JPH0198896A - Heat exchanger - Google Patents

Abstract

PURPOSE:To improve a heat exchanging performance by a method wherein inner fins are integrally formed with louvers for crossing flow of heat exchanging medium between the adjoining heat exchanging medium passages defined by the inner fins. CONSTITUTION:Although coolant passes within a flat tube 4 along a plurality of coolant passages 7 defined by inner fins 10, the inner fins 10 are formed with several louvers 11, so that the coolant which is apt to flow toward a downstream side of the coolant passages 7 is changed in its flow direction by the louvers 11. The louvers 11 are cut and raised toward the coolant passages 7 adjacent to the upstream side of the air flow. The coolant flowing in the coolant passage 7 at the downstream side of the air flow direction is guided toward the coolant passages 7 adjacent to the upstream side of the air in sequence. The coolant is guided between the adjoining coolant passages 7 toward the high condensing side, so that the coolant may be mixed to each other and then there is no difference in temperature between the coolant passages 7 in a direction of air flow. Due to this fact, no eccentric condensation of air is generated and thus an efficiency of heat exchanging operation is improved.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a heat exchanger used in near conditioners for vehicles and homes.

[Prior art 1] As is well known, a heat exchanger exchanges heat by thermal conduction between a heat exchange medium flowing inside a tube and air flowing outside the tube, and in the case of a near conditioner, the heat exchange medium It is designed to heat or cool the outside air.

The structure of a conventional heat exchanger of this type will be explained based on a car air conditioner condenser shown in FIGS. 10 to 12.

In the figure, 1 is the inlet header, 2 is the outlet header, and 3.
3 is a side plate, 4 is a flat tube, and 5 is a corrugated fin as an outer fin.

The flat tube 4 is formed into a flat cross-sectional shape by extruding or drawing a metal with excellent thermal conductivity such as aluminum, and is provided between the inlet header 1 and the outlet header 2.
They are spanned and joined by brazing material so as to form a meandering path as a whole.

The full gate fin 5 as an outer fin is also made of a metal plate having excellent thermal conductivity, such as aluminum, processed into a corrugated shape, and is joined between adjacent flat tubes 4 via a brazing material. Note that the joint structure between the flat tube 4 and the full gate fins 5 is called a core portion.

In such a configuration, a heat exchange medium, for example, a gasified thermal refrigerant, is supplied from the inlet header 1, and this gas refrigerant is flowed along a meandering path through the flat tubes 4... to the outlet header. 2, and during this time, external air is forced to pass through the corrugated fins 5 as shown by the arrow by a fan or the like (not shown). Then, heat is exchanged between the gas refrigerant and the air, the thermal refrigerant is cooled by the external air, and the gas refrigerant is condensed. That is, this heat exchanger functions as a condenser.

By the way, in the past, in order to increase heat exchange efficiency, the first
As shown in FIGS. 1 and 12, the flat tube 4
has partition walls 6 formed integrally, and these partition walls 6.
... has adopted a structure in which the refrigerant passage is divided into a plurality of passages 7....

In this way, the area in which the heat exchange medium contacts the surface of the flat tube 4 increases, improving thermal conductivity and improving heat exchange efficiency.

However, such partition walls 6 are formed at the same time as the flat tube 4 is processed by extrusion or drawing, and therefore the wall thickness of partition walls 6 cannot be made very thin, and the passages 7... The size of the heat exchange medium cannot be made small, so there is a limit to the number of divided passages, and there is a limit to increasing the contact area of the heat exchange medium with the flat tube 4.

For this reason, as shown in FIGS. 13 and 14, instead of the partition wall 6, a structure in which a corrugated inner fin 8 is fitted into the flat tube 4 and brazed has been developed. ing. According to this, the inner fin 8 is formed independently of the extrusion or drawing process of the flat tube 4, so it is not restricted by the plate thickness or the pitch of the corrugations, and therefore the size of each passage 1 can be controlled. It can be made smaller, the number of divided passages can be increased, and the contact area of the heat exchange medium with the flat tube 4 can be increased.

[Problems to be Solved by the Invention] However, in general, in this type of heat exchanger, the heat exchange performance tends to be high on the air inlet side, and therefore, the heat exchange medium in the flat tube 4 is along the temperature distribution (shown as characteristic T in FIGS. 12 and 14).

) occurs.

As a result, as in the conventional car air conditioner condenser shown in FIGS. 12 and 14, the refrigerant passages 7 and
In the case of a structure in which the refrigerant passage 7 on the upstream side of the airflow is divided, the refrigerant is quickly condensed and condensate accumulates, and on the downstream side, the refrigerant remains in a gasified state. Therefore, an imbalance occurs in the flow of the refrigerant within the flat tube 4, resulting in a problem that heat dissipation performance becomes insufficient.

The present invention aims to provide a heat exchanger that eliminates temperature differences in refrigerant between refrigerant passages divided along the direction of airflow and improves heat exchange performance.

[Means for Solving the Problems] The present invention integrates a louver into an inner fin fitted into a flat tube, which allows the flow of a heat exchange medium to be exchanged between adjacent heat exchange medium passages partitioned by the inner fin. It is characterized by being formed.

