Heat exchanger and air conditioner including the same

Abstract

To inhibit water droplets from splashing out from a heat exchanger in the plate lamination type heat exchanger.SOLUTION: A heat exchanger 18 includes a plurality of first and second plates 50, 52 that come into contact with each other and form a plurality of fins 46 each having a first flow passage P1 in which first fluid flows. The plurality of fins 46 are laminated at intervals so as to form second flow passages P2 where second fluid A flows. In each of the plurality fo fins 46, end surfaces 50j, 52j on the upstream side in a flowing direction of the second fluid A in the first and second plates 50, 52 are shifted from each other in the flowing direction of the second fluid A.SELECTED DRAWING: Figure 12A

Description

[Technical field]

[0001] The present disclosure relates to a heat exchanger and an air conditioner including the heat exchanger. [Background technology]

[0002] Conventionally, as described in, for example, Patent Document 1, there is known a plate stacking type heat exchanger having a plurality of fins each formed by joining a first plate and a second plate. In each of the plurality of fins, a flow path through which a refrigerant flows is formed between the first and second plates. Heat exchange occurs between the air flowing between the plurality of fins and the refrigerant flowing inside each of the fins.

[0003] A stack of multiple fins (fin stack) in such a plate-stacked heat exchanger is produced by stacking first and second plates alternately, and then heating them while pressing them in the stacking direction. For this purpose, each of the first and second plates is produced, for example, by press-molding a thin metal plate (brazing plate) with a brazing material layer provided on both sides. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Patent Publication No. 2021-63637 Summary of the Invention [Problem to be solved by the invention]

[0005] In the case of a plate stacking type heat exchanger, the fins are made up of two plates and are therefore thicker than the fins of a fin-tube type heat exchanger, which are made up of a single plate. As a result, large water droplets form on the edge of the fin on the upstream side of the air flow direction between the fins, and the water droplets may fly out of the heat exchanger.

[0006] Specifically, when air is cooled by a heat exchanger, moist air hits the thick edges of the upstream fins and condenses, forming large water droplets on the edges. This increases the ventilation resistance in the gaps (flow paths) between the fins through which the air flows, and the air flow speed increases. This air with increased flow speed blows the large water droplets on the edges out of the heat exchanger. When the air that has exchanged heat with the heat exchanger is supplied to a room, the large water droplets are blown out into the room.

[0007] Therefore, an object of the present disclosure is to prevent water droplets from flying out of a plate stacked type heat exchanger. [Means for solving the problem]

[0008] In order to solve the above-mentioned problems, according to one aspect of the present disclosure, a plurality of first and second plates in contact with one another to form a plurality of fins having a first flow passage through which a first fluid flows; The plurality of fins are stacked at intervals to form a second flow path therebetween through which a second fluid flows; A heat exchanger is provided in which, in each of the plurality of fins, end faces on the upstream side in the flow direction of the second fluid of each of the first and second plates are offset from each other in the flow direction of the second fluid.

[0009] According to another aspect of the present disclosure, A compressor that outputs a refrigerant; a heat exchanger through which a refrigerant flows; a fan that generates an air flow that passes through the heat exchanger; the heat exchanger includes a plurality of first and second plates in contact with each other and forming a plurality of fins having a first flow passage through which a refrigerant flows; The plurality of fins are stacked at intervals to form a second flow passage through which air flows; In the air conditioner, in each of the plurality of fins, end faces on the upstream side in the air flow direction of the first and second plates are offset from each other in the air flow direction. Effect of the Invention

[0010] According to the present disclosure, in a plate stacked type heat exchanger, it is possible to suppress water droplets from splashing out of the heat exchanger. [Brief description of the drawings]

