JP3212350B2 - Plate heat exchanger - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a plate-type heat exchanger, and more particularly, the distance between opposed heat transfer surfaces can be set to be wide and narrow according to the type and flow characteristics of a heat exchange medium. The present invention relates to a plate heat exchanger configured as described above.

[0002]

2. Description of the Related Art A plate-type heat exchanger in which a plurality of heat transfer plates are stacked with a gasket interposed therebetween is commercially available. For example, Japanese Patent Publication No. 2-33959 proposes a plate-type heat exchanger in which the wave-contact portion of the heat transfer surface is concave in order to reduce the gap in the medium flow path when the flow rate of the heat exchange medium is different. Have been.

This heat transfer plate is formed by press working. As shown in FIGS. 6 and 7, the plate (1) has a corrugated shape formed by ridges (2) and grooves (3). I have.

The ridge (2) has an adjacent plate (4)
A recess (5) is provided in order to form a surface area where the abutment comes into contact.

[0005] When the plate (1) having the concave portion (5) and the plate (4) having no concave portion are alternately stacked, the corrugated groove (6) of the plate (4) becomes the plate (1). (5). Thus, the passage gap (7) between the two plates (1) and (4) is reduced while the other passage gap (8) is partially reduced, but the amount is relatively small.

In the plate heat exchanger having such a configuration, a medium having a large flow rate flows into a wide gap (8), and a medium having a small flow rate flows into a narrow gap (7).

[0007]

In the conventional system illustrated in FIGS. 6 and 7, a plate (1) having a recess (5) in a surface area where an adjacent plate (4) abuts on a ridge (2) is used. Since the plate heat exchanger is constructed by alternately stacking plates (4) having no concave portion (5), two types of presses are used for pressing the plates (1) and (4). A mold is required. For this reason, the manufacturing cost of the press die increases, and the productivity is reduced because the die is replaced during press working.

More specifically, when a plate type heat exchanger is used, if there is a large difference in flow conditions, temperature, etc. between the two types of media that perform heat exchange, the characteristics of each fluid are changed. It is desirable to adjust the lamination conditions of the heat transfer plate so as to obtain a lamination structure of plates having different flow path gaps.

However, in the conventional plate type heat exchangers shown in FIGS. 6 and 7, the medium passage gap has only two combinations, that is, a normal one and a slightly narrow one. It is difficult to exhibit excellent performance.

[0010]

According to the present invention, as a means for solving the above-mentioned problems, a plurality of heat transfer plates each having a heat transfer surface and a corrugated portion for generating a turbulent flow are stacked via a gasket. In the configured plate heat exchanger, the support surface of the gasket provided at the peripheral portion of the heat transfer surface is positioned substantially at the center of the forming depth of the heat transfer plate, and the heat transfer plate is disposed on the heat transfer surface. A bead having a height larger than the turbulent flow generating corrugated portion is disposed at an asymmetric position when viewed from the width direction of the heat transfer plate, and a specific one of the plurality of heat transfer plates is provided. This heat transfer plate is turned upside down on the same plane as the heat transfer plate, or the heat transfer plate is turned upside down or upside down on the heat transfer surface with the horizontal axis or vertical axis orthogonal to each other as the center of rotation. And up and down By stacking the remaining heat transfer plates that have not been inverted or turned upside down in a predetermined stacking order, the height of the flow path of the heat exchange medium between the adjacent heat transfer plates can be adjusted in a wide and narrow manner. The present invention provides a plate heat exchanger characterized by having the above structure.

[0011]

[Function] Of a plurality of heat transfer plates constituting a plate type heat exchanger, a specific one is turned upside down by 180 ° on the same plane as the heat transfer plate, or orthogonal to each other on the heat transfer surface. 180 ° upside down with the horizontal axis or vertical axis as the center of rotation, and the heat transfer plate that is turned upside down or turned upside down is combined with the remaining heat transfer plate that is not turned upside down or turned upside down in a predetermined stacking order. By overlapping, the height of the flow path of the heat exchange medium between the adjacent heat transfer plates is changed in multiple stages so as to be wide and narrow.

[0012]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A laminated structure of a plate heat exchanger according to the present invention will be described below with reference to FIGS.

The plate heat exchanger (10) has a heat transfer surface (1).
An obliquely running wavy part (12) for turbulence generation is formed in 1),
Through the corners (3A) (3B) (3C) (3
A plurality of heat transfer plates (20) each having an opening D) are stacked via a gasket (16) in a predetermined order.

