Heat exchanger and air conditioner using the same

Abstract

To suppress generation of buckling of a fin during insertion of a heat transfer pipe, while providing crest parts and trough parts of the fin to enlarge a heat transfer area to improve heat exchange efficiency.SOLUTION: A heat exchanger comprises a plurality of heat transfer pipes arranged in multiple stages, and a long plate-shaped fin extending along an arrangement direction of the plurality of heat transfer pipes and attached to the heat transfer pipes. The fin extends midway from one long side part to the other long side part, and comprises a plurality of notches into which the plurality of heat transfer pipes are respectively inserted, and a plurality of heat transfer regions sandwiched between adjacent notches. In the heat transfer regions, crest parts folded toward a short side direction of the fin and trough parts folded toward the short side direction, and a flat part extending along the short side direction without being folded between the crest part or the trough part and the notch, are formed.SELECTED DRAWING: Figure 2

Description

Technical Field

[0001] The present invention relates to a heat exchanger and an air conditioner using this heat exchanger.

Background Art

[0002] In a heat exchanger assembled by inserting a heat transfer tube into a notch formed in a fin, there is one that provides a peak portion and a valley portion on the fin to increase the heat transfer area and improve the heat exchange efficiency (Patent Document 1).

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] By the way, in such a heat exchanger, when inserting the heat transfer tube into the notch, a force along the insertion direction is applied to the fin that slides in contact with the heat transfer tube. If the fin has a valley and peak portion as in Patent Document 1, due to the force acting on the fin during the insertion of the heat transfer tube, stress concentrates on the valley and peak portions, and the fin is likely to buckle at the valley and peak portions.

[0005] The present invention has been made to solve the above-described problems, and while providing a peak portion and a valley portion on the fin to increase the heat transfer area and improve the heat exchange efficiency, the main problem is to suppress the occurrence of buckling of the fin during the insertion of the heat transfer tube.

Means for Solving the Problems

[0006] That is, the heat exchanger according to the present invention includes a plurality of heat transfer tubes arranged in multiple stages, and a long plate-shaped fin that extends along the arrangement direction of the plurality of heat transfer tubes and is attached to the heat transfer tubes. The fin extends to the middle from one long side portion toward the other long side portion, and includes a plurality of notches into which each of the plurality of heat transfer tubes is inserted, and a plurality of heat transfer regions sandwiched between the adjacent notches. In the heat transfer region, a mountain portion that is folded into a peak in the short side direction of the fin and a valley portion that is folded into a trough are formed, and a flat portion that extends along the short side direction without being bent is formed between the mountain portion or the valley portion and the notch.

[0007] With such a configuration, the heat exchange efficiency can be improved by expanding the heat transfer area at the mountain portion and the valley portion. In addition, since a flat portion that extends flatly is provided between the mountain portion and the valley portion where stress concentration causes easy buckling and the notch into which the heat transfer tube is inserted, the sliding resistance generated between the inserted heat transfer tube and the fin can be received by the flat portion that is resistant to buckling, and the stress generated in the mountain portion or the valley portion that is vulnerable to buckling can be reduced. Thereby, buckling of the fin during insertion of the heat transfer tube can be suppressed.

[0008] Preferably, the flat portion is formed across the mountain portion and the valley portion. In this case, since one flat portion can support the mountain portion and the valley portion together, the generation of buckling of the fin during insertion of the heat transfer tube can be more effectively suppressed with a simple configuration.

[0009] Preferably, the flat portion is formed to extend from one end of the notch located on the one long side portion side to the other end of the notch. In this case, buckling of the fin during insertion of the heat transfer tube can be suppressed across the entire heat transfer region.

[0010] Preferably, the flat portion is formed between both of the two notches sandwiching the heat transfer region and the mountain portion and the valley portion. In this case, since flat portions are formed at both ends in the longitudinal direction of the heat transfer region that extends in the short side direction of the fin along the notch, buckling of the fin can be more effectively suppressed throughout the heat transfer region.

[0011] Preferably, the ridge portion and the valley portion are formed so as to protrude in opposite directions in the thickness direction of the flat portion. In this case, the height of the ridge portion and the valley portion with respect to the flat portion can be reduced. Therefore, when deforming the flat fin to form the ridge portion and the valley portion, while preventing the fin from being torn, the gap between the ridge portion and the valley portion can be increased to expand the heat transfer area.

