TW202234010A - Heat exchanger and refrigeration cycle apparatus - Google Patents

Abstract

A heat exchanger (100) of the present invention includes a first header (11) and a second header (12), and a plurality of heat transfer members (1) having one end in a second direction (Z) connected to a first header and the other end in the second direction connected to a second header. Each of the plurality of heat transfer members is configured so as to perform heat exchange between a first heat exchange medium flowing in an internal space in the second direction and a second heat exchange medium flowing in a third direction (Y) in an outer space of each of the plurality of heat transfer members. A heat exchanger further includes a plurality of heat transfer promoting members (2) extending along the third direction (Y) in the outer space arranged in the central portion between two heat transfer members adjacent to each other in a first direction (X) among the plurality of heat transfer members and.

Description

Heat Exchangers and Refrigeration Cycle Devices

The present invention relates to a heat exchanger and a refrigeration cycle device.

Japanese Patent Laid-Open No. 2018-155481 (Patent Document 1) describes a heat exchanger including a plurality of heat transfer tube units 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 arrangement direction of the heat transfer tube units. In each heat transfer tube unit, a plurality of heat transfer tubes extend along the extending direction of the heat transfer tubes perpendicular to the arrangement direction of the heat transfer tube units, and a plurality of fins and a plurality of heat transfer tubes are arranged against the heat transfer tube unit. The arrangement direction and the heat transfer tube separation direction perpendicular to the extending direction of the heat transfer tubes are alternately arranged. In each heat transfer tube unit, the plurality of fins have portions inclined with respect to the separation direction of the heat transfer tubes. Each heat transfer unit is connected to a first header and a second header. [Prior Art Literature] [Patent Literature]

[Patent Document 1] Japanese Patent Laid-Open No. 2018-155481

[The problem to be solved by the invention]

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 of the arrangement direction of each heat transfer tube unit is widened, the air flowing between adjacent heat transfer tube units tends to concentrate on the adjacent heat transfer tube units in the arrangement direction of each heat transfer tube unit It flows through the central part between the tube units.

However, when the pitch in the arrangement direction of each heat transfer tube unit is set to be narrow, the pitch of a plurality of insertion holes for inserting each heat transfer tube in each of the first header and the second header It also needs to be set to be narrow. The narrower the pitch of the plurality of insertion holes, the lower the formability of the first header and the second header.

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.

The 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 including the heat exchanger. [Technical means to solve problems]

The heat exchanger of the present invention includes: a first header and a second header extending along the first direction and arranged at intervals in the second direction orthogonal to the first direction; and a plurality of heat transfer pipes The members are arranged spaced apart from each other in the first direction, and have one end connected to the first header in the second direction and the other end connected to the second header in the second direction. Each of the first header, the second header, and the plurality of heat transfer members is divided into an inner space for the circulation of the first heat exchange medium and an outer space for the circulation of the second heat exchange medium. The inner space of the first header communicates with the inner space of the second header via the inner space of each of the plurality of heat transfer members. The inner space of each of the first header and the second header is communicated through the inner space of each of the plurality of heat transfer members. The heat exchanger further includes: at least one heat transfer promoting member, which is connected to the external space, and is arranged in a central portion between two heat transfer members adjacent in the first direction among the plurality of heat transfer members, along the second heat transfer member. extending in three directions; and at least one positioning member tied to the above-mentioned outer space and positioning the at least one heat transfer promoting member relative to the first header, the second header, and the plurality of heat transfer members. At least one positioning member is arranged only on the downstream side of the third direction in which the second heat exchanging medium circulates than the inner space of each of the plurality of heat transfer members. [Effect of invention]

According to the present invention, it is possible 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 including the heat exchanger.

Hereinafter, embodiments of the present invention will be described with reference to the drawings. In addition, in the following drawings, the same reference signs are attached to the same or corresponding parts, and the description thereof will not be repeated. In addition, for convenience of description, the 1st direction X, the 2nd direction Z, and the 3rd direction Y which are orthogonal to each other are shown in each drawing.

Implementation type 1. <Configuration of Heat Exchanger 100 > As shown in FIGS. 1 to 4 , the heat exchanger 100 of the first embodiment 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 The positioning member 3 , the first reinforcing member 13 , and the second reinforcing member 14 .

The heat exchanger 100 is provided in such a manner that the first heat exchange medium (eg, refrigerant) flowing in the second direction Z and the second heat exchange medium (eg, air) flowing in the third direction Y perform heat exchange. The second direction Z is, for example, along the up-down direction. 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 plurality of 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 divides an inner space for refrigerant circulation and an outer space for air circulation. The inner space of each of the first header 11 and the second header 12 is communicated through the inner space of each of the plurality of heat transfer members 1 . In other words, the inner spaces of each of the plurality of heat transfer members 1 are juxtaposed to each other and connected to the inner spaces of each of the first header 11 and the second header 12 . For example, the refrigerant flowing into the inner space of the first header 11 from the first outflow and inflow portion 15 is distributed to the inner space of each of the plurality of heat transfer members 1 . The refrigerant flowing in the second direction in the respective inner spaces of the plurality of heat transfer members 1 exchanges heat with the air flowing in the third direction Y in the outer spaces of the plurality of heat transfer members 1 . The refrigerant circulating in the inner space of each of the plurality of heat transfer members 1 flows out to the inner space of the second header 12 and merges, and then flows out from the second outflow and inflow portion 16 to the outside of the heat exchanger 100 .

The outer space of each of the first header 11 , the second header 12 , and the plurality of heat transfer members 1 (ie, the first header 11 , the second header 12 , the first reinforcing member 13 , and the second header 12 ) The outer space surrounded by the reinforcing member 14) is arranged in such a way that the air flows toward the third direction Y. Hereinafter, the upstream side of the air flowing in the third direction Y is simply referred to as the upstream side in the third direction Y, and the downstream side of the air flowing in the third direction Y is referred to simply as the downstream side in the third direction Y. The above-mentioned external space is opened in each of the upstream side and the downstream side of the third direction Y.

