WO2023233725A1

WO2023233725A1 - Heat exchanger

Info

Publication number: WO2023233725A1
Application number: PCT/JP2023/005565
Authority: WO
Inventors: 紘章中西; 喜之近藤; 吉輝小室; 浩一谷本; 雅哉畑中; 陽一上藤; 駿作江口
Original assignee: 三菱重工業株式会社
Priority date: 2022-05-31
Filing date: 2023-02-16
Publication date: 2023-12-07
Also published as: JP2023176623A

Abstract

A heat exchanger according to the present disclosure comprises: a plurality of heat exchanger tubes that are arranged in a gas flow, extend in a second direction intersecting a first direction in which the gas flows, and are arrayed in spaced relation to each other; and a plurality of plate fins that extend in the first direction, and are disposed so as to straddle the plurality of heat exchanger tubes, and are arrayed spaced apart from each other in the second direction. The plate fins are provided with a plurality of slits that extend in a third direction intersecting both the first direction and the second direction and that are arrayed spaced apart in the first direction. The plurality of slits each have a zigzag shape that extends diagonally toward the upstream side and the downstream side alternately in the first direction in which the gas flows, and the slits have identical intervals at which the zigzag shape is repeated.

Description

Heat exchanger

The present disclosure relates to heat exchangers.
This application claims priority to Japanese Patent Application No. 2022-089006 filed in Japan on May 31, 2022, the contents of which are incorporated herein.

In a so-called fin-tube type heat exchanger equipped with plate fins and heat transfer tubes, it is desired to improve the heat transfer coefficient in the plate fins in order to increase heat exchange efficiency. Patent Document 1 discloses that plate fins around a heat transfer tube are cut and raised to form guide fins that are inclined with respect to the gas flow direction, and the guide fins guide the gas flow to a downstream region of the heat transfer tube in the gas flow direction. The configuration is disclosed.

Patent Document 2 discloses that a cutout portion that widens toward the upstream side in the gas flow direction is provided at each position equidistant from two adjacent heat exchanger tubes among the edge portions of the plate fins on the upstream side in the gas flow direction. A configuration is disclosed in which ventilation resistance is reduced by providing a.

Patent Document 3 discloses that plate fins are cut so that curved lines or bent lines are continuous in the row direction of the heat exchanger tubes at a distance that is approximately half the distance between the heat exchanger tubes in the row direction of the heat exchanger tubes, and the unevenness engages with each other as a whole. A configuration is disclosed. In Patent Document 3, by forming the plate fins in this way, it is possible to reduce the variation in heat conduction distance from each heat transfer tube to the edge of the plate fins without changing the area of the plate fins, thereby increasing the fin efficiency. We are trying to improve.

International Publication No. 2007/004457 Japanese Patent No. 3910475 Japanese Patent Application Publication No. 2001-033183

In fin-tube heat exchangers such as those described in Patent Documents 1 to 3, the amount of heat exchanged can be efficiently increased by increasing the heat transfer coefficient from the gas flow to the plate fins. That is, in the heat exchanger described above, the heat exchange amount can be easily improved by expanding the heat transfer area. However, when the heat transfer area is expanded, there is a problem that the heat exchanger becomes larger and it becomes difficult to reduce the weight of the heat exchanger.
The present disclosure has been made in view of the above circumstances, and provides a heat exchanger that can reduce the weight while increasing the amount of heat exchanged.

In order to solve the above problems, the following configuration is adopted.
According to a first aspect of the present disclosure, the heat exchanger is disposed in a gas flow, and includes a plurality of heat exchangers arranged at intervals, extending in a second direction intersecting a first direction in which the gas flows. a heat tube; and a plurality of plate fins that extend in the first direction, are provided so as to straddle the plurality of heat transfer tubes, and are arranged at intervals in the second direction; a plurality of slits extending in a third direction that intersects both one direction and the second direction and arranged at intervals in the first direction; It has a zigzag shape that extends obliquely toward the upstream side and the downstream side in the first direction, and the periods of the zigzag shapes are the same.

According to a second aspect of the present disclosure, the heat exchanger is disposed in the gas flow and extends in a second direction intersecting the first direction of the gas flow, and mutually extends in the first direction and the first direction. a plurality of heat exchanger tubes staggered alternately in a third direction, which is a direction intersecting both the first direction and the second direction; a plurality of plate fins arranged at intervals in the second direction, the plate fins penetrating upstream of the plurality of heat transfer tubes in the first direction in the second direction; Equipped with a hole.

According to the heat exchanger according to the present disclosure, it is possible to reduce the weight while increasing the amount of heat exchange.

FIG. 1 is a diagram showing a schematic configuration of a heat exchanger in a first embodiment of the present disclosure. 2 is a sectional view taken along line II-II in FIG. 1. FIG. FIG. 3 is a sectional view corresponding to FIG. 2 of a heat exchanger according to a second embodiment of the present disclosure. FIG. 4 is an enlarged view of the main part of FIG. 3; FIG. 5 is an enlarged view corresponding to FIG. 4 of a heat exchanger in a first modification of the second embodiment of the present disclosure. FIG. 5 is an enlarged view corresponding to FIG. 4 of a heat exchanger in a second modified example of the second embodiment of the present disclosure. FIG. 5 is an enlarged view corresponding to FIG. 4 of a heat exchanger in a third modification of the second embodiment of the present disclosure. FIG. 5 is an enlarged view corresponding to FIG. 4 of a heat exchanger in a fourth modification of the second embodiment of the present disclosure. FIG. 3 is a sectional view corresponding to FIG. 2 of a heat exchanger in a fifth modification of the second embodiment of the present disclosure. 2 is a sectional view taken along line XX in FIG. 1. FIG. FIG. 11 is a sectional view corresponding to FIG. 10 of a heat exchanger according to a fourth embodiment of the present disclosure. FIG. 12 is an enlarged view of the main part of FIG. 11; FIG. 13 is an enlarged view corresponding to FIG. 12 of a heat exchanger in a first modified example of the fourth embodiment of the present disclosure. FIG. 13 is an enlarged view corresponding to FIG. 12 of a heat exchanger in a second modified example of the fourth embodiment of the present disclosure. FIG. 13 is an enlarged view corresponding to FIG. 12 of a heat exchanger in a third modified example of the fourth embodiment of the present disclosure. FIG. 13 is an enlarged view corresponding to FIG. 12 of a heat exchanger in a fourth modification of the fourth embodiment of the present disclosure.

