JPS6033490A - Heat exchanger - Google Patents

Abstract

PURPOSE:To permit to accommodate the heat exchanger into a small installation space equal to the same in a multi-flow type heat exchanger, constitute the flow directions of all flow paths so as to be perfect opposing flows and prevent generation of pressure loss by a method wherein high temperature fluid flow paths and low temperature fluid flow paths are formed into continuous one pair of spiral flow paths. CONSTITUTION:One piece 9 of the heat exchanger is constituted of the combined body of the high temperature fluid flow path 1 and the low temperature fluid flow path 2, which are in neighboring relation on the front and rear surfaces of a heat transfer plate 3, and is cut at every 1/2 pitches of the spiral line thereof while both end faces 10, 11 thereof are constituted so as to have a phase difference p/2 of one pitch (p) of the spiral line thereof. Accordingly, both ends of the unit spiral line, formed so as to have one pitch of the spiral line, are provided with the phase difference corresponding to one pitch (p) of the spiral line by arranging one pair of pieces 9, 9 of same shapes opposingly and connecting the opposing end faces 10, 11. According to this method, the heat exchanger may be accommodated into the small installation space equal to the same in the multi-flow type heat exchanger and, further, the flow directions of all flow paths may be constituted of perfect opposing counter-flows.

Description

[Detailed Description of the Invention] This invention relates to a heat exchanger, in which a high-temperature fluid flow path and a low-temperature fluid flow path are provided on the front and back surfaces of a heat transfer plate in an instantaneous contact relationship with a wide contact surface between them. This relates to a preheat exchanger, a so-called plate heat exchanger. Conventionally, in a multi-flow plate heat exchanger, the flow direction of each fluid flowing along both sides of the heat transfer plate is directed through the entire heat transfer surface. The feature is that the surface heat transfer coefficient is higher than that of narrow type heat exchangers because counterflow cannot be created! However, it has the disadvantage that the logarithmic average temperature difference is not large enough.To explain this using drawings, Figures 7 to 21 all show conventional plate heat exchangers. , Figure 27 shows the single flow type.
The figure shows a multi-flow type. A high-temperature fluid flow path and a low-temperature fluid flow path are provided adjacent to each other on the front and back sides of the heat transfer plate 3. Da is the inlet of high temperature fluid,! is the exit 9
%g is the inlet of the cryogenic fluid and 7 is its outlet. The solid line arrows in the figure indicate the flow direction of the high temperature fluid, and the broken line arrows indicate the flow direction of the low temperature fluid. In both cases, the flow is completely opposite, but in the multi-flow type shown in Fig. 7, the relationship in the flow direction between the flow path / and the flow path C is as follows. θ-chi is a counter flow, and the remaining 30% is a parallel flow, which means that it is not possible to obtain a large logarithmic average temperature difference.

However, if the multi-flow structure is eliminated and a single-flow structure is adopted, the installation space will increase.In addition, the turning point in the flow direction of the fluid flow path, for example, the turning point in Figure 12, will increase the installation space. In ♂171 + + +, excessive pressure loss occurred due to folded flow, which was an essential drawback of plate heat exchangers.0 This invention eliminates the above-mentioned conventional drawbacks of plate heat exchangers. However, it can be accommodated in a small installation space equivalent to that of a multi-flow type, and all flow paths can be configured to have completely opposite flow directions, and there is no excessive pressure loss in the middle of the flow path. This was done with the aim of realizing a heat exchanger that does not have a turning point in the flow direction.As a means to achieve this purpose, high temperature fluid flow channels and low temperature fluid flow channels are installed on the front and back sides of the heat transfer plate. In a heat exchanger in which channels are provided adjacently with a wide contact surface between them, the high-temperature fluid channel and the low-temperature fluid channel are configured as a pair of continuous spiral channels. 0 to K This inventive device will be specifically explained based on an embodiment shown in the drawings. In Figure 27 and Oko diagram, peace? is constructed as a combination of a high-temperature fluid flow path and a low-temperature fluid flow path provided adjacent to each other on the front and back sides of the heat transfer plate 30, and is cut at every three pitches of screwing, and the end face 10 and the is constructed so that it has a phase difference l of a of the screwing step P. Therefore, is it a pair of equal-shaped pieces? ,? 't-1 By arranging the opposing end faces /θ and // of -1 as shown in the figure and joining them, both ends of the unit screw formed as one pitch of the screw are:
As shown in Fig. 22, a phase difference corresponding to the screwing step p is provided.

