Patent Application
20160076824
The present invention relates to a stacking-type header, a heat exchanger, and an air-conditioning apparatus.
As a related-art stacking-type header, there is known a stacking-type header including a first plate-shaped unit having a plurality of outlet flow passages formed therein, and a second plate-shaped unit stacked on the first plate-shaped unit and having a distribution flow passage formed therein, for distributing refrigerant, which passes through an inlet flow passage to flow into the second plate-shaped unit, to the plurality of outlet flow passages formed in the first plate-shaped unit to cause the refrigerant to flow out from the second plate-shaped unit. The distribution flow passage includes a branching flow passage having a plurality of grooves extending perpendicular to a refrigerant inflow direction. The refrigerant passing through the inlet flow passage to flow into the branching flow passage passes through the plurality of grooves to be branched into a plurality of flows, to thereby pass through the plurality of outlet flow passages formed in the first plate-shaped unit to flow out from the first plate-shaped unit (for example, see Patent Literature 1).
In such a stacking-type header, when the inflow position of the refrigerant flowing into the branching flow passage is misaligned from the center of the plurality of grooves due to manufacture error caused during processing, lamination, or other factors, the refrigerant may be increased or decreased in inflow amount in any of the branching directions, which may cause a deficiency or an excess of the refrigerant. Further, when the stacking-type header is used under a state in which the inflow direction of the refrigerant flowing into the branching flow passage is not parallel to the gravity direction, the refrigerant may be affected by the gravity to cause a deficiency or an excess of the refrigerant in any of the branching directions. In other words, the related-art stacking-type header has a problem in that the uniformity in distribution of the refrigerant is low.
The present invention has been made in view of the above-mentioned problems, and has an object to provide a stacking-type header improved in uniformity in distribution of refrigerant. Further, the present invention has an object to provide a heat exchanger improved in uniformity in distribution of refrigerant. Further, the present invention has an object to provide an air-conditioning apparatus improved in uniformity in distribution of refrigerant.
According to one embodiment of the present invention, there is provided a stacking-type header, including: a first plate-shaped unit having a plurality of first outlet flow passages formed therein; and a second plate-shaped unit stacked on the first plate-shaped unit, the second plate-shaped unit having a distribution flow passage formed therein, the distribution flow passage being configured to distribute refrigerant, which passes through a first inlet flow passage to flow into the second plate-shaped unit, to the plurality of first outlet flow passages to cause the refrigerant to flow out from the second plate-shaped unit, in which the distribution flow passage includes a branching flow passage including a straight-line part perpendicular to a gravity direction, and in which the refrigerant flows into the branching flow passage through a part between both ends of the straight-line part, passes through both the ends, and flows out from the branching flow passage through a plurality of end portions.
In the stacking-type header according to the one embodiment of the present invention, the distribution flow passage includes the branching flow passage including the straight-line part perpendicular to the gravity direction, and the refrigerant flows into the branching flow passage through the part between both the ends of the straight-line part, passes through both the ends, and flows out from the branching flow passage through the plurality of end portions. Therefore, the phenomenon that a deficiency or an excess of the refrigerant is caused in any of the branching directions due to the misalignment of the inflow position of the refrigerant flowing into the branching flow passage is suppressed, which improves the uniformity in distribution of the refrigerant. Further, the angles of the respective branching directions in the branching flow passage with respect to the gravity direction are uniform, which reduces the influence of the gravity and improves the uniformity in distribution of the refrigerant.
Now, a stacking-type header according to the present invention is described with reference to the drawings.
Note that, in the following, there is described a case where the stacking-type header according to the present invention distributes refrigerant flowing into a heat exchanger, but the stacking-type header according to the present invention may distribute refrigerant flowing into other devices. Further, the configuration, operation, and other matters described below are merely examples, and the present invention is not limited to such configuration, operation, and other matters. Further, in the drawings, the same or similar components are denoted by the same reference symbols, or the reference symbols therefor are omitted. Further, the illustration of details in the structure is appropriately simplified or omitted. Further, overlapping description or similar description is appropriately simplified or omitted.
A heat exchanger according to Embodiment 1 is described.
Now, the configuration of the heat exchanger according to Embodiment 1 is described.
As illustrated in
The stacking-type header 2 includes a refrigerant inflow port 2A and a plurality of refrigerant outflow ports 2B. The header 3 includes a plurality of refrigerant inflow ports 3A and a refrigerant outflow port 3B. Refrigerant pipes are connected to the refrigerant inflow port 2A of the stacking-type header 2 and the refrigerant outflow port 3B of the header 3. The plurality of first heat transfer tubes 4 are connected between the plurality of refrigerant outflow ports 2B of the stacking-type header 2 and the plurality of refrigerant inflow ports 3A of the header 3.
