WO2020234931A1

WO2020234931A1 - Heat exchanger and refrigeration cycle device

Info

Publication number: WO2020234931A1
Application number: PCT/JP2019/019726
Authority: WO
Inventors: 貴之勝丸; 真紀岡田; 亮平川端; 亮一池田
Original assignee: 三菱電機株式会社
Priority date: 2019-05-17
Filing date: 2019-05-17
Publication date: 2020-11-26

Abstract

Provided is a heat exchanger comprising a plurality of flattened heat transfer tubes having a flattened cross section, with the flattened surfaces on the long side of the flattened shape being arranged facing each other and spaced apart, and having therein a flow path through which fluid flows, and a plurality of corrugated fins arranged between two adjacent flattened heat transfer tubes and joined to the flattened heat transfer tubes at the flattened surfaces, wherein when viewing the plurality of flattened heat transfer tubes and the plurality of corrugated fins from the flow path direction, an unfinned area where the corrugated fins are not arranged is provided between at least some of the two adjacent flattened heat transfer tubes in a portion in the longitudinal direction between the facing flattened surfaces.

Description

Heat exchanger and refrigeration cycle equipment

The present invention relates to a heat exchanger and a refrigeration cycle device. In particular, it relates to a heat exchanger or the like configured by combining a corrugated fin and a flat heat transfer tube.

For example, a corrugated fin tube type heat exchanger in which corrugated fins are arranged between flat portions of a plurality of flat tubes connected between a pair of headers is widespread. Then, in the corrugated fin tube type heat exchanger, a heat exchanger in which two types of fins having different widths are alternately arranged at the bent portion of the heat exchanger along the axial direction of the header has been proposed (for example). , Patent Document 1).

Japanese Patent No. 6185669

In such a heat exchanger, if a bending force is applied to the heat exchanger, the corrugated fins may buckle. In particular, when bending is performed to create a bent portion, a compressive force is generated on the inner circumference side of the heat exchanger. As a result, the corrugated fins buckle on the inner peripheral side of the heat exchanger, causing the fins to fall. For this reason, the performance of the heat exchanger deteriorates because the air passage is blocked by the buckling of the corrugated fins.

An object of the present invention is to obtain a heat exchanger and a refrigeration cycle device capable of suppressing buckling of corrugated fins and suppressing performance deterioration in order to solve the above problems.

The heat exchanger according to the present invention has a flat cross section, and the flat surfaces on the longitudinal side of the flat shape are arranged so as to face each other with a gap between them, and a plurality of flat transmissions having a flow path through which fluid flows are provided inside. A heat exchanger having a heat tube and a plurality of corrugated fins arranged between two adjacent flat heat transfer tubes and joined to the flat heat transfer tube in a flat surface, wherein the plurality of flat heat transfer tubes and the plurality of corrugated fins are provided. When viewed from the flow path direction, a fin-unarranged portion in which corrugated fins are not arranged in a part of the longitudinal direction between the opposing flat planes between at least a part of two adjacent flat heat transfer tubes. It has.

Further, the refrigeration cycle apparatus according to the present invention has the above heat exchanger.

According to the present invention, when a plurality of flat heat transfer tubes and a plurality of corrugated fins are viewed from the flow path direction, a part of the flat shape in the longitudinal direction is provided between two adjacent flat heat transfer tubes of the heat exchanger. Has an unarranged portion in which the corrugated fins are not arranged. Therefore, a space is created between the adjacent flat heat transfer tubes, and buckling of the corrugated fins due to the compressive force generated by bending or the like can be prevented. Therefore, air can pass through without blocking the air passage, and heat exchange efficiency can be improved.