As shown in FIG. 1 , the first header 11 and the second header 12 extend along the first direction X, respectively, and are arranged in the second direction Z with an interval therebetween. The first header 11 has a first outflow and inflow portion 15 for the inflow or outflow of the refrigerant. The second header 12 has a second outflow and inflow portion 16 for the outflow or inflow of the refrigerant.

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

Specifically, the first header 11 is formed with a plurality of insertion holes arranged at intervals in the first direction X from each other. 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 arranged at intervals in the first direction X from each other. The other end in the first direction X of each of the plurality of heat transfer members 1 is inserted into each of the plurality of insertion holes formed in the second header 12 .

The plurality of heat transfer promoting members 2 are for suppressing the flow of the air circulating between the two adjacent heat transfer members 1 in the first direction X from concentrating on the central portion in the first direction X between the two heat transfer members 1 . By. As shown in FIGS. 1 to 4 , each of the plurality of heat transfer promoting members 2 is arranged between the two heat transfer members 1 that are adjacent in the first direction X among the plurality of heat transfer members 1 arranged in the external space. the central part of the room. Each of the plurality of heat transfer promoting members 2 is arranged to overlap in the second direction Z with a center line C1 passing through the first direction between the two heat transfer members 1 adjacent in the first direction X, for example. The center of X and extending along the third direction Y. The center line passing through the center of each of the plurality of heat transfer promoting members 2 in the first direction X and extending along the third direction Y is disposed so as to overlap the center line C1 in the second direction Z, for example. Each of the plurality of heat transfer promoting members 2 extends along the third direction Y. Each of the plurality of heat transfer promoting members 2 divides the above-mentioned external space in the first direction X.

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 promoting 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 the first header 11 and the second header 12 . The surface of each of the plurality of heat transfer promoting members 2 facing the first direction X is, for example, a plane. The surface facing the first direction X of each of the plurality of heat transfer promoting members 2 is, for example, parallel to the surface facing the first direction X of each of the plurality of heat transfer members 1 . For example, through-holes from one surface facing the first direction X to the other surface are not formed in each of the plurality of heat transfer promoting members 2 . Each of the plurality of heat transfer promoting members 2 is not connected to a fin not shown.

The plurality of positioning members 3 are used to position each of the plurality of heat transfer promoting members 2 relative to the first header 11, the second header 12, the first reinforcing member 13, the second reinforcing member 14, and a plurality of heat transfer members 1 positioned. Each of the plurality of positioning members 3 is connected to each of the plurality of heat transfer promoting 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 plurality of positioning members 3 is not in contact with the plurality of heat transfer members 1 . Each of the plurality of positioning members 3 is not connected to a fin not shown.

Each of the plurality of positioning members 3 has a beam portion 3A that spans between the first reinforcing member 13 and the second reinforcing member 14 and is connected to the plurality of heat transfer promoting members 2; a connecting portion 3B is connected to the first reinforcing member 2 The member 13 is connected; and the connecting portion 3C is connected with the second reinforcing member 14 .

Each of the plurality of positioning members 3 is arranged at intervals in the second direction Z from each other. Each of the plurality of positioning members 3 is arranged, for example, on 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 constituting 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 constituting each of the plurality of heat transfer promoting members 2 and the plurality of positioning members 3 may also be lower than the thermal conductivity of the material constituting the plurality of heat transfer members 1 .

The first reinforcing member 13 and the second reinforcing member 14 are used to supplement 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 1st reinforcement member 13 and the 2nd reinforcement member 14 are spaced apart from each other in the 1st direction X, and are arrange|positioned in the said external space. The first reinforcing member 13 and the second reinforcing member 14 are arranged in the first direction X across the plurality of heat transfer members 1 and the plurality of heat transfer promoting members 2 . The first reinforcing member 13 and the second reinforcing member 14 are connected to the outer surface of each of the first header 11 and the second header 12 . The first reinforcing member 13 is connected to one end surface 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 surface 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 promoting members 2 has, for example, the same configuration as each other. Each of the plurality of positioning members 3 has, for example, a structure equal to each other. The number of each of the plurality of heat transfer members 1 , the plurality of heat transfer promotion members 2 , and the plurality of positioning members 3 is not particularly limited. The number of the plurality of heat transfer promoting members 2 is, for example, one less than the number of the plurality of heat transfer members 1 . The number of the plurality of positioning members 3 is, for example, two.

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 promotion members 2 , and the plurality of positioning members 3 of the heat exchanger 100 will be described.

As shown in FIGS. 2 and 3 , each of the plurality of heat transfer members 1 has a first end portion 1A located on the upstream side of the third direction Y, and a second end portion 1B located on the downstream side of the third direction Y . Each of the first end portions 1A is arranged on the downstream side of the end portion located on the upstream side of each of the first reinforcing member 13 and the second reinforcing member 14 . Each second end portion 1B is arranged on the upstream side of the end portion located on the downstream side 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 2A located on the upstream side in the third direction Y, and a fourth end located on the downstream side in the third direction Y Section 2B. Each of the third end portions 2A is arranged on the downstream side of each of the first end portions 1A. Each fourth end portion 2B is arranged on the downstream side of each second end portion 1B.

As shown in FIGS. 1 and 2 , the beam portion 3A of each of the plurality of positioning members 3 is located in the above-mentioned outer space, and is only disposed in the third direction Y relative to the inner space of each of the plurality of heat transfer members 1 on the downstream side. In other words, the beam portion 3A of each of the plurality of positioning members 3 is arranged only at the downstream side of the third direction Y than the second end portion 1B of each of the plurality of heat transfer members 1 . For example, the connecting portions 3B and 3C of each of the plurality of positioning members 3 are also arranged only on the downstream side of the third direction Y than the inner space of each of the plurality of heat transfer members 1 in the above-mentioned outer space.

