JPH0547978Y2 - - Google Patents

Description

[Detailed description of the invention] <<Industrial application>> The present invention relates to an endothermic fin inserted into a heat exchanger, and in particular, to an endothermic fin that can increase the endothermic surface area without reducing the cross-sectional area of the fluid flow path. Regarding Finn.

<<Prior Art>> In general, an oil cooler is a conventional heat exchanger using this type of heat absorption fin, and the heat absorption fin has a shape as shown in FIGS. 6 and 7. That is, this heat-absorbing fin 1 has a protruding line 2 and a recessed line 3 formed on a metal plate, and both side walls 4 of the concave and protruding lines 3, 2 are partially formed with a predetermined width across the lower wall 3a of the concave shape 3. A protrusion 5 that protrudes left and right on the protrusion 2 is formed by tearing it and protruding it upward, and the side wall 5 a newly formed by this protrusion 5 and the side wall that remains uncut from the side wall 4 are A large number of heat absorbing pieces 6 are formed with the portion 4a.

Moreover, the endothermic fin 1 formed in this way is
Although not shown in detail, mail plates 8 and 9 defining the upper and lower walls of this passage 7 are installed in the oil passage 7 of the heat exchange unit that constitutes the heat exchanger of the oil cooler.
By passing the oil to be cooled as shown by the broken line arrow in FIG. The oil is cooled by exchanging heat with a cooling medium flowing outside the mail plates 8, 9, etc.

<<Problems to be solved by the invention>> However, in the case of the heat-absorbing fin 1 of such a conventional heat exchanger, the sum of the heat-absorbing surface area of the heat-absorbing piece 6 is determined by the concavities, protrusions 2, and ridges formed on the heat-absorbing fin 1. Since it is uniquely determined by the total length of 3 and its height, in order to increase the sum of the heat absorption surface area within the volume of the heat exchange unit whose dimensions are determined, the pitch of the concave and convex ridges 2 and 3 is determined by You must try to fill it with ₁ . However, when doing so, the heat absorbing fin 1
The cross-sectional area of the oil passage 7 of the heat exchanger unit into which the heat exchanger is inserted becomes smaller, and therefore a sufficient flow rate of oil cannot be obtained, resulting in an effective increase in heat exchange efficiency. I can't.

In other words, the performance of a heat exchanger is roughly divided into the amount of heat exchanged and the resistance, and each of these is influenced by the sum of the heat-absorbing surface area of the heat exchange unit and the cross-sectional area of the passage.In the conventional heat-absorbing fin 1, the heat-absorbing piece 6 The total heat-absorbing surface area of the heat exchanger and the cross-sectional area of the flow path have a contradictory relationship, and there are limits to improving the heat exchange efficiency of the heat exchanger.

Therefore, an object of the present invention is to provide a heat absorbing fin that can increase the contact area between the fluid and the heat absorbing piece without reducing the fluid passage cross-sectional area, thereby improving the heat exchange efficiency of the heat exchanger. With the goal.

《Means and effects for solving the problems》 In order to achieve the above-mentioned object, the present invention is arranged so that the belt-like parts between the notches formed in the metal plate are alternately arranged vertically and vertically. The heat absorption fin has a large number of curved concave and convex portions for heat exchange, and the cut is formed perpendicularly to the flow direction of the fluid, and the concave and convex portions have a projected shape in the flow direction. They are characterized by being arranged so as to overlap each other.

According to the present invention configured as described above, the projected shapes of the concave and convex portions in the fluid flow direction are arranged so as to overlap with each other, so that the cross-sectional area of the flow path is not reduced. As a result, fluid resistance does not increase.

<<Example>> Hereinafter, an example of the present invention will be described in detail based on the drawings.

FIG. 1 and FIG. 2 show an endothermic fin 12 showing an embodiment of the present invention, and this endothermic fin 12 has a fourth
An example will be described in which the present invention is used in an oil cooler as a fluid cooler shown in FIGS.

That is, this oil cooler has a heat exchanger 10, and is constructed by immersing the heat exchanger 10 in a cooling medium, that is, cooling water. The heat exchanger 10 includes a heat exchange unit 1 composed of an endothermic fin 12 and a pair of mail plates 14 and 16.
It has a plurality of 8.