It is a figure explaining the structure of the heat exchanger which concerns on Embodiment 1. FIG. FIG. 5 is a perspective view of a main part for explaining the arrangement relationship between the flat heat transfer tube and the corrugated fin in the heat exchanger according to the first embodiment. It is a figure which shows the heat exchanger which performed the bending process which concerns on Embodiment 1. FIG. It is a figure explaining the shape of the heat exchanger which concerns on Embodiment 1. FIG. It is a figure which shows the heat exchanger which was bent in the bent part which concerns on Embodiment 1. FIG. It is a figure explaining the shape of the heat exchanger which concerns on Embodiment 2. FIG. It is a figure which shows the heat exchanger which was bent in the bent part which concerns on Embodiment 2. FIG. It is a figure explaining the shape of the heat exchanger which concerns on Embodiment 3. FIG. It is a figure which shows the heat exchanger which was bent in the bent part which concerns on Embodiment 3. FIG. It is a figure explaining the shape of the heat exchanger which concerns on Embodiment 4. FIG. It is a figure which shows the heat exchanger which bent at the bending part which concerns on Embodiment 4. It is a figure explaining the shape of the heat exchanger which concerns on Embodiment 5. It is a figure which shows the heat exchanger which bent at the bending part which concerns on Embodiment 4. It is a figure which shows the structure of the air conditioner in Embodiment 6.

Hereinafter, the heat exchanger and the refrigeration cycle apparatus according to the embodiment will be described with reference to drawings and the like. In the following drawings, those having the same reference numerals are the same or equivalent thereof, and are common to the entire text of the embodiments described below. Further, in the drawings, the relationship between the sizes of the constituent members may differ from the actual one. The form of the component represented in the entire specification is merely an example, and is not limited to the form described in the specification. In particular, the combination of components is not limited to the combination in each embodiment, and the components described in other embodiments can be applied to other embodiments. Further, the high and low pressure and temperature are not fixed in relation to the absolute values, but are relatively fixed in the state and operation of the device and the like. In addition, when it is not necessary to distinguish or specify a plurality of devices of the same type that are distinguished by subscripts, the subscripts and the like may be omitted.

Embodiment 1.
FIG. 1 is a diagram illustrating a configuration of a heat exchanger according to the first embodiment. As shown in FIG. 1, the heat exchanger 1 is a corrugated fin tube type heat exchanger having a parallel piping type. The heat exchanger 1 has a pair of headers 2 (2A and 2B), a plurality of flat heat transfer tubes 3 and a plurality of corrugated fins 4.

Each header 2 has a refrigerant inlet / outlet pipe 5 (5A and 5B) into which a refrigerant from the outside, which is a fluid, flows in and out. A plurality of flat heat transfer tubes 3 are arranged in parallel between the two headers 2 so as to be perpendicular to each header 2. Each flat heat transfer tube 3 is inserted into the header 2 via a flat tube insertion hole (not shown). Then, the contact portions between the header 2A and the header 2B and the flat heat transfer tubes 3 are joined by a brazing material. As a result, the headers 2A and 2B and the inside of each flat heat transfer tube 3 communicate with each other. In the first embodiment, the refrigerant flows from the refrigerant inlet / outlet pipe 5A into the header 2A. Then, the refrigerant passes through each of the flat heat transfer tubes 3, merges at the header 2B, and flows out from the refrigerant inlet / outlet pipe 5B. However, the present invention is not limited to this, and the inflow and outflow directions of the refrigerant may be opposite. Here, as shown in FIG. 2 described later, when the heat exchanger 1 is used as a condenser, high-temperature and high-pressure refrigerant flows through the refrigerant flow path in the flat heat transfer tube 3. When the heat exchanger 1 is used as an evaporator, low-temperature and low-pressure refrigerant flows through the refrigerant flow path in the flat heat transfer tube 3.

