Diverters and air conditioners

Abstract

To provide a shunt that can suppress variations in the ratio of liquefied refrigerant and gasified refrigerant in refrigerants that have been distributed to a plurality of pipes.SOLUTION: A shunt according to an embodiment comprises a first cylinder part, a second cylinder part, two guides, and a bulkhead. The first cylinder part is connected to a first pipe, is provided with a first flow passage extending in a first direction therein, and has an internal peripheral surface surrounding the first flow passage. The second cylinder part is connected to a plurality of second pipes and is provided with a second flow passage therein. The guides are arranged in the first flow passage so as to form a clearance from the internal peripheral surface and are separated from each other on the side opposite to the clearance. The bulkhead separates the first flow passage and the second flow passage and is separated from the guides. A through hole that connects the first flow passage with the second flow passage is open at a position opposing a clearance between the two guides.SELECTED DRAWING: Figure 3

Description

[Technical Field]

[0001] Embodiments of the present invention relate to a flow divider and an air conditioner. [Background Art]

[0002] In an air conditioner such as an air conditioner, a refrigerant circulates through a refrigeration cycle. Conventionally, there has been known an air conditioner including a flow divider that branches a pipe through which a refrigerant flows. The refrigerant is distributed to a plurality of pipes branched from the flow divider, and supplied to, for example, a heat exchanger. [Prior Art Literature] [Patent Literature]

[0003] [Patent Literature 1] Japanese Unexamined Patent Application Publication No. 2001-059662 [Summary of the Invention] [Problem to be Solved by the Invention]

[0004] When the refrigerant flowing into the flow divider is a gas-liquid two-phase flow, the ratio of liquid refrigerant to gaseous refrigerant may differ among the refrigerants distributed to the plurality of pipes branched from the flow divider. That is, the ratio of liquid refrigerant to gaseous refrigerant in each of the plurality of pipes deviates from a desired ratio, which may reduce the heat exchange efficiency of the heat exchanger.

[0005] An example of the problem to be solved by the present invention is to provide a flow divider and an air conditioner that can suppress the variation in the ratio of liquid refrigerant to gaseous refrigerant among refrigerants distributed to a plurality of pipes. [Means for Solving the Problem]

[0006] A flow divider according to one embodiment of the present invention comprises a first cylindrical section, a second cylindrical section, two guides, and a partition wall. The first cylindrical section is configured to be connected to a first pipe and has a first flow path extending in a first direction inside, and an inner circumferential surface surrounding the first flow path. The second cylindrical section is configured to be connected to a plurality of second pipes and has a second flow path inside. The two guides are positioned in the first flow path such that they form a gap with the inner circumferential surface, and are spaced apart from each other on the opposite side of the gap. The partition wall separates the first flow path and the second flow path, is spaced apart from the two guides, and has a through hole connecting the first flow path and the second flow path opening between the two guides. The partition wall has two first inclined surfaces on either side of the through-hole on the first flow path side, which are inclined to move away from the second flow path as they approach the through-hole side from the gap side. Each of the two guides has a second inclined surface opposite to the first inclined surface, which is inclined to move away from the second flow path as it approaches the through-hole side from the gap side.

[0008] In the above-described flow divider, the second cylindrical portion has an end wall spaced apart from the partition wall in the first direction, and a protrusion projecting from the end wall toward the through hole.

[0009] In the above-described current divider, the protrusion faces the through-hole and has a plane that intersects with the first direction.

[0010] An air conditioner according to one embodiment of the present invention comprises the above-mentioned flow divider, the first piping, and the plurality of second piping.

[0011] In the above-described air conditioner, the first piping has a first portion connected to the first cylindrical portion and a second portion that is perpendicular to the first direction from the first portion and moves away in a second direction toward the through-hole side from the gap side.

[0012] The above-described flow divider and air conditioner make it possible to suppress, for example, the difference in the ratio of liquid refrigerant to gaseous refrigerant in the refrigerant distributed to multiple second pipes. [Brief explanation of the drawing]

[0013] [Figure 1] Figure 1 is a schematic refrigerant system diagram showing an air conditioner during cooling operation according to the first embodiment. [Figure 2] Figure 2 is a schematic front view showing a heat exchanger and a portion of the refrigerant piping in the first embodiment. [Figure 3] Figure 3 is a schematic cross-sectional view showing a portion of the refrigerant piping in the first embodiment. [Figure 4] Figure 4 is a schematic cross-sectional view showing a current shunt according to the first embodiment. [Figure 5] Figure 5 is a schematic cross-sectional view showing the current shunt of the first embodiment along line AA in Figure 4. [Figure 6] Figure 6 is a schematic cross-sectional view showing a flow shunt in one modified example of the first embodiment, along line AA in Figure 4. [Figure 7] Figure 7 is a schematic cross-sectional view showing the current shunt of the first embodiment along the line BB in Figure 4. [Figure 8] Figure 8 is a schematic cross-sectional view showing a flow shunt in one modified example of the first embodiment, along the line BB in Figure 4. [Figure 9] Figure 9 is a schematic refrigerant system diagram showing an air conditioner during cooling operation according to the second embodiment. [Figure 10] Figure 10 is a schematic side view showing a heat exchanger according to the third embodiment. [Modes for carrying out the invention]

[0014] (First Embodiment) The first embodiment will be described below with reference to Figures 1 to 8. In this specification, the vertically upward direction is generally defined as the upward direction, and the vertically downward direction as the downward direction. Furthermore, in this specification, the components of the embodiment and their descriptions may be described using multiple expressions. The components and their descriptions are examples and are not limited by the expressions used in this specification. Components may also be identified by names different from those used in this specification. Furthermore, components may also be described using expressions different from those used in this specification.

[0015] Fig. 1 is a refrigerant system diagram schematically showing the air conditioner 10 according to the first embodiment during cooling operation. The air conditioner 10 is, for example, a household air conditioner. Note that the air conditioner 10 is not limited to this example, and may be another air conditioner such as a commercial air conditioner.

[0016] As shown in Fig. 1, the air conditioner 10 includes an outdoor unit 11, an indoor unit 12, a refrigerant pipe 13, and a control device 14. The outdoor unit 11 is disposed, for example, outdoors. The indoor unit 12 is disposed, for example, indoors.