[0011] [Figure 1] 1 is a schematic diagram of an air conditioner according to an embodiment of the present disclosure; FIG. [Diagram 2] Schematic cross-sectional view of an indoor unit of an air conditioner. [Diagram 3] FIG. 1 is a perspective view of a heat exchanger according to an embodiment of the present disclosure; [Figure 4] FIG. 1 is a perspective view of a portion of a fin stack in a heat exchanger; [Diagram 5] 1 is a front view of a portion of a fin stack; [Figure 6] 1 is a cross-sectional view of a portion of a fin stack; [Figure 7] Top perspective view of the fin [Figure 8] A bottom perspective view of the fin [Figure 9] An exploded perspective view of the fin from above [Figure 10A] FIG. 13 is a perspective view of a heat exchanger of a comparative example in which the fins are deformed in the short-side direction. [Figure 10B] FIG. 13 is a perspective view of a heat exchanger of a comparative example in which the fins are deformed in the longitudinal direction. [Figure 11] FIG. 1 is a top view of the fins of a heat exchanger in an example orientation. [Figure 12A] FIG. 2 is a cross-sectional view of a fin stack in a state where water droplets are generated in the heat exchanger according to the embodiment; [Figure 12B] FIG. 13 is a cross-sectional view of a fin stack in a state where water droplets are generated in a heat exchanger according to a comparative example. [Figure 13] FIG. 13 is a cross-sectional view of a fin stack in a state where water droplets are generated in a heat exchanger according to another embodiment of the present disclosure. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0012] A heat exchanger according to one embodiment of the present disclosure has a plurality of first and second plates that are in contact with each other and form a plurality of fins having a first flow path through which a first fluid flows, the plurality of fins are stacked at intervals to form a second flow path through which a second fluid flows, and the upstream end faces of each of the first and second plates in the flow direction of the second fluid of the plurality of fins are offset relative to each other in the flow direction of the second fluid.

[0013] According to this aspect, in a plate stacking type heat exchanger, it is possible to suppress water droplets from splashing out of the heat exchanger.

[0014] For example, the first plate may include a first through hole, and the second plate may include a second through hole connected to the first through hole, in which case, in each of the plurality of fins, portions of the inner circumferential surface of the first and second through holes downstream in the flow direction of the second fluid are shifted from each other in the flow direction of the second fluid.

[0015] For example, the first flow passage may be meandering-shaped when viewed in the stacking direction of the fins, in which case the first and second through holes are formed between two portions of the first flow passage that face each other with a gap therebetween.

[0016] For example, the first plate and the second plate may have the same contour shape when viewed in the stacking direction of the plurality of fins.

[0017] Another embodiment of an air conditioner of the present disclosure comprises a compressor that outputs a refrigerant, a heat exchanger through which the refrigerant flows, and a fan that generates a flow of air passing through the heat exchanger, wherein the heat exchanger has a plurality of first and second plates that are in contact with each other and form a plurality of fins having a first flow path through which the refrigerant flows, the plurality of fins are stacked at intervals to form a second flow path through which air flows, and the upstream end faces of the first and second plates in each of the plurality of fins in the air flow direction are offset from each other in the air flow direction.

[0018] According to this alternative embodiment, it is possible to prevent water droplets from splashing out of the heat exchanger.

[0019] Hereinafter, an embodiment of the present disclosure will be described with reference to the drawings.

[0020] Fig. 1 is a schematic diagram of an air conditioner according to an embodiment of the present disclosure, and Fig. 2 is a schematic cross-sectional view of an indoor unit of the air conditioner.

[0021] As shown in FIG. 1, an air conditioner 10 according to this embodiment has an indoor unit 12 disposed indoors, and an outdoor unit 14 disposed outdoors.

[0022] As shown in FIG. 1 and FIG. 2, the indoor unit 12 is equipped with a housing 16 installed indoors, a heat exchanger 18 arranged in the housing 16 to exchange heat with indoor air, and a cross-flow fan 20 that generates a flow of indoor air so that the indoor air passes through the heat exchanger 18. The housing 16 is formed with an intake port 16a that opens upward, an intake port 16b that opens forward, and an outlet port 16c that faces diagonally downward. When the cross-flow fan 20 rotates, indoor air flows into the housing 16 through the intake ports 16a and 16b and passes through the heat exchanger 18. The air that has passed through the heat exchanger 18 is blown out of the housing 16 through the outlet port 16c. A drain pan 22 that stores moisture in the air that condenses on the surface of the heat exchanger 18 is provided below the heat exchanger 18.