[0012] By the way, when the heat exchanger is housed in a housing such as an outdoor unit, it may be bent so that the whole becomes an L shape, a U shape, or the like. During this bending process, if there are ridge portions or valley portions where stress easily concentrates in the region of the fin that is not sandwiched and supported by the heat transfer tubes, buckling is likely to occur.

[0013] Therefore, in the fin, it is preferable that a flat region where the ridge portion and the valley portion are not provided is formed from the inner part of the notch to the other long side portion. In this case, since ridge portions or valley portions where stress easily concentrates are not formed in the region of the fin that is not sandwiched by the heat transfer tubes, buckling can be suppressed in the flat region of the fin during the bending process of the heat exchanger.

[0014] By the way, even if a flat region is provided as described above, it is conceivable that stress during the bending process concentrates at the boundary between the heat transfer region fixed to the heat transfer tubes and the flat region that is not fixed.

[0015] Therefore, it is preferable that the fin has a first reinforcing structure that extends in the short side direction across the heat transfer region and the flat region, and the first reinforcing structure is formed by partially raising the surface of the fin in the thickness direction of the flat portion. In this case, since the reinforcing structure is provided across the boundary between the heat transfer region and the flat region, for example, buckling of the fins at the boundary between the heat transfer region and the flat region during bending of the heat exchanger can be suppressed.

[0016] The first reinforcing structure is preferably formed continuously with the peak portion closest to the flat region and is formed to have substantially the same height as the peak portion closest to the flat region in the thickness direction. In this case, it is possible to prevent a step from occurring at the portion where the peak portion closest to the flat region and the first reinforcing structure are continuous, and during bending of the heat exchanger, stress concentration at that portion can be prevented, thereby preventing the fins from being deformed or buckled.

[0017] The first reinforcing structure preferably extends from the end of the peak portion closest to the flat region in the longitudinal direction of the fins. In this case, since the end of the peak portion closest to the flat region and the end of the first reinforcing structure are continuous, the boundary formed at the continuous portion can be reduced, and during bending of the heat exchanger, stress concentration at that boundary can be prevented, thereby preventing the fins from being deformed or buckled.

[0018] The peak portion closest to the flat region is preferably formed such that its inclination toward the flat region side is gentler than its inclination toward the opposite side. In this case, while increasing the length of the first reinforcing structure extending in the short direction of the fins in the heat transfer region, the range occupied by the peak portion in the heat transfer region can be widened, so that further improvement in heat exchange efficiency and prevention of fin buckling can be achieved.

[0019] The heat transfer tube is preferably flat. In this case, it is possible to improve heat exchange efficiency while achieving refrigerant savings. In addition, the fins slide on the flat surface of the inserted heat transfer tube, generating a large stress at the peak and valley portions, so that the effect of preventing buckling by the flat portion is more beneficially exerted.

[0020] On the slope of the ridge portion or the valley portion, a turbulent flow portion formed by cutting and raising the plate surface is further provided, and it is preferable that the turbulent flow portion is inclined at 13° to 15° with respect to the short side direction when viewed from the thickness direction of the flat portion. In this case, in addition to the ridge portion and the valley portion, the turbulent flow portion can also disrupt the air flow between the fins, and further improve the heat exchange efficiency.

[0021] The air conditioner according to the present invention is characterized by including the heat exchanger described above. With such an air conditioner, the effects of the heat exchanger described above can be exerted.

Effects of the Invention

[0022] According to the present invention configured as described above, it is possible to suppress the occurrence of buckling of the fins during the insertion of the heat transfer tubes while improving the heat exchange efficiency.

Brief Description of the Drawings

[0023]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Embodiments for Carrying Out the Invention

[0024] Hereinafter, a first embodiment of a heat exchanger according to the present invention will be described with reference to the drawings.

[0025] The heat exchanger according to this embodiment constitutes an air conditioner equipped with a refrigerant circuit and is used as one or both of an outdoor heat exchanger and an indoor heat exchanger.