[0017] The air conditioner 10 includes a refrigeration cycle in which the outdoor unit 11 and the indoor unit 12 are connected by the refrigerant pipe 13. The refrigerant flows between the outdoor unit 11 and the indoor unit 12 through the refrigerant pipe 13. Further, the outdoor unit 11 and the indoor unit 12 are electrically connected to each other by, for example, electric wiring.

[0018] The outdoor unit 11 includes an outdoor heat exchanger 21, an outdoor blower fan 22, a compressor 23, an accumulator 24, a four-way valve 25, and an expansion valve 26. The indoor unit 12 includes an indoor heat exchanger 31 and an indoor blower fan 32.

[0019] The refrigerant pipe 13 is, for example, a pipe made of metal. The refrigerant pipe 13 has two refrigerant pipes 41 and 42. The refrigerant pipe 41 connects the indoor heat exchanger 31 and the outdoor heat exchanger 21. The compressor 23, the accumulator 24, and the four-way valve 25 are provided in the refrigerant pipe 41. The refrigerant pipe 42 connects the outdoor heat exchanger 21 and the indoor heat exchanger 31. The expansion valve 26 is provided in the refrigerant pipe 42.

[0020] In cooling operation, the refrigerant flows from the indoor heat exchanger 31 to the outdoor heat exchanger 21 through the refrigerant pipe 41, and flows from the outdoor heat exchanger 21 to the indoor heat exchanger 31 through the refrigerant pipe 42. The arrows in Fig. 1 indicate the flow of the refrigerant during cooling operation. In heating operation, the refrigerant flows from the outdoor heat exchanger 21 to the indoor heat exchanger 31 through the refrigerant pipe 41, and flows from the indoor heat exchanger 31 to the outdoor heat exchanger 21 through the refrigerant pipe 42.

[0021] The outdoor heat exchanger 21 of the outdoor unit 11 acts as a condenser to release heat from the refrigerant during cooling operation and as an evaporator to absorb heat from the refrigerant during heating operation. The outdoor blower fan 22 blows air toward the outdoor heat exchanger 21, promoting heat exchange between the refrigerant and the air in the outdoor heat exchanger 21.

[0022] The compressor 23 has an inlet 23a and a discharge port 23b. The compressor 23 draws in refrigerant from the inlet 23a and discharges the compressed refrigerant from the discharge port 23b. In this way, the compressor 23 compresses the refrigerant in the refrigeration cycle and also creates a circulation of the refrigerant.

[0023] The accumulator 24 is connected to the suction port 23a of the compressor 23. The accumulator 24 separates the liquid refrigerant from the gaseous refrigerant. This allows the compressor 23 to draw in the gaseous refrigerant that has passed through the accumulator 24 from the suction port 23a. By being integrated with the compressor 23, the accumulator 24 can serve as the suction port of the compressor 23.

[0024] The four-way valve 25 is connected to the outdoor heat exchanger 21, the indoor heat exchanger 31, the discharge port 23b of the compressor 23, and the accumulator 24 (the suction port 23a of the compressor 23). The four-way valve 25 switches the flow paths connected to the outdoor heat exchanger 21, the indoor heat exchanger 31, the discharge port 23b of the compressor 23, and the accumulator 24, respectively, depending on whether it is in heating or cooling operation, thereby changing the direction in which the refrigerant flows.

[0025] As shown by the solid line in Figure 1, during cooling operation, the four-way valve 25 connects the outdoor heat exchanger 21 to the discharge port 23b of the compressor 23. Furthermore, during cooling operation, the four-way valve 25 connects the indoor heat exchanger 31 to the accumulator 24. As a result, the refrigerant compressed by the compressor 23 flows to the outdoor heat exchanger 21, and the refrigerant evaporated in the indoor heat exchanger 31 flows to the accumulator 24.

[0026] As shown by the dashed line in Figure 1, during heating operation, the four-way valve 25 connects the outdoor heat exchanger 21 and the accumulator 24. Furthermore, during heating operation, the four-way valve 25 connects the indoor heat exchanger 31 and the discharge port 23b of the compressor 23. As a result, the refrigerant compressed by the compressor 23 flows to the indoor heat exchanger 31, and the refrigerant evaporated in the outdoor heat exchanger 21 flows to the accumulator 24.

[0027] The expansion valve 26 is, for example, an electromagnetic expansion valve. However, the expansion valve 26 may be any other type of expansion valve. The expansion valve 26 is controlled by the control device 14 to regulate the amount of refrigerant passing through it.

[0028] The indoor heat exchanger 31 of the indoor unit 12 absorbs heat as an evaporator during cooling operation and releases heat as a condenser during heating operation. The indoor blower fan 32 blows air toward the indoor heat exchanger 31, promoting heat exchange between the indoor heat exchanger 31 and the air.

[0029] The control device 14 includes, for example, an outdoor control device 14a and an indoor control device 14b. The outdoor control device 14a and the indoor control device 14b are electrically connected to each other by electrical wiring. However, the control device 14 is not limited to this example. For example, the control device 14 may have only one of the outdoor control device 14a and the indoor control device 14b.

[0030] The outdoor control unit 14a controls the outdoor blower fan 22, compressor 23, four-way valve 25, and expansion valve 26 of the outdoor unit 11. The indoor control unit 14b controls the indoor blower fan 32 of the indoor unit 12.

[0031] The control device 14 controls the outdoor unit 11 and the indoor unit 12 so that the air conditioner 10 can perform cooling, heating, dehumidifying, and other operations. The indoor control device 14b may receive signals from, for example, a remote controller, or from an information terminal such as a smartphone via a communication device.

[0032] Figure 2 is a schematic front view showing a portion of the heat exchanger 50 and refrigerant piping 13 of the first embodiment. The heat exchanger 50 of the first embodiment is a microchannel heat exchanger. The outdoor heat exchanger 21 and the indoor heat exchanger 31 each have a heat exchanger 50.

[0033] The heat exchanger 50 of the outdoor heat exchanger 21 and the heat exchanger 50 of the indoor heat exchanger 31 have a similar general configuration. Therefore, the following description of the heat exchanger 50 is generally applicable to both the heat exchanger 50 of the outdoor heat exchanger 21 and the heat exchanger 50 of the indoor heat exchanger 31. However, the heat exchanger 50 of the outdoor heat exchanger 21 and the heat exchanger 50 of the indoor heat exchanger 31 may differ from each other in terms of shape, size, or arrangement. Furthermore, the two heat exchangers 50 may be of different types or configurations, such as one being a microchannel heat exchanger and the other being a fin-tube heat exchanger.

