JPH07104115B2 - Heat exchanger - Google Patents

Description

Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a plate fin type heat exchanger having a vertically stacked structure, and more particularly to measures for preventing the rectifying fins from collapsing.

[Conventional technology]

The plate fin type heat exchanger has a large heat transfer area per unit volume and is widely used as a relatively small and highly efficient heat exchanger. It can be divided into three types: counter-current type, counter-current type, and orthogonal (oblique) flow type. As the air-to-air heat exchangers used in air conditioners, counterflow type and crossflow type are usually adopted, but until now the basic structure has been as shown in Fig. 15. Plate that divides two fluids (10
1) is vertically laminated with a corrugated plate-shaped rectifying fin (102) forming a plurality of rows of parallel flow channels sandwiched therebetween. This first
In the air conditioner shown in Fig. 5, the plate (101) is made of a paper material based on Japanese paper having both heat conductivity and moisture permeability, and the rectifying fins (102) are the same as the plate (101). It is obtained by processing the material into a corrugated plate. However, as described above, in a heat exchanger having a laminated structure in which a corrugated plate-like rectifying fin (102) is sandwiched between flat plate-shaped plates (101), two members must be alternately laminated in the vertical direction. Therefore, there is a problem that the manufacturability is poor and that the directionality of the rectifying fins (102) is likely to vary during the stacking.

As a measure to solve the above-mentioned problems in manufacturing, there is a method of integrally forming a unit heat exchange member on one surface of a plate by extruding a solid rectifying fin. The shape is as shown in Fig. 17 in order to prevent the difference in plate thickness between the rectifying fin (3) and the plate (2) from being so great or to reduce the material of the rectifying fin (3). Rectifying fins as shown (3)
The lower bottom width dimension T must be smaller than its height dimension H. Specifically, when the height dimension H is about 2 mm,
The bottom width T was about 0.1 to 0.8 mm and T / H was in the range of 0.05 to 0.4.

[Problems to be solved by the invention]

As described above, in the case where the solid rectifying fins are integrally formed on the plate by extrusion, the width of the bottom of each rectifying fin is small. The rectifying fins (3) are liable to fall down, which is a cause of damage to the plate, or has a drawback such as a decrease in performance such as air leakage.

An object of the present invention is to prevent the straightening fins from collapsing and to reduce the amount of material used so as to solve the above-mentioned conventional drawbacks.

[Means for solving problems]

In the case of the present invention, the cross-sectional shape orthogonal to the longitudinal direction of each rectifying fin is specified, and the lower bottom width dimension T of each rectifying fin is set to T / H of 0.5 to 1.5 with respect to its height dimension H. It is set within the range to prevent each rectifying fin from collapsing during stacking.

[Action]

In the case of the present invention, the amount of material used can be reduced by specifying the cross-sectional shape of each rectifying fin, and due to the increase in T / H of each rectifying fin, the rectifying fin itself has a reaction force against falling. Will occur.

〔Example〕

First, considering the direction of force and the tilting direction when a conventional rectifying fin having the shape shown in FIG. 20 is diagonally struck by a load from above, the rectifying fin (3) is tilted as shown in the figure. , When the unit heat exchange member (4) in the upper stage is placed on this and a load is applied, a downward force F is applied to the upper part of the rectifying fin (3), and a reaction force F ₁ against it is generated at the lower bottom part. In addition, the rotational force A is generated by these two forces F and F ₁ , so that the rectifying fin (3) falls. From this, in the case of the heat exchanger of the present invention shown in FIG. 1, each rectifying fin is formed as shown in FIGS. 2 and 3, and in this case, as shown in FIG. H becomes about 1, so that this rectifying fin is
When the same unit heat exchange member (4) is placed on the same angle as in the case of the figure and a load is applied, a rectifying fin (3)
Since the force F and the reaction force F _{1 applied to} are in the state shown in FIG. 3, the rotational force A is applied in the direction to prevent the collapse, which can prevent the commutation fins from falling during stacking. Becomes Specifically, if the allowable tilt angle of the rectifying fin is 25 °, the T / H should be 0.47 or more, and if the allowable tilt angle is 60 °, the T / H should be 1.732, which is the above-mentioned commercially available current It has been experimentally confirmed that it is optimal to set the above T / H to about 0.5 to 1.5 in the case of a plate material having both heat conductivity and moisture permeability.

Further, FIGS. 4, 5 and 6 show an embodiment of the present invention in consideration of the reduction of the amount of the material used as the rectifying fin. That is, it is sufficient to set T / H to a minimum of 0.5 to prevent the rectifying fin from collapsing as described above, but it is desirable to set T / H to about 1 effectively. However, in the case of this shape, the amount of material used as the rectifying fins is twice as much as that in the case of T / H = 0.5, and the cost increases accordingly, so in order to improve this, in the longitudinal direction of the rectifying fins. Let the orthogonal cross-sectional shape be a trapezoid of lower bottom width dimension T, upper bottom width dimension W, and height H, for example, as shown in FIGS. 4 to 6, and reduce the amount of material used while securing the lower bottom width dimension T. In this case, for example, T / H = 1.0, W / T = 0.2
When set to, the cross-sectional area of the rectifying fin is Therefore, this is the same as in the case of a rectangular cross section with T / H = 0.6. Then, when the amount of change in the height of the bottom surface due to the same inclination occurs at this time, the trapezoid of T / H = 1.0 is T / H = 0.6.
In the case of the rectangle, it is 1.67 times, and since the inclination of 1 / 1.67 occurs only for the displacement of the same plate, the stability is improved.
That is, by making the cross-sectional shape trapezoidal, it is possible to save the materials used while ensuring the stability of the rectifying fins. When the W / T at this time is 0.4 or less, the material reduction effect is high, but due to the molding method of this shape, etc., it is used within the range of 0.1 to 0.9.