The first heat transfer tube 4 is a flat tube having a plurality of flow passages formed therein. The first heat transfer tube 4 is made of, for example, aluminum. End portions of the plurality of first heat transfer tubes 4 on the stacking-type header 2 side are connected to the plurality of refrigerant outflow ports 2B of the stacking-type header 2 under a state in which the end portions are retained by the plate-shaped retaining member 5. The retaining member 5 is made of, for example, aluminum. The plurality of fins 6 are joined to the first heat transfer tubes 4. The fin 6 is made of, for example, aluminum. It is preferred that the first heat transfer tubes 4 and the fins 6 be joined by brazing. Note that, in
Now, the flow of the refrigerant in the heat exchanger according to Embodiment 1 is described.
The refrigerant flowing through the refrigerant pipe passes through the refrigerant inflow port 2A to flow into the stacking-type header 2 to be distributed, and then passes through the plurality of refrigerant outflow ports 2B to flow out toward the plurality of first heat transfer tubes 4. In the plurality of first heat transfer tubes 4, the refrigerant exchanges heat with air supplied by a fan, for example. The refrigerant flowing through the plurality of first heat transfer tubes 4 passes through the plurality of refrigerant inflow ports 3A to flow into the header 3 to be joined, and then passes through the refrigerant outflow port 3B to flow out toward the refrigerant pipe. The refrigerant can reversely flow.
Now, the configuration of the stacking-type header of the heat exchanger according to Embodiment 1 is described.
As illustrated in
The first plate-shaped unit 11 is stacked on the refrigerant outflow side. The first plate-shaped unit 11 includes a first plate-shaped member 21. The first plate-shaped unit 11 has a plurality of first outlet flow passages 11A formed therein. The plurality of first outlet flow passages 11A correspond to the plurality of refrigerant outflow ports 2B in
The first plate-shaped member 21 has a plurality of flow passages 21A formed therein. The plurality of flow passages 21A are each a through hole having an inner peripheral surface shaped conforming to an outer peripheral surface of the first heat transfer tube 4. When the first plate-shaped member 21 is stacked, the plurality of flow passages 21A function as the plurality of first outlet flow passages 11A. The first plate-shaped member 21 has a thickness of about 1 mm to 10 mm, and is made of aluminum, for example. When the plurality of flow passages 21A are formed by press working or other processing, the work is simplified, and the manufacturing cost is reduced.
The end portions of the first heat transfer tubes 4 are projected from the surface of the retaining member 5. When the first plate-shaped unit 11 is stacked on the retaining member 5 so that the inner peripheral surfaces of the first outlet flow passages 11A are fitted to the outer peripheral surfaces of the respective end portions of the first heat transfer tubes 4, the first heat transfer tubes 4 are connected to the first outlet flow passages 11A. The first outlet flow passages 11A and the first heat transfer tubes 4 may be positioned through, for example, fitting between a convex portion formed in the retaining member 5 and a concave portion formed in the first plate-shaped unit 11. In such a case, the end portions of the first heat transfer tubes 4 may not be projected from the surface of the retaining member 5. The retaining member 5 may be omitted so that the first heat transfer tubes 4 are directly connected to the first outlet flow passages 11A. In such a case, the component cost and the like are reduced.
The second plate-shaped unit 12 is stacked on the refrigerant inflow side. The second plate-shaped unit 12 includes a second plate-shaped member 22 and a plurality of third plate-shaped members 23_1 to 23_3. The second plate-shaped unit 12 has a distribution flow passage 12A formed therein. The distribution flow passage 12A includes a first inlet flow passage 12a and a plurality of branching flow passages 12b. The first inlet flow passage 12a corresponds to the refrigerant inflow port 2A in
The second plate-shaped member 22 has a flow passage 22A formed therein. The flow passage 22A is a circular through hole. When the second plate-shaped member 22 is stacked, the flow passage 22A functions as the first inlet flow passage 12a. The second plate-shaped member 22 has a thickness of about 1 mm to 10 mm, and is made of aluminum, for example. When the flow passage 22A is formed by press working or other processing, the work is simplified, and the manufacturing cost and the like are reduced.
For example, a fitting or other such component is provided on the surface of the second plate-shaped member 22 on the refrigerant inflow side, and the refrigerant pipe is connected to the first inlet flow passage 12a through the fitting or other such component. The inner peripheral surface of the first inlet flow passage 12a may be shaped to be fitted to the outer peripheral surface of the refrigerant pipe so that the refrigerant pipe may be directly connected to the first inlet flow passage 12a without using the fitting or other such component. In such a case, the component cost and the like are reduced.
The plurality of third plate-shaped members 23_1 to 23_3 respectively have a plurality of flow passages 23A_1 to 23A_3 formed therein. The plurality of flow passages 23A_1 to 23A_3 are each a through groove. The shape of the through groove is described in detail later. When the plurality of third plate-shaped members 23_1 to 23_3 are stacked, each of the plurality of flow passages 23A_1 to 23A_3 functions as the branching flow passage 12b. The plurality of third plate-shaped members 23_1 to 23_3 each have a thickness of about 1 mm to 10 mm, and are made of aluminum, for example. When the plurality of flow passages 23A_1 to 23A_3 are formed by press working or other processing, the work is simplified, and the manufacturing cost and the like are reduced.
