JP6872598B1 - Plate heat exchanger - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a plate type heat exchanger with suppressed distribution resistance.
SOLUTION: In the present invention, a plate laminated portion is formed through an alternating region portion in which a holding region of a gasket and a flow path region through which fluid can flow are alternately formed via a heat transfer plate, and via a heat transfer plate. The alternating region components of the heat transfer plate have the same region portion where each sandwiching region is formed, and the first portion along the plane direction orthogonal to the stacking direction and the mating plate extending from the first portion. It has a second portion that forms a sandwiching region by bending with respect to the first portion in a direction away from the heat transfer plate, and the same region component of the heat transfer plate is a third portion along a plane direction orthogonal to the stacking direction. It has a site and a fourth site that forms a sandwiching region by bending with respect to the third site in a direction extending from the third site and away from the mating plate, and the angle of the second site with respect to the first site is It is characterized in that it is larger than the angle of the fourth part with respect to the third part.
[Selection diagram] FIG. 9

Description

The present invention relates to a plate heat exchanger comprising a plurality of stacked heat transfer plates and a gasket that is sandwiched between the heat transfer plates to form a flow path between the heat transfer plates.

Conventionally, there is known a plate-type heat exchanger in which a flow path is formed between the heat transfer plates by sandwiching the gasket between the heat transfer plates (see Patent Document 1).

As shown in FIG. 20, this plate heat exchanger is sandwiched between a plurality of heat transfer plates 110 stacked in a predetermined direction and adjacent heat transfer plates 110, so that the fluid A is sandwiched between the heat transfer plates 110. , B includes a plurality of gaskets 120a and 120b forming the flow path (first flow path C1, second flow path C2).

As shown in FIGS. 21 and 22, each heat transfer plate 110 has a rectangular shape and has communication holes 111, 112, 113, 114 at four corners.

The gasket 120a sandwiched between the heat transfer plates 110 on which the second flow path C2 is formed surrounds the outer peripheral portion of the heat transfer plate 110 so that the two communication holes 111 and 112 that form one set are located inside. One flow path forming portion 121a, two first annular portions 122a surrounding the entire circumference of the other pair of communication holes 113 and 114, and the first flow path forming portion 121a and the first annular portion 122a are connected to each other. It has a plurality of first connection portions 123a (see FIG. 21).

Further, the gasket 120b sandwiched between the heat transfer plates 110 on which the first flow path C1 is formed surrounds the outer peripheral portion of the heat transfer plate 110 so that the other pair of communication holes 113 and 114 are located inside. The second flow path forming portion 121b, the two second annular portions 122b that surround the entire circumference of the two communication holes 111 and 112 that form one set, and the second flow path forming portion 121b and the second annular portion 122b. It has a plurality of second connecting portions 123b and a plurality of second connecting portions 123b (see FIG. 22).

These gaskets 120a and 120b have the same cross-sectional shape (cross-section orthogonal to the extending direction) at each position, and as shown in FIGS. 23 and 24, recesses (recesses) provided in the heat transfer plate 110. Grooves) are arranged in 115 and 116. The cross-sectional shapes of the recesses 115 and 116 in which the gaskets 120a and 120b are arranged are also the same at each position.

For example, in the heat exchanger 100, a region in which the gaskets 120a and 120b are sandwiched via the heat transfer plate 110 in the overlapping direction of the heat transfer plates 110 and a region in which the fluids A and B can flow are alternately formed. Gaskets 120a and 120b are sandwiched between the cross-sectional shape of the recess 115 of the portion (for example, the position of XXIII-XXIII in FIG. 21: see FIG. 23 for the cross section) and the heat transfer plate 110 via the heat transfer plate 110. The cross-sectional shape of the recess 116 of each of the regions where the regions are formed (for example, the position of XXIV-XXIV in FIG. 21: see FIG. 24 for the cross section) is the same.

