JPS6123474B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a plate heat exchanger, which allows a fluid to be heat exchanged to be branched and distributed well to each heat exchanger plate, and to be collected well, and has excellent pressure resistance. Regarding headers.

A conventionally commonly used plate heat exchanger has a structure as shown in FIG. In FIG. 1, the upper side plate 1 seals the inside of the heat exchanger and the outside of the heat exchanger, and the heat transfer plate 3 and the side plate 1 are integrated with the seal plate 2 interposed therebetween. The space formed between the heat exchanger plate 3 and the side plate 1 communicates with the outside of the heat exchanger at both longitudinal ends of the heat exchanger. The heat exchanger plate 3 and the heat exchanger plate 6 are integrated via a seal plate 8,
The space formed between the heat exchanger plate 3 and the heat exchanger plate 6 is
Both longitudinal ends of the heat exchanger communicate with the outside of the heat exchanger in a direction perpendicular to the longitudinal direction. In addition, the heat exchanger plate 6 and the lower side plate 1 are integrated through the seal plate 2, and the space formed between the heat exchanger plate 6 and the side plate 1 is located outside the heat exchanger at both longitudinal ends of the heat exchanger. I understand.
Here, the heat exchanger plate 3 has an uneven corrugated surface 4 serving as a heat transfer portion at the center and header surfaces 9 at both ends in the longitudinal direction. In this heat exchanger, the flow direction of the two fluids is such that one fluid is parallel to the longitudinal direction of the heat exchanger plate and the other fluid is perpendicular to the longitudinal direction of the heat exchanger plate.
It becomes parallel to the longitudinal direction on the corrugated surface and emerges again at right angles to the longitudinal direction. For this purpose, seal plates 2 are attached to both ends of the heat transfer plate 3 in the longitudinal direction.
A sealing plate 8 is mounted on the heat exchanger plate 6 so that one side in the direction perpendicular to the longitudinal direction on the header surface 9 is open. If there is not much pressure difference between the two fluids separated by each heat transfer plate, a smooth header surface 9 is sufficient, but if the pressure difference between the two fluids is large, strength problems may occur. When the convex protrusions 5 and 7 are processed and stacked, the apex of the protrusion 5 and the apex of the protrusion 7 are brought into contact with each other to provide pressure resistance. However, in this case, the fluid flow paths formed within the header surfaces of the heat exchanger plates 3 and 6 become complicated, the fluid flow resistance increases, and the protrusions 5 and 7 may be displaced.

FIG. 2 is a diagram illustrating a second example of the prior art, and shows the structure of a heat exchanger in which heat exchanger plates 11 having corrugated surfaces 4 and header surfaces 10 made smooth are laminated. . In FIG. 2, the upper side plate 1 seals the inside of the heat exchanger and the outside of the heat exchanger, and the heat exchanger plate 11 and the upper side plate 1 are connected to the seal plate 2.
and are integrated via a corrugated plate 12. The space formed between the heat exchanger plate 11 and the upper side plate 1 communicates with the outside of the heat exchanger at both longitudinal ends of the heat exchanger. The heat exchanger plate 11 and the heat exchanger plate 11 below it are integrated via the seal plate 8 and the corrugated plate 13, and the space formed between these two heat exchanger plates extends in the longitudinal direction of the heat exchanger. Both ends communicate with the outside of the heat exchanger in a direction perpendicular to the longitudinal direction. Further, the heat exchanger plate 11 and the lower side plate 1 are integrated through the seal plate 2 and the corrugated plate 12, and the space formed between the heat exchanger plate 11 and the lower side plate 1 is the space of the heat exchanger. Both longitudinal ends communicate with the outside of the heat exchanger. Here header side 1
0, a corrugated plate 12 and a corrugated plate 13 are inserted between the header surfaces of the laminated heat transfer plates 11 as reinforcing materials for strength. At this time, the height of the corrugations of the corrugated plates 12 and 13 is made to match the spacing between the header surfaces. The corrugated plate 12 is for a flow path in the header in which the fluid flow direction is parallel to the longitudinal direction of the heat exchanger plate 11, and the corrugated plate 13 is for a flow path in the header in which the fluid flow direction at the inlet and outlet is perpendicular to the longitudinal direction of the heat exchanger plate 11. This is for the flow path inside the header.