Hereinafter, an example of the size relationship between the dimensions 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 the 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 greater than the width of each of the plurality of heat transfer members 1 in the third direction Y The width in one direction X is wider. In a cross section orthogonal to the second direction, each of the plurality of heat transfer members 1 has a long-side direction along the third direction Y and a short-side direction along the first direction X. Each of the plurality of heat transfer members 1 is, for example, a flat tube.

As shown in FIGS. 2 and 3 , the plurality of heat transfer promoting members 2 are arranged in the center between the two heat transfer members 1 adjacent to each other in the first direction X, respectively. The width in the first direction X of the plurality of heat transfer promoting members 2 is narrower than the interval in the first direction X between two adjacent heat transfer members 1 in the first direction X. In the cross section orthogonal to the second direction Z, the width in the third direction Y of each of the plurality of heat transfer promoting members 2 is larger than the width in the first direction X of each of the plurality of heat transfer promoting members 2 width. Each of the plurality of heat transfer promoting members 2 has a long-side direction along the third direction Y and a short-side direction along the first direction X in a cross section orthogonal to the second direction.

As shown in FIGS. 2 and 3 , the interval in the first direction X between the two heat transfer members 1 adjacent in the first direction X is compared with the heat transfer promotion between the heat transfer members 1 adjacent in the first direction X and the heat transfer. The spacing in the first direction X between the members 2 is wider.

As shown in FIGS. 2 and 3 , the width in the first direction X of each of the plurality of heat transfer promoting members 2 is narrower than the width in the first direction X of each of the plurality of heat transfer members 1 . For example, regardless of the position of the third direction Y, the width of each of the plurality of heat transfer promoting members 2 in the first direction X is constant. The interval in the first direction X between the heat transfer members 1 and the heat transfer promoting members 2 adjacent in the first direction X does not reach the first direction between the two heat transfer members 1 adjacent in the first direction X, for example half the interval of X.

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

As shown in FIG. 1 , the width in the second direction Z of the beam portion 3A of each 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 the beam portion 3A of each 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 is wider than The width in the first direction X of each of the plurality of heat transfer members 1 is narrower.

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

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

The heat exchanger of Comparative Example 1 differs from the heat exchanger 100 only in that the heat transfer promoting member 2 is not provided. In the heat exchanger of Comparative Example 1, the interval in the first direction X of two adjacent heat transfer members 1 is the interval in the first direction X of two adjacent heat transfer members 1 in the heat exchanger 100 equal.

The heat exchanger of Comparative Example 2 differs from the heat exchanger 100 only in that the heat transfer promoting member 2 is not provided, and the interval in the first direction X of two adjacent heat transfer members is the adjacent one in the heat exchanger 100 . half of the interval in the first direction X of the two heat transfer members. In the heat exchanger of Comparative Example 2, the interval in the first direction X of two adjacent heat transfer members 1 is the same as the distance in the first direction X of the heat transfer member 1 and the heat transfer promoting member 2 in the heat exchanger 100 The intervals are roughly equal.

The heat exchanger 100 is provided with a plurality of heat transfer promoting members 2, and the plurality of heat transfer promoting members 2 are arranged in the above-mentioned external space, and are arranged in two adjacent heat transfer members in the first direction X among the plurality of heat transfer members 1. The central portion between the thermal members 1 extends along the third direction Y. Thereby, the air circulating between the two heat transfer members 1 adjacent to each other in the first direction X is restrained from being concentrated in the central portion in the first direction X between the two heat transfer members 1 and flowing by the heat transfer promoting members 2 . Therefore, the air that circulates between the two adjacent heat transfer members 1 tends to follow the surface of the heat transfer members 1 . As a result, the heat transfer rate outside the tube of the heat exchanger 100 is higher than that of the heat exchanger of Comparative Example 1, which is the interval in the first direction X of two adjacent heat transfer members 1 . It is a heat exchanger 100 that is equal to the interval in the first direction X of two adjacent heat transfer members 1 but does not include the heat transfer promoting member 2 . In addition, the heat transfer rate outside the tubes of the heat exchanger 100 was substantially the same as the heat transfer rate outside the tubes of the heat exchanger of Comparative Example 1.

On the other hand, in the heat exchanger of Comparative Example 2, the interval 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 must be It is set as narrow as the space|interval of the 1st direction X of each heat transfer member. As a result, the formability of the first header and the second header in the heat exchanger of Comparative Example 2 was lower than that of the first header and the second header in the heat exchanger of Comparative Example 1.

On the other hand, compared with the heat exchanger of Comparative Example 2, in the heat exchanger 100, a plurality of pieces for inserting the heat transfer members 1 in each of the first header 11 and the second header 12 The interval between the insertion holes in the first direction X is wide, and can be set to be wide similarly to the heat exchanger of Comparative Example 1.

As a result, compared with the heat exchanger of Comparative Example 1, the heat exchanger 100 can improve the heat transfer performance without reducing the formability of the first header 11 and the second header 12 . Compared with the heat exchanger of Comparative Example 2, the heat exchanger 100 can improve the formability of the first header 11 and the second header 12 without reducing the heat transfer performance.

Also, each of the plurality of heat transfer promoting members 2 may be lighter in weight than each of the plurality of heat transfer members 1 . Therefore, compared with the heat exchanger of Comparative Example 2, the weight of the heat exchanger 100 can be reduced. Also, the manufacturing cost of each of the plurality of heat transfer promoting members 2 can be reduced more than the manufacturing cost of each of the plurality of heat transfer members 1 . Therefore, compared with the manufacturing cost of the heat exchanger of Comparative Example 2, the manufacturing cost of the heat exchanger 100 can be reduced.

