JP7374066B2 - Heat exchanger fins and heat exchangers equipped with the same - Google Patents

Description

The present invention relates to a heat exchanger fin and a heat exchanger equipped with the same.

Generally, a heat exchanger is composed of heat exchanger fins arranged parallel to each other at predetermined intervals, and heat exchanger tubes arranged in a plurality of rows passing through the heat exchanger fins in the normal direction. Then, heat exchange is performed between the air flowing between adjacent heat exchanger fins and the liquid medium flowing inside the heat transfer tube due to a heat transfer effect.

As described in Patent Document 1, a conventional heat exchanger fin has a plurality of slit groups cut and raised on its front and back surfaces so as to have openings of a predetermined height toward the air flow. It is being In order to reduce ventilation resistance, each of the slit groups is formed in a step-like manner, with slits adjacent to each other in the air flow direction being cut and raised in opposite directions with respect to the heat exchanger fins.

In order to further enhance the heat transfer effect than in Patent Document 1 mentioned above, the length of the adjacent slits in the direction of air flow is set to three or more steps, thereby further increasing the heat transfer effect. Something has also been proposed.

Japanese Patent Application Publication No. 2003-161588 Patent No. 6189263

However, in the slit group of the heat exchanger fin of Patent Document 1, the slits adjacent to each other in the air flow direction are cut and raised in opposite directions with respect to the heat exchanger fin, and are formed in a stepped shape. Therefore, when the airflow hits the first slit on the upstream side, it is difficult for the airflow to hit the slits located downstream, and there is a concern that the airflow will become laminar (stratified).

Here, heat is transferred through a temperature boundary layer formed around the slit. Therefore, the heat transfer effect of the slits on the airflow side is significantly reduced if the number of times the airflow hits the slits is small. As a result, the heat exchanger fin of Patent Document 1 has a problem in that the heat transfer effect is low.

Furthermore, although it can be recognized that the heat transfer effect is further enhanced in Patent Document 2, it is similar in that it is mainly composed of slits adjacent to each other in the air flow direction.

Therefore, the main object of the present invention is to provide a heat exchanger fin with a high heat transfer effect, and to provide a heat exchanger equipped with the same.

A fin for a heat exchanger according to the present invention includes a heat sink and a plurality of opening holes for heat transfer tubes formed in four or more and arranged in two or more rows for heat transfer tubes passing through the heat sink. is characterized in that a planar protrusion is formed in a portion surrounded by four adjacent heat exchanger tube opening holes of the plurality of heat exchanger tube opening holes and facing the heat exchanger tube. This is a fin for a heat exchanger.

Further, a heat exchanger according to the present invention includes a plurality of heat exchanger fins described above arranged at predetermined intervals, and heat exchanger tubes arranged in plural rows passing through the heat exchanger fins. This is a heat exchanger characterized by the following.

With these types, the protrusion is formed with a planar part facing the heat exchanger tube, so that the air flow in the space between the heat exchanger tube opening hole and the protrusion is directed in the flow direction. By flowing in a direction different from that of the heat transfer tube, a turbulent region is formed between the heat exchanger tube opening and the protrusion. Therefore, the air in this turbulent flow region will be located in a high heat conduction region around the heat transfer tube. As a result, more air comes into contact with the high heat conduction region around the heat exchanger tubes, so it is possible to provide a heat exchanger fin with a high heat transfer effect, and a heat exchanger equipped with this heat exchanger fin.

In addition, in order to efficiently bring air into contact with the high heat conduction area around each heat exchanger tube, the protrusions are interposed between adjacent heat exchanger tube opening holes. It is preferable that the heat exchanger tube be surrounded by four heat exchanger tube opening holes arranged in a direction perpendicular to the direction.

In order to bring the air into contact with the high heat conduction area around the heat transfer tube more strongly, the protrusion preferably has an orthogonal surface facing in a direction perpendicular to the flow direction.

In order to ensure both smooth flow of air and the amount of air in contact with the high heat conduction area around the heat transfer tube, the protrusion has an inclined surface facing in a direction inclined to the flow direction. can be mentioned.