[0026] Specifically, as shown in FIG. 1, this heat exchanger 100 is a so-called fin-and-tube heat exchanger, and includes a plurality of heat transfer tubes 1 through which refrigerant flows inside, and a plurality of fins 2 attached to these heat transfer tubes 1. Heat exchange is performed between the refrigerant flowing inside the heat transfer tubes 1 and the air flowing between the fins 2.

[0027] As shown in FIG. 2 or FIG. 3, the heat transfer tube 1 has a flat shape and is called a multi-hole flat tube having a plurality of internal flow paths 11 through which refrigerant flows. The heat transfer tube 1 of this embodiment is arranged such that the flat surface faces up and down, that is, the flat surface is horizontal, and the refrigerant is provided to flow along the horizontal direction inside it. A plurality of such heat transfer tubes 1 are arranged in multiple rows, for example, at equal intervals in the vertical direction, and the extending directions of each heat transfer tube 1 are the same.

[0028] As shown in FIG. 2 or FIG. 3, the fin 2 has a long plate shape extending along the vertical direction, and a plurality of heat transfer tubes 1 provided in multiple rows are inserted into it. The fins 2 are arranged at predetermined intervals along the extending direction of the heat transfer tubes 1.

[0029] As shown in FIG. 2, this fin 2 has a notch 3 extending to the middle from one long side portion 2p to the other long side portion 2q. In the notch 3, one end on the side of one long side portion 2p of the fin 2 is taken as one end, and the other end on the other side (also referred to as the inner part 3z of the notch) is taken as the other end.

[0030] The notches 3 are formed at a plurality of locations on the fin 2 so as to correspond to each of the plurality of heat transfer tubes 1 provided in multiple rows, and each heat transfer tube 1 is inserted into each of these notches 3.

[0031] This notch 3 is for inserting the flat heat transfer tube 1 along its width direction, and the heat transfer tube 1 is fixedly attached to the fins 2, for example, by brazing, etc., without play.

[0032] The heat exchanger 100 of the present embodiment is arranged such that air flows from one long side portion 2p (where the notch 3 is open) side of the fins 2 toward the other long side portion 2q side.

[0033] That is, in the present embodiment, one long side portion 2p is arranged on the upstream side of the air flow, and the other long side portion 2q is arranged on the downstream side of the air flow. By arranging the other long side portion 2q where the notch 3 is not open on the leeward side in this way, the bias of the heat flux in the heat transfer tube 1 can be reduced, and an improvement in heat exchange efficiency can be expected.

[0034] In such a configuration, as shown in FIG. 2, the fins 2 are provided with a heat transfer region 21 that transfers heat between air and refrigerant in a region sandwiched between adjacent notches 3.

[0035] The heat transfer region 21 is a region including at least the portion of the fins 2 that contacts the heat transfer tube 1, and here it is a region extending the same length as the notch 3 from one long side portion 2p toward the other long side portion 2q.

[0036] This heat transfer region 21 is provided intermittently along the vertical direction of the fins 2, and each heat transfer region 21 is separated by the notch 3.

[0037] Here, as shown in FIG. 2, when assuming a virtual line V connecting the innermost parts 3z of each notch 3, the portion of the fins 2 on the side of one long side portion 2p with respect to the virtual line V functions as the heat transfer region 21.

[0038] Note that the innermost part 3z of the notch 3 is the location closest to the other long side portion 2q in the notch 3, in other words, the abutment of the notch 3 toward the other long side portion 2q.

[0039] In this embodiment, since each notch 3 is formed with the same dimensions, the virtual line V is a straight line along the longitudinal direction of the fin 2.

[0040] Here, in order to improve the heat exchange efficiency, as shown in FIG. 4, the heat transfer region 21 is provided with a mountain portion 21x formed by folding the heat transfer region 21 from one long side portion 2p toward the other long side portion 2q, and a valley portion 21y formed by folding the heat transfer region 21 from one long side portion 2p toward the other long side portion 2q in a valley fold. FIG. 4(a) is a cross-sectional view taken along line A-A' of the fin 2 in FIG. 3, and FIG. 4(b) is a side view of the fin 2 in FIG. 3 viewed from the vertical direction. For convenience in these figures, the heat transfer tubes are omitted.

