JP2015117876A - Fin and tube type heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a fin and tube type heat exchanger that can be easily manufactured by eliminating the necessity of tube expansion and that enables improvement of corrosion resistance.SOLUTION: A fin and tube type heat exchanger includes: a plurality of plate-shaped aluminum fins 2; and flat porous aluminum refrigerant pipes 3 inserted to insertion holes 21 provided on the respective fins 2. The fin 2 and the refrigerant pipe 3 are joined to each other via an adhesive 4 applied to the surface of the refrigerant pipe 3, and a potential difference between the fin 2 and the refrigerant pipe 3 is -40 mV to -60 mV.

Description

  TECHNICAL FIELD The present invention relates to a fin-and-tube heat exchanger, and more specifically, a fin-and-tube heat exchange including an aluminum plate-like fin and an aluminum flat porous refrigerant tube. It is about a vessel. Here, aluminum is meant to include an aluminum alloy.

  Conventionally, fin-and-tube heat exchangers have been used particularly in the field air conditioner field. This type of fin-and-tube heat exchanger is a method of laminating plate-like fins provided with a plurality of insertion holes, inserting a refrigerant pipe through the insertion hole, and mechanically expanding the refrigerant pipe. It is manufactured by fixing the fin and the refrigerant pipe.

  A copper round tube that is easy to expand and excellent in heat transfer is used as the refrigerant tube, and an aluminum plate fin is used as the fin from the viewpoint of cost and corrosion resistance.

  However, the use of copper as a material for the refrigerant tube has a problem that the cost is higher than that of aluminum, and the aluminum is corroded and dropped off early due to a large potential difference from the aluminum fin.

  On the other hand, in the car air conditioner field, a flat tube having better heat transfer performance than a round tube is used as a refrigerant tube, and is generally manufactured by brazing as a parallel flow type heat exchanger.

  Because this flat tube is difficult to expand, it is difficult to apply it to a fin-and-tube heat exchanger with the conventional tube expansion method. Like a heat exchanger for a car air conditioner, a fin-and-tube heat exchanger with a brazing method is used. Has been proposed.

  However, the production by the brazing method cannot use pre-coated fins that have been surface-treated in advance in a fin-and-tube heat exchanger from the viewpoint of corrosion resistance, and large-scale equipment such as a brazing furnace. Therefore, there is a problem that there are many factors that increase the cost for the production by the pipe expansion method.

  As a conventional fin-and-tube heat exchanger of this type that does not depend on the brazing method, a plurality of aluminum plate-like fins and a flat aluminum product inserted through the insertion holes provided in each fin What joins a porous flat tube with an adhesive agent is known (for example, refer patent document 1).

JP 2010-249374 A

  However, in the thing of patent document 1, the joining method of a fin and a flat tube is not mentioned, and the corrosion resistance of the heat exchanger at the time of using an adhesive agent is not mentioned.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a fin-and-tube heat exchanger that can be easily manufactured without the need for expansion of the tube and can improve the corrosion resistance.

  In order to achieve the above object, a fin-and-tube heat exchanger according to the present invention includes a plurality of aluminum plate-like fins and an aluminum flat porous material inserted into an insertion hole provided in each fin. A fin-and-tube heat exchanger having a shape of a refrigerant pipe, wherein the fin and the refrigerant pipe are joined via an adhesive applied to the surface of the refrigerant pipe, The potential difference between the fin and the refrigerant pipe is -40 mV to -60 mV (Claim 1).

  Here, the potential difference will be described. In general, metal corrosion is described from an electrochemical point of view. The heat exchanger uses this electrochemical corrosion mechanism to create a potential difference in which the refrigerant pipe is “precious” and the fin is “base”, and the fin is preferentially corroded to corrode the refrigerant pipe. Sacrificial protection to prevent is given. This sacrificial anticorrosion effect can be obtained if the potential difference between the fin and the refrigerant pipe is −40 mV to −60 mV. The reason is that if the potential difference between the fin and the refrigerant tube exceeds -60 mV, the fin is positively corroded, and the fin falls off at an early stage, so that the effect of sacrificial corrosion protection cannot be obtained. Further, if the potential difference between the fin and the refrigerant pipe is less than −40 mV, the potential difference is so small that a sufficient sacrificial anticorrosive effect cannot be obtained, and corrosion may proceed simultaneously in the fin and the refrigerant pipe.