[0023] 1, the outdoor unit 14 is equipped with a heat exchanger 24 that exchanges heat with outdoor air, an axial flow fan 26 that generates a flow of outdoor air so that the outdoor air passes through the heat exchanger 24, and a compressor 28 that sends out a refrigerant (first fluid) that passes through the heat exchangers 18, 24. The heat exchanger 18, the heat exchanger 24, and the compressor 28 are connected via a refrigerant piping 30. An expansion valve 32 that reduces the pressure of the refrigerant, and a four-way valve 34 that changes the flow direction of the refrigerant are arranged on the refrigerant piping 30.

[0024] During cooling operation, the refrigerant is discharged from the compressor 28, passes through the four-way valve 34, the heat exchanger 24 of the outdoor unit 14, the expansion valve 32, and the heat exchanger 18 of the indoor unit 12, in that order, and returns to the compressor 28. During heating operation, the refrigerant is discharged from the compressor 28, passes through the four-way valve 34, the heat exchanger 18 of the indoor unit 12, the expansion valve 32, and the heat exchanger 24 of the outdoor unit 14, in that order, and returns to the compressor 28. The four-way valve 34 switches the flow of the refrigerant during cooling operation and the flow of the refrigerant during heating operation. During cooling operation, water droplets generated by condensation of indoor air on the surface of the heat exchanger 18 flow along the surface of the heat exchanger 18 and fall into the drain pan 22.

[0025] Fig. 3 is a perspective view of a heat exchanger according to an embodiment of the present disclosure, Fig. 4 is a perspective view of a portion of a fin stack in the heat exchanger, Fig. 5 is a front view of a portion of the fin stack, and Fig. 6 is a cross-sectional view of a portion of the fin stack.

[0026] The XYZ orthogonal coordinate system shown in the drawings is for facilitating understanding of the embodiment, and does not limit the embodiment. The X-axis direction indicates the short-side direction of the fins constituting the fin structure in the heat exchanger, the Y-axis direction indicates the long-side direction of the fins, and the Z-axis direction indicates the stacking direction of the fins. In the drawings, the outline arrows indicate the flow direction of air A (second fluid) flowing into heat exchanger 18. In this embodiment, air A passing through heat exchanger 18 flows in the X-axis direction.

[0027] 3 and 4, the heat exchanger 18 includes a fin stack 40. The fin stack 40 is disposed between two end plates 42, 44. One of the end plates 42 is provided with an inlet-side connecting pipe 42a that is connected to the refrigerant piping 30 and through which the refrigerant flows in, and an outlet-side connecting pipe 42b that is connected to the refrigerant piping 30 and through which the refrigerant flows out.

[0028] 4 to 6, the fin stack 40 is formed by stacking a plurality of fins 46. By stacking the many fins 46, the heat exchanger 18 becomes a flat plate that is long in the stacking direction of the fins 46 (Z-axis direction), as shown in Fig. 3. In the present embodiment, the multiple fins 46 are stacked in the left-right direction of the indoor unit 12.

[0029] As shown in FIG. 6, inside each of the fins 46, a first flow path P1 through which the coolant flows is provided.

[0030] Fig. 7 is a top perspective view of the fin, Fig. 8 is a bottom perspective view of the fin, and Fig. 9 is an upper exploded perspective view of the fin.

[0031] 9, each of the multiple fins 46 is formed by bonding a first plate 50 and a second plate 52 to each other in the stacking direction (Z-axis direction) of the fin stack 40. As shown in Fig. 6, a first flow path P1 is formed between the first plate 50 and the second plate 52.

[0032] In this embodiment, the first plate 50 and the second plate 52 are fabricated by processing, for example, pressing, a metal thin plate having brazing material layers on both sides, a so-called brazing plate. The brazing plate is fabricated, for example, by forming an aluminum-silicon alloy layer as a brazing material on both sides of a thin plate made of an aluminum alloy. The first plate 50 and the second plate 52 are joined by heating the brazing material layer to melt it once and then solidifying it again.