In the heat exchanger 100 , each of the plurality of positioning members 3 is arranged only on the downstream side of the third direction Y relative to the inner space of each of the plurality of heat transfer members 1 . In this way, when the refrigeration cycle apparatus including the heat exchanger 100 performs a defrosting operation, for example, when the heat exchanger 100 functions as a condenser in a low temperature environment, each positioning member 3 is less likely to hinder the third direction. Drainage of the generated frost melting water is concentrated on the upstream side of 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 positions of the plurality of heat transfer promoting members 2 with respect to each of the plurality of heat transfer members 1 are less likely to change, so that the change in the heat transfer rate outside the tube caused by the change in the position can be suppressed. Decreased, increased pressure loss (decreased ventilation).

In addition, 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 constituting each of the plurality of positioning members 3 is relatively low, the heat transfer member 1 may pass through the plurality of positioning members. Since the thermal resistance of the heat path from the member 3 to the plurality of heat transfer promoting members 2 becomes high, the heat transfer loss (heat loss) in the heat path becomes large. 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-described heat path is not formed, and heat transfer loss can be suppressed.

In addition, when the heat exchanger 100 functions as an evaporator in a low-temperature environment, the water vapor in the air circulating between the two adjacent heat transfer members 1 is cooled by each heat transfer member 1 and turns into frost. Attached to the heat transfer member 1 . Since the temperature of the gas flowing on the surface of each heat transfer member 1 gradually decreases from the first end portion 1A toward the second end portion 1B of each heat transfer member 1, the structure of the surface of each heat transfer member 1 is The amount of frost is the largest on the first end 1A side and gradually decreases toward the second end 1B. As a result, assuming that each of the plurality of heat transfer promoting members 2 is arranged to overlap with the first end portion 1A when viewed from the first direction X, the gap between the heat transfer member 1 and the heat transfer promoting member 2 is easily blocked by frost . On the other hand, in the heat exchanger 100 , the third end portion 2A of each of the plurality of heat transfer promoting members 2 is arranged at the third position relative to the first end portion 1A of each of the plurality of heat transfer members 1 . At the downstream side in the direction Y, compared with the case where each of the plurality of heat transfer promoting members 2 is arranged to overlap with the first end 1A when viewed from the first direction X, the heat transfer member 1 and the heat transfer promoting member The members 2 are not easily blocked by frost.

<Variation of Heat Exchanger 100 > The following modifications are allowed for each of the plurality of heat transfer members 1 in the heat exchanger 100 .

As shown in FIG. 5 , each of the plurality of heat transfer members 1 may also include a heat transfer tube portion 1C, a fin portion 1D, and a fin portion 1E. The heat transfer tube portion 1C is provided with the above-described internal space, and has the same configuration as 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 formed, for example.

In each of the plurality of heat transfer members 1 , the fin portion 1D extends toward the upstream side of the third direction Y from the heat transfer tube portion 1C. The end of the fin portion 1D on the upstream side in the third direction Y forms the first end 1A of the heat transfer member 1 . The fin portion 1E extends toward the downstream side in the third direction Y from the heat transfer tube portion 1C. The end portion of the fin portion 1E on the downstream side in the third direction Y constitutes the second end portion 1B of the heat transfer member 1 . A space for circulating the refrigerant 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 also be constituted by a plurality of heat transfer tubes 1G arranged at intervals in the third direction Y in a row. 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 an end portion located on the upstream side of one heat transfer tube 1G arranged on the most upstream side among the plurality of heat transfer tubes 1G. The above-mentioned second end portion 1B of each of the plurality of heat transfer members 1 is an end portion located on the downstream side of one heat transfer tube 1G on the most downstream side among the plurality of heat transfer tubes 1G.

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

Implementation type 2. The heat exchanger 101 of the second embodiment has basically the same structure as the heat exchanger 100 of the first embodiment, and exerts the same function, and the difference from the heat exchanger 100 is that each of the plurality of positioning members 3 is different. which is connected to each of the plurality of heat transfer members 1 . Hereinafter, the difference from the heat exchanger 100 will be mainly described.

As shown in FIGS. 8 to 11 , each of the plurality of heat transfer members 1 of the heat exchanger 101 has the same configuration as the heat transfer member 1 of the aforementioned first modification. 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 1C is provided with the above-described internal space, and has the same configuration as 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 formed, for example.

In each of the plurality of heat transfer members 1 , the fin portion 1D extends toward the upstream side of the third direction Y from the heat transfer tube portion 1C. The end of the fin portion 1D on the upstream side in the third direction Y forms the first end 1A of the heat transfer member 1 . The fin portion 1E extends toward the downstream side in the third direction Y from the heat transfer tube portion 1C. The end portion of the fin portion 1E on the downstream side in the third direction Y constitutes the second end portion 1B of the heat transfer member 1 . A space for circulating the refrigerant is not formed in the fin portion 1D and the fin portion 1E.

Holes 1F arranged to overlap each other when viewed from the first direction X are formed in the fin portion 1E of each of the plurality of heat transfer members 1 . The beam portion 3A of each of the plurality of positioning members 3 is inserted through the hole portion 1F of each of the plurality of heat transfer members 1 . The beam portion 3A of each of the plurality of positioning members 3 is connected to the fin portion 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, including at least one of aluminum (Al) and copper (Cu).

The third end portion 2A of each of the plurality of heat transfer promoting members 2 is arranged on the downstream side in the third direction Y than the first end portion 1A of each of the plurality of heat transfer members 1 . The third end portion 2A is disposed on the upstream side of the third direction Y relative to the plurality of heat transfer tube portions 1C.