In the following, in some cases, the plurality of third plate-shaped members 23_1 to 23_3 are collectively referred to as the third plate-shaped member 23. In the following, in some cases, the plurality of flow passages 23A_1 to 23A_3 are collectively referred to as the flow passage 23A. In the following, in some cases, the retaining member 5, the first plate-shaped member 21, the second plate-shaped member 22, and the third plate-shaped member 23 are collectively referred to as the plate-shaped member.
The branching flow passage 12b branches the refrigerant flowing therein into two flows to cause the refrigerant to flow out therefrom. Therefore, when the number of the first heat transfer tubes 4 to be connected is eight, at least three third plate-shaped members 23 are required. When the number of the first heat transfer tubes 4 to be connected is sixteen, at least four third plate-shaped members 23 are required. The number of the first heat transfer tubes 4 to be connected is not limited to powers of 2. In such a case, the branching flow passage 12b and a non-branching flow passage may be combined with each other. Note that, the number of the first heat transfer tubes 4 to be connected may be two.
As illustrated in
In order to branch the refrigerant flowing into the flow passage to have different heights and cause the refrigerant to flow out therefrom, the end portion 23a and the end portion 23b are positioned at heights different from each other. In particular, when one of the end portion 23a and the end portion 23b is positioned on the upper side relative to the straight-line part 23c, and the other thereof is positioned on the lower side relative to the straight-line part 23c, each distance from the opening port 23f along the flow passage 23A to each of the end portion 23a and the end portion 23b can be less biased without complicating the shape. When the straight line connecting between the end portion 23a and the end portion 23b is set parallel to the longitudinal direction of the third plate-shaped member 23, the dimension of the third plate-shaped member 23 in the transverse direction can be decreased, which reduces the component cost, the weight, and the like. Further, when the straight line connecting between the end portion 23a and the end portion 23b is set parallel to the array direction of the first heat transfer tubes 4, space saving can be achieved in the heat exchanger 1.
As illustrated in
The branching flow passage 12b may branch the refrigerant flowing therein into two flows, and further branch the branched refrigerant into a plurality of flows. In such a case, the flow passage 23A may be formed as a through groove shaped so that a connecting part 23g for connecting the end portion 23d of the straight-line part 23c to the end portion 23a and a connecting part 23h for connecting the end portion 23e of the straight-line part 23c to the end portion 23b are branched. When the branching flow passage 12b branches the refrigerant flowing therein into two flows, but does not further branch the branched refrigerant into a plurality of flows, the uniformity in distribution of the refrigerant is reliably improved. The connecting parts 23g and 23h may each be a straight line or a curved line.
Now, the flow of the refrigerant in the stacking-type header of the heat exchanger according to Embodiment 1 is described.
As illustrated in
Similarly, the refrigerant flowing into the opening port 23f of the flow passage 23A formed in the third plate-shaped member 23_2 hits against the surface of the member stacked adjacent to the third plate-shaped member 23_2, and is branched into two flows respectively toward the end portion 23d and the end portion 23e of the straight-line part 23c. The branched refrigerant reaches each of the end portions 23a and 23b of the flow passage 23A, and flows into the opening port 23f of the flow passage 23A formed in the third plate-shaped member 23_3.
Similarly, the refrigerant flowing into the opening port 23f of the flow passage 23A formed in the third plate-shaped member 23_3 hits against the surface of the member stacked adjacent to the third plate-shaped member 23_3, and is branched into two flows respectively toward the end portion 23d and the end portion 23e of the straight-line part 23c. The branched refrigerant reaches each of the end portions 23a and 23b of the flow passage 23A, and passes through the flow passage 21A of the first plate-shaped member 21 to flow into the first heat transfer tube 4.
Now, a method of stacking the respective plate-shaped members of the stacking-type header of the heat exchanger according to Embodiment 1 is described.
The respective plate-shaped members may be stacked by brazing. A both-side clad member having a brazing material rolled on both surfaces thereof may be used for all of the plate-shaped members or alternate plate-shaped members to supply the brazing material for joining. A one-side clad member having a brazing material rolled on one surface thereof may be used for all of the plate-shaped members to supply the brazing material for joining. A brazing-material sheet may be stacked between the respective plate-shaped members to supply the brazing material. A paste brazing material may be applied between the respective plate-shaped members to supply the brazing material. A both-side clad member having a brazing material rolled on both surfaces thereof may be stacked between the respective plate-shaped members to supply the brazing material.
Through lamination with use of brazing, the plate-shaped members are stacked without a gap therebetween, which suppresses leakage of the refrigerant and further secures the pressure resistance. When the plate-shaped members are pressurized during brazing, the occurrence of brazing failure is further suppressed. When processing that promotes formation of a fillet, such as forming a rib at a position at which leakage of the refrigerant is liable to occur, is performed, the occurrence of brazing failure is further suppressed.
Further, when all of the members to be subjected to brazing, including the first heat transfer tube 4 and the fin 6, are made of the same material (for example, made of aluminum), the members may be collectively subjected to brazing, which improves the productivity. After the brazing in the stacking-type header 2 is performed, the brazing of the first heat transfer tube 4 and the fin 6 may be performed. Further, only the first plate-shaped unit 11 may be first joined to the retaining member 5 by brazing, and the second plate-shaped unit 12 may be joined by brazing thereafter.