[0034] For convenience, the X, Y, and Z axes are defined below. The X, Y, and Z axes are orthogonal to each other. The X and Y axes extend approximately horizontally. The Z axis extends approximately vertically. Note that the X, Y, and Z axes may also be inclined at an angle to the horizontal and vertical directions.

[0035] Furthermore, the X, Y, and Z directions are defined herein. The X direction is the direction along the X axis and includes the +X direction indicated by the X-axis arrow and the -X direction which is the opposite direction of the X-axis arrow. The Y direction is the direction along the Y axis and includes the +Y direction indicated by the Y-axis arrow and the -Y direction which is the opposite direction of the Y-axis arrow. The Z direction is the direction along the Z axis and includes the +Z direction (up) indicated by the Z-axis arrow and the -Z direction (down) which is the opposite direction of the Z-axis arrow.

[0036] The heat exchanger 50 has two headers 51 and 52, a plurality of heat transfer tubes 53, and a plurality of fins 54. The two headers 51 and 52 are spaced apart from each other, for example, in the X direction. The plurality of heat transfer tubes 53 and the plurality of fins 54 are provided between the two headers 51 and 52.

[0037] Header 51 is connected to refrigerant piping 42. Header 52 is connected to refrigerant piping 41. Inside headers 51 and 52, flow paths are formed for the refrigerant to flow. For example, when the heat exchanger 50 functions as an evaporator, mainly liquid or gas-liquid two-phase refrigerant flows through header 51. On the other hand, for example, gaseous refrigerant flows through header 52. Note that the refrigerant flowing through headers 51 and 52 is not limited to this example.

[0038] The multiple heat transfer tubes 53 are flat, porous tubes made of a metal such as copper or aluminum. The multiple heat transfer tubes 53 are arranged with spacing in the Z direction and extend approximately in the X direction between the two headers 51 and 52. The refrigerant flows through the multiple heat transfer tubes 53 between the two headers 51 and 52. By providing the heat exchanger 50 with multiple heat transfer tubes 53, the pressure loss of the refrigerant flowing through the heat exchanger 50 can be reduced, and the performance of the heat exchanger 50 can be improved.

[0039] Multiple fins 54 are arranged with spacing in the X direction. Each of the multiple fins 54 is connected to at least one of the multiple heat transfer tubes 53. This allows the multiple fins 54 to facilitate heat exchange between the refrigerant flowing through the multiple heat transfer tubes 53 and the air.

[0040] The refrigerant piping 42 includes a main pipe 61, a plurality of branch pipes 62, and a flow divider 63. The main pipe 61 is an example of a first piping. The plurality of branch pipes 62 are an example of a plurality of second piping.

[0041] The main piping 61 is installed between the expansion valve 26 and the flow divider 63. One end 62a of each of the multiple branch pipes 62 is connected to the header 51 of the heat exchanger 50. The other end 62b of each of the multiple branch pipes 62 is connected to the flow divider 63. In other words, the refrigerant piping 41 branches from the main piping 61 to the multiple branch pipes 62 at the flow divider 63.

[0042] The refrigerant can flow from the main piping 61, through the flow divider 63, and into multiple branch pipes 62. Conversely, the refrigerant can also merge from the multiple branch pipes 62 through the flow divider 63 and flow into the main piping 61. In this way, the refrigerant flows through the main piping 61, the multiple branch pipes 62, and the flow divider 63.

[0043] A portion of the main piping 61 is bent into a roughly U-shape to accommodate it in a limited space, for example, inside the outdoor unit 11 or indoor unit 12. The main piping 61 has two straight sections 61a and 61b and a bent section 61c. The straight section 61a is an example of the first part. The straight section 61b is an example of the second part.

[0044] Each of the straight sections 61a and 61b extends linearly in the approximately Z direction (vertical direction). The end of the straight section 61a in the +Z direction is connected to the flow divider 63. The straight section 61b is provided between the straight section 61a and the expansion valve 26. The straight section 61b is spaced apart from the straight section 61a in the -X direction. The bent section 61c extends in an approximately arc shape and connects the ends of the straight sections 61a and 61b in the -Z direction.

[0045] The main piping 61 is not limited to the example described above. For example, the straight section 61b may extend in the X direction. In this case, a portion of the main piping 61, including the straight sections 61a, 61b and the bent section 61c, is bent into a roughly L-shape.

[0046] Figure 3 is a schematic cross-sectional view showing a portion of the refrigerant piping 42 of the first embodiment. As shown in Figure 3, the flow divider 63 has a first cylindrical section 71, a second cylindrical section 72, a partition wall 73, and two guides 74 and 75. The guides 74 and 75 may also be referred to as, for example, plate-like structures.

[0047] The first cylindrical portion 71 and the second cylindrical portion 72 are formed in a cylindrical shape extending substantially in the Z direction. The Z direction is an example of a first direction. The first cylindrical portion 71 and the second cylindrical portion 72 have a common central axis Ax. The central axis Ax extends substantially in the Z direction. Note that the first cylindrical portion 71 and the second cylindrical portion 72 are not limited to this example.

[0048] The first cylindrical section 71 and the second cylindrical section 72 are aligned approximately in the Z direction. The partition wall 73 is provided between the end of the first cylindrical section 71 in the +Z direction and the end of the second cylindrical section 72 in the -Z direction. The end of the straight section 61a in the +Z direction is connected to the end of the first cylindrical section 71 in the -Z direction. The ends 62b of the multiple branch pipes 62 are connected to the end of the second cylindrical section 72 in the +Z direction. The straight section 61a may be connected to other parts of the first cylindrical section 71, and the ends 62b of the multiple branch pipes 62 may be connected to other parts of the second cylindrical section 72.

[0049] Figure 4 is a schematic cross-sectional view of the flow divider 63 of the first embodiment. As shown in Figure 4, a first flow path 81 is provided inside the first cylindrical portion 71. The first flow path 81 extends approximately in the Z direction inside the first cylindrical portion 71. Furthermore, a second flow path 82 is provided inside the second cylindrical portion 72. The second flow path 82 extends approximately in the Z direction inside the second cylindrical portion 72.