Returning to FIG. 20, in the above heat exchanger 100, the flow path (first flow path) C1 through which the first fluid A flows and the flow path (second flow path) C2 through which the second fluid B flows are each heat transfer plate 110. First fluid A flowing through the first flow path C1 and second fluid B flowing through the second flow path C2 through the heat transfer plate 110 which is alternately formed through the first flow path C1 and the second flow path C2. And exchange heat with each other.

Japanese Unexamined Patent Publication No. 9-72686

In recent years, in the plate type heat exchanger 100 in which the gaskets 120a and 120b are sandwiched between the heat transfer plates 110 as described above, it is required to suppress the pressure loss.

Therefore, an object of the present invention is to provide a plate heat exchanger in which pressure loss is suppressed.

The plate heat exchanger of the present invention
A plate laminated portion having a plurality of heat transfer plates stacked in a predetermined direction and a plurality of gaskets sandwiched between the heat transfer plates to form a flow path through which a fluid can flow between the heat transfer plates. ,
The plate laminated portion is
An alternating region portion in which a holding region in which the gasket is sandwiched in the predetermined direction and a flow path region through which the fluid can flow are alternately formed via the heat transfer plate.
The sandwiching region has the same region portion formed via the heat transfer plate in the predetermined direction.
The alternating region constituent portion constituting the alternating region portion in the heat transfer plate is
The first part along the virtual plane orthogonal to the predetermined direction,
A second sandwiching region is formed between the first portion and the other plate by bending the first portion in a direction away from the mating plate, which is a heat transfer plate adjacent to the first portion and adjacent to the first portion. With the part,
The same region constituent portion constituting the same region portion in the heat transfer plate is
The third part along the virtual surface and
It has a fourth portion that extends from the third portion and bends with respect to the third portion in a direction away from the counterpart plate to form the sandwiching region with the counterpart plate.
The angle of the second part with respect to the first part is larger than the angle of the fourth part with respect to the third part.

In this way, by making the angle of the second part (first angle) with respect to the first part larger than the angle of the fourth part (second angle) with respect to the third part, the first angle is made the second. Compared to the configuration with the same angle as the above, the pressure loss when the fluid passes through the flow path region (flow path formed between the heat transfer plates) of the alternating region portion in the direction in which the first portion and the second portion are lined up It can be suppressed.

In the plate heat exchanger
The alternating region component of the heat transfer plate
A fifth portion arranged at a distance from the first portion and along the virtual surface in the direction from the first portion to the second portion,
A sixth portion that extends from the fifth portion toward the first portion and bends with respect to the fifth portion in a direction away from the mating plate to form a sandwiching region between the fifth portion and the mating plate. Have and
The angle of the sixth part with respect to the fifth part may be larger than the angle of the fourth part with respect to the third part.

According to such a configuration, the pressure loss when the fluid passes through the flow path region of the alternating region portion in the direction in which the first portion and the second portion are aligned can be more effectively suppressed.

Further, in the plate heat exchanger,
The alternating region component of the heat transfer plate has a seventh portion that connects the tip of the second portion and the tip of the sixth portion and is along the virtual surface.
The portion of the gasket that is arranged in the sandwiching area is
A central portion sandwiched between the seventh portion and the mating plate,
A first outer portion adjacent to the central portion and sandwiched between the second portion and the mating plate,
It has a second outer portion that is adjacent to the central portion and is sandwiched between the sixth portion and the mating plate.
The elastic force in the predetermined direction at the central portion is preferably larger than the elastic force in the predetermined direction at the first outer portion and the second outer portion.

According to this configuration, the second portion and the sixth portion are pushed in a predetermined direction by the first outer portion and the second outer portion, resulting in deformation of the alternating region constituent portion (heat transfer plate) (see FIG. 17). While preventing a decrease in the airtightness between the alternating region constituent portion and the gasket, it is possible to prevent deformation of the portion with respect to a force applied to the second portion and the sixth portion in a predetermined direction. The details are as follows.