  The potential difference between the aluminum fin and the refrigerant tube can be set in the range of −40 mV to −60 mV by slightly changing the aluminum composition of the fin and the refrigerant tube. For example, Fe: 0.40 mass% or less, Si: 0.25 mass% or less, Cu: 0.05 mass% or less, Mn: 0.05 mass% or less, Mg: Aluminum containing 0.05% by mass or less, Zn: 0.05% by mass or less, Ti: 0.03% by mass or less, V: 0.05% by mass or less, the balance being composed of Al and inevitable impurities When an alloy is used, as an alloy of the refrigerant tube, Fe: 0.05 to 0.20 mass%, Si: 0.10 mass% or less, Cu: 0.15 to 0.32 mass%, Zr: 0.05 Less than mass%, Ti: 0.06-0.15 mass%, Mn: 0.08-0.15 mass%, Mg: 0.02 mass% or less, Zn: 0.03% by mass or less, the balance Uses aluminum alloy with a composition consisting of Al and inevitable impurities That. Thereby, the electric potential difference of the said fin and a refrigerant pipe can be made into the range of -40mV--60mV.

  By comprising as mentioned above, since an aluminum plate-shaped fin and an aluminum flat porous refrigerant | coolant pipe | tube are joined with an adhesive agent, pipe expansion can be made unnecessary. Further, by making the potential difference between the fin and the refrigerant tube in the range of −40 mV to −60 mV, sacrificial corrosion prevention that preferentially corrodes the fin and prevents corrosion of the refrigerant tube can be performed.

  In the present invention, the adhesive is preferably an adhesive mainly composed of a thermoplastic resin (claim 2). By using an adhesive mainly composed of a thermoplastic resin, the fin and the refrigerant pipe can be joined as follows. First, after applying a thermoplastic adhesive to the surface of the refrigerant pipe, the adhesive is dried, and the refrigerant pipe is inserted into an insertion hole provided in the fin and assembled. Next, the assembly of the fin and the refrigerant tube is heated to a temperature at which the adhesive melts, and the adhesive is filled between the inner surface of the fin insertion hole and the surface of the refrigerant tube, and then the assembly is cooled. And a fin and a refrigerant | coolant pipe | tube can be joined by solidifying an adhesive agent.

  Further, it is preferable that the adhesive is coated on the surface of the refrigerant pipe. By comprising in this way, the condensed water adhering to the surface of a refrigerant pipe can be discharged | emitted rapidly.

  In the present invention, the fin is preferably a pre-coated fin having a surface coated with a film having hydrophilicity, water repellency, and corrosion resistance.

  By comprising in this way, the condensed water adhering to the surface of a fin can be discharged | emitted rapidly.

  In addition, in the present invention, it is preferable that the long side in the cross section orthogonal to the longitudinal direction of the refrigerant pipe is inclined with respect to the direction of gravity in the installed state of the heat exchanger.

  By comprising in this way, the condensed water adhering to the surface of a refrigerant pipe can be discharged | emitted along the inclined surface of a refrigerant pipe.

  According to this invention, since it is configured as described above, the following effects can be obtained.

  (1) According to the first and second aspects of the present invention, the expansion of the pipe can be made unnecessary by joining the plate-like fin and the flat porous refrigerant pipe with an adhesive, so that it is easily manufactured. it can. Further, since the sacrificial anticorrosion for preferentially corroding the fins to prevent the corrosion of the refrigerant pipe can be performed, the corrosion resistance can be improved.

  (2) According to the invention described in claim 3, the condensed water adhering to the surface of the refrigerant pipe can be quickly discharged by coating the surface of the refrigerant pipe with the adhesive. In addition, the corrosion resistance can be further improved.

  (3) According to the invention described in claim 4, the condensed water adhering to the surface of the fin is quickly discharged by using the pre-coated fin having the surface coated with a film having hydrophilicity, water repellency, and corrosion resistance. Therefore, in addition to the above (1) and (2), the corrosion resistance can be further improved.

  (4) According to the invention described in claim 5, since condensed water adhering to the surface of the refrigerant pipe can be discharged along the inclined surface of the refrigerant pipe, in addition to the above (1) to (3), Corrosion resistance can be improved.