An example of the projection having the above-mentioned inclined surface is a projection having a rhombus shape in plan view .

In order to realize a configuration that can generate turbulence, which is a random air flow, between the heat exchanger tube and the protrusion, it is desirable to apply a configuration in which the protrusion is octagonal in plan view .

Alternatively, as another configuration capable of generating turbulence, which is a random air flow, between the heat exchanger tube and the protrusion, the protrusion may be hexagonal in plan view .

In order to effectively exert the function of the protrusions described above and to suitably position the plurality of heat sinks, the heat sinks are spaced at predetermined intervals along the extending direction of the heat exchanger tubes. Preferably, a plurality of protrusions are arranged, and the height at which the protrusions protrude is the same as the predetermined interval.

As an example of a configuration for efficiently manufacturing the heat sink, the heat dissipation plate may be made of a metal plate, and the protrusion may have a hollow portion formed on the back side of the protrusion so as to seal air. Preferably.

According to the present invention, it is possible to provide a heat exchanger fin with a high heat transfer effect, and also to provide a heat exchanger equipped with the same.

The above-mentioned objects, other objects, features, and advantages of the present invention will become more apparent from the following description of the mode for carrying out the invention, which is given with reference to the drawings.

FIG. 1 is an external perspective view showing a part of a heat exchanger fin that constitutes a part of a heat exchanger according to an embodiment of the present invention. It is a top view which shows the fin for heat exchangers. It is a top view which expands and shows the principal part which shows the fin for heat exchangers. FIG. 4 is an explanatory diagram of the operation according to FIG. 3; 4 is a sectional view taken along line VV in FIG. 3. FIG. It is a top view of the fin for heat exchangers concerning the modification of one embodiment of this invention. FIG. 4 is a plan view corresponding to FIG. 3 of a heat exchanger fin according to another modification. FIG. 4 is a plan view corresponding to FIG. 3 of a heat exchanger fin according to still another modification.

Hereinafter, one embodiment of the present invention will be specifically described with reference to FIGS. 1 to 5.

FIG. 1 is an external perspective view showing a part of a heat exchanger fin 10 that constitutes a part of a heat exchanger 2 according to an embodiment of the present invention. FIG. 2 is a plan view showing the heat exchanger fin 10. FIG. 3 is a plan view showing an enlarged main part of the heat exchanger fin 10. As shown in FIG. FIG. 4 is an explanatory diagram of the operation related to FIG. 3. FIG. 5 is a sectional view taken along line VV in FIG.

Hereinafter, the heat exchanger fin 10 that constitutes a part of the heat exchanger 2 according to the embodiment will be described. In addition, in this specification, "planar view" means the viewpoint when looking from the normal line direction of the heat exchanger fins 10 (above the heat exchanger fins 10 in FIG. 1).

(1) Heat Exchanger The heat exchanger 2 has heat exchanger fins 10 arranged parallel to each other at predetermined intervals, and a heat exchanger fin 10 that passes through the heat exchanger fins 10 in the normal direction. It is composed of heat exchanger tubes 4 arranged in multiple rows. The air ar (medium) flowing between the adjacent heat exchanger fins 10 is in contact with the outer circumferential surface 6, and heat is transferred between the liquid medium (not shown) flowing inside the heat exchanger tube 4 along the inner surface 8. Heat exchange takes place due to the effect.

As shown in FIGS. 1 to 5, the heat exchanger tube 4 is a so-called round pipe material having an approximately perfect circular outer shape. The heat exchanger tube 4 exchanges heat with air ar (medium) guided by the heat exchanger fins 10 while flowing a liquid medium inside the inner surface 8 . The liquid medium is, for example, heat transfer oil, steam, hot water, cooling water, refrigerant liquid, or the like.

As the material for the heat exchanger tubes 4, it is customary to use stainless steel to ensure the strength of the heat exchanger 2 itself, but iron, copper, etc. may also be used to increase thermal conductivity. good. The heat exchanger tube 4 is formed into a cylindrical shape by bending these metal materials.