≪First embodiment≫
Next, a heat exchanger according to a first embodiment of the present disclosure will be described based on the drawings.
FIG. 1 is a diagram showing a schematic configuration of a heat exchanger in a first embodiment of the present disclosure.
As shown in FIG. 1, the heat exchanger 101 of the first embodiment exchanges heat between gas G and refrigerant R, which are supplied from the outside. The heat exchanger 101 includes heat exchanger tubes 102 and plate fins 103. In addition, in the following description, the flow of the gas G heat-exchanged within a heat exchanger is simply called a gas flow. Further, the direction in which the gas G flows is referred to as a first direction D1, the upstream side of the gas flow is referred to as a first direction upstream side D1u, and the downstream side is referred to as a first direction downstream side D1d.

The heat exchanger tube 102 is placed in the gas flow. The heat exchanger tube 102 extends in a second direction D2 that intersects the first direction D1. A plurality of heat exchanger tubes 102 are arranged at intervals in the gas flow. A heat exchanger tube group 105 is constituted by a plurality of these heat exchanger tubes 102 arranged. The heat exchanger tubes 102 of the heat exchanger tube group 105 illustrated in this embodiment all have the same shape, and the refrigerant R is circulated inside the heat exchanger tubes 102 . Although the second direction D2 in this embodiment is exemplified as being perpendicular to the first direction D1, it is not limited to being perpendicular. In addition, in the following description, the direction which intersects the first direction D1 and the second direction D2 is called the third direction D3 (refer FIG. 2).

FIG. 2 is a sectional view taken along line II-II in FIG.
As shown in FIG. 2, the heat exchanger tubes 102 constituting the heat exchanger tube group 105 are arranged in a so-called staggered arrangement. In other words, the heat exchanger tubes 102 of the heat exchanger tube group 105 are arranged in a rhombic lattice. That is, a plurality of heat exchanger tubes 102 of the heat exchanger tube group 105 are arranged so as to be alternately shifted in the first direction D1 and the third direction D3.

The heat exchanger tubes 102 of the heat exchanger tube group 105 of this embodiment form a first row C1 and a second row C2 extending in the first direction D1, and these first row C1 and second row C2 are arranged in a third row. They are arranged alternately in direction D3. Moreover, the heat exchanger tubes 102 in the first row C1 are arranged at intervals of a distance L1 in the first direction D1. The heat exchanger tubes 102 in the second row C2 are arranged at intervals of a distance L1 in the first direction D1, and are spaced apart by a distance L2, which is half the distance L1, from the position of the heat exchanger tubes 102 in the first row C1. They are arranged shifted in one direction D1. In the following description, the heat exchanger tubes 102 arranged in the first direction D1 are sometimes referred to as rows (C), and those arranged in the third direction D3 are sometimes referred to as stages (S). The heat exchanger tube group 105 of this embodiment includes heat exchanger tubes 102 in multiple rows and stages. Further, for convenience of illustration, in FIG. 2, in order to indicate the rows C (C1, C2) and the stages S, the axes passing through the centers of the heat exchanger tubes 102 constituting each are labeled.

The plate fins 103 extend in the first direction D1 and are provided so as to straddle the plurality of heat exchanger tubes 102. A plurality of plate fins 103 are arranged at intervals in the second direction D2 (see FIG. 1). The plurality of plate fins 103 in this embodiment are each formed into a thin plate shape and arranged at equal intervals in the second direction D2. The above-described gas flow flows between these plate fins 103 from the upstream side D1u in the first direction to the downstream side D1d in the first direction.

The plate fin 103 includes a slit 104. The slit 104 extends in the third direction D3. More specifically, the slit 104 is formed to cross the plate fin 103 in the third direction D3. A plurality of slits 104 are arranged at intervals in the first direction D1. These plurality of slits 104 penetrate in the second direction D2, which is the thickness direction of the plate fin 103. The slit 104 of this embodiment is provided for each two-stage heat exchanger tube 102 adjacent in the first direction D1 of the heat exchanger tube group 105.

The plurality of slits 104 have a zigzag shape that alternately extends diagonally on the upstream side D1u in the first direction and on the downstream side D1d in the first direction. These plurality of slits 104 have the same zigzag period. In other words, the plurality of slits 104 are located at, for example, the position of the convex portion 106 formed in a convex shape toward the first direction upstream side D1u in the third direction D3, and the first direction downstream side D1d in the third direction D3. The positions of the concave portions 107 formed in a concave shape toward each other coincide with each other. Further, the zigzag period of the slits 104 illustrated in this embodiment matches the period at which the heat exchanger tubes 102 are arranged at regular intervals in the third direction D3. Further, the amplitude of the zigzag shape of the slit 104 is constant.

The slit 104 extends toward the upstream side D1u in the first direction at a position between the heat transfer tubes 102 adjacent in the third direction D3 of the stage S adjacent to the upstream side D1u in the first direction. Further, the slit 104 extends toward the downstream side D1d in the first direction at a position between the heat exchanger tubes 102 adjacent in the third direction D3 of the stage S adjacent to the downstream side D1d in the first direction. In this embodiment, the positions of the zigzag-shaped tops t in the third direction D3 correspond to the positions of the heat exchanger tubes 102 in the third direction D3.

More specifically, in the present embodiment, the folded positions of the convex portions 106, which are the tops t of the slits 104 in the third direction D3, respectively coincide with the center positions of the heat exchanger tubes 102 in the first row C1. . Similarly, the folded positions of the recesses 107, which are the tops t of the slits 104 in the third direction D3, respectively coincide with the center positions of the heat exchanger tubes 102 in the second row C2. Further, in the present embodiment, the distances in the first direction D1 between the tops t and the heat exchanger tubes 102 arranged closest to the tops t in the first direction D1 are all equal distances. . Note that the folded positions of these convex portions 106 and recessed portions 107 are not limited to being coincident with the center position of the heat exchanger tube 102, and may be slightly shifted from the center position of the heat exchanger tube 102, for example.