The mail plates 14 and 16 are formed such that the peripheral edge of the upper mail plate 14 is flat, and the peripheral edge of the lower mail plate 16 is bent upward to form a dish shape.

And these upper and lower mail plates 14,1
The heat absorbing fins 12 are sandwiched between the upper mail plate 14 and the lower mail plate 16 by folding and welding the peripheral edge of the upper mail plate 14 to cover the heat absorbing fins 12 and forming these mail plates. 14 and 16 are coupled in a liquid-tight manner.

An opening 20 for oil inflow is formed at one end of the pair of mail plates 14, 16, and an opening 22 for oil discharge is formed at the other end. In the heat exchange unit 18, the oil inflow openings 20 are communicated with each other, and
The oil discharge openings 22 are in communication with each other,
The heat exchanger 10 is configured.

The uppermost layer heat exchange unit 18 also includes oil inflow and oil discharge openings 20 of the upper mail plate 14,
Flanges 30, 30a for oil inflow and oil discharge are fitted and fixed to 22, and pipes (not shown) are connected to these flanges 30, 30a, respectively.

The heat exchanger 10 configured in this way has each unit 1
8 are stacked, an appropriate interval δ is provided between each heat exchange unit 18 to allow cooling water to pass therethrough.

By the way, the heat absorption fins 12 are as shown in FIG.
As shown in FIG. 2, one metal plate 31
The cross section is bent into a wave shape by press molding, and a large number of convex portions 32 to concave portions 34 for allowing oil to pass are formed adjacent to each other alternately.

These concave and convex portions 34 and 32 are formed on the metal plate 31 in the lateral direction (metal plate 31
Cuts 35 are formed over a predetermined length at predetermined intervals along the direction perpendicular to the oil flow direction when the metal plate 31 is installed in the oil cooler. (oil flow direction when the metal plate 31 is installed in the oil cooler) and are formed uniformly at arbitrary intervals, and each of the metal plates formed by aligning in the vertical direction It is formed by making the band-shaped portions 36 between the cuts 35 alternately protrude vertically and trapezoidally along the vertical and horizontal directions of the metal plate 31, respectively.

Therefore, between the concave portions 34 and the convex portions 32 formed adjacent to each other in the horizontal direction of the metal plate 31, there is a metal plate parallel to the mail plates 14 and 16 defining the upper and lower walls of the oil passage 19, and both surfaces of which are in contact with the fluid. horizontal wall 3
8 is formed over the entire vertical length of the metal plate 31, and this horizontal wall 38 and each concave and convex portion 34, 3
The side wall portions 34b and 32b of 2 form a heat absorbing piece 40, and the shape of the heat absorbing fin 12 when projected in the vertical direction becomes a lattice shape connected by the horizontal walls 38, as shown in FIG.

In addition, in the case of this illustrated example, each recess, portion 34, 3
2 is left and right symmetrical and protrudes in a trapezoidal shape with side walls 34b and 32b being inclined. Therefore, the heat absorption fin 12 formed in this way has a cross section that resembles a staircase as shown in FIG. It has a wavy shape, and its longitudinally projected shape is in the form of a hexagonal lattice connected by horizontal walls 38, as shown in FIG.

Therefore, when comparing the heat absorption fin 12 of this embodiment and the conventional heat absorption fin 1 described above in FIG. 2 and FIG. 7, it is found that the heat absorption fin 12 of this embodiment shown in FIG.
Pitch p ₂ for one cycle of concave and convex portions 34 and 32
corresponds to the pitch p ₁ for one cycle of the concave and convex ridges 3 and 2 of the conventional heat absorbing fin 1 shown in FIG. 7, and if the pitch width w and height h are made equal, In this embodiment, the total surface area of the portions functioning as heat absorbing pieces is increased by the surface area of the horizontal wall 38 and the concavity, and the side wall portions 34b, 32b of the convex portions 34, 32 are formed to be inclined.

