Patent Application
20240328729
The present disclosure relates to a refrigerant distributor that distributes refrigerant to plural heat transfer tubes, a heat exchanger including the refrigerant distributor, and a refrigeration cycle apparatus including the heat exchanger.
In recent years, the diameter of a heat transfer tube in a heat exchanger used for an air-conditioning apparatus has been increasingly reduced to reduce a refrigerant amount and to increase the performance of the heat exchanger. When the diameter of a heat transfer tube is reduced, it is required to suppress an increase in pressure loss during the passage of refrigerant through the heat transfer tube. Thus, the number of paths that is the number of branches of the heat exchanger is increased.
To increase the number of paths, a heat exchanger usually includes a multibranch refrigerant distributor that distributes and supplies the refrigerant flowing in from one inlet flow passage, to plural paths. In this case, for the heat exchanger, a compact-size refrigerant distributor that can suppress an uneven flow of refrigerant into each of the paths is required to maintain the heat exchange performance. For example, Patent Literature 1 discloses, as such a refrigerant distributor, one configured by stacking a plate-like member having a through groove for dividing refrigerant into two branches and a plate-like member having a through hole for causing refrigerant to flow through the through groove.
In the refrigerant distributor of Patent Literature 1, the plate-like member having the through groove is sandwiched between other plate-like members for the through groove formed in the plate-like member to have effect as a flow passage. The refrigerant distributor of Patent Literature 1 further includes two plate-like members having only openings in which flat tubes are inserted, to ensure the insertion spaces of the flat tubes. As described above, the refrigerant distributor of Patent Literature 1 includes many plate-like members having no function of distributing refrigerant, thereby having a large size.
The present disclosure has been made to solve such an above-described problem, and an object thereof is to provide a downsized refrigerant distributor, a heat exchanger, and a refrigeration cycle apparatus including the heat exchanger.
A refrigerant distributor according to an embodiment of the present disclosure in which a refrigerant pipe and a plurality of heat transfer tubes are connected, and refrigerant flowing in from the refrigerant pipe is caused to flow through flow passages formed inside to thereby cause the refrigerant to be distributed to the plurality of the heat transfer tubes, includes a first plate-like member, a second plate-like member and a third plate-like member arranged in a first direction, the first plate-like member being a member to which the refrigerant pipe is connected and the third plate-like member being a member to which the plurality of the heat transfer tubes are connected. The first plate-like member includes an inflow passage formed so as to penetrate in the first direction and into which refrigerant flows from the refrigerant pipe, and a plurality of return flow passages that cause the refrigerant flowing from the second plate-like member side to make a return-flow to the second plate-like member side. The second plate-like member includes a plurality of through passages formed so as to penetrate in the first direction. The third plate-like member includes a plurality of projections that project in a direction opposite to the second plate-like member. Each of the plurality of the through passages is communicated with the inflow passage or one of the plurality of the return flow passages. The plurality of the projections each have, in its inside, a space that is communicated with the plurality of the through passages.
In the present disclosure, the flow passages are partially formed in the projections of the third plate-like member to which flat tubes are connected. Thus, the refrigerant distributor according to an embodiment of the present disclosure is downsized by reducing the plate-like members that are required to form part of the flow passages.
Hereinafter, a refrigeration cycle apparatus 1 including a refrigerant distributor according to Embodiment 1 will be described with reference to, for example, the drawings. In the following description, parts denoted by the same reference signs are the same or equivalent to one another, and the same applies throughout the entire descriptions of the embodiments below. Moreover, in the drawings, the relationships of the sizes of constituting members sometimes differ from the relationships of the sizes of actual ones. In addition, detailed structures are appropriately simplified or omitted. The forms of the constituting elements represented in the entire description are merely examples, and the constituting elements are not limited to the forms described in the description.
The compressor 5 sucks refrigerant in a low-temperature and low-pressure state, compresses the sucked refrigerant to bring the refrigerant into a high-temperature and high-pressure state, and discharges the refrigerant. The flow-switching valve 6 switches flowing directions of the refrigerant in the refrigerant circuit and is, for example, a four-way valve. The expansion valve 8 reduces the pressure of the refrigerant to expand the refrigerant and is, for example, an electronic expansion valve. The outdoor heat exchanger 9 exchanges heat between the refrigerant and outdoor air and is, for example, a fin-and-tube heat exchanger. The outdoor heat exchanger 9 operates as a condenser during a cooling operation and operates as an evaporator during a heating operation. The outdoor fan 9a is a device that sends the outdoor air to the outdoor heat exchanger 9.
