CN115667830A

CN115667830A - Heat exchanger and refrigeration cycle device

Info

Publication number: CN115667830A
Application number: CN202080101390.5A
Authority: CN
Inventors: 森田敦; 前田刚志; 八柳晓; 石桥晃
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2020-06-01
Filing date: 2020-06-01
Publication date: 2023-01-31
Also published as: US20230175747A1; JPWO2021245734A1; EP4160112A1; JP7353489B2; WO2021245734A1; EP4160112A4

Abstract

The heat exchanger is provided with: a first header collecting and distributing refrigerant and extending in a first direction; a second header provided at a position opposed to the first header, collecting and distributing the refrigerant, and extending in the first direction; and a plurality of heat transfer members extending from the first header toward the second header and disposed at intervals in the first direction, the heat transfer members having: a plurality of heat transfer tubes extending from the first header toward the second header and having refrigerant flowing therein; and an extension part which is provided on the heat transfer pipe and promotes the heat transfer performance of the heat transfer pipe, the extension part having: a base portion extending from the heat transfer pipe in a second direction, which is a flow direction of air flowing between the plurality of heat transfer pipes; and a spacer portion extending from the base portion in the first direction and abutting against the adjacent heat transfer member.

Description

Heat exchanger and refrigeration cycle device

Technical Field

The present invention relates to a heat exchanger and a refrigeration cycle apparatus that perform heat exchange between refrigerant and air.

Background

Conventionally, as a heat exchanger for exchanging heat between a refrigerant and air, a finless heat exchanger is known in which no fins are provided in the arrangement direction of heat transfer tubes. Since the finless heat exchanger has no fins, the heat transfer tubes are not held in the direction in which the heat transfer tubes are arranged. Therefore, the heat transfer pipe is easily bent by thermal stress and assembly error. This makes it difficult to make the pitches between adjacent heat transfer tubes uniform. If there is a portion where the pitch is locally narrowed in the adjacent heat transfer tubes, the air flow resistance increases due to the drift of air, and clogging due to dust and clogging due to frost at the time of frosting are likely to occur.

In order to solve the above problem, patent document 1 discloses a heat exchanger in which comb-tooth-shaped auxiliary members extending in the direction of arrangement of refrigerant flow paths are provided between adjacent heat transfer tubes. In this way, patent document 1 attempts to maintain a uniform pitch between adjacent heat transfer tubes.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2018-162953

Disclosure of Invention

Problems to be solved by the invention

However, in the heat exchanger disclosed in patent document 1, although the pitch between the adjacent heat transfer tubes is intended to be uniform, the heat transfer performance of the heat transfer tubes is low because the fins are not present.

The present invention has been made to solve the above-described problems, and provides a heat exchanger and a refrigeration cycle apparatus that make the pitch between heat transfer tubes uniform and improve the heat transfer performance of the heat transfer tubes.

Means for solving the problems

The heat exchanger of the present invention comprises: a first header collecting and distributing refrigerant and extending in a first direction; a second header provided at a position opposed to the first header, collecting and distributing the refrigerant, and extending in the first direction; and a plurality of heat transfer members extending from the first header toward the second header and disposed at intervals in the first direction, the heat transfer members having: a plurality of heat transfer tubes extending from the first header toward the second header, inside which refrigerant flows; and an extension portion provided to the heat transfer pipe to promote heat transfer performance of the heat transfer pipe, the extension portion including: a base portion that extends from the heat transfer pipe in a second direction that is a flow direction of air flowing between the plurality of heat transfer pipes; and a spacer portion extending in the first direction from the base portion and abutting against the adjacent heat transfer member.

Effects of the invention

According to the present invention, the heat transfer member includes the heat transfer pipe and the extension portion, and the extension portion includes the spacing portion extending in the first direction from the base portion and abutting against the adjacent heat transfer member. Since the spacer portion abuts on the adjacent heat transfer member, the pitch between the heat transfer tubes can be made uniform. Further, the extension portion has a base portion extending in the second direction from the heat transfer pipe, so that the heat transfer performance of the heat transfer pipe is improved. Thus, the heat exchanger can make the pitch between the heat transfer tubes uniform and improve the heat transfer performance of the heat transfer tubes.

Drawings

Fig. 1 is a circuit diagram showing a refrigeration cycle apparatus according to embodiment 1.

Fig. 2 is a perspective view showing a heat exchanger according to embodiment 1.

Fig. 3 is a front view showing a heat exchanger according to embodiment 1.

Fig. 4 is a plan view showing a state where the first header of the heat exchanger according to embodiment 1 is removed.

Fig. 5 is a side view showing a method of manufacturing a heat exchanger according to embodiment 1.

Fig. 6 is a plan view showing a state where the first header of the heat exchanger according to the first modification of embodiment 1 is removed.