(2) Heat exchanger fin The heat exchanger fin 10 according to the present embodiment includes a plate-shaped heat sink 12 extending in the normal direction of the heat exchanger tube 4 and a heat exchanger tube 4 penetrating through the heat sink 12. A plurality of heat exchanger tube opening holes 14 are formed and arranged in two or more rows. It is characterized in that a planar projection 20 is formed in a portion surrounded by the holes 14 and facing the heat exchanger tube 4.

Hereinafter, a specific configuration of the heat exchanger fin 10 will be described. This heat exchanger fin 10 is mainly made of a metal plate material, that is, a sheet metal material. In this embodiment, the material of the heat exchanger fins 10 is stainless steel. Further, as described above, the heat exchanger fin 10 has a heat sink 12 and a heat exchanger tube opening hole 14.

As shown in FIGS. 1 to 4, the heat exchanger tube opening holes 14 are arranged at predetermined intervals along the flow direction F of the air ar, which is the short dimension direction (direction perpendicular to the longitudinal direction) of the heat sink 12. In the embodiment, two rows are arranged. This is because the heat exchanger tubes 4 are positioned in a grid pattern according to the arrangement. In this case, as shown in the figure, the four heat exchanger tube opening holes 14 surround a part of the heat sink 12.

The heat exchanger tube opening hole 14 has an inner circumferential surface 14a that corresponds to the shape of the outer circumferential surface 6 of the heat exchanger tube 4 and is sandwiched therebetween without any gap. Thereby, the distance between the plurality of heat exchanger tubes 4 is stabilized.

As shown in FIGS. 1 to 4, particularly FIG. 2, the heat sink 12 has a rectangular shape in plan view and a generally thin plate shape. As shown in FIG. 2, this heat radiating plate 12 has a region surrounded by four heat transfer tubes 4 in almost all parts through which air ar flows. The thickness of the heat sink 12 is preferably 0.2 mm or more and 0.4 mm or less, and in this embodiment, it is set to 0.3 mm.

Here, the present embodiment is characterized in that the protrusion 20 is provided in a region surrounded by four adjacent opening holes 14 for heat exchanger tubes. In other words, the protrusions 20 are interposed between the adjacent heat exchanger tube opening holes 14, and more specifically, the protrusions 20 are interposed between the heat exchanger tube opening holes 14 adjacent to each other, and more specifically, the protrusions 20 are interposed between the plurality of protrusions 20 disposed in the flow direction F of the air ar and in the direction orthogonal to the flow direction F. It is provided surrounded by four of the heat exchanger tube opening holes 14 .

Here, as described above, since the material of the heat exchanger fins 10 is stainless steel, its thermal conductivity is lower than that of aluminum or copper. Therefore, the center of the portion surrounded by the four heat exchanger tubes 4 becomes a low heat conduction area.

Therefore, in order to guide the air ar (medium) to flow into the high heat conduction region 30 around the four heat transfer tubes 4, a protrusion 20, also called a dowel, is arranged at the center of the heat transfer tube 4 surrounded by the four heat transfer tubes 4. do. Thereby, loss in heat conduction can be prevented and thermal efficiency can be improved.

Hereinafter, the shape and aspect of the protrusion 20 will be specifically explained.

The protrusion 20 is integrally formed on the heat sink 12 . The protrusion 20 is manufactured by, for example, press-molding a sheet metal material used for the heat sink 12 so as to have a front surface 20a that is in direct contact with the air ar and a back surface 20b that is located on the back side of the front surface 20a.

As shown in FIGS. 1 to 4, the protrusion 20 is an octagonal protrusion 208 that is octagonal in plan view . That is, in this embodiment, by adjusting the orientation of the octagonal protrusion 208, the protrusion 20 has an orthogonal surface 22 facing in a direction perpendicular to the flow direction F and a surface facing in a direction oblique to the flow direction F. It has an inclined surface 24.