In this case, the lower wall 3 of the concave and convex portions 34 and 32 is increased by the amount that the horizontal wall 38 is formed and the side wall portions 34b and 32b of the concave and convex portions 34 and 32 are inclined.
4a and the upper wall 32a are formed to be smaller than the _width w1 of the lower wall 3a and the upper wall _2a of the conventional concave and convex strips 3, 2. The projected area in the vertical direction becomes approximately equal to or decreases from that of the conventional one shown in FIG. , Therefore, the projected area of the oil passage 19 is not reduced, and as a result, the heat absorption fin 1
The heat exchange efficiency of the heat exchange unit 18 that houses the heat exchanger 2 can be greatly improved.

Therefore, as is clear from the above description, in the oil cooler equipped with the heat absorbing fins 12 of the present invention, the oil introduced from the oil inflow openings 20 of the heat exchanger 10 passes through each heat exchanger unit 18 and becomes oil. When the oil is discharged from the discharge opening 22 and passes through the heat absorption fins 12 in each heat exchange unit 18, the heat of the oil is transferred to the heat absorption piece 40 formed by the side walls 32b, 34b and the horizontal wall 36. Heat is absorbed. At this time, the total surface area of the heat-absorbing piece 40, that is, the total heat-absorbing surface area, is significantly expanded compared to the conventional one, and the projected area in the oil flow direction of the oil passage 19 in the heat exchange unit 18 and its flow path Since the cross-sectional area is not reduced, the amount of heat absorbed from the oil is increased as much as possible. The oil heat thus absorbed by the heat-absorbing fins 12 is exchanged with cooling water via the mail plates 14 and 16, thereby cooling the oil.

Therefore, the heat exchange efficiency of the heat exchanger 10 is significantly improved, and accordingly, the heat exchanger 10 can be made as compact as possible.

In addition, in this embodiment shown in FIGS. 1 and 2,
A band-shaped portion 3 along the horizontal direction of the metal plate 31
6 are alternately protruded vertically to form concave and convex portions 34, 32.
However, as shown in FIG. 3, in the horizontal direction, all the strip-shaped portions 36 are made to protrude upward or downward in the same way, and only in the longitudinal direction, the strip-shaped portions 36 are made to protrude upward or downward. The uneven portions may be formed by protruding alternately.

In the illustrated embodiment, the concave and convex portions 34 and 32 are formed in a protruding trapezoidal shape with side walls 34b and 32b symmetrically inclined; however, the side walls may be rectangular without being inclined. It may be formed to protrude.

<<Effects of the invention>> According to the invention, the projected cross-sectional area of the heat-absorbing fin in the flow direction of the fluid increases and the resistance of the fluid increases, thereby reducing the flow rate. The area can be increased, and as a result, the heat exchange efficiency of the heat exchanger can be improved.

[Brief explanation of the drawing]

Fig. 1 is a perspective view of a main part showing an embodiment of the heat absorption fin according to the present invention, Fig. 2 is an enlarged cross-sectional view of the main part of Fig. 1, and Fig. 3 is a modified embodiment of the heat absorption fin according to the present invention. 4 is an exploded perspective view of an oil cooler using the heat absorption fin of the present invention, FIG. 5 is a sectional view of the main part of the oil cooler, and FIG. 6 is a perspective view of the main part of a conventional heat absorption fin. , FIG. 7 is an enlarged cross-sectional view of the main part of FIG. 6. 10... Heat exchanger, 12... Endothermic fin, 1
4, 16...Mail plates on the upper and lower walls, 19...
...Oil (fluid) passage, 31...Metal plate,
32... Protrusion, 32a... Upper wall of the protrusion, 34...
... recess, 34a ... lower wall of recess, 35 ... notch, 36 ... band-shaped part.

Claims (1)

[Claims for Utility Model Registration] A heat absorbing fin that is housed in a fluid passage of a heat exchanger and has a large number of concave and convex portions for heat exchange, which are formed by vertically bending strip-shaped portions between cuts formed in a metal plate. The heat exchanger is characterized in that the cut is formed perpendicularly to the flow direction of the fluid, and the uneven portions are arranged so that their projected shapes in the flow direction overlap each other. endothermic fins.