Fig. 7 is a plan view showing a state where the first header of the heat exchanger according to the second modification of embodiment 1 is removed.

Fig. 8 is a plan view showing a state where the first header of the heat exchanger according to the third modification of embodiment 1 is removed.

Fig. 9 is a plan view showing a state where the first header of the heat exchanger of embodiment 2 is removed.

Fig. 10 is a side view showing a method of manufacturing a heat exchanger according to embodiment 2.

Fig. 11 is a side view showing a heat exchanger according to embodiment 3.

Fig. 12 is a plan view showing a state where the first header of the heat exchanger according to embodiment 3 is removed.

Fig. 13 is a side view showing a heat exchanger according to a first modification of embodiment 3.

Fig. 14 is a plan view showing a state where the first header of the heat exchanger according to the first modification of embodiment 3 is removed.

Fig. 15 is a side view showing a heat exchanger according to a second modification of embodiment 3.

Fig. 16 is a plan view showing a state where the first header of the heat exchanger according to the second modification of embodiment 3 is removed.

Fig. 17 is a plan view showing a heat exchanger according to embodiment 4 with the first header removed.

Fig. 18 is a plan view showing a heat exchanger according to a modification of embodiment 4 with the first header removed.

Fig. 19 is a front view showing a heat exchanger according to embodiment 5.

Fig. 20 is a front view showing a heat exchanger according to a modification of embodiment 5.

Fig. 21 is a front view showing a heat exchanger according to embodiment 6.

Fig. 22 is a front view showing a heat exchanger according to a modification of embodiment 6.

Detailed Description

Embodiments of a heat exchanger and a refrigeration cycle apparatus according to the present invention will be described below with reference to the drawings. The present invention is not limited to the embodiments described below. In the following drawings including fig. 1, the relationship in size of each component may be different from the actual one. In the following description, terms indicating directions are used as appropriate in order to facilitate understanding of the present invention, but these terms are used for the purpose of describing the present invention and do not limit the present invention. Examples of the terms indicating the direction include "up", "down", "right", "left", "front", and "rear".

Embodiment mode 1

Fig. 1 is a circuit diagram showing a refrigeration cycle apparatus 1 according to embodiment 1. The refrigeration cycle apparatus 1 is, for example, an air conditioner that adjusts indoor air, and includes an outdoor unit 2 and an indoor unit 3, as shown in fig. 1. The outdoor unit 2 is provided with, for example, a compressor 6, a flow switching device 7, a heat exchanger 8, an outdoor fan 9, and an expansion unit 10. The indoor unit 3 is provided with, for example, an indoor heat exchanger 11 and an indoor fan 12.

The compressor 6, the flow path switching device 7, the heat exchanger 8, the expansion unit 10, and the indoor heat exchanger 11 are connected by the refrigerant pipe 5 to constitute the refrigerant circuit 4. The compressor 6 sucks a low-temperature and low-pressure refrigerant, compresses the sucked refrigerant to a high-temperature and high-pressure refrigerant, and discharges the refrigerant. The flow switching device 7 is a device for switching the direction in which the refrigerant flows through the refrigerant circuit 4, and is, for example, a four-way valve. The heat exchanger 8 is a device that performs heat exchange between outdoor air and refrigerant, for example. The heat exchanger 8 functions as a condenser during the cooling operation and functions as an evaporator during the heating operation. The outdoor blower 9 is a device that sends outdoor air to the heat exchanger 8.

The expansion unit 10 is a decompression valve or an expansion valve that decompresses and expands the refrigerant. The expansion unit 10 is, for example, an electronic expansion valve whose opening degree is adjusted. The indoor heat exchanger 11 is a device that performs heat exchange between indoor air and refrigerant, for example. The indoor heat exchanger 11 functions as an evaporator during the cooling operation and functions as a condenser during the heating operation. The indoor fan 12 is a device that sends indoor air to the indoor heat exchanger 11. The refrigerant may be water or an antifreeze.

(operation mode, cooling operation)

Next, the operation mode of the refrigeration cycle apparatus 1 will be described. First, the cooling operation will be described. In the cooling operation, the refrigerant drawn into the compressor 6 is compressed by the compressor 6 and discharged in a high-temperature and high-pressure gas state. The high-temperature and high-pressure refrigerant in a gas state discharged from the compressor 6 passes through the flow switching device 7, flows into the heat exchanger 8 functioning as a condenser, exchanges heat with the outdoor air sent by the outdoor air-sending device 9 in the heat exchanger 8, and is condensed and liquefied.

The condensed refrigerant in a liquid state flows into the expansion unit 10, and is expanded and decompressed in the expansion unit 10, thereby becoming a low-temperature and low-pressure refrigerant in a gas-liquid two-phase state. The two-phase gas-liquid refrigerant then flows into the indoor heat exchanger 11 functioning as an evaporator, and is evaporated and gasified in the indoor heat exchanger 11 by exchanging heat with the indoor air sent by the indoor air-sending device 12. At this time, the indoor air is cooled, and cooling is performed indoors. The evaporated low-temperature low-pressure refrigerant in a gas state is sucked into the compressor 6 through the flow switching device 7.

