WO2022180823A1

WO2022180823A1 - Heat exchanger and refrigeration cycle device

Info

Publication number: WO2022180823A1
Application number: PCT/JP2021/007502
Authority: WO
Inventors: 暁八柳; 剛志前田; 伸中村
Original assignee: 三菱電機株式会社
Priority date: 2021-02-26
Filing date: 2021-02-26
Publication date: 2022-09-01
Also published as: EP4300023A4; JPWO2022180823A1; TWI809718B; EP4300023A1; US20240060722A1; TW202234010A

Abstract

This heat exchanger (100) comprises: a first header (11) and a second header (12); and a plurality of heat transfer members (1) each having one end in a second direction (Z) connected to the first header and the other end in the second direction connected to the second header. Each of the heat transfer members is provided so as to exchange heat between a first heat exchange medium that flows in an internal space in the second direction and a second heat exchange medium that flows in an external space of the heat transfer member in a third direction (Y). The heat exchanger further comprises a plurality of heat transfer promotion members (2) that are each, in the external space, disposed at a middle portion between two of the plurality of heat transfer members adjacent to each other in a first direction (X) and that extend in the third direction (Y).

Description

Heat exchanger and refrigeration cycle equipment

The present disclosure relates to heat exchangers and refrigeration cycle devices.

Japanese Patent Laying-Open No. 2018-155481 (Patent Document 1) describes a heat exchanger including a plurality of heat transfer tube units each having a plurality of fins and a plurality of heat transfer tubes. The plurality of heat transfer tube units are arranged at intervals in the heat transfer tube unit arrangement direction. In each heat transfer tube unit, the plurality of heat transfer tubes extends in the heat transfer tube extension direction perpendicular to the heat transfer tube unit arrangement direction, and the plurality of fins and the plurality of heat transfer tubes extend in the heat transfer tube unit arrangement direction and the heat transfer tube extension direction. They are arranged alternately in the vertical heat transfer tube separation direction. In each heat transfer tube unit, the plurality of fins have portions that are inclined with respect to the heat transfer tube separation direction. Each heat transfer unit is connected to the first header and the second header.

JP 2018-155481 A

In the heat exchanger described in Patent Document 1, in order to improve the heat transfer performance of each heat transfer tube unit, it is necessary to set the pitch in the arrangement direction of each heat transfer tube unit relatively narrow.

This is because when the pitch in the arrangement direction of each heat transfer tube unit becomes wider, the air flowing between the adjacent heat transfer tube units tends to concentrate in the central portion between the adjacent heat transfer tube units in the arrangement direction of each heat transfer tube unit. be.

However, when the pitch in the arrangement direction of the heat transfer tube units is set narrow, the pitch of the plurality of insertion holes for inserting the heat transfer tubes in each of the first header and the second header also needs to be set narrow. be. The moldability of the first header and the second header deteriorates as the pitch of the plurality of insertion holes becomes narrower.

Therefore, in the heat exchanger described in Patent Document 1, it is difficult to improve the heat transfer performance without reducing the formability of the first header and the second header.

A main object of the present invention is to provide a heat exchanger capable of improving heat transfer performance without reducing the formability of the first header and the second header, and a refrigeration cycle apparatus equipped with this heat exchanger. .

A heat exchanger according to the present disclosure includes first and second headers extending along a first direction and spaced apart in a second direction orthogonal to the first direction; a plurality of heat transfer members spaced apart from each other and having one end in the second direction connected to the first header and the other end in the second direction connected to the second header; Prepare. Each of the first header, the second header, and the plurality of heat transfer members partitions an inner space through which the first heat exchange medium flows and an outer space through which the second heat exchange medium flows. The internal space of the first header communicates with the internal space of the second header via the internal spaces of each of the plurality of heat transfer members. The internal spaces of each of the first header and the second header are in communication via the internal spaces of each of the plurality of heat transfer members. The heat exchanger is disposed in the outer space in a central portion between two heat transfer members adjacent in the first direction among the plurality of heat transfer members, and has at least one heat transfer member extending along the third direction. Further comprising a heat facilitating member and at least one positioning member positioning the at least one heat transfer facilitating member relative to the first header, the second header and the plurality of heat transfer members in the exterior space. At least one positioning member is arranged only downstream of the internal space of each of the plurality of heat transfer members in the third direction in which the second heat exchange medium flows.

According to the present invention, it is possible to provide a heat exchanger capable of improving heat transfer performance without degrading the formability of the first header and the second header, and a refrigeration cycle apparatus equipped with this heat exchanger.

1 is a perspective view showing a heat exchanger according to Embodiment 1; FIG. 2 is a cross-sectional view as seen from arrow II-II in FIG. 1; FIG. FIG. 2 is a cross-sectional view as seen from arrows III-III in FIG. 1; 2 is a partial front view of the heat exchanger shown in FIG. 1; FIG. FIG. 5 is a partial cross-sectional view showing a first modification of a plurality of heat transfer members of the heat exchanger according to Embodiment 1; FIG. 7 is a partial cross-sectional view showing a second modification of a plurality of heat transfer members of the heat exchanger according to Embodiment 1; FIG. 10 is a partial cross-sectional view showing a third modification of a plurality of heat transfer members of the heat exchanger according to Embodiment 1; FIG. 8 is a perspective view showing a heat exchanger according to Embodiment 2; 9 is a cross-sectional view as seen from arrow IX-IX in FIG. 8; FIG. FIG. 9 is a cross-sectional view seen from arrow X-X in FIG. 8; FIG. 11 is a partial cross-sectional view as seen from arrows XI-XI in FIGS. 9 and 10; FIG. 11 is a partial cross-sectional view showing a heat transfer promoting member of a heat exchanger according to Embodiment 3; FIG. 11 is a partial cross-sectional view showing a third modification of the heat transfer promoting member of the heat exchanger according to Embodiment 3; FIG. 12 is a partial cross-sectional view showing a fourth modification of the heat transfer promoting member of the heat exchanger according to Embodiment 3; FIG. 12 is a partial cross-sectional view showing a fifth modification of the heat transfer promoting member of the heat exchanger according to Embodiment 3; FIG. 12 is a partial cross-sectional view showing a sixth modification of the heat transfer promoting member of the heat exchanger according to Embodiment 3; FIG. 11 is a partial cross-sectional view showing a heat exchanger according to Embodiment 4; The ratio ΔP1/ΔP2 between the pressure loss ΔP1 of the air flowing through the air passage shown in FIG. 4 is a graph showing that the dimensional ratio of each heat transfer enhancing member varies with that of the heat transfer enhancing members. 19 is a graph derived from the graph shown in FIG. 18, and is a graph showing the dimensional ratio of each heat transfer member and each heat transfer enhancement member that can make the pressure loss ratio ΔP1/ΔP2 equal to or less than 100%. FIG. FIG. 10 is a diagram showing a refrigeration cycle apparatus according to Embodiment 5;

Embodiments of the present disclosure will be described below with reference to the drawings. In the drawings below, the same or corresponding parts are denoted by the same reference numerals, and the description thereof will not be repeated. For convenience of explanation, each drawing shows a first direction X, a second direction Z, and a third direction Y that are orthogonal to each other.

