heat transfer tubes 23. The insertion space 53 is formed in an interior portion of the header 21. The header 21 further includes the pipe penetration wall portion 68, the convex wall 45, and the plurality of refrigerant inlet ports 67. The plurality of flat heat transfer tubes 23 pass through the pipe penetration wall portion 68 such that the plurality of downwind side flow channels 35 are connected to the downwind side insertion space 62 formed in the insertion space 53, and, also, such that the plurality of upwind side flow channels 34 are connected to the upwind side insertion space 61 formed in the insertion space 53. The convex wall 45 divides the insertion space 53 into the downwind side insertion space 62 and the upwind side insertion space 61. The plurality of refrigerant inlet ports 67 supplies the refrigerant to the downwind side insertion space 62 such that the refrigerant flows toward the downwind side inner wall surface 65 that is in contact with the downwind side insertion space 62 and that is included in the pipe penetration wall portion 68. At this time, the convex wall 45 is away from the pipe penetration wall portion 68 such that the communication path 63 through which the refrigerant flows from the downwind side insertion space 62 toward the upwind side insertion space 61 is formed between the convex wall 45 and the pipe penetration wall portion 68.
The heat exchanger 7 according to the first embodiment is able to allow the gas-liquid two-phase refrigerant that is supplied from the plurality of refrigerant inlet ports 67 to the downwind side insertion space 62 to come into collision with the downwind side inner wall surface 65, and is thus able to allow the gas-liquid two-phase refrigerant to be divided into the liquid refrigerant and the gas refrigerant. The convex wall 45 is able to prevent the gas refrigerant from flowing from the downwind side insertion space 62 to the upwind side insertion space 61, and is able to prevent the liquid refrigerant from flowing from the upwind side insertion space 61 to the downwind side insertion space 62. The heat exchanger 7 is able to allow a proportion of the liquid refrigerant in the gas-liquid two-phase refrigerant that is present in the downwind side insertion space 62 to be larger than a proportion of the liquid refrigerant in the gas-liquid two-phase refrigerant that is present in the upwind side insertion space 61. The heat exchanger 7 is able to allow the flow rate of the refrigerant flowing through the plurality of upwind side flow channels 34 formed in the plurality of flat heat transfer tubes 23 to be larger than the flow rate of the refrigerant flowing through the plurality of downwind side flow channels 35. The heat exchanger 7 is able to improve the heat exchange amount between the air and the refrigerant in the case where the heat exchanger 7 is used as an evaporator and the plurality of upwind side flow channels 34 is disposed on the upwind side.
Furthermore, the plurality of refrigerant inlet ports 67 included in the heat exchanger 7 according to the first embodiment is formed in an area which the downwind side inner wall surface 65 faces. At this time, the heat exchanger 7 according to the first embodiment is able to appropriately allow the gas-liquid two-phase refrigerant supplied from the plurality of refrigerant inlet ports 67 to the downwind side insertion space 62 to come into collision with the pipe penetration wall portion 68, and is able to appropriately separate the gas-liquid two-phase refrigerant into the liquid refrigerant and the gas refrigerant. As a result, the heat exchanger 7 is able to allow the flow rate of the gas-liquid two-phase refrigerant flowing through the plurality of upwind side flow channels 34 formed in the plurality of flat heat transfer tubes 23 to be larger than the flow rate of the gas-liquid two-phase refrigerant flowing through the plurality of downwind side flow channels 35, and is able to improve the heat exchange amount between the air and the refrigerant.
A heat exchanger according to a second embodiment has a configuration in which, as illustrated in
The heat exchanger according to the second embodiment includes, as illustrated in
As a result of the convex wall 71 being disposed in the insertion space 53, an insertion space 75-1 included in the plurality of insertion spaces 75 is divided into, as illustrated in
In the case where the heat exchanger according to the second embodiment is used as an evaporator, a gas-liquid two-phase refrigerant is supplied to the refrigerant inflow space 51 via the refrigerant pipe 16. The gas-liquid two-phase refrigerant supplied to the refrigerant inflow space 51 is supplied to the lower part of the first circulation path 56 formed in the circulation space 54 via the refrigerant inlet port 60, ascends the first circulation path 56, similarly to the case of heat exchanger 7 according to the first embodiment, and descends the second circulation path 57, thus circulating the circulation space 54.