(operation mode, heating operation)

Next, the heating operation will be described. In the heating operation, the refrigerant drawn into the compressor 6 is compressed by the compressor 6 and discharged in a high-temperature and high-pressure gas state. The high-temperature and high-pressure refrigerant in a gas state discharged from the compressor 6 passes through the flow switching device 7 and flows into the indoor heat exchanger 11 functioning as a condenser. The refrigerant flowing into the indoor heat exchanger 11 exchanges heat with the indoor air sent by the indoor air-sending device 12 in the indoor heat exchanger 11, condenses, and liquefies. At this time, the indoor air is heated, and heating is performed in the room.

The condensed refrigerant in a liquid state flows into the expansion unit 10, and is expanded and decompressed in the expansion unit 10, thereby becoming a low-temperature and low-pressure refrigerant in a gas-liquid two-phase state. The two-phase gas-liquid refrigerant then flows into the heat exchanger 8 functioning as an evaporator, and is evaporated and gasified in the heat exchanger 8 by exchanging heat with the outdoor air sent by the outdoor air-sending device 9. The evaporated low-temperature low-pressure refrigerant in a gas state is sucked into the compressor 6 through the flow switching device 7.

(Heat exchanger 8)

Fig. 2 is a perspective view showing a heat exchanger 8 according to embodiment 1. As shown in fig. 2, the heat exchanger 8 includes a first header 20, a second header 30, and a heat transfer member 40. In the drawings of fig. 2 and the following, the direction in which the first header 20 and the second header 30 extend is referred to as a first direction, the direction of air flow is referred to as a second direction, and the direction of gravity is referred to as a third direction. In embodiment 1, the direction of gravity is defined as the third direction, but may be defined as the first direction or as the second direction. In embodiment 1, the case where the heat exchanger 8 is applied to an outdoor heat exchanger provided in the outdoor unit 2 is illustrated, but the present invention may be applied to an indoor heat exchanger 11 provided in the indoor unit 3. The heat exchanger 8 according to embodiment 1 can be used as a device functioning as a condenser or an evaporator.

(first header 20)

The first header 20 is a rectangular parallelepiped member extending in the first direction, and a refrigerant flows therein. The first header 20 collects and distributes the refrigerant. The first header 20 is not limited to a rectangular parallelepiped shape, and may be cylindrical or formed in another shape. The first header 20 distributes the refrigerant flowing in from the refrigerant pipes 5 to the heat transfer tubes 50 of the heat transfer member 40, and gathers the refrigerant flowing out from the heat transfer tubes 50 and flows out to the refrigerant pipes 5.

(second header 30)

The second header 30 is a rectangular parallelepiped member provided at a position facing the first header 20 and extending in the first direction, and a refrigerant flows therein. The second header 30 collects and distributes the refrigerant. The second header 30 is not limited to a rectangular parallelepiped shape, and may be cylindrical or formed in another shape. The second header 30 distributes the refrigerant flowing in from the refrigerant pipes 5 to the heat transfer tubes 50 of the heat transfer member 40, and gathers the refrigerant flowing out from the heat transfer tubes 50 and flows out to the refrigerant pipes 5.

(Heat transfer component 40)

Fig. 3 is a front view showing the heat exchanger 8 according to embodiment 1, and fig. 4 is a plan view showing a state where the first header 20 of the heat exchanger 8 according to embodiment 1 is removed. The heat transfer members 40 are members that transfer heat, and as shown in fig. 2, 3, and 4, extend from the first header 20 toward the second header 30, and are arranged at intervals in the first direction. The heat transfer member 40 is provided in plurality and has a heat transfer pipe 50 and an extension portion 60.

(Heat-transfer pipe 50)

The heat transfer pipe 50 is a flat pipe having a plurality of flow paths 51 formed therein. The heat transfer pipe 50 may be a circular pipe. The heat transfer pipes 50 are members that extend in the third direction from the first header 20 toward the second header 30. The refrigerant flowing from the first header 20 or the second header 30 flows through the plurality of flow paths 51. The heat transfer pipe 50 is made of aluminum, for example, but other metals may be used.

(extension 60)

The extension portion 60 is provided in the heat transfer pipe 50 to promote heat transferability of the heat transfer pipe 50. The extension portions 60 extend in the second direction away from each other from the apexes of the two ends of the heat transfer pipe 50 in the second direction. That is, 2 extension portions 60 are provided for 1 heat transfer pipe 50. In fig. 2, the length of 1 extending portion 60 in the second direction is slightly shorter than the length of the heat transfer pipe 50 in the second direction, but the length of the extending portion 60 may be the same as the length of the heat transfer pipe 50 or may be longer than the length of the heat transfer pipe 50. The extension 60 is, for example, aluminum, but other metals may be used. The extension portion 60 may be provided integrally with the heat transfer pipe 50 by extrusion molding. The extension portion 60 may be formed separately from the heat transfer tube 50 and then joined to the heat transfer tube 50. The extension 60 has a base 61 and a spacer 62.