In each heat transfer plate (20),
A support surface (15) for the gasket (16) is provided on the periphery of the heat transfer surface (11). This support surface (15) is located substantially at the center of the molding depth (H), that is, at the height of H / 2, as shown on the uppermost part of FIG. It is pressed so that the support portion of the gasket (16) is located at the bottom. And the heat transfer surface (11)
Above, the beads (14A) (14B) having a height larger than that of the turbulence generating corrugated portion (12) are arranged in parallel at the asymmetric position of the heat transfer plate (20) as viewed from the Y axis. are doing. In the example shown, two beads (14A) (14A) (14A) aligned in parallel with each other are arranged on the surface side of one heat transfer plate (20).
B) is provided, but is not limited thereto, as long as it is provided at an asymmetrical position when viewed from the width direction of the heat transfer plate (20), the heat exchange conditions or the heat exchange medium The number of beads to be arranged is 3 according to the change of flow characteristics
It is possible to increase more than books.

When laminating the heat transfer plates (20), as shown in FIGS. 2A, 2B, 2C, and 2D, adjacent ones of the heat transfer plates 20 are changed according to changes in the flow rate, temperature, or flow characteristics of the heat exchange medium. The height of the flow path is changed between the heat transfer plates.

FIG. 2A is a longitudinal sectional view of a heat transfer plate (20) in which the surface side of the heat transfer surface (11) and the support surface (15) of the gasket (16) face upward. In this state, the upper end of the turbulent flow generating wave portion (12) and the upper end of the spacing bead (14A) (14B) protrude upward from the heat transfer surface (11).

On the other hand, FIG. 2B shows a heat transfer surface (1).
With the front side of 1) and the support surface (15) of the gasket (16) facing upward, the heat transfer plate (20) is turned upside down by 180 ° on a plane including the heat transfer surface (11). is there. In this state, the corrugated portion (12) and the bead (14A) (14
The position of B) is left and right opposite to that shown in FIG.

FIG. 2C shows a state in which the heat transfer plate (20) is moved along the vertical axis (Y) with the heat transfer surface (11) and the support surface (15) of the gasket (16) facing upward. It is a longitudinal cross-sectional view of the heat transfer plate (20) in which the front and back surfaces are inverted by rotating 180 ° about the axis). In this state, the vertices of the corrugated portion (12) and the beads (14A) (14B) are upside down from those shown in FIG. 2 (B).

Finally, FIG. 2 (D) shows the heat transfer plate (20) with the heat transfer surface (11) facing upward and the support surface (15) of the gasket (16) facing upward. It is a longitudinal cross-sectional view of the heat transfer plate (20) in which the front and back surfaces are inverted by rotating 180 ° about the X axis) as a rotation center. In this state, the vertices of the corrugated portion (12) and the beads (14A) (14B) are upside down from those shown in FIG. 2 (A).

For convenience of explanation, the heat transfer plate shown in FIG. 2A is (20A), the heat transfer plate shown in FIG. 2B is (20B), and the heat transfer plate shown in FIG. To (20
C), the heat transfer plate shown in (D) of FIG. 2 is referred to as (20D). Hereinafter, the stacking order of the plate heat exchanger (10) and the flow path of the heat exchange medium will be described with reference to FIGS. The height adjustment procedure will be described.

In the first embodiment, as shown in FIG. 3, a heat transfer plate (20B) is superimposed on a heat transfer plate (20A) via a gasket (16), and a heat transfer plate (20) is placed on the heat transfer plate (20B). 20A) is repeated. Beads (1) between opposing heat transfer plates (20A) and (20B)
The contact of the corrugated portion (4) with the corrugated portion (12) forms a flow path for the heat exchange medium having an intermediate facing space (M) between these heat transfer plates.

In the second embodiment, as shown in FIG. 4, a heat transfer plate (20) is inserted through a gasket (16).
D) The stacking operation of stacking the heat transfer plate (20A) on the heat transfer plate is repeated. When this stacking order is adopted, the corrugated portions (12) and (20) are placed between the heat transfer plates (20A) and (20D) with which the beads (14A) (14A) and the beads (14B) (14B) are in contact. The distance (12) opposed to (12) becomes the maximum (L), and a wide flow path of the heat exchange medium is formed. In the adjacent space, that is, between the heat transfer plates (20D) and (20A), the corrugated portion (1
The bottom surface and the top surface of 2) are in contact with each other, and a heat exchange medium flow path having a minimum distance (S) is formed.