The gas-liquid two-phase refrigerant that is present in the first circulation path 56 is supplied to the downwind side insertion space 77 formed in each of the plurality of insertion spaces 75 via the plurality of refrigerant inlet ports 67 formed in the second partition member 43. The gas-liquid two-phase refrigerant supplied to the downwind side insertion space 77 becomes a jet stream as a result of passing through the plurality of refrigerant inlet ports 67, flows toward the downwind side inner wall surface 65 of the cylindrical member 46, and comes into collision with the downwind side inner wall surface 65. A large amount of liquid refrigerant out of the gas-liquid two-phase refrigerant that has come into collision with the upwind side inner wall surface 64 adheres to the downwind side inner wall surface 65, and a large amount of the gas refrigerant flows into the plurality of downwind side flow channels 35. That is, the gas-liquid two-phase refrigerant is separated into a liquid refrigerant and a gas refrigerant. As a result of the liquid refrigerant adhered to the downwind side inner wall surface 65 being pushed by the gas-liquid two-phase refrigerant that is supplied from the plurality of refrigerant inlet ports 67 to the downwind side insertion space 77, the liquid refrigerant moves along the pipe penetration wall portion 68 formed in the cylindrical member 46, and is supplied to the upwind side insertion space 76 via the communication path 63. The flow of the gas refrigerant into the upwind side insertion space 76 is blocked by the convex wall 71. As a result, a proportion of the liquid refrigerant in the gas-liquid two-phase refrigerant that is present in the upwind side insertion space 76 is larger than a proportion of the liquid refrigerant in the gas-liquid two-phase refrigerant that is present in the downwind side insertion space 77.
The gas-liquid two-phase refrigerant that is present in the upwind side insertion space 76 flows into the plurality of upwind side flow channels 34 formed in the plurality of flat heat transfer tubes 23, respectively, and flows through the plurality of upwind side flow channels 34. The gas-liquid two-phase refrigerant that is present in the downwind side insertion space 77 flows into the plurality of downwind side flow channels 35 formed in the plurality of flat heat transfer tubes 23, respectively, and flows through the plurality of downwind side flow channels 35. The gas-liquid two-phase refrigerant flowing through the plurality of upwind side flow channels 34 and the plurality of downwind side flow channels 35 absorbs heat as a result of performing heat exchange with the air flowing outside the plurality of flat heat transfer tubes 23, changes its state to the low pressure gas phase refrigerant that is in an overheated state, is supplied to the header 22, and is supplied to the refrigerant pipe 14 via the header 22.
The distance (d1) between the convex wall 71 and the cylindrical member 46 formed in the heat exchanger according to the second embodiment is smaller than the distance between the convex wall 45 and the cylindrical member 46 formed in the heat exchanger 7 according to the first embodiment described above. The liquid refrigerant that has come into collision with the downwind side inner wall surface 65 and that is then separated is distributed along the pipe penetration wall portion 68 in a membranous manner. As the distance d1 between the edge 72 of the convex wall 71 and the pipe penetration wall portion 68 is made small, the distance between the edge 72 of the convex wall 71 and the membrane surface of the liquid refrigerant that is not illustrated becomes small. The distance described here indicates a width of the flow channel in the communication path 63 in which the gas refrigerant flows, and as the distance is smaller, an amount of the gas refrigerant that is supplied from the downwind side insertion space 77 to the upwind side insertion space 76 via the communication path 78 is decreased. Accordingly, the heat exchanger according to the second embodiment is able to reduce an amount of the gas refrigerant that is supplied from the downwind side insertion space 77 to the upwind side insertion space 76 via the communication path 78 as compared to the heat exchanger 7 according to the first embodiment. Furthermore, as a result of a reduction in the distance between the edge 72 of the convex wall 71 and the membrane surface of the liquid refrigerant that is not illustrated, an amount of the liquid refrigerant that flows, in the opposite direction, from the upwind side insertion space 76 to the downwind side insertion space 77 via the communication path 78 is reduced, so that, when compared to the heat exchanger 7 according to the first embodiment described above, the heat exchanger according to the second embodiment is able to reduce the amount of the liquid refrigerant that is supplied from the upwind side insertion space 76 to the downwind side insertion space 77 via the communication path 78. As a result, the heat exchanger according to the second embodiment is able to allow a proportion of the liquid refrigerant included in the gas-liquid two-phase refrigerant that is supplied to the plurality of upwind side flow channels 34 formed in the plurality of flat heat transfer tubes 23 to be larger than a proportion of the liquid refrigerant included in the gas-liquid two-phase refrigerant supplied to the plurality of downwind side flow channels 35.