The fourth end portion 2B of each of the plurality of heat transfer promoting members 2 is arranged on the upstream side of the third direction Y relative to the second end portion 1B of each of the plurality of heat transfer members 1 .

The beam portion 3A of each of the plurality of positioning members 3 is disposed on the downstream side of the third direction Y relative to the plurality of heat transfer tube portions 1C. The beam portion 3A of each of the plurality of positioning members 3 is arranged on the upstream side of the third direction Y relative to the second end portion 1B of the plurality of heat transfer members 1 .

The heat exchanger 101 does not include, for example, the first reinforcing member 13 and the second reinforcing member 14 . Furthermore, 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 plurality of positioning members 3 is connected to each of the plurality of heat transfer members 1 . Therefore, even in the heat exchanger 101, the position of the plurality of heat transfer promoting members 2 with respect to each of the plurality of heat transfer members 1 is not easily changed, so that the heat transfer rate outside the tube caused by the change in the position can be suppressed. decrease in pressure loss and increase in pressure loss (decreased ventilation). In addition, in the heat exchanger 101, each of the plurality of positioning members 3 can function as a reinforcing member that complements the strength of the heat exchanger 101.

In the heat exchanger 101, the material constituting each of the plurality of heat transfer promoting members 2 and the plurality of positioning members 3 includes a material having a relatively high thermal conductivity (for example, at least one of Al and Cu), so the materials from each 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, 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 tubes, in the heat exchanger 101, due to the tube The outer heat transfer area becomes larger, so the heat transfer performance improves.

In addition, each of the plurality of heat transfer members 1 of the heat exchanger 101 may have the same configuration as that of the third modification of the heat transfer member 1 shown in FIG. 7 .

Implementation type 3. The heat exchanger according to the third embodiment has basically the same configuration and the same effect as the heat exchanger 100 according to the first embodiment, and is different from the heat exchanger 100 in that one of the plurality of heat transfer promoting members 2 is used. Each has a protruding portion 21 . Hereinafter, the difference from the heat exchanger 100 will be mainly described.

As shown in FIG. 12 , each of the plurality of heat transfer promoting members 2 has a first portion 20A, a second portion 20B, a third portion 20C, a protruding portion 21 , and a protruding portion 22 . In each heat transfer promoting member 2, the first portion 20A 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 of the heat transfer promoting members 2, the third portion 20C is located in the center of the third direction Y.

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

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

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 respect to each of the flat plate portion 21A and the flat plate portion 21B. The flat plate portion 21C extends along the third direction Y.

The protruding portion 22 is located more downstream than the third portion 20C in the third direction Y, and protrudes toward the first direction X from the third portion 20C. The protruding portion 22 is located more upstream than the second portion 20B in the third direction Y, and protrudes toward the first direction X from the second portion 20B. The protruding portion 22 protrudes toward the opposite side to the protruding portion 21 .

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

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. The flat plate portion 22C forms an obtuse angle with respect to each of the flat plate portion 22A and the flat plate portion 22B. The flat plate portion 22C extends along the third direction Y.

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

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

Among the distances in the first direction X between the heat transfer member 1 and the protruding portion 21, between the heat transfer member 1 and the protruding portion 21 on one side of the center in the first direction X of the two adjacent heat transfer members 1 The distance in the first direction X will be greater than the distance in the first direction X between the heat transfer member 1 and the protruding portion 21 on the other side of the center of the first direction X of the two adjacent heat transfer members 1 . short. Among the distances in the first direction X between the heat transfer member 1 and the protruding portion 22 , the distance between the heat transfer member 1 and the protruding portion 22 on one side is closer than the center of the first direction X of the two adjacent heat transfer members 1 The distance in the first direction X will be greater than the distance in the first direction X between the heat transfer member 1 and the protruding portion 22 on the other side of the center of the first direction X of the two adjacent heat transfer members 1 . long.

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

Compared with the heat exchanger in which each of the plurality of heat transfer promoting members 2 does not include the protruding portion 21, in the heat exchanger of Embodiment 3, since each of the plurality of heat transfer promoting members 2 includes the protruding portion 21, Therefore, the air circulating between the two adjacent heat transfer members 1 easily flows along the surface of the heat transfer members 1, thereby increasing the outdoor heat transfer rate.

<Modification of the heat transfer promoting member 2> In each of the plurality of heat transfer promoting members 2 of the heat exchanger of Embodiment 3, the following modifications are allowed.

As shown in FIG. 13 , in a cross section perpendicular to the second direction Z, the respective external shapes of the protruding portion 21 and the protruding portion 22 may also be triangular. In a cross section perpendicular to the second direction Z, the respective external shapes of the protruding portion 21 and the protruding portion 22 are, for example, an isosceles triangle shape. In the 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 , at least one through hole 23 penetrating the protruding portion 21 in the first direction X may be formed in each of the plurality of heat transfer promoting members 2 . A plurality of through holes 23 may be formed in the protruding portion 21 . For example, a plurality of through holes 23 penetrating each of the flat plate portion 21A, the flat plate portion 21B, and the flat plate portion 21C of the protruding portion 21 are formed.

In this way, between the two adjacent heat transfer members 1 , the two ventilation paths formed across the heat transfer promoting member 2 are communicated through the through holes 23 . Therefore, air flows from the other ventilation path into a region where the width in the first direction X between the heat transfer member 1 and the heat transfer promotion member 2 is narrowed by the protrusion 21 in the one ventilation path. As a result, the out-of-tube heat transfer rate of the heat exchanger provided with the plurality of heat transfer promotion members 2 shown in FIG. 14 is improved compared to the heat exchanger provided with the plurality of heat transfer promotion members 2 shown in FIG. 12 .

