JP2891486B2 - Heat exchanger - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger such as a condenser or an evaporator used for a car air conditioner or a room air conditioner.

Conventional technology Conventionally, a plurality of flat tubes and corrugated fins are alternately stacked as this type of heat exchanger, and both ends of each tube are connected to a cylindrical hollow header, and a partition is provided in the header, It is known that the entire heat exchange medium passage constituted by a tube is divided into a plurality of passage groups, and the heat exchange medium is configured to circulate through each passage group in a meandering manner.

By the way, in the condenser, the refrigerant passage is roughly divided into a refrigerant condensing part near the inlet side where the refrigerant is in a gaseous state and a supercooling part near the outlet side where the refrigerant is in the liquefied state. In order to increase the heat exchange efficiency, it is necessary to secure a large heat transfer area in the condensing section, and the heat transfer area in the supercooling section may be relatively small. Thus, for example,
As shown in No. 63-34466, by changing the number of tubes constituting each passage group by appropriately setting the partition position of the header, the passage cross-sectional area of the passage group was reduced from the entrance side to the exit side. Things have been suggested.

Problems to be Solved by the Invention However, in the heat exchanger as described above, since the passage sectional area of each passage group is set by the number of tubes, the passage sectional area of each passage group is set to each tube. Can be changed only stepwise for each tube cross-section area, and the necessary and sufficient passage cross-section area required for each passage group cannot be finely adjusted, or the number of partitions to increase the number of passes If the number of passages is increased, the required minimum cross-sectional area of the passage cannot be ensured, and the pressure loss increases, resulting in inconvenience that the number of passes must be limited. For this reason, it was not always possible to set the optimum state with the highest heat exchange efficiency.

The present invention has been made in view of the above-described problems, and has as its object to provide a heat exchanger with further improved heat exchange efficiency.

Means for Solving the Problems According to the present invention, the setting of the passage cross-sectional area of each passage group is not determined by the number of tubes, but tubes having different passage cross-sectional areas are used as tubes constituting each passage group. By doing so, the above-mentioned problems are solved and a design that does not increase the difficulty in assembling and manufacturing is provided.

That is, the present invention is characterized in that a plurality of flat tubes and corrugated fins are alternately laminated and hollow headers are connected and connected to both ends of the tubes, and a partition portion is provided in the headers, so that the tube Is divided into a plurality of passage groups, the heat exchange medium is configured to meander at least once, and circulates at least once, and at least an inlet-side passage group and an outlet-side passage group form a tube. Tubes with different widths and the same tube height are used, while corrugated fins with the same fin height are used. Characterized in that the heat exchange medium is reduced or increased in accordance with the volume reduction or volume increase of the heat exchange medium from the side toward the outlet side. Vessels and it is an gist.

The passage cross-sectional area of each passage group is reduced or increased in accordance with the decrease or increase in the volume of the heat exchange medium from the inlet side to the outlet side, so that the pressure loss is reduced and the heat exchange efficiency is improved. I do. In addition, the passage cross-sectional area of the passage group is reduced and increased by using tubes having only the same width but different heights, and using corrugated fins having the same height so that the tube pitch is not changed. As a result, the cross-sectional area of the passage group can be easily and delicately adjusted as compared with the case where the number of tubes is changed, and the position of the partition portion and the position of each passage group can be adjusted. The number or width can be set to an appropriate state and the core can be easily assembled.

Embodiment Hereinafter, the present invention will be described based on an embodiment applied to a condenser for a car air conditioner.

In this specification, the term aluminum is used to include an aluminum alloy.

In FIGS. 1 to 4, (1) is a plurality of tubes arranged vertically in a horizontal state, and (2) is a corrugated fin interposed between its adjacent tubes (1) and (1).

The tube (1) is made of an extruded material made of an aluminum material, and may be a porous type so-called harmonica tube. In addition, an electric resistance welded tube may be used without depending on the extruded material.

The corrugated fin (2) is also made of aluminum and is joined to the tube (1) by brazing. As the corrugated fin (1), it is desirable to use a cutout of the louver (2a).

(3) and (4) are left and right aluminum hollow headers having circular cross sections, which are connected to both ends of each tube (1). The upper ends of the left and right headers (3) and (4) are closed by upper lids (5) and (5), and the lower ends are closed by lower lids (6) and (6).

Further, a heat exchange medium inlet pipe (7) is connected to an outer upper part of the left header (3), and an outlet pipe (8) is connected to an outer lower part of the header (3). The entrance / exit pipes (7) and (8) have a header contact surface on the insertion end side formed in a corresponding shape along the headers (3) and (4), and can be easily positioned in the temporarily assembled state. By increasing the contact area with the headers (3) and (4), it is possible to join more firmly. As shown in FIG. 1, a partition plate (9) for dividing the header (3) into upper and lower chambers is provided at a longitudinally intermediate portion of the left header (3), and a total heat exchange constituted by the tube is provided. The medium passage is divided into two upper and lower passage groups (A) and (B), and the heat exchange medium flows through the passage groups (A) and (B) in a U-turn shape and flows out of the heat exchange medium outlet pipe (8). During this time, heat exchange is performed with the air flowing through the air flow gap including the corrugated fins (2) formed between the tubes (1) to condense.