(base 61)

The base portion 61 is a plate-like member that extends from the heat transfer tubes 50 in the second direction, which is the flow direction of air flowing between the heat transfer tubes 50. The base portion 61 occupies most of the extension portion 60, and plays a role of mostly promoting the heat transfer performance of the heat transfer pipe 50.

(spacer 62)

The spacer 62 extends in the first direction from the base 61. The spacer 62 is formed by bending a part of the base 61 and extending in the first direction. In embodiment 1, the spacer 62 is provided at the upper end of the base 61 in the third direction, adjacent to the first header 20. The spacer 62 may be provided at the lower end portion of the base 61 in the third direction, or may be provided at another position. As shown in fig. 4, the base ends of the spacer portions 62 are connected to the heat transfer pipe 50, the spacer portions 62 are bent and extend in the first direction, and the tip ends of the spacer portions 62 are bent and extend in the second direction. The ends of the pair of partitions 62 provided at both ends of the heat transfer pipe 50 extend in the second direction so as to face each other. Here, the length of the spacer 62 extending in the first direction is set to the distance between the adjacent heat transfer tubes 50, that is, the pitch.

The spacer 62 abuts on the adjacent heat transfer member 40. In embodiment 1, the spacer portions 62 abut against the heat transfer tubes 50 in the heat transfer member 40.

(production method)

Fig. 5 is a side view showing a method of manufacturing the heat exchanger 8 according to embodiment 1. Next, a method for manufacturing the spacer 62 will be described. As shown in fig. 5, the spacer 62 is formed by forming a notch 63 in the second direction in the base 61. That is, the spacer 62 is formed by bending the base 61, in which the notch 63 is formed in the second direction, in the first direction.

According to embodiment 1, the heat transfer member 40 having the heat transfer pipe 50 and the extension portion 60 is provided, and the extension portion 60 has the spacing portion 62 extending in the first direction from the base portion 61 and abutting against the adjacent heat transfer member 40. Since the spacers 62 abut on the adjacent heat transfer members 40, the pitch between the heat transfer tubes 50 can be made uniform. Further, since the extension portion 60 has the base portion 61 extending in the second direction from the heat transfer pipe 50, the heat transfer performance of the heat transfer pipe 50 is improved. In this way, the heat exchanger 8 can make the pitches of the heat transfer tubes 50 uniform, and improve the heat transferability of the heat transfer tubes 50. In addition, when the spacer portions 62 are provided at the center of the base portion 61 in the third direction, the variation in the pitch between the heat transfer pipes 50 in the third direction can be further suppressed. The heat exchanger 8 can make the distance between the heat transfer pipes 50 uniform, and therefore, can suppress the drift of air and suppress the increase in power of the outdoor fan 9.

The spacer 62 is formed by bending a part of the base 61 and extending in the first direction. Thus, the spacing portions 62 are not in line contact with the heat transfer member 40 but in surface contact therewith, and therefore the pitch between the heat transfer tubes 50 can be stably ensured. The spacer 62 abuts against the heat transfer pipe 50. In this way, the spacer portions 62 can stably ensure the pitch between the heat transfer tubes 50 by abutting against the heat transfer tubes 50 having high rigidity.

Conventionally, a heat exchanger has been disclosed in which comb-teeth-shaped auxiliary members extending in the direction of arrangement of refrigerant flow paths are provided between adjacent heat transfer tubes. However, in this conventional technique, since the auxiliary member separate from the heat transfer pipe is provided, the number of components increases. In addition, in the conventional technique, since a process of assembling the auxiliary member is required, the number of manufacturing processes increases. In contrast, in embodiment 1, the heat transfer pipe 50 and the extension portion 60 can be integrally molded. Therefore, the number of parts can be reduced, and the number of manufacturing processes can be reduced.

(first modification)

Fig. 6 is a plan view showing a state where the first header 20 of the heat exchanger 108 according to the first modification of embodiment 1 is removed. In the first modification example, as shown in fig. 6, a plurality of heat transfer pipes 50 are provided along the second direction. In the first modification, the case where 2 heat transfer pipes 50 are provided is exemplified, but 3 or more heat transfer pipes 50 may be provided. The base portions 61 of the extended portions 60 are provided on one end side (left side in the drawing) of one heat transfer pipe 50, on the other end side (right side in the drawing) of the other heat transfer pipe 50, and between the one heat transfer pipe 50 and the other heat transfer pipe 50. The number of the base portions 61 may be 1, 2, or 4 or more. In the first modification as well, the same effects as those of embodiment 1 are exhibited.