[0033] The first plate 50 and the second plate 52 are joined together to form a first flow path P1 through which the coolant flows between them. In this embodiment, a meandering recess 52b is formed on the inner surface 52a of the second plate 52 facing the first plate 50. Meanwhile, a protrusion 50b that covers the meandering recess 52b is formed on the inner surface 50a of the first plate 50 facing the second plate 52. The recess 52b and the protrusion 50b are meandering when viewed in the stacking direction (Z-axis direction) of the multiple fins 46, and define the first flow path P1 through which the coolant flows. As a result, the fin 46 having the first flow path P1 therein is formed. In this embodiment, the first flow path P1 is formed in the center of the fin 46 in the longitudinal direction (Y-axis direction) when viewed in the stacking direction.

[0034] 7 and 8, the first flow passage P1 communicates with the insides of the first and second tubular headers 46a, 46b provided at both ends of the fin 46 in the longitudinal direction (Y-axis direction). That is, the first flow passage P1 is disposed between the first and second headers 46a, 46b. The first and second headers 46a, 46b are formed by joining the cylindrical portions 50c, 50d of the first plate 50 and the cylindrical portions 52c, 52d of the second plate 52, respectively.

[0035] 4, a first manifold 40a is formed by connecting and joining the first headers 46a of the multiple fins 46. The first manifold 40a is connected to an inlet side connecting pipe 42a of the end plate 42, and guides the refrigerant that has passed through the inlet side connecting pipe 42a to the first flow path P1 of each of the fins 46.

[0036] 4, the second headers 46b of the fins 46 are connected and joined to form a second manifold 40b. The second manifold 40b is connected to an outlet-side connecting pipe 42b of the end plate 42, and guides the refrigerant that has flowed out from the first flow paths P1 of the fins 46 to the outlet-side connecting pipe 42b.

[0037] In the present embodiment, as shown in Figs. 6 to 9, the first and second plates 50 and 52 are formed with first and second through holes 50e and 52e extending in the longitudinal direction (Y-axis direction) of the fins 46. The first and second through holes 50e and 52e are connected to each other to form a through-hole-shaped heat insulating portion 46c in the fin 46, which penetrates in the stacking direction (Z-axis direction) of the multiple fins 46. As shown in Figs. 7 and 8, the heat insulating portion 46c is formed between two portions of the first flow path P1 that face each other in the short side direction (X-axis direction) of the fin 46 with a gap therebetween, that is, that face the flow direction of the air A. The heat insulating portion 46c suppresses the transfer of heat (heat shortcut) from the refrigerant flowing in one part of the first flow path P1 to the refrigerant flowing in the other part of the first flow path P1 through the first and second plates 50 and 52.

[0038] As shown in Figs. 7 and 9, the outer surface 50f of the first plate 50 is provided with a plurality of cut-and-raised portions 50g.

[0039] 7, the cut-and-raised portion 50g has a bracket shape when viewed in the flow direction of air A (X-axis direction), and is formed when press-molding the first plate 50. Specifically, two parallel slits are first formed, and the portion between the slits is pressed and stretched, thereby forming the first cut-and-raised portion 50g on the outer surface 50f.

[0040] The cut-and-raised portion 50g of each fin 46 functions as a spacer that supports the adjacent fin 46 while securing a space between the fin 46 and the adjacent fin 46. The outer surface 52f of the second plate 52 of the adjacent fin 46 is joined to the top of the cut-and-raised portion 50g. As a result, as shown in Figures 5 and 6, the multiple fins 46 are stacked with spaces between them, and a second flow path P2 through which air A flows is formed between the two fins 46.

[0041] As shown in Figures 7 and 8, the outer surfaces 50f, 52f of the first and second plates 50, 52 are provided with a plurality of first and second rib portions 50h, 52h, respectively. As shown in Figure 5, the plurality of first rib portions 50h protrude toward the second plate 52 of the other fin 46 adjacent to one of the fins. Also, the plurality of second rib portions 52h protrude toward the second plate 52 of the other fin 46 adjacent to the other of the fins. The first rib portion 50h of one of the two adjacent fins 46 and the second rib portion 52h of the other fin 46 are joined to each other via their top surfaces.