[0041] These mountain portions 21x and valley portions 21y are respectively provided along the air flow direction (width direction of the fin 2), and are formed so as to straddle the crease portions along the vertical direction (longitudinal direction of the fin 2). Note that the crease portions in the present embodiment are parallel to the longitudinal direction of the fin 2.

[0042] In the heat transfer region 21 of the present embodiment, the mountain portions 21x and valley portions 21y are alternately and continuously formed along the short side direction of the fin 2. In the present embodiment, among the mountain portions 21x and valley portions 21y formed in the heat transfer region 21, the mountain portion 21x is disposed closest to the other long side portion 2q side of the fin 2.

[0043] Thus, in the heat transfer region 21 of the heat exchanger 100 according to the present embodiment, as shown in FIGS. 2 and 3, a flat portion F is formed between the mountain portion 21x and the valley portion 21y and the notch 3. The flat portion F is formed so as to extend without being bent along the short side direction of the fin 2.

[0044] The flat portion F in the present embodiment is formed to straddle at least the mountain portion 21x and the valley portion 21y adjacent to each other along the short side direction of the fin 2. More specifically, it is formed at the peripheral edge of the notch 3 so as to sandwich the mountain portion 21x and the valley portion 21y continuously formed in the heat transfer region 21 from above and below.

[0045] The flat portion F of the present embodiment is formed to extend from one end to the other end of the notch 3, and sandwiches and grips the heat transfer tube 1 inserted into the notch 3 from above and below. More specifically, the flat portion F has an elongated plate shape orthogonal to the flat surface of the heat transfer tube 1 and extends along the width direction of the heat transfer tube 1.

[0046] In each heat transfer region, flat portions F are formed between both of the two notches 3 sandwiching the heat transfer region 21 and the peak portion 21x and the valley portion 21y. The flat portions F provided in these respective heat transfer regions 21 are arranged on substantially the same plane. The plurality of flat portions F formed in each heat transfer region are each arranged on substantially the same plane. Specifically, they are arranged on a plane extending along the vertical direction and the width direction of the heat transfer tube 1.

[0047] The peak portion 21x and the valley portion 21y are formed so as to protrude in opposite directions to each other in the thickness direction of the flat portion F. Specifically, the peak portion 21x and the valley portion 21y of the present embodiment are each formed so as to protrude from the flat portion F by substantially the same height.

[0048] Incidentally, the heat exchanger 100 is housed in a housing such as an outdoor unit or an indoor unit, and as shown in FIG. 4, a bending roller is pressed against it and bent at least once or more. For example, it may be bent once to form an L shape, bent twice to form a U shape, or bent three or more times.

[0049] In the present embodiment, in order to arrange the other long side portion 2q on the downwind side to improve the heat exchange efficiency, the heat exchanger 100 is bent with the other long side portion 2q on the inside. Specifically, the outer peripheral surface of a cylindrical bending roller is pressed all at once against the other long side portion 2q of the plurality of fins 2 constituting the heat exchanger 100, and the extending direction of the heat transfer tube 1 is bent. Note that the outer peripheral surface of the bending roller may be pressed against one long side portion 2p of the fin 2 for bending.

[0050] During this bending process, there is a concern that the fin 2 in contact with the bending roller may buckle under a large load.

[0051] Since the heat transfer region 21 described above is sandwiched and supported between a pair of heat transfer tubes 1, the region on the back side of the notch 3 (the region on the other long side portion 2q side from the virtual line V) is more likely to buckle.

[0052] In the present embodiment, the region on the back side of the notch 3 is considered to be particularly likely to buckle because a large load is applied when the bending roller is pressed against the other long side portion 2q.

[0053] Therefore, in the present embodiment, as shown in FIGS. 2 and 3, the flat region 22, which is the region from the inner part 3z of the notch 3 to the other long side portion 2q, is not provided with the peak portion 21x and the valley portion 21y.

[0054] Here, the flat region 22 does not necessarily mean that the entire region is flat, and it is sufficient that it is flatter than at least the heat transfer region 21, and some undulations or holes may be formed. The flat region 22 of the present embodiment is arranged on substantially the same plane as the flat portion F of the heat transfer region 21.

[0055] The flat region 22 is the region on the other long side portion 2q side of the fin 2 from the virtual line V. Here, it continuously extends from one longitudinal end portion to the other longitudinal end portion of the fin 2.

