JPH0654198B2 - Stacked heat exchanger - Google Patents

Description

TECHNICAL FIELD The present invention relates to a laminated heat exchanger, for example, a laminated heat exchanger suitable for use as a refrigerant evaporator in a refrigeration cycle in an automobile air conditioner. Regarding

[Conventional technology]

The shape of the core plate 100 of the refrigerant evaporator which is a conventional laminated heat exchanger is as shown in FIG. 5, and an inlet side header portion 103 and an outlet side header portion 104 are provided in parallel at one end thereof. , 104 project toward the back side of the paper. In addition, the through hole 10
5, 106 are provided, and both the header portions 103,
A center rib 107 is provided from an intermediate position of 104 to a midpoint in the longitudinal direction of the core plate 100, forming a U-shaped refrigerant passage 102 and forming a U-turn portion 108. Reference numeral 101 denotes a rib provided by press working, which is regularly inclined in one direction to appropriately disperse the refrigerant in the refrigerant passage 102. The core plates 100 are joined to face each other to form a heat exchange unit. In this heat exchange unit, as shown in FIG. 6, the rib 101 of the lower core plate 100 shown by the solid line and the upper core plate shown by the dotted line are shown. Ribs 101 of 100 are combined in an X shape, and are brazed at 109 at the intersection of the X shapes to form a complicated refrigerant passage, and a zigzag refrigerant flow as indicated by arrows in the drawing is performed. The heat exchange unit is formed such that the outer peripheral edge portion 110 of the your plate 100, the center rib 107, and the rib 101 are joined to each other by brazing at the intersection 109 of the X-shaped joints.

And a large number of heat exchange units are laminated and connected in parallel, and heat-dissipating corrugated fins are provided between the heat exchange units.
The inlet-side header and the outlet-side header formed of the respective header parts are respectively connected to the condenser side and the compressor side to form a laminated evaporator.

[Problems to be solved by the invention]

However, in the conventional device described above, the core plate 10
The ribs 101 are joined in an X-shape in the U-shaped refrigerant passage 102 in the state where 0 is opposed to each other to form a heat exchange unit, and the refrigerant flows approximately in a zigzag manner. In the U-turn portion 108 where the flow of the refrigerant changes direction, the pressure loss of the refrigerant becomes very large because the refrigerant flows in a more zigzag manner.
Further, since the U-turn groove is not provided with the center rib 107, there is a problem that the pressure resistance is low and the portion is always broken from this portion. Therefore, an object of the present invention is to improve the pressure resistance of the U-turn portion in the U-shaped refrigerant passage and reduce the pressure loss.

[Means for solving problems]

Therefore, in the present invention, in order to achieve the above-mentioned object, a U-shaped refrigerant passage is formed by a center rib formed halfway in the longitudinal direction between an inlet-side header portion and an outlet-side header portion provided in parallel at one end. Forming a heat exchange unit by facing each other to form a heat exchange unit, stacking a large number of the heat exchange units, forming an air flow path between the adjacent heat exchange units, and performing heat exchange on the air flow path. In the laminated heat exchanger provided with the fins, the core plate is substantially V-shaped symmetrically with respect to the longitudinal centerline of the core plate in the U-turn portion of the U-shaped refrigerant passage. It adopts the technical means that it has a U-turn rib stamped on.

[Action]

To explain the operation of the above technical means, by providing a substantially V-shaped rib in the U-turn portion of the U-shaped refrigerant passage in the heat exchange unit, the flow of the refrigerant in the U-turn portion is not a zigzag flow. Since the flow of the refrigerant is rectified by the substantially V-shaped ribs in the U-turn portion and flows very smoothly, the pressure loss of the refrigerant in the U-turn portion can be reduced. Furthermore, the rib in the V-shape at the U-turn is
When the heat exchange unit is formed, the ribs are brazed over the entire surface, so that the joining area can be made much larger than that of the conventional ribs joined in an X shape and brazed only at the intersections.