[0042] 7 and 8, the first rib portion 50h is provided on the fin 46 (first plate 50) around, i.e., surrounding, the first and second headers 46a, 46b (cylindrical portions 50c, 50d), for reasons that will be described later. Similarly, the second rib portion 52h is provided on the fin 46 (second plate 52) around, i.e., surrounding, the first and second headers 46a, 46b (cylindrical portions 52c, 52d). As a result, in the case of this embodiment, the multiple first and second rib portions 50h, 52h are provided at both ends of the fin 46 in the longitudinal direction (Y-axis direction) together with the first and second headers 46a, 46b.

[0043] The first and second rib portions 50h, 52h are joined together to improve the rigidity of the fin stack 40. In particular, the rigidity against deformation in a direction perpendicular to the stacking direction (Z-axis direction) of the multiple fins 46 is improved. To explain the reason for this, a heat exchanger of a comparative example in which the fins do not have the first and second rib portions will be described. Note that, except for not having the first and second rib portions, the heat exchanger of the comparative example is substantially the same as the heat exchanger 18 of the present embodiment.

[0044] Fig. 10A is a perspective view of a heat exchanger of a comparative example in which the fins are deformed in the short-side direction, and Fig. 10B is a perspective view of the heat exchanger of the comparative example in which the fins are deformed in the long-side direction.

[0045] 10A shows a state in which an external force F1 is applied in the short-side direction (X-axis direction) of the fin to a central portion in the stacking direction (Z-axis direction) of a fin stack 140 in a heat exchanger 118 of a comparative example in which the fins do not have first and second rib portions. This external force F1 causes the fin stack 140 of the comparative example to bend and deform in the short-side direction of the fin.

[0046] 10B shows a state in which an external force F2 is applied in the longitudinal direction (Y-axis direction) of the fin to a central portion in the stacking direction (Z-axis direction) of the fin stack 140 in a comparative heat exchanger 118 in which the fins do not have first and second rib portions. This external force F2 causes the fin stack 140 of the comparative example to bend and deform in the longitudinal direction of the fin.

[0047] Naturally, if these external forces F1, F2 become large, the fin stack 140 may undergo plastic deformation and may not be able to return to its original shape.

[0048] In the case of the fin stack 140 of the comparative example, each of the multiple fins is joined to adjacent fins via the first and second headers and the cut-and-raised portions. Therefore, when external forces F1 and F2 are applied to the fin stack 140, each fin is likely to be significantly displaced relative to the adjacent fins.

[0049] In contrast, in the case of the fin stack 40 of the present embodiment, each of the multiple fins 46 is joined to adjacent other fins 46 via the first and second headers 46a, 46b and the cut-and-raised portion 50g, as well as the first and second rib portions 50h, 52h. The joining of the first and second rib portions 50h, 52h improves the rigidity of the fin stack 40 compared to the fin stack 140 of the comparative example. Therefore, the amount of deflection when the same external forces F1, F2 are applied is smaller in the fin stack 40 than in the fin stack 140 of the comparative example. That is, in the fin stack 40 of the embodiment, the amount of displacement of the fin 46 relative to the adjacent other fins 46 when the external forces F1, F2 are applied is smaller than that of the fin stack 140 of the comparative example.

[0050] In particular, in the case of this embodiment, as shown in Figs. 7 and 8, the first and second rib portions 50h, 52h are provided around the first and second headers 46a, 46b provided at both ends of the fin 46 in the longitudinal direction (Y-axis direction). As a result, the fin 46 is substantially joined to the adjacent other fins 46 at both ends. As a result, the fin stack 40 has high rigidity against an external force F2 acting in the longitudinal direction (Y-axis direction) of the fin 46 as shown in Fig. 10B. In addition, by disposing the first and second rib portions 50h, 52h at both ends of the fin 46 in the longitudinal direction, the first and second rib portions 50h, 52h are prevented from interfering with the air A flowing in the lateral direction (X-axis direction) of the fin 46 along the first flow path P1 disposed in the center of the longitudinal direction.