When the elastic force in the predetermined direction (overlapping direction of the heat transfer plates) in the first outer part and the second outer part is larger than the elastic force in the predetermined direction in the central part, the second part and the sixth part are the first outer part and the sixth part. When pushed by the second outer portion, the alternating region constituents are deformed so as to bend (see FIG. 17), which tends to reduce the airtightness between the alternating region constituents and the gasket. However, as in the above configuration, by making the elastic force of the central portion larger than the elastic force of the first outer portion and the second outer portion, the deformation of the alternating region constituent portion is suppressed and the central portion is the seventh. It is in close contact with the site sufficiently, which can prevent the deterioration of the airtightness. Moreover, according to the above configuration, since the angle of the second part with respect to the first part and the angle of the sixth part with respect to the fifth part are larger than the angle of the fourth part with respect to the third part, the fluid flows between the heat transfer plates. The part is easily deformed by the force from the flow path region side (force in a predetermined direction) applied to the second part and the sixth part, but even if the force from the flow path area side is applied, the first part is Since the second and sixth parts are supported by the first outer part and the second outer part, deformation of the parts can be prevented.

In this case, for example
The central portion, the first outer portion, and the second outer portion are integrated.
The portions arranged in the sandwiching region of the gasket are the first outer portion and the second portion when the central portion is in contact with the seventh portion in a state where the elastic force in the predetermined direction is not generated. In a state where the gasket is sandwiched between the heat transfer plates and the fluid can flow through the flow path, the predetermined state is formed. The central portion and the seventh portion are in contact with each other in a state where elastic force is generated in the direction, the first outer portion and the second portion are in contact with each other, and the second outer portion and the sixth portion are in contact with each other. It may have a shape.

With such a shape, when the gasket is sandwiched between the heat transfer plates and the fluid can flow through the flow path of the plate laminated portion, in the portion arranged in the sandwiching region of the gasket, the predetermined direction at the central portion. The elastic force of the above can be made larger than the elastic force in the predetermined direction in the first outer portion and the second outer portion.

Further, in the plate heat exchanger,
Each of the plurality of heat transfer plates has a through hole and has a through hole.
The plate laminated portion has a communication passage formed by connecting the through holes in the predetermined direction.
The communication passage communicates with the flow path formed between the heat transfer plates, and communicates with the communication passage.
The alternating region portion may be arranged so that the first portion and the second portion are lined up in a direction away from the through hole at the peripheral edge portion of the communication passage in the plate laminated portion.

According to such a configuration, it is possible to suppress the pressure loss at the portion (alternate region portion) immediately after flowing into the inter-plate flow path (the flow path formed between the heat transfer plates) from the continuous passage where the pressure loss tends to be large.

Further, in the plate heat exchanger,
In the heat transfer plate pair forming the sandwiching region in the alternating region portion, the first portions face each other in an abutting state, and in the heat transfer plate pair forming the flow path region, the heat transfer plate pair is described. The first parts face each other at intervals in the predetermined direction,
The alternating region portion may be arranged so that the first portion of each alternating region constituent portion faces the communication passage, and may extend along the peripheral edge of the communication passage.

According to such a configuration, the inlet when the fluid flows into the inter-plate flow path from the communication passage (the part where the first parts in the alternating region part are spaced from each other: the entrance of the flow path area) is along the peripheral edge of the communication passage. Therefore, the opening area (flow path cross-sectional area) of the inlet is sufficiently secured, and thus the pressure loss at the inlet is suppressed.

Further, in the plate heat exchanger,
The through hole of the heat transfer plate is circular and has a circular shape.
The gasket has an annular portion that surrounds the through hole and has an annular shape.
The annular portion may include a portion arranged in the sandwiching region and may be arranged at a position eccentric to the alternating region portion side with respect to the through hole.