In particular, a plate-shaped member having a brazing material rolled on both surfaces thereof, in other words, a both-side clad member may be stacked between the respective plate-shaped members to supply the brazing material. As illustrated in
The both-side clad member 24 has a flow passage 24A, which passes through the both-side clad member 24, formed in a region that is opposed to a refrigerant outflow region of the flow passage formed in the plate-shaped member stacked adjacent on the refrigerant inflow side. The flow passage 24A formed in the both-side clad member 24 stacked between the second plate-shaped member 22 and the third plate-shaped member 23 is a circular through hole. The flow passage 24A formed in the both-side clad member 24_5 stacked between the first plate-shaped member 21 and the retaining member 5 is a through hole having an inner peripheral surface shaped conforming to the outer peripheral surface of the first heat transfer tube 4.
When the both-side clad member 24 is stacked, the flow passage 24A functions as a refrigerant partitioning flow passage for the first outlet flow passage 11A and the distribution flow passage 12A. Under a state in which the both-side clad member 24_5 is stacked on the retaining member 5, the end portions of the first heat transfer tubes 4 may be or not be projected from the surface of the both-side clad member 24_5. When the flow passage 24A is formed by press working or other processing, the work is simplified, and the manufacturing cost and the like are reduced. When all of the members to be subjected to brazing, including the both-side clad member 24, are made of the same material (for example, made of aluminum), the members may be collectively subjected to brazing, which improves the productivity.
Through formation of the refrigerant partitioning flow passage by the both-side clad member 24, in particular, the branched flows of refrigerant flowing out from the branching flow passage 12b can be reliably partitioned from each other. Further, by the amount of the thickness of each both-side clad member 24, an entrance length for the refrigerant flowing into the branching flow passage 12b or the first outlet flow passage 11A can be secured, which improves the uniformity in distribution of the refrigerant. Further, the flows of the refrigerant can be reliably partitioned from each other, and hence the degree of freedom in design of the branching flow passage 12b can be increased.
As illustrated in
As shown in
Now, an example of a usage mode of the heat exchanger according to Embodiment 1 is described.
Note that, in the following, there is described a case where the heat exchanger according to Embodiment 1 is used for an air-conditioning apparatus, but the present invention is not limited to such a case, and for example, the heat exchanger according to Embodiment 1 may be used for other refrigeration cycle apparatus including a refrigerant circuit. Further, there is described a case where the air-conditioning apparatus switches between a cooling operation and a heating operation, but the present invention is not limited to such a case, and the air-conditioning apparatus may perform only the cooling operation or the heating operation.
As illustrated in
The controller 59 is connected to, for example, the compressor 52, the four-way valve 53, the expansion device 55, the heat source-side fan 57, the load-side fan 58, and various sensors. The controller 59 switches the flow passage of the four-way valve 53 to switch between the cooling operation and the heating operation. The heat source-side heat exchanger 54 acts as a condensor during the cooling operation, and acts as an evaporator during the heating operation. The load-side heat exchanger 56 acts as the evaporator during the cooling operation, and acts as the condensor during the heating operation.
The flow of the refrigerant during the cooling operation is described.
The refrigerant in a high-pressure and high-temperature gas state discharged from the compressor 52 passes through the four-way valve 53 to flow into the heat source-side heat exchanger 54, and is condensed through heat exchange with the outside air supplied by the heat source-side fan 57, to thereby become the refrigerant in a high-pressure liquid state, which flows out from the heat source-side heat exchanger 54. The refrigerant in the high-pressure liquid state flowing out from the heat source-side heat exchanger 54 flows into the expansion device 55 to become the refrigerant in a low-pressure two-phase gas-liquid state. The refrigerant in the low-pressure two-phase gas-liquid state flowing out from the expansion device 55 flows into the load-side heat exchanger 56 to be evaporated through heat exchange with indoor air supplied by the load-side fan 58, to thereby become the refrigerant in a low-pressure gas state, which flows out from the load-side heat exchanger 56. The refrigerant in the low-pressure gas state flowing out from the load-side heat exchanger 56 passes through the four-way valve 53 to be sucked into the compressor 52.
The flow of the refrigerant during the heating operation is described.
The refrigerant in a high-pressure and high-temperature gas state discharged from the compressor 52 passes through the four-way valve 53 to flow into the load-side heat exchanger 56, and is condensed through heat exchange with the indoor air supplied by the load-side fan 58, to thereby become the refrigerant in a high-pressure liquid state, which flows out from the load-side heat exchanger 56. The refrigerant in the high-pressure liquid state flowing out from the load-side heat exchanger 56 flows into the expansion device 55 to become the refrigerant in a low-pressure two-phase gas-liquid state. The refrigerant in the low-pressure two-phase gas-liquid state flowing out from the expansion device 55 flows into the heat source-side heat exchanger 54 to be evaporated through heat exchange with the outside air supplied by the heat source-side fan 57, to thereby become the refrigerant in a low-pressure gas state, which flows out from the heat source-side heat exchanger 54. The refrigerant in the low-pressure gas state flowing out from the heat source-side heat exchanger 54 passes through the four-way valve 53 to be sucked into the compressor 52.
