Heat exchanger and air conditioner with same

Abstract

In a plate-laminated heat exchanger, water droplets are prevented from flying out of the heat exchanger. The heat exchanger (18) has a plurality of first and second plates (50, 52) that are in contact with each other and form a plurality of fins (46) including a first flow path (P1) through which a first fluid flows. The plurality of fins (46) are stacked at intervals so that second flow paths (P2) through which a second fluid (A) flows are formed between the fins (46). In each of the plurality of fins (46), upstream end surfaces (50j, 52j) of the first and second plates (50, 52) in the direction of flow of the second fluid (A) are offset from each other in the direction of flow of the second fluid (A).

Description

Technical Field

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

[0002] In the prior art, for example, as described in Patent Document 1, there is known a plate stack type heat exchanger which includes a plurality of fins formed by joining a first plate and a second plate. In each of the plurality of fins, a flow path for the refrigerant to flow is formed between the first plate and the second plate. Heat exchange is performed between air flowing between the plurality of fins and the refrigerant flowing inside each of the fins.

[0003] The stack of multiple fins in this plate stack type heat exchanger (fin stack) is produced by alternately stacking the first plate and the second plate and then heating them while pressing them in the stacking direction. Therefore, each of the first plate and the second plate is produced, for example, by stamping a metal thin plate (brazing plate) having a brazing material layer on both sides.

[0004] Prior art literature

[0005] Patent Literature

[0006] Patent Document 1: Japanese Patent Application Publication No. 2021-63637 Summary of the invention

[0007] Problems to be solved by the invention

[0008] However, in the case of a plate stack type heat exchanger, the fins are composed of two plates and therefore are thicker than the fins of a fin-tube type heat exchanger composed of one plate. Therefore, large water droplets are generated on the edges of the fins on the upstream side of the flow direction of the air flowing between the fins, and the water droplets tend to fly out of the heat exchanger.

[0009] Specifically, when the air is cooled by the heat exchanger, the moist air condenses on the thick edge on the upstream side of the fin, thereby generating large water droplets on the edge. As a result, the ventilation resistance of the gap (flow path) between the fins through which the air flows increases, and the flow rate of the air increases. The air with the increased flow rate blows the large water droplets on the edge to the outside of the heat exchanger. When the air that has exchanged heat with the heat exchanger is supplied to the room, the large water droplets are blown into the room.

[0010] Therefore, an object of the present invention is to suppress water droplets from flying out of a heat exchanger in a plate stack type heat exchanger.

[0011] Methods for solving problems

[0012] In order to solve the above problems, according to one aspect of the present invention, a heat exchanger is provided.

[0013] The invention comprises a plurality of first plates and a second plate, wherein the first plates and the second plates are in contact with each other to form a plurality of fins including a first flow path for a first fluid to flow.

[0014] The plurality of fins are stacked at intervals so as to form a second flow path through which the second fluid flows therebetween.

[0015] In each of the plurality of fins, end surfaces of the first plate and the second plate on the upstream side in the flow direction of the second fluid are offset from each other in the flow direction of the second fluid.

[0016] In addition, according to another aspect of the present invention, there is provided an air conditioner, comprising:

[0017] a compressor, which delivers refrigerant;

[0018] a heat exchanger in which a refrigerant flows; and

[0019] a fan which generates an air flow through the heat exchanger,

[0020] The heat exchanger includes a plurality of first plates and a second plate, wherein the first plates and the second plates are in contact with each other to form a plurality of fins including a first flow path through which a refrigerant flows.

[0021] The plurality of fins are stacked at intervals so as to form a second flow path for air flow therebetween.

[0022] In each of the plurality of fins, end surfaces on the upstream side of the first plate and the second plate in the air flow direction are offset from each other in the air flow direction.

[0023] Effects of the Invention

[0024] According to the present invention, in a plate stack type heat exchanger, it is possible to suppress water droplets from flying out of the heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1 This is a schematic diagram of an air conditioner according to an embodiment of the present invention.

[0026] Figure 2 This is a schematic cross-sectional view of an indoor unit in an air conditioner.

[0027] Figure 3 This is a perspective view of a heat exchanger according to one embodiment of the present invention.