Embodiment 1.
<Configuration of heat exchanger 100>
As shown in FIGS. 1 to 4, a heat exchanger 100 according to Embodiment 1 includes a first header 11, a second header 12, a plurality of heat transfer members 1, a plurality of heat transfer promoting members 2, a plurality of A positioning member 3 , a first reinforcing member 13 and a second reinforcing member 14 are provided.

The heat exchanger 100 is provided so that a first heat exchange medium (eg, refrigerant) flowing in the second direction Z exchanges heat with a second heat exchange medium (eg, air) flowing in the third direction Y. The second direction Z is along the vertical direction, for example. The first direction X and the third direction Y are, for example, along the horizontal direction. The first header 11 and the second header 12 are so-called distributors. The multiple heat transfer members 1 are so-called heat transfer tubes. The plurality of heat transfer promoting members 2 are not so-called heat transfer tubes.

Each of the first header 11, the second header 12, and the plurality of heat transfer members 1 partitions an internal space through which the refrigerant can flow and an external space through which air can flow. The internal space of each of the first header 11 and the second header 12 communicates via the internal space of each of the plurality of heat transfer members 1 . In other words, the internal spaces of the plurality of heat transfer members 1 are connected in parallel to the internal spaces of the first header 11 and the second header 12 . For example, the coolant that has flowed into the internal space of the first header 11 from the first inflow/outlet portion 15 is distributed to the internal spaces of the plurality of heat transfer members 1 . The refrigerant flowing in the second direction through the internal spaces of the multiple heat transfer members 1 exchanges heat with the air flowing in the third direction Y through the external spaces of the multiple heat transfer members 1 . The refrigerant that has flowed through the internal space of each of the plurality of heat transfer members 1 flows out into the internal space of the second header 12 and merges therewith.

A space outside each of the first header 11, the second header 12, and the plurality of heat transfer members 1 and surrounded by the first header 11, the second header 12, the first reinforcing member 13, and the second reinforcing member 14 The external space is provided so that air can flow in the third direction Y. As shown in FIG. Hereinafter, the upstream side of the air flowing in the third direction Y will simply be referred to as the third direction Y upstream side, and the downstream side of the air flowing in the third direction Y will simply be referred to as the third direction Y downstream side. The external space is open on the upstream side and the downstream side in the third direction Y, respectively.

As shown in FIG. 1, each of the first header 11 and the second header 12 extends along the first direction X and is spaced apart from each other in the second direction Z. As shown in FIG. The first header 11 has a first inflow/outflow portion 15 for inflow or outflow of the coolant. The second header 12 has a second inlet/outlet portion 16 through which the coolant flows.

As shown in FIG. 1, the plurality of heat transfer members 1 are arranged in the first direction X at intervals. Each of the plurality of heat transfer members 1 has one end in the second direction Z connected to the first header 11 and the other end in the second direction Z connected to the second header 12 .

Specifically, the first header 11 is formed with a plurality of insertion holes spaced apart from each other in the first direction X. One end of each of the plurality of heat transfer members 1 in the first direction X is inserted into each of the plurality of insertion holes formed in the first header 11 . Similarly, the second header 12 is formed with a plurality of insertion holes spaced apart from each other in the first direction X. As shown in FIG. The other end of each of the multiple heat transfer members 1 in the first direction X is inserted into each of multiple insertion holes formed in the second header 12 .

The plurality of heat transfer promoting members 2 are such that the air flowing between two heat transfer members 1 adjacent in the first direction X flows intensively in the center portion in the first direction X between the two heat transfer members 1. It is intended to suppress As shown in FIGS. 1 to 4, each of the plurality of heat transfer enhancing members 2 is located between two heat transfer members 1 adjacent in the first direction X among the plurality of heat transfer members 1 in the external space. is placed in the center of Each of the plurality of heat transfer promoting members 2 includes, for example, a center line C1 extending along the third direction Y and passing through the center in the first direction X between two heat transfer members 1 adjacent in the first direction X; They are arranged so as to overlap in two directions Z. A centerline extending along the third direction Y through the center of the first direction X of each of the plurality of heat transfer promoting members 2 is arranged so as to overlap the centerline C1 in the second direction Z, for example. Each of the plurality of heat transfer promoting members 2 extends along the third direction Y. As shown in FIG. Each of the plurality of heat transfer promoting members 2 divides the external space in the first direction X. As shown in FIG.

Each of the plurality of heat transfer promoting members 2 is separated from each of the plurality of heat transfer members 1 . The plurality of heat transfer enhancing members 2 are not in contact with each of the plurality of heat transfer members 1 . The plurality of heat transfer promoting members 2 are separated from each of the first header 11 and the second header 12 . The plurality of heat transfer promoting members 2 are not in contact with each of first header 11 and second header 12 . A surface facing the first direction X of each of the plurality of heat transfer promoting members 2 is, for example, a flat surface. The surface facing the first direction X of each of the plurality of heat transfer promoting members 2 is parallel to the surface facing the first direction X of each of the plurality of heat transfer members 1, for example. Each of the plurality of heat transfer promoting members 2 does not have a through hole extending from one surface facing the first direction X to the other surface, for example. Each of the plurality of heat transfer promoting members 2 is not connected to fins (not shown).

In the external space, the plurality of positioning members 3 are configured such that each of the plurality of heat transfer promoting members 2 is provided with a first header 11, a second header 12, a first reinforcing member 13, a second reinforcing member 14, and a plurality of heat transfer members. It is for positioning with respect to the member 1 . Each of the plurality of positioning members 3 is connected to each of the plurality of heat transfer enhancing members 2 , the first reinforcing member 13 and the second reinforcing member 14 . Each of the plurality of positioning members 3 is separated from the plurality of heat transfer members 1 . Each of the multiple positioning members 3 is not in contact with the multiple heat transfer members 1 . Each of the plurality of positioning members 3 is not connected to fins (not shown).

Each of the plurality of positioning members 3 includes a beam portion 3A spanning between a first reinforcing member 13 and a second reinforcing member 14 and connected to the plurality of heat transfer promoting members 2, and a first reinforcing member 13 and a connecting portion 3C connected to the second reinforcing member 14 .

Each of the plurality of positioning members 3 are spaced apart from each other in the second direction Z. Each of the plurality of positioning members 3 is arranged, for example, closer to the first header 11 side or the second header 12 side than the center in the second direction Z between the first header 11 and the second header 12 .