Of the slits 104 exemplified in this embodiment, the portion extending toward the upstream side D1u in the first direction is a portion of the slit 104 that is located at the first direction from the center of the heat exchanger tube 102 of the stage S adjacent to the upstream side D1u of the slit 104 in the first direction. It extends to the upstream side D1u in the direction. On the other hand, the portion of the slit 104 extending toward the upstream side D1u in the first direction extends to the upstream side D1u in the first direction from the heat exchanger tube 102 of the stage adjacent to the upstream side D1u in the first direction of the slit 104. has not extended. That is, the slit 104 is located at the same position as the point P1 of the heat exchanger tube 102 of the stage S adjacent to the upstream side D1u in the first direction, which is the most upstream side D1u in the first direction, or at the downstream side D1d in the first direction.

Similarly, the portion of the slit 104 illustrated in this embodiment that extends toward the downstream side D1d in the first direction is from the center of the heat exchanger tube 102 of the stage S adjacent to the downstream side D1d of the slit 104 in the first direction. It also extends to the downstream side D1d in the first direction. On the other hand, the portion of the slit 104 extending toward the downstream side D1d in the first direction extends further downstream D1d in the first direction than the heat exchanger tube 102 of the stage S adjacent to the downstream side D1d of the slit 104 in the first direction. do not have. That is, the slit 104 is located at the same position as the point P2 of the heat exchanger tube 102 of the stage S adjacent to the downstream side D1d in the first direction, which is the most downstream side D1d in the first direction, or at the upstream side D1u in the first direction.

(effect)
In the heat exchanger 101 of the first embodiment, the plate fins 103 are provided with a plurality of slits 104 extending in the third direction D3 and arranged at intervals in the first direction D1. On the other hand, it has a zigzag shape that extends diagonally alternately toward the upstream side D1u and the first direction downstream side D1d, and the periods of the zigzag shapes are the same.
Therefore, when the gas G flows from the upstream side D1u in the first direction to the downstream side D1d in the first direction, the gas flow is disturbed by the slit 104, and the temperature boundary layer of the gas flow can be thinned. It is possible to increase the amount of heat exchange by making the temperature gradient steeper. Furthermore, by forming the slits 104 in a zigzag shape, the length of the slits 104 can be increased compared to when the slits 104 are formed in a straight line, so that the weight of the plate fin 103 can be reduced. I can do it. Furthermore, since the zigzag periods of the plurality of slits 104 extending in the third direction D3 are the same, it is possible to equalize the distance between adjacent slits 104 in the first direction D1, and also to improve gas flow and plate fins. It is possible to secure a contact area of As a result, it is possible to suppress a decrease in the amount of heat exchange while reducing the development of a temperature boundary layer.

In the heat exchanger 101 of the first embodiment, the heat exchanger tubes 102 are arranged in a staggered manner, and the slits 104 are adjacent to the slits 104 on the upstream side D1u in the first direction, and the plurality of heat exchanger tubes 102 are arranged in the third direction D3. The heat pipes 102 extend toward the upstream side D1u in the first direction.
Thereby, when the heat exchanger tubes 102 are arranged in a staggered manner, the heat exchanger tubes 102 disposed on the upstream side D1u in the first direction by one stage than the heat exchanger tubes 102 in the stage adjacent to the upstream side D1u in the first direction; The distance from the slit 104 on the first direction downstream side D1d of 102 can be reduced. Therefore, it is possible to suppress the development of a temperature boundary layer on the downstream side D1d of the heat exchanger tube 102 in the first direction, so that the amount of heat exchange can be increased.

In the heat exchanger 101 of the first embodiment, the position of the zigzag top portion t in the third direction D3 further coincides with the position of the heat exchanger tube 102 in the third direction D3.
Thereby, the distances between the staggered heat exchanger tubes 102 and the slits 104 can be made even more uniform.

In the heat exchanger 101 of the first embodiment, the slits 104 are further provided for each two-stage heat exchanger tube 102 arranged in the third direction D3 and adjacent in the first direction D1.
Thereby, the amount of heat exchange can be increased more effectively.

(Modified example of first embodiment)
The width dimension of the slit 104 in the first direction D1 in the first embodiment described above may be made narrower as the flow rate of the gas flow is higher, and wider as the flow rate of the gas flow is lower, for example. By doing so, it is possible to more effectively suppress the development of the temperature boundary layer even when the flow rate of the gas flow is low.

≪Second embodiment≫
Next, a second embodiment of the present disclosure will be described based on the drawings. The heat exchanger 201 of this second embodiment has a protrusion added to the heat exchanger 101 of the first embodiment described above. Therefore, while referring to FIG. 1, the same parts as those in the first embodiment described above will be described with the same reference numerals, and explanations that overlap with those in the first embodiment will be omitted.

FIG. 3 is a sectional view corresponding to FIG. 2 of a heat exchanger according to a second embodiment of the present disclosure.
As shown in FIGS. 1 and 3, the heat exchanger 201 in the second embodiment, like the heat exchanger 101 in the first embodiment described above, exchanges gas G and refrigerant R supplied from the outside, respectively. exchange heat. Heat exchanger 201 includes heat exchanger tubes 102, plate fins 103, and protrusions 110.

FIG. 4 is an enlarged view of the main part of FIG. 3.
As shown in FIGS. 3 and 4, the protrusion 110 protrudes from the plate fin 103 in the second direction D2 and extends in the first direction D1. The protrusion 110 of this embodiment extends so as to straddle adjacent plate fins 103 in the second direction D2. Two protrusions 110 are provided in pairs on the first direction upstream side D1u and the first direction downstream side D1d of the heat exchanger tube 102, respectively. The two protrusions 110 provided on the upstream side D1u of the heat exchanger tube 102 in the first direction are arranged at a distance L3 in the third direction D3. Similarly, the two protrusions 110 provided on the first direction downstream side D1d of the heat exchanger tube 102 are also arranged with an interval L3 in the third direction D3.

The interval L3 is smaller than the outer diameter R1 of the heat exchanger tube 102. In this embodiment, the interval L3 is exemplified to be half the outer diameter R1 of the heat exchanger tubes 102. Furthermore, the length of the protrusion 110 in the first direction D1 may be any length as long as it can protrude beyond the heat exchanger tube 102 in the first direction. Further, the thickness of the protrusion 110 in the third direction D3 is smaller than the thickness of the tube wall of the heat exchanger tube 102. In this embodiment, a case is illustrated in which the thickness of the protrusion 110 is about half the thickness of the tube wall of the heat exchanger tube 102, but the thickness is not limited to this.