As shown in the sectional view taken along line VV in FIG. 5, a plurality of heat sink plates 12 are arranged at predetermined intervals along the extending direction of the heat exchanger tubes 4. To specifically explain the illustrated embodiment , the heat exchanger fins 10 have a predetermined interval of, for example, 2 mm. FIG. 1 shows an embodiment in which four heat exchanger fins 10 and five heat exchanger fins 10 are stacked at predetermined intervals in FIG. 5 .

The height at which the protrusions 20 protrude is the same as the predetermined interval, for example, 2 mm. This is because the heat sinks 12 are arranged at a pitch of 2 mm. Thereby, the air ar in contact with the protrusion 20 flows along the surface 20a of the protrusion 20.

As shown in FIG. 5, the protrusion 20 has a hollow portion 20c formed on the rear surface 20b side of the protrusion 20 so as to be able to seal air ar. In particular, providing such a hollow portion 20c means that the upper and lower heat sinks 12 are connected to each other. This effectively prevents the stacked heat exchanger fins 10 from being bent or distorted as a whole.

Next, the heat transfer effect of the heat exchanger fins 10 according to the present embodiment will be described in detail with reference to FIG. 4.
The protrusion 20 shown in FIGS. 1 to 4 has an octagonal shape in plan view . When air ar is introduced in the flow direction F to the heat exchanger fins 10 having such a shape, a heat exchanger tube side flow ar1 that flows along the outer circumferential surface 6 of the heat exchanger tube 4 is generated. If there is no protrusion 20, this heat exchanger tube side flow ar1 normally does not pass through the high heat conduction region 30 formed around the heat exchanger tubes 4, but passes through the low heat conduction region in the center between the heat exchanger tubes 4. It is discharged from the fin 10. Therefore, even if the air ar flows into the region between the heat exchanger tubes 4, the heat exchangeability from the heat exchanger tubes 4 to the air ar is low.

In this embodiment, protrusions 20 are provided at locations intervening between the heat exchanger tubes 4 to suppress passage between the heat exchanger tubes 4 . The protrusion 20 has a straight portion facing the heat exchanger tube 4, so that the air ar that comes into contact with the heat exchanger tube 4 and undergoes heat exchange passes between the heat exchanger tube 4 and the protrusion 20. A flow occurs.
Each flow of air ar passing through the heat exchange fins 10 according to the present embodiment will be described below.

First, a rectilinear flow ar2 extending in a direction along the flow direction F is generated. Air ar in contact with this rectilinear flow ar2 flows between the heat exchanger tube 4 and the protrusion 20 along the inclined surface 24 of the protrusion 20. It becomes an inclined flow ar3.

Therefore, the velocity difference between the inclined flow ar3, which is the flow along the inclined surface 24 of the protrusion 20, and the heat exchanger tube side flow ar1, which is the flow along the outer circumferential surface 6 of the heat exchanger tube 4, and the heat exchanger tube side flow ar1, which is the flow along the outer peripheral surface 6 of the heat exchanger tube 4, as air ar. By colliding with the inclined flow ar3, a turbulent flow region 40 as shown in FIG. 4 is generated.

Specifically, when air ar (medium) flows between the protrusion 20 and the heat exchanger tube 4, the heat exchanger tube side flow ar1 flowing along the outer peripheral surface 6 of the heat exchanger tube 4 and the surface 20a of the protrusion 20 A turbulent flow region is generated in the space between the heat exchanger tube 4 and the protrusion 20 due to the speed difference between the straight forward flow ar2 and the inclined flow ar3 and the collision of the heat exchanger tube side flow ar1 and the inclined flow ar3 as air ar. It becomes easier. As a result, the turbulent region 40 becomes a resistance to the flow of air ar. As shown in FIG. 4, this turbulent flow region 40 substantially coincides with the high heat conduction region 30 formed around the heat exchanger tube 4. Therefore, in the high heat conduction region 30, the heat of the heat exchanger tube 4 is easily transmitted by the air ar (target medium).
Furthermore, it is desirable that the portion of the protrusion 20 that the air ar (medium) first hits is also a straight line (flat portion). This is to increase the resistance to which air ar (medium) flows.