FIG. 2 is a perspective view of a main part for explaining the arrangement relationship between the flat heat transfer tube and the corrugated fin in the heat exchanger according to the first embodiment. As shown in FIG. 2, the flat heat transfer tube 3 of the first embodiment has a flat cross section, and the outer surface on the longitudinal side of the flat shape in the air flow direction is a flat surface (hereinafter referred to as a flat surface). , A heat transfer tube having a curved outer surface on the short side orthogonal to the longitudinal direction. Therefore, the flat heat transfer tube 3 has a pair of flat surface portions 3A of the heat transfer tube and a pair of curved surface portions 3B of the heat transfer tube. Further, the flat heat transfer tube 3 has a plurality of refrigerant flow paths 3C inside. Here, it is desirable that the flat heat transfer tube 3 is made of a metal having good heat transfer properties. Therefore, the flat heat transfer tube 3 is made of, for example, aluminum. Hereinafter, the longitudinal direction and the lateral direction in the flat shape of the flat heat transfer tube 3 and the flow path direction orthogonal to these will be described as a reference of the direction.

Further, as shown in FIG. 2, the corrugated fin 4 is a fin formed in a bellows shape by a zigzag fold in which a plate-shaped member is repeatedly folded in a mountain fold and a valley fold. The corrugated fin 4 has a fin flat surface portion 4A serving as an abdomen and a fin curved surface portion 4B serving as a top portion. Then, the flat surface portions 3A of the heat transfer tubes facing each other of the adjacent flat heat transfer tubes 3 and the curved surface portion 4B of the fins of the corrugated fins 4 are joined by brazing. In the first embodiment, as will be described later, the first fin 41 and the second fin 42, which are distinguished by the joining position of the flat heat transfer tube 3 with the flat surface portion 3A of the heat transfer tube, are provided as corrugated fins 4. Here, it is desirable that the corrugated fin 4 is also made of a metal having good heat transfer properties. Therefore, the corrugated fin 4 is made of, for example, aluminum.

FIG. 3 is a diagram showing a heat exchanger in which the bending process according to the first embodiment is performed. The heat exchanger 1 according to the first embodiment has a flat lateral direction in which a plurality of flat heat transfer tubes 3 are arranged in a row direction before being mounted on an outdoor unit of a refrigeration cycle device, for example. Bending is performed once or multiple times in the axial direction of the header 2. When the heat exchanger 1 shown in FIG. 1 is bent once, the heat exchanger 1 as shown in FIG. 3 can be obtained.

FIG. 4 is a diagram illustrating the shape of the heat exchanger according to the first embodiment. FIG. 4 shows the shape of the heat exchanger 1 before bending. The heat exchanger 1 of the first embodiment has a straight portion 6 that is not bent and a bent portion 7 that is bent. For example, in the case of one-time bending, the heat exchanger 1 has a bending portion 7 between the straight portions 6 at both ends. The straight portion 6 and the bent portion 7 have different joint positions between the fin curved surface portion 4B of the corrugated fin 4 and the heat transfer tube flat surface portion 3A of the flat heat transfer tube 3.

Of the corrugated fins 4, the corrugated fin 4 at the bent portion 7 is designated as the first fin 41. Further, the corrugated fin 4 in the straight line portion 6 is referred to as a second fin 42. In the second fin 42, the entire fin curved surface portion 4B, which is the top of the corrugated fin 4, is joined to the flat surface portion 3A of the heat transfer tube of the flat heat transfer tube 3. Therefore, the flat heat transfer tube 3 and the second fin 42 are joined in a normal positional relationship. The first fin 41 has a positional relationship different from the positional relationship between the second fin 42 and the flat heat transfer tube 3 in the straight portion 6 in the longitudinal direction which is the air passage direction, and the heat transfer tube flat surface portion 3A of the flat heat transfer tube 3 It is joined with. In the first embodiment, the first fin 41 is joined to the flat heat transfer tube 3 by shifting the position so as to project toward the outer peripheral side of the heat exchanger 1 by bending. Therefore, in the first embodiment, as shown in FIG. 4, when the flat heat transfer tube 3 and the first fin 41 are viewed from the direction of the refrigerant flow path 3C, the two flat heat transfer tubes adjacent to each other in the bent portion 7 are viewed. A space is formed in the fin-unarranged portion 43 in which the first fin 41 is not arranged between the three. Further, on the outer peripheral side of the heat exchanger 1, a part of the fin curved surface portion 4B is joined to the heat transfer tube flat surface portion 3A of the flat heat transfer tube 3 because the first fin 41 protrudes from the end portion of the flat heat transfer tube 3. Not done. Here, the first fin 41 and the second fin 42 in the first embodiment differ only in the positions where they are arranged between the adjacent flat heat transfer tubes 3. Therefore, the first fin 41 and the second fin 42 can use corrugated fins 4 having the same fin width corresponding to the longitudinal direction.