The material forming each of the plurality of heat transfer promoting members 2 and the plurality of positioning members 3 is not particularly limited. The thermal conductivity of the material forming each of the plurality of heat transfer promoting members 2 and the plurality of positioning members 3 may be lower than the thermal conductivity of the material forming the plurality of heat transfer members 1 .

The first reinforcing member 13 and the second reinforcing member 14 are for supplementing the strength of the structure of the first header 11, the second header 12, and the plurality of heat transfer members 1 assembled as described above. . The first reinforcing member 13 and the second reinforcing member 14 are spaced apart from each other in the first direction X in the external space. The first reinforcing member 13 and the second reinforcing member 14 are arranged so as to sandwich the plurality of heat transfer members 1 and the plurality of heat transfer promoting members 2 in the first direction X. As shown in FIG. First reinforcing member 13 and second reinforcing member 14 are connected to outer surfaces of first header 11 and second header 12, respectively. The first reinforcing member 13 is connected to one end face in the first direction X of each of the first header 11 and the second header 12 . The second reinforcing member 14 is connected to the other end surfaces in the first direction X of each of the first header 11 and the second header 12 .

Each of the plurality of heat transfer members 1 has, for example, the same configuration as each other. Each of the plurality of heat transfer enhancing members 2 has, for example, the same configuration as each other. Each of the plurality of positioning members 3 has, for example, the same configuration as each other. The numbers of each of the plurality of heat transfer members 1, the plurality of heat transfer promoting members 2, and the plurality of positioning members 3 are not particularly limited. The number of heat transfer enhancing members 2 is one less than the number of heat transfer members 1, for example. The number of positioning members 3 is two, for example.

Next, an example of the positional relationship in the third direction Y of each of the plurality of heat transfer members 1, the plurality of heat transfer promoting members 2, and the plurality of positioning members 3 of the heat exchanger 100 will be described.

2 and 3, each of the plurality of heat transfer members 1 has a first end portion 1A positioned upstream in the third direction Y and a second end portion 1A positioned downstream in the third direction Y. and end 1B. Each first end 1A is arranged downstream of the upstream end of each of the first reinforcing member 13 and the second reinforcing member 14 . Each second end portion 1B is arranged upstream of the downstream end portion of each of the first reinforcing member 13 and the second reinforcing member 14 .

As shown in FIGS. 2 and 3 , each of the plurality of heat transfer promoting members 2 has a third end portion 2A located upstream in the third direction Y and a third end portion 2A located downstream in the third direction Y. It has four ends 2B. Each third end 2A is arranged downstream of each first end 1A. Each fourth end 2B is arranged downstream of each second end 1B.

As shown in FIGS. 1 and 2, the beam portion 3A of each of the plurality of positioning members 3 is positioned downstream in the third direction Y from the interior space of each of the plurality of heat transfer members 1 in the outer space. are placed only in In other words, the beam portion 3A of each of the plurality of positioning members 3 is arranged only downstream in the third direction Y from the second end portion 1B of each of the plurality of heat transfer members 1 . For example, the

connection portions

3B and 3C of each of the plurality of positioning members 3 are also arranged only on the downstream side in the third direction Y from the interior space of each of the plurality of heat transfer members 1 in the outer space.

Below, an example of the size relationship of each of the plurality of heat transfer members 1, the plurality of heat transfer promoting members 2, and the plurality of positioning members 3 of the heat exchanger 100 will be described.

As shown in FIGS. 2 and 3, in a cross section orthogonal to the second direction, the width of each of the plurality of heat transfer members 1 in the third direction Y is the width of each of the plurality of heat transfer members 1 in the first direction X wider than the width of Each of the plurality of heat transfer members 1 has a longitudinal direction along the third direction Y and a lateral direction along the first direction X in a cross section orthogonal to the second direction. Each of the plurality of heat transfer members 1 is, for example, a flat tube.

As shown in FIGS. 2 and 3, each of the plurality of heat transfer promoting members 2 is arranged in the center between two heat transfer members 1 adjacent to each other in the first direction X. As shown in FIGS. The width of the plurality of heat transfer promoting members 2 in the first direction X is narrower than the interval in the first direction X between two heat transfer members 1 adjacent to each other in the first direction X. In a cross section perpendicular to the second direction Z, the width of each of the plurality of heat transfer promoting members 2 in the third direction Y is wider than the width of each of the plurality of heat transfer promoting members 2 in the first direction X. Each of the plurality of heat transfer promoting members 2 has a longitudinal direction along the third direction Y and a lateral direction along the first direction X in a cross section perpendicular to the second direction.

As shown in FIGS. 2 and 3, the distance in the first direction X between two heat transfer members 1 adjacent in the first direction X is equal to the distance between the heat transfer member 1 and the heat transfer promoting member adjacent in the first direction X. 2 in the first direction X.

As shown in FIGS. 2 and 3, the width in the first direction X of each of the plurality of heat transfer enhancing members 2 is narrower than the width in the first direction X of each of the plurality of heat transfer members 1 . The width in the first direction X of each of the plurality of heat transfer promoting members 2 is constant regardless of the position in the third direction Y, for example. The distance in the first direction X between the heat transfer member 1 and the heat transfer promoting member 2 adjacent in the first direction X is, for example, the distance in the first direction X between two heat transfer members 1 adjacent in the first direction X. less than half the interval.

The length in the second direction Z of each of the heat transfer promoting members 2 is shorter than the interval in the second direction Z between the first header 11 and the second header 12 .

As shown in FIG. 1 , the width in the second direction Z of each beam portion 3A of the plurality of positioning members 3 is narrower than the width in the second direction Z of the plurality of heat transfer promoting members 2 . As shown in FIG. 4 , the width in the second direction Z of each beam portion 3A of the plurality of positioning members 3 is wider than the width in the first direction X of each of the plurality of heat transfer promoting members 2, and the plurality of It is narrower than the width in the first direction X of each heat transfer member 1 .

As shown in FIGS. 2 and 4, the width of each of the plurality of positioning members 3 in the first direction X is equal to or greater than the distance in the first direction X between the first reinforcing member 13 and the second reinforcing member 14, for example. is.

<Effect of heat exchanger 100>
Next, the effect of the heat exchanger 100 will be described based on comparison with a comparative example.

The heat exchanger according to Comparative Example 1 differs from the heat exchanger 100 only in that it does not include the heat transfer promoting member 2 . In the heat exchanger according to Comparative Example 1, the distance between two adjacent heat transfer members 1 in the first direction X is equal to that of the heat exchanger 100 .

The heat exchanger according to Comparative Example 2 does not include the heat transfer promoting member 2, and the distance between two adjacent heat transfer members in the first direction X is half that of the heat exchanger 100. , is different from the heat exchanger 100 . In the heat exchanger according to Comparative Example 2, the distance in the first direction X between two adjacent heat transfer members 1 is the distance in the first direction X between the heat transfer member 1 and the heat transfer promoting member 2 of the heat exchanger 100. and approximately equal.

