JPS61246595A - Heat exchanger - Google Patents

Abstract

PURPOSE:To obtain a heat exchanger surpassing in heat transferring property, by certainly joining a fin to a pipe by providing a part where no through-holes are provided around a fin collar which serves as a joining part of fin and pipe, and by raising the holeless part as high as a fin pitch. CONSTITUTION:A fin collar 3 is molded in such a manner that it is raised by a factor of the height 'H', which corresponds to the fin pitch of a heat exchanger from the center line in the direction of the height of a trapezoid shape. A fin '1a' and a fin '1b' are laid so that the upper end of a fin collar 3 is contacted to one surface of the other fin. Then a pipe 2 is inserted into the fin collar 3 provided to each fin '1a' and '1b' to expand the pipe 2, and the fin 1 and the pipe 2 are thermally joined to each other at the fin collar part 3.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to the structure of a heat exchanger used in an air conditioner.

[Conventional technology]

FIG. 9 is a block diagram showing a heat exchanger proposed in Japanese Patent Application No. 59-264087, which is composed of trapezoidal wave-shaped fins having a plurality of through holes and pipes. In the figure, (1) represents a fin having a plurality of through holes and bent in a trapezoidal wave shape. (2) is a pipe arranged so as to prevent the air flow (A) from flowing between the laminated fins (1). αJ is the through hole provided in the fin (11). In this figure, the fin (1) is 1
The layers are stacked to shift the phase of the trapezoidal wavy bends.

The effects of the heat exchanger configured in this way are explained by the cross-sectional view of the fins in FIG. A flow path (51), a fin (1b) and a fin (1C
) is defined as a second flow path (52). If the flow rate and total pressure of the fluid flowing through the first flow path (51) and the second flow path (52) are the same, in each cross section (X-X) perpendicular to the flow direction CA in Figure 9, The cross-sectional area of the first flow path (51) and the second flow path (52) are different as a result. For example, considering the XX cross section, the cross-sectional area of the first flow path (51) is different from that of the second flow path (52). Since it is larger than the second flow path (52), the flow velocity of the fluid flowing through the first flow path (51) at that part is lower than that of the second flow path (52).
), a static pressure difference occurs between the first flow path (51) and the second flow path (52), and as a result, the first flow path (5
A part of the fluid (air) flows from 1) into the second flow path (52) through the through hole α3. At this time, the fin (
1b), as shown in FIG. 8, the waveforms flow from the first flow path (51) to the second flow path (52) and from the second flow path (52) to the first flow path according to the aforementioned substantially trapezoidal modified waveform. A periodic flow of fluid into the channel (51) will occur. In other words, if the fins (11) are configured in this way, the uniform suction and uniform outlet surfaces are arranged in order in the flow direction, and the boundary layer is formed on the heat transfer surface of the uniform suction section. By being extremely thin, a solid heat transfer promotion effect can be obtained, and on the outlet surface, the same high heat transfer performance can be achieved due to the repeated effect of the run-up section. Fluid air in the water area moves through the 9 through holes α3, eliminating flow stagnation, improving heat transfer characteristics in the dead area area, and providing heat exchange with extremely high heat transfer characteristics that were previously unimaginable. It is said that it is possible to obtain equipment.

Regarding pressure loss, compared to the case where the leading edge effect is used, at least the fins are not separated, so the shape resistance of the leading edge of the strip is naturally eliminated, and the effect is said to be greater.

[The intergranular point that the invention attempts to solve]

In this way, in Japanese Patent Application No. 59-264087.

Only small aspects such as improving heat transfer performance and increasing pressure loss, that is, performance aspects, are mentioned, but there is no mention of laminating fins and joining fins and pipes, that is, precautions to take when manufacturing a heat exchanger. In view of the above points, it is an object of the present invention to make it possible to efficiently manufacture a heat exchanger without degrading the first characteristic, which improves the transfer characteristics.

[Means for solving problems]

As a means of thermally joining the fins and pipes, a common method for this type of heat exchanger is to put a fin collar on the fins, allow the pipe to pass through part of the collar, and then expand the pipe to make the fins and pipes come into close contact. It's a method. For this reason, in order to enable the fin collar to stand up and prevent a decrease in adhesion efficiency and fin efficiency, the 9 through holes are only partially machined in the fin collar.

Also, it is not applied at a certain distance (for example, 2-) from the outer diameter of the fin collar.

In addition, the means for stacking fins with a constant fin pitch is as follows:
The starting point of the rise of the fin collar is on the center line in the height direction of the trapezoidal shape, and the height of the fin collar is set at the set height, so the fin pitch and pitch can be maintained at the set dimensions and stacking can be performed automatically.

[Effect]

In the heat exchanger according to the present invention, the fin collar is machined so that the starting point of the fin collar is on the center line in the height direction of the trapezoidal shape, and the through holes are machined on the fins at a certain distance from the outer diameter of the fin collar. As a result, the automatic stacking of fins and the fastening of fins and pipes can be performed sufficiently, making it possible to efficiently manufacture a heat exchanger while maintaining high heat transfer characteristics. 1 is a perspective view showing a heat exchanger according to an embodiment of the invention, in which (1) is a heat transfer fin having a plurality of through holes, and (2) is a pipe.

FIG. 2 is a plan view of a heat transfer fin according to the present invention, and FIG.
FIG. 2 is a cross-sectional view showing the m-tu cross section, FIG. 4 is a cross-sectional view showing the joint between the fin and the pipe when the fins shown in FIG. 2 are stacked, and FIG. It is a figure which shows the VV cross section when laminated|stacked.