1 is a schematic perspective view showing a first embodiment of a fin-and-tube heat exchanger according to the present invention. It is a principal part front view which shows the joining state of the fin and refrigerant pipe in 1st Embodiment of this invention. It is sectional drawing which follows the II line | wire of FIG. It is sectional drawing which follows the II-II line of FIG. It is a disassembled perspective view which shows the fin and refrigerant pipe in 1st Embodiment of this invention. It is the cross-sectional view (a) and front view (b) which show the state which penetrates the refrigerant | coolant pipe | tube in 1st Embodiment in the penetration hole provided in the fin. It is the cross-sectional view (a) and front view (b) which show the state which presses the refrigerant pipe in 1st Embodiment to the rear edge side opening part of the insertion hole provided in the fin. It is a principal part front view which shows the state which the long side of the refrigerant pipe in 1st Embodiment of this invention inclines with respect to the gravity direction. It is a schematic perspective view which shows 2nd Embodiment of the fin and tube type heat exchanger which concerns on this invention. It is a disassembled perspective view which shows the fin and refrigerant | coolant pipe | tube in 2nd Embodiment of this invention. It is a principal part front view which shows the state which the long side of the refrigerant pipe in 2nd Embodiment of this invention inclines with respect to the gravity direction. It is a principal part front view which shows the state which the long side of the refrigerant pipe in 3rd Embodiment of this invention inclines with respect to the gravity direction.

  EMBODIMENT OF THE INVENTION Below, the form for implementing this invention is demonstrated in detail based on an accompanying drawing.

<First Embodiment>
The fin-and-tube heat exchanger 1 (hereinafter referred to as heat exchanger 1) according to the present invention includes a plurality of aluminum (including aluminum alloy) members, as shown in FIGS. The plate-like fins 2 are joined to the refrigerant tubes 3, which are aluminum flat porous tubes inserted into the insertion holes 21 provided in the fins 2, through an adhesive 4. The protruding end portions of the refrigerant pipe 3 inserted through the insertion holes 21 of the plurality of fins 2 are connected by an elbow-shaped flat connection pipe 5.

  The refrigerant pipe 3 is formed of an aluminum extruded shape, and has a narrow taper shape from a widthwise front edge portion 33 located on the leeward side toward a widthwise rear edge portion 34 located on the leeward side. Is formed. In this case, the front edge portion 33 is formed in a large-diameter semicircular arc shape, the rear edge portion 34 is formed in a small-diameter semicircular arc shape, and a tapered portion 35 is provided between the front edge portion 33 and the rear edge portion 34. Is formed.

  In addition, the refrigerant pipe 3 has a plurality of rectangular flow passages 32 having the same cross-sectional area in which a cross section perpendicular to the longitudinal direction of the refrigerant pipe 3 is partitioned by a partition wall 31.

  On the other hand, the fins 2 are provided with insertion holes 21 at appropriate intervals in the vertical direction. In this case, the insertion hole 21 includes a front edge side opening 23 having a gap 50 between the refrigerant pipe 3 and the front edge 33, a rear edge side opening 24 in contact with the rear edge 34 of the refrigerant pipe 3, It consists of a tapered portion 25 connecting the edge side opening 23 and the trailing edge side opening 24.

  The leading edge side opening 23 is formed in a semicircular arc shape having a radius larger than the radius of the semicircular arc leading edge portion 33 of the refrigerant tube 3, and the trailing edge side opening portion is a semicircular arc trailing edge portion of the refrigerant tube 3. It is formed in a semicircular arc shape having the same diameter as the radius of 34 or a slightly larger radius. Each insertion hole 21 is provided with a collar portion 22 having a shape similar to that of the insertion hole 21 in the same direction.

  With this configuration, when the refrigerant tube 3 is inserted into the insertion hole 21, the front edge portion 33 of the refrigerant tube 3 is brought into sliding contact with the front edge side opening 23 of the insertion hole 21 and the inner surface of the collar portion 22. Can be inserted. Further, after inserting the refrigerant pipe into the insertion hole 21, the rear edge 34 of the refrigerant pipe 3 is pressed toward the rear edge side opening 24 of the insertion hole 21, and the rear edge 34 is brought into contact with the rear edge side opening 24. Can be made. The operation of pressing the rear edge 34 of the refrigerant pipe 3 toward the rear edge side opening 24 may be performed simultaneously with the insertion of the refrigerant pipe 3 through the insertion hole 21.