The heat exchanger 1 is used for at least one of the heat source-side heat exchanger 54 or the load-side heat exchanger 56. When the heat exchanger 1 acts as the evaporator, the heat exchanger 1 is connected so that the refrigerant flows in from the stacking-type header 2 and the refrigerant flows out from the header 3. In other words, when the heat exchanger 1 acts as the evaporator, the refrigerant in the two-phase gas-liquid state passes through the refrigerant pipe to flow into the stacking-type header 2, and the refrigerant in the gas state passes through the first heat transfer tube 4 to flow into the header 3. Further, when the heat exchanger 1 acts as the condensor, the refrigerant in the gas state passes through the refrigerant pipe to flow into the header 3, and the refrigerant in the liquid state passes through the first heat transfer tube 4 to flow into the stacking-type header 2.
Now, an action of the heat exchanger according to Embodiment 1 is described.
The second plate-shaped unit 12 of the stacking-type header 2 has the distribution flow passage 12A including the branching flow passage 12b formed therein. In the branching flow passage 12b, the refrigerant flows therein through the opening port 23f formed between the end portion 23d and the end portion 23e of the straight-line part 23c of the flow passage 23A, passes through each of the end portion 23d and the end portion 23e, and flows out therefrom through the end portions 23a and 23b of the flow passage 23A. Therefore, even when the position of the opening port 23f is misaligned due to the manufacture error caused during processing, lamination, or other factors, the phenomenon that the refrigerant is increased or decreased in inflow amount in any of the branching directions is less liable to occur, which improves the uniformity in distribution of the refrigerant. Further, the angles of the respective branching directions with respect to the gravity direction are uniform, which reduces the influence of the gravity and improves the uniformity in distribution of the refrigerant.
Further, in the stacking-type header 2, in the branching flow passage 12b, the refrigerant flows therein through a part between the end portion 23d and the end portion 23e of the straight-line part 23c of the flow passage 23A in a direction perpendicular to the straight-line part 23c. Therefore, in addition to the angles of the respective branching directions with respect to the gravity direction, the angles of the respective branching directions with respect to the refrigerant inflow direction become uniform, which further improves the uniformity in distribution of the refrigerant.
Further, the flow passage 23A formed in the third plate-shaped member 23 is a through groove, and the branching flow passage 12b is formed by stacking the third plate-shaped member 23. Therefore, the processing and assembly are simplified, and the production efficiency, the manufacturing cost, and the like are reduced.
In particular, even when the refrigerant is intended to be distributed into flows having different heights, in other words, even when the end portion 23a and the end portion 23b of the flow passage 23A are positioned at heights different from each other, in the branching flow passage 12b, the refrigerant branches at the straight-line part 23c perpendicular to the gravity direction. Therefore, the uniformity in distribution of the refrigerant is improved.
In particular, even when the heat exchanger 1 is used in an inclined manner, in other words, even when the array direction of the first outlet flow passages 11A intersects with the gravity direction, in the branching flow passage 12b, the refrigerant branches at the straight-line part 23c perpendicular to the gravity direction. Therefore, the uniformity in distribution of the refrigerant is improved.
In particular, in the related-art stacking-type header, when the refrigerant flowing therein is in a two-phase gas-liquid state, the refrigerant is easily affected by the gravity, and it is difficult to equalize the flow rate and the quality of the refrigerant flowing into each heat transfer tube. In the stacking-type header 2, however, regardless of the flow rate and the quality of the refrigerant in the two-phase gas-liquid state flowing therein, the refrigerant is less liable to be affected by the gravity, and the flow rate and the quality of the refrigerant flowing into each first heat transfer tube 4 can be equalized.
In particular, in the related-art stacking-type header, when the heat transfer tube is changed from a circular tube to a flat tube for the purpose of reducing the refrigerant amount or achieving space saving in the heat exchanger, the stacking-type header is required to be upsized in the entire peripheral direction perpendicular to the refrigerant inflow direction. On the other hand, the stacking-type header 2 is not required to be upsized in the entire peripheral direction perpendicular to the refrigerant inflow direction, and thus space saving is achieved in the heat exchanger 1. In other words, in the related-art stacking-type header, when the heat transfer tube is changed from a circular tube to a flat tube, the sectional area of the flow passage in the heat transfer tube is reduced, and thus the pressure loss caused in the heat transfer tube is increased. Therefore, it is necessary to further reduce the angular interval between the plurality of grooves forming the branching flow passage to increase the number of paths (in other words, the number of heat transfer tubes), which causes upsize of the stacking-type header in the entire peripheral direction perpendicular to the refrigerant inflow direction. On the other hand, in the stacking-type header 2, even when the number of paths is required to be increased, the number of the third plate-shaped members 23 is only required to be increased, and hence the upsize of the stacking-type header 2 in the entire peripheral direction perpendicular to the refrigerant inflow direction is suppressed. Note that, the stacking-type header 2 is not limited to the case where the first heat transfer tube 4 is a flat tube.