FIG. 5 is a diagram showing a heat exchanger in which bending is performed in the bent portion according to the first embodiment. When the heat exchanger 1 shown in FIG. 4 is bent at the bending portion 7, the heat exchanger 1 shown in FIG. 5 can be manufactured. As described above, the bending process in the bent portion 7 is performed in the direction in which the protruding side of the first fin 41 is the outer circumference. Therefore, the inner peripheral side of the bent portion 7 is a space created by the fin unarranged portion 43 in which the first fin 41 is not arranged. Therefore, the compressive force acting on the first fin 41 is reduced during the bending process. Therefore, buckling due to bending can be suppressed at the first fin 41 of the bending portion 7. Here, regarding the space created in the fin-unarranged portion 43, the first fin 41 and the flat heat transfer tube 3 are not joined to the length in the longitudinal direction of the flat heat transfer tube 3, and the portion not arranged is 20% or more. If a space having a length of 2 is secured, the effect of suppressing buckling can be obtained.

As described above, according to the heat exchanger 1 of the first embodiment, the bending portion 7 to be bent is more air-like than the positional relationship between the second fin 42 of the straight portion 6 and the flat heat transfer tube 3. The first fin 41 is joined to a position shifted in the passing direction. As a result, in the bent portion 7, a space is formed between the adjacent flat heat transfer tubes 3 by the fin-unarranged portion 43 in which the first fin 41 is not arranged. Therefore, it is possible to prevent the first fin 41 from buckling due to the compressive force applied to the first fin 41 during bending. At the bent portion 7, it is possible to suppress blockage of the air passage through which air passes. Therefore, the heat exchanger 1 of the first embodiment can suppress a decrease in heat exchange efficiency.

Further, the same type of corrugated fin 4 can be used for the second fin 42 of the straight portion 6 and the first fin 41 of the bent portion 7. Therefore, in the production of the heat exchanger 1, it is not necessary to change the setup and prepare new equipment and molds, and the production cost and the production space can be reduced.

Embodiment 2.
FIG. 6 is a diagram illustrating the shape of the heat exchanger according to the second embodiment. In FIG. 6, the members and the like having the same reference numerals as those in FIG. 4 and the like are the same as those described in the first embodiment. In the second embodiment, the positional relationship between the first fin 41 and the flat heat transfer tube 3 in the bent portion 7 is defined in more detail.

As described above, the first fin 41 is joined to the flat heat transfer tube 3 by the fin-unarranged portion 43 so as to protrude in the outer peripheral direction by bending. At this time, as shown in FIG. 6, of the two fin ends in the longitudinal direction of the first fin 41, the fin end on the side joined to the flat heat transfer tube 3 is in the longitudinal direction of the flat heat transfer tube 3. It is located at the central portion or on the outer peripheral side of the heat exchanger 1. Therefore, in the two fin ends, one fin end is in the center portion, or both fin ends including the other fin end are located on the same side. Here, the widths of the first fin 41 and the second fin 42 are the same.

FIG. 7 is a diagram showing a heat exchanger in which bending is performed in the bent portion according to the second embodiment. When the heat exchanger 1 shown in FIG. 6 is bent at the bending portion 7, the heat exchanger 1 shown in FIG. 7 can be manufactured. In the heat exchanger 1 of the second embodiment, the portion where the first fin 41 and the flat heat transfer tube 3 are not joined is 50% of the length in the longitudinal direction of the flat heat transfer tube 3 due to the fin unarranged portion 43. A space with the above length is secured. Therefore, buckling of the first fin 41 can be prevented.