[0056] This flat region 22 has neither the peak portion 21x formed by mountain folding the fin 2 nor the valley portion 21y formed by valley folding. In other words, no crease portion is formed in the flat region 22 along the longitudinal direction (vertical direction) of the fin 2.

[0057] By providing the flat region 22 in this way, stress concentration in the region from the inner part 3z of the notch 3 to the other long side portion 2q is suppressed.

[0058] On the other hand, there is a concern that the boundary portion between the heat transfer region 21 and the flat region 22 (corresponding to the portion including the virtual line V described above) may appear as the following stress concentration location.

[0059] Therefore, in order to prevent buckling at this boundary portion, the fin 2 of the present embodiment has a first reinforcing structure 4a spanning the flat region 22 and the heat transfer region 21 as shown in FIGS. 2 to 4.

[0060] The first reinforcing structure 4a is for improving the strength of the boundary portion. Specifically, it is a concave portion formed by recessing at least a part of the boundary portion toward the valley portion 21y side, or a convex portion formed by bulging at least a part of the boundary portion toward the peak portion 21x side. Note that the first reinforcing structure 4a may be formed by combining these concave and convex portions.

[0061] Specifically, the first reinforcing structure 4a is a convex strip or a concave groove extending along the width direction of the fin 2 and is provided across the virtual line V. However, the first reinforcing structure 4a may be inclined with respect to the width direction of the fin 2.

[0062] The first reinforcing structure 4a is a bead-shaped or rib-shaped convex strip extending in the width direction of the fin 2, which is formed by partially raising the surface of the fin 2 in the thickness direction of the flat portion F. In the present embodiment, a plurality of sets (here, two sets) of the first reinforcing structures 4a are formed by raising the surface of the fin 2 toward the peak portion 21x side between the heat transfer tubes 1 adjacent to each other.

[0063] The first reinforcing structure 4a is formed continuously with the peak portion 21x (the peak portion 21x closest to the flat region 22) disposed closest to the other long side portion 2q side of the fin 2.

[0064] In the thickness direction of the flat portion F, the height of the first reinforcing structure 4a rising from the flat portion F is formed to be substantially the same as the height of the peak portion 21x (especially the peak portion 21x closest to the flat region 22) rising from the flat portion F.

[0065] Further, the first reinforcing structure 4a is formed so as to extend from the end of the peak portion 21x closest to the flat region 22 in the longitudinal direction of the fin 2. The first reinforcing structure 4a that rises from the fin 2 has substantially the same rising manner as the peak portion 21x that rises from the flat portion F, and the first reinforcing structure 4a and the peak portion 21x continuous thereto are continuously integrally formed.

[0066] The peak portion 21x closest to the flat region 22 is formed such that the inclination toward the flat region 22 side is gentler than the inclination toward the opposite side.

[0067] In addition, as shown in FIGS. 2 to 4, a turbulent flow portion 5 formed by raising the plate surface of the fin 2 is further provided on the slope of the peak portion 21x or the valley portion 21y formed on the fin 2. This turbulent flow portion 5 is inclined at 13° to 15° with respect to the short side direction of the fin 2 when viewed from the thickness direction of the flat portion F.

[0068] The turbulent flow portion 5 of the present embodiment is provided at two locations between the heat transfer tubes 1 adjacent to each other, and both are provided on the way from the peak portion 21x toward the valley portion 21y when viewed from one long side portion 2p of the fin 2. The turbulent flow portion 5 may be provided on the way from the valley portion 21y toward the peak portion 21x, or may be provided in the flat region 22.

[0069] According to the heat exchanger 100 configured as described above, since the peak portion 21x and the valley portion 21y are formed, the heat transfer area can be expanded and the heat exchange efficiency can be improved. At the same time, a flat portion F extending flatly is provided between the peak portion 21x and the valley portion 21y that are likely to buckle due to stress concentration and the notch 3 into which the heat transfer tube 1 is inserted, so that the stress generated in the peak portion 21x or the valley portion 21y can be reduced, and buckling of the fin 2 during heat transfer tube insertion can be suppressed.

[0070] Since the flat portion F is continuously formed at the upper and lower ends of the heat transfer region, buckling of the fin can be suppressed over the entire heat transfer region.