The plurality of refrigerant inlet ports 67 do not face the end portion of the plurality of flat heat transfer tubes 23, respectively, so that the heat exchanger according to the second embodiment is able to prevent the gas-liquid two-phase refrigerant that is supplied to the downwind side insertion space 77 via the plurality of refrigerant inlet ports 67 from coming into collision with the end portion of the plurality of flat heat transfer tubes 23. As a result of the gas-liquid two-phase refrigerant being prevented from coming into contract with end portion of the plurality of flat heat transfer tubes 23, the heat exchanger according to the second embodiment is able to prevent the liquid refrigerant included in the gas-liquid two-phase refrigerant supplied from the plurality of refrigerant inlet ports 67 to the downwind side insertion space 77 from directly flowing into the plurality of downwind side flow channels 35 formed in the plurality of flat heat transfer tubes 23 without coming into collision with the downwind side inner wall surface 65. That is, the heat exchanger according to the second embodiment is able to further reduce the proportion of the liquid refrigerant included in the gas-liquid two-phase refrigerant supplied to the plurality of downwind side flow channels 35. As a result, the heat exchanger according to the second embodiment is able to further allow a proportion of the liquid refrigerant included in the gas-liquid two-phase refrigerant supplied to the plurality of upwind side flow channels 34 formed in the plurality of flat heat transfer tubes 23 to be larger than a proportion of the liquid refrigerant included in the gas-liquid two-phase refrigerant supplied to the plurality of downwind side flow channels 35. The heat exchanger according to the second embodiment is able to improve the heat exchange amount between the air and the gas-liquid two-phase refrigerant as a result of the proportion of the liquid refrigerant in the gas-liquid two-phase refrigerant supplied to the plurality of upwind side flow channels 34 being larger than the proportion of the liquid refrigerant in the gas-liquid two-phase refrigerant supplied to the plurality of downwind side flow channels 35.
In the case where the heat exchanger according to the second embodiment is used as a condenser, the high pressure gas phase refrigerant is supplied to the interior portion space of the header 22 via the refrigerant pipe 14. The high pressure gas phase refrigerant supplied to the interior portion space formed in the header 22 is substantially equally branched off and flows into the plurality of flow channels 33 formed in the plurality of flat heat transfer tubes 23. The gas refrigerant flowing through the plurality of flow channels 33 changes its state to a high pressure liquid phase refrigerant that is in a supercooled state as a result of performing heat exchange with the air flowing outside the plurality of flat heat transfer tubes 23. The high pressure liquid phase refrigerant flowing through the plurality of flow channels 33 is supplied to the plurality of insertion spaces 75 formed in the header 21. The high pressure liquid phase refrigerant supplied to the plurality of insertion spaces 75 is retained in the lower part of the plurality of insertion spaces 75. The high pressure liquid phase refrigerant retained in the lower part of the plurality of insertion spaces 75 is supplied to the first circulation path 56 via the plurality of refrigerant inlet ports 67, descends the first circulation path 56, and is retained in the lower part of the first circulation path 56. The high pressure liquid phase refrigerant retained in the lower part of the first circulation path 56 is supplied to the refrigerant inflow space 51 via the refrigerant inlet port 60 and supplied to the refrigerant pipe 16.