In the present embodiment, a case has been described in which the pair of protrusions 110 are arranged with the same distance L3, but the distance between the pair of protrusions 110 is the first direction upstream side D1u and the first direction downstream side D1d. It is also possible to set different intervals between the two. Further, although the protrusion 110 of the second embodiment is formed in a flat plate shape extending in the first direction D1 when viewed from the second direction D2, the protrusion 110 is not limited to a flat plate shape, and may be slightly curved, for example. It may have a shape that looks like this.

(effect)
In the second embodiment, the heat exchanger 201 includes a pair of protrusions 110 on the first direction upstream side D1u and the first direction downstream side D1d of the heat exchanger tube 102, respectively.
As a result, the gas flows in the first direction D1 outside the third direction D3 of the pair of protrusions 110, thereby reducing the flow path area of the first direction upstream side D1u and the first direction upstream side D1u of the heat exchanger tube 102. Gas flow rate can be increased. Therefore, in addition to suppressing the development of the temperature boundary layer by the slits 104, it is possible to further suppress the development of the temperature boundary layer on the plate fins 103.

Furthermore, since the heat transfer area of the heat transfer tube 102 can be expanded by the protrusion 110, the amount of heat exchange can be further increased.

≪First modification of second embodiment≫
FIG. 5 is an enlarged view corresponding to FIG. 4 of a heat exchanger in a first modified example of the second embodiment of the present disclosure.
The case where the projection 110 of the second embodiment described above is formed integrally with the heat exchanger tube 102 has been described. However, the protrusion 110 is not limited to a configuration in which it is formed integrally with the heat exchanger tube 102. For example, the protrusion 110 shown in FIG. 5 may be formed by cutting and raising the plate fin 103.

<<Second modification of the second embodiment>>
FIG. 6 is an enlarged view corresponding to FIG. 4 of a heat exchanger in a second modified example of the second embodiment of the present disclosure.
Since the protrusion 110 of the second embodiment described above is formed integrally with the heat exchanger tube 102, it is necessary to attach the protrusion 110 by welding, adhesive, etc. after the heat exchanger tube 102 is penetrated through the plate fin 103.
However, as in a second modified example of the second embodiment shown in FIG. Even after the heat exchanger tubes 102 are attached, it is possible to penetrate the plate fins 103. Thereby, the heat exchanger 201 provided with the protrusion 110 can be easily assembled.

<<Third modification of the second embodiment>>
FIG. 7 is an enlarged view corresponding to FIG. 4 of a heat exchanger in a third modification of the second embodiment of the present disclosure.
Although the projection 110 of the second embodiment described above is formed integrally with the heat exchanger tube 102, the structure is not limited to this.
For example, as in a third modification of the second embodiment shown in FIG. 7, a gap G1 through which gas can flow may be provided between the protrusion 110 and the heat exchanger tube 102. The length of the gap G1 in the first direction D1 may be approximately the thickness of the tube wall of the heat exchanger tube 102 described above. Note that the protrusion 110 of the third modification of the second embodiment may be formed by cutting and raising it from the plate fin 103 similarly to the protrusion 110 of the first modification of the second embodiment, for example. As in the second modification of the second embodiment, a protrusion through hole through which the protrusion 110 can pass is provided, the protrusion 110 is inserted into the protrusion through hole, and then the protrusion 110 and the plate fin 103 are fixed by welding, adhesive, etc. You may also do so.

By configuring as in the third modification of the second embodiment, for example, even if the plate fins 103 around the heat exchanger tubes 102 are burred, the protrusions 110 can be easily provided. becomes possible. Furthermore, since the gas G flows through the gap G1 between the protrusion 110 and the heat transfer tube 102, the stagnation area of the gas G between the pair of protrusions 110 is reduced, and as a result, it is possible to promote the heat transfer effect. Become.

≪Fourth modification of the second embodiment≫
FIG. 8 is an enlarged view corresponding to FIG. 4 of a heat exchanger in a fourth modification of the second embodiment of the present disclosure.
In the second embodiment described above, a case has been described in which the protrusions 110 are provided on the first direction upstream side D1u and the first direction downstream side D1d of the heat exchanger tubes 102, but for example, among the heat exchanger tube group 105, the first direction For some of the heat exchanger tubes 102 on the downstream side D1d, a protrusion 112 protrudes in a direction away from the heat exchanger tubes 102 in the third direction D3, as in the fourth modification of the second embodiment shown in FIG. may be provided. By providing such a protrusion 112, the heat transfer area of the heat transfer tube 102 can be expanded, so especially on the downstream side D1d in the first direction where the temperature difference during heat exchange between the gas G and the refrigerant R is small. It becomes possible to ensure the amount of heat transfer in some of the heat exchanger tubes 102. Note that the shape of the protrusion 112 may be any shape that can expand the heat transfer area, and is not limited to the shape shown in FIG. 8 .

<<Fifth modification of the second embodiment>>
FIG. 9 is a sectional view corresponding to FIG. 2 of a heat exchanger in a fifth modification of the second embodiment of the present disclosure.
In the second embodiment described above, the case where the heat exchanger tubes 102 are arranged in a staggered manner when viewed from the second direction D2 has been described, but the heat exchanger tubes 102 are not limited to the case where they are arranged in a staggered manner. For example, as in a fifth modification of the second embodiment shown in FIG. 9, the heat exchanger tubes 102 may be arranged in a so-called square lattice or rectangular lattice when viewed from the second direction D2.
Furthermore, in the case of the staggered arrangement, the slits 104 are provided at intervals in the first direction D1 for every two stages S of the heat exchanger tubes 102 arranged in the third direction D3. However, as shown in FIG. 9, in the case of a square lattice or rectangular lattice arrangement, the zigzag-shaped slits 104 may be provided at intervals in the first direction D1 for each stage S of the heat exchanger tubes 102.
By arranging the slits 104 in this way, in the case of a square lattice or rectangular lattice arrangement as described above, the heat transfer coefficient in the first direction D1, which is the gas flow direction in the heat exchanger 201, is averaged. It becomes possible to efficiently exchange heat.

(Other variations of the second embodiment)
Similarly to the first embodiment, the width dimension in the first direction D1 of the slit 104 in the second embodiment and each modification described above is narrower as the flow rate of the gas flow is higher, and wider as the flow rate of the gas flow is lower. It may also be formed. Further, the length of the protrusion 110 in the first direction D1 may be formed to be shorter as the flow rate of the gas flow is higher, and longer as the flow rate of the gas flow is lower. By doing so, it becomes possible to more effectively suppress the development of the temperature boundary layer even when the flow rate of the gas flow is low.