[0051] In the present embodiment, as shown in Fig. 7 and Fig. 8, the first and second rib portions 50h, 52h are configured so that the size of the fin 46 in the short side direction (X-axis direction) is larger than the size of the fin 46 in the long side direction (Y-axis direction), thereby improving the rigidity against the external force F1 acting in the short side direction (X-axis direction) of the fin 46 as shown in Fig. 10A (compared to the case where the size of the fin 46 in the short side direction at the first and second rib portions 50h, 52h is smaller than the size of the fin 46 in the long side direction). Also, such a shape reduces the ventilation resistance of the first and second rib portions 50h, 52h to the air A.

[0052] In order to reduce the ventilation resistance to the air A, it is preferable to provide a large number of relatively small first and second rib portions 50h, 52h rather than providing a small number of relatively large first and second rib portions 50h, 52h.

[0053] Moreover, it is preferable that the first and second rib portions 50h, 52h are provided with gaps between them and the first and second headers 46a, 46b. The reason for this will be explained with reference to FIG.

[0054] FIG. 11 is a top view of the fins of the heat exchanger in an example orientation.

[0055] 11, the heat exchanger 18 may be used in some cases with the longitudinal direction (Y-axis direction) of the fins 46 generally aligned with the vertical direction V. In this case, when the heat exchanger 18 cools the moist air A, the moist air A condenses on the surfaces of the fins 46, generating water droplets that move downward along the surfaces of the fins 46. That is, in the example shown in FIG. 11, the water droplets move toward the first header 46a located below.

[0056] At this time, if the first and second rib portions 50h, 52h are connected to the first header 46a, the water droplets may accumulate in the corners formed by the first and second rib portions 50h, 52h and the first header 46a. As a result, the water droplets may not be able to fall into the drain pan 22 located below the heat exchanger 18.

[0057] Therefore, in this embodiment, as shown in Figures 7 and 11, gaps are provided between the first and second headers 46a, 46b and the first rib portion 50h so that water droplets generated on the surfaces of the fins 46 due to condensation can fall into the drain pan 22 regardless of the position in which the heat exchanger 18 is used. Similarly, as shown in Figure 8, gaps are provided between the first and second headers 46a, 46b and the second rib portion 52h.

[0058] In order to verify the effects of the first and second rib portions 50h, 52h, the inventors simulated the deformation due to dropping of the fin stack 40 of the present embodiment and the fin stack 140 of the comparative example. Specifically, the inventors dropped the fin stack in the short direction of the fins from the same height position and calculated the maximum displacement of the fin stack in the short direction by simulation. As a result, the maximum displacement of the fin stack 40 of the embodiment was 25.2% lower than the maximum displacement of the fin stack 140 of the comparative example. The simulation results demonstrate that the rigidity of the fin stack is improved by the first and second rib portions 50h, 52h.

[0059] Regarding water droplets generated by condensation of the moist air A in the heat exchanger 18, the heat exchanger according to the present embodiment has a further feature.

[0060] Fig. 12A is a cross-sectional view of a fin stack in a heat exchanger according to the present embodiment with water droplets generated, and Fig. 12B is a cross-sectional view of a fin stack in a heat exchanger according to a comparative example with water droplets generated.

[0061] 12A, depending on the attitude of the heat exchanger 18, water droplets W may form on the upstream edge 46d of each fin 46 in the flow direction of the air A. Specifically, during cooling operation in which the air conditioner 10 cools the air A using the heat exchanger 18, when the moist air A hits the upstream edge 46d of the fin 46 and condenses, water droplets W form on the edge 46d. The fins 46 of the present embodiment are configured so that the water droplets W do not grow large.