Furthermore, the through hole 23 may be provided so as to penetrate at least the flat plate portion 21C. In addition, at least one through hole 23 penetrating the protruding portion 22 in the first direction X may be formed in each of the plurality of heat transfer promoting members 2 . In addition, at least one through hole 23 penetrating the third portion 20C in the first direction X may be formed in each of the plurality of heat transfer promoting members 2 .

Moreover, the through-hole 23 may be comprised as the slit accompanying the guide part which guides the wind direction like the louver (louver) formed as a corrugated fin (corrugate fin).

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 connected in the third direction Y, for example. Each of the plurality of groove portions 24 is formed in, for example, the flat plate portion 21C of the protruding portion 21 . Each of the plurality of grooves 24 is formed, for example, in a groove between two protrusions that protrude in the first direction X and are adjacent to the third direction Y with respect to the outer peripheral surface of the flat plate portion 21C facing the first direction X. Each of the plurality of groove portions 24 has, for example, two inclined surfaces inclined so as to form an acute angle with respect to the third direction Y. The cross-sectional shape of each of the plurality of grooves 24 is, for example, a V-shape.

Such a groove portion 24 can function as a drainage path for condensed water or frost melting water. Furthermore, at least one groove portion 24 may be formed on the outer peripheral surfaces of the plurality of heat transfer promoting members 2 facing in the first direction X. The cross-sectional shape of the groove portion 24 may be, for example, a U-shape. The groove portion 24 may be formed in at least any one of the first portion 20A, the second portion 20B, the third portion 20C, the flat plate portion 21A, the flat plate portion 21B, and the flat plate portion 21C.

In the heat transfer promoting member 2 shown in FIGS. 12 to 15 , the protruding amount of the protruding portion 21 relative to the first portion 20A and the third portion 20C in the first direction X may be larger than that of the protruding portion 22 relative to the second portion The amount of protrusion in the first direction X of 20B and the third portion 20C is larger. In addition, the protruding amount of the protruding portion 21 relative to the first portion 20A and the third portion 20C in the first direction X may be larger than the protruding amount of the protruding portion 22 relative to the second portion 20B and the third portion 20C in the first direction X less quantity.

As shown in FIG. 16 , the distance in the first direction X between a heat transfer promoting member 2 and a heat transfer member 1 adjacent to the heat transfer promoting member 2 can also be set to follow the distance from the third direction Y The upstream side is gradually shortened toward the downstream side. In other words, the width in the first direction X of one heat transfer promoting member 2 may be set to gradually increase from the upstream side toward the downstream side in the third direction Y. For example, the distance in the first direction X between one heat transfer promoting member 2 and each of the two heat transfer members 1 that are adjacent to each other in the first direction X across the heat transfer promoting member 2 may be set to vary with It gradually becomes shorter from the upstream side toward the downstream side in the third direction Y. The interval W1 in the first direction X between the third end 2A of the heat transfer promoting member 2 and each of the two heat transfer members 1 adjacent in the first direction X across the heat transfer promoting member 2 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 described above.

The heat transfer promoting member 2 has, for example, two inclined surfaces 25 and two flat surfaces 26 . Each of the inclined surfaces 25 is inclined so as to form an acute angle with respect to the third direction Y. As shown in FIG. An end of an inclined surface 25 on the downstream side is connected to an end of a flat surface 26 on the upstream side. The one inclined surface 25 and the one flat surface 26 and the other inclined surface 25 and the other flat surface 26 are in a line-symmetric relationship with respect to the center line of the heat transfer promoting member 2 extending along the third direction Y, for example. Each of the inclined surfaces 25 is connected to the third end portion 2A. Each flat surface 26 is connected to the fourth end portion 2B. Each inclined surface 25 and each flat surface 26 are, for example, flat surfaces. Each of the inclined surfaces 25 and each of the flat surfaces 26 may be curved surfaces, for example.

The air flowing between the two adjacent heat transfer members 1 in the first direction X tends to concentrate in the first direction X between the two heat transfer members 1 as it goes to the downstream side of the third direction Y. Central Department. Compared with the heat exchanger 100 provided with the heat transfer promotion member 2 shown in FIGS. 2 and 3 , in the heat exchanger provided with the heat transfer promotion member 2 shown in FIG. 16 , the air is more likely to flow downstream in the third direction Y The side flows along the surface of the heat transfer member 1, thereby increasing the heat transfer rate outside the tube.

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

In addition, in the heat exchanger of Embodiment 3 and the above-described modification, the heat transfer member 1 may have the same configuration as any of the modifications shown in FIGS. 5 to 7 . Moreover, the groove part 24 shown in FIG. 15 may be formed in the heat transfer promotion member 2 of the heat exchanger of Embodiment 1 or Embodiment 2.

Implementation type 4. The heat exchanger according to Embodiment 4 has basically the same configuration as the heat exchanger 100 according to Embodiment 1, and exerts the same effect, and differs from the heat exchanger 100 in that the following relational expression is established. Hereinafter, the difference from the heat exchanger 100 will be mainly described.

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

[Formula 1]

The above-mentioned relational expression is derived based on a computational fluid dynamics (Computational Fluid Dynamics: CFD) method.

First, the control equation describing the flow of air in the ventilation path shown in FIG. 17 is a simultaneous equation of a continuous equation and a Navier-Stokes equation, and the SIMPLEC method is used to solve the simultaneous equation equation, thereby deriving the graph shown in FIG. 18 .