  As the fin 2 formed in this way, a pre-coated fin is used in which a surface of an aluminum material is coated with a resin film having hydrophilicity, water repellency, and corrosion resistance.

  In the heat exchanger 1 configured as described above, the potential difference between the fin 2 and the refrigerant pipe 3 is set to −40 mV to −60 mV. The reason why the potential difference between the fin 2 and the refrigerant pipe 3 is set to −40 mV to −60 mV is that when the potential difference between the fin 2 and the refrigerant pipe 3 exceeds −60 mV, the fin 2 is positively corroded, and the fin 2 Will fall off and the sacrificial protection effect will no longer be obtained. In addition, if the potential difference between the fin 2 and the refrigerant tube 3 is less than −40 mV, the potential difference is so small that a sufficient sacrificial anticorrosive effect cannot be obtained, and corrosion may proceed simultaneously in the fin and the refrigerant tube. .

  The potential difference between the aluminum fin 2 and the refrigerant pipe 3 can be set in the range of −40 mV to −60 mV by slightly changing the aluminum composition of the fin 2 and the refrigerant pipe 3.

  For example, Fe: 0.40 mass% or less, Si: 0.25 mass% or less, Cu: 0.05 mass% or less, Mn: 0.05 mass% or less, Mg: Aluminum containing 0.05% by mass or less, Zn: 0.05% by mass or less, Ti: 0.03% by mass or less, V: 0.05% by mass or less, the balance being composed of Al and inevitable impurities When an alloy is used, the alloy for the refrigerant tube 3 is Fe: 0.05-0.20 mass%, Si: 0.10 mass% or less, Cu: 0.15-0.32 mass%, Zr: 0.00. 05% by mass or less, Ti: 0.06 to 0.15% by mass, Mn: 0.08 to 0.15% by mass, Mg: 0.02% by mass or less, Zn: 0.03% by mass or less, Use an aluminum alloy with the balance consisting of Al and inevitable impurities. To. Thereby, the electric potential difference of the fin 2 and the refrigerant pipe 3 can be made into the range of -40mV--60mV.

  The heat exchanger 1 according to the first embodiment configured as described above is manufactured by the following procedure. First, a plurality of fins 2 each having an insertion hole 21 and a collar portion 22 are formed by pressing an aluminum plate material having a predetermined size in which a resin film having hydrophilicity, water repellency, and corrosion resistance is coated on the surface of an aluminum material. prepare.

  On the other hand, for example, an epoxy adhesive 4 mainly composed of a thermoplastic resin is applied to the surface of the extruded refrigerant tube 3 by using a known spray method or roller method. After the adhesive 4 is applied, the refrigerant tube 3 is dried by heating, for example, at 50 ° C. or more for 5 minutes or more. In this way, the refrigerant pipe 3 whose surface is coated with the adhesive 4 is prepared.

  Next, the plurality of fins 2 are stacked at a predetermined interval in a state where the insertion holes 21 and the collar portions 22 provided in the fins 2 are matched, and are fixed by a fixture (not shown). Then, as shown in FIG. 6, after inserting the refrigerant pipe 3 so as to contact the insertion hole 21 provided in each fin 2 and the front edge side opening 23 of the collar portion 22, or simultaneously with the insertion, as shown in FIG. 7. In this manner, the rear edge 34 of the refrigerant pipe 3 is pressed and assembled so as to contact the rear edge side opening 24 of the insertion hole 21.

  Next, the assembly of the fin 2 and the refrigerant tube 3 is heated to a temperature at which the adhesive 4 melts, for example, 100 ° C. or more for 5 minutes or more, and the insertion hole 21 of the fin 2 and the inner surface of the collar portion 22 Adhesive 4 is filled between the surfaces of the refrigerant tubes.

  Next, the assembly is cooled to solidify the adhesive 4, thereby joining the fins 2 and the refrigerant pipe 3 to produce the heat exchanger 1.

  According to this manufacturing method, the refrigerant tube 3 can be easily inserted into the insertion hole 21 provided in the fin 2, the thermal resistance due to the contact between the fin 2 and the refrigerant tube 3 is reduced, and the refrigerant tube 3 with respect to the fin 2 is reduced. Positioning can be facilitated. Moreover, since the expansion of the tube is not required, the apparatus and equipment for expanding the tube are not necessary, and the heat exchanger 1 can be easily manufactured with fewer steps.