The heat exchanger 100 is arranged in the outer space at the center between two heat transfer members 1 adjacent in the first direction X among the plurality of heat transfer members 1, and along the third direction Y It has a plurality of heat transfer enhancing members 2 that extend. As a result, each heat transfer promoting member 2 is such that the air flowing between two heat transfer members 1 adjacent in the first direction X concentrates on the central portion in the first direction X between the two heat transfer members 1. suppress flow. Therefore, the air flowing between two adjacent heat transfer members 1 easily follows the surfaces of the heat transfer members 1 . As a result, the extra-tube heat transfer coefficient of the heat exchanger 100 was such that the distance between two adjacent heat transfer members 1 in the first direction X was equal to that of the heat exchanger 100, but the heat transfer promoting member 2 was not provided in Comparative Example 1. Higher than the outside heat transfer coefficient of the heat exchanger according to It should be noted that the extra-tube heat transfer coefficient of the heat exchanger 100 is substantially the same as the extra-tube heat transfer coefficient of the heat exchanger according to the second comparative example.

On the other hand, in the heat exchanger according to Comparative Example 2, the intervals in the first direction X of the plurality of insertion holes for inserting the heat transfer members in each of the first header and the second header are equal to the distances between the heat transfer members. should be set as narrow as the interval in the first direction X of . As a result, the formability of the first header and the second header in the heat exchanger according to Comparative Example 2 is lower than the formability of the first header and the second header in the heat exchanger according to Comparative Example 1. .

On the other hand, in the heat exchanger 100, the intervals in the first direction X of the plurality of insertion holes for inserting the heat transfer members 1 in each of the first header 11 and the second header 12 are It is wider than the heat exchanger, and can be set as wide as the heat exchanger according to Comparative Example 1.

As a result, the heat exchanger 100 can improve the heat transfer performance without lowering the formability of the first header 11 and the second header 12 compared to the heat exchanger of Comparative Example 1. The heat exchanger 100 can improve the moldability of the first header 11 and the second header 12 without deteriorating the heat transfer performance, as compared with the heat exchanger of Comparative Example 2.

Also, the weight of each of the plurality of heat transfer enhancing members 2 can be made lighter than the weight of each of the plurality of heat transfer members 1 . Therefore, the heat exchanger 100 can be lighter than the heat exchanger according to the second comparative example. Moreover, the manufacturing cost of each of the plurality of heat transfer enhancing members 2 can be lower than the manufacturing cost of each of the plurality of heat transfer members 1 . Therefore, the manufacturing cost of the heat exchanger 100 can be reduced compared to the manufacturing cost of the heat exchanger according to the second comparative example.

In the heat exchanger 100 , each of the plurality of positioning members 3 is arranged only on the downstream side in the third direction Y from the internal space of each of the plurality of heat transfer members 1 . In this way, when the heat exchanger 100 acts as a condenser in a low-temperature environment, such as when the refrigeration cycle apparatus including the heat exchanger 100 is in defrosting operation, each positioning member 3 is It is difficult to obstruct the drainage of frost-melting water that is concentratedly generated on the upstream side in the three directions Y.

In the heat exchanger 100 , each of the plurality of positioning members 3 is connected to each of the first reinforcing member 13 and the second reinforcing member 14 . As a result, in the heat exchanger 100, the position of each of the plurality of heat transfer enhancing members 2 relative to the plurality of heat transfer members 1 is less likely to fluctuate. An increase in pressure loss (decrease in ventilation) is suppressed.

Further, when the plurality of positioning members 3 are connected to each of the plurality of heat transfer members 1 and the thermal conductivity of the material forming each of the plurality of positioning members 3 is relatively low, each heat transfer member Since the thermal resistance of the heat path from the member 1 to the plurality of heat transfer promoting members 2 via the plurality of positioning members 3 increases, the heat transfer loss (heat loss) in the heat path increases. On the other hand, in the heat exchanger 100, since each of the plurality of positioning members 3 is separated from the plurality of heat transfer members 1, the above heat paths are not formed, and heat transfer loss is suppressed. .

Further, when the heat exchanger 100 acts as an evaporator in a low-temperature environment, the water vapor in the air flowing between the two adjacent heat transfer members 1 is cooled by each heat transfer member 1 and becomes frost to transfer heat. It adheres to the member 1. Since the temperature of the gas flowing on the surface of each heat transfer member 1 gradually decreases from the first end 1A to the second end 1B of each heat transfer member 1, the temperature of the surface of each heat transfer member 1 The amount of frost formed shows a distribution in which the amount is highest on the first end portion 1A side and gradually decreases toward the second end portion 1B. As a result, if each of the plurality of heat transfer promoting members 2 is arranged so as to overlap the first end portion 1A when viewed from the first direction X, the distance between the heat transfer member 1 and the heat transfer promoting member 2 is reduced. are more likely to be blocked by frost. On the other hand, in the heat exchanger 100, the third end 2A of each of the plurality of heat transfer promoting members 2 is downstream of the first end 1A of each of the plurality of heat transfer members 1 in the third direction Y. , compared to the case where each of the plurality of heat transfer promoting members 2 is arranged so as to overlap the first end 1A when viewed from the first direction X, the heat transfer member 1 and the heat transfer promoting The space between the members 2 is hard to be blocked by frost.

<Modified example of heat exchanger 100>
The following modifications are allowed for each of the heat transfer members 1 of the heat exchanger 100 .

As shown in FIG. 5, each of the multiple heat transfer members 1 may include a heat transfer tube portion 1C, a fin portion 1D, and a fin portion 1E. The heat transfer tube portion 1</b>C is provided with the internal space described above, and has a configuration similar to that of the plurality of heat transfer members 1 of the heat exchanger 100 . The heat transfer tube portion 1C, the fin portion 1D and the fin portion 1E are integrally molded, for example.

In each of the plurality of heat transfer members 1, the fin portion 1D extends upstream in the third direction Y from the heat transfer tube portion 1C. The end portion of the fin portion 1D located on the upstream side in the third direction Y forms the first end portion 1A of the heat transfer member 1. As shown in FIG. The fin portion 1E extends downstream in the third direction Y from the heat transfer tube portion 1C. The end portion of the fin portion 1E located on the downstream side in the third direction Y forms the second end portion 1B of the heat transfer member 1. As shown in FIG. A space through which the coolant flows is not formed in the fin portion 1D and the fin portion 1E.

As shown in FIG. 6, each of the plurality of heat transfer members 1 may be composed of a plurality of heat transfer tubes 1G arranged side by side in the third direction Y at intervals. Each of the plurality of heat transfer tubes 1G is, for example, a circular tube. In this case, the first end portion 1A of each of the plurality of heat transfer members 1 is the end portion located on the upstream side of one of the plurality of heat transfer tubes 1G arranged on the most upstream side of the heat transfer tube 1G. . The second end portion 1B of each of the plurality of heat transfer members 1 is an end portion located downstream of one of the plurality of heat transfer tubes 1G arranged on the most downstream side of the heat transfer tube 1G.