(second modification)

Fig. 7 is a plan view showing a state where the first header 20 of the heat exchanger 208 according to the second modification of embodiment 1 is removed. Fig. 7 shows adjacent 2 heat transfer members 40 among the plurality of heat transfer members 40 arranged. In the second modification, as shown in fig. 7, the spacer 262 abuts on the adjacent extension 60. In the second modification, the same effects as those of embodiment 1 are also obtained.

(third modification)

Fig. 8 is a plan view showing a state where the first header 20 of the heat exchanger 308 according to the third modification of embodiment 1 is removed. Fig. 8 shows adjacent 2 heat transfer members 40 among the plurality of heat transfer members 40 arranged. In the third modification, as shown in fig. 8, the spacer 362 is formed into an embossed shape (japanese: 12456125311250812473. Specifically, the base ends of the spacers 362 are connected to the heat transfer pipe 50, and the spacers 362 are bent perpendicularly to extend in the first direction and are bent perpendicularly to extend in the second direction. Then, the spacer 362 is vertically bent to extend in the direction opposite to the first direction, and is vertically bent to extend in the second direction. Thus, the spacer 362 has a projection 362a, and the projection 362a abuts against the adjacent extension 60. Thus, the tip of the protruding portion 362a, not the spacer 362, abuts against the extending portion 60, thereby increasing the rigidity of the spacer 362.

Embodiment mode 2

Fig. 9 is a plan view showing a state where the first header 20 of the heat exchanger 408 of embodiment 2 is removed. Fig. 9 shows adjacent 2 heat transfer members 40 among the plurality of heat transfer members 40 arranged. The heat exchanger 408 of embodiment 2 is different from embodiment 1 in the shape of the partition 462. In embodiment 2, the same reference numerals are given to the same portions as those in embodiment 1, and the description thereof is omitted, and the differences from embodiment 1 will be mainly described.

As shown in fig. 9, the spacer 462 is formed by bending a part of the base portion 61 and extending in the first direction. The partition 462 is formed in a planar shape in a plan view, unlike embodiment 1.

(production method)

Fig. 10 is a side view showing a method of manufacturing the heat exchanger 408 according to embodiment 2. Next, a method for manufacturing the spacer 462 will be described. As shown in fig. 10, the partition 462 is formed by forming a slit 63 in the third direction in the base portion 61. That is, the spacer 462 is formed by bending the base 61, in which the slit 63 is formed in the third direction, in the first direction. As a result, the spacer 462 is formed planar in a plan view as shown in fig. 9. In embodiment 2, the case where the spacer 462 is provided at both the upper end and the lower end of the base 61 is illustrated, but may be provided at either one of them or at another position.

According to embodiment 2, the spacer 462 is formed by bending the base portion 61, in which the slit 63 is formed in the third direction, in the first direction. Thus, when the heat exchanger 408 functions as an evaporator, the condensed water flowing down from the heat transfer pipe 50 can be received. Therefore, the condensed water can be prevented from being blocked from being discharged from the heat exchanger 408.

Embodiment 3

Fig. 11 is a side view showing a heat exchanger 508 of embodiment 3. The heat exchanger 508 of embodiment 3 is different from those of

embodiments

1 and 2 in the shape of the spacer 562. In embodiment 3, the same reference numerals are given to the same parts as those in

embodiments

1 and 2, and the description thereof is omitted, and the differences from

embodiments

1 and 2 will be mainly described.

As shown in fig. 11, the spacer 562 is formed by cutting a part of the base 61 and extending in the first direction. The spacer 562 is formed by forming a notch 63 in the second direction in the base 61. The spacer 562 is provided at an upper portion of the base 61 in the third direction, but may be provided at a lower portion or may be provided at a central portion.

Fig. 12 is a plan view showing a state where the first header 20 of the heat exchanger 508 of embodiment 3 is removed. Fig. 12 shows adjacent 2 heat transfer members 40 among the plurality of heat transfer members 40 arranged. As shown in fig. 12, the spacer 562 is provided at a position other than the edge portion of the base 61, and therefore, the spacer 562 is provided between the base 61 and the base 61 in a top view.

According to embodiment 3, the spacer 562 is formed by cutting out a part of the base 61 and extending in the first direction. Therefore, the area of the spacer 562 is reduced, and thus the base 61 can be left in a large amount. Therefore, the effective heat transfer area of the entire extension portion 60 can be maintained.

(first modification)

Fig. 13 is a side view showing a heat exchanger 608 according to a first modification of embodiment 3. In the first modification example, as shown in fig. 13, the spacer portions 662 are formed by making cuts 63 in the base portion 61 in the third direction, which is the direction in which the heat transfer tubes 50 extend. The spacer 662 is provided at an upper portion of the base 61 in the third direction, but may be provided at a lower portion or may be provided at a central portion.