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

The vertical axis of the graph shown in FIG. 18 is the ratio of the pressure loss ΔP1 of the air flowing through the ventilation path shown in FIG. 17 to the pressure loss ΔP2 of the air flowing through the ventilation path of the comparative example. The pressure loss ΔP2 is the pressure loss of the air flowing through the ventilation path of the comparative example. The ventilation path of this comparative example is the ventilation path formed in the heat exchanger of the above-mentioned comparative example 2. Specifically, the ventilation path of the comparative example differs from the ventilation path shown in FIG. 17 only in that the heat transfer promoting member 2 is not provided, and the interval in the first direction X between two adjacent heat transfer members is the same as that shown in FIG. 17 . The half value of the pitch p in the first direction X between the two adjacent heat transfer members 1 shown.

As shown in FIG. 18, the ratio ΔP1/ΔP2 changes according to the ratio tP/(p-b). If the ratio ΔP1/ΔP2 is 100% or less, the pressure loss of the air flowing in the ventilation path shown in FIG.

Then, the graph shown in FIG. 18 is derived by arranging the graph shown in FIG. 18 with the ratio L/a and the ratio tP/(p-b) at which the ratio ΔP1/Δp2 becomes 100% or less. The equation in FIG. 19 is a relational expression between the ratio tP/(p-b) and the ratio L/a when the ratio ΔP1/ΔP2 becomes 100%.

In the heat exchanger of Embodiment 4, the above relational expression is established in the range of 0<tP/(p-b)<1, so the pressure loss is suppressed to be equal to or less than that of the above-mentioned comparative example, and the heat transfer performance is comparable. Compared with the above-mentioned comparative example, it is improved. Furthermore, the difference between the heat exchanger of Embodiment 4 and the heat exchanger of Embodiment 2 or 3 may be established only in that the above-mentioned relational expression is established. The average width tP of each heat transfer promoting member 2 shown in FIGS. 12 to 16 is obtained by dividing the cross-sectional area of each heat transfer promoting member 2 perpendicular to the second direction Z by the above-mentioned length L of each heat transfer promoting member 2 . obtained value. In addition, the heat transfer member 1 of the heat exchanger according to Embodiment 4 may have the same configuration as that of each of the heat transfer members 1 shown in FIGS. 5 to 7 .

Implementation type 5. ＜Refrigeration cycle device＞ The refrigeration cycle apparatus 200 of Embodiment 5 includes any one of the heat exchangers of Embodiments 1 to 4. As shown in FIG. 20 , the refrigeration cycle apparatus 200 mainly includes, for example, a heat exchanger 100 , a compressor 111 , a four-way valve 112 , a heat exchanger 113 , an expansion valve 114 , and a blower 115 . The blower 115 sends air to the heat exchanger 100 in the third direction Y. The four-way valve 112 switches between an operation mode in which the heat exchanger 100 functions as an evaporator and an operation mode in which the heat exchanger 100 functions as a condenser.

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

Since the refrigeration cycle apparatus 200 is provided with any one of the heat exchangers of Embodiments 1 to 4, energy saving can be achieved as compared with the refrigeration cycle apparatus provided with the heat exchanger of Comparative Example 1. In addition, since the refrigeration cycle apparatus 200 includes any one of the heat exchangers of Embodiments 1 to 4, compared with the refrigeration cycle apparatus including the heat exchanger of Comparative Example 2, the manufacturing cost and weight can be reduced, and energy saving can be achieved change.

The implementation forms disclosed this time should be considered as examples in all contents and not for limitation. The technical scope shown in the present disclosure is not represented by the description of the above-mentioned embodiments. Rather, it is indicated by the scope of the patent application, and is intended to include the meaning equivalent to the scope of the patent application and all changes within the scope.

1: heat transfer components 1A: First end 1B: Second end 1C: Heat transfer tube part 1D, 1E, 1H: Fins 1F: Hole 1G: Heat transfer tube 2: Heat transfer promoting member 2A: The third end 2B: Fourth end 3: Positioning components 3A: Beam Section 3B, 3C: Connection part 11: The first header 12: Second header 13: The first reinforcement member 14: Second reinforcement member 15: The first outflow and inflow part 16: The second outflow and inflow part 20A: Part 1 20B: Part II 20C: Part III 21,22: Protruding part 21A, 21B, 21C, 22A, 22B, 22C: Flat part 23: Through hole 24: Groove 25: Inclined surface 26: Flat surface 100, 101, 113: Heat Exchangers 111: Compressor 112: Four-way valve 114: Expansion valve 115: Blower 200: Refrigeration cycle device C1, C2: Centerline W1,W2: Interval p: pitch tP: average width b: width a,L: length

FIG. 1 is a perspective view showing a heat exchanger of Embodiment 1. FIG. FIG. 2 is a cross-sectional view taken from the arrow II-II in FIG. 1 . FIG. 3 is a cross-sectional view taken from arrows III-III in FIG. 1 . FIG. 4 is a partial front view of the heat exchanger shown in FIG. 1. FIG. 5 is a partial cross-sectional view showing a first modification of the plurality of heat transfer members of the heat exchanger of Embodiment 1. FIG. 6 is a partial cross-sectional view showing a second modification of the plurality of heat transfer members of the heat exchanger of Embodiment 1. FIG. 7 is a partial cross-sectional view showing a third modification of the plurality of heat transfer members of the heat exchanger of Embodiment 1. FIG. FIG. 8 is a perspective view showing the heat exchanger of Embodiment 2. FIG. FIG. 9 is a cross-sectional view taken from the arrow IX-IX in FIG. 8 . FIG. 10 is a cross-sectional view taken from the arrow X-X in FIG. 8 . FIG. 11 is a partial cross-sectional view viewed from arrows XI-XI in FIGS. 9 and 10 . 12 is a partial cross-sectional view showing the heat transfer promoting member of the heat exchanger of Embodiment 3. FIG. 13 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. 14 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. 15 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. 16 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. FIG. 17 is a partial cross-sectional view showing the heat exchanger of Embodiment 4. FIG. FIG. 18 shows the ratio ΔP1/ΔP2 of the pressure loss ΔP1 of the air circulating in the ventilation path shown in FIG. 17 to the pressure loss ΔP2 of the air circulating in the ventilation path of the comparative example in response to the heat shown in FIG. 17 Graph of the change in the size ratio of each heat transfer member to each heat transfer promoting member of the exchanger. Fig. 19 is a graph derived from the graph shown in Fig. 18, and shows a graph showing the size ratio of each heat transfer member and each heat transfer promoting member so that the ratio of force loss ΔP1/ΔP2 becomes 100% or less . FIG. 20 is a diagram showing a refrigeration cycle apparatus of Embodiment 5. FIG.