≪Third embodiment≫
Next, a heat exchanger according to a third embodiment of the present disclosure will be described based on the drawings. The heat exchanger 301 of this third embodiment differs from the heat exchanger 101 of the first embodiment described above in the shape of plate fins. Therefore, the description will be made with reference to FIG. 1 and with the same reference numerals attached to the same parts as in the first embodiment described above.

As shown in FIG. 1, the heat exchanger 301 of the third embodiment exchanges heat between gas G and refrigerant R supplied from the outside. The heat exchanger 301 includes heat exchanger tubes 102 and plate fins 303. Note that the flow of gas G that undergoes heat exchange within the heat exchanger 301 is simply referred to as a gas flow. Further, the direction in which the gas G flows is referred to as a first direction D1, the upstream side of the gas flow is referred to as a first direction upstream side D1u, and the downstream side is referred to as a first direction downstream side D1d.

The heat exchanger tube 102 is placed in the gas flow. The heat exchanger tube 102 extends in a second direction D2 that intersects the first direction D1. A plurality of heat transfer tubes 102 are arranged at intervals in the gas flow. A heat exchanger tube group 105 is constituted by a plurality of these heat exchanger tubes 102 arranged. The heat exchanger tubes 102 of the heat exchanger tube group 105 illustrated in this embodiment all have the same shape, and the refrigerant R is circulated inside the heat exchanger tubes 102 . Although the second direction D2 in this embodiment is exemplified as being perpendicular to the first direction D1, it is not limited to being perpendicular. In addition, in the following description, the direction which intersects the first direction D1 and the second direction D2 is called the third direction D3.

FIG. 10 is a sectional view taken along line XX in FIG. 1.
As shown in FIG. 10, the heat exchanger tubes 102 constituting the heat exchanger tube group 105 are arranged in a so-called staggered arrangement. In other words, the heat exchanger tubes 102 of the heat exchanger tube group 105 are arranged in a rhombic lattice arrangement with respect to the first direction D1. That is, a plurality of heat exchanger tubes 102 of the heat exchanger tube group 105 are arranged so as to be alternately shifted in the first direction D1 and the third direction D3.

The heat exchanger tubes 102 of the heat exchanger tube group 105 of this embodiment form a first row C1 and a second row C2 extending in the first direction D1, and these first row C1 and second row C2 are arranged in a third row. They are arranged alternately in direction D3. Moreover, the heat exchanger tubes 102 in the first row C1 are arranged at intervals of a distance L1 in the first direction D1. The heat exchanger tubes 102 in the second row C2 are arranged at intervals of a distance L1 in the first direction D1, and are spaced apart by a distance L2, which is half the distance L1, from the position of the heat exchanger tubes 102 in the first row C1. They are arranged shifted in one direction D1. In the following description, the heat exchanger tubes 102 arranged in the first direction D1 are sometimes referred to as rows (C), and those arranged in the third direction D3 are sometimes referred to as stages (S). The heat exchanger tube group 105 of this embodiment includes heat exchanger tubes 102 in multiple rows and stages. In addition, although only two rows of heat exchanger tubes 102 are shown in this third embodiment, three or more rows may be provided.

The plate fins 303 extend in the first direction D1 and are provided so as to straddle the plurality of heat exchanger tubes 102. A plurality of plate fins 103 are arranged at intervals in the second direction D2. The plurality of plate fins 103 in this embodiment are each formed into a thin plate shape and arranged at equal intervals in the second direction D2. The above-described gas flow flows between these plate fins 103 from the upstream side D1u in the first direction to the downstream side D1d in the first direction.

The plate fin 103 includes a hole 304 penetrating in the second direction D2. The holes 304 are formed on the upstream side D1u of the plurality of heat exchanger tubes 102 in the first direction, respectively. The hole 304 in this third embodiment has a rectangular shape whose longitudinal direction is the first direction D1 when viewed from the second direction D2. Furthermore, the holes 304 in this third embodiment are formed on the extension line of the axis passing through the center of the rectangular shape in the third direction D3 when viewed from the second direction D2, in the heat exchanger tube 102 adjacent to the downstream side D1d in the first direction. The center is located. Further, the center position of the hole 304 in this third embodiment is the same in the first direction D1 as the center position of the heat exchanger tube 102 in the row C adjacent in the third direction D3 to the row C in which the hole 304 is formed. Although the center positions are shown as examples, these center positions may be shifted in the first direction D1.

The hole 304 is formed in a region of the plate fin 303 that has been found to have a small contribution to heat transfer through optimization analysis performed in advance. In this third embodiment, the short side of the rectangular hole 304 is formed to be smaller than the outer diameter R1 of the heat exchanger tube 102. Further, in this third embodiment, the short side of the rectangular hole 304 is slightly shorter than half the outer diameter of the heat exchanger tube 102, and the longer side of the hole 304 is slightly shorter than the inner diameter R2 of the heat exchanger tube 102. This shows the case where it is formed small. The shape of the hole 304 is not limited to the above shape and size as long as it includes the region of the plate fin 303 that has been found to have a small contribution to heat transfer through optimization analysis or the like. When the shape of the hole 304 is made into the above-mentioned rectangular shape, it is advantageous in that it can be easily machined.

(effect)
In the heat exchanger 301 of the third embodiment, the plurality of heat exchanger tubes 102 are arranged in the gas flow, extend in the second direction D2, and are arranged in a staggered manner alternately shifted from each other in the first direction D1 and the third direction D3. It is said that The plate fins 303 extend in the first direction D1 and are provided so as to straddle the plurality of heat transfer tubes 102, and are arranged in plurality at intervals in the second direction D2. The plate fin 303 is provided with a hole 304 penetrating in the second direction D2 on the upstream side D1u of the plurality of heat exchanger tubes 102 in the first direction.
As a result, when the gas G flows from the upstream side D1u in the first direction to the downstream side D1d in the first direction, the gas flow is disturbed by the holes 304, and the temperature boundary layer of the gas flow can be thinned, so the plate fin The temperature gradient from 303 can be made steeper to increase the amount of heat exchange. Furthermore, since the holes 304 penetrate the plate fins 303, the weight of the plate fins 303 can be reduced by the opening area of the holes 304 compared to a case where the holes 304 are not provided. As a result, it is possible to suppress a decrease in the amount of heat exchange while reducing the development of a temperature boundary layer.