[Function] According to the configuration of the present invention, the louvers formed in the inner fins allow the heat exchange medium to interact between adjacent passages, thereby reducing the occurrence of temperature differences between the partitioned passages. Since uneven heat radiation and condensation are prevented from occurring, heat exchange performance is improved.

[Example] The present invention will be described below based on a first example shown in FIGS. 1 to 4.

In this embodiment, the flat tube 4 and the outer fin 5 may be the same as the conventional ones, and in this embodiment, the flat tube 4
The inner fin 10 housed inside is different from the conventional one.

That is, by fitting the inner fin 10 processed into a corrugated shape into the flat tube 4, a plurality of refrigerant passages 7 are formed inside the flat tube 4 along the air flow direction.
The inner fin 10 has a large number of louvers 11 cut and raised.

These louvers 11 are in the shape of tongues that are cut and raised obliquely toward the end along the flow direction of the refrigerant and further toward the downstream side in the flow direction of the refrigerant.

In such a configuration, the refrigerant is passed in the direction of arrow B, and the outside air is forcibly blown in the six directions of arrows by a fan (not shown).

Inside the flat tube 4, the refrigerant tries to pass along a plurality of refrigerant passages 1 divided by inner fins 10, but this inner fin 10 has a large number of louvers 11.
. . is formed, the refrigerant flowing toward the downstream side through the refrigerant passages 7 . . . has its flow direction changed by the louvers 11 . That is, since the louvers 11 are cut up toward the refrigerant passages 7 adjacent to the upstream side in the air flow direction, the refrigerant flowing through the refrigerant passages 7 on the downstream side in the air flow direction is The air is sequentially guided toward the refrigerant passages 7 adjacent to the upstream side in the air flow direction.

That is, the refrigerant is guided between adjacent refrigerant passages 7 in the direction of high condensation performance, and therefore the refrigerants interact and mix, resulting in a temperature difference between the refrigerant passages 7 in the direction of air flow. It will no longer occur.

Therefore, condensation does not occur unevenly, and heat exchange efficiency is improved.

Note that the present invention is not limited to the first embodiment described above.

That is, FIGS. 5 to 7 show a second embodiment of the present invention, in which the inner fin 20 of this embodiment has tongue-shaped louvers 21, 22, etc. formed adjacent to each other. Moreover, these louvers 21..., 22... are formed in opposite directions.

With such a structure, the refrigerant is alternately exchanged between the refrigerant passages 7 adjacent to each other in the air flow direction, thereby preventing a temperature difference from occurring.

Further, FIGS. 8 and 9 show third and fourth embodiments of the present invention, and the inner fin 30 of these embodiments.
40 are louvers 31..., 32...

41 . . . , 42 . . . are formed of stamped-out ribs with one end open, and even in this case, the same effects as in the previous embodiment can be obtained.

Furthermore, the present invention is applicable not only to a condenser in a near conditioner but also to an evaporator and various other heat exchangers.

[Effects of the Invention] As explained above, according to the present invention, the louvers formed in the inner fins allow the heat exchange medium to exchange between adjacent passages, and therefore the heat exchange medium exchanges between the refrigerant passages divided along the direction of air flow. Temperature differences in the refrigerant are reduced. This prevents uneven heat radiation, condensation, etc. from occurring within the flat tube, thereby improving heat exchange performance.

[Brief explanation of the drawing]

1 to 4 show a first embodiment of the present invention, FIG. 1 is a perspective view of a core portion consisting of an outer fin and a flat tube, FIG. 2 is a perspective view of an inner fin, and FIG. 3 is a flat tube. FIG. 4 is a sectional view taken along line rV-IV in FIG. 1, FIGS. 5 to 7 show a second embodiment of the present invention, FIG. 5 is a perspective view of the inner fin, and FIG. is a front view of the flat tube, Figure 7 is a cross-sectional view corresponding to Figure 4, and Figure 8 is a front view of the flat tube.
9 and 9 are perspective views of inner fins showing third and fourth embodiments of the present invention, respectively, and FIGS.
The figures show the conventional structure, Fig. 10 is a perspective view showing the entire heat exchanger, Fig. 11 is a perspective view of the core section consisting of outer fins and flat tubes, and Fig. 12 is x - in Fig. 11.
13 and 14 show other conventional structures, FIG. 13 is a perspective view of the core section consisting of an outer fin and a flat tube, and FIG.
It is a sectional view taken along the V-xrv line. 1...Inlet side header, 2...Outlet side header, 4...
・Flat tube, 7... Refrigerant passage, 10.20.30
．． 40... Innafin, 11.21.22.31.
32.41.42...Luba. Patent attorney Takehiko Suzue Figure 1 Figure 3 Figure 6 Figure 7 Guan 8 Figure 9

Claims (1)

[Scope of Claims] A heat exchanger in which a flat tube through which a heat exchange medium passes is provided with an inner fin that divides the inside of the flat tube into a plurality of heat exchange medium passages, A heat exchanger characterized in that a louver is integrally formed to exchange the flow of a heat exchange medium between adjacent heat exchange medium passages.