[0071] Since the fin 2 is provided with a plate-like flat portion F along the insertion direction at a portion (periphery of the notch 3) that slidably contacts the heat transfer tube 1 to be inserted, it is possible to prevent a bending moment from occurring in the heat transfer region 21 during the insertion of the heat transfer tube 1, and it is possible to suppress buckling of the fin 2.

[0072] Since the peak portions 21x and the valley portions 21y are formed so as to protrude in opposite directions to each other in the thickness direction of the flat portion F, the heights of the peak portions 21x and the valley portions 21y with respect to the flat portion F can be reduced. Therefore, when the flat fin 2 is deformed to manufacture such a fin 2, it is possible to prevent the peak portion 21x or the valley portion 21y from being overstretched from the flat portion F and the fin from being broken. At the same time, the gap between the peak portions 21x and the valley portions 21y can be made as large as possible, the heat transfer area can be expanded, and the heat exchange efficiency can be improved.

[0073] In addition, since a flat region 22 having no peak portions 21x and valley portions 21y is provided in the region from the inner part 3z of the notch of the fin 2 to the other long side portion 2q, stress is dispersed in the flat region 22, and buckling in the flat region 22 during bending can be suppressed.

[0074] In addition, while arranging the other long side portion 2q where the notch 3 is not open on the leeward side, since a flat region 22 is provided in a region where stress concentrates during the bending process for such an arrangement, the unevenness of the heat flux in the heat transfer tube 1 can be reduced, the heat exchange efficiency can be improved, and buckling of the fin 2 can be suppressed. That is, it is possible to achieve both ensuring the heat exchange efficiency and taking countermeasures against buckling of the fin 2.

[0075] Since the flat region 22 is formed on substantially the same plane as the flat portion F of the heat transfer region 21, it is possible to suppress stress concentration at the boundary between the heat transfer region 21 and the flat region 22 and buckling of the fin 2 when the heat transfer tube 1 is inserted.

[0076] Since the first reinforcing structure 4a is provided across the flat region 22 and the heat transfer region 21, it is possible to suppress buckling from occurring at the boundary between the flat region 22 and the heat transfer region 21 during bending.

[0077] This first reinforcing structure 4a is formed continuously with the peak portion 21x closest to the flat region 22, and since its height is substantially the same as that of the peak portion 21x, it is possible to prevent stress from concentrating at the boundary between the first reinforcing structure 4a and the peak portion 21x connected thereto during bending. Thereby, buckling or deformation of the fin 2 can be suppressed. At the same time, since the structure of the fin 2 can be simplified, the risk of breakage during the forming of the fin 2 can also be reduced.

[0078] Furthermore, since the first reinforcing structure 4a and the peak portion 21x closest to the flat region connected thereto are integrally formed, it is possible to prevent stress from concentrating at these boundaries. Thereby, buckling or deformation of the fin 2 can be suppressed. At the same time, the structure of the fin 2 can be simplified.

[0079] Since the inclination on the flat region 22 side of the peak portion 21x closest to the flat region 22 is gently formed (since the distance between the peak portion 21x and the flat region 22 is long), it is possible to widely secure the heat transfer area in the heat transfer region 21 to improve the heat exchange efficiency, and at the same time, it is possible to make the first reinforcing structure 4a connected to the peak portion 21x as long as possible to suppress buckling.

[0080] The air flowing between the fins 2 can be disturbed in the thickness direction of the fins 2 by the above-described peak portion 21x and valley portion 21y. Furthermore, since the turbulent flow portion 5 is provided, the air flowing between the fins 2 can also be disturbed in the vertical direction, and further improvement in heat exchange efficiency can be achieved. By disturbing the air flowing between the fins 2 in two directions, a synergistic effect is generated compared to the case of disturbing in only one direction, and the heat exchange efficiency is further increased.

[0081] [Other Embodiments] As shown in FIG. 5, in order to increase the contact area with the heat transfer tube 1, the fin 2 has a collar 31 that rises from the flat portion F around the notch 3 and is in surface contact with the flat surface of the heat transfer tube 1.