By arranging the annular portion at a position eccentric to the alternating region portion side with respect to the through hole in this way, the peripheral edge of the through hole on the alternating region portion side and the annular portion (the portion arranged in the holding region of the gasket) Since the interval becomes wide, it becomes easy for the first portions of the alternating region portions to form (arrange) the portions spaced in a predetermined direction. Moreover, while securing a region for forming a portion in which the first portions of the alternating region portions are spaced apart from each other in a predetermined direction, the corresponding portion (annular portion) of the gasket should not be provided with a bent portion having an annular shape. Therefore, the sealing property at the site is stable.

From the above, according to the present invention, it is possible to provide a plate type heat exchanger in which pressure loss is suppressed.

FIG. 1 is a perspective view of a plate heat exchanger according to the present embodiment. FIG. 2 is an exploded perspective view of the plate heat exchanger. FIG. 3 is a front view of a plate laminated portion included in the plate heat exchanger. FIG. 4 is an exploded perspective view of the pair of frames and the plate laminated portion. FIG. 5 is a view of the heat transfer plate included in the plate laminated portion as viewed from the front surface side. FIG. 6 is a view of the heat transfer plate viewed from the second surface side. FIG. 7 is an enlarged view of the first region and its periphery in one communication portion of FIG. FIG. 8 is an enlarged view of the second region and its periphery in one communication portion of FIG. FIG. 9 is an enlarged view of the end face of the cut portion at the IX-IX position of FIG. FIG. 10 is an enlarged cross-sectional perspective view at the IX-IX position of FIG. FIG. 11 is an enlarged view of the end face of the cut portion at the XI-XI position of FIG. FIG. 12 is a front view of the gasket included in the plate heat exchanger. FIG. 13 is an enlarged cross-sectional view at the XIII-XIII position of FIG. FIG. 14 is an enlarged cross-sectional view at the XIV-XIV position of FIG. FIG. 15 is a cross-sectional view of a state in which the first arc portion of the gasket is sandwiched between the inner portions of the first arrangement portion in a state where no elastic force in the X-axis constant direction is generated. FIG. 16 is a cross-sectional view of a state in which the first arc portion of the gasket is sandwiched between the inner portions of the first arrangement portion in a state where an elastic force in the X-axis direction is generated. FIG. 17 is a schematic cross-sectional view showing a state in which the alternating region constituents of the heat transfer plate are deformed so as to bend. FIG. 18 is a graph showing the results of flow analysis in the plate heat exchanger. FIG. 19 is a schematic cross-sectional view showing an inner portion of the first arrangement portion of the heat transfer plate according to another embodiment. FIG. 20 is an exploded perspective view for explaining the configuration of a conventional plate heat exchanger. FIG. 21 is a front view of a state in which the gasket forming the second flow path is arranged on the heat transfer plate. FIG. 22 is a front view of a state in which the gasket forming the first flow path is arranged on the heat transfer plate. FIG. 23 is a cross-sectional view of the plate heat exchanger at the XXIII-XXIII positions of FIG. FIG. 24 is a cross-sectional view of the plate heat exchanger at the XXIV-XXIV position of FIG.

Hereinafter, an embodiment of the present invention will be described with reference to FIGS. 1 to 17.

As shown in FIGS. 1 to 4, the plate-type heat exchanger according to the present embodiment (hereinafter, simply referred to as “heat exchanger”) has a plate laminated portion 2 having a plurality of heat transfer plates 3 and a plate. A direction in which the distance between the pair of frames 5a and 5b that sandwich the laminated portion 2 and the guide portion 6 that guides the plate laminated portion 2 and the pair of frames 5a and 5b to the arrangement position and the pair of frames 5a and 5b become smaller. A plurality of tightening members 7 that can be tightened are provided.

The plate laminated portion 2 is sandwiched between a plurality of heat transfer plates 3 that are superposed in a predetermined direction and the heat transfer plates 3, so that the fluids (first fluid A, second fluid B) are sandwiched between the heat transfer plates 3. It has a plurality of gaskets 4 that form a flowable flow path (first flow path Ra, second flow path Rb). In the plate laminated portion 2 of the present embodiment, one type of rectangular (rectangular) heat transfer plates 3 are superposed in an inverted state, so that the first fluid is bounded by each heat transfer plate 3. The first flow path Ra through which A can flow and the second flow path Rb through which the second fluid B can flow are alternately formed.