On the other hand, in the third specific example, as shown in FIG. 5, a heat transfer plate (20) is inserted through a gasket (16).
Heat transfer plate (20D), (20A), (20B) on A)
And (20A) are sequentially repeated.
Two heat transfer plates (20A) and (20B) arranged opposite to each other
By bringing the bead (14) and the corrugated portion (12) into contact with each other between the heat transfer plates (20B) and (20A),
Between these heat transfer plates, a flow path for the heat exchange medium having an intermediate facing distance (M) is formed. Also,
By bringing the bottom surface and the top surface of the corrugated portion (12) into contact with each other between the heat transfer plates (20A) and (20D), a heat exchange having a small opposing interval (S) is provided between these heat transfer plates. A medium flow path is formed. Meanwhile, the heat transfer plate (20
Between D) and (20A), between the beads (14A) (14A) and the beads (14B) (14B), a flow path of the heat exchange medium having a large facing distance (L) is formed. . As described above, the flow path configuration suitable for the medium flow rate difference can be performed by the stacking order of the plates and the mounting of the gasket corresponding thereto.

[0024]

According to the present invention, the size of the flow path of the heat exchange medium, that is, the facing arrangement, is changed by changing the stacking order of one heat transfer plate (20) and the upside-down and upside down states. The facing distance between the two heat transfer plates thus set can be set in multiple stages from the maximum value (L) to the minimum value (S). Therefore, even when there is a difference in flow characteristics such as a flow rate and a viscosity exceeding an allowable limit between the two types of heat exchange media, it is possible to select an optimal flow path size.

Further, since the plate type heat exchanger (10) can be formed from a single heat transfer plate (20) and a gasket (16), two types of heat transfer plates (1) are used as in the conventional apparatus. It is no longer necessary to use differently, and a remarkable effect can be exerted on labor saving of the assembly process of the plate heat exchanger and reduction of the manufacturing cost.

[Brief description of the drawings]

FIG. 1 is a plan view of a heat transfer plate used in the present invention.

2A is a first longitudinal sectional view of a heat transfer plate used in the present invention. FIG. 2B is a second longitudinal sectional view of a heat transfer plate used in the present invention. FIG. 2C is a heat transfer plate used in the present invention. (D) Fourth longitudinal sectional view of a heat transfer plate used in the present invention

FIG. 3 is a longitudinal sectional view for explaining a first lamination form of the heat transfer plate.

FIG. 4 is a vertical cross-sectional view illustrating a second lamination form of the heat transfer plate.

FIG. 5 is a longitudinal sectional view illustrating a third lamination form of the heat transfer plate.

FIG. 6 is a plan view of one of a pair of conventional heat transfer plates.

FIG. 7 is a longitudinal sectional view of a laminated portion of a conventional heat transfer plate.

[Explanation of symbols]

 10 Plate heat exchanger 11 Heat transfer surface 12 Corrugated portion 14A bead 14B bead 15 Gasket support surface 16 Gasket 20 Heat transfer plate L Maximum distance between heat transfer plates M Intermediate distance between heat transfer plates S Heat transfer plate Minimum facing distance of

Claims (1)

(57) [Claims] 1. A plate type heat exchanger comprising a plurality of heat transfer plates each having a heat transfer surface and a corrugated portion for generating turbulent flow formed by laminating a plurality of heat transfer plates via a gasket. The support surface of the gasket provided on the peripheral edge of the heat transfer plate is positioned at the center of the molding depth of the heat transfer plate, and the heat transfer plate is positioned at an asymmetric position on the heat transfer surface as viewed from the width direction of the heat transfer plate. A bead having a height greater than the turbulence generating waveform portion is provided, and a specific one of the plurality of heat transfer plates is turned upside down on the same plane as the heat transfer plate. Alternatively, the heat transfer plate is turned upside down with the horizontal axis or vertical axis orthogonal to each other on the heat transfer surface as the center of rotation, and the heat transfer plate turned upside down or turned upside down, and the remaining heat transfer not turned upside down or turned upside down play A plate heat exchanger, wherein the height of the flow path of the heat exchange medium between adjacent heat transfer plates can be adjusted in a wide and narrow manner by superimposing the heat exchange media in a predetermined lamination order. .