[0028] Figure 4 This is a perspective view of a portion of a fin stack in a heat exchanger.

[0029] Figure 5This is a front view of a portion of a fin stack.

[0030] Figure 6 This is a cross-sectional view of a portion of a fin stack.

[0031] Figure 7 This is a three-dimensional view from above of the fin.

[0032] Figure 8 This is a three-dimensional view of the bottom of the fin.

[0033] Fig. 9 This is an exploded perspective view of the top of the fin.

[0034] Fig. 10A This is a perspective view of a heat exchanger of a comparative example in which the fins are deformed in the short-side direction.

[0035] Fig. 10B This is a perspective view of a heat exchanger of a comparative example in which the fins are deformed in the long-side direction.

[0036] Fig.11 This is a plan view of fins in a heat exchanger arranged in an example posture.

[0037] Fig. 12A This 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.

[0038] Fig. 12B This is a cross-sectional view of a fin stack in a state where water droplets are generated in a heat exchanger of a comparative example.

[0039] Fig.13 This is a cross-sectional view of a fin stack in a state where water droplets are generated in a heat exchanger according to a different embodiment of the present invention.

[0040] Description of Reference Numerals

[0041] 18Heat exchanger

[0042] 46 fins

[0043] 50 Plate 1

[0044] 50j upstream end face

[0045] 52 Plate 2

[0046] 52j upstream end face

[0047] A Second fluid (air)

[0048] P1 1st flow path

[0049] P2 second flow path DETAILED DESCRIPTION

[0050] A heat exchanger according to one aspect of the present invention comprises a plurality of first plates and a second plate, wherein the first plates and the second plates are in contact with each other to form a plurality of fins including a first flow path for a first fluid to flow, and the plurality of fins are stacked at intervals to form a second flow path for a second fluid to flow therebetween, and in each of the plurality of fins, end surfaces on the upstream side of the flow direction of the second fluid in each of the first plates and the second plates are offset from each other in the flow direction of the second fluid.

[0051] According to this aspect, in the plate stack type heat exchanger, it is possible to suppress water droplets from flying out of the heat exchanger.

[0052] 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 this case, in each of the plurality of fins, portions of the inner peripheral surface on the downstream side of the flow direction of the second fluid in each of the first through hole and the second through hole are offset from each other in the flow direction of the second fluid.

[0053] For example, the first flow path may be serpentine when viewed from the stacking direction of the plurality of fins. In this case, the first through hole and the second through hole are formed between two portions of the first flow path that face each other at a distance.

[0054] For example, the first plate and the second plate may have the same outline shape when viewed from the stacking direction of the plurality of fins.

[0055] An air conditioner in another aspect of the present invention includes: a compressor that delivers refrigerant; a heat exchanger in which the refrigerant flows; and a fan that generates an air flow through the heat exchanger, the heat exchanger having a plurality of first plates and a second plate, the first plates and the second plates being in contact with each other to form a plurality of fins including a first flow path for the refrigerant to flow, the plurality of fins being stacked at intervals to form a second flow path for the air to flow therebetween, and in each of the plurality of fins, end faces on the upstream side of the air flow direction in each of the first plates and the second plates are offset from each other in the air flow direction.

[0056] According to this other aspect, it is possible to suppress water droplets from flying out of the heat exchanger.

[0057] Hereinafter, one embodiment of the present invention will be described with reference to the drawings.

[0058] Figure 1 This is a schematic diagram of an air conditioner according to one embodiment of the present invention. Figure 2 This is a schematic cross-sectional view of an indoor unit in an air conditioner.

[0059] like Figure 1As shown, the air conditioner 10 of the present embodiment includes an indoor unit 12 disposed indoors and an outdoor unit 14 disposed outdoors.

