JPS59205591A - Heat exchanger - Google Patents

Abstract

PURPOSE:To make the thickness of a partition wall smaller as well as increase the number of parallel refrigerant paths by forming the partition wall in the porous refrigerant tube into a latticed shape. CONSTITUTION:In a porous refrigerant tube 2 of a flat cross section, made of aluminum by extrusion molding, latticed internal partition walls 4a and 4b are provided to form many refrigerant paths 5. Since the thickness t1 and t2 of the internal partition walls 4a and 4b are sufficient small to prevent the lowering of the strength, the raduction of the cross section of the refrigerant paths 5 can be avoided. When the thickness t1 of the partition wall 4a is uniform, the buckling resistance of the partition wall 4a is more greatly raised, th shorter the length of the wall 4a becomes.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention is directed to a heat exchanger having porous refrigerant tubes used in a cooling/refrigeration system.

In general, a heat exchanger for a refrigeration/cooling system includes a refrigerant pipe 2 bent into a meandering shape, such as a condenser 1 shown in FIG.
and h9. connected between this refrigerant pipe 2. It is composed of corrugated fins 3 for heat. This condenser 1 is
As is well known, the high temperature and high pressure waste refrigerant inside the refrigerant pipe 2 is released through the refrigerant pipe 2 and the corkated fins 3,
It is designed to be a liquid refrigerant. Therefore, in order to improve the heat exchange efficiency in the conventional refrigerant pipe 2, a partition wall 4 is provided inside the refrigerant pipe 2 to form a plurality of parallel refrigerant passages 5, as shown in FIG. This increases the heat transfer area of the refrigerant. That is, as the number of refrigerant passages 5 increases, the heat exchange rate in the porous refrigerant pipes 2 increases, and as a result, the performance of the condenser 1 improves. Furthermore, the condenser 1 is required to be lightweight and to reduce material costs. In order to improve this performance and reduce weight, the thickness t of the partition wall 4 of the porous refrigerant pipe 2 is
It is necessary to make it thinner. On the other hand, the porous refrigerant sparrow 2 must be bent into a meandering shape as shown in FIG.
A problem arises in that the partition wall 4 buckles during bending.

The present invention has been made in view of the above points, and in a heat exchanger such as a condenser used in a refrigeration/cooling device, a porous refrigerant can be used without reducing the strength of the porous refrigerant pipes 2 constituting the heat exchanger. The purpose is to make the internal partition wall 4 of the pipe 2 thinner.

The present invention will be explained below with reference to embodiments shown in the figures.

FIG. 3 shows the cross-sectional shape of the porous refrigerant pipe 2 of the present invention, and the porous refrigerant pipe 2 is formed by extruding and hardening aluminum into the flat cross-sectional shape shown in the figure. Inside the porous refrigerant pipe 2, there are lattice-shaped internal partition walls (4a, 4b
), and a large number of refrigerant passages 5 are formed by the partition walls (4a, 4b).

The above-mentioned partition walls (4a, 4b) of this embodiment are constructed by providing a horizontal partition wall 4b that divides the partition wall 4a into two equal parts at right angles in addition to the conventional vertical partition wall 4a. It is characterized by being formed in the shape of

Therefore, the porous refrigerant pipe 2 of this embodiment has twice the number of refrigerant passages 5 compared to the porous refrigerant pipe 2 shown in FIG.
The heat transfer area of the refrigerant is doubled, and the internal partition walls (4a,
4b) (IJ thickness tl, t2) can be made thinner without reducing the strength as described below, so the cross-sectional area of the refrigerant passage 5 does not decrease. Therefore, if the porous refrigerant pipe 2 of this embodiment is applied to the condenser 1 shown in FIG. 1, the cooling performance of the condenser 1 will be improved.

In addition, the thicknesses of the partition walls (4a, 4b) are tl and t2.
) is 0.2 to 0.4 with current extrusion processing technology.
It can be made as thin as +u, but as the thickness Ll, t2) of the partition walls (4a, 4b) becomes thinner, the buckling strength of the partition walls (4a, 4b) also decreases accordingly.
When bending the porous refrigerant pipe 2 into a meandering shape as shown in FIG. buckle.