The indoor heat exchanger 7 exchanges heat between indoor air and the refrigerant. The indoor heat exchanger 7 operates as an evaporator during the cooling operation and operates as a condenser during the heating operation. The indoor fan 7a is a device that sends the indoor air to the indoor heat exchanger 7 and is, for example, a cross-flow fan.
The indoor heat exchanger 7 includes a refrigerant distributor 7b. The refrigerant distributor 7b is provided on the inflow side through which the refrigerant in a liquid phase rich state flows when the indoor heat exchanger 7 operates as an evaporator. The outdoor heat exchanger 9 includes a refrigerant distributor 9b. The refrigerant distributor 9b is provided on the inflow side when the outdoor heat exchanger 9 operates as an evaporator. The refrigerant distributor 7b and the refrigerant distributor 9b will be described later.
Here, an operation of the refrigeration cycle apparatus 1 will be described. First, the cooling operation will be described. The refrigeration cycle apparatus 1 performs the cooling operation by switching the flow-switching valve 6 such that the discharge side of the compressor 5 and the outdoor heat exchanger 9 are connected. In the cooling operation, the refrigerant sucked into the compressor 5 is compressed by the compressor 5, and the refrigerant that has turned into a high-temperature and high-pressure gas state is discharged from the compressor 5. The refrigerant in a high-temperature and high-pressure gas state that has been discharged from the compressor 5 passes through the flow-switching valve 6 and flows into the outdoor heat exchanger 9 operating as a condenser. The refrigerant that has flowed into the outdoor heat exchanger 9 exchanges heat with the outdoor air sent by the outdoor fan 9a and is thus condensed to be liquefied. The refrigerant in a liquid state flows into the expansion valve 8 and is reduced in pressure and expanded to turn into a low-temperature and low-pressure two-phase gas-liquid state. The refrigerant in a two-phase gas-liquid state flows into the indoor heat exchanger 7 operating as an evaporator. The refrigerant that has flowed into the indoor heat exchanger 7 exchanges heat with the indoor air sent by the indoor fan 7a and is thus evaporated to be gasified. At this time, the indoor air is cooled, and air cooling is thus performed in the room. Subsequently, the evaporated refrigerant in a low-temperature and low-pressure gas state passes through the flow-switching valve 6 and is sucked into the compressor 5.
Next, the heating operation will be described. The refrigeration cycle apparatus 1 performs the heating operation by switching the flow-switching valve 6 such that the discharge side of the compressor 5 and the indoor heat exchanger 7 are connected to one another. In the heating operation, the refrigerant sucked into the compressor 5 is compressed by the compressor 5, and the refrigerant that has turned into a high-temperature and high-pressure gas state is discharged from the compressor 5. The refrigerant in a high-temperature and high-pressure gas state that has been discharged from the compressor 5 passes through the flow-switching valve 6 and flows into the indoor heat exchanger 7 operating as a condenser. The refrigerant that has flowed into the indoor heat exchanger 7 exchanges heat with the indoor air sent by the indoor fan 7a and is thus condensed to be liquefied. At this time, the indoor air is heated, and air heating is thus performed in the room. The refrigerant in a liquid state flows into the expansion valve 8 and is reduced in pressure and expanded to turn into a low-temperature and low-pressure two-phase gas-liquid state. The refrigerant in a two-phase gas-liquid state flows into the outdoor heat exchanger 9 operating as an evaporator. The refrigerant that has flowed into the outdoor heat exchanger 9 exchanges heat with the outdoor air sent by the outdoor fan 9a and is thus evaporated to be gasified. Subsequently, the evaporated refrigerant in a low-temperature and low-pressure gas state passes through the flow-switching valve 6 and is sucked into the compressor 5.