[0062] Specifically, as shown in Figures 6, 7, 11, and 12A, in each of the fins 46, an upstream end face 50j of the first plate 50 constituting the edge 46d in the flow direction of the air A and an upstream end face 52j of the second plate 52 are offset from each other in the flow direction of the air A. In the present embodiment, the upstream end face 52j of the second plate 52 is located upstream in the flow direction of the air A with respect to the upstream end face 50j of the first plate 50. Also, in the present embodiment, the upstream end faces 50j, 52j are offset from each other by, for example, 0.2 to 2.0 mm.

[0063] By misaligning the upstream end faces 50j, 52j of the first and second plates 50, 52 with respect to each other in this manner, the water droplets W that form on the edges 46d of the fins 46 become smaller.

[0064] In contrast, when the upstream end faces 150j, 152j of the first and second plates 150, 152 are not misaligned and the positions in the flow direction of the air A are consistent, as in the fin stack 140 of the comparative heat exchanger 118 shown in Figure 12B, large water droplets W may form on the edges 146d of the fins 146.

[0065] 12A, in this embodiment, the edge 46d of the fin 46 that the moist air A hits is small because it is formed only by the upstream end surface 52j of the second plate 52. Therefore, the water droplets W generated on the edge 46d cannot grow large on the edge 46d. Without growing large, the water droplets W are eventually pushed by the flow of the air A and separate from the edge 46d, and move downward on the surface of the fin 46 toward the drain pan 22.

[0066] 12B, in the comparative example, edge 146d of fin 146 that hits moist air A is large because it is composed of upstream end face 150j of first plate 150 and upstream end face 152j of second plate 152. Therefore, water droplets W generated on edge 146d continue to absorb moisture from moist air A and grow large on edge 146d.

[0067] 12B, as the water droplets W grow larger, the flow rate of the air A increases through the first flow path P1 between the fins 146. Specifically, the opening area of ​​the inlet of the second flow path P2 is substantially reduced by the large water droplets W, so that the flow rate of the air A increases when it flows into the second flow path P2.

[0068] When the flow velocity of the air A flowing through the second flow path P2 increases, the water droplets W that have grown large may be blown away by the high-speed air A and fly out of the heat exchanger 118. That is, the water droplets W that have grown large may not move toward the drain pan on the surfaces of the fins 146. The large water droplets W that fly out of the heat exchanger 118 may be sucked into the fan and ultimately blown out from the fan into the room.

[0069] Therefore, as shown in FIG. 12A, the upstream end faces 50j, 52j of the first and second plates 50, 52 are offset from each other so that water droplets W generated on the edges 46d of the fins 46 do not splash out to the outside of the heat exchanger 18.

[0070] As shown in FIG. 6, in this embodiment, the downstream end surface 50k of the first plate 50 and the downstream end surface 52k of the second plate 52 are also shifted in the flow direction of the air A. This is because the first and second plates 50, 52 have the same contour shape when viewed in the stacking direction (Z-axis direction) of the fins 46. That is, the first and second plates 50, 52 are formed by press molding a material plate having the same contour shape. By producing the first and second plates 50, 52 from the same material plate, the manufacturing cost of the fin stack 40 is reduced and the manufacturing time is shortened. In addition, the first and second plates 50, 52 can have substantially the same heat capacity. As a result, the first and second plates 50, 52 can exchange heat with the air A flowing therebetween with substantially the same heat transfer efficiency. As a result, the heat exchange rate of the heat exchanger 18 is improved.

[0071] The inventors have also conducted an experiment to confirm the effect of the upstream end faces 50j, 52j of the first and second plates 50, 52 being misaligned with respect to each other. When moist air was flowed at a flow rate of 1 m / s into the heat exchanger 18 of this embodiment shown in FIG. 12A and the heat exchanger 118 of the comparative example shown in FIG. 12B, the ventilation resistance of this embodiment was 93% of that of the comparative example. This reduction in ventilation resistance indicates that large water droplets are not generated on the edges of the fins.

[0072] Such water droplets W may also occur in areas other than the upstream end faces 50j, 52j of the first and second plates 50, 52.

[0073] FIG. 13 is a cross-sectional view of a fin stack in a heat exchanger according to a different embodiment of the present disclosure in a state in which water droplets are generated.