As described above, in the heat exchanger fins 10 and the heat exchanger 2 according to the present embodiment, the planar projections 20 are formed in the portions facing the heat exchanger tubes 4, so that the heat exchanger fins 10 and the heat exchanger 2 according to the present embodiment The air ar flowing in the space between the outer circumferential surface 6 and the protrusion 20 generates air ar (ar2, ar3) flowing in a direction different from the flow direction F. That is, a speed difference occurs between the heat exchanger tube side flow ar1 that flows along the outer circumferential surface 6 of the direct heat exchanger tube 4 and the inclined flow ar3 that flows along the inclined surface 24 of the protrusion 20. As a result, a turbulent flow region 40 is formed between the heat exchanger tube 4 and the protrusion 20, and the air ar in the turbulent flow region 40 can efficiently pass through the high heat conduction region 30 around the heat exchanger tube 4. It is possible to provide heat exchanger fins 10 and heat exchanger 2 with high heat transfer effects.

Furthermore, in this embodiment, in order to efficiently bring the air ar into contact with the high heat conduction region 30 formed around each of the heat exchanger tube opening holes 14, the protrusions 20 are arranged in the adjacent heat exchanger tube opening holes 14 Among the opening holes 14 for heat exchanger tubes interposed between the two, the hole 14 for heat exchanger tubes is surrounded by the four opening holes 14 for heat exchanger tubes that are arranged in the flow direction F of the air ar and in the direction orthogonal to the flow direction F, especially in the center. It is assumed that the

In order to make the air ar more strongly contact with the high heat conduction region 30 formed around the heat exchanger tube opening hole 14, in this embodiment, the protrusion 20 has an orthogonal surface 22 facing in a direction perpendicular to the flow direction F. It is assumed that it is equipped with the following.

In this embodiment, the protrusion 20 has a surface facing in a direction inclined with respect to the flow direction F, in order to achieve both a smooth flow of the air ar and an amount of the air ar in contact with the heat exchanger tube opening hole 14. It is provided with an inclined surface 24.

Further, in this embodiment, by providing the hollow portion 20c inside the protrusion 20, the upper and lower heat sinks 12 are connected to each other, so that the stacked heat exchanger fins 10 as a whole can be bent or distorted. This is effectively prevented.

(3) Modification Examples Each modification example according to the present embodiment will be described below. Regarding each modification described below, each component corresponding to the component described in the above embodiment is given the same reference numeral, and detailed explanation thereof will be omitted.

In the embodiment described above, as shown in FIG. In this embodiment, two rows are arranged at intervals, but the invention is not limited thereto.

FIG. 6 is a plan view of a heat exchanger fin 10 according to a modification of the embodiment described above. That is, as shown in FIG. 6, the heat exchanger tube opening holes 14 according to this modification are formed in a predetermined direction along the flow direction F of the air ar, which is the short dimension direction (direction perpendicular to the longitudinal direction) of the heat sink 12. In this embodiment, three rows are arranged at intervals. This is because the heat exchanger tubes 4 are positioned in a grid pattern according to the arrangement. In this case, as shown in the figure, the four heat exchanger tube opening holes 14 surround a part of the heat sink 12.

Even in this case, by forming the planar projections 20 in the portion facing the heat exchanger tubes 4, the air ar flowing into the space between the outer circumferential surface 6 of the heat exchanger tubes 4 and the projections 20 can be reduced. Air ar (ar2, ar3) whose flow is in a direction different from the flow direction F is generated. That is, a speed difference occurs between the heat exchanger tube side flow ar1 that flows along the outer circumferential surface 6 of the direct heat exchanger tube 4 and the inclined flow ar3 that flows along the inclined surface 24 of the protrusion 20. As a result, a turbulent flow region 40 is formed between the heat exchanger tube 4 and the protrusion 20, and the air ar in the turbulent flow region 40 can efficiently pass through the high heat conduction region 30 formed around the heat exchanger tube 4. As a result, it is possible to provide the heat exchanger fins 10 and heat exchanger 2 with high heat transfer effects, which is the same effect as in the embodiment described above.