In the following, the direction in which the heat transfer plates 3 are overlapped is defined as the X-axis direction of the Cartesian coordinate system, the short side direction of the heat transfer plate 3 is defined as the Y-axis direction of the Cartesian coordinate system, and the long side direction of the heat transfer plate 3 is orthogonal. The Z-axis direction of the coordinate system.

Each of the plurality of heat transfer plates 3 extends along a virtual surface V (see FIGS. 9 and 11) orthogonal to the X-axis direction. As shown in FIGS. 5 and 6, each of the plurality of heat transfer plates 3 has a first surface S1 which is one surface in the X-axis direction and a surface opposite to the first surface S1 (the other surface). ), Each of the second surface S2 has a plurality of convex portions 9a and a plurality of concave portions 9b. The heat transfer plate 3 is formed by press-molding a metal plate (thin plate). Therefore, on the second surface S2, the recess 9b is located at a position corresponding to the convex portion 9a of the first surface S1 (a position overlapping when viewed from the X-axis direction), and a position corresponding to the concave portion 9b of the first surface S1 (a position corresponding to the concave portion 9b of the first surface S1). The convex portion 9a is located at a position where it overlaps when viewed from the X-axis direction). That is, the concave portion 9b of the second surface S2 is located on the back side of the convex portion 9a of the first surface S1, and the convex portion 9a of the second surface S2 is located on the back side of the concave portion 9b of the first surface S1.

Specifically, each heat transfer plate 3 has a main heat transfer portion 30 arranged at the center in the Z-axis direction, a pair of communication portions 31 arranged at the end in the Z-axis direction, and a main heat transfer portion 30. It has a pair of weir portions 32 arranged between the communication portion 31 and the communication portion 31. Further, the heat transfer plate 3 of the present embodiment has a pair of guide notches 33 at both ends in the Z-axis direction.

The main heat transfer unit 30 is formed between the fluids (the first fluid A and the second fluid B) flowing between the first flow path Ra and the second flow path Rb formed on the heat transfer plate 3 with the heat transfer plate 3 as a boundary. This is the part where most of the heat exchange takes place. The surface of the main heat transfer portion 30 on the first surface S1 side excluding the end portion in the Y-axis direction is the first main heat transfer region 300a, and the surface of the main heat transfer portion 30 excluding the end portion in the Y-axis direction is the first. The surface on the side of the two surfaces S2 is the second main heat transfer region 300b. That is, the region (part) corresponding to the portion of the main heat transfer portion 30 of the first surface S1 and the second surface S2 of the heat transfer plate 3 excluding the end portion in the Y-axis direction is the main heat transfer region (the first). One main heat transfer region 300a, second main heat transfer region 300b). The main heat transfer portion 30 of the present embodiment is a square portion when viewed from the X-axis direction.

The main heat transfer portion 30 has a plurality of convex portions 91a (9a) and a plurality of concave portions 91b (9b) on both sides (first and second main heat transfer regions) 300a and 300b, respectively. The arrangement and form of the plurality of convex portions 91a and the plurality of concave portions 91b are set according to the heat transfer efficiency and the types of fluids (first and second fluids) A and B for heat exchange. The plurality of convex portions 91a and the plurality of concave portions 91b of the first and second main heat transfer regions 300a and 300b of the present embodiment have a so-called herringbone shape (arrangement), but are not limited to this shape (arrangement).