[0074] As shown in FIG. 13, in a fin stack 240 of a heat exchanger 218 according to another embodiment of the present disclosure, a through-hole-shaped insulating portion 246c of a fin 246 has a large size in the flow direction of air A (X-axis direction). Therefore, water droplets W may be generated on the downstream side of the flow direction of air A on the inner circumferential surface of the through-hole-shaped insulating portion 246c. To prevent the water droplets W from growing large, the inner circumferential surface portions of the first and second through-holes 250e and 252e of each of the fins 246 on the downstream side of the flow direction of air A are shifted in the flow direction of air A relative to each other. As a result, large water droplets W are generated in the through-hole-shaped insulating portion 246c of the fin 246, and the large water droplets W are prevented from flying out of the heat exchanger 218.

[0075] According to the present embodiment as described above, in a plate stacking type heat exchanger, it is possible to prevent water droplets from splashing out of the heat exchanger.

[0076] Although the present invention has been described above with reference to the above-mentioned embodiments, the present disclosure is not limited to the above-mentioned embodiments.

[0077] For example, in the above-described embodiment, the first and second plates 50, 52 are made of a metal sheet having a brazing layer on both sides. The first plate 50 and the second plate 52 are joined to each other by the brazing layer. However, the embodiment of the present disclosure is not limited to this. As long as the first to third plates can be brought into contact with each other and can maintain the contact state, the first and second plates may be made of a metal sheet not having a brazing layer on both sides.

[0078] Furthermore, the heat exchanger according to the above-mentioned embodiment is provided in an air conditioner that performs indoor air conditioning. However, the embodiment of the present disclosure is not limited thereto. The heat exchanger according to the embodiment of the present disclosure can be used in a device that needs to perform heat exchange between a first fluid and a second fluid.

[0079] That is, a heat exchanger according to an embodiment of the present disclosure is, in a broad sense, a heat exchanger having a plurality of first and second plates that are in contact with each other and form a plurality of fins having a first flow path through which a first fluid flows, the plurality of fins are stacked at intervals to form a second flow path between them through which a second fluid flows, and the upstream end faces of each of the plurality of fins in the flow direction of the second fluid of the first and second plates are offset from each other in the flow direction of the second fluid. [Industrial Applicability]

[0080] The present disclosure is applicable to a heat exchanger that exchanges heat between a first fluid and a second fluid. [Explanation of symbols]

[0081] 18 Heat exchanger 46 Finn 50 First Plate 50j Upstream end face 52 Second Plate 52j Upstream end face A Second Fluid (Air) P1 First flow path P2 Second flow path

Claims

1. a plurality of first and second plates in contact with one another to form a plurality of fins having a first flow passage through which a first fluid flows; the plurality of fins are stacked at intervals to form a second flow path therebetween through which a second fluid flows; A heat exchanger, wherein, for each of the plurality of fins, end faces on the upstream side in the flow direction of the second fluid of the first and second plates are offset from each other in the flow direction of the second fluid.

2. the first plate includes a first through hole; the second plate includes a second through hole connected to the first through hole; 2. The heat exchanger according to claim 1, wherein in each of the plurality of fins, portions of the inner circumferential surface downstream in the flow direction of the second fluid in each of the first and second through holes are offset relative to each other in the flow direction of the second fluid.

3. The first flow path has a meandering shape when viewed in a stacking direction of the plurality of fins, The heat exchanger of claim 2 , wherein the first and second through holes are formed between two spaced apart opposing portions of the first flow passage.

4. The heat exchanger according to claim 1 , wherein the first plate and the second plate have the same contour shape when viewed in a stacking direction of the plurality of fins.

5. A compressor that outputs a refrigerant; a heat exchanger through which a refrigerant flows; a fan for generating an air flow through the heat exchanger; the heat exchanger having a plurality of first and second plates in contact with each other and forming a plurality of fins with a first flow passage through which a refrigerant flows; The plurality of fins are stacked at intervals to form a second flow passage through which air flows; an air conditioner, wherein in each of the plurality of fins, end faces on the upstream side in the air flow direction of the first and second plates are offset from each other in the air flow direction.

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