In the above embodiment, the shape of the protrusion 20 is octagonal in plan view , but of course the shape of the protrusion 20 is not limited to this. FIG. 7 is a plan view corresponding to FIG. 3 of a heat exchanger fin 10 according to another modification. That is, in the heat exchanger tube opening hole 14 according to this modification, as shown in FIG. 7, the protrusion 20 is a hexagonal protrusion 206 that is hexagonal in plan view .

Even with such a device, although the direction and number of surfaces are different, effects similar to those of the above-described embodiments and modifications can be achieved.

In the above embodiments and modifications, the shape of the protrusion 20 is octagonal or hexagonal in plan view , but of course the shape is not limited thereto. FIG. 8 is a plan view corresponding to FIG. 3 of a heat exchanger fin 10 according to still another modification.

As shown in FIG. 8, the protrusion 20 is a diamond-shaped protrusion 208 that is diamond-shaped in plan view . In particular, the illustrated protrusion 20 is shaped like a diamond with a wider width, specifically, the dimensions are larger in the direction orthogonal to the flow direction F to guide more air ar to the heat exchanger tubes 4.

Even with such a structure, the same effects as in the above embodiment can be achieved even without the orthogonal surface 22 disclosed in the above embodiment.

Note that, as described above, although the embodiments of the present invention are disclosed in the above description, the present invention is not limited thereto. For example, the number of rows in which the heat exchanger tube opening holes are arranged may be four or more. This is because it can be applied to the manner in which the heat exchanger tubes are arranged. Further, the number of protrusions surrounded by the four heat exchanger tubes is not limited to one. There may be more than one at the location.

That is, various changes can be made to the embodiment described above in terms of mechanism, shape, material, quantity, position, arrangement, etc. without departing from the scope of the technical idea and purpose of the present invention. and are included in the present invention.

2 Heat exchanger 4 Heat exchanger tube 6 Outer surface 8 Inner surface 10 Fin for heat exchanger 12 Heat sink 14 Opening hole for heat exchanger tube 14a Inner peripheral surface 20 Projection 20a Front surface 20b Back surface 22c Hollow part 22 Orthogonal surface 24 Inclined surface 30 High heat conduction area 40 Turbulent flow region 204 Diamond-shaped protrusion 206 Hexagonal protrusion 208 Octagonal protrusion ar Air ar1 Heat exchanger tube side flow ar2 Straight flow ar3 Inclined flow F Flow direction

Claims (7)

A heat sink,
a plurality of heat exchanger tube opening holes arranged in a grid pattern in two or more rows, four or more for heat exchanger tubes passing through the heat sink;
Equipped with
The heat sink has a protrusion formed in a region between the four heat exchanger tube opening holes,
The protrusion has an orthogonal surface facing in a direction perpendicular to the air flow direction and a plurality of inclined surfaces facing in a direction inclined with respect to the air flow direction, and the orthogonal surface and the inclined surface are both planar,
The orthogonal surface is the part where air first hits the protrusion,
Each of the plurality of inclined surfaces is a surface facing each of the four heat exchanger tube opening holes,
Fins for heat exchangers featuring The protrusion is octagonal in plan view .
The fin for a heat exchanger according to claim 1. The protrusion is hexagonal in plan view .
The fin for a heat exchanger according to claim 1. A plurality of the heat sinks are arranged at predetermined intervals along the extending direction of the heat exchanger tube,
The height at which the protrusion protrudes is the same as the predetermined interval;
The fin for a heat exchanger according to any one of claims 1 to 3. The protrusion has a hollow portion formed on the back side of the protrusion so as to be able to seal air.
The fin for a heat exchanger according to claim 4. The heat exchanger tube opening holes are provided in two rows along the air flow direction,
The fin for a heat exchanger according to any one of claims 1 to 5. The heat exchanger fins according to any one of claims 1 to 6 arranged at predetermined intervals;
heat exchanger tubes arranged in multiple rows passing through the heat exchanger fins;
Equipped with
A heat exchanger featuring:

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