Further, the main heat transfer portion 30 has an arrangement portion 301 in which the gasket 4 is arranged at both ends in the Y-axis direction. The arrangement portion 301 has a band-shaped flat portion 3011 extending in the Z-axis direction along the virtual surface V and unevenness in the X-axis direction (in the X-axis direction) on both sides of the flat portion 3011 in the width direction (Y-axis direction). It has a pair of concave-convex portions 3012 in which concave portions and convex portions) are repeated in the Z-axis direction. The pair of concave-convex portions 3012 suppresses the displacement of the gasket 4 in the width direction by the wall portion (fourth portion) 3012a on the flat portion 3011 side in each convex portion of the concave-convex portion 3012 (see FIG. 11). In the arrangement portion 301 of the present embodiment, the concave-convex portion 3012 of one of the pair of concave-convex portions 3012 (center side of the heat transfer plate 3 in the Y-axis direction: the left side in FIG. 11) has main heat transfer regions 300a and 300b. It is composed of a convex portion 91a and a concave portion 91b.

Each of the pair of communication portions 31 has a communication hole (through hole) 311 that penetrates in the X-axis direction. Each communication portion 31 of the present embodiment has two communication holes 311a and 311b. These two communication holes 311a and 311b are arranged at intervals in the Y-axis direction. As a result, communication holes 311 are arranged at the four corners of the heat transfer plate 3. In the heat transfer plate 3 of the present embodiment, each of the four communication holes 311 is a circular hole, and the size (diameter) of each communication hole 311 is the same.

Each configuration of the communication portion 31a of one of the pair of communication portions 31 (upper side of FIG. 5) and each configuration of the communication portion 31b of the other of the pair of communication portions 31 (lower side of FIG. 5) are When viewed from the X-axis direction, it is line symmetric with the horizontal center line CL2 as the axis of symmetry. The horizontal center line CL2 extends in the Y-axis direction from the center of the heat transfer plate 3 in the Z-axis direction.

Further, each of the configurations of the communication portions 31a and 31b has a line-symmetrical arrangement and shape with the vertical center line CL1 as the axis of symmetry when viewed from the X-axis direction. Here, the vertical center line CL1 extends the center of the heat transfer plate 3 in the Y-axis direction in the Z-axis direction. Then, each configuration in the first region T1 of one side (left side in FIG. 5 / right side in FIG. 6) of the vertical center line CL1 in the communication portions 31a and 31b and the other of the vertical center lines CL1 in the communication portions 31a and 31b. The displacement direction in the X-axis direction is opposite to that of each configuration in the second region T2 on the side (right side in FIG. 5 / left side in FIG. 6).

For example, specifically, the configuration of the first region T1 corresponding to the configuration (for example, a convex portion) protruding (displaced) on one side in the X-axis direction in the second region T2 is recessed on the other side in the X-axis direction (for example). The configuration of the first region T1 corresponding to the configuration (for example, a concave portion) that is recessed (displaced) on the other side in the X-axis direction in the second region T2 is one side in the X-axis direction. It is a configuration (for example, a convex portion) that protrudes (displaces).

As shown in FIG. 7, the first region T1 of the communication portions 31a and 31b is the first arrangement in which the gasket 4 surrounding the communication hole 311a or a part of the gasket 4 (annular portion 42: see FIG. 12) is arranged. Along the boundary position between the portion 35, the hole peripheral edge portion (first portion) 36 forming a part of the peripheral edge of the communication hole 311a inside the first arrangement portion 35, and the communication portions 31a and 31b and the weir portion 32. A second arrangement portion 37 in which a portion of the gasket 4 or a part of the gasket 4 (a part of the flow path defining portion 41 (widening portion) 411: see FIG. 12) is arranged, and a first arrangement portion 35 and a second arrangement portion. It has a connecting portion (fifth portion) 38 for connecting to the 37.

The first arrangement portion 35 has an inner portion 351 which is a semicircular portion on the weir portion 32 side and an outer portion 352 which is a semicircular portion on the corner side of the heat transfer plate 3. In the first arrangement portion 35, the annular portion (annular portion) 42 of the gasket 4 is arranged at a position eccentric (displaced position) toward the weir portion 32 with respect to the communication hole 311.