In this heat exchanger, laminated heat transfer plates 1
Another corrugated plate is inserted into the fluid flowing between the header surfaces of heat transfer plate 11 and corrugated plate 1.
If the contact surfaces with 2 and 13 are not integrated by welding or brazing, problems such as vibration of the corrugated plate due to the flowing fluid will occur. Moreover, if the above-mentioned integration is not performed, the corrugated plate will not contribute as a fin or a heat transfer plate, and the heat transfer area between the two fluids via the header surface 10 will be smaller than the heat transfer area on the corrugated surface 4. As the heat exchange efficiency decreases, the heat exchange efficiency deteriorates.

The object of the present invention is to provide a plate heat exchanger having a header structure that is sufficiently reliable in terms of strength without adding reinforcing members such as fins other than the heat transfer plate to the header surface by forming the header surface on the heat transfer plate. It is to provide the equipment.

The main points of the present invention will be described below. A heat transfer plate having a heat transfer part having a corrugated surface in the longitudinal center of the heat transfer plate and a smooth header surface at both ends thereof, and a heat transfer plate having a corrugated surface in the longitudinal center of the heat transfer plate. Heat exchanger plates having corrugated surfaces with the same surface and pitch but with a longer longitudinal length and slightly smooth surfaces at both ends are laminated together. In this way, the corrugated surface and the smooth surface are combined with each other in the header section, and the high-pressure fluid is allowed to flow through the header section passage formed without the smooth surface and the top of the corrugated surface coming into contact with each other. , low pressure fluid is caused to flow through the header passage formed by the smooth surface and the troughs of the corrugated surface. Therefore, in the header portion, the smooth surface of the high-pressure fluid passage is supported by the apex of the corrugated surface of the low-pressure fluid passage, which has excellent pressure resistance.

The details of the present invention will be explained below based on the drawings.

3 to 11 are diagrams for explaining one embodiment of the present invention.

Figures 3 to 5 show one heat exchanger plate 1 of two types of heat exchanger plates used in an embodiment of the present invention.
6 is a diagram showing the structure of No. 6. 3 is a front view of one heat exchanger plate 16, FIG. 4 is a right side view thereof, and FIG. 5 is a plan view of FIG. 3. This heat exchanger plate 16
has a semicircular wavy surface 14 with unevenness at its center and a smooth surface 15 at its periphery. The pitch of the corrugated surface is d, which is the same as the pitch of the corrugated surface of the other heat exchanger plate 19, which will be described later. The length of the corrugated surface 14 is ₁ , which is equal to the length ₂ of the corrugated surface on the other heat exchanger plate 19, which will be described later.
shorter.

Figures 6 to 8 show the other heat exchanger plate 1 of the two types of heat exchanger plates used in one embodiment of the present invention.
9 is a diagram showing the structure of No. 9. 6 is a front view of one of the other heat transfer plates 19, FIG. 7 is a right side view thereof, and FIG. 8 is a plan view of FIG. 6. This heat exchanger plate 19
has a semicircular wavy surface 17 with unevenness at its center and a smooth surface 18 at its periphery. This heat exchanger plate 19 differs from the heat exchanger plate 16 described above only in the length of the corrugated surface, and the other specifications are the same. In FIGS. 3 to 8, the waveform surfaces 14, 17
are molded at a constant height and at equal pitches. Moreover, when the heat exchanger plates 16 and the heat exchanger plates 19 are laminated alternately,
The vertices of the concave and convex portions of the corrugated surface 17 of the heat exchanger plate 19 are in contact with the apexes of the convex and concave portions of the corrugated surface 14 of the heat exchanger plate 16, respectively, and a semicircular arc is formed between the heat exchanger plates. Flow paths for two fluids are configured respectively.