As illustrated in
The plurality of flow passages 22A may not be formed in regions opposed to refrigerant inflow regions of the flow passages 23A formed in the third plate-shaped member 23. As illustrated in
As illustrated in
As illustrated in
The third plate-shaped member 23 (for example, the third plate-shaped member 23_1) stacked on the third plate-shaped member 23 having the flow passage 23B formed therein on the side opposite to the side on which the first plate-shaped unit 11 is present may include a flow passage 23C for returning the refrigerant flowing therein through the flow passage 23B to the flow passage 23A of the third plate-shaped member 23 having the flow passage 23B formed therein without branching the refrigerant, or may include the flow passage 23A for returning the refrigerant while branching the refrigerant.
As illustrated in
As illustrated in
As illustrated in
As illustrated in
A heat exchanger according to Embodiment 2 is described.
Note that, overlapping description or similar description to that of Embodiment 1 is appropriately simplified or omitted.
Now, the configuration of the heat exchanger according to Embodiment 2 is described.
As illustrated in
The stacking-type header 2 includes the refrigerant inflow port 2A, the plurality of refrigerant outflow ports 2B, a plurality of refrigerant inflow ports 2C, and a refrigerant outflow port 2D. The refrigerant pipes are connected to the refrigerant inflow port 2A of the stacking-type header 2 and the refrigerant outflow port 2D of the stacking-type header 2. The first heat transfer tube 4 is a flat tube subjected to hair-pin bending. The plurality of first heat transfer tubes 4 are connected between the plurality of refrigerant outflow ports 2B of the stacking-type header 2 and the plurality of refrigerant inflow ports 2C of the stacking-type header 2.
Now, the flow of the refrigerant in the heat exchanger according to Embodiment 2 is described.
The refrigerant flowing through the refrigerant pipe passes through the refrigerant inflow port 2A to flow into the stacking-type header 2 to be distributed, and then passes through the plurality of refrigerant outflow ports 2B to flow out toward the plurality of first heat transfer tubes 4. In the plurality of first heat transfer tubes 4, the refrigerant exchanges heat with air supplied by a fan, for example. The refrigerant passing through the plurality of first heat transfer tubes 4 passes through the plurality of refrigerant inflow ports 2C to flow into the stacking-type header 2 to be joined, and then passes through the refrigerant outflow port 2D to flow out toward the refrigerant pipe. The refrigerant can reversely flow.
Now, the configuration of the stacking-type header of the heat exchanger according to Embodiment 2 is described.
As illustrated in
The first plate-shaped unit 11 has the plurality of first outlet flow passages 11A and a plurality of second inlet flow passages 11B formed therein. The plurality of second inlet flow passages 11B correspond to the plurality of refrigerant inflow ports 2C in
The first plate-shaped member 21 has a plurality of flow passages 21B formed therein. The plurality of flow passages 21B are each a through hole having an inner peripheral surface shaped conforming to an outer peripheral surface of the first heat transfer tube 4. When the first plate-shaped member 21 is stacked, the plurality of flow passages 21B function as the plurality of second inlet flow passages 11B.
The second plate-shaped unit 12 has the distribution flow passage 12A and a joining flow passage 12B formed therein. The joining flow passage 12B includes a mixing flow passage 12c and a second outlet flow passage 12d. The second outlet flow passage 12d corresponds to the refrigerant outflow port 2D in
The second plate-shaped member 22 has a flow passage 22B formed therein. The flow passage 22B is a circular through hole. When the second plate-shaped member 22 is stacked, the flow passage 22B functions as the second outlet flow passage 12d. Note that, a plurality of flow passages 22B, in other words, a plurality of second outlet flow passages 12d may be formed.
The plurality of third plate-shaped members 23_1 to 23_3 respectively have a plurality of flow passages 23D_1 to 23D_3 formed therein. The plurality of flow passages 23D_1 to 23D_3 are each a rectangular through hole passing through substantially the entire region in the height direction of the third plate-shaped member 23. When the plurality of third plate-shaped members 23_1 to 23_3 are stacked, each of the flow passages 23D_1 to 23D_3 functions as the mixing flow passage 12c. The plurality of flow passages 23D_1 to 23D_3 may not have a rectangular shape. In the following, in some cases, the plurality of flow passages 23D_1 to 23D_3 may be collectively referred to as the flow passage 23D.
In particular, it is preferred to stack the both-side clad member 24 having a brazing material rolled on both surfaces thereof between the respective plate-shaped members to supply the brazing material. The flow passage 24B formed in the both-side clad member 24_5 stacked between the retaining member 5 and the first plate-shaped member 21 is a through hole having an inner peripheral surface shaped conforming to the outer peripheral surface of the first heat transfer tube 4. The flow passage 24B formed in the both-side clad member 24_4 stacked between the first plate-shaped member 21 and the third plate-shaped member 23_3 is a circular through hole. The flow passage 24B formed in other both-side clad members 24 stacked between the third plate-shaped member 23 and the second plate-shaped member 22 is a rectangular through hole passing through substantially the entire region in the height direction of the both-side clad member 24. When the both-side clad member 24 is stacked, the flow passage 24B functions as the refrigerant partitioning flow passage for the second inlet flow passage 11B and the joining flow passage 12B.