[0060] like Figure 1 and Figure 2 As shown, the indoor unit 12 is equipped with a housing 16 disposed indoors, a heat exchanger 18 disposed in the housing 16 and performing heat exchange with the indoor air, and a cross-flow fan 20 that generates an indoor air flow by passing the indoor air through the heat exchanger 18. The housing 16 is provided with an air inlet 16a opened upward, an air inlet 16b opened forward, and an air outlet 16c opened obliquely downward. When the cross-flow fan 20 rotates, the indoor air flows into the housing 16 through the air inlets 16a and 16b and passes through the heat exchanger 18. The air passing through the heat exchanger 18 is discharged from the housing 16 to the outside through the air outlet 16c. In addition, a drain pan 22 is provided below the heat exchanger 18 to store moisture in the air condensed on the surface of the heat exchanger 18.

[0061] like Figure 1 As shown, the outdoor unit 14 is equipped with a heat exchanger 24 for exchanging heat with outdoor air, an axial flow fan 26 for generating an outdoor air flow by passing the outdoor air through the heat exchanger 24, and a compressor 28 for sending out the refrigerant (first fluid) passing through the heat exchangers 18 and 24. The heat exchanger 18, the heat exchanger 24, and the compressor 28 are connected via a refrigerant pipe 30. The refrigerant pipe 30 is provided with an expansion valve 32 for reducing the pressure of the refrigerant and a four-way valve 34 for changing the flow direction of the refrigerant.

[0062] During cooling operation, the refrigerant is sent out 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 sequence, and returns to the compressor 28. During heating operation, the refrigerant is sent out 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 sequence, and returns to the compressor 28. The flow of the refrigerant during cooling operation and the flow of the refrigerant during heating operation are switched by the four-way valve 34. In addition, 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.

[0063] Figure 3 This is a perspective view of a heat exchanger according to one embodiment of the present invention. Figure 4 This is a perspective view of a portion of a fin stack in a heat exchanger. Figure 5 This is a front view of a portion of the fin stack. Figure 6 This is a cross-sectional view of a portion of a fin stack.

[0064] In addition, the XYZ orthogonal coordinate system shown in the drawings is a coordinate system for easy understanding of the embodiment and does not limit the embodiment. The X-axis direction represents the short side direction of the fins constituting the fin structure in the heat exchanger, the Y-axis direction represents the long side direction of the fins, and the Z-axis direction represents the stacking direction of the fins. In addition, in the figure, the hollow arrow represents the flow direction of the air A (second fluid) flowing into the heat exchanger 18. In the case of this embodiment, the air A passing through the heat exchanger 18 flows along the X-axis direction.

[0065] like Figure 3 and Figure 4 As shown, the heat exchanger 18 includes a fin stack 40. The fin stack 40 is disposed between two end plates 42 and 44. An inlet-side connecting pipe 42a connected to the refrigerant pipe 30 and through which the refrigerant flows in, and an outlet-side connecting pipe 42b connected to the refrigerant pipe 30 and through which the refrigerant flows out are provided on one end plate 42.

[0066] like Figures 4 to 6 As shown in FIG. 1 , the fin stack 40 is formed by stacking a plurality of fins 46. By stacking a plurality of fins 46, the heat exchanger 18 is formed as shown in FIG. Figure 3 The fin 46 is in the shape of a flat plate that is long in the stacking direction (Z-axis direction) of the fins 46. In the present embodiment, a plurality of fins 46 are stacked in the left-right direction of the indoor unit 12.

[0067] like Figure 6 As shown, a first flow path P1 through which the refrigerant flows is provided inside each of the plurality of fins 46 .

[0068] Figure 7 This is a three-dimensional view of the fin from above. Figure 8 This is a three-dimensional view of the fin from below. Fig. 9 This is an exploded perspective view of the top of the fin.

[0069] like Fig. 9 As shown in FIG. 1 , each of the plurality of fins 46 is formed by joining a first plate 50 and a second plate 52 to each other in the stacking direction (Z-axis direction) of the fin stack 40. Figure 6 As shown, a first flow path P1 is formed between the first plate 50 and the second plate 52 .

[0070] In the case of this embodiment, the first plate 50 and the second plate 52 are made by processing, for example, stamping, a metal thin plate having a brazing material layer on both sides, namely a so-called brazing plate. The brazing plate is made 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 melting the brazing material layer once by heating and solidifying it again.