As shown in FIG. 7, each of the plurality of heat transfer members 1 may be composed of a plurality of heat transfer tubes 1G, fins 1D, fins 1E, and fins 1H. The plurality of heat transfer tubes 1G are arranged side by side in the third direction Y at intervals. The fin portion 1D extends upstream in the third direction Y from the heat transfer tube 1G arranged on the most upstream side among the plurality of heat transfer tubes 1G. The fin portion 1E extends downstream in the third direction Y from the most downstream heat transfer tube 1G among the plurality of heat transfer tubes 1G. The fin portion 1H connects the heat transfer tubes 1G.

Embodiment 2.
The heat exchanger 101 according to the second embodiment has basically the same configuration as the heat exchanger 100 according to the first embodiment, and has the same effect. It differs from the heat exchanger 100 in that it is connected to each of the heat members 1 . Differences from the heat exchanger 100 are mainly described below.

As shown in FIGS. 8 to 11, each of the heat transfer members 1 of the heat exchanger 101 has the same configuration as the heat transfer member 1 of the first modified example. Each of the plurality of heat transfer members 1 includes a heat transfer tube portion 1C, a fin portion 1D, and a fin portion 1E. The heat transfer tube portion 1</b>C is provided with the internal space described above, and has a configuration similar to that of the plurality of heat transfer members 1 of the heat exchanger 100 . The heat transfer tube portion 1C, the fin portion 1D and the fin portion 1E are integrally molded, for example.

The fins 1E of each of the plurality of heat transfer members 1 are formed with holes 1F arranged so as to overlap each other when viewed from the first direction X. The beam portions 3A of the plurality of positioning members 3 are inserted through the holes 1F of the plurality of heat transfer members 1, respectively. The beam portions 3A of each of the plurality of positioning members 3 are connected to the fin portions 1E of each of the plurality of heat transfer members 1 .

The material constituting each of the plurality of heat transfer promoting members 2 and the plurality of positioning members 3 may be any material having relatively high thermal conductivity. For example, at least one of aluminum (Al) and copper (Cu) including

The third end 2A of each of the plurality of heat transfer promoting members 2 is arranged downstream in the third direction Y from the first end 1A of each of the plurality of heat transfer members 1 . The third end portion 2A is arranged upstream in the third direction Y from the plurality of heat transfer tube portions 1C.

[Correction under Rule 91 22.06.2022]
The fourth end 2B of each of the plurality of heat transfer promoting members 2 is arranged upstream in the third direction Y from the second end 1B of each of the plurality of heat transfer members 1 .

The beam portions 3A of each of the plurality of positioning members 3 are arranged downstream in the third direction Y from the plurality of heat transfer tube portions 1C. The beam portion 3A of each of the plurality of positioning members 3 is arranged upstream in the third direction Y from the second end portions 1B of the plurality of heat transfer members 1 .

The heat exchanger 101 does not include the first reinforcing member 13 and the second reinforcing member 14, for example. Note that the heat exchanger 101 may include the first reinforcing member 13 and the second reinforcing member 14 .

In the heat exchanger 101 , each of the multiple positioning members 3 is connected to each of the multiple heat transfer members 1 . Therefore, even in the heat exchanger 101, the position of each of the plurality of heat transfer enhancing members 2 relative to the plurality of heat transfer members 1 is less likely to fluctuate. An increase in loss (decrease in ventilation) is suppressed. Moreover, in the heat exchanger 101 , each of the plurality of positioning members 3 can act as a reinforcing member that supplements the strength of the heat exchanger 101 .

In the heat exchanger 101, the material forming each of the plurality of heat transfer promoting members 2 and the plurality of positioning members 3 includes a material with relatively high thermal conductivity (for example, at least one of Al and Cu). The thermal resistance of the heat path from the heat member 1 to the plurality of heat transfer promoting members 2 via the plurality of positioning members 3 is relatively low, and the heat transfer loss (heat loss) in the heat path is relatively small. Therefore, in the heat exchanger 101, the surface of each of the plurality of heat transfer promoting members 2 and the plurality of positioning members 3 can be effectively used as a heat transfer surface outside the tube. As a result, in the heat exchanger 101, compared to the heat exchanger 100 in which the surface of each of the plurality of heat transfer promoting members 2 and the plurality of positioning members 3 cannot be effectively used as a heat transfer surface outside the tube, Heat transfer performance is enhanced due to the larger heat area.

Note that each of the plurality of heat transfer members 1 of the heat exchanger 101 may have the same configuration as the third modification of the heat transfer member 1 shown in FIG.

Embodiment 3.
The heat exchanger according to Embodiment 3 has basically the same configuration as the heat exchanger 100 according to Embodiment 1, and has similar effects, but each of the plurality of heat transfer promoting members 2 has a projecting portion. 21 is different from the heat exchanger 100 . Differences from the heat exchanger 100 are mainly described below.

As shown in FIG. 12, each of the plurality of heat transfer enhancing members 2 has a first portion 20A, a second portion 20B, a third portion 20C, a protruding portion 21 and a protruding portion 22. The first portion 20</b>A is located on the most upstream side in the third direction Y in each heat transfer promoting member 2 . The second portion 20B is located on the most downstream side in the third direction Y in each heat transfer promoting member 2 . The third portion 20</b>C is positioned at the center in the third direction Y in each heat transfer promoting member 2 .

The protruding portion 21 is located downstream of the first portion 20A in the third direction Y and protrudes in the first direction X from the first portion 20A. The protruding portion 21 is located upstream in the third direction Y from the third portion 20C and protrudes in the first direction X from the third portion 20C.

The projecting portion 21 has flat plate portions 21A to 21C. The upstream end of the flat plate portion 21A is connected to the downstream end of the first portion 20A. The upstream end of the flat plate portion 21B is connected to the upstream end of the third portion 20C. The flat plate portion 21C connects the downstream end of the flat plate portion 21A and the upstream end of the flat plate portion 21B.

The flat plate portion 21A forms an obtuse angle with respect to the first portion 20A. The flat plate portion 21B forms an obtuse angle with respect to the third portion 20C. The flat plate portion 21C forms an obtuse angle with each of the

flat plate portions

21A and 21B. The flat plate portion 21C extends along the third direction Y. As shown in FIG.

The projecting portion 22 is located downstream of the third portion 20C in the third direction Y and projects in the first direction X from the third portion 20C. The projecting portion 22 is positioned upstream in the third direction Y relative to the second portion 20B and projects in the first direction X from the second portion 20B. The protruding portion 22 protrudes on the side opposite to the protruding portion 21 .