Embodiment 3.
FIG. 8 is a diagram illustrating the shape of the heat exchanger according to the third embodiment. In FIG. 8, the members and the like having the same reference numerals as those in FIG. 4 and the like are the same as those described in the first embodiment. In the third embodiment, the flat heat transfer tube 3 is displaced so that the second fin 42 of the straight portion 6 has the fin unarranged portion 43 and protrudes in the direction of the outer circumference when the bending process is performed. Is joined with.

FIG. 9 is a diagram showing a heat exchanger in which bending is performed in the bent portion according to the third embodiment. When the heat exchanger 1 shown in FIG. 8 is bent at the bending portion 7, the heat exchanger 1 shown in FIG. 9 can be manufactured. Here, the heat exchanger 1 of the third embodiment can be bent to form the bent portion 7 in any portion. Therefore, in the manufacturing process, the heat exchanger 1 can be manufactured without specifying the bent portion 7 and the straight portion 6 to be bent in advance, so that the types of the heat exchanger 1 required for manufacturing are not increased. I live in. Further, in the production of the heat exchanger 1, it is not necessary to change the setup and prepare new equipment and molds, and the production cost and the production space can be reduced.

Embodiment 4.
FIG. 10 is a diagram illustrating the shape of the heat exchanger according to the fourth embodiment. In FIG. 10, the members and the like having the same reference numerals as those in FIG. 4 and the like are the same as those described in the first embodiment. The corrugated fins 4 of the first to third embodiments have a width that matches the length of the flat surface portion 3A of the heat transfer tube in the longitudinal direction of the flat heat transfer tube 3. In the heat exchanger 1 of the fourth embodiment, the width of the corrugated fin 4 is 0.5 times the length of the flat surface portion 3A of the heat transfer tube in the longitudinal direction of the flat heat transfer tube 3. Then, in the straight line portion 6, the corrugated fins 4 are arranged in parallel in two stages in the width direction to form the second fin 42. Further, in the bent portion 7, the corrugated fins 4 are arranged in one step in the width direction to form the first fin 41. Here, in the fourth embodiment, the first fin 41 has the corrugated fin 4 arranged on the outer peripheral side of the heat exchanger 1 by bending. Therefore, a space is formed on the inner circumference side of the heat exchanger 1 by bending.

FIG. 11 is a diagram showing a heat exchanger in which bending is performed in the bent portion according to the fourth embodiment. When the heat exchanger 1 shown in FIG. 10 is bent at the bending portion 7, the heat exchanger 1 shown in FIG. 11 can be manufactured. Therefore, as in the first embodiment, the first fin 41 is not joined to the inner peripheral side of the bent portion 7. Therefore, the first fin 41 is not subjected to the compressive force due to the bending process, and the buckling of the first fin 41 can be prevented. Then, it is possible to eliminate the blockage of the air passage in the bent portion 7 and prevent the heat exchange efficiency in the heat exchanger 1 from being lowered. The width of the first fin 41 is short because the corrugated fin 4 having a length of 0.5 times the length of the flat surface portion 3A of the heat transfer tube is formed in one stage. Although the surface area of the corrugated fin 4 is reduced by that amount, the heat exchange efficiency is not lowered because the air passage can be secured in the bent portion 7.

Further, in the heat exchanger 1 of the fourth embodiment, since the corrugated fins 4 do not protrude to the outside, there is no possibility that the fins on the design surface will fall during the bending process. Further, the same type of corrugated fin 4 can be used for the second fin 42 and the first fin 41. Therefore, the manufacturing cost and the manufacturing space can be reduced.