Hereinafter, the configuration of the heat exchanger will be described while the indoor heat exchanger 7 is referred to as an example. The outdoor heat exchanger 9 and the refrigerant distributor 9b of the outdoor heat exchanger 9 have configurations similar to the configurations of the indoor heat exchanger 7 and the refrigerant distributor 9b of the indoor heat exchanger 7, and the descriptions thereof are thus omitted. Note that, the contents of the present disclosure may be applied to only any one of the indoor heat exchanger 7 with the refrigerant distributor 9b and the outdoor heat exchanger 9 with the refrigerant distributor 9b.
Each of the heat transfer tubes 50 is, for example, a flat tube having plural flow passages or a circular tube. The heat transfer tube 50 is made of, for example, copper or aluminum. An end portion of the heat transfer tube 50 on the refrigerant distributor 7b side is inserted in the refrigerant distributor 7b. Note that, although
A flow of refrigerant in the indoor heat exchanger 7 according to Embodiment 1 will be described. The refrigerant flowing through the refrigerant pipe 4 flows into the refrigerant distributor 7b and is caused to be distributed to and to flow out into the plural heat transfer tubes 50 when, for example, the indoor heat exchanger 7 functions as an evaporator The refrigerant in the plural heat transfer tubes 50 exchanges heat with, for example, the air supplied by the indoor fan 7a. Portions of the refrigerant flowing through the plural heat transfer tubes 50 flow into the gas header to merge with one another and flow out into the refrigerant pipe 4. Note that the refrigerant flows in the reverse direction when the indoor heat exchanger 7 functions as a condenser.
A return flow passage 13a is formed inside each of the lying-astride projections 12a. The return flow passage 13a causes the refrigerant flowing from a through passage 21b of the second plate-like member 20, which will be described later, to make a return-flow to a through passage 21c of the second plate-like member 20. A return flow passage 13b is formed inside each of the lying-astride projections 12b. The return flow passage 13b causes the refrigerant flowing from a through passage 21d of the second plate-like member 20, which will be described later, to make a return-flow to a through passage 21e of the second plate-like member 20. The first plate-like member 10 includes an inflow passage 11. The inflow passage 11 is formed so as to penetrate the first plate-like member 10 in the stacking direction. The refrigerant pipe 4 is connected to the first plate-like member 10, and the inside space of the refrigerant pipe 4 is communicated with the inflow passage 11. The inflow passage 11, the return flow passages 13a, and the return flow passages 13b constitute the flow passages of the refrigerant distributor 7b,
The second plate-like member 20 includes a through passage 21a, two through passages 21b, two through passages 21c, four through passages 21d, and four through passages 21e formed so as to penetrate in the stacking direction. When viewed in the stacking direction, the through passage 21a is substantially circular and is formed at substantially the center of the second plate-like member 20. The through passage 21a is communicated with the inflow passage 11 of the first plate-like member 10 and a first communication passage 41a of the fourth plate-like member 40, which will be described later. When viewed in the stacking direction, each of the through passages 21b is substantially circular and is formed adjacent to the through passage 21a in the width direction. Each of the through passages 21b is communicated with the return flow passage 13a of the first plate-like member 10 and a first communication passage 41b of the fourth plate-like member 40, which will be described later. When viewed in the stacking direction, the through passages 21c are each substantially circular, are formed at equal intervals from the through passage 21a, and are each formed at substantially the center in the width direction. Each of the through passages 21c is communicated with the return flow passage 13a of the first plate-like member 10 and a first communication passage 41c of the fourth plate-like member 40, which will be described later.
When viewed in the stacking direction, each of the through passages 21d is substantially circular and is formed adjacent to the through passage 21c in the width direction. Each of the through passages 21d is communicated with the return flow passage 13b of the first plate-like member 10 and a first communication passage 41d of the fourth plate-like member 40, which will be described later. When viewed in the stacking direction, the through passages 21e are each substantially circular and are formed alternately with the through passage 21a and the two through passages 21c in the arrangement direction. The through passages 21e are formed at equal intervals in the arrangement direction. Each of the through passages 21e is communicated with the return flow passage 13b and a second communication passage 42 of the fourth plate-like member 40, which will be described later. The through passage 21a, the two through passages 21b, the two through passages 21c, the four through passages 21d, and the four through passages 21e constitute the flow passages of the refrigerant distributor 7b.