Note that, the flow passage 22B functioning as the second outlet flow passage 12d may be formed in a different plate-shaped member other than the second plate-shaped member 22 of the second plate-shaped unit 12, the both-side clad member 24, or other members. In such a case, a notch may be formed, which communicates between a part of the flow passage 23D or the flow passage 24B and, for example, a side surface of the different plate-shaped member or the both-side clad member 24. The mixing flow passage 12c may be turned back so that the flow passage 22B functioning as the second outlet flow passage 12d is formed in the first plate-shaped member 21. In other words, the present invention encompasses a configuration in which the second outlet flow passage 12d is formed in the first plate-shaped unit 11, and the “joining flow passage” of the present invention encompasses joining flow passages other than the joining flow passage 12B in which the second outlet flow passage 12d is formed in the second plate-shaped unit 12.
Now, the flow of the refrigerant in the stacking-type header of the heat exchanger according to Embodiment 2 is described.
As illustrated in
Now, an example of a usage mode of the heat exchanger according to Embodiment 2 is described.
As illustrated in
Now, the action of the heat exchanger according to Embodiment 2 is described. In the stacking-type header 2, the first plate-shaped unit 11 has the plurality of second inlet flow passages 11B formed therein, and the second plate-shaped unit 12 has the joining flow passage 12B formed therein. Therefore, the header 3 is unnecessary, and thus the component cost and the like of the heat exchanger 1 are reduced. Further, the header 3 is unnecessary, and accordingly, it is possible to extend the first heat transfer tube 4 to increase the number of the fins 6 and the like, in other words, increase the mounting volume of the heat exchanging unit of the heat exchanger 1.
A heat exchanger according to Embodiment 3 is described.
Note that, overlapping description or similar description to that of each of Embodiment 1 and Embodiment 2 is appropriately simplified or omitted.
Now, the configuration of the heat exchanger according to Embodiment 3 is described.
As illustrated in
The stacking-type header 2 includes a plurality of refrigerant turn-back ports 2E. Similarly to the first heat transfer tube 4, the second heat transfer tube 7 is a flat tube subjected to hair-pin bending. The plurality of first heat transfer tubes 4 are connected between the plurality of refrigerant outflow ports 2B and the plurality of refrigerant turn-back ports 2E of the stacking-type header 2, and the plurality of second heat transfer tubes 7 are connected between the plurality of refrigerant turn-back ports 2E and the plurality of refrigerant inflow ports 2C of the stacking-type header 2.
Now, the flow of the refrigerant in the heat exchanger according to Embodiment 3 is described.
The refrigerant flowing through the refrigerant pipe passes through the refrigerant inflow port 2A to flow into the stacking-type header 2 to be distributed, and then passes through the plurality of refrigerant outflow ports 2B to flow out toward the plurality of first heat transfer tubes 4. In the plurality of first heat transfer tubes 4, the refrigerant exchanges heat with air supplied by a fan, for example. The refrigerant passing through the plurality of first heat transfer tubes 4 flows into the plurality of refrigerant turn-back ports 2E of the stacking-type header 2 to be turned back, and flows out therefrom toward the plurality of second heat transfer tubes 7. In the plurality of second heat transfer tubes 7, the refrigerant exchanges heat with air supplied by a fan, for example. The flows of the refrigerant passing through the plurality of second heat transfer tubes 7 pass through the plurality of refrigerant inflow ports 2C to flow into the stacking-type header 2 to be joined, and the joined refrigerant passes through the refrigerant outflow port 2D to flow out therefrom toward the refrigerant pipe. The refrigerant can reversely flow.
Now, the configuration of the stacking-type header of the heat exchanger according to Embodiment 3 is described.
As illustrated in
The first plate-shaped unit 11 has the plurality of first outlet flow passages 11A, the plurality of second inlet flow passages 11B, and a plurality of turn-back flow passages 11C formed therein. The plurality of turn-back flow passages 11C correspond to the plurality of refrigerant turn-back ports 2E in
The first plate-shaped member 21 has a plurality of flow passages 21C formed therein. The plurality of flow passages 21C are each a through hole having an inner peripheral surface shaped to surround the outer peripheral surface of the end portion of the first heat transfer tube 4 on the refrigerant outflow side and the outer peripheral surface of the end portion of the second heat transfer tube 7 on the refrigerant inflow side. When the first plate-shaped member 21 is stacked, the plurality of flow passages 21C function as the plurality of turn-back flow passages 11C.
In particular, it is preferred to stack the both-side clad member 24 having a brazing material rolled on both surfaces thereof between the respective plate-shaped members to supply the brazing material. The flow passage 24C formed in the both-side clad member 24_5 stacked between the retaining member 5 and the first plate-shaped member 21 is a through hole having an inner peripheral surface shaped to surround the outer peripheral surface of the end portion of the first heat transfer tube 4 on the refrigerant outflow side and the outer peripheral surface of the end portion of the second heat transfer tube 7 on the refrigerant inflow side. When the both-side clad member 24 is stacked, the flow passage 24C functions as the refrigerant partitioning flow passage for the turn-back flow passage 11C.