FIG. 9 is a front view of a heat exchanger in which two sets of heat exchanger plates 16 and 19 are stacked, FIG. 10 is a side view of FIG. 9, and FIG. 11 is a cross-section of FIG. It is a diagram. In FIGS. 9 to 11, the upper and lower ends of the stacked heat transfer plate group are sealed with side plates 1,
The end face side where the header 20 and the header 21 are not attached in the width direction of the heat exchanger plate is sealed with the outside of the heat exchanger by the seal plate 2 and the seal plate 8. On the end face side where the header 20 and the header 21 are attached, the fluid flow path where the fluid flow direction is parallel to the longitudinal direction of the heat exchanger is the seal plate 2, and the fluid flow direction is the header inlet/outlet and the heat exchanger longitudinal direction. In a fluid flow path perpendicular to the direction, the fluid flow path opening 2
The portion other than 2 is sealed with a seal plate 8. Furthermore, at both longitudinal ends of the heat exchanger, the fluid flow path is parallel to the heat exchanger longitudinal direction.The fluid flow path is open without a seal plate, but the fluid flow direction is parallel to the heat exchanger longitudinal direction at the header inlet/outlet. The fluid flow path that is perpendicular to this is sealed with a seal plate 23. The current flow situation of the two fluids is shown in Figures 9 to 1.
This will be explained using Figure 1. This heat exchange is shown when used in a low boiling point fluid, and the low pressure fluid A' is a low boiling point fluid, and the low pressure fluid header is not shown. In addition, in the figure, the corrugated surface 1 of the heat exchanger plate 19
The peaks of 7 are shown as 17a, and the valleys are shown as 17b. Also, regarding the heat exchanger plate 16, the peaks of the corrugated surface 14 are shown as 14a, and the valleys are shown as 14b.

A low-pressure fluid A' whose flow direction is parallel to the longitudinal direction of the heat exchanger passes through the flow path A shown in FIG.
It flows inside the heat exchanger from the bottom to the top in FIGS. 9 and 10. The low-pressure fluid A' flows into the flow path A formed between the troughs 14b of the heat exchanger plate 16 and the peaks 17a of the heat exchanger plate 19 at the longitudinal center of the heat exchanger, widening the flow path, After exchanging heat with other fluids, at the upper part of the heat exchanger in the longitudinal direction, again between the smooth surface 15 of the heat exchanger plate 16 and the crest 17a of the heat exchanger plate 19, and between the ridge 17a of the heat exchanger plate 19 and the side plate 1. It is discharged to the outside of the heat exchanger through a flow path A formed in . High pressure fluid
B' flows downward from the header 20 above the heat exchanger in the direction perpendicular to the plane of the paper in FIG. 9, and is distributed to the fluid passage ports 22, respectively. Fluid B' is the 11th
From the header 20 shown in the figure, it flows into the flow path B through the gap formed between the corrugated surface 17 of the heat exchanger plate 19 and the smooth surface 15 of the heat exchanger plate 16. And Figure 9, 1st
The liquid flows from the upper side of Figure 0 to the lower side through the flow path B shown in Figure 11. The flow path B is formed between the troughs 17b of the corrugated surface of the heat exchanger plate 19 and the peaks 14a of the corrugated surface of the heat exchanger plate 16. fluid
B' exchanges heat with low-pressure fluid A' flowing in channel A from below to above during the period of flow in channel B. The fluid flows into the gap formed between the corrugated surface 17 of the heat exchanger plate 19 and the smooth surface 15 of the heat exchanger plate 16 at the lower part of the heat exchanger in the longitudinal direction, and flows out through the header 21 from the fluid passage port 22. do.

Although the present embodiment has been described above for the case where the fluid flow is countercurrent, the same effect can be achieved even when the fluid flow is parallel flow.

According to one embodiment of the present invention, the corrugated surface of the heat transfer section that performs heat exchange between two fluids, and the smooth and corrugated surfaces of the header section that performs fluid distribution are continuously formed on the same heat transfer plate. The high-pressure fluid flow path in the header section is formed by the corrugated surface 17 of the heat exchanger plate 19 supported by the side plate 1 in the stacking direction of the heat exchanger plates, and the adjacent heat exchanger plate 19 constituting the high-pressure fluid flow path. It consists of the smooth surface 15 of the heat exchanger plate 16 supported by the corrugated surface 17 of This has the effect of making it possible to construct an excellent header section.