The inner portion 351 is a groove-shaped portion in which the gasket 4 is arranged (see FIG. 9). Specifically, the inner portion 351 includes a band-shaped bottom wall portion (seventh portion) 3511 along the virtual surface V and a pair of side wall portions extending from both ends in the width direction of the bottom wall portion 3511 to one side in the X-axis direction. (First side wall portion (second portion) 3512, second side wall portion (sixth portion) 3513). In this inner portion 351, the angle θ1 of the first side wall portion 3512 with respect to the bottom wall portion 3511 and the angle θ2 of the second side wall portion 3513 with respect to the bottom wall portion 3511 are the same (see FIG. 9).

The bottom wall portion 3511 extends in a semicircular shape when viewed from the X-axis direction. The position of the bottom wall portion 3511 in the X-axis direction is the same as that of the flat portion 3011 of the arrangement portion 301 of the main heat transfer portion 30, and the width of the bottom wall portion 3511 is the same as that of the flat portion 3011.

Each of the first side wall portion 3512 and the second side wall portion 3513 has a plurality of truncated cone-shaped support portions 3514 recessed on the other side (back side in FIG. 7) in the X-axis direction (see FIG. 10). When the heat transfer plates 3 are overlapped with each other, the support portion 3514 has the tip of the heat transfer plate 3 having the support portion 3514 and the corresponding support portion 3514 of the heat transfer plate (counterpart plate) 3 adjacent to each other in the X-axis direction. By bringing them into contact with each other, the distance between the heat transfer plate 3 and the mating plate 3 is maintained. These plurality of support portions 3514 are arranged at intervals in the circumferential direction in each of the first side wall portion 3512 and the second side wall portion 3513. The bottom of each support 3514 is located on the other side of the bottom wall 3511 in the X-axis direction.

In the outer portion 352, the band-shaped first flat portion 3521 along the virtual surface V and the unevenness (concave and convex portions) in the X-axis direction extend on both sides of the first flat portion 3521 in the width direction of the first flat portion 3521. It has a pair of widthwise defining portions 3522 that are repeated along the direction.

The first flat portion 3521 extends in a semicircular shape when viewed from the X-axis direction. The position of the first flat portion 3521 in the X-axis direction is the same as the position of the bottom wall portion 3511 of the inner portion 351 and the position of the flat portion 3011 in the arrangement portion 301 of the main heat transfer portion 30. Further, the width of the first flat portion 3521 is the same as the width of the bottom wall portion 3511 of the inner portion 351 and the width of the flat portion 3011 in the arrangement portion 301 of the main heat transfer portion 30.

Similar to the pair of uneven portions 3012 of the arrangement portion 301 in the main heat transfer portion 30, the pair of widthwise defining portions 3522 has a gasket 4 (annular portion 42: see FIG. 12) due to each convex portion of the width direction defining portion 3522. Suppresses misalignment in the width direction (diameter direction) of.

The hole peripheral edge portion 36 is a portion arranged inside the inner portion 351 (inward in the radial direction of the communication hole 311) and along the virtual surface V (see FIG. 9). Specifically, the hole peripheral edge 36 extends from the end of the inner portion 351 on the communication hole 311 side (the end of the first side wall 3512) toward the center of the communication hole 311 and in the circumferential direction (periphery) of the communication hole 311. Extends in the direction). The hole peripheral edge portion 36 of the present embodiment is provided in a range corresponding to the inner portion 351 in the circumferential direction of the communication hole 311. Further, the width of the hole peripheral portion 36 (the radial dimension of the communication hole 311) gradually increases as it advances from both ends in the circumferential direction toward the center. The communication hole 311 is defined by the hole peripheral edge portion 36 and the outer portion 352 of the first arrangement portion 35.

The hole peripheral edge portion 36 of the present embodiment is parallel to the bottom wall portion 3511 in the inner portion 351 of the first arrangement portion 35. Therefore, the angle of the first side wall portion 3512 of the inner portion 351 with respect to the hole peripheral edge portion 36 is the same as the angle θ1 of the first side wall portion 3512 with respect to the bottom wall portion 3511 of the inner portion 351 (see FIG. 9).