  According to the heat exchanger 1 of the first embodiment manufactured as described above, the fins 2 and the refrigerant pipe 3 are joined via the adhesive 4 applied to the surface of the refrigerant pipe 3, so It can be easily manufactured without using it. Further, by setting the potential difference between the fin 2 and the refrigerant pipe 3 to −40 mV to −60 mV, sacrificial corrosion prevention that prevents the corrosion of the refrigerant pipe 3 by preferentially corroding the fin 2 can be performed. Corrosion resistance can be improved.

  Further, since the adhesive 4 is coated on the surface of the refrigerant pipe 3, the condensed water adhering to the surface of the refrigerant pipe 3 can be quickly discharged.

  Further, since the fin 2 is a pre-coated fin having a surface coated with a hydrophilic, water-repellent, and corrosion-resistant film, condensed water adhering to the surface of the fin 2 can be quickly discharged.

  Further, the refrigerant pipe 3 is formed in a narrow taper shape from the front edge portion 33 in the width direction located on the leeward side toward the rear edge portion 34 in the width direction located on the leeward side, as shown in FIG. Further, the long side (tapered portion 35) in the cross section orthogonal to the longitudinal direction of the refrigerant pipe 3 is inclined with respect to the gravity direction G in the installed state of the heat exchanger 1. Therefore, the condensed water adhering to the surface of the refrigerant pipe 3 can be quickly discharged, and the corrosion resistance can be improved.

Second Embodiment
As shown in FIGS. 9 to 11, the heat exchanger 1 </ b> A of the second embodiment is provided on each of the fins 2 and a plurality of plate-like fins 2 each made of an aluminum (including aluminum alloy) member. An aluminum flat porous refrigerant pipe 3 </ b> A inserted through an insertion hole 21 </ b> A inclined with respect to the vertical direction (gravity direction G) is joined via an adhesive 4. In addition, the protrusion side end parts of the refrigerant pipe 3 </ b> A inserted through the insertion holes 21 </ b> A of the plurality of fins 2 are connected by an elbow-shaped flat connection pipe 5.

  The refrigerant pipe 3A is formed of an aluminum extruded profile, and the front and back surfaces are formed in a flat oval shape parallel to each other, and a cross section perpendicular to the longitudinal direction of the refrigerant pipe 3A is partitioned by a partition wall 31. A plurality of rectangular channels 32 having the same cross-sectional area are provided.

  On the other hand, the fin 2 is provided with an inclined insertion hole 21A at an appropriate interval in the vertical direction. In this case, the insertion hole 21A is provided with a flat elliptical collar portion 22A in the same direction. The inner peripheral surfaces of the insertion hole 21A and the collar portion 22A are formed to be the same as or slightly larger than the outer peripheral surface of the refrigerant pipe 3A.

  In the second embodiment, the other parts are the same as those in the first embodiment, and thus the description thereof is omitted.

  The heat exchanger 1A according to the second embodiment is manufactured by the following procedure. First, a plurality of fins 2 having insertion holes 21A and collar portions 22A are formed by pressing an aluminum plate having a predetermined size, in which a surface of an aluminum material is coated with a resin film having hydrophilicity, water repellency, and corrosion resistance. prepare.

  On the other hand, for example, an epoxy adhesive 4 mainly composed of a thermoplastic resin is applied to the surface of the extruded refrigerant tube 3A by using a known spray method or roller method. After the adhesive 4 is applied, the refrigerant pipe 3A is dried by heating, for example, at 50 ° C. or more for 5 minutes or more. In this way, the refrigerant pipe 3A whose surface is coated with the adhesive 4 is prepared.

  Next, the plurality of fins 2 are stacked at a predetermined interval in a state where the insertion holes 21 </ b> A and the collar portions 22 </ b> A provided in the fins 2 are matched, and are fixed by a fixture (not shown). Then, the refrigerant pipe 3A is inserted into the insertion hole 21A and the collar portion 22A provided in each fin 2 and assembled.

  Next, the assembly of the fin 2 and the refrigerant tube 3A is heated to a temperature at which the adhesive 4 melts, for example, 100 ° C. or more for 5 minutes or more, and the insertion hole 21A of the fin 2 and the inner surface of the collar portion 22A Adhesive 4 is filled between the surfaces of the refrigerant tubes.