[0050] The first flow path 81 and the second flow path 82 are spaces (passages) through which the refrigerant flows. The straight section 61a of the main piping 61 communicates with the first flow path 81. The multiple branch pipes 62 communicate with the second flow path 82. For example, the refrigerant flows from the straight section 61a into the first flow path 81 and flows out from the second flow path 82 into the multiple branch pipes 62.

[0051] Each of the multiple branch pipes 62 connects to the second flow path 82 and the header 51. Each of the multiple branch pipes 62 is connected to at least two of the multiple heat transfer tubes 53 through the header 51. In other words, each of the multiple branch pipes 62 branches off to the multiple heat transfer tubes 53 at the header 51. The flow divider 63 and the header 51 can reduce the pressure loss of the refrigerant by branching the refrigerant piping 42.

[0052] The first cylindrical portion 71 has an inner circumferential surface 71a. The inner circumferential surface 71a is a cylindrical surface that extends substantially in the Z direction along the central axis Ax. The inner circumferential surface 71a faces inward from the first cylindrical portion 71 and forms (defines, partitions) at least a part of the first flow path 81. That is, the inner circumferential surface 71a surrounds the first flow path 81.

[0053] Figure 5 is a schematic cross-sectional view of the flow divider 63 of the first embodiment along line AA in Figure 4. Figure 6 is a schematic cross-sectional view of the flow divider 63 in one modified example of the first embodiment along line AA in Figure 4. As shown in Figure 5, the inner circumferential surface 71a of this embodiment is formed in a substantially rectangular tubular shape. However, the inner circumferential surface 71a is not limited to this example and may be formed in a substantially cylindrical shape as shown in Figure 6, or in other shapes.

[0054] As shown in Figure 4, the second cylindrical portion 72 has a circumferential wall 85, an end wall 86, and a protrusion 87. The circumferential wall 85 is a cylindrical wall extending substantially in the Z direction along the central axis Ax. The end wall 86 closes the end of the circumferential wall 85 in the +Z direction. The end wall 86 is spaced apart from the partition wall 73 in the +Z direction (Z direction). The circumferential wall 85 and the end wall 86 form (define, partition) at least a part of the second flow path 82.

[0055] The protrusion 87 is located in the second flow channel 82 and protrudes from the end wall 86 along the central axis Ax in a substantially -Z direction. The protrusion 87 has a plane 87a. The plane 87a is provided at the end of the protrusion 87 in the -Z direction. The plane 87a is formed to be substantially flat and faces substantially in the -Z direction. In other words, the plane 87a is formed to intersect (orthogonal in this embodiment) the Z direction. Note that the end of the protrusion 87 in the -Z direction is not limited to a plane 87a, but may have a curved surface, a conical surface, a pyramidal surface, or other shape.

[0056] Figure 7 is a schematic cross-sectional view of the flow divider 63 of the first embodiment along the line BB in Figure 4. Figure 8 is a schematic cross-sectional view of the flow divider 63 in one modified example of the first embodiment along the line BB in Figure 4.

[0057] As shown in Figure 7, the peripheral wall 85 of this embodiment is formed in a substantially rectangular tubular shape. Furthermore, the protrusion 87 of this embodiment has a plurality of substantially rectangular parallelepiped-shaped parts connected to each other in the Z direction. Note that the peripheral wall 85 and the protrusion 87 are not limited to this example. For example, the peripheral wall 85 may be formed in a substantially cylindrical shape as shown in Figure 8, or in other shapes. Also, the protrusion 87 may have a cylindrical part as shown in Figure 8, or parts of other shapes.

[0058] The ends 62b of the multiple branch pipes 62 are arranged at approximately equal intervals around the central axis Ax. As shown in Figure 7, the refrigerant piping 42 of this embodiment has four branch pipes 62. The refrigerant piping 42 may also have six branch pipes 62, as shown in Figure 8. Alternatively, the refrigerant piping 42 may have two branch pipes 62 spaced apart from each other in the X direction, with a protrusion 87 positioned between the two branch pipes 62 in the X direction. The number and arrangement of the branch pipes 62 are not limited to these examples.

[0059] As shown in Figure 4, the partition wall 73 separates the first flow path 81 from the second flow path 82. In other words, the partition wall 73 is interposed between the first flow path 81 and the second flow path 82, separating them.

[0060] A through-hole 89 is provided in the partition wall 73. The through-hole 89 penetrates the partition wall 73 in the Z direction along the central axis Ax, connecting the first flow path 81 and the second flow path 82. The width Wp of the through-hole 89 in the X direction is smaller than the width Wc of the first flow path 81 in the X direction. For example, the width Wp is set to 20% to 40% of the width Wc, specifically about 30% of the width Wc. Note that the widths Wp and Wc are not limited to this example.

[0061] As shown in Figure 5, the cross-section of the through-hole 89 in this embodiment is formed to be approximately rectangular. However, the cross-section of the through-hole 89 is not limited to this example and may be formed to be approximately circular as shown in Figure 6, or to other shapes. In this specification, the cross-section is a cross-section perpendicular to the Z direction.

[0062] The width Wp of the through-hole 89 in the X direction is set to be approximately the same as the width of the through-hole 89 in the Y direction. However, the width of the through-hole 89 in the Y direction may be different from the width Wp of the through-hole 89 in the X direction.

[0063] As shown in Figure 4, the partition wall 73 has two end faces 73a and 73b. End face 73a is located on the side of the first flow path 81 and faces the first flow path 81. In other words, end face 73a, together with the inner circumferential surface 71a of the first cylindrical portion 71, forms (defines, partitions) at least a portion of the first flow path 81. End face 73b is located on the opposite side of end face 73a. End face 73b is located on the side of the second flow path 82 and faces the second flow path 82. In other words, end face 73b, together with the circumferential wall 85 and end wall 86 of the second cylindrical portion 72, forms at least a portion of the second flow path 82. The through hole 89 opens into end faces 73a and 73b.

[0064] The protrusion 87 projects from the end wall 86 toward the through hole 89 that opens into the end face 73b. The plane 87a of the protrusion 87 faces the through hole 89 that opens into the end face 73b, with a gap in between. The plane 87a is larger than the cross-section of the through hole 89 that opens into the end face 73b. Therefore, the width Ws of the plane 87a in the X direction is larger than the width Wp of the through hole 89 in the X direction.