[0071] The first plate 50 and the second plate 52 are joined to each other to form a first flow path P1 for refrigerant flow therebetween. In the case of the present embodiment, a meandering recess 52b is formed on the inner surface 52a of the second plate 52 opposite to the first plate 50. On the other hand, a convex portion 50b covering the meandering recess 52b is formed on the inner surface 50a of the first plate 50 opposite to the second plate 52. The recess 52b and the convex portion 50b are meandering when viewed from the stacking direction (Z-axis direction) of the plurality of fins 46, and define the first flow path P1 for refrigerant flow. As a result, the fin 46 including the first flow path P1 is formed inside. In addition, in the case of the present embodiment, the first flow path P1 is formed in the central portion of the long side direction (Y-axis direction) of the fin 46 when viewed from the stacking direction.

[0072] In addition, if Figure 7 and Figure 8 As shown, the first flow path P1 is connected to the inside of the first and second tubular headers 46a and 46b provided at both ends of the long side direction (Y-axis direction) of the fin 46. That is, the first flow path P1 is arranged between the first and second headers 46a and 46b. In addition, each of these first and second headers 46a and 46b is formed by joining the cylindrical portions 50c and 50d of the first plate 50 and the cylindrical portions 52c and 52d of the second plate 52.

[0073] By connecting and joining the first headers 46a of the plurality of fins 46, as shown in FIG. Figure 4 As shown, the first manifold 40 a is configured. The first manifold 40 a is connected to the inlet-side connecting pipe 42 a of the end plate 42 , and guides the refrigerant passing through the inlet-side connecting pipe 42 a to the first flow passages P1 of the respective fins 46 .

[0074] In addition, by connecting and joining the second headers 46b of the plurality of fins 46, as shown in FIG. Figure 4 As shown, the second manifold 40b is configured. The second manifold 40b is connected to the outflow-side connecting pipe 42b of the end plate 42, and guides the refrigerant flowing out of the first flow passages P1 of each fin 46 to the outflow-side connecting pipe 42b.

[0075] In addition, in the case of this embodiment, if Figure 6 to Figure 9 As shown in FIG. 1 , a first through hole and a second through hole 50e and 52e extending in the long side direction (Y-axis direction) of the fin 46 are formed on each of the first plate and the second plate 50 and 52. The first through hole and the second through hole 50e and 52e are connected to each other, and a through hole-shaped heat insulating portion 46c penetrating in the stacking direction (Z-axis direction) of the plurality of fins 46 is formed on the fin 46. Figure 7 and Figure 8As shown, the heat insulating portion 46c is formed at a distance between two portions of the first flow path P1 of the fin 46 that are opposite in the short-side direction (X-axis direction), that is, opposite in the flow direction of the air A. The heat insulating portion 46c suppresses heat transfer (thermal shortcut) from the refrigerant flowing through a portion of the first flow path P1 to the refrigerant flowing through another portion of the first flow path P1 via the first plate 50 and the second plate 52.

[0076] In addition, if Figure 7 and Fig. 9 As shown in FIG. 1 , a plurality of cut-out portions 50 g are provided on the outer surface 50 f of the first plate 50 .

[0077] Specifically, if Figure 7 As shown, the cut-out formed portion 50g is in a bracket shape when viewed from the flow direction (X-axis direction) of the air A, and is formed by stamping the first plate 50. Specifically, two parallel slits are first formed, and the portion between the slits is extended by pressing, so that the first cut-out formed portion 50g is formed on the outer surface 50f.

[0078] The cut-out formed portion 50g of each fin 46 ensures a space between the fin 46 and the adjacent fin 46, and also functions as a spacer for supporting the adjacent fin 46. The outer surface 52f of the second plate 52 in the adjacent fin 46 is bonded to the top of the cut-out formed portion 50g. Figure 5 and Figure 6 As shown, a plurality of fins 46 are stacked at intervals, and a second flow path P2 through which the air A flows is formed between two fins 46 .

[0079] like Figure 7 and Figure 8 As shown in FIG. 1 , a plurality of first and second ribs 50h and 52h are provided on the outer surfaces 50f and 52f of the first and second plates 50 and 52, respectively. Figure 5 As shown, a plurality of first ribs 50h protrude toward the second plate 52 in the other fin 46 adjacent to the one fin. In addition, a plurality of second ribs 52h protrude toward the second plate 52 in the other fin 46 adjacent to the other fin. The first ribs 50h in one fin and the second ribs 52h in the other fin 46 of the two adjacent fins 46 are joined to each other via their top surfaces.