〔Example〕

The present invention will be described below with reference to embodiments shown in the drawings. First to
FIG. 3 shows a laminated refrigerant evaporator 1 of an air conditioner for an automobile according to the present invention. The evaporator 1 is formed by stacking a large number of heat exchange units 3 each including two core plates 2, and an inlet header 4 is provided on the front side of the upper end of the evaporator 1 in the drawing.
However, an outlet header 5 is provided in parallel with the inlet header 4 on the inner side of the upper end in the drawing. The inlet-side header 4 and the outlet-side header 5 are formed by stacking header portions 13 and 14 of the core plate 2 described later. Further, a flat air passage 23 is formed between the adjacent heat exchange units 3, and each air passage 23 has a corrugated fin 24.
Are installed.

As shown in FIG. 2, each heat exchange unit 3 is composed of a pair of core plates 2 facing each other. Core plate 2
Is an aluminum plate material (thickness 0.5
~ 0.6 mm) is pressed, and the outer peripheral edge 12
Is left and the whole is molded in a dish shape, and at one end, header portions 13 and 14 for the inlet and outlet of the refrigerant are bulged downward in the direction perpendicular to the paper surface. Further, through holes 15 and 16 through which the refrigerant flows are punched out by presses in the parts forming the header parts 13 and 14, respectively. The embossing ribs 17 are composed of long ribs 17a and short ribs 17b which are regularly embossed vertically upward in the plane of the drawing with a certain inclination angle.

The ribs 17 are provided on the left and right of the center rib 18 which is punched upward from the middle of the header portions 13 and 14 in the longitudinal direction of the core plate to the middle of the sheet. , U-turn portion 19 is formed. The U-turn portion 19 also has a rib protruding upward in the plane of the drawing, but here, a U having a substantially V shape is symmetrical to the center line XX in the longitudinal direction of the core plate 2.
The turn ribs 20 are combined. U-turn rib 20
In the corner portion of the core plate 2, a linear rib 20a parallel to a part of the V-shaped diagonal line is provided. Further, triangular ribs 20b are provided at the corners of the core plate 2. This is to obtain a large brazing area as much as possible when brazing the core plate 2 and to obtain a joining force.

Reference numeral 21 is a refrigerant passage for connecting the inlet side header portion 14 of the core plate 2 to the outlet side header portion 15 in a U-shape. Here, the outer peripheral edge portion 12, the ribs 17a and 17b,
Since the center rib 18 and the ribs 20, 20a, 20b are punched out at the same height, when forming the heat exchange unit 3 by stacking the core plates 2 on each other, as shown in FIG. The ribs 18, the U-turn ribs 20 and the ribs 21 are coupled with the core plate 2 of the other party. Since the ribs 17a and 17b intersect in an X shape, they are joined at the intersection 22.

At this time, the ribs 17a and 17b are configured to form a zigzag flow path in an oblique direction so that the refrigerant flowing through the refrigerant passage 21 is appropriately diffused throughout the refrigerant passage 21. Such a rib 17 shape can obtain an efficient refrigerant flow rate.

Further, in the U-turn portion 19 in which the direction of the refrigerant flow is reversed, the rib 20 is stamped out in a substantially V shape, and further the linear ribs 20a and the triangular ribs 20b are provided at the corners to prevent the zigzag refrigerant flow. Since the refrigerant smoothly flows along the ribs 20, the pressure loss of the refrigerant can be suppressed, and conversely, the refrigerant flow rate increases and the heat exchange performance of the evaporator as a whole increases. By the way, in the evaporator 1, first, a large number of heat exchange units 3 are arranged in parallel, and at this time, the corrugated fins 24 are arranged in the air passages 23 formed between the heat exchange units 3 adjacent to each other. And combine them.

Of course, each component is coated on the surface with a brazing material prior to the combination. Subsequently, the combination is heated in a furnace to melt the brazing material and braze the components together.