[0065] The end face 73a has an intermediate face 73c and two inclined faces 73d and 73e. Inclined faces 73d and 73e are examples of the first inclined face. The intermediate face 73c and the inclined faces 73d and 73e are aligned in the X direction. The intermediate face 73c is provided between the two inclined faces 73d and 73e.

[0066] The intermediate surface 73c is formed to be approximately flat and oriented approximately in the -Z direction. The intermediate surface 73c extends approximately in the Y direction. The through hole 89 opens into the intermediate surface 73c of the end surface 73a. Therefore, the two inclined surfaces 73d and 73e are located on either side of the through hole 89 in the X direction.

[0067] The two slopes 73d and 73e are inclined with respect to the X direction so that they taper toward the -Z direction. In other words, the two slopes 73d and 73e are inclined with respect to the X direction so that they move away from the second flow path 82 as they approach the through hole 89. To put it another way, the two slopes 73d and 73e are inclined with respect to the X direction so that they move away from the second flow path 82 as they approach each other.

[0068] The two guides 74 and 75 are formed in the shape of roughly rectangular parallelepiped plates. Note that the guides 74 and 75 are not limited to this example. The guides 74 and 75 are positioned in the first flow channel 81. As shown in Figure 5, the guides 74 and 75 extend in the Y direction. Both ends of the guides 74 and 75 in the Y direction are connected to the inner circumferential surface 71a of the first cylindrical portion 71.

[0069] The two guides 74 and 75 are spaced apart from each other in the X direction. As a result, a gap G1 is formed between the guides 74 and 75. In addition, a gap G2 is formed between guide 74 and the inner surface 71a in the X direction, and a gap G3 is formed between guide 75 and the inner surface 71a. That is, the two guides 74 and 75 are spaced apart from each other on the opposite side of gaps G2 and G3.

[0070] As shown in Figure 4, the partition wall 73 is spaced apart from the guides 74 and 75. As a result, a gap G4 is formed between the guide 74 and the partition wall 73, and a gap G5 is formed between the guide 75 and the partition wall 73. Gaps G1 and G2 communicate with each other through gap G4. Gaps G1 and G3 communicate with each other through gap G5.

[0071] The through-hole 89 is located between the two guides 74 and 75 in the X direction. Therefore, the through-hole 89 opens in the partition wall 73 at a position opposite the gap G1 between the two guides 74 and 75. The gap G1 between the two guides 74 and 75 extends approximately in the Z direction along the central axis Ax and communicates with the through-hole 89.

[0072] Guide 74 has inclined surfaces 74a and 74b. Inclined surface 74a is an example of a second inclined surface. Inclined surface 74a faces inclined surface 73d of partition wall 73 with a gap between them. A gap G4 is provided between inclined surface 74a of guide 74 and inclined surface 73d of partition wall 73. Inclined surface 74b is located on the opposite side of inclined surface 74a.

[0073] The slopes 74a and 74b are approximately parallel to the slope 73d of the partition wall 73. Therefore, the slope 74a is inclined with respect to the X direction so as it approaches the through-hole 89, it moves away from the second flow path 82. In other words, the slopes 73d, 74a, and 74b are inclined so as they approach the through-hole 89 from the gap G2 side. Note that the slopes 74a and 74b do not necessarily have to be parallel to the slope 73d of the partition wall 73.

[0074] Guide 75 has inclined surfaces 75a and 75b. Inclined surface 75a is an example of a second inclined surface. Inclined surface 75a faces inclined surface 73e of partition wall 73 with a gap between them. A gap G5 is provided between inclined surface 75a of guide 75 and inclined surface 73e of partition wall 73. Inclined surface 75b is located on the opposite side of inclined surface 75a.

[0075] The slopes 75a and 75b are approximately parallel to the slope 73e of the partition wall 73. Therefore, the slope 75a is inclined with respect to the X direction so as it approaches the through-hole 89, it moves away from the second flow path 82. In other words, the slopes 73e, 75a, and 75b are inclined so as they approach the through-hole 89 from the gap G3 side. Therefore, the two slopes 74a and 75a are inclined with respect to the X direction so as they taper toward the -Z direction. Note that the slopes 75a and 75b do not necessarily have to be parallel to the slope 73e of the partition wall 73.

[0076] As described above, the straight section 61b is spaced apart from the straight section 61a in the -X direction. The -X direction is the direction from the gap G2 side towards the through hole 89 side, and is an example of a second direction. The refrigerant flows from the straight section 61b through the bent section 61c to the straight section 61a.

[0077] The refrigerant flowing through the main piping 61 is mainly a two-phase gas-liquid flow. Therefore, the refrigerant includes both liquid and gaseous refrigerant. Liquid refrigerant has a higher specific gravity than gaseous refrigerant. For this reason, as schematically shown by the arrows in Figure 3, when liquid refrigerant flows through the bend 61c, it tends to accumulate relatively easily at the outer end due to centrifugal force. On the other hand, when gaseous refrigerant flows through the bend 61c, it tends to accumulate relatively easily at the inner end. For this reason, the distribution of liquid and gaseous refrigerant may become uneven after passing through the bend 61c.

[0078] As schematically shown by the arrows in Figure 4, the refrigerant that has passed through the bent section 61c flows into the first flow path 81. Due to the non-uniform distribution of liquid and gaseous refrigerant in the bent section 61c, the liquid refrigerant tends to accumulate relatively near the end 81a of the first flow path 81 in the +X direction. On the other hand, the gaseous refrigerant tends to accumulate relatively near the end 81b of the first flow path 81 in the -X direction.

[0079] A gas-liquid two-phase flow refrigerant, in which the liquid and gaseous refrigerants are distributed in a state close to that before passing through the bend 61c, that is, a gas-liquid two-phase flow refrigerant in which the liquid and gaseous refrigerants are distributed relatively uniformly (hereinafter referred to as the refrigerant in the first state), collects in the center of the first flow path 81 in the X direction. The gap G1 between the two guides 74 and 75 is located approximately in the center of the first flow path 81 in the X direction. Therefore, the refrigerant in the first state flows into the gap G1.