[0080] In addition, if Figure 7 and Figure 8As shown, for reasons described later, the first rib 50h is provided on the fin 46 (first plate 50) in a manner surrounding the first and second headers 46a, 46b (cylindrical portions 50c, 50d). Similarly, the second rib 52h is provided on the fin 46 (second plate 52) in a manner surrounding the first and second headers 46a, 46b (cylindrical portions 52c, 52d). As a result, in the case of the present embodiment, a plurality of first and second ribs 50h, 52h are provided at each of the two ends in the longitudinal direction (Y-axis direction) of the fin 46 together with the first and second headers 46a, 46b.

[0081] By joining the first and second ribs 50h and 52h to each other, the rigidity of the fin stack 40 is improved. In particular, the rigidity against deformation in a direction orthogonal to the stacking direction (Z-axis direction) of the plurality of fins 46 is improved. In order to explain the reason, a heat exchanger of a comparative example in which the fin does not include the first and second ribs is described. In addition, the heat exchanger of the comparative example is substantially the same as the heat exchanger 18 of the present embodiment except that the first and second ribs are not included.

[0082] 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. Fig. 10B This is a perspective view of a heat exchanger of a comparative example in which the fins are deformed in the long-side direction.

[0083] Fig. 10A The figure shows a state where an external force F1 is applied along the short side direction (X-axis direction) of the fin stack 140 in the heat exchanger 118 of the comparative example in which the fin does not include the first and second ribs. The external force F1 causes the fin stack 140 of the comparative example to bend and deform in the short side direction of the fin.

[0084] in addition, Fig. 10B The figure shows a state where an external force F2 is applied along the long side direction (Y-axis direction) of the fin stack 140 in the heat exchanger 118 of the comparative example in which the fin does not include the first and second ribs. Due to the external force F2, the fin stack 140 of the comparative example is bent and deformed in the long side direction of the fin.

[0085] Of course, if the external forces F1 and F2 increase, the fin stack 140 may be plastically deformed and may not be able to return to its original shape.

[0086] In the case of the fin stack 140 of the comparative example, each of the plurality of fins is joined to another adjacent fin via the first and second headers and the cut-out portions. Therefore, when external forces F1 and F2 are applied to the fin stack 140, each of the fins is easily displaced greatly relative to another adjacent fin.

[0087] In contrast, in the case of the fin stack 40 of the present embodiment, each of the plurality of fins 46 is joined to another adjacent fin 46 via the first and second ribs 50h and 52h in addition to the first and second headers 46a and 46b and the cut-out formed portion 50g. The joining of the first and second ribs 50h and 52h improves the rigidity of the fin stack 40 compared to the fin stack 140 of the comparative example. Therefore, the fin stack 40 has a smaller deflection amount when the same external forces F1 and F2 are applied than the fin stack 140 of the comparative example. That is, in the fin stack 40 of the embodiment, the displacement amount of the fin 46 relative to another adjacent fin 46 when the external forces F1 and F2 are applied is smaller than that of the fin stack 140 of the comparative example.

[0088] In particular, in the case of this embodiment, if Figure 7 and Figure 8 As shown in FIG. 1 , first and second ribs 50h and 52h are provided around the first and second headers 46a and 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 another adjacent fin 46 at both ends. As a result, the fin 46 is Fig. 10B The fin stack 40 has high rigidity by the external force F2 in the long side direction (Y-axis direction) of the fin 46 shown in FIG. In addition, by the arrangement of the first and second ribs 50h and 52h at both ends in the long side direction of the fin 46, the first and second ribs 50h and 52h are suppressed from obstructing the air A flowing in the short side direction (X-axis direction) of the fin 46 along the first flow path P1 arranged in the center in the long side direction.