Next, another embodiment is shown in FIG. The press-formed core plate 25 has the same shape as the U-turn portion 19 except for the rib shape.
Since the other components are substantially the same as the core plate 2, the same components as those of the core plate 2 are designated by the same reference numerals and the description thereof will be omitted.

In the core plate 25, the ribs 26 of the U-turn portion 19 are embossed in a discontinuous substantially V-shape that is symmetrical with respect to the center line of the core plate 2 in the longitudinal direction. Therefore, each rib shape consists of a linear shape, but the U-turn part 1
The triangular ribs 20a are provided at the corners of 9 as in FIG. 2, and the direction of the refrigerant flow can be smoothly changed as a whole. In this case also, the refrigerant flow is the same as in the first embodiment. The pressure loss in the passage can be kept low.

In the above embodiments, the rib shape in the U-turn portion 19 is substantially V-shaped, but the substantially V-shaped shows a wide range including continuous and discontinuous U-shaped. In the embodiment, the ribs 17 other than the U-turn portion 19 are long ribs 17.
It was a regular combination of a and the short rib 17b. The shape of the rib 17 is not limited to this, and various shapes can be considered. Next, the triangular rib 2 at the corner of the U-turn portion 19
0b may have a linear shape instead of a triangular shape if there is no problem in pressure resistance.

〔The invention's effect〕

As described above, according to the present invention, in the U-turn portion where the refrigerant flow direction of the pair of core plates constituting the heat exchange unit changes, the substantially V-shaped ribs are symmetrical with respect to the center line in the longitudinal direction of the core plates. By providing the refrigerant, the refrigerant can smoothly make a U-turn because the refrigerant flows along the ribs, so that the pressure loss can be suppressed low at the U-turn portion. Therefore, an efficient flow rate of the refrigerant can be passed through the refrigerant passage, and the heat exchange performance of the heat exchanger as a whole is improved.

Further, the rib shape at the U-turn portion is a rib shape that is symmetrical with respect to the center line, and since brazing joining at this portion is performed linearly over the entire length of the rib, the joining area can be increased and the pressure resistance can be increased. Since the pressure can be greatly increased, the pressure resistance of the heat exchange unit can be increased, and thus the pressure resistance of the laminated heat exchanger can be increased. Therefore, it is possible to provide a laminated heat exchanger having good heat exchange performance and durability.

[Brief description of drawings]

FIG. 1 is a front view showing a first embodiment of a core plate of a refrigerant evaporator for an automobile to which the present invention is applied, and FIG. 2 is a partial longitudinal section showing a front view of a refrigerant flow by joining the core plates shown in FIG. 1 to each other. FIG. 3 is an enlarged view, FIG. 3 is a sectional view of a refrigerant evaporator for an automobile using the core plate of FIG. 1, FIG. 4 is a partially enlarged front view showing a second embodiment of the core plate, and FIG. 5 is a conventional automobile. FIG. 6 is a partial front view showing a core plate of a refrigerant evaporator for a vehicle, and FIG. 6 is an enlarged partial sectional view showing a refrigerant flow when the core plates of FIG. 2 ... Core plate, 3 ... Heat exchange unit, 13, 1
4 ... Header part, 18 ... Center rib, 19 ... U turn part, 20 ... U turn rib, 21 ... Refrigerant passage, 23
...... Air passage, 24 ...... Corrugated fins (fins).

Claims (1)

[Claims] 1. A core plate that forms a U-shaped refrigerant passage by a center rib that is formed halfway in the longitudinal direction between an inlet-side header portion and an outlet-side header portion that are provided in parallel at one end and faces each other. A laminated type in which a heat exchange unit is formed by joining, a plurality of the heat exchange units are laminated, an air flow path is formed between adjacent heat exchange units, and a fin for heat exchange is provided in the air flow path. In the heat exchanger, the core plate has a U-turn rib punched out in a substantially V-shape that is symmetrical with respect to the center line in the longitudinal direction of the core plate at the U-turn portion of the U-shaped refrigerant passage. A laminated heat exchanger characterized by being provided.