[0080] The gap G2 between the guide 74 and the inner surface 71a communicates with the end 81a of the first flow path 81. Therefore, the gas-liquid two-phase flow refrigerant (hereinafter referred to as the refrigerant in the second state), which has more liquid refrigerant than the refrigerant in the first state, flows into the gap G2. Furthermore, the inclined surface 74b of the guide 74 guides the refrigerant in the second state into the gap G2. The refrigerant in the second state passes through gaps G2 and G4 and collides with the refrigerant in the first state that has passed through gap G1. In other words, the inclined surface 73d of the partition wall 73 and the inclined surface 74a of the guide 74 guide the refrigerant in the second state to the point where gaps G1 and G4 merge.

[0081] The gap G3 between the guide 75 and the inner circumferential surface 71a communicates with the end 81b of the first flow path 81. Therefore, the gas-liquid two-phase flow refrigerant (hereinafter referred to as the refrigerant in the third state), which has a larger proportion of gaseous refrigerant compared to the refrigerant in the first state, flows into the gap G3. Furthermore, the inclined surface 75b of the guide 75 guides the refrigerant in the third state into the gap G3. The refrigerant in the third state passes through gaps G3 and G5 and collides with the refrigerant in the first state that has passed through gap G1. In other words, the inclined surface 73e of the partition wall 73 and the inclined surface 75a of the guide 75 guide the refrigerant in the third state to the point where gaps G1 and G5 merge.

[0082] The refrigerant in the first state, flowing approximately through the center of the first flow path 81, flows through the gap G1 in approximately the +Z direction. Therefore, the velocity of the refrigerant in the first state flowing through gap G1 has a component in the +Z direction. On the other hand, the velocity of the refrigerant in the second state flowing through gap G4 and the velocity of the refrigerant in the third state flowing through gap G5 have a component in the -Z direction. Consequently, the relative velocities at the time of collision between the refrigerant in the first state that has passed through gap G1, the refrigerant in the second state that has passed through gap G4, and the refrigerant in the third state that has passed through gap G5 become large.

[0083] The refrigerant in the first state, the refrigerant in the second state, and the refrigerant in the third state are mixed almost uniformly by colliding with each other at the points where gaps G1, G4, and G5 are connected. As a result, a gas-liquid two-phase flow of refrigerant, in which the liquid and gaseous refrigerants are mixed almost uniformly, flows through the through-hole 89 into the second flow path 82.

[0084] The refrigerant, which is mixed in a nearly uniform gas-liquid two-phase flow, collides with the plane 87a of the protrusion 87 in the second flow path 82. As a result, the velocity difference in the Z direction between the liquid refrigerant and the gaseous refrigerant contained in the gas-liquid two-phase flow is temporarily reduced. The gas-liquid two-phase flow refrigerant that collides with the plane 87a diffuses in a direction substantially perpendicular to the Z direction and is distributed to multiple branch pipes 62.

[0085] Because the distribution of liquid refrigerant and gaseous refrigerant is made nearly uniform in the flow divider 63, the ratio of liquid refrigerant to gaseous refrigerant in the multiple branch pipes 62 is nearly equal. Therefore, the ratio of liquid refrigerant to gaseous refrigerant is also nearly equal in the multiple heat transfer tubes 53.

[0086] As described above, the flow divider 63 forms a flow path similar to a so-called Tesla valve, causing multiple refrigerant flows, which have been branched by the guides 74 and 75, to collide with each other. While a Tesla valve obstructs fluid flow by causing fluid flows to collide with each other, the flow divider 63 in this embodiment mixes the refrigerants by causing the refrigerant flows to collide with each other.

[0087] In cooling operation, the heat exchanger 50 of the indoor heat exchanger 31 functions as an evaporator. Because the ratio of liquid refrigerant to gaseous refrigerant in the multiple heat transfer tubes 53 is approximately equal, the heat exchanger 50 can efficiently absorb heat from the refrigerant in the multiple heat transfer tubes 53.

[0088] In heating operation, the heat exchanger 50 of the outdoor heat exchanger 21 functions as an evaporator. Because the ratio of liquid refrigerant to gaseous refrigerant in the multiple heat transfer tubes 53 is approximately equal, the heat exchanger 50 can efficiently absorb heat from the refrigerant in the multiple heat transfer tubes 53.

[0089] The following describes some examples of how to manufacture the flow divider 63. Note that the method of manufacturing the flow divider 63 is not limited to the method described below, and other methods may be used. The flow divider 63 in this embodiment includes, for example, an outer cylinder 100, a first structure 101, a second structure 102, and a third structure 103. The outer cylinder 100, the first structure 101, the second structure 102, and the third structure 103 are made of, for example, brass or stainless steel.

[0090] The outer cylinder 100 has a small cylindrical portion 111 and a large cylindrical portion 112. The small cylindrical portion 111 and the large cylindrical portion 112 are formed in a cylindrical shape that extends substantially in the Z direction along the central axis Ax. The end of the small cylindrical portion 111 in the +Z direction is connected to the end of the large cylindrical portion 112 in the -Z direction. The cross-section of the inner space of the large cylindrical portion 112 is larger than the cross-section of the inner space of the small cylindrical portion 111.

[0091] The first structure 101 has two guides 74 and 75. The second structure 102 has a partition wall 73. The first structure 101 and the second structure 102 are attached to the inside of the small cylindrical portion 111, for example, by crimping or welding. The inner circumferential surface 71a of the first cylindrical portion 71 is formed, for example, by at least one of the small cylindrical portion 111 and the first structure 101.

[0092] The large cylindrical section 112 has a circumferential wall 85. The third structure 103 has an end wall 86 and a protrusion 87. The end wall 86 of the third structure 103 is attached to the end of the circumferential wall 85 in the +Z direction, for example, by welding or crimping. As described above, the flow divider 63 can be easily manufactured, for example, by attaching the first structure 101, the second structure 102, and the third structure 103 to the outer cylinder 100.

[0093] In the air conditioner 10 according to the first embodiment described above, the first cylindrical portion 71 is configured to be connected to the main body piping 61. A first flow path 81 extending in the Z direction is provided inside the first cylindrical portion 71. The first cylindrical portion 71 has an inner circumferential surface 71a surrounding the first flow path 81. The second cylindrical portion 72 is configured to be connected to a plurality of branch pipes 62. A second flow path 82 is provided inside the second cylindrical portion 72. Two guides 74 and 75 are positioned in the first flow path 81 such that they form gaps G2 and G3 between themselves and the inner circumferential surface 71a. The two guides 74 and 75 are spaced apart from each other on the opposite side of the gaps G2 and G3. A partition wall 73 separates the first flow path 81 and the second flow path 82 and is spaced apart from the two guides 74 and 75. In the partition wall 73, a through hole 89 connecting the first flow path 81 and the second flow path 82 opens between the two guides 74 and 75, facing each other.