[0089] In addition, in the case of this embodiment, if Figure 7 and Figure 8 As shown, the first and second ribs 50h and 52h are configured such that the dimension of the short side direction (X-axis direction) of the fin 46 is larger than the dimension of the long side direction (Y-axis direction), thereby Fig. 10A The external force F1 in the short-side direction (X-axis direction) of the fin 46 shown in the figure increases the rigidity (compared with the case where the short-side dimension of the fin 46 in the first and second ribs 50h and 52h is smaller than the long-side dimension). In addition, with this shape, the ventilation resistance of the first and second ribs 50h and 52h to the air A is reduced.

[0090] Furthermore, in order to reduce the ventilation resistance to the air A, it is more preferable to provide a large number of relatively small first and second ribs 50h and 52h rather than to provide a small number of relatively large first and second ribs 50h and 52h.

[0091] In addition, it is preferable that the plurality of first and second ribs 50h and 52h are provided with gaps between the first and second headers 46a and 46b. Fig.11 The reason is explained.

[0092] Fig.11 This is a plan view of fins in a heat exchanger arranged in an example posture.

[0093] like Fig.11 As shown in FIG. 1 , the heat exchanger 18 is sometimes used in a state where the long side direction (Y-axis direction) of the fin 46 is roughly aligned with the vertical direction V. In this case, when the heat exchanger 18 cools the humid air A, the humid air A condenses on the surface of the fin 46 and the water droplets generated move downward along the surface of the fin 46. That is, Fig.11 In the example shown, the water droplets move toward the first header 46a located below.

[0094] At this time, if the first and second ribs 50h and 52h are connected to the first header 46a, water drops may accumulate at the corner formed by the first and second ribs 50h and 52h and the first header 46a. As a result, water drops may not fall into the drain pan 22 located below the heat exchanger 18.

[0095] Therefore, in this embodiment, no matter what posture the heat exchanger 18 is used in, water droplets generated on the surface of the fin 46 due to condensation can fall into the drain pan 22. Figure 7 and Fig.11 As shown in FIG. 1 , a gap is provided between the first and second headers 46a, 46b and the first rib 50h. Figure 8 As shown, a gap is also provided between the first and second headers 46a, 46b and the second rib 52h.

[0096] In addition, in order to verify the effects of the first and second ribs 50h and 52h, the inventor simulated the deformation caused by the falling of the fin stack 40 of the present embodiment and the fin stack 140 of the comparative example. Specifically, the inventor dropped the fin stack from the same height position along the short side direction of the fin, and calculated the maximum displacement of the fin stack in the short side direction through simulation. As a result, the maximum displacement of the fin stack 40 of the embodiment is 25.2% lower than the maximum displacement of the fin stack 140 of the comparative example. According to the simulation results, it is confirmed that the rigidity of the fin stack is improved by the first and second ribs 50h and 52h.

[0097] The heat exchanger of the present embodiment includes further features regarding water droplets generated by condensation of the humid air A in the heat exchanger 18 .

[0098] Fig. 12A This is a cross-sectional view of a fin stack in a state where water droplets are generated in the heat exchanger of this embodiment. Fig. 12B This is a cross-sectional view of a fin stack in a state where water droplets are generated in a heat exchanger of a comparative example.

[0099] like Fig. 12A As shown in FIG. 1 , depending on the posture of the heat exchanger 18, water droplets W may be generated on the edge 46d on the upstream side of each fin 46 in the flow direction of the air A. Specifically, during the cooling operation in which the air conditioner 10 cools the air A through the heat exchanger 18, if the moist air A contacts the upstream edge 46d of the fin 46 and condenses, water droplets W are generated on the edge 46d. The fin 46 of the present embodiment is configured so that the water droplets W do not grow significantly.

[0100] Specifically, if Figure 6 , Figure 7 , Fig.11 and Fig. 12A As shown, in each of the fins 46, the upstream end surface 50j in the flow direction of the air A in the first plate 50 and the upstream end surface 52j in the second plate 52 constituting the edge 46d are offset from each other in the flow direction of the air A. In the case of the present embodiment, the upstream end surface 52j of the second plate 52 is located on the upstream side of the flow direction of the air A relative to the upstream end surface 50j of the first plate 50. In addition, in the case of the present embodiment, the upstream end surfaces 50j and 52j are offset from each other by, for example, 0.2 to 2.0 mm.