1: heat transfer components

2: Heat transfer promoting member

3: Positioning components

11: The first header

12: Second header

13: The first reinforcement member

14: Second reinforcement member

100: heat exchanger

Claims (14)

A heat exchanger comprising: The first header and the second header extend along the first direction and are arranged at intervals in the second direction orthogonal to the first direction; and A plurality of heat transfer members are arranged at intervals in the first direction, and have one end connected to the second direction of the first header, and one end connected to the second direction of the second header. the other end; of which, Each of the first header, the second header, and the plurality of heat transfer members is divided into an inner space for the circulation of the first heat exchange medium and an outer space for the circulation of the second heat exchange medium; The inner space of the first header communicates with the inner space of the second header via the inner space of each of the plurality of heat transfer members; and The heat exchanger further has: At least one heat transfer promoting member is located in the outer space, and is disposed in a central portion between two heat transfer members adjacent to the first direction among the plurality of heat transfer members, and is located along the same length as the first heat transfer member. extending in a third direction orthogonal to the aforementioned second direction; and at least one positioning member, tied to the outer space, positioning the at least one heat transfer promoting member relative to the first header, the second header, and the plurality of heat transfer members; wherein The at least one positioning member is only disposed on the downstream side of the third direction in which the second heat exchange medium circulates than the inner space of each of the plurality of heat transfer members. The heat exchanger of claim 1, wherein the at least one heat transfer promoting member is separate from each of the plurality of heat transfer members. The heat exchanger of claim 1, wherein, The width of the at least one positioning member in the first direction is wider than the interval between two adjacent heat transfer members 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; and The at least one positioning member is connected to the aforementioned plurality of heat transfer members. The heat exchanger according to claim 3, wherein each of the plurality of heat transfer members comprises: a heat transfer tube portion provided with the inner space of each of the plurality of heat transfer members; and fins a portion extending from the heat transfer tube portion toward the downstream side; and The fins of each of the plurality of heat transfer members are formed with holes arranged to overlap each other when viewed from the first direction; The at least one positioning member is inserted through the hole of each of the plurality of heat transfer members. The heat exchanger according to claim 3, wherein the material constituting the at least one positioning member includes at least one of aluminum (Al) and copper (Cu). The heat exchanger according to claim 1, further comprising: a first reinforcing member and a second reinforcing member, wherein the first reinforcing member and the second reinforcing member are connected in the outer space, and the plurality of the plurality of reinforcing members are separated in the first direction. a heat transfer member is configured and connected to each of the first header and the second header; and The width of the at least one positioning member in the first direction is greater than the interval between the first reinforcing member and the second reinforcing member in the first direction; 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; The at least one positioning member is connected to each of the first reinforcing member and the second reinforcing member, and is separated from the plurality of heat transfer members. The heat exchanger according to claim 6, wherein the thermal conductivity of the material constituting the at least one positioning member is lower than the thermal conductivity of the material constituting the plurality of heat transfer members. The heat exchanger according to any one of claims 1 to 7, wherein each of the plurality of heat transfer members has a first one located on the most upstream side in the third direction in which the second heat exchange medium flows. an end portion, and a second end portion located on the most downstream side in the aforementioned third direction; The at least one heat transfer promoting member has a third end portion located on the most upstream side in the third direction, and a fourth end portion located on the most downstream side in the third direction; The third end portion is disposed at the downstream side of the third direction relative to the first end portion. The heat exchanger according to any one of claims 1 to 7, wherein the at least one heat transfer promoting member has: a first portion located on the upstream side in the third direction; and a protruding portion located on the upstream side of the third direction The three directions are located on the downstream side of the first portion, and protrude from the first portion toward the first direction. The heat exchanger according to claim 9, wherein at least one through hole penetrating the protruding portion in the first direction is formed in the at least one heat transfer promoting member. The heat exchanger according to any one of claims 1 to 7, wherein, in a cross section perpendicular to the second direction, at least one heat transfer promoting member is formed on the outer peripheral surface of the at least one heat transfer promoting member facing the first direction. a groove; The at least one groove portion extends along the second direction. The heat exchanger according to any one of claims 1 to 7, wherein the first direction between the at least one heat transfer promoting member and one of the heat transfer members adjacent to the at least one heat transfer promoting member The distance is set to be gradually shortened from the upstream side toward the downstream side in the third direction. The heat exchanger according to any one of claims 1 to 7, wherein the length a of each of the plurality of heat transfer members in the third direction, the length a of the third direction of the at least one heat transfer promoting member The length L, the maximum width b in the first direction of each of the plurality of heat transfer members, the pitch p in the first direction of each of the plurality of heat transfer members, and the distance between the at least one heat transfer promoting member The aforementioned average width tP in the first direction is within the range of 0<tP/(pb)<1, and satisfies the following relational expression: [Equation 1]

. A refrigeration cycle device is provided with: The first heat exchange circuit includes the heat exchanger according to any one of claims 1 to 13, wherein the first heat exchange medium is a refrigerant, the second heat exchange medium is air, and the first heat exchange medium The circuit is for the circulation of the aforesaid refrigerant; and The blower sends the air to the heat exchanger in the third direction.

Images