Similarly to the heat exchanger 7 according to the first embodiment described above, the heat exchanger according to the second embodiment is able to be appropriately used as a condenser. Furthermore, the plurality of refrigerant inlet ports 67 are formed at the lower parts of the plurality of insertion spaces 75, respectively, the heat exchanger according to the second embodiment is further able to appropriately supply the high pressure liquid phase refrigerant that is retained in each of the lower parts of the plurality of insertion spaces 75 to the first circulation path 56. As a result, even if the plurality of insertion spaces are formed, the heat exchanger according to the second embodiment is able to reduce the amount of the high pressure liquid phase refrigerant retained in each of the lower parts of the plurality of insertion spaces 75 and is able to appropriately supply the high pressure liquid phase refrigerant to the expansion valve 8 in the case where the heat exchanger is used as a condenser.
Incidentally, the plurality of refrigerant inlet ports 67 included in the heat exchanger according to the second embodiment is formed such that the plurality of refrigerant inlet ports 67 do not face the end portions of the plurality of flat heat transfer tubes 23, respectively; however, the plurality of refrigerant inlet ports 67 may face the end portions of the plurality of flat heat transfer tubes 23. Even if the plurality of refrigerant inlet ports 67 face the end portions of the plurality of flat heat transfer tubes 23, respectively, the heat exchanger according to the second embodiment is able to further allow the mass flow rate of the refrigerant flowing through the plurality of upwind side flow channels 34 to be larger than the mass flow rate of the refrigerant flowing through the plurality of downwind side flow channels 35 in the case where the heat exchanger according to the second embodiment is used as an evaporator. As a result, the heat exchanger according to the second embodiment is able to improve the heat exchange amount between the air and the gas-liquid two-phase refrigerant.
As illustrated in
The convex wall 83 is formed in a substantially strip shape.
As illustrated in
The flow divider 81 is connected to the refrigerant pipe 16 and is connected to one end of a plurality of refrigerant pipes 92. The other end of each of the plurality of refrigerant pipes 92 is connected to the plurality of respective insertion spaces 84. As illustrated in
In the case where the heat exchanger according to the third embodiment is used as an evaporator, a gas-liquid two-phase refrigerant is supplied to the flow divider 81 via the refrigerant pipe 16. The flow divider 81 is, for example, a distributor, branches off the gas-liquid two-phase refrigerant supplied via the refrigerant pipe 16 so as to have substantially the same degree of dryness, and supplies, to the downwind side insertion space 87 of each of the plurality of insertion spaces 84, the gas-liquid two-phase refrigerants having substantially the same degree of dryness via the plurality of refrigerant pipes 92, respectively. The gas-liquid two-phase refrigerant supplied to the downwind side insertion space 87 formed in the insertion space 85 becomes a jet stream as a result of passing through the plurality of refrigerant inlet ports 67, flows toward the downwind side inner wall surface 65 of the cylindrical member 46, and comes into collision with the downwind side inner wall surface 65. A large amount of a liquid refrigerant out of the gas-liquid two-phase refrigerant that has come into collision with the upwind side inner wall surface 64 adheres to the downwind side inner wall surface 65, and a large amount of gas refrigerant flows in the plurality of downwind side flow channels 35. That is, the gas-liquid two-phase refrigerant is separated into a liquid refrigerant and a gas refrigerant. As a result of the liquid refrigerant adhered to the downwind side inner wall surface 65 being pushed by the gas-liquid two-phase refrigerant that is supplied from the refrigerant pipe 93 to the downwind side insertion space 87, the liquid refrigerant moves along the pipe penetration wall portion 68 of the cylindrical member 46, and is supplied to the upwind side insertion space 86 via the communication path 89. The flow of the gas refrigerant into the upwind side insertion space 86 is blocked by the convex wall 83. As a result, a proportion of the liquid refrigerant in the gas-liquid two-phase refrigerant that is present in the upwind side insertion space 86 is larger than a proportion of the liquid refrigerant in the gas-liquid two-phase refrigerant that is present in the downwind side insertion space 87.