[0101] By shifting the upstream end surfaces 50j and 52j of the first and second plates 50 and 52 from each other in this manner, the water droplets W generated at the edges 46d of the fins 46 become smaller.

[0102] In contrast, in Fig. 12B When the upstream end surfaces 150j and 152j of the first and second plates 150 and 152 are not offset to align the flow direction of the air A as in the fin stack 140 of the heat exchanger 118 of the comparative example shown, large water droplets W may be generated on the edges 146d of the fins 146.

[0103] As specified, Fig. 12A As shown in the figure, in the case of the present embodiment, the edge 46d of the fin 46 that the moist air A contacts is small because it is composed only of the upstream end surface 52j of the second plate 52. Therefore, the water droplets W generated on the edge 46d cannot grow greatly on the edge 46d. The water droplets W do not grow greatly, but are eventually pressed by the flow of air A and leave the edge 46d, and move on the surface of the fin 46 in the downward direction of the drain pan 22.

[0104] On the other hand, Fig. 12B As shown in FIG. 1 , in the comparative example, the edge 146d of the fin 146 that the humid air A contacts is large because it is composed only of the upstream end surface 150j of the first plate 150 and the upstream end surface 152j of the second plate 152. Therefore, the water droplets W generated on the edge 146d continue to take moisture from the humid air A and grow greatly on the edge 146d.

[0105] like Fig. 12B As shown, if the water droplets W grow significantly, the flow rate of the air A flowing through the first flow path P1 between the fins 146 increases. Specifically, the opening area of ​​the inlet of the second flow path P2 is substantially reduced by the large water droplets W, thereby increasing the flow rate of the air A when flowing into the second flow path P2.

[0106] If the flow velocity of the air A flowing through the second flow path P2 increases, the large-growing water droplets W may be blown away by the high-speed air A and fly out of the heat exchanger 118. In other words, the large-growing water droplets W may not move toward the drain pan on the surface of the fin 146. The large water droplets W that fly out of the heat exchanger 118 may be sucked into the fan and eventually discharged from the fan into the room.

[0107] Therefore, if Fig. 12A As shown, the upstream end surfaces 50j and 52j of the first and second plates 50 and 52 are offset from each other so that water droplets W generated on the edges 46d of the fins 46 do not fly out of the heat exchanger 18.

[0108] In addition, if Figure 6 As shown, in the case of the present embodiment, the downstream side end face 50k of the first plate 50 and the downstream side end face 52k of the second plate 52 are also offset in the flow direction of the air A. This is because the first plate and the second plate 50, 52 have the same contour shape when viewed from the stacking direction (Z-axis direction) of the fin 46. That is, this is because the first plate and the second plate 50, 52 are formed by stamping a material plate having the same contour shape. By making the first plate and the second plate 50, 52 from the same material plate, the production cost of the fin stack 40 is reduced and the production time is shortened. In addition, therefore, the first plate and the second plate 50, 52 can include substantially the same heat capacity. As a result, each of the first plate and the second plate 50, 52 can perform heat exchange with the air A flowing therethrough at substantially the same heat transfer efficiency. As a result, the heat exchange rate of the heat exchanger 18 is improved.

[0109] In addition, the inventor conducted an experiment to investigate the effect of the upstream end surfaces 50j and 52j of the first plate 50 and the second plate 52 being offset from each other. Moisturized air was flowed into the first plate 50 at a flow rate of 1 m / s. Fig. 12A The heat exchanger 18 and Fig. 12BAs a result, the ventilation resistance of the present embodiment was 93% of the ventilation resistance of the comparative example in each of the heat exchangers 118 shown. This reduction in ventilation resistance means that large water droplets are not generated on the edges of the fins.

[0110] In addition, such water droplets W may also be generated in portions other than the upstream end surfaces 50 j and 52 j of the first and second plates 50 and 52 .

[0111] Fig.13 This is a cross-sectional view of a fin stack in a state where water droplets are generated in a heat exchanger according to a different embodiment of the present invention.