The projection 31 including the branch passage 34a is provided at substantially the center of the third plate-like member 30 in the arrangement direction. The branch passage 34a causes the first communication passage 41a and the first communication passages 41b of the fourth plate-like member 40 to be communicated. The projections 31 including the branch passages 34b are provided at equal intervals from the projection 31 including the branch passage 34a in the arrangement direction. Each of the branch passage 34b causes the first communication passage 41c and the first communication passages 41d of the fourth plate-like member 40 to be communicated. The projections 31 including the branch passages 34c are provided alternately with the projection 31 including the branch passage 34a and the two projections 31 including the branch passages 34b in the arrangement direction. The projections 31 including the branch passages 34c are formed at equal intervals in the arrangement direction. Each of the branch passages 34c causes a first communication passage 41e and the second communication passages 42 of the fourth plate-like member 40, which will be described later, to be communicated.
As
When viewed in the stacking direction, each of the first communication passages 41b is substantially circular and is formed adjacent to the first communication passage 41a in the width direction. Each of the first communication passages 41b is communicated with the through passage 21b of the second plate-like member 20 and the branch passage 34a of the third plate-like member 30. That is, the through passage 21b of the second plate-like member 20 and the branch passage 34a of the third plate-like member 30 are communicated through the first communication passage 41b, When viewed in the stacking direction, the first communication passages 41c are each substantially circular, are formed at equal intervals from the first communication passage 41a, and are each formed at substantially the center in the width direction. Each of the first communication passages 41c is communicated with the through passage 21c of the second plate-like member 20 and the branch passage 34b of the third plate-like member 30. That is, the through passage 21c of the second plate-like member 20 and the branch passage 34b of the third plate-like member 30 are communicated through the first communication passage 41c.
When viewed in the stacking direction, each of the first communication passages 41d is substantially circular and is formed adjacent to the first communication passage 41c in the width direction. Each of the first communication passages 41d is communicated with the through passage 21d of the second plate-like member 20 and the branch passage 34b of the third plate-like member 30. That is, the through passage 21d of the second plate-like member 20 and the branch passage 34b of the third plate-like member 30 are communicated through the first communication passage 41d. When viewed in the stacking direction, the first communication passages 41e are each substantially circular and are formed alternately with the first communication passage 41a and the two first communication passages 41c. The first communication passages 41e are formed at equal intervals in the arrangement direction. Each of the first communication passages 41e is communicated with the through passage 21e of the second plate-like member 20 and the branch passage 34c of the third plate-like member 30. That is, the through passage 21e of the second plate-like member 20 and the branch passage 34c of the third plate-like member 30 are communicated through the first communication passage 41e.
When viewed in the stacking direction, each of the second communication passages 42 is substantially L-shaped and is formed so as to surround the first communication passage 41e. Each of the second communication passages 42 is communicated with the branch passage 34c and the insertion space 33 of the third plate-like member 30. That is, the branch passage 34c of the third plate-like member 30 and the insertion space 33 of the third plate-like member 30 are communicated through the second communication passage 42. Thus, the through passage 21e of the second plate-like member 20 and the insertion space 33 of the third plate-like member 30 are communicated through the first communication passage 41e, the branch passage 34c of the third plate-like member 30, and the second communication passage 42. The first communication passage 41a, the two first communication passages 41b, the two first communication passages 41c, the four first communication passages 41d, the four first communication passages 41e, and the eight second communication passages 42 constitute the flow passages of the refrigerant distributor 7b.
Next, as
The refrigerant that has made such a return-flow then passes through the through passage 21e of the second plate-like member 20 and the first communication passage 41e of the fourth plate-like member 40 and reaches the branch passage 34c of the third plate-like member 30. The refrigerant that has reached the branch passage 34c of the third plate-like member 30 is divided into flows and makes a return-flow to the fourth plate-like member 40 side. The refrigerant of one divided flow passes through the second communication passage 42 of the fourth plate-like member 40 and makes a return-flow to the third plate-like member 30 side. The refrigerant that has made such a return-flow reaches the insertion space 33 of the third plate-like member 30 and flows out into one of the heat transfer tubes 50.