In Fig. 2, (3) is the fin collar, (4) is the part without through holes around the fin collar (3), and α3 is the through hole.As shown in Fig. 3, this cross section is in the air flow direction A. The fin collar (3) is periodically bent in a trapezoidal wave shape along the trapezoidal shape, and the fin collar (3) stands up by a distance H corresponding to the heat exchanger fin pitch from the center line in the height direction of the trapezoidal shape.

nu,) a [Machining of the height deviation between the part without a through hole (3) and the trapezoidal part, and 3) with the fin collar, the rising base point of the fin collar (3) is performed by drawing. I try to keep it that way.

The action and effect will be explained with reference to FIGS. 3, 4, and 5.

As mentioned above, the trapezoidal shape of the fin collar (3) is based on the portion without through holes (4) and has a predetermined dimension, that is, the fin collar (3).
) has a rising dimension H and a trapezoidal shape height of, for example, 0.5U, and is drawn into a wavy shape. Therefore, as shown in a part of the cross section of the third factor fin lamination, there is a part (4) without through holes.
The strength for molding the fin collar (3) can be maintained and the molding can be reliably made, and the fins (1a) and fins (1) can be molded reliably.
In b), it is possible to stack the fin collar (3) so that the upper end thereof is in contact with one surface of another fin. At this time, the fins (between 11 and 11), that is, the fin pitch, maintains the rising dimension H of the fin collar (3), and can be stacked while automatically maintaining the fin pitch.Furthermore, the pipe (2) is connected to each fin (1a). The tube is expanded by inserting it into the fin collar (3) provided at 5 to obstruct the air flow path formed by (1b), and the fin + 11 and pipe (2) are inserted into the fin collar (3).
) can be thermally bonded. The performance will be explained using the fin configuration as shown in FIG. 5, but this improvement in performance is similar to that of the prior art Japanese Patent Application No. 59-264087.

Although the details are omitted, the fin (1a) and the fin (1b)
) formed by a first air flow path (51) and a fin (1b)
and a second flow path (52) formed by a fin (1C),
For example, if the air flow rate and total pressure flowing through the first flow path (51) and the second flow path (52) are in the direction, then the flow direction (4) in Figure 1 is given.
In each cross section (X-X) perpendicular to The air velocity flowing through the second flow path (
52), so the first flow path (51) and the second
A static pressure difference occurs between the flow paths (52), and a portion of the fluid flows from the first flow path (51) to the second flow path (52) through the through hole αJ. As a result, the boundary layer can be made extremely thin on the heat transfer surface of the uniform suction section, resulting in a dramatic heat transfer promotion effect, and on the blowout surface.

High heat transfer performance can be achieved due to the repeated effect of the run-up section. Furthermore, as shown in Figure 4, in order to prevent flow stagnation that occurs downstream of the pipe (2), the flat part of the non-perforated part (4) is drawn into a five-trapezoidal shape in an extremely small area. By repeating this process, the occurrence of stagnation in the air flow is reduced, and the stagnation fluid moves through the through hole 03, which is a mutual effect, thereby improving the heat transfer characteristics in the dead area.

In addition, in another embodiment shown in FIG. 6, a small groove (ring) (6) is provided in the part without a through hole, so that the strength for processing the fin collar (3) is maintained and the pipe (2 ) It is more effective for regenerating the dead water area in the wake.

〔Effect of the invention〕

As explained above, the present invention provides a fin having a plurality of negative through holes and periodically bending in a trapezoidal wave shape, and a portion without through holes is provided around the fin collar, which is the joint between the fin and the pipe. The part without through holes was placed on the center line of the trapezoidal shape in the height direction, and the fin collar and trapezoidal shape were formed by drawing.

Since the fin collar can be formed reliably regardless of the trapezoid period, it is possible to stack the fins while maintaining the fin pitch by simply stacking them, making it possible to efficiently manufacture heat exchangers. In addition, it has the effect of sufficiently thermally bonding with the pipe, and in terms of performance, it eliminates dead areas and has a repeatable effect.
The effect of thinning the boundary layer due to the through holes makes it possible to reliably connect the fins with high heat transfer effects to the pipes, resulting in the effect of obtaining a heat exchanger with excellent heat transfer characteristics.

[Brief explanation of the drawing]

FIG. 1 is a perspective view showing a heat exchanger according to an embodiment of the present invention;
FIG. 2 is a plan view of a fin according to an embodiment of the present invention, and FIG. 3 is a sectional view taken along line 1ll-I in FIG. FIG. 4 is a cross-sectional view of the joint between the fin and the pipe. FIG. 5 is a sectional view taken along the line V-V in FIG. 2. FIG. 6 is a sectional view of a portion of the fin collar according to another embodiment. Note that the same symbols in the figures indicate the same or equivalent parts, (1)
is fin, (2) is pipe, (3) is fin collar, +
41 is a part without a through hole, (6) is a small ring, α3 is a through hole, (Sl) is a first flow path, and (52) is a second flow path.

Claims (1)

[Claims] 1) Fins having a plurality of through holes and periodically bent in a trapezoidal wave shape along the air flow direction are stacked, and the pipe is arranged so as to obstruct the air flowing between the fins. In the heat exchanger arranged and constructed, the starting point of the rise of the fin collar that joins the laminated fins and pipes is on the center line of the trapezoidal shape height direction, and the fin collar part and trapezoidal shape are characterized by a drawing method. heat exchanger. 2) Claim 1, characterized in that the fin has a plurality of through holes provided at a certain distance from the outer diameter of the fin collar, and the portion without through holes is located on the center line of the trapezoidal shape in the height direction. Heat exchanger as described in section. 3) The heat exchanger according to claims 1 and 2, characterized in that a ring having a chevron shape is provided in the portion without through holes.