Now, the flow of the refrigerant in the stacking-type header of the heat exchanger according to Embodiment 3 is described.
As illustrated in
Now, an example of a usage mode of the heat exchanger according to Embodiment 3 is described.
As illustrated in
Further, when the heat exchanger 1 acts as the condensor, the heat exchanger 1 is arranged so that the first heat transfer tube 4 is positioned on the upstream side (windward side) of the air stream generated by the heat source-side fan 57 or the load-side fan 58 with respect to the second heat transfer tube 7. In other words, there is obtained a relationship that the flow of the refrigerant from the second heat transfer tube 7 to the first heat transfer tube 4 and the air stream are opposed to each other. The refrigerant of the first heat transfer tube 4 is lower in temperature than the refrigerant of the second heat transfer tube 7. The air stream generated by the heat source-side fan 57 or the load-side fan 58 is lower in temperature on the upstream side of the heat exchanger 1 than on the downstream side of the heat exchanger 1. As a result, in particular, the refrigerant can be subcooled (so-called subcooling) by the low-temperature air stream flowing on the upstream side of the heat exchanger 1, which improves the condensor performance. Note that, the heat source-side fan 57 and the load-side fan 58 may be arranged on the windward side or the leeward side.
Now, the action of the heat exchanger according to Embodiment 3 is described. In the heat exchanger 1, the first plate-shaped unit 11 has the plurality of turn-back flow passages 11C formed therein, and in addition to the plurality of first heat transfer tubes 4, the plurality of second heat transfer tubes 7 are connected. For example, it is possible to increase the area in a state of the front view of the heat exchanger 1 to increase the heat exchange amount, but in this case, the housing that incorporates the heat exchanger 1 is upsized. Further, it is possible to decrease the interval between the fins 6 to increase the number of the fins 6, to thereby increase the heat exchange amount. In this case, however, from the viewpoint of drainage performance, frost formation performance, and anti-dust performance, it is difficult to decrease the interval between the fins 6 to less than about 1 mm, and thus the increase in heat exchange amount may be insufficient. On the other hand, when the number of rows of the heat transfer tubes is increased as in the heat exchanger 1, the heat exchange amount can be increased without changing the area in the state of the front view of the heat exchanger 1, the interval between the fins 6, or other matters. When the number of rows of the heat transfer tubes is two, the heat exchange amount is increased about 1.5 times or more. Note that, the number of rows of the heat transfer tubes may be three or more. Still further, the area in the state of the front view of the heat exchanger 1, the interval between the fins 6, or other matters may be changed.
Further, the header (stacking-type header 2) is arranged only on one side of the heat exchanger 1. For example, when the heat exchanger 1 is arranged in a bent state along a plurality of side surfaces of the housing incorporating the heat exchanger 1 in order to increase the mounting volume of the heat exchanging unit, the end portion may be misaligned in each row of the heat transfer tubes because the curvature radius of the bent part differs depending on each row of the heat transfer tubes. When, as in the stacking-type header 2, the header (stacking-type header 2) is arranged only on one side of the heat exchanger 1, even when the end portion is misaligned in each row of the heat transfer tubes, only the end portions on one side are required to be aligned, which improves the degree of freedom in design, the production efficiency, and other matters as compared to the case where the headers (stacking-type header 2 and header 3) are arranged on both sides of the heat exchanger 1 as in the heat exchanger according to Embodiment 1. In particular, the heat exchanger 1 can be bent after the respective members of the heat exchanger 1 are joined to each other, which further improves the production efficiency.
Further, when the heat exchanger 1 acts as the condensor, the first heat transfer tube 4 is positioned on the windward side with respect to the second heat transfer tube 7. When the headers (stacking-type header 2 and header 3) are arranged on both sides of the heat exchanger 1 as in the heat exchanger according to Embodiment 1, it is difficult to provide a temperature difference in the refrigerant for each row of the heat transfer tubes to improve the condensor performance. In particular, when the first heat transfer tube 4 and the second heat transfer tube 7 are flat tubes, unlike a circular tube, the degree of freedom in bending is low, and hence it is difficult to realize providing the temperature difference in the refrigerant for each row of the heat transfer tubes by deforming the flow passage of the refrigerant. On the other hand, when the first heat transfer tube 4 and the second heat transfer tube 7 are connected to the stacking-type header 2 as in the heat exchanger 1, the temperature difference in the refrigerant is inevitably generated for each row of the heat transfer tubes, and obtaining the relationship that the refrigerant flow and the air stream are opposed to each other can be easily realized without deforming the flow passage of the refrigerant.
The present invention has been described above with reference to Embodiment 1 to Embodiment 3, but the present invention is not limited to those embodiments. For example, a part or all of the respective embodiments, the respective modified examples, and the like may be combined.
| Filing Document | Filing Date | Country | Kind |
|---|---|---|---|
| PCT/JP2013/063609 | 5/15/2013 | WO | 00 |