Embodiment 5.
FIG. 12 is a diagram illustrating the shape of the heat exchanger according to the fifth embodiment. In FIG. 12, the members and the like having the same reference numerals as those in FIG. 4 and the like are the same as those described in the first embodiment. The corrugated fins 4 of the first to third embodiments have a width that matches the length of the flat surface portion 3A of the heat transfer tube in the longitudinal direction of the flat heat transfer tube 3. In the heat exchanger 1 of the fourth embodiment, the width of the corrugated fins 4 to be the first fin 41 and the second fin 42 is set to 0. The width shall be 5 times or more and less than 1 time. More preferably, the width is smaller than 0.8 times. Then, in both the straight portion 6 and the bent portion 7, a space is formed between the two adjacent flat heat transfer tubes 3 by the fin-unarranged portion 43 in which the first fin 41 and the second fin 42 are not arranged. To do so. Further, in the straight portion 6 and the bent portion 7, the position of the fin end portion on the side opposite to the fin end portion on the fin unarranged portion 43 side does not exceed the heat transfer tube end portion in the flat heat transfer tube 3.

When the width of the corrugated fin 4 is 0.8 times or more the length of the flat heat transfer tube 3A, the space formed between the two adjacent flat heat transfer tubes 3 is narrow and the fins are suppressed from collapsing. It may not be effective. On the other hand, if the width of the corrugated fin 4 is smaller than 0.5 times the length of the flat surface portion 3A of the heat transfer tube, the surface area of the corrugated fin 4 becomes small, so that the heat exchange efficiency decreases. Therefore, the width of the corrugated fin 4 is set to be 0.5 times or more and less than 0.8 times the length of the flat surface portion 3A of the heat transfer tube.

FIG. 13 is a diagram showing a heat exchanger in which bending is performed in the bent portion according to the fourth embodiment. When the heat exchanger 1 shown in FIG. 12 is bent at the bending portion 7, the heat exchanger 1 shown in FIG. 13 can be manufactured. Here, the heat exchanger 1 of the fifth embodiment can be bent to form the bent portion 7 in any portion. Therefore, in the manufacturing process, the heat exchanger 1 can be manufactured without specifying in advance the bending portion 7 and the straight portion 6 to be bent, without increasing the types of the heat exchanger 1 required for manufacturing. I'm sorry. Further, in the production of the heat exchanger 1, it is not necessary to change the setup and prepare new equipment and molds, and the production cost and the production space can be reduced. Further, in the heat exchanger 1 of the fifth embodiment, since the corrugated fins 4 do not protrude to the outside, there is no possibility that the fins on the design surface will fall during the bending process.

Embodiment 6.
FIG. 14 is a diagram showing the configuration of the air conditioner according to the sixth embodiment. In the sixth embodiment, an air conditioner will be described as an example of the refrigeration cycle device. As shown in FIG. 14, in the air conditioner, a refrigerant circuit is configured by connecting the outdoor unit 200 and the indoor unit 100 with a gas refrigerant pipe 300 and a liquid refrigerant pipe 400. The outdoor unit 200 includes a compressor 210, a four-way valve 220, and an outdoor heat exchanger 230. In the air conditioner of the sixth embodiment, it is assumed that one outdoor unit 200 and one indoor unit 100 are connected by piping.

The compressor 210 compresses the sucked refrigerant and discharges it. Although not particularly limited, the compressor 210 of the first embodiment can change the capacity of the compressor 210 by arbitrarily changing the operating frequency by, for example, an inverter circuit or the like. The four-way valve 220 is a valve that switches the flow of the refrigerant depending on, for example, the cooling operation and the heating operation.

The outdoor heat exchanger 230 exchanges heat between the refrigerant and the outdoor air. For example, it functions as an evaporator during heating operation to evaporate and vaporize the refrigerant. In addition, it functions as a condenser during cooling operation to condense and liquefy the refrigerant.

The indoor heat exchanger 110 exchanges heat between, for example, the air in the room to be air-conditioned and the refrigerant. During heating operation, it functions as a condenser to condense and liquefy the refrigerant. In addition, it functions as an evaporator during cooling operation to evaporate and vaporize the refrigerant.