The projecting portion 22 has flat plate portions 22A to 22C. The upstream end of the flat plate portion 22A is connected to the downstream end of the third portion 20C. The upstream end of the flat plate portion 22B is connected to the upstream end of the second portion 20B. The flat plate portion 22C connects the downstream end of the flat plate portion 22A and the upstream end of the flat plate portion 22B.

The flat plate portion 22A forms an obtuse angle with respect to the third portion 20C. The flat plate portion 22B forms an obtuse angle with respect to the second portion 20B. Plate portion 22C forms an obtuse angle with each of plate portion 22A and plate portion 22B. 22 C of flat plate parts are extended along the 3rd direction Y. FIG.

The first portion 20A, the second portion 20B, the third portion 20C, the protruding portion 21, and the protruding portion 22 are integrally molded, for example. The first portion 20A, the second portion 20B, the third portion 20C, the projecting portion 21, and the projecting portion 22 are formed, for example, by bending one plate member. In this case, each of projecting portion 21 and projecting portion 22 constitutes a recess.

The first portion 20A, the second portion 20B, and the third portion 20C are arranged in the center of the two adjacent heat transfer members 1 in the first direction X. The protruding portion 21 is arranged closer to one heat transfer member 1 than the center in the first direction X of two adjacent heat transfer members 1 . The projecting portion 22 is arranged closer to the other heat transfer member 1 than the center in the first direction X of the two adjacent heat transfer members 1 .

The distance in the first direction X between one heat transfer member 1 and the protruding portion 21 is greater than the center in the first direction X of the two adjacent heat transfer members 1 . The distance in the first direction X between the other heat transfer member 1 and the projecting portion 21 is shorter than the center in the direction X. The distance in the first direction X between one heat transfer member 1 and the protruding portion 22 is greater than the center in the first direction X of the two adjacent heat transfer members 1 . It is longer than the center in the direction X than the distance in the first direction X between the other heat transfer member 1 and the projecting portion 22 .

The amount of protrusion in the first direction X of the protruding portion 21 with respect to the first portion 20A and the third portion 20C is equal to the amount of protrusion in the first direction X of the protruding portion 22 with respect to the second portion 20B and the third portion 20C, for example. The heat transfer promoting member 2 is arranged rotationally symmetrical about 180 degrees with respect to the center in the third direction Y, for example.

In the heat exchanger according to Embodiment 3, since each of the plurality of heat transfer promoting members 2 includes the protruding portion 21, compared to a heat exchanger in which each of the plurality of heat transfer promoting members 2 does not include the protruding portion 21, , the air flowing between two adjacent heat transfer members 1 easily flows along the surfaces of the heat transfer members 1, thereby improving the outdoor heat transfer coefficient.

<Modified Example of Heat Transfer Accelerating Member 2>
The following modifications are allowed for each of the plurality of heat transfer enhancing members 2 of the heat exchanger according to the third embodiment.

As shown in FIG. 13, in a cross section perpendicular to the second direction Z, each outer shape of the protruding portion 21 and the protruding portion 22 may be triangular. In a cross section perpendicular to the second direction Z, each outer shape of the protruding portion 21 and the protruding portion 22 is, for example, an isosceles triangle shape. In a cross section perpendicular to the second direction Z, the angle formed by the isosceles is, for example, an obtuse angle.

As shown in FIG. 14, each of the plurality of heat transfer promoting members 2 may be formed with at least one through-hole 23 penetrating the projecting portion 21 in the first direction X. As shown in FIG. A plurality of through holes 23 may be formed in the projecting portion 21 . For example, a plurality of through holes 23 are formed through each of flat plate portion 21A, flat plate portion 21B, and flat plate portion 21C of projecting portion 21 .

With this configuration, two air passages formed between two adjacent heat transfer members 1 with the heat transfer promoting member 2 therebetween are communicated by the through holes 23 . Therefore, air from the other air passage flows into the area where the width in the first direction X between the heat transfer member 1 and the heat transfer promoting member 2 is narrowed by the projecting portion 21 in one air passage. become. As a result, the heat exchanger provided with the plurality of heat transfer promoting members 2 shown in FIG. 14 has an improved extra-tube heat transfer coefficient compared to the heat exchanger provided with the plurality of heat transfer promoting members 2 shown in FIG. do.

Note that the through hole 23 may be provided so as to penetrate at least the flat plate portion 21C. At least one through-hole 23 penetrating the projecting portion 22 in the first direction X may be formed in each of the plurality of heat transfer promoting members 2 . Further, at least one through-hole 23 penetrating in the first direction X through the third portion 20C may be formed in each of the plurality of heat transfer promoting members 2 .

Also, the through-holes 23 may be configured as slits with guide portions that guide the direction of the wind, such as louvers formed on corrugated fins.

As shown in FIG. 15, in a cross section perpendicular to the second direction Z, a plurality of grooves 24 may be formed on the outer peripheral surfaces of the plurality of heat transfer promoting members 2 facing the first direction X. Each of the plurality of grooves 24 extends along the second direction Z. As shown in FIG. Each of the plurality of grooves 24 is continuous in the third direction Y, for example. Each of the plurality of grooves 24 is formed in the flat plate portion 21C of the projecting portion 21, for example. Each of the plurality of grooves 24 is, for example, a groove formed between two protrusions that protrude in the first direction X from the outer peripheral surface of the flat plate portion 21C facing the first direction X and are adjacent to each other in the third direction Y. . Each of the plurality of grooves 24 has two inclined surfaces that are inclined to form an acute angle with respect to the third direction Y, for example. The cross-sectional shape of each of the plurality of grooves 24 is, for example, V-shaped.

[Correction under Rule 91 22.06.2022]
Such grooves 24 can act as drainage paths for condensed or melted water.
At least one groove portion 24 may be formed on the outer peripheral surface facing the first direction X of the plurality of heat transfer promoting members 2 . The cross-sectional shape of the groove portion 24 may be U-shaped, for example. Grooves 24 may be formed in at least one of first portion 20A, second portion 20B, third portion 20C, flat plate portion 21A, flat plate portion 21B, and flat plate portion 21C.

In the heat transfer promoting member 2 shown in FIGS. 12 to 15, the projection amount in the first direction X of the projecting portion 21 with respect to the first portion 20A and the third portion 20C is It may be larger than the amount of protrusion in the first direction X of the portion 22 . Also, the amount of protrusion in the first direction X of the protruding portion 21 with respect to the first portion 20A and the third portion 20C is larger than the amount of protrusion in the first direction X of the protruding portion 22 with respect to the second portion 20B and the third portion 20C. Less is fine.