[0112] like Fig.13 As shown, in the fin stack 240 of the heat exchanger 218 of the different embodiment of the present invention, the dimension of the through-hole-shaped heat insulating portion 246c of the fin 246 in the flow direction of air A (X-axis direction) is large. Therefore, water droplets W may be generated in the portion on the downstream side of the flow direction of air A in the inner peripheral surface of the through-hole-shaped heat insulating portion 246c. In each of the fins 246, the portions of the inner peripheral surface on the downstream side of the flow direction of air A in the first through-hole and the second through-hole 250e and 252e are offset from each other in the flow direction of air A so that the water droplets W do not grow significantly. As a result, the generation of large water droplets W in the through-hole-shaped heat insulating portion 246c of the fin 246 and the flying of the large water droplets W to the outside of the heat exchanger 218 are suppressed.

[0113] According to the present embodiment described above, in the plate stack type heat exchanger, it is possible to suppress water droplets from flying out of the heat exchanger.

[0114] As mentioned above, although the present invention has been described by taking the above-mentioned embodiment as an example, the present invention is not limited to the above-mentioned embodiment.

[0115] For example, in the above-mentioned embodiment, the first plate and the second plate 50, 52 are made of metal thin plates with brazing material layers on both sides. Through the brazing material layer, the first plate 50 and the second plate 52 are joined to each other. However, the embodiment of the present invention is not limited to this. As long as the first to third plates are in contact with each other and can maintain the contact state, the first plate and the second plate can also be made of metal thin plates without brazing material layers on both sides.

[0116] Furthermore, the heat exchanger of the above embodiment is provided in an air conditioner for indoor air conditioning. However, the embodiment of the present invention is not limited thereto. The heat exchanger of the embodiment of the present invention can be used in a device that requires heat exchange between a first fluid and a second fluid.

[0117] That is, the heat exchanger according to the embodiment of the present invention is, in a broad sense, a heat exchanger comprising a plurality of first plates and a second plate, the first plates and the second plates being in contact with each other to form a plurality of fins including a first flow path for a first fluid to flow, the plurality of fins being stacked at intervals to form a second flow path for a second fluid to flow therebetween, and in each of the plurality of fins, end surfaces on the upstream side of the flow direction of the second fluid in each of the first plates and the second plates are offset from each other in the flow direction of the second fluid.

[0118] Industrial Applicability

[0119] The present invention can be applied to a heat exchanger that performs heat exchange between a first fluid and a second fluid.

Claims

1. A heat exchanger, characterized in that: A plurality of first plates and second plates are provided, wherein the first plates and the second plates are in contact with each other to form a plurality of fins including a first flow path for a first fluid to flow. The plurality of fins are stacked at intervals so as to form a second flow path through which the second fluid flows therebetween. In each of the plurality of fins, end surfaces of the first plate and the second plate on the upstream side in the flow direction of the second fluid are offset from each other in the flow direction of the second fluid.

2. The heat exchanger according to claim 1, characterized in that: The first plate has a first through hole, The second plate has a second through hole connected to the first through hole, In each of the plurality of fins, portions of the inner peripheral surface of each of the first through hole and the second through hole on the downstream side in the flow direction of the second fluid are offset from each other in the flow direction of the second fluid.

3. The heat exchanger according to claim 2, characterized in that: The first flow path is serpentine when viewed from the stacking direction of the plurality of fins. The first through hole and the second through hole are formed between two portions of the first flow path that face each other with a gap therebetween.

4. The heat exchanger according to claim 1, characterized in that: The first plate and the second plate have the same outline shape when viewed from a stacking direction of the plurality of fins.

5. An air conditioner, characterized in that: include: a compressor, which delivers refrigerant; a heat exchanger in which a refrigerant flows; and a fan which generates an air flow through the heat exchanger, The heat exchanger includes a plurality of first plates and a second plate, wherein the first plates and the second plates are in contact with each other to form a plurality of fins including a first flow path through which a refrigerant flows. The plurality of fins are stacked at intervals so as to form a second flow path for air flow therebetween. In each of the plurality of fins, end surfaces on the upstream side of the first plate and the second plate in the air flow direction are offset from each other in the air flow direction.

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