Further, since it is only necessary to form the hole 304 penetrating the plate fin 303 in the second direction D2, manufacturing is easy and the processing process can be prevented from becoming complicated.

≪Fourth embodiment≫
Next, a fourth embodiment of the present disclosure will be described based on the drawings. The heat exchanger 401 of the fourth embodiment has a protrusion added to the heat exchanger 301 of the third embodiment described above. Therefore, while referring to FIG. 1, the same parts as those in the third embodiment described above will be described with the same reference numerals, and explanations that overlap with those in the third embodiment will be omitted.

FIG. 11 is a sectional view corresponding to FIG. 10 of the heat exchanger in the fourth embodiment of the present disclosure. As shown in FIGS. 1 and 11, the heat exchanger 401 in the fourth embodiment, like the heat exchanger 101 in the first embodiment described above, exchanges gas G and refrigerant R supplied from the outside, respectively. exchange heat. Heat exchanger 401 includes heat exchanger tubes 102, plate fins 303, and protrusions 110.

FIG. 12 is an enlarged view of the main part of FIG. 11.
As shown in FIGS. 11 and 12, the protrusion 110 protrudes from the plate fin 303 in the second direction D2 and extends in the first direction D1. The protrusion 110 of the fourth embodiment extends so as to straddle adjacent plate fins 303 in the second direction D2. Two protrusions 110 are provided in pairs on the first direction upstream side D1u and the first direction downstream side D1d of the heat exchanger tube 102, respectively. The two protrusions 110 provided on the upstream side D1u of the heat exchanger tube 102 in the first direction are arranged at a distance L3 in the third direction D3. Similarly, the two protrusions 110 provided on the first direction downstream side D1d of the heat exchanger tube 102 are also arranged with an interval L3 in the third direction D3.

The interval L3 is smaller than the outer diameter of the heat exchanger tube 102. In this embodiment, the interval L3 is exemplified to be half the outer diameter of the heat exchanger tubes 102. Furthermore, the length of the protrusion 110 in the first direction D1 may be any length as long as it can protrude beyond the heat exchanger tube 102 in the first direction. Further, the thickness of the protrusion 110 in the third direction D3 is smaller than the thickness of the tube wall of the heat exchanger tube 102. In this embodiment, a case is illustrated in which the thickness of the protrusion 110 is about half the thickness of the tube wall of the heat exchanger tube 102, but the thickness is not limited to this.

In the fourth embodiment, a case has been described in which the pair of protrusions 110 are arranged with the same distance L3, but the distance between the pair of protrusions 110 is on the upstream side D1u in the first direction and on the downstream side in the first direction. The spacing may be different between the side D1d and the side D1d. Further, although the protrusion 110 of the fourth embodiment is formed in a flat plate shape extending in the first direction D1 when viewed from the second direction D2, the protrusion 110 is not limited to a flat plate shape, and may be slightly curved, for example. It may have a shape that looks like this.

(effect)
In the fourth embodiment, the heat exchanger 401 includes a pair of protrusions 110 on the first direction upstream side D1u and the first direction downstream side D1d of the heat exchanger tube 102, respectively.
As a result, the gas flows in the first direction D1 outside the third direction D3 of the pair of protrusions 110, thereby reducing the flow path area of the first direction upstream side D1u and the first direction upstream side D1u of the heat exchanger tube 102. Gas flow rate can be increased. Therefore, in addition to suppressing the development of the temperature boundary layer by the holes 304, it is possible to further suppress the development of the temperature boundary layer on the plate fins 103.

<<First modification of the fourth embodiment>>
FIG. 13 is an enlarged view corresponding to FIG. 12 of a heat exchanger in a first modified example of the fourth embodiment of the present disclosure.
The case where the projection 110 of the fourth embodiment described above is formed integrally with the heat exchanger tube 102 has been described. However, the protrusion 110 is not limited to a configuration in which it is formed integrally with the heat exchanger tube 102. For example, the protrusion 110 shown in FIG. 13 may be formed by cutting and raising the plate fin 303.

<<Second modification of the fourth embodiment>>
FIG. 14 is an enlarged view corresponding to FIG. 12 of a heat exchanger in a second modified example of the fourth embodiment of the present disclosure.
Since the protrusion 110 of the fourth embodiment described above is formed integrally with the heat exchanger tube 102, it is necessary to attach the protrusion 110 by welding, adhesive, etc. after the heat exchanger tube 102 is penetrated through the plate fin 303.
However, as in the second modified example of the fourth embodiment shown in FIG. 14, by forming a protrusion through hole 111 through which the protrusion 110 can pass in the second direction D2, the protrusion 110 can be inserted into the heat exchanger tube 102. Even after the heat exchanger tubes 102 are attached, it is possible to penetrate the plate fins 303. Thereby, the heat exchanger 401 provided with the protrusion 110 can be easily assembled.

<<Third modification of the fourth embodiment>>
FIG. 15 is an enlarged view corresponding to FIG. 12 of a heat exchanger in a third modification of the fourth embodiment of the present disclosure.
Although the projection 110 of the fourth embodiment described above is formed integrally with the heat exchanger tube 102, it is not limited to this configuration.
For example, as in a third modification of the fourth embodiment shown in FIG. 15, a gap G1 through which gas can flow may be provided between the protrusion 110 and the heat exchanger tube 102. The length of the gap G1 in the first direction D1 may be approximately the thickness of the tube wall of the heat exchanger tube 102 described above. Note that the protrusion 110 of the third modification of the fourth embodiment may be formed by cutting and raising it from the plate fin 303 similarly to the protrusion 110 of the first modification of the fourth embodiment, for example. , as in the second modification of the fourth embodiment, a protrusion through hole through which the protrusion 110 can pass is provided, the protrusion 110 is inserted into the protrusion through hole, and then the protrusion 110 and the plate fin 303 are fixed by welding, adhesive, etc. You may also do so.

By configuring as in the third modification of the fourth embodiment, for example, even if the plate fins 303 around the heat exchanger tubes 102 are burred, the protrusions 110 can be easily provided. becomes possible. Further, since gas flows through the gap G1 between the protrusions 110 and the heat transfer tube 102, the gas stagnation area between the pair of protrusions 110 is reduced, and as a result, it is possible to promote the heat transfer effect.