  Next, the assembly is cooled to solidify the adhesive 4, thereby joining the fins 2 and the refrigerant pipe 3A to produce the heat exchanger 1A.

  According to this manufacturing method, pipe expansion is not required, so that an apparatus and equipment for pipe expansion are not required, and the heat exchanger 1A can be easily manufactured with fewer steps.

  According to the heat exchanger 1A of the second embodiment manufactured as described above, as shown in FIG. 11, the long side in the cross section orthogonal to the longitudinal direction of the refrigerant pipe 3A is the installation state of the heat exchanger 1A. Therefore, the condensed water adhering to the surface of the refrigerant pipe 3A can be quickly discharged, and the corrosion resistance can be improved.

  Moreover, according to 1 A of heat exchangers of 2nd Embodiment, the effect similar to the heat exchanger 1 of 1st Embodiment is acquired. That is, since the fins 2 and the refrigerant pipe 3A are joined via the adhesive 4 applied to the surface of the refrigerant pipe 3A, the pipe can be easily manufactured without the need for expansion. In addition, by setting the potential difference between the fin 2 and the refrigerant pipe 3A to −40 mV to −60 mV, sacrificial corrosion prevention that preferentially corrodes the fin 2 to prevent corrosion of the refrigerant pipe 3 can be performed. Corrosion resistance can be improved.

  Further, since the adhesive 4 is coated on the surface of the refrigerant pipe 3A, the condensed water adhering to the surface of the refrigerant pipe 3 can be quickly discharged.

  Further, since the fin 2 is a pre-coated fin having a surface coated with a hydrophilic, water-repellent, and corrosion-resistant film, condensed water adhering to the surface of the fin 2 can be quickly discharged.

<Third Embodiment>
As shown in FIG. 12, the heat exchanger 1 </ b> B of the third embodiment is provided with flat elliptical refrigerant tubes 3 </ b> A formed in the same manner as in the second embodiment in parallel to the rectangular plate-like fins 2. In the installed state of the heat exchanger 1B, the long side of the cross section orthogonal to the longitudinal direction of the refrigerant pipe 3A is gravity-inserted into the flat elliptical insertion hole 21B and the collar portion (not shown). The structure is inclined with respect to the direction G.

  By configuring in this way, as in the first and second embodiments, the long side in the cross section orthogonal to the longitudinal direction of the refrigerant pipe 3A is inclined with respect to the gravity direction G, and therefore, on the surface of the refrigerant pipe 3A. The adhering condensed water can be quickly discharged, and the corrosion resistance can be improved.

  In the third embodiment, the other parts are the same as those in the first embodiment. Therefore, the same parts are denoted by the same reference numerals and description thereof is omitted.

1, 1A, 1B Heat exchanger 2 Fin 3, 3A Refrigerant tube 4 Adhesives 21, 21A, 21B Insertion hole 22, 22A Collar 31 Partition wall 32 Channel 35 Taper

Claims (5)

A fin-and-tube heat exchanger comprising a plurality of plate-like fins made of aluminum, and a flat porous refrigerant tube made of aluminum inserted into an insertion hole provided in each fin,
The fin and the refrigerant pipe are joined through an adhesive applied to the surface of the refrigerant pipe,
A fin-and-tube heat exchanger, wherein a potential difference between the fin and the refrigerant tube is -40 mV to -60 mV. The fin-and-tube heat exchanger according to claim 1,
A fin-and-tube heat exchanger, wherein the adhesive is an adhesive mainly composed of a thermoplastic resin. In the fin-and-tube heat exchanger according to claim 1 or 2,
A fin-and-tube heat exchanger, wherein the adhesive is coated on the surface of the refrigerant pipe. In the fin and tube type heat exchanger according to any one of claims 1 to 3,
The fin-and-tube heat exchanger according to claim 1, wherein the fin is a pre-coated fin having a surface coated with a film having hydrophilicity, water repellency, and corrosion resistance. The fin-and-tube heat exchanger according to any one of claims 1 to 4,
A fin-and-tube heat exchanger, characterized in that a long side in a cross section perpendicular to the longitudinal direction of the refrigerant tube is inclined with respect to the direction of gravity in the installed state of the heat exchanger.

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