Fig. 14 is a plan view showing a state where the first header 20 of the heat exchanger 608 of the first modification of embodiment 3 is removed. Fig. 14 shows adjacent 2 heat transfer members 40 among the plurality of heat transfer members 40 arranged. As shown in fig. 14, the spacer 662 is provided at a position other than the edge of the base 61, and therefore, the spacer 662 is provided between the base 61 and the base 61 in a top view.

According to the first modification, the spacing portion 662 is formed by cutting a part of the base portion 61 and extending in the first direction. Therefore, the area of the spacer 662 is reduced, and thus the base 61 can be left in a large amount. Therefore, as in embodiment 3, the effective heat transfer area of the entire extension portion 60 can be maintained. The spacer 662 is formed by bending the base 61, in which the slit 63 is formed in the third direction, in the first direction. This allows the condensed water flowing down from the heat transfer pipe 50 to be received. Therefore, the condensed water can be prevented from being blocked from being discharged from the heat exchanger 608.

(second modification)

Fig. 15 is a side view showing a heat exchanger 708 according to a second modification of embodiment 3. In the second modification, as shown in fig. 15, the partition 762 is formed in a burring shape in which a hole 64 is opened in the base 61 (japanese: 1259612512512522\12564. The partition 762 is provided at an upper portion of the base 61 in the third direction, but may be provided at a lower portion or may be provided at a central portion.

Fig. 16 is a plan view showing a state where the first header 20 of the heat exchanger 708 according to the second modification of embodiment 3 is removed. Fig. 16 shows adjacent 2 heat transfer members 40 among the plurality of heat transfer members 40 arranged. As shown in fig. 16, the spacer 762 is provided at a position other than the edge of the base 61, and therefore, the spacer 762 is provided between the base 61 and the base 61 in a top view.

According to the second modification, the spacer 762 is formed by cutting out a part of the base 61 and extending in the first direction. Therefore, the area for the spacer 762 is reduced, and thus the base 61 can be left in a large amount. Therefore, as in embodiment 3, the effective heat transfer area of the entire extension portion 60 can be maintained.

Embodiment 4

Fig. 17 is a plan view showing a state where the first header 20 of the heat exchanger 808 of embodiment 4 is removed. The shape of spacer 862 of heat exchanger 808 in embodiment 4 is different from that in embodiments 1 to 3. In embodiment 4, the same reference numerals are given to the same portions as those in embodiments 1 to 3, and the description thereof is omitted, and the differences from embodiments 1 to 3 will be mainly described.

Fig. 17 shows 1 heat transfer member 40 among the plurality of heat transfer members 40 arranged. As shown in fig. 17, the 2 spacers 862 are provided at positions point-symmetrical with respect to the center of the heat transfer pipe 50, and are formed by forming the cutouts 63 in the second direction in the base portion 61. That is, the spaced portions 862 on one end side of the heat transfer pipe 50 extend toward one adjacent heat transfer member 40, and the spaced portions 862 on the other end side of the heat transfer pipe 50 extend toward the other adjacent heat transfer member 40.

According to embodiment 4, the number of the spacers 862 is 2, and the spacers are provided at positions that are point-symmetrical with respect to the center of the heat transfer pipe 50. Therefore, in the assembly process of heat exchanger 808, the shape of spacer 862 is common even if the front and back of heat transfer tubes 50 are reversed when heat transfer tubes 50 are arranged. Therefore, when arranging the heat exchangers 808, it is not necessary to align the orientations of the plurality of heat transfer pipes 50. Therefore, the arrangement process of the heat transfer pipes 50 is simplified. The spacer 862 may be formed by bending a part of the base portion 61, or may be formed by cutting and folding a part of the base portion 61.

(modification example)

Fig. 18 is a plan view showing a state where the first header 20 of the heat exchanger 908 according to the modification of embodiment 4 is removed. Fig. 18 shows 1 heat transfer member 40 among the plurality of heat transfer members 40 arranged. In the modification, as shown in fig. 18, the 2 spacer portions 962 are provided at positions that are symmetrical with respect to the center of the heat exchanger tube 50, and are formed by forming the notches 63 in the base portion 61 in the third direction, which is the direction in which the heat exchanger tube 50 extends.

According to the modification, 2 spacers 962 are provided at positions that are symmetrical with respect to the center of the heat transfer pipe 50. Therefore, in the assembly process of the heat exchanger 908, the shape of the spacer 962 is common even if the heat transfer tubes 50 are reversed when the heat transfer tubes 50 are arranged. Therefore, when the heat exchangers 908 are arranged, it is not necessary to align the orientations of the plurality of heat transfer pipes 50. Therefore, the arrangement process of the heat transfer pipes 50 is simplified. The spacer 962 is formed by bending the base portion 61, in which the slit 63 is formed in the third direction, in the first direction. This allows the condensed water flowing down from the heat transfer pipe 50 to be received. Therefore, the condensed water can be prevented from being blocked from being discharged from the heat exchanger 908.