Figure 23 shows a pair of pieces in the above example? , 9f
: 6 An example is shown in which each piece/, 2 in which the screws are continuously cut at each pitch is created in advance, and these pieces are sequentially connected to form a spiral shape. In this case as well, the pieces /, 2 to be connected can be created by connecting pieces of exactly the same shape.

74 is a different embodiment in which a piece 73 for configuring a spiral self-path is formed into a semicircular shape.0 piece /3 has its end face /4t and /! The layout of the 0% flow path configured to have a phase difference %t of % of the screwing step p is the same as that shown in FIG. 77. In this example, the overall structure is made of circumferential pieces that can be called a screw type. Therefore, the flow of fluid in each flow path is also different from that in Figures 72 and 73. The diagrams 0 and 1-j, which are extremely smooth, are 0-co-diagrams or og-diagrams showing an example in which one pitch of a thread is made into m by connecting 4 pieces of equal shape to each other with pieces/l. In the example shown above, the phase difference P at both ends of one pitch corresponds to the thickness of a pair of adjacent two fluid straight paths, whereas the example shown in which the phase difference is doubled is shown below. By changing t-3 times and g times, a compact heat exchanger can be formed according to the amount of water.Since the heat exchanger according to the present invention is constructed as described above, it is a multi-flow type. It can be accommodated in a small installation space equivalent to that of a , and all flow paths can be configured to have completely opposite flow directions, and there are no sharp turning points in the flow direction in the middle of the flow path. Since a smooth spiral flow is maintained throughout the entire length of the flow path, there are excellent effects such as very little pressure loss.

[Brief explanation of the drawing]

,? / Figure is a perspective view of the main parts for explaining the configuration of the device of the present invention, the top view is a side view of one embodiment of the device of the present invention, and Figures 3, 3, and 23 are each of the device of the present invention. A perspective view of a different embodiment, 7 is a front view of a conventional device, 7
Both FIG. 2 and FIG. /00. High temperature fluid flow path, 2, Low temperature fluid flow path, 30
6. Heat transfer plate, g, Otsu08. Entrance, evening, 7. ...Exit, ♂00. Turning point, also/2. /3. /Otsu16.
Peace, 10. //, /4t, /j +++ end face. 2- A'77

Claims (3)

[Claims] (1) In a heat exchanger in which a high-temperature fluid flow path and a low-temperature fluid flow path are provided adjacently with a wide contact surface between them on the front and back sides of a heat transfer plate, the high-temperature fluid flow path and the low-temperature fluid flow path are A heat exchanger characterized in that it is configured as a pair of continuous spiral flow paths. (2) The combination of high-temperature fluid flow channels and low-temperature fluid flow channels provided adjacently or in relation to each other on the front and back of the heat transfer plate is cut at each spiral/pitch, and both end surfaces are aligned with the steps of the spiral. The heat exchanger according to claim 1, wherein the heat exchanger is configured as uniform pieces having an equal phase difference, and a spiral heat exchanger body is formed by sequentially connecting a large number of the pieces. (3) A combination of a high temperature fluid flow path and a low temperature fluid flow path provided adjacently on the front and back sides of the heat transfer plate.
It is cut at every % pitch of N, and both end faces have a phase difference equal to Δ of the spiral step! Formed as a shaped piece,
The heat exchanger according to claim 7(1), wherein a vA linear heat exchanger body is formed by sequentially connecting a large number of the pieces.