In addition, (10) and (11) shown in FIG. 1 are upper and lower side plates arranged outside the outermost corrugated fin (2).

The configuration described above is the same as that of the conventional condenser, but in the condenser according to this embodiment, the width (W) of the tube (1) constituting the passage group (A) on the refrigerant inlet side (upper stage) is set. )
Is set to be larger than the width (W) of the tube (1) constituting the passage group (B) on the refrigerant outlet side (lower stage). However, the tubes (1) and (1) of both passage groups (A) and (B) are different from each other only in the width (W) and have the same height (H). The corrugated fins (2) in both passage groups (A) and (B) have the same height (h). Therefore, the tube pitch in both passage groups (A) and (B) is set to be the same. The heat exchanger core can be easily assembled by alternately stacking the tubes (1) and the corrugated fins (2).

The refrigerant passing through the upper passage group (A) is still in a gasified state with a large volume. However, since a wide tube is used as the tube (1) constituting the passage group (A), The heat transfer area is large and the refrigerant is efficiently condensed. The refrigerant passing through the lower passage group (B) exhibits a partially liquefied gas-liquid mixed state or a liquefied state and has a small volume, so that the passage cross-sectional area may be small. Since the cross-sectional area is set smaller than that of the upper stage, there is no waste of space for passing the refrigerant. As described above, by decreasing the tube width of each passage group from the inlet-side passage group (A) corresponding to the condensing section to the outlet-side passage group (B) corresponding to the subcooling section, efficient heat is obtained. The exchange will take place.

FIG. 5 shows another embodiment, which is substantially the same as the above embodiment, except that the left and right headers are each divided into upper and lower parts, and the upper and lower left and right headers (3) and (3) are connected to each other by the connecting partition member ( 12), while the right and left upper and lower headers (4) and (4) are connected in a communicating state. By adopting such a structure, manufacturing efficiency can be improved. Other configurations are the same as those of the above-described embodiment, and the corresponding portions are denoted by the same reference numerals and description thereof is omitted.

In the above embodiment, the passage cross-sectional area of the passage group on the inlet side (upper stage) is set to be larger than that of the passage group on the outlet side (lower stage). On the contrary, it goes without saying that the passage cross-sectional area of the outlet side passage group is set to be larger than that of the inlet side.

Further, in the above-described embodiment, the case where the total heat exchange medium passage is divided into upper and lower stages is shown, but the present invention can be applied even if the total heat exchange medium passage is divided into three or more stages. In the case of three or more sections, the passage cross-sectional area of the passage group may be decreased or increased in accordance with the decrease or increase in the volume of the heat exchange medium from the inlet side to the outlet side. The passage cross-sectional areas of all the passage groups do not have to be reduced or increased stepwise, and the passage cross-sectional areas may be decreased or increased for any one or more passage groups.

As described above, in the heat exchange air according to the present invention, the passage cross-sectional area of each passage group is reduced or increased in accordance with a decrease or increase in the volume of the heat exchange medium from the inlet side to the outlet side. Therefore, the pressure loss is reduced and the heat exchange efficiency is improved. In addition, since the passage cross-sectional area of the passage group is reduced or increased by adopting tubes having different tube widths, the passage cross-sectional area of each passage group is adjusted by changing half of the tubes. In comparison with this, it is possible to easily and delicately set a necessary and sufficient passage cross-sectional area required for each passage group. Instead, the passage cross-sectional area of each passage group can be arbitrarily set, so that an optimum state with the highest heat exchange efficiency can be set. Therefore, a highly efficient heat exchanger can be provided while being small.

Furthermore, the two passage groups are configured using a tube having the same tube height but having the same tube height but a corrugated fin having the same height, so that the tube and the corrugated fin are separated from each other. The heat exchanger core assembling operation, which is performed by alternately stacking, can be easily performed by a simple operation process without the need to change the tube pitch on the way, and thus the productivity can be improved.

[Brief description of the drawings]

The drawings show an embodiment of the present invention. FIG. 1 is an overall front view of a heat exchanger, FIG. 2 is a plan view thereof, and FIG.
4 is a partial perspective view showing an exploded state, and FIG. 5 is an overall perspective view showing an exploded state showing another embodiment. (1) ... tube, (2) ... corrugated fin,
(3) (4) ... header, (9) ... partition part, (A)
(B) ... heat exchange medium passage group, (H) ... tube height, (W) ... tube width, (h) ... fin height.

Continuation of the front page (58) Field surveyed (Int.Cl. ⁶ , DB name) F28D 1/00-9/02 F25B 39/00-39/04 F28F 1/00-9/26

Claims (1)

(57) [Claims] 1. A plurality of flat tubes and corrugated fins are alternately stacked, and hollow headers are connected and connected to both ends of the tubes, and partition portions are provided on the headers, so that the tubes can be used. The configured heat exchange medium passages are divided into a plurality of passage groups, and the heat exchange medium is configured to meander at least once and circulate, and the tube width is defined by at least the inlet side passage group and the outlet side passage group. In contrast, tubes with the same tube height are used, while corrugated fins with the same fin height are used. Characterized in that the heat exchanger is reduced or increased in accordance with a decrease or increase in volume of the heat exchange medium from the outlet to the outlet side.