Embodiment 5

Fig. 19 is a front view showing a heat exchanger 1008 of embodiment 5. The heat exchanger 1008 of embodiment 5 differs from embodiments 1 to 4 in that the partition 1062 abuts against the first header 20 and the second header 30. In embodiment 5, the same reference numerals are given to the portions common to embodiments 1 to 4, and the description thereof is omitted, and the differences from embodiments 1 to 4 will be mainly described.

As shown in fig. 19, the partition 1062 abuts the first header 20 and the second header 30, and is formed by forming a notch 63 in the second direction in the base 61. Specifically, the partition 1062 provided at the upper end of the base 61 abuts on the first header pipe 20, and the partition 1062 provided at the lower end of the base 61 abuts on the second header pipe 30. In embodiment 5, the case where the partition 1062 abuts on the first header pipe 20 and the second header pipe 30 is illustrated, but the partition 1062 may contact either one of the first header pipe 20 and the second header pipe 30.

According to embodiment 5, the partition 1062 abuts against the first header 20 or the second header 30. The length by which both end portions of the heat transfer pipe 50 protrude from the spacer portions 1062 is the length of the insertion amount S of the heat transfer pipe 50 in the third direction. That is, the spacer 1062 has a guide function of confirming the length of the insertion amount S in the third direction when the heat exchanger tubes 50 are inserted into the first header 20 or the second header 30. Further, since the partition 1062 is disposed at the upper end and the lower end of the base portion 61, it is possible to prevent the air flow from being obstructed.

(modification example)

Fig. 20 is a front view showing a heat exchanger 1108 according to a modification of embodiment 5. In the modification, as shown in fig. 20, the partition 1162 abuts against the first header 20 and the second header 30. The spacer 1162 is formed by forming a notch 63 in the base portion 61 in the third direction, which is the direction in which the heat transfer tube 50 extends, and bending the portion of the base portion 61 corresponding to the notch 63 in the first direction.

According to a modification, the spacer 1162 abuts the first header 20 or the second header 30. The length by which both end portions of the heat transfer pipe 50 protrude from the spacer 1162 is the length of the insertion amount S of the heat transfer pipe 50 in the third direction. That is, the spacer 1162 has a guiding function of confirming the length of the insertion amount S in the third direction when the heat transfer tubes 50 are inserted into the first header 20 or the second header 30. Further, since the spacer 1162 is disposed at the upper end and the lower end of the base portion 61, it is possible to suppress the air flow from being obstructed. The spacer 1162 is formed by bending the base 61, in which the cut 63 is formed in the third direction, in the first direction. This allows the condensed water flowing down from the heat transfer pipe 50 to be received. Therefore, the condensed water can be prevented from being blocked from being discharged from the heat exchanger 1108.

Embodiment 6

Fig. 21 is a front view showing a heat exchanger 1208 of embodiment 6. The heat exchanger 1208 of embodiment 6 is different from those of embodiments 1 to 5 in that a plurality of the spacers 1262 are provided along the third direction. In embodiment 6, the same reference numerals are given to the same portions as those in embodiments 1 to 5, and the description thereof is omitted, and the differences from embodiments 1 to 5 will be mainly described.

As shown in fig. 21, the plurality of spacers 1262 are provided and are arranged at equal intervals along the direction in which the heat transfer pipe 50 extends, that is, the third direction. The spacer portions 1262 are formed by making cuts 63 in the third direction, which is the direction in which the heat transfer tube 50 extends, in the base portion 61.

According to embodiment 6, since the partition portions 1262 that slightly obstruct the flow of air are arranged at equal intervals along the third direction, the pressure loss can be made uniform over the entire third direction. Therefore, the drift of the air can be suppressed in the entire third direction. Therefore, an increase in the power of the outdoor blower 9 can be suppressed.

(modification example)

Fig. 22 is a front view showing a heat exchanger 1308 according to a modification of embodiment 6. In the modification, as shown in fig. 22, the spacer portions 1362 are provided in plural numbers, and the number on the leeward side of the heat transfer tubes 50 is larger than the number on the windward side of the heat transfer tubes 50. The spacer 1362 is formed by forming a notch 63 in the base 61 in the third direction, which is the direction in which the heat transfer tube 50 extends. In the modification, a case where 2 spacer portions 1362 are provided on the windward side of the heat transfer pipe 50 and 4 spacer portions 1362 are provided on the leeward side of the heat transfer pipe 50 is illustrated, but the number of spacer portions 1362 may be changed as appropriate. Note that the interval portions 1362 on the windward side of the heat transfer pipe 50 may be omitted.

