JPH035512B2 - - Google Patents

Description

[Detailed description of the invention]

[Industrial Application Field] The present invention relates to a heat exchange device having a plate-fin type heat exchanger having a unique heat exchange fluid system that is not a counterflow type, counterflow type, or cross flow type (or oblique flow type). In particular, by making efficient use of the inside of the outer shell casing that houses the heat exchanger, the entire device can be made compact, installation work is simple, and highly efficient heat exchange action can be obtained. [Prior Art] Since FIGS. 3 to 7 show the basic heat exchanger used in the heat exchange device of the present invention,
First, I will explain the basics. FIG. 3 is a perspective view showing unit members for constructing a basic heat exchanger, and the heat exchange element 9 is first a corrugated plate-like fin that forms a plurality of parallel flow paths 7a to control the flow. A plate 8 that partitions two fluids to be heat exchanged is fixed to the upper and lower sides of 7 with adhesive or the like. Next, in order to provide a predetermined distribution state of static pressure loss in the fin portion, a heat exchange element 9 is prepared which is cut into a trapezoidal shape with the short side at the rear. Finally, the unit member 11 is completed by fixing the control body 10, which has both a spacer and a fluid guide function, to the end of one of the diagonally cut oblique sides with an adhesive or the like. Various materials can be used for the plate 8, such as thin metal plates, ceramic plates, and plastic plates. However, in the air conditioning field, when temperature and humidity are exchanged between supply air and exhaust air, porous materials can be used. A moisture-permeable treated paper obtained by treating paper with a chemical is suitable. The same materials can be used for the fins 7, but kraft paper is suitable for use in air conditioning. Further, similar materials can be used for the control body 10, but in the case of air conditioning, cardboard or plastic board is suitable. On the other hand, the thickness of the plate 8 and the fins 7 is preferably as thin as possible within the range of mechanical strength, specifically about 0.05 to 0.2 mm.
Furthermore, if the height of the fins 7 (corresponding to the distance between the plates 8) and the pitch (the distance between the crests in the waveform as in the example) are too large, the fluid rectification effect will be small, and if they are too small, the static pressure loss will occur. , so specifically, a range of 1 to 10 mm is suitable. In the examples, the height was 2.0 mm or 2.7 mm, and the pitch was 4 mm. On the other hand, the thickness of the control body 10 needs to be precisely aligned with the thickness of the fin 7 sandwiched between two plates 8, and when the number of laminated stages, that is, the number of layers is 100 or more as in the embodiment, If the thickness of the control body 10 is not uniform, a well-shaped heat exchanger cannot be obtained. Note that the control body 10
A commercially available adhesive is used for fixing. Next, FIG. 4 shows a perspective view of a heat exchanger HE, which forms the basis of the present invention and has a so-called trapezoidal planar shape, in which the unit members 11 configured as shown in FIG. 3 are laminated. That is, in this figure, a and a ₁ in the figure are the primary fluid M
b, b ₁ are the secondary fluid

[Problem that the invention seeks to solve]