12 to 16 show other embodiments of the present invention. FIG. 12 is a front view of one heat exchanger plate 24 used in another embodiment, FIG. 13 is a side view of FIG. 12, and FIG. 14 is a plan view of FIG. 12. In another embodiment, the heat exchanger is constructed by alternately stacking the heat exchanger plates 16 and 24 shown in FIG. 3.
The heat exchanger plate 24 has a corrugated surface 25 at the center and a smooth surface 27 at the periphery thereof. Also, the waveform surface 2
The pitch of 5 is d. Therefore, in these respects, heat exchanger plate 24 and heat exchanger plate 19 are similar. However, in the heat transfer plate 24, the lengths of all the wavy surfaces 25 are not constant, and wavy surfaces having a length of ₂ and wavy surfaces having a length of ₁ are alternately provided. Therefore, the heat exchanger plate 24 has a smooth surface 26 that the heat exchanger plate 19 does not have. FIG. 15 shows the heat exchanger plate 24 and the heat exchanger plate 1.
6 shows the upper end of a heat exchanger constructed by laminating layers 6 to 6. The difference in the configuration of the heat exchanger from FIGS. 9 to 11 is that in the header part, the high-pressure fluid flow path flowing vertically downward from the page of FIG. Smooth surface 26, smooth surface 27
and the smooth surface 15 of the heat exchanger plate 16, and the other low pressure fluid flow path flowing upward in FIG. and between the smooth surface 15 of the heat exchanger plate 16. Note that the header section at the lower end of the heat exchanger also constitutes a fluid flow path similar to that at the upper end. In this embodiment, the low-pressure fluid flow path can secure a flow path area at the header portions at the upper and lower ends that is almost the same as the flow path cross-sectional area at the center of the heat exchanger plate, so the flow resistance in the low-pressure fluid path is In addition, the high-pressure fluid passage is formed by the corrugated surface 25 of the heat exchanger plate 24 supported in the stacking direction of the heat exchanger plates of the side plate 1 and adjacent to the corrugated surface 25 of the heat exchanger plate 24 constituting the high-pressure fluid passage. 25 and the smooth surface 1 of the heat exchanger plate 16 supported by the convex portion
5, it is possible to construct a header portion with excellent pressure resistance against pressure differences between two fluids.

According to the present invention, it is possible to form a header surface with a corrugated surface and a smooth surface on the heat exchanger plates themselves to be laminated, and to configure a header portion between the header surfaces of the laminated heat exchanger plates. The high-pressure fluid flow path in the section has excellent pressure resistance, and has the effect that the header section can be constructed without inserting other reinforcing members between the header surfaces.

[Brief explanation of the drawing]

Figures 1 and 2 are schematic diagrams illustrating the structure of a plate heat exchanger according to the prior art, and Figures 3 to 5 are two types of corrugated heat exchanger plates used in the plate heat exchanger of the present invention. FIG. 6 is a diagram of one of the heat exchanger plates, showing a front view, a side view, and a plan view, respectively, and FIGS. 6 to 8 are diagrams of the other heat exchanger plate of the corrugated heat exchanger plate. , respectively show a front view, a side view, and a plan view, and FIGS. 9 to 11 are diagrams for explaining an embodiment of the present invention, and FIG. 9 shows a plate heat exchanger according to an embodiment of the present invention. 10 is a side view of FIG. 9, and FIG. 11 is a header part of FIG. 9.
The sectional views, FIGS. 12 to 14, are diagrams showing corrugated heat exchanger plates used in other embodiments of the present invention.
The figure is a front view of the heat exchanger plate, Figure 13 is a side view of Figure 12, Figure 14 is a plan view of Figure 12, and Figures 15 and 16 show plate heat exchangers of other embodiments. FIG. 15 shows the header portion at the upper end of the heat exchanger, and FIG. 16 is a cross-sectional view taken from FIG. 15. 16, 19, 24... Heat exchanger plate, 14, 17, 2
5... Waveform surface, 15, 18, 26, 27... Smooth surface, 20, 21... Header.

Claims (1)

[Claims] 1 Between the laminated corrugated heat transfer plates, the peaks of the convex and convex portions of the corrugated surface of one heat transfer plate are the same as the apexes of the concave and convex portions of the corrugated surface of the heat transfer plate and the adjacent heat transfer plate, respectively. arranged so as to be in contact to form a flow path for two fluids,
A plate-type heat exchanger that allows two fluids to exchange heat to flow through the formed two-fluid flow path, and has header sections at both ends of the flow path that allow one fluid to flow. In an exchanger, a corrugated surface is formed in the center of two types of heat exchanger plates to be laminated in the same pitch and shape in the width direction of the heat exchanger plates, and these corrugated surfaces are formed on one side of the heat exchanger plate and the other side. The heat exchanger plates are formed to have different lengths in the longitudinal direction, and the periphery of the corrugated surface of these heat exchanger plates is made a smooth surface, and these heat exchanger plates are stacked to form a flat surface on both ends of the waveform surface in the longitudinal direction of the heat exchanger plate. A plate heat exchanger characterized in that a gap is formed in which a fluid can flow in the width direction of the heat exchanger plate, and a header is attached to the gap to allow the fluid to flow.