According to the modification, the spacers 1362 are provided in plural numbers, and the number on the leeward side of the heat transfer tubes 50 is larger than the number on the windward side of the heat transfer tubes 50. When the heat exchanger 1308 functions as an evaporator, the leeward side has a higher possibility of frost formation than the leeward side of the heat transfer tubes 50. In the modification, since the number of the spacer portions 1362 is larger on the leeward side of the heat transfer tubes 50 than on the windward side of the heat transfer tubes 50, the total amount of the frost stacked on the spacer portions 1362 can be reduced.

Description of the reference symbols

1: a refrigeration cycle device; 2: an outdoor unit; 3: an indoor unit; 4: a refrigerant circuit; 5: a refrigerant pipe; 6: a compressor; 7: a flow path switching device; 8: a heat exchanger; 9: an outdoor blower; 10: an expansion part; 11: an indoor heat exchanger; 12: an indoor blower; 20: a first header; 30: a second header; 40: a heat transfer member; 50: a heat transfer tube; 51: a flow path; 60: an extension portion; 61: a base; 62: a spacer section; 63: cutting; 64: an aperture; 108: a heat exchanger; 208: a heat exchanger; 262: a spacer section; 308: a heat exchanger; 362: a spacer section; 362a: a protrusion; 408: a heat exchanger; 462: a spacer section; 508: a heat exchanger; 562: a spacer section; 608: a heat exchanger; 662: a spacer section; 708: a heat exchanger; 762: a spacer section; 808: a heat exchanger; 862: a spacer section; 908: a heat exchanger; 962: a spacer section; 1008: a heat exchanger; 1062: a spacer section; 1108: a heat exchanger; 1162: a spacer section; 1208: a heat exchanger; 1262: a spacer section; 1308: a heat exchanger; 1362: a spacer portion.

Claims

1. A heat exchanger is provided with:

a first header collecting and distributing refrigerant and extending in a first direction;

a second header provided at a position opposed to the first header, collecting and distributing refrigerant, and extending in the first direction; and

a plurality of heat transfer members extending from the first header toward the second header and disposed at intervals along the first direction,

the heat transfer member has:

a plurality of heat transfer tubes extending from the first header toward the second header, inside which refrigerant flows; and

an extension portion provided to the heat transfer pipe to promote heat transfer performance of the heat transfer pipe,

the extension has:

a base portion extending from the heat transfer pipe in a second direction, which is a flow direction of air flowing between the plurality of heat transfer pipes; and

and a spacer portion extending in the first direction from the base portion and abutting against the adjacent heat transfer member.

2. The heat exchanger of claim 1,

the spacer is formed by bending a part of the base and extending in the first direction.

3. The heat exchanger of claim 2,

the spacer is formed by cutting the base in the second direction.

4. The heat exchanger according to claim 2 or 3,

the spacer portion is formed by cutting the base portion in a third direction, which is a direction in which the heat transfer tube extends.

5. The heat exchanger according to any one of claims 1 to 4,

the partition portion is formed by cutting a part of the base portion and extending in the first direction.

6. The heat exchanger of claim 5,

the spacer is formed by cutting the base in the second direction.

7. The heat exchanger according to claim 5 or 6,

the spacer portion is formed by cutting the base portion in a third direction, which is a direction in which the heat transfer pipe extends.

8. The heat exchanger according to any one of claims 5 to 7,

the partition is formed in a burring shape in which a hole is opened in the base.

9. The heat exchanger according to any one of claims 1 to 8,

the spacing part is provided with a plurality of spacing parts,

the spacer portions are provided at positions that are point-symmetrical with respect to the center of the heat transfer pipe.

10. The heat exchanger according to any one of claims 1 to 9,

the spacer portion abuts against the heat transfer pipe.

11. The heat exchanger according to any one of claims 1 to 10,

the spacer abuts the extension.

12. The heat exchanger according to any one of claims 1 to 11,

the spacer abuts the first header or the second header.

13. The heat exchanger according to any one of claims 1 to 12,

the spacing part is provided with a plurality of spacing parts,

the spacers are arranged at equal intervals along a third direction, which is a direction in which the heat transfer pipe extends.

14. The heat exchanger according to any one of claims 1 to 13,

the spacing part is provided with a plurality of spacing parts,

the number of the spacer portions is larger on the leeward side of the heat transfer pipe than on the windward side of the heat transfer pipe.

15. The heat exchanger according to any one of claims 1 to 14,

the partition portion is formed in an embossed shape extending in the first direction and then folded back.

16. The heat exchanger according to any one of claims 1 to 15,

the heat transfer pipe is provided in plurality along the second direction.

17. A refrigeration cycle apparatus, wherein,

the heat exchanger of any one of claims 1 to 16 functioning as a condenser or an evaporator.