Here, when bending the porous refrigerant pipe 2, the stress applied to the porous refrigerant pipe 2 is the Calano stress in the direction of the arrow in FIG. It is. Generally, when the thickness tl of the partition wall 4a is constant,
The buckling strength of the partition wall 4a against stress from the entrance direction is:
It is inversely proportional to the square of the length hl of the partition wall 4a. That is,
Thickness of partition wall 4a 1. are the same, the shorter the length of the partition wall 4a, the higher the buckling strength of the partition wall 4a.

Therefore, in this embodiment, as described above, the vertical partition wall 4
Since the horizontal partition wall 4b is provided to divide a into two, the length of the vertical partition wall 4a, which used to be hl, has been shortened to h2 (h2=h+/2). ing.

Therefore, if the thickness tl of the partition wall 4a is the same, the buckling strength is four times higher than that of the conventional structure shown in FIG. In other words, the thickness of the partition wall 4a is 1. Even if it becomes thinner than before, it can maintain the same strength as before.

Next, other embodiments of the present invention will be described. Figure 4 shows
This figure shows the cross-sectional shape of the porous refrigerant pipe 2 of the embodiment shown in FIG. 2, which is characterized by increasing the number of horizontal partition walls 4b described in the first embodiment to two. Therefore, when compared with the conventional porous refrigerant pipe 2 shown in FIG. 2, the number of refrigerant passages 5, that is, the heat transfer area of the refrigerant, is tripled. Further, since the length h3 of the partition wall 4a in the vertical direction is 1/3, the buckling strength of the partition wall 4a is improved by nine times. That is, even if the thickness of the partition wall 4a is reduced, sufficient buckling strength can be obtained.

Although there are two horizontal partition walls 4b, if the number is further increased, the heat transfer area of the refrigerant and the buckling strength of the vertical partition walls 4a will naturally increase.

FIG. 5 shows the cross-sectional shape of the porous refrigerant pipe 2 of the third embodiment, where the vertical partition wall 4δ is different from the horizontal partition wall 4b.
As shown in the figure, it is shifted by β in the horizontal direction.

The cross-sectional shape of the partition walls (4a, 4b) of this third embodiment is as follows:
This is included in the lattice shape referred to in the present invention. In this case, with the porous refrigerant %-2 of the third embodiment, the heat transfer area of the refrigerant is almost twice that of the conventional one shown in Figure 31, as in the first embodiment, and the ih force direction partition wall The buckling strength is four times higher.

Further, as in the second embodiment, it goes without saying that by increasing the number of horizontal partition walls 4b, the heat transfer area of the refrigerant and the strength of the vertical partition walls are improved.

Further, in the embodiments described above, the present invention is applied to the condenser 1 of a cooling/refrigeration system, or it can be applied to an evaporator as well as a condenser.

As described above, in the present invention, since the partition walls inside the porous refrigerant pipe are shaped like a lattice, the buckling strength of the partition wall is improved compared to the conventional method. This has the effect that the internal partition wall does not buckle during processing (the partition wall can be made thinner).

Further, by making the partition wall inside the porous refrigerant pipe into a lattice shape, the number of parallel refrigerant passages increases and the heat transfer area of the refrigerant increases. Moreover, since it is possible to reduce the thickness of the internal partition wall, the cross-sectional area of the refrigerant passage does not decrease even if the number of partition walls increases. As a result, there is an effect that the performance of the heat exchanger is also improved.

[Brief explanation of drawings]

Fig. 1 is a perspective view of a condenser to which the porous refrigerant pipe of the present invention is applied, Fig. 2 is a sectional view showing the internal structure of a conventional porous refrigerant pipe, and Fig. 3 is a perspective view of a condenser to which the porous refrigerant pipe of the present invention is applied. 4 is a sectional view showing the internal structure of the porous refrigerant pipe according to the second embodiment of the present invention. FIG. 5 is a sectional view showing the third embodiment of the porous refrigerant pipe of the present invention. It is. ■... Condenser, 2... Porous refrigerant pipe, 3... Collaget fins, 4a, 4b... Internal partition wall. Representative Patent Attorney Takashi Okabe

Claims (1)

[Claims] In a heat exchanger that combines a porous refrigerant pipe having a flat cross-section and being bent and enclosed in a serpentine shape, and corrugated fins joined to this multi-fL refrigerant pipe, A heat exchanger characterized in that a grid-like partition wall is provided to form parallel refrigerant passages.