[0082] This collar 31 is a thin plate that raises part or all of the portion surrounding the notch 3 in the fin 2. Here, the entire collar 31 is formed by being bent from the back side to the front side of the fin 2. However, a part of the collar 31 may be bent from the front side to the back side of the fin 2. Note that the front side of the fin 2 is the side where the peak portion 21x bulges here, and is also the side where the convex portions forming the first reinforcing structure 4a and the second reinforcing structure 4b bulge.

[0083] In addition, the fin 2 is provided with a spacer 32 integrally formed with the collar 31. This spacer 32 is for keeping the distance between the fins 2 constant.

[0084] In the above embodiment, the heat exchanger 100 was arranged such that air flows from one long side portion 2p side of the fin 2 toward the other long side portion 2q side. However, it may be arranged such that air flows from the other long side portion 2q side of the fin 2 toward one long side portion 2p side.

[0085] The peak portion 21x and the valley portion 21y are preferably formed by corrugation processing or drawing processing.

[0086] The shape of the peak portion 21x and the shape of the valley portion 21y only need to disturb the flow of air passing between the fins 2, and their specific shapes may be changed as appropriate.

[0087] Needless to say, the present invention is not limited to the above embodiment, and various modifications are possible without departing from the spirit thereof.

Explanation of Reference Numerals

[0088] 100 ··· Heat exchanger 1 ··· Heat transfer tube 11 ··· Internal flow path 2 ··· Fin 2p ··· One long side of the fin 2q ··· The other long side of the fin 21 ··· Heat transfer region 21x ··· Crest 21y ··· Trough F ··· Flat part 22 ··· Flat region 3 ··· Notch 3z ··· The inner part of the notch 31 ··· Color 32 ··· Spacer 4a ··· First reinforcing structure 5 ··· Turbulent flow part

Claims

1. A plurality of heat transfer tubes arranged in multiple stages, and a long plate-shaped fin extending along the arrangement direction of the plurality of heat transfer tubes and attached to the heat transfer tubes, wherein the fin extends to midway from one long side portion to the other long side portion, and has a plurality of notches into which each of the plurality of heat transfer tubes is inserted, and a plurality of heat transfer regions sandwiched between the adjacent notches, wherein in the heat transfer region there are provided a mountain portion folded in a mountain shape and a valley portion folded in a valley shape in the short side direction of the fin, and a flat portion extending along the short side direction without being bent between the mountain portion or the valley portion and the notch, and a heat exchanger.

2. The heat exchanger according to claim 1, wherein the flat portion is formed across the mountain portion and the valley portion.

3. The heat exchanger according to claim 2, wherein the flat portion is formed to extend from one end portion of the notch in the short side direction to the other end portion of the notch.

4. The heat exchanger according to claim 3, wherein in the heat transfer region, the flat portion is formed between both of the two notches sandwiching the heat transfer region and the mountain portion and the valley portion.

5. The heat exchanger according to claim 4, wherein the mountain portion and the valley portion are formed to protrude in opposite directions in the thickness direction of the flat portion.

6. The heat exchanger according to claim 1, wherein in the fin, a flat region in which the mountain portion and the valley portion are not provided is formed from the other end portion of the notch to the other long side portion of the fin.

7. The fin has a first reinforcing structure extending in the short side direction across the heat transfer region and the flat region, and the heat exchanger according to claim 6, wherein the first reinforcing structure is formed by partially raising the surface of the fin in the thickness direction of the flat portion.

8. The heat exchanger according to claim 7, wherein the first reinforcing structure is formed continuously with the mountain portion closest to the flat region, and is formed to have substantially the same height as the mountain portion closest to the flat region in the thickness direction.

9. The heat exchanger according to claim 8, wherein the first reinforcing structure extends from the end portion of the mountain portion closest to the flat region in the longitudinal direction of the fin.

10. The heat exchanger according to claim 8, wherein the inclination of the mountain portion closest to the flat region toward the flat region side is formed to be gentler than the inclination toward the opposite side.

11. The heat exchanger according to claim 1, wherein the heat transfer tube has a flat shape.

12. On the slope of the mountain portion or valley portion, a turbulent flow portion formed by cutting and raising the plate surface is further provided, The heat exchanger according to claim 1, wherein the turbulent flow portion is inclined at 13° to 15° with respect to the short side direction when viewed from the thickness direction of the flat portion.

13. An air conditioner comprising the heat exchanger according to claim 1.

Images