The gas-liquid two-phase refrigerant that is present in the upwind side insertion space 86 flows into the plurality of upwind side flow channels 34 formed in the plurality of flat heat transfer tubes 23, respectively, and flows through the plurality of upwind side flow channels 34. The gas-liquid two-phase refrigerant that is present in the downwind side insertion space 87 flows into the plurality of downwind side flow channels 35 formed in the plurality of flat heat transfer tubes 23, respectively, and flows through the plurality of downwind side flow channels 35. The gas-liquid two-phase refrigerant flowing through the plurality of upwind side flow channels 34 and the plurality of downwind side flow channels 35 absorbs heat as a result of performing heat exchange with the air flowing outside the plurality of flat heat transfer tubes 23, changes its state to the low pressure gas phase refrigerant that is in an overheated state, is supplied to the header 22, and is supplied to the refrigerant pipe 14 via the header 22.
similarly to the above described heat exchanger according to the second embodiment, when the heat exchanger according to the third embodiment is used as an evaporator, the heat exchanger according to the third embodiment is able to allow the mass flow rate of the gas-liquid two-phase refrigerant supplied to the plurality of upwind side flow channels 34 formed in the plurality of flat heat transfer tubes 23 to be larger than the mass flow rate of the gas-liquid two-phase refrigerant supplied to the plurality of downwind side flow channels 35. As a result, the heat exchanger according to the third embodiment is able to improve the heat exchange amount between the air and the gas-liquid two-phase refrigerant.
In the case where the heat exchanger according to the third embodiment is used as a condenser, the high pressure gas phase refrigerant is supplied to the interior portion space of the header 22 via the refrigerant pipe 14. The high pressure gas phase refrigerant supplied to the interior portion space of the header 22 is substantially equally branched off and flows into the plurality of flow channels 33 formed in the plurality of flat heat transfer tubes 23. The gas refrigerant flowing into the plurality of flow channels 33 changes its state to the high pressure liquid phase refrigerant that is in a supercooled state as a result of performing heat exchange with the air flowing outside the plurality of flat heat transfer tubes 23. The high pressure liquid phase refrigerant flowing through the plurality of flow channels 33 is supplied to each of the plurality of insertion spaces 84 formed in the header 80. The high pressure liquid phase refrigerant supplied to the plurality of insertion spaces 84 is supplied to the flow divider 81 via the plurality of refrigerant pipes 92, and is supplied to the refrigerant pipe 16. In this way, similarly to the heat exchanger according to the heat exchanger according to the first and the second embodiment as described above, the heat exchanger according to the third embodiment is able to be appropriately used as a condenser.
Incidentally, the plurality of upwind side flow channels 34 and the plurality of downwind side flow channels 35 formed in the flat heat transfer tube 31 are divided at the center 36 of the end surface of the flat heat transfer tube 31, but may be divided at another position that is different from the center 36 of the end surface of the flat heat transfer tube 31. In this case, also, when the heat exchanger is used as an evaporator, the heat exchanger is able to allow the mass flow rate of the plurality of upwind side flow channels 34 to be larger than the mass flow rate of the plurality of downwind side flow channels 35, and is thus able to improve the heat exchange amount between the refrigerant.
As described above, the embodiment has been described; however, the embodiment is not limited by the described content. Furthermore, the components described above includes one that can easily be thought of by those skilled in the art, one that is substantially the same, one that is within the so-called equivalents. In addition, the components described above may also be appropriately used in combination. In addition, at least one of various omissions, replacements, and modifications of components may be made without departing from the scope of the embodiment.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2020-131928 | Aug 2020 | JP | national |
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2021/028276 | 7/30/2021 | WO |