In Embodiment 1, the insertion spaces 33, the branch passage 34a, the branch passages 34b, and the branch passages 34c, that is, some parts of the flow passages are formed in the projections 31 of the third plate-like member 30 to which the heat transfer tubes 50 are connected. Thus, the refrigerant distributor 7b of Embodiment 1 is downsized by reducing the plate-like members that are required to form parts of the flow passages.
In addition, in most cases, to cause refrigerant to smoothly flow out into the heat transfer tube 50, the insertion space 33 is required to have predetermined dimensions with which the refrigerant does not build up. When the insertion space 33 is formed in the plate-like member, dimensions such as the thickness or the width of the entire plate-like member need to be increased to satisfy the required dimensions. Here, in Embodiment 1, the insertion space 33 is formed in the projection 31 of the third plate-like member. Thus, when the dimensions of the insertion space 33 are ensured, there is no need to increase the sizes of parts not contributing to the formation of the insertion spaces 33. Thus, the refrigerant distributor 7b of Embodiment 1 can be downsized.
Similarly, the branch passage 34a, the branch passage 34b, and the branch passage 34c are also required to have predetermined dimensions with which the refrigerant does not build up, to cause refrigerant to be smoothly divided thereinto. In Embodiment 1, the branch passage 34a, the branch passage 34b, and the branch passage 34c are formed in the projections 31 of the third plate-like member. Thus, when the dimensions of the branch passage 34a, the branch passage 34b, and the branch passage 34c are ensured, there is no need to increase the sizes of parts not contributing to the formation of the insertion spaces 33. Thus, the refrigerant distributor 7b of Embodiment 1 can be downsized.
In addition, with such downsized refrigerant distributor 7b, in the indoor heat exchanger 7, the mounting areas of the heat transfer tubes 50 are ensured, and the heat exchange performance can be improved. In addition, the refrigerant distributor 7b and the indoor heat exchanger 7 can thus be reduced in weight.
In addition, in the refrigerant distributor 7b, reduction in the plate-like members that are required to form parts of the flow passages enables a simplified manufacturing process, thereby enabling manufacturing cost reduction.
In addition, in Embodiment 1, the return flow passages 13a and the return flow passages 13b, that is, some parts of the flow passages are formed in the lying-astride projections 12a and the lying-astride projections 12b of the first plate-like member 10. Thus, the refrigerant distributor 7b of Embodiment 1 is downsized by reducing the plate-like members that are required to form parts of the flow passages.
In addition, the first plate-like member 10 including the return flow passage 13a and the return flow passage 13b can cause the refrigerant that has made a round-trip between the first plate-like member 10 and the third plate-like member 30 to flow again to the third plate-like member 30 side. Thus, refrigerant can flow through the same plate-like member multiple times, and required plate-like members are thereby reduced.
The arc-shaped downstream region of the inside of the projection 31 can prevent the refrigerant flowing through the flow passages of the refrigerant distributor 7b from being concentrated in one place in the downstream region of the inside of the projection 31. Thus, the pressure resistance of the third plate-like member 30A is increased. Accordingly, the thickness can be reduced, and the manufacturing cost can thereby be reduced.
With the third plate-like member 308 having such a tapered shape, sudden widening of the flow passage just in front of a position where refrigerant flows into the heat transfer tube 50 is suppressed. Thus, pressure loss is suggested, and the heat exchange performance of the indoor heat exchanger 7 can thereby be improved.
The flow passages of the refrigerant distributor 7Ab will be described while differences from Embodiment 1 are focused. The through passage 21a is communicated with the inflow passage 11 of the first plate-like member 10 and the branch passage 34a of the third plate-like member 30. Each of the through passages 21b is communicated with the return flow passage 13a of the first plate-like member 10 and the branch passage 34a of the third plate-like member 30. Each of the through passages 21c is communicated with the return flow passage 13a of the first plate-like member 10 and the branch passage 34b of the third plate-like member 30. Each of the through passages 21d is communicated with the return flow passage 13b of the first plate-like member 10 and the branch passage 34b of the third plate-like member 30. Each of the through passages 21e is communicated with the return flow passage 13b of the first plate-like member 10 and the branch passage 34c of the third plate-like member 30.