Since the conventional heat exchanger and its outer shell casing that houses it are constructed as described above, the depth of the outer shell casing is large in proportion to the heat exchange area of the internal heat exchanger, and the contents of the outer shell casing are large. There was a lot of waste in the use of space, and there was the inconvenience that large holes had to be made in the partition walls during installation work. In view of these points, the present invention has devised the relationship between the use of the heat exchanger, which forms the basis of the present invention, and the outer shell casing that houses the heat exchanger. [Means for Solving the Problems] In the case of the present invention, the internal heat exchanger is configured so that its planar shape forms a trapezoid, and the front side of each of the primary fluid and secondary fluid passing through this is configured. The outlet is parallel to and as close as possible to the front outlet of the outer shell casing, and the drive source for the primary fluid and secondary fluid is provided so as to utilize the oblique side of the trapezoidal heat exchanger. [Function] By bringing each front outlet of the heat exchanger close to the front outlet of the outer shell casing in a parallel state, the depth dimension of the outer shell casing is reduced, and
By arranging the driving sources for the primary fluid and the secondary fluid using the oblique side of the trapezoidal heat exchanger, it is possible to eliminate wastage of the internal volume of the outer shell casing. [Embodiment] Fig. 1 shows an embodiment of the heat exchange device of the present invention, and the internal heat exchanger HE is the heat exchanger which forms the basis of the above-mentioned present invention explained in Figs. 3 to 7. In this case, as shown in the figure, a trapezoidal planar shape is used, and an outer shell casing 1 is used to house the trapezoid.
The installation work in step 4 is carried out in the same manner as in the conventional example shown in Fig. 8, and the same or corresponding parts are indicated by the same reference numerals. Each front outlet a ₁ , b ₁
is arranged parallel to and adjacent to each of the front air outlets 21 and 22 provided in the outer shell casing 14 of this heat exchanger, and the oblique side thereof is provided with both side suction ports a and b of the heat exchanger HE. A drive source 1 for the primary fluid M and secondary fluid N is provided between each of the suction ports 19 and 20 provided on the other side of the outer shell casing 14 using the oblique side of the internal heat exchanger.
7 and 18 are disposed to fill their respective suction ports to utilize the internal volume of the outer shell casing, and are characterized in that the flow path resistance of each fluid is minimized as much as possible. FIG. 2 shows another embodiment of the heat exchange device of the present invention, in which the suction port 20 for the secondary fluid N is simply provided on the rear wall of the outer shell casing 14. The difference is that the same actions and effects as those shown in Figure 1 can be expected. In summary, the occupation state of the space inside the outer shell casing of the heat exchanger in the heat exchanger of the present invention is as follows.
This is as shown by the chain line in the figure. [Effects of the Invention] Since the heat exchange device of the present invention is configured as described above, a heat exchanger with a large heat exchange area can be housed in a small outer shell casing without waste. As a result, a heat exchange device with high heat exchange efficiency and easy installation can be obtained.

[Brief explanation of the drawing]

FIGS. 1 and 2 are cross-sectional views showing an embodiment of the heat exchange device of the present invention in an installed state, and FIGS.
5, 6 and 7 are explanatory diagrams of a heat exchanger used in the heat exchanger of the present invention, and FIG. 8 is an illustration of a heat exchanger using a conventional cross flow type heat exchanger. FIG. 3 is a sectional view in an installed state. In the figure, 7 is a fin, 7a is a parallel flow path, 8 is a plate, 9 is a heat exchange element, 10 is a control body, 11 is a unit member, 12 is a space, HE is a heat exchanger, and 14 is an outer shell casing. , 17 and 18 are driving sources, 19 and 20 are suction ports,
21 and 22 are front air outlets, M is a primary fluid, N is a secondary fluid, a and b are side suction ports, and a ₁ and b ₁ are front air outlets. In other figures, the same reference numerals indicate the same or corresponding parts.

Claims (1)

[Claims] 1. Plates facing each other with a predetermined gap to partition two fluids to be heat exchanged, and a plurality of plates provided in the gap between these plates to control the flow of the fluid in the gap. a portion having fins forming parallel flow paths, forming a plurality of layers of gaps formed by the plates, and having fins located upstream of the fluid in each of the gaps of the plurality of layers; Spaces without fins located on the downstream side of the fluid are provided so as to be arranged alternately on the left and right with respect to the central lamination axis, and space portions without fins are provided at the outer ends of each of the plates, and from the opposite side, each of the layers is provided. A control body is provided that distributes and introduces the primary fluid and the secondary fluid alternately into the gap and guides them in the same direction, and the fluids are introduced from opposite directions to each other through the fins and are directed in the same direction in the space. The primary fluid and the secondary fluid, which are bent and led out in the same direction, exchange heat through the plates of each layer, and by setting a predetermined static pressure loss distribution state in the fin, the fin and the space are The heat exchanger is configured to have a trapezoidal planar shape, and the primary and secondary fluids exchange heat with each other. The front blow-off ports of the following fluids are arranged in parallel and close proximity to the front blow-off ports provided in the outer shell casing of this heat exchanger, and the oblique side is provided with the side suction ports of the heat exchanger. and a suction port provided on the other side of the outer shell casing, using the oblique side of the internal heat exchanger to provide driving sources for the primary fluid and the secondary fluid, respectively. Device.