[0094] For example, when refrigerant flows from the main piping 61 through the flow divider 63 to multiple branch piping 62, the refrigerant first flows into the first flow path 81. In this refrigerant, liquid and gaseous refrigerant may be unevenly distributed in the X direction, for example, due to centrifugal force. For example, a first state of refrigerant, in which liquid and gaseous refrigerant are relatively uniformly distributed, is located in the X direction between a second state of refrigerant, in which there is more liquid refrigerant than in the first state, and a third state of refrigerant, in which there is more gaseous refrigerant than in the first state. That is, the refrigerant in the first state is located approximately in the center in the X direction and passes through the gap G1 between the two guides 74 and 75. The refrigerant in the second state passes through the gap G2 between the guide 74 and the inner circumferential surface 71a, and further passes through the gap G4 between the guide 74 and the partition wall 73, and collides with the refrigerant in the first state that has passed through the gap G1 between the two guides 74 and 75. The refrigerant in the third state flows through the gap G3 between the guide 75 and the inner circumferential surface 71a, and further through the gap G5 between the guide 75 and the partition wall 73, and collides with the refrigerant in the first state that has passed through the gap G1. That is, the refrigerant in the first state that has passed through the gap G1 collides with the refrigerant in the second state branched by the guide 74 and the refrigerant in the third state branched by the guide 75. As a result, the refrigerant in the first state, the refrigerant in the second state, and the refrigerant in the third state are mixed with each other and then distributed to the multiple branch pipes 62 through the through hole 89 and the second flow path 82. As a result, even if the liquid refrigerant and gaseous refrigerant are unevenly distributed in the X direction, the flow divider 63 can introduce the gas-liquid two-phase flow of the refrigerant, which is a mixture of liquid and gaseous refrigerant, to the multiple branch pipes 62 in a substantially equal manner. Therefore, the flow divider 63 can suppress the ratio of liquid refrigerant to gaseous refrigerant in the refrigerant distributed to the multiple branch pipes 62 from being different.

[0095] The partition wall 73 has two inclined surfaces 73d and 73e on either side of the through-hole 89, on the first flow path 81 side, which are inclined to move away from the second flow path 82 as you approach the through-hole 89 side from the gap G2 and G3 side. The two guides 74 and 75 face the inclined surfaces 73d and 73e and have inclined surfaces 74a and 75a which are inclined to move away from the second flow path 82 as you approach the through-hole 89 side from the gap G2 and G3 side. As a result, the refrigerant flow through gaps G4 and G5 has a component in the opposite direction to the refrigerant flow through gap G1. Therefore, the relative velocity at the time of collision between the refrigerant in the first state that has passed through gap G1, the refrigerant in the second state branched by guides 74 and 75, and the refrigerant in the third state branched by guides 74 and 75 is increased, and the refrigerant in the first state, the refrigerant in the second state, and the refrigerant in the third state is mixed more uniformly.

[0096] The second cylindrical portion 72 has an end wall 86 spaced apart in the Z direction from the partition wall 73, and a protrusion 87 projecting from the end wall 86 toward the through hole 89. The refrigerant passing through the through hole 89 collides with the protrusion 87. This collision reduces the velocity difference between the liquid refrigerant and the gaseous refrigerant, making the distribution of the liquid and gaseous refrigerants more uniform. Therefore, the flow divider 63 can introduce the gas-liquid two-phase flow of refrigerant, which is a mixture of liquid and gaseous refrigerant, to the multiple branch pipes 62 in a substantially uniform manner.

[0097] The protrusion 87 has a plane 87a that faces the through-hole 89 and intersects with the Z direction. The refrigerant that has passed through the through-hole 89 collides with the plane 87a of the protrusion 87. This collision more effectively reduces the velocity difference between the liquid refrigerant and the gaseous refrigerant, and the distribution of the liquid refrigerant and gaseous refrigerant becomes more uniform. Therefore, the flow divider 63 can introduce the gas-liquid two-phase flow of refrigerant, which is a mixture of liquid refrigerant and gaseous refrigerant, to the multiple branch pipes 62 in a substantially uniform manner.

[0098] The main piping 61 has a straight section 61a connected to the first cylindrical section 71, and a section extending from the straight section 61a to Z directionIt has a straight section 61b that is perpendicular to the gap G2 and separated in the -X direction from the gap G2 side toward the through hole 89 side. When refrigerant flows from the main piping 61 through the splitter 63 to the multiple branch pipes 62, the refrigerant in the main piping 61 flows from the straight section 61b to the straight section 61a. As a result, in the refrigerant flowing from the main piping 61 into the first flow path 81, liquid refrigerant and gaseous refrigerant are unevenly distributed in the X direction, for example, due to centrifugal force or inertia. However, even if liquid refrigerant and gaseous refrigerant are unevenly distributed in the X direction, the splitter 63 of this embodiment can introduce the refrigerant, which is a mixture of liquid refrigerant and gaseous refrigerant in a gas-liquid two-phase flow, to the multiple branch pipes 62 in a substantially equal manner. Accordingly, the air conditioner 10 of this embodiment can suppress the uneven distribution of liquid refrigerant and gaseous refrigerant in the refrigerant distributed to the multiple branch pipes 62.

[0099] (Second embodiment) A second embodiment will be described below with reference to Figure 9. In the following descriptions of multiple embodiments, components having the same function as those already described will be denoted by the same reference numerals as those previously described, and their descriptions may be omitted. Furthermore, multiple components denoted by the same reference numerals do not necessarily share all functions and properties, and may have different functions and properties depending on the embodiment.

[0100] Figure 9 is a schematic refrigerant system diagram showing the air conditioner 10 during cooling operation according to the second embodiment. As shown in Figure 9, the air conditioner 10 in the second embodiment is a so-called multi-air conditioner having a plurality of indoor units 12.