Next, the refrigerant that has made such a return-flow passes through the through passage 21c of the second plate-like member 20 and reaches the branch passage 34b of the third plate-like member 30. The refrigerant that has reached the branch passage 34b of the third plate-like member 30 is divided into flows and makes a return-flow to the second plate-like member 20 side. The refrigerant of one divided flow passes through the through passage 21d of the second plate-like member 20, reaches the return flow passage 13b of the first plate-like member 10, and makes a return-flow to the second plate-like member 20 side.
The refrigerant that has made such a return-flow then passes through the through passage 21e of the second plate-like member 20 and reaches the branch passage 34c of the third plate-like member 30. The refrigerant that has reached the branch passage 34c of the third plate-like member 30 is divided into the insertion spaces 33 of the third plate-like member 30. The refrigerant of one divided flow flows out into one of the heat transfer tubes 50.
In Embodiment 2, the insertion spaces 33, the branch passage 34a, the branch passages 34b, and the branch passages 34c, that is, some parts of the flow passages are formed in the projections 31 of the third plate-like member 30 to which the heat transfer tubes 50 are connected. Thus, the refrigerant distributor 7Ab of Embodiment 2 is downsized by reducing the plate-like members that are required to form parts of the flow passages.
In addition, in Embodiment 2, in the third plate-like member 30, two projections 31 having the insertion spaces 33 and the projection 31 including the branch passage 34c are formed as one body. Thus, functions of dividing the flow of refrigerant converge into the third plate-like member 30. Consequently, other plate-like members for dividing the flow of refrigerant can be omitted, and the refrigerant distributor 7Ab can thereby be further downsized.
A flow passage of the refrigerant distributor 7Bb will be described while differences from Embodiment 1 are focused. The through passage 21a is communicated with the inflow passage 11 of the first plate-like member 10 and a first sub-branch passage 43a of the fourth plate-like member 40, which will be described later. Each of the through passages 21b is communicated with the return flow passage 13a of the first plate-like member 10 and the first sub-branch passage 43a of the fourth plate-like member 40. Each of the through passages 21c is communicated with the return flow passage 13a of the first plate-like member 10 and a first sub-branch passage 43b of the fourth plate-like member 40, which will be described later. Each of the through passages 21d is communicated with the return flow passage 13b of the first plate-like member 10 and the first sub-branch passage 43b of the fourth plate-like member 40. Each of the through passages 21e is communicated with the return flow passage 13b of the first plate-like member 10 and a second sub-branch passage 44 of the fourth plate-like member 40, which will be described later.
As
When viewed in the stacking direction from the − side to the + side, the second sub-branch passages 44 are each substantially S-shaped and are formed alternately with the first sub-branch passage 43a and the two first sub-branch passages 43b. The second sub-branch passages 44 are formed at equal intervals in the arrangement direction. Each of the second sub-branch passages 44 is communicated with the through passage 21e of the second plate-like member 20 and two insertion spaces 33 of the third plate-like member 30. The first sub-branch passage 43a, the two second sub-branch passages 44, and the four second sub-branch passages 44 constitute the flow passages of the refrigerant distributor 7Bb.
Next, the refrigerant that has made such a return-flow passes through the through passage 21c of the second plate-like member 20 and reaches the first sub-branch passage 43b of the fourth plate-like member 40. The refrigerant that has reached the first sub-branch passage 43b of the fourth plate-like member 40 is divided into flows and makes a return-flow to the second plate-like member 20 side. The refrigerant of one divided flow passes through the through passage 21d of the second plate-like member 20, reaches the return flow passage 13b of the first plate-like member 10, and makes a return-flow to the second plate-like member 20 side.
The refrigerant that has made such a return-flow then passes through the through passage 21e of the second plate-like member 20 and reaches the second sub-branch passage 44 of the fourth plate-like member 40. The refrigerant that has reached the second sub-branch passage 44 of the fourth plate-like member 40 is divided into two insertion spaces 33 of the third plate-like member 30. The refrigerant of one divided flow flows out into one of the heat transfer tubes 50.
In Embodiment 3, the insertion spaces 33, that is, some parts of the flow passage are formed in the projections 31 of the third plate-like member 30 to which the heat transfer tubes 50 are connected. Thus, in Embodiment 3, the refrigerant distributor 7Bb is also downsized by reducing the plate-like members that are required to form parts of the flow passages.