As shown in FIG. 16 , the distance in the first direction X between one heat transfer promoting member 2 and one heat transfer member 1 adjacent to the heat transfer promoting member 2 is upstream in the third direction Y It may be provided so as to gradually become shorter from the side toward the downstream side. In other words, the width of one heat transfer promoting member 2 in the first direction X may be provided so as to gradually widen from the upstream side in the third direction Y toward the downstream side. For example, the distance in the first direction X between one heat transfer promoting member 2 and each of two heat transfer members 1 adjacent in the first direction X with the heat transfer promoting member 2 interposed therebetween is It may be provided so as to gradually become shorter from the upstream side of Y toward the downstream side. A distance W1 in the first direction X between the third end portion 2A of the heat transfer promoting member 2 and each of the two heat transfer members 1 adjacent to each other in the first direction X with the heat transfer promoting member 2 interposed therebetween is It is longer than the interval W2 in the first direction X between the fourth end portion 2B of the heat transfer promoting member 2 and each of the two heat transfer members 1 .

The heat transfer promoting member 2 has, for example, two inclined surfaces 25 and two flat surfaces 26. Each inclined surface 25 is inclined with respect to the third direction Y so as to form an acute angle. The downstream end of one inclined surface 25 is connected to the upstream end of one flat surface 26 . One inclined surface 25 and one flat surface 26, and another inclined surface 25 and another flat surface 26 are arranged relative to the center line of the heat transfer enhancing member 2 extending along the third direction Y, for example. are in a line-symmetrical relationship. Each inclined surface 25 continues to the third end 2A. Each flat surface 26 continues to the fourth end 2B. Each inclined surface 25 and each flat surface 26 are planes, for example. Each inclined surface 25 and each flat surface 26 may be curved, for example.

The air flowing between two heat transfer members 1 adjacent to each other in the first direction X concentrates at the center in the first direction X between the two heat transfer members 1 toward the downstream side in the third direction Y. easier. In the heat exchanger provided with the heat transfer promoting member 2 shown in FIG. 16, the air is It becomes easy to flow along the surface of the heat transfer member 1, and the heat transfer coefficient outside the tube is improved.

In the heat transfer promoting member 2 shown in FIGS. 12 to 16, the shortest distance between one heat transfer member 1 and the heat transfer promoting member 2 of two adjacent heat transfer members 1 with the heat transfer promoting member 2 interposed therebetween The distance is equal to the shortest distance between the other heat transfer member 1 of the two heat transfer members 1 adjacent to each other with the heat transfer promoting member 2 interposed therebetween, but is not limited to this. . In the heat transfer promoting member 2 shown in FIGS. 12 to 16, the former shortest distance may be different from the latter shortest distance.

In addition, in the heat exchanger according to Embodiment 3 and its modification, the heat transfer member 1 may have the same configuration as that of any of the modifications shown in FIGS. Further, a groove portion 24 as shown in FIG. 15 may be formed in the heat transfer promoting member 2 of the heat exchanger according to the first embodiment or the second embodiment.

Embodiment 4.
The heat exchanger according to the fourth embodiment has basically the same configuration as the heat exchanger 100 according to the first embodiment, and has similar effects. It is different from the vessel 100. Differences from the heat exchanger 100 are mainly described below.

[Correction under Rule 91 22.06.2022]
As shown in FIG. 17, let a be the length in the third direction Y of each of the plurality of heat transfer members 1 . Let L be the length in the third direction Y of each of the plurality of heat transfer promoting members 2 . Let b be the maximum width in the first direction X of each of the plurality of heat transfer members 1 . Let p be the pitch in the first direction X of each of the plurality of heat transfer members 1 . The pitch p is defined by the center line C2 extending along the third direction Y passing through the center of one of the two adjacent heat transfer members 1 in the first direction X and the distance between the two adjacent heat transfer members 1 . It is the distance in the first direction X between the center line C2 extending along the third direction Y and passing through the center in the first direction X of the other heat transfer member 1 . Let tP be the average width in the first direction X of the plurality of heat transfer enhancing members 2 . The average width tP is a value obtained by dividing the cross-sectional area of the heat transfer promoting member 2 perpendicular to the second direction Z by the length L described above. The length a, the length L, the maximum width b, the pitch p, and the average width tP satisfy the following relational expression within the range of 0<tP/(pb)<1.

The above relational expression was derived based on the Computational Fluid Dynamics (CFD) method.

First, the governing equations describing the flow of air in the air passage shown in FIG. The graph shown is derived.

The horizontal axis of the graph shown in FIG. 18 is the ratio L/a of the length L of the heat transfer enhancing member 2 in the third direction Y to the length a of the heat transfer member 1 in the third direction Y.

The vertical axis of the graph shown in FIG. 18 is the ratio of the pressure loss ΔP1 of air flowing through the air passage shown in FIG. 17 to the pressure loss ΔP2 of air flowing through the air passage according to the comparative example. The pressure loss ΔP2 is the pressure loss of air flowing through the air passage according to the comparative example. The air passage according to the comparative example is an air passage formed by the heat exchanger according to the second comparative example. Specifically, the air passage according to the comparative example does not include the heat transfer enhancing member 2, and the distance in the first direction X between the two adjacent heat transfer members is two adjacent heat transfer members shown in FIG. 17 only in that the pitch p in the first direction X between the members 1 is half the value.

As shown in FIG. 18, the ratio ΔP1/ΔP2 changes according to the ratio tP/(pb). If the ratio ΔP1/ΔP2 is 100% or less, the pressure loss of the air flowing through the air passage shown in FIG. 17 is equal to or less than the pressure loss of the air flowing through the air passage according to the comparative example. .

Next, the graph shown in FIG. 19 is derived by arranging the graph shown in FIG. 18 by the ratio L/a and the ratio tP/(pb) at which the ratio ΔP1/ΔP2 is 100% or less. . The formula in FIG. 19 is a relational expression between the ratio tP/(pb) and the ratio L/a when the ratio ΔP1/ΔP2 is 100%.

In the heat exchanger according to Embodiment 4, since the above relational expression holds in the range of 0<tP/(pb)<1, the pressure loss is suppressed to be equal to or less than that of the above comparative example. , the heat transfer performance is improved as compared with the above comparative example. The heat exchanger according to Embodiment 4 may differ from the heat exchanger according to

Embodiment

2 or 3 only in that the above relational expression holds. The average width tP of each heat transfer promoting member 2 shown in FIGS. 12 to 16 is the value obtained by dividing the cross-sectional area of each heat transfer promoting member 2 perpendicular to the second direction Z by the length L thereof. Moreover, the heat transfer member 1 of the heat exchanger according to Embodiment 4 may have the same configuration as each of the heat transfer members 1 shown in FIGS.

Embodiment 5.
<Refrigeration cycle equipment>
A refrigeration cycle apparatus 200 according to the fifth embodiment includes any one of the heat exchangers according to the first to fourth embodiments. As shown in FIG. 20, the refrigeration cycle apparatus 200 mainly includes a heat exchanger 100, a compressor 111, a four-way valve 112, a heat exchanger 113, an expansion valve 114, and a blower 115, for example. The blower 115 sends air in the third direction Y to the heat exchanger 100 . The four-way valve 112 switches between an operation mode in which the heat exchanger 100 acts as an evaporator and an operation mode in which the heat exchanger 100 acts as a condenser.