≪Fourth modification of the fourth embodiment≫
FIG. 16 is an enlarged view corresponding to FIG. 12 of a heat exchanger in a fourth modification of the fourth embodiment of the present disclosure.
In the fourth embodiment described above, the case where the protrusions 110 are provided on the upstream side D1u in the first direction and the downstream side D1d in the first direction of the heat exchanger tubes 102 has been described. For some of the heat exchanger tubes 102 on the downstream side D1d, a protruding portion 112 protrudes in a direction away from the heat exchanger tubes 102 in the third direction D3, as in the fourth modification of the fourth embodiment shown in FIG. may be provided. By providing such a protrusion 112, the heat transfer area of the heat transfer tube 102 can be expanded, so especially on the downstream side D1d in the first direction where the temperature difference during heat exchange between the gas G and the refrigerant R is small. It becomes possible to ensure the amount of heat transfer in some of the heat exchanger tubes 102. Note that the shape of the protrusion 112 may be any shape that can expand the heat transfer area, and is not limited to the shape shown in FIG. 16.

(Other variations of the fourth embodiment)
In the fourth embodiment and each modified example described above, the length of the protrusion 110 in the first direction D1 may be formed to be shorter as the flow velocity of the gas flow is higher, and longer as the flow velocity of the gas flow is lower. By doing so, it becomes possible to more effectively suppress the development of the temperature boundary layer even when the flow rate of the gas flow is low.

≪Other embodiments≫
The present disclosure is not limited to the configurations of the embodiments and modifications described above, and design changes can be made without departing from the gist thereof.
For example, although the slits 104 in the first and second embodiments are formed like a triangular wave, the edges forming the slits 104 are formed linearly when viewed from the second direction D2. Not limited to. For example, the shape may be a combination of straight lines and curved lines. Moreover, the number of rows and the number of stages of the heat exchanger tubes 102 constituting the heat exchanger tube group 105 may be plural, and are not limited to the number of rows and the number of stages of each of the embodiments and modifications described above.

<Additional notes>
The

heat exchangers

101, 201, 301, and 401 described in the above embodiments can be understood, for example, as follows.

(1) According to the first aspect, a plurality of heat exchangers are disposed in the flow of gas, extend in a second direction D2 intersecting the first direction D1 in which the gas flows, and are arranged at intervals from each other. and a plurality of plate fins 103 that extend in the first direction D1, are provided so as to straddle the plurality of heat transfer tubes 102, and are arranged in plurality at intervals in the second direction D2, The plate fin 103 extends in a third direction D3 that intersects both the first direction D1 and the second direction D2, and has a plurality of slits 104 arranged at intervals in the first direction D1. The plurality of slits 104 have a zigzag shape that alternately extends obliquely toward an upstream side D1u and a downstream side D1d in the first direction D1 through which the gas flows, and the periods of the zigzag shapes match each other. ing.

As a result, the gas flow is disturbed by the slits 104 and the temperature boundary layer of the gas flow can be thinned, so that the temperature gradient from the plate fins 103 can be made steeper and the amount of heat exchange can be increased. Furthermore, since the length of the slit 104 can be increased by forming the slit 104 in a zigzag shape, the weight of the plate fin 103 can be reduced.

(2) According to the second aspect, the heat exchanger is the heat exchanger of (1), in which the heat exchanger tubes 102 are arranged in a staggered manner alternately shifted in the first direction D1 and the third direction D3. The slit 104 is arranged between the plurality of heat transfer tubes 102 arranged in the third direction D3 so as to be adjacent to each other on the upstream side D1u of the first direction D1 with respect to the slit 104. It extends toward the upstream side D1u in one direction D1.
Thereby, when the heat exchanger tubes 102 are arranged in a staggered manner, the heat exchanger tubes 102 disposed on the upstream side D1u in the first direction by one stage than the heat exchanger tubes 102 in the stage adjacent to the upstream side D1u in the first direction; The distance from the slit 104 on the first direction downstream side D1d of 102 can be reduced.

(3) According to a third aspect, the heat exchanger is the heat exchanger of (2), in which the position of the zigzag-shaped top t in the third direction D3 is This corresponds to the position of the heat tube 102.
Thereby, the distances between the staggered heat exchanger tubes 102 and the slits 104 can be made even more uniform.

(4) According to the fourth aspect, the heat exchanger is the heat exchanger of (2) or (3), in which the slits 104 are arranged in the third direction D3 and adjacent in the first direction D1. It is provided for each of the two heat exchanger tubes 102 that match.
Thereby, the amount of heat exchange can be increased more effectively.

(5) According to the fifth aspect, the heat exchanger is any one of (1) to (4), in which the heat exchanger protrudes from the plate fin 103 in the second direction D2 and A pair of protrusions 110 extending in one direction D1 and spaced apart in the third direction D3 are provided, and the pair of protrusions 110 are arranged on an upstream side D1u and a downstream side D1d of the heat exchanger tube 102 in the first direction D1. located respectively.
As a result, the gas G flows in the first direction D1 outside the third direction D3 of the pair of protrusions 110, so that the flow path area on the first direction upstream side D1u and the first direction downstream side D1d of the heat exchanger tube 102 is reduced. Thus, the flow rate of gas G can be increased. Therefore, development of a temperature boundary layer on the plate fins 103 can be suppressed.

(6) According to the sixth aspect, the heat exchanger is the heat exchanger of (5), and has a gap G1 between the protrusion 110 and the heat transfer tube 102 through which the gas G can flow.
This makes it possible to easily provide the protrusion 110. Furthermore, since the gas G flows through the gap G1 between the protrusion 110 and the heat transfer tube 102, the stagnation area of the gas G between the pair of protrusions 110 is reduced, and as a result, it is possible to promote the heat transfer effect. Become.

(7) According to the seventh aspect, the heat exchanger is the heat exchanger according to (5) or (6), in which one of the plurality of heat transfer tubes 102 is located on the downstream side D1d in the first direction D1. The heat exchanger tube 102 includes a protrusion 112 that protrudes from the heat exchanger tube 102 in the third direction D3.
As a result, the heat transfer area of the heat transfer tubes 102 can be expanded, so that the temperature difference during heat exchange between the gas G and the refrigerant R is particularly small in the part of the heat transfer tubes 102 on the downstream side D1d in the first direction. It becomes possible to secure the amount of heat.