Further, FIGS. 7, 8 and 9 are examples for further reducing the amount of material used as compared with the above trapezoidal rectifying fin, and W / T in these cases is within the range of 0.1 to 0.9. Is set to. Further, since the plate for partitioning the fluid is made of a material having heat conductivity and moisture permeability, total heat exchange is possible, and heat recovery efficiency as an air-to-air heat exchanger can be increased.

Others FIG. 10 shows a pair of upper and lower flow passages for alternately passing two air streams to be heat-exchanged, the inlets (5) of which are arranged side by side on the same side of the front and the outlets (6) are opposite to each other. This is the case where the rectifying fin configuration shown in FIGS. 2 to 9 is applied to the counterflow type heat exchangers opened on both sides so as to face the direction, and FIGS. 11 and 12 show the crossflow type and This is a case in which a connecting plate (7) is inserted in a bridging state at the ends between the rectifying fins of the counterflow heat exchanger, and the rectifying fins in these cases are also shown in FIGS. The rectifying fin configuration shown in FIG.

Further, in FIGS. 13 and 14, the outermost rectifying fins are formed wider than the other rectifying fins to improve the assemblability at the time of forming the heat exchanger and prevent air leakage in the completed state. 2 shows the cross flow type and counter flow type unit heat exchange members, and the rectifying fins shown in FIGS. 2 to 9 are similarly implemented.

〔The invention's effect〕

As described above, the heat exchanger of the present invention has good productivity because a unitary heat exchanging member is formed by integrally molding a solid rectifying fin by extrusion on one surface of a flat plate having heat conductivity. Moreover, there is an effect that the performance does not deteriorate due to the fall of the rectifying fins after the assembly and the material cost can be reduced.

[Brief description of drawings]

FIG. 1 is a perspective view showing a cross-flow heat exchanger as an application example of the present invention, and FIG. 2 is a side view showing a dimensional relationship of rectifying fins in a unit heat exchange member showing an embodiment of the present invention,
FIG. 3 is a side view showing the force relationship when the fall of the rectifying fins is corrected, and FIGS. 4, 7, 8 and 9 are other unit heats of other embodiments of the present invention. FIG. 5 is a side view showing the exchange member, FIG. 5 is a side view showing the dimensional relationship of the rectifying fins in FIG. 4, and FIG. 6 is a side view showing the force relationship when the fall of the rectifying fins is corrected. FIG. 10 is a perspective view showing a counterflow type heat exchanger in which the rectifying fin structure of the present invention is implemented, and FIG. 12 is another embodiment in which connecting plates are inserted at the ends between the rectifying fins. FIG. 11 is a perspective view showing another embodiment in which a connecting plate is provided at each end between the rectifying fins in the cross-flow heat exchanger in which the rectifying fin structure of the present invention is implemented, Figures 13 and
FIG. 14 is a perspective view showing a unit heat exchange member for cross-flow type and counter-flow type heat exchangers in which the rectifying fin structure of the present invention in which the outermost rectifying fin is formed wider than other rectifying fins is used. Fig. 15 is a perspective view showing a conventional cross-flow heat exchanger,
FIG. 16 is a side view showing a conventional unit heat exchange member, FIG. 17 is a side view showing the dimensional relationship of the rectifying fins, and FIGS. 18 and 19 are side views showing the fall of the rectifying fins, 20. [Fig. 6] is a side view showing a force relationship when the rectifying fins fall. In the figure, (1) is a heat exchanger, (2) is a plate, and (3)
Is a rectifying fin, (4) is a unit heat exchange member, (5) is an inlet, (6) is an outlet, (7) is a connecting plate, T is the bottom width, H is the height, and W is the top width. The dimensions are shown.

Claims (5)

[Claims] 1. A unit heat exchange member, which is integrally formed by extruding a solid rectifying fin in an upright state on one surface of a flat plate having heat conductivity and moisture permeability, is laminated in a plurality of rows in the vertical direction, In a structure in which two air streams to be heat-exchanged are alternately passed through the flow passages partitioned by the plates to perform heat exchange of air to air, the cross-sections orthogonal to the longitudinal direction of the rectifying fins are crossed. A heat exchanger characterized in that a surface shape is set such that a ratio T / H of a fin bottom width dimension T and a fin height dimension H is within a range of 0.5 to 1.5. 2. The cross-sectional shape of each rectifying fin has a lower bottom width dimension T,
The heat exchanger according to claim 1, wherein the heat exchanger has a trapezoidal shape in which W / T is 0.1 to 0.9 when the width W of the upper bottom is set. 3. A pair of upper and lower flow passages for alternately passing two air streams to be heat-exchanged are provided on both sides so that the inlets thereof are on the same side of the front face and the outlets are oriented in opposite left and right directions. Claims 1 and 2 formed in a counter-flow type
The heat exchanger described in any one of the items. 4. The heat exchanger according to any one of claims 1, 2 and 3 in which a connecting plate is inserted in a bridging state at the ends between the respective rectifying fins. . 5. A rectifying fin formed on one side of a flat plate, wherein the outermost rectifying fin has a wider connecting surface with the plate than the other rectifying fins therebetween. The heat exchanger described in any one of item 1, item 2, item 3, and item 4.