A flow passage of the refrigerant distributor 7Cb will be described while differences from Embodiment 1 are focused.
The positions where the projections 31 including the branch passage 34a, the branch passages 34b, and the branch passages 34c are formed are the same as those of Embodiment 1. In addition, the flow passages from the inflow passage 11 of the first plate-like member 10 to the second communication passage 42 of the fourth plate-like member 40 are also the same as those of Embodiment 1. In Embodiment 4, the branch passage 34a, the branch passages 34b, and the branch passages 34c also constitute the flow passages of the refrigerant distributor 7Cb.
In Embodiment 4, the insertion openings 32 are formed in a planar part of the third plate-like member 30. Thus, the second communication passage 42 of the fourth plate-like member 40 is communicated with the branch passage 34c of the third plate-like member 30 and the insertion opening 32 of the third plate-like member 30.
In Embodiment 4, the branch passage 34a, the branch passages 34b, and the branch passages 34c, that is, some parts of the flow passages are formed in the projections 31 of the third plate-like member 30 to which the heat transfer tubes 50 are connected. Thus, in Embodiment 4, the refrigerant distributor 7Cb is also downsized by reducing the plate-like members that are required to form parts of the flow passages.
Although Embodiments 1 to 4 are described above, the present disclosure is not limited to Embodiments 1 to 4 described above, and modification or application may be made without departing from the spirit of the present disclosure. For example, the indoor heat exchanger 7 or the outdoor heat exchanger 9 may have plural fins joined to the heat transfer tubes 50. The fins are made of, for example, aluminum.
In addition, although the refrigerant distributor 7b with eight branches is described in Embodiments 1 to 4, this is not the only option, and the number of such branches may be changed to a number other than eight by changing the number of the branch passages.
In addition, in Embodiments 1 to 4, there is described a case in which, in the first plate-like member 10, the return flow passage 13a is formed inside the lying-astride projection 12a, and the return flow passage 13b is formed inside the lying-astride projection 12b. However, the return flow passage 13a and the return flow passage 13b may each serve as a flow passage by being formed as grooves penetrating the first plate-like member 10 and being closed by another plate-like member. In addition, the return flow passage 13a and the return flow passage 13b may each be a groove having a thickness smaller than the thickness of the first plate-like member 10. In such cases, the refrigerant distributor 7b can still be downsized as long as a part of the flow passages is formed in the projection 31 of the third plate-like member 30.
In addition, Embodiment 2 may also be combined with Modification 1 of Embodiment 1, and a downstream region of the inside of the projection 31 may have an arc shape. In addition, Embodiment 2 may also be combined with Modification 2 of Embodiment 1, and the face of the third plate-like member 30 on the second plate-like member 20 side may have a tapered shape.
1: refrigeration cycle apparatus, 2: outdoor unit, 3: indoor unit, 4: refrigerant pipe, 5: compressor, 6: flow-switching valve, 7: indoor heat exchanger, 7b: refrigerant distributor, 7Ab: refrigerant distributor, 7Bb: refrigerant distributor, 7Cb: refrigerant distributor, 7a: indoor fan, 8: expansion valve, 9: outdoor heat exchanger, 9a: outdoor fan, 9b: refrigerant distributor, 10: first plate-like member, 11: inflow passage, 12a: lying-astride projection, 12b: lying-astride projection, 13a: return flow passage, 13b: return flow passage, 20: second plate-like member, 21a: through passage, 21b: through passage, 21c: through passage, 21d: through passage, 21e: through passage, 30: third plate-like member, 30A: third plate-like member, 30B: third plate-like member, 31: projection, 32: insertion opening, 33: insertion space, 34a: branch passage, 34b: branch passage, 34c: branch passage, 40: fourth plate-like member, 41a: first communication passage, 41b: first communication passage, 41c: first communication passage, 41d: first communication passage, 41e: first communication passage, 42: second communication passage, 43a: first sub-branch passage, 43b: first sub-branch passage, 44: second sub-branch passage, 50: heat transfer tube
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2021/024368 | 6/28/2021 | WO |