(8) According to the eighth aspect, the heat exchanger is disposed in the flow of gas G, extends in a second direction D2 intersecting the first direction D1 in which the gas G flows, and mutually extends in the first direction D1. and a plurality of heat exchanger tubes 102 arranged in a staggered arrangement alternately in a third direction D3, which is a direction intersecting both the first direction D1 and the second direction D2, and extending in the first direction D1. and a plurality of plate fins 303 arranged so as to straddle the plurality of heat exchanger tubes 102 and arranged at intervals in the second direction D2, and the plate fins 303 are arranged so as to straddle the plurality of heat exchanger tubes 102. A hole 304 penetrating in the second direction D2 is provided on the upstream side D1u in the first direction. As a result, when the gas G flows from the upstream side D1u in the first direction to the downstream side D1d in the first direction, the gas flow is disturbed by the holes 304, and the temperature boundary layer of the gas flow can be thinned, so the plate fin The temperature gradient from 303 can be made steeper to increase the amount of heat exchange. Furthermore, since the holes 304 penetrate the plate fins 303, the weight of the plate fins 303 can be reduced by the opening area of the holes 304 compared to a case where the holes 304 are not provided.

(9) According to a ninth aspect, the heat exchanger is the heat exchanger according to (8), which protrudes from the plate fin 103 in the second direction D2 and extends in the first direction D1. A pair of protrusions 110 are provided at intervals in three directions D3, and the pair of protrusions 110 are located on the upstream side D1u and downstream side D1d of the heat exchanger tube 102 in the first direction D1, respectively.
As a result, the gas G flows in the first direction D1 outside the third direction D3 of the pair of protrusions 110, so that the flow path area on the first direction upstream side D1u and the first direction downstream side D1d of the heat exchanger tube 102 is reduced. gas flow rate can be increased. Therefore, development of a temperature boundary layer on the plate fins 103 can be suppressed.

(10) According to the tenth aspect, the heat exchanger is the heat exchanger of (9), and has a gap G1 between the protrusion 110 and the heat transfer tube 102 through which the gas G can flow.
This makes it possible to easily provide the protrusion 110. Furthermore, since the gas G flows through the gap G1 between the protrusion 110 and the heat transfer tube 102, the stagnation area of the gas G between the pair of protrusions 110 is reduced, and as a result, it is possible to promote the heat transfer effect. Become.

(11) According to the eleventh aspect, the heat exchanger is the heat exchanger according to (9) or (10), and is one of the plurality of heat transfer tubes 102 on the downstream side D1d in the first direction D1. The heat exchanger tube 102 includes a protrusion 112 that protrudes from the heat exchanger tube 102 in the third direction D3.
As a result, the heat transfer area of the heat transfer tubes 102 can be expanded, so that the temperature difference during heat exchange between the gas G and the refrigerant R is particularly small in the part of the heat transfer tubes 102 on the downstream side D1d in the first direction. It becomes possible to secure the amount of heat.

According to the heat exchanger of the above aspect, it is possible to reduce the weight while increasing the amount of heat exchange.

101,201,301,401...Heat exchanger 102,...Heat transfer tube 103,303...Plate fin 104...Slit 105...Heat transfer tube group 106...Protrusion 107...Recess 110...Protrusion 111...Protrusion through hole 112...Protrusion 304 ...hole G...gas G1...gap R...refrigerant t...top

Claims

A plurality of heat transfer tubes arranged in a gas flow, extending in a second direction intersecting the first direction in which the gas flows, and arranged at intervals from each other;
a plurality of plate fins extending in the first direction, provided so as to straddle the plurality of heat transfer tubes, and arranged in plurality at intervals in the second direction;
Equipped with
The plate fin is
A plurality of slits extending in a third direction, which is a direction intersecting both the first direction and the second direction, and arranged at intervals in the first direction,
The plurality of slits are
The heat exchanger has a zigzag shape that alternately extends diagonally toward an upstream side and a downstream side in the first direction in which the gas flows, and the periods of the zigzag shapes match each other.
The heat exchanger tubes are arranged in a staggered manner alternately shifted in the first direction and the third direction,
The slit extends toward the upstream side in the first direction between the plurality of heat transfer tubes arranged in the third direction so as to be adjacent to each other on the upstream side in the first direction with respect to the slit. The heat exchanger according to claim 1.
The heat exchanger according to claim 2, wherein the position of the zigzag top in the third direction matches the position of the heat exchanger tube in the third direction.
The heat exchanger according to claim 2 or 3, wherein the slit is arranged in the third direction and provided for each of two stages of the heat transfer tubes adjacent in the first direction.
comprising a pair of protrusions that protrude from the plate fin in the second direction, extend in the first direction, and are spaced apart in the third direction;
The heat exchanger according to any one of claims 1 to 3, wherein the paired protrusions are located on the upstream and downstream sides of the heat exchanger tube in the first direction, respectively.
The heat exchanger according to claim 5, wherein there is a gap between the protrusion and the heat exchanger tube through which the gas can flow.
The heat exchanger according to claim 5, further comprising a protrusion that protrudes toward the third direction from some of the heat exchanger tubes on the downstream side in the first direction, among the plurality of heat exchanger tubes.
disposed in a gas flow, extending in a second direction that intersects the first direction in which the gas flows, and intersects each other in the first direction and both the first direction and the second direction. A plurality of heat exchanger tubes arranged in a staggered arrangement alternately shifted in a third direction;
a plurality of plate fins extending in the first direction, provided so as to straddle the plurality of heat transfer tubes, and arranged in plurality at intervals in the second direction;
Equipped with
The plate fin is a heat exchanger including holes penetrating in the second direction on the upstream side of the plurality of heat exchanger tubes in the first direction.
comprising a pair of protrusions that protrude from the plate fin in the second direction, extend in the first direction, and are spaced apart in the third direction;
The heat exchanger according to claim 8, wherein the paired protrusions are located on the upstream and downstream sides of the heat exchanger tube in the first direction, respectively.
The heat exchanger according to claim 9, wherein there is a gap between the protrusion and the heat exchanger tube through which the gas can flow.
The heat exchanger according to claim 9 or 10, further comprising a protrusion that protrudes toward the third direction from a portion of the plurality of heat exchanger tubes on the downstream side in the first direction.