On the other hand, the indoor unit 100 has an indoor heat exchanger 110, an expansion valve 120, and an indoor fan 130. The expansion valve 120, such as a throttle device, decompresses and expands the refrigerant. For example, in the case of an electronic expansion valve or the like, the opening degree is adjusted based on an instruction from a control device (not shown) or the like. Further, the indoor heat exchanger 110 exchanges heat between the air in the room, which is the space subject to air conditioning, and the refrigerant. For example, during heating operation, it functions as a condenser to condense and liquefy the refrigerant. In addition, it functions as an evaporator during cooling operation to evaporate and vaporize the refrigerant. The indoor fan 130 passes the indoor air through the indoor heat exchanger 110, and supplies the air that has passed through the indoor heat exchanger 110 into the room.

As described above, according to the air conditioner of the sixth embodiment, the heat exchanger described in the first to fifth embodiments is used as the outdoor heat exchanger 230, so that the heat exchange performance is improved. It is possible to measure and improve the operating efficiency of the air conditioner.

Although the above-described sixth embodiment has described the air conditioner, it can also be applied to other refrigeration cycle devices such as a refrigerating device, a refrigerating device, and a hot water supply device.

1 heat exchanger, 2, 2A, 2B header, 3 flat heat transfer tube, 3A heat transfer tube flat surface, 3B heat transfer tube curved surface, 3C refrigerant flow path, 4 corrugated fin, 4A fin flat surface, 4B fin curved surface, 5, 5A, 5B Refrigerant inlet / outlet pipe, 6 straight part, 7 bending part, 41 first fin, 42 second fin, 43 fin unplaced part, 100 indoor unit, 110 indoor heat exchanger, 120 expansion valve, 130 indoor fan, 200 Outdoor unit, 210 compressor, 220 four-way valve, 230 outdoor heat exchanger, 300 gas refrigerant pipe, 400 liquid refrigerant pipe.

Claims

A plurality of flat heat transfer tubes having a flat cross section, having flat surfaces on the longitudinal side of the flat shape facing each other and arranged with a gap between them, and having a flow path through which a fluid flows.
A heat exchanger that is arranged between two adjacent flat heat transfer tubes and includes a plurality of corrugated fins that are joined to the flat heat transfer tubes in the flat surface.
When the plurality of flat heat transfer tubes and the plurality of corrugated fins are viewed from the flow path direction, the longitudinal direction between the flat surfaces facing each other between at least a part of the two adjacent flat heat transfer tubes. A heat exchanger having a fin-unarranged portion in which the corrugated fin is not arranged.
The heat exchanger according to claim 1, wherein the fin-unarranged portion is a portion on the inner peripheral side of a bent portion in which a row in which a plurality of the flat heat transfer tubes are arranged is bent by bending.
The heat exchanger according to claim 1, which has the fin-unarranged portion between all two adjacent flat heat transfer tubes.
Of the two fin ends of the corrugated fin corresponding to the longitudinal direction, the fin end portion of the one joined to the flat heat transfer tube is the central portion of the flat heat transfer tube in the longitudinal direction or the other fin. The heat exchanger according to any one of claims 1 to 3, which is located on the same side as the end portion.
The corrugated fin has a width of 0.5 times the length of the flat heat transfer tube in the longitudinal direction.
One corrugated fin is arranged in the longitudinal direction in the fin-unarranged portion.
The heat exchanger according to any one of claims 1 to 4, wherein two corrugated fins are arranged in parallel in the longitudinal direction in a portion other than the fin-unarranged portion.
The corrugated fin
The ratio of the flat heat transfer tube to the length in the longitudinal direction is greater than 0.5 and has a width less than 1.
A claim in which the fin end portion on the side opposite to the fin non-arranged portion of the fin end portions corresponding to the longitudinal direction is arranged at a position not exceeding the heat transfer tube end portion in the longitudinal direction of the flat heat transfer tube. The heat exchanger according to any one of claims 1 to 3.
A refrigeration cycle apparatus having the heat exchanger according to any one of claims 1 to 6.