The first header 11 of the heat exchanger 100 is connected to the discharge port and the suction port of the compressor 111 via a four-way valve 112, for example. The second header 12 of the heat exchanger 100 is connected to an expansion valve 114, for example.

Since the refrigerating cycle device 200 includes any one of the heat exchangers according to Embodiments 1 to 4, energy saving is realized compared to the refrigerating cycle device including the heat exchanger according to Comparative Example 1. In addition, since the refrigerating cycle device 200 includes any one of the heat exchangers according to Embodiments 1 to 4, the manufacturing cost and weight are reduced as compared with the refrigerating cycle device including the heat exchanger according to Comparative Example 2. However, energy saving has been achieved.

The embodiments disclosed this time should be considered illustrative in all respects and not restrictive. The technical scope indicated by the present disclosure is indicated by the scope of claims rather than the description of the above-described embodiments, and is intended to include all modifications within the scope and meaning equivalent to the scope of the claims. .

1 heat transfer member, 1A first end, 1B second end, 1C heat transfer tube portion, 1D, 1E, 1H fin portion, 1F hole, 1G heat transfer tube, 2 heat transfer promoting member, 2A third end, 2B fourth end, 3 positioning member, 3A beam portion, 3B, 3C connecting portion, 11 first header, 12 second header, 13 first reinforcing member, 14 second reinforcing member, 15 first inflow/outlet portion, 16 second 2 inflow/outflow part, 20A first part, 20B second part, 20C third part, 21, 22 projecting parts, 21A, 21B, 21C, 22A, 22B, 22C flat plate part, 23 through hole, 24 groove part, 25 inclined surface, 26 flat surface, 100, 101, 113 heat exchanger, 111 compressor, 112 four-way valve, 114 expansion valve, 115 blower, 200 refrigeration cycle device.

Claims

first and second headers extending along a first direction and spaced apart in a second direction perpendicular to the first direction;
one end in the second direction connected to the first header and the other end in the second direction connected to the second header, which are spaced apart from each other in the first direction and a plurality of heat transfer members having
each of the first header, the second header, and the plurality of heat transfer members defines an internal space through which a first heat exchange medium flows and an external space through which a second heat exchange medium flows,
the internal space of the first header communicates with the internal space of the second header via the internal space of each of the plurality of heat transfer members;
In the external space, the heat transfer member is arranged in a central portion between two heat transfer members adjacent in the first direction among the plurality of heat transfer members, and is perpendicular to the first direction and the second direction. at least one heat transfer enhancing member extending along three directions;
further comprising at least one positioning member that positions the at least one heat transfer enhancing member with respect to the first header, the second header, and the plurality of heat transfer members in the external space;
The heat exchanger, wherein the at least one positioning member is arranged only downstream of the internal space of each of the plurality of heat transfer members in the third direction in which the second heat exchange medium flows.
The heat exchanger according to claim 1, wherein said at least one heat transfer enhancing member is spaced apart from each of said plurality of heat transfer members.
the width of the at least one positioning member in the first direction is wider than the interval between two heat transfer members adjacent to each other in the first direction among the plurality of heat transfer members;
the width of the at least one positioning member in the second direction is narrower than the width of the at least one heat transfer promoting member in the second direction;
3. The heat exchanger according to claim 1 or 2, wherein said at least one positioning member is connected with said plurality of heat transfer members.
each of the plurality of heat transfer members includes a heat transfer tube portion in which the internal space of each of the plurality of heat transfer members is provided; and a fin portion extending from the heat transfer tube portion to the downstream side,
The fins of each of the plurality of heat transfer members are formed with holes arranged so as to overlap each other when viewed from the first direction,
4. The heat exchanger according to claim 3, wherein said at least one positioning member is inserted through said hole of each of said plurality of heat transfer members.
The heat exchanger according to claim 3 or 4, wherein the material forming said at least one positioning member includes at least one of aluminum (Al) and copper (Cu).
a first reinforcing member and a second reinforcing member arranged in the external space so as to sandwich the plurality of heat transfer members in the first direction and connected to each of the first header and the second header; further comprising a member,
the width of the at least one positioning member in the first direction is greater than or equal to the spacing in the first direction between the first reinforcing member and the second reinforcing member;
the width of the at least one positioning member in the second direction is narrower than the width of the at least one heat transfer promoting member in the second direction;
2. The heat exchanger of claim 1, wherein said at least one positioning member is connected to each of said first reinforcing member and said second reinforcing member and is spaced apart from said plurality of heat transfer members.
The heat exchanger according to claim 6, wherein the thermal conductivity of the material forming said at least one positioning member is lower than the thermal conductivity of the material forming said plurality of heat transfer members.
Each of the plurality of heat transfer members has a first end positioned furthest upstream in the third direction in which the second heat exchange medium flows, and a second end positioned furthest downstream in the third direction. and
The at least one heat transfer promoting member has a third end positioned furthest upstream in the third direction and a fourth end positioned furthest downstream in the third direction,
The heat exchanger according to any one of claims 1 to 7, wherein the third end is arranged downstream of the first end in the third direction.
The at least one heat transfer promoting member includes a first portion located upstream in the third direction, and a heat transfer member located downstream of the first portion in the third direction and extending from the first portion to the first portion. A heat exchanger according to any one of claims 1 to 8, having a projecting portion projecting in a direction.
The heat exchanger according to claim 9, wherein said at least one heat transfer promoting member is formed with at least one through-hole penetrating said projecting portion in said first direction.
In a cross section perpendicular to the second direction, at least one groove is formed in an outer peripheral surface of the at least one heat transfer promoting member facing the first direction,
The heat exchanger according to any one of claims 1 to 10, wherein said at least one groove extends along said second direction.
The distance in the first direction between the at least one heat transfer enhancing member and the one heat transfer member adjacent to the at least one heat transfer enhancing member is from the upstream side to the downstream side in the third direction. 12. The heat exchanger according to any one of claims 1 to 11, provided so as to gradually become shorter as the length increases.
Length a of each of the plurality of heat transfer members in the third direction, length L of the at least one heat transfer promoting member in the third direction, length of each of the plurality of heat transfer members in the first direction The maximum width b, the pitch p in the first direction of each of the plurality of heat transfer members, and the average width tP of the at least one heat transfer enhancement member in the first direction are 0<tP/(pb) The heat exchanger according to any one of claims 1 to 12, which satisfies the following relational expression in the range of <1.
the first heat exchange medium is a refrigerant, the second heat exchange medium is air,
A first heat exchange circuit including the heat exchanger according to any one of claims 1 to 13, in which the refrigerant circulates;
A refrigeration cycle apparatus comprising: a blower that sends the air in the third direction to the heat exchanger.