[0101] Between the outdoor unit 11 and the multiple indoor units 12, each of the refrigerant pipes 41 and 42 has a main pipe 61, multiple branch pipes 62, and a flow divider 63. The number of branch pipes 62 is the same as the number of multiple indoor units 12. Each of the branch pipes 62 is connected to the heat exchanger 50 of the corresponding indoor heat exchanger 31 among the multiple indoor units 12.

[0102] Each of the multiple flow dividers 63 can make the distribution of liquid refrigerant and gaseous refrigerant between the outdoor unit 11 and the multiple indoor units 12 as uniform as in the first embodiment. Therefore, the ratio of liquid refrigerant to gaseous refrigerant in the indoor heat exchangers 31 of the multiple indoor units 12 becomes approximately equal.

[0103] (Third embodiment) A third embodiment will be described below with reference to Figure 10. Figure 10 is a schematic side view showing a heat exchanger 50 according to the third embodiment. As shown in Figure 10, the heat exchanger 50 of the third embodiment is a fin-tube heat exchanger. The heat exchanger 50, which is a fin-tube heat exchanger, has a first heat exchanger 301, two second heat exchangers 302, and connecting piping 303. Note that the structure of the fin-tube heat exchanger is not limited to this example.

[0104] Each of the first heat exchanger 301 and the two second heat exchangers 302 is part of the heat exchanger 50 and has a plurality of heat transfer tubes 53 and a plurality of fins 54. In each of the first heat exchanger 301 and the two second heat exchangers 302, at least two heat transfer tubes 53 are connected in series.

[0105] In the example shown in Figure 10, in each of the first heat exchanger 301 and the two second heat exchangers 302, for example, two sets of heat transfer tubes 53 connected in series are provided in parallel. Note that the number, arrangement, and connection of the multiple heat transfer tubes 53 in the heat exchanger 50 are not limited to the example shown in Figure 10.

[0106] The connecting pipe 303 connects the heat transfer tubes 53 of the first heat exchanger 301 to the heat transfer tubes 53 of the two second heat exchangers 302. The connecting pipe 303 has a main pipe 61, a plurality of branch pipes 62, and a flow divider 63.

[0107] The main piping 61, branch piping 62, and flow divider 63 are at least broadly the same as in the first embodiment, except as described below. The main piping 61 in Figure 10 is connected to the heat transfer tubes 53 of the first heat exchanger 301. The multiple branch pipings 62 are connected to the heat transfer tubes 53 of the two second heat exchangers 302. In this way, the multiple branch pipings 62 are connected to the second heat exchanger 302.

[0108] The heat transfer tubes 53 of the first heat exchanger 301 are connected to the refrigerant piping 42. On the other hand, the heat transfer tubes 53 of each of the two second heat exchangers 302 are connected to the refrigerant piping 41. The heat transfer tubes 53 of the two second heat exchangers 302 may be merged and connected to the refrigerant piping 41.

[0109] For example, when the heat exchanger 50 functions as an evaporator, a refrigerant, mainly in liquid or gas-liquid two-phase flow, flows from the refrigerant piping 42 to the heat transfer tubes 53 of the first heat exchanger 301. The refrigerant then flows from the first heat exchanger 301 through the connecting piping 303, which is branched by the flow divider 63, to the heat transfer tubes 53 of the two second heat exchangers 302. For example, a refrigerant, mainly in gaseous form, flows from the second heat exchanger 302 to the refrigerant piping 41. Note that the refrigerant flowing through the first heat exchanger 301 and the second heat exchangers 302 is not limited to the examples above.

[0110] As in the third embodiment described above, the flow divider 63 may be installed between two parts (the first heat exchanger 301 and the second heat exchanger 302) inside the outdoor heat exchanger 21 or the indoor heat exchanger 31. Alternatively, the flow divider 63 may be installed at other locations where the branch piping 62 is directly or indirectly connected to the heat exchanger.

[0111] In the above explanation, suppression is defined, for example, as preventing the occurrence of an event, effect, or influence, or reducing the degree of an event, effect, or influence.

[0112] While several embodiments of the present invention have been described, these embodiments are presented as examples only and are not intended to limit the scope of the invention. These novel embodiments can be carried out in a variety of other forms, and various omissions, substitutions, and modifications can be made without departing from the spirit of the invention. These embodiments and their variations are included in the scope and spirit of the invention, as well as in the claims of the invention and its equivalents. [Explanation of symbols]

[0113] 10...Air conditioner, 61...Main piping, 61a, 61b...Straight section, 62...Branch piping, 63...Flow divider, 71...First cylindrical section, 71a...Inner surface, 72...Second cylindrical section, 73...Partition wall, 73d, 73e...Slope, 74, 75...Guide, 74a, 75a...Slope, 81...First flow path, 82...Second flow path, 86...End wall, 87...Convex section, 87a...Flat surface, 89...Through hole, Wc, Wp...Width, G2, G3...Gap.

Claims

1. A first cylindrical portion is configured to be connected to a first pipe, has a first flow path extending in a first direction inside, and has an inner circumferential surface surrounding the first flow path, A second cylindrical section is configured to be connected to multiple second pipes and has a second flow path inside, Two guides are arranged in the first flow channel such that a gap is formed between them and the inner circumferential surface, and are spaced apart from each other on the opposite side of the gap, A partition wall separates the first flow path and the second flow path, is spaced apart from the two guides, and has a through hole connecting the first flow path and the second flow path opening at a position opposite to the two guides, It is equipped with, The partition wall has two first inclined surfaces on either side of the through-hole, which are inclined on the first flow path side such that they move away from the second flow path as they approach the through-hole side from the gap side. Each of the two guides has a second slope that faces the first slope and is inclined to move away from the second flow path as it approaches the through-hole side from the gap side. Flow divider.

2. The second cylindrical portion has an end wall spaced apart from the partition wall in the first direction, and a protrusion projecting from the end wall toward the through hole. A current shunt according to claim 1.

3. The protrusion has a plane that faces the through hole and intersects with the first direction. A current shunt according to claim 2.

4. A shunt device comprising any one of claims 1 to 3, The first piping, The plurality of second pipes, An air conditioner equipped with the following features.

5. The first piping has a first portion connected to the first cylindrical portion, and a second portion that is perpendicular to the first direction from the first portion and moves away in a second direction toward the through-hole side from the gap side. The air conditioner according to claim 4.

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