The second arrangement portion 37 is a groove-shaped portion in which the gasket 4 is arranged (see FIG. 9). Specifically, the second arrangement portion 37 includes a band-shaped second flat portion 371 along the virtual surface V and a pair of side wall portions extending from both ends in the width direction of the second flat portion 371 to one side in the X-axis direction. It has a third side wall portion 372 and a fourth side wall portion 373). In the second arrangement portion 37, the angle θ3 of the third side wall portion 372 with respect to the second flat portion 371 and the angle θ4 of the fourth side wall portion 373 with respect to the second flat portion 371 are different (see FIG. 9).

In the second arrangement portion 37 of the present embodiment, the angle θ3> the angle θ4. The angle θ4 is the angle θ5 (see FIG. 11) of the wall portion (fourth portion) 3012a of the uneven portion 3012 with respect to the flat portion (third portion) 3011 in the arrangement portion 301 of the main heat transfer portion 30, and the first arrangement portion. It is the same as the angle of the wall portion of the width direction defining portion 3522 (the wall portion corresponding to the wall portion 3012a of the arrangement portion 301: the fourth portion) with respect to the first flat portion (third portion) 3521 in the outer portion 352 of the 35. .. Further, in the first region T1 of the present embodiment, the angle θ1 = the angle θ2 = the angle θ3.

The second flat portion 371 extends linearly in a direction inclined with respect to each of the vertical center line CL1 and the horizontal center line CL2 when viewed from the X-axis direction. The positions of the second flat portion 371 in the X-axis direction are the position of the bottom wall portion 3511 in the inner portion 351 of the first arrangement portion 35, the position of the first flat portion 3521 in the outer portion 352 of the first arrangement portion 35, and It is the same as each of the positions of the flat portion 3011 in the arrangement portion 301 of the main heat transfer portion 30. The width of the second flat portion 371 is the width of the bottom wall portion 3511 in the inner portion 351 of the first arrangement portion 35, the width of the first flat portion 3521 in the outer portion 352 of the first arrangement portion 35, and the main heat transfer. It is the same as the width of the flat portion 3011 in the arrangement portion 301 of the portion 30.

The connecting portion 38 is a portion along the virtual surface V, and is an end portion of the second side wall portion 3513 of the first arrangement portion 35 (inner portion 351) and an end portion of the third side wall portion 372 of the second arrangement portion 37. And connect. The connecting portion 38 is arranged along a virtual surface V common to the hole peripheral portion 36 of the heat transfer plate 3 including the connecting portion 38 (see FIG. 9).

The connecting portion 38 of the present embodiment is parallel to the bottom wall portion 3511 in the inner portion 351 of the first arrangement portion 35. Therefore, the angle of the second side wall portion 3513 of the inner portion 351 with respect to the connecting portion 38 is the same as the angle θ2 of the second side wall portion 3513 with respect to the bottom wall portion 3511 of the inner portion 351 (see FIG. 9). Further, the connecting portion 38 is parallel to the second flat portion 371 of the second arrangement portion 37. Therefore, the angle of the third side wall portion 372 of the second arrangement portion 37 with respect to the connection portion 38 is the same as the angle θ3 of the third side wall portion 372 with respect to the second flat portion 371 of the second arrangement portion 37 (see FIG. 9). ).

As described above, each configuration of the second region T2 in each of the communication portions 31a and 31b (first arrangement portion 35r, hole peripheral portion 36r, second arrangement portion 37r, connection portion 38r) has common communication portions 31a and 31b. In a line-symmetrical arrangement and shape with each configuration 35 to 38 of the first region T1 and the vertical center line CL1 as the axes of symmetry (see FIG. 8), and the displacement directions in the X-axis direction are opposite to each other. ing.

It should be noted that each configuration of the first region T1 of the first surface S1 viewed from the first surface S1 side in the X-axis direction and the second region T2 of the second surface S2 viewed from the second surface S2 side in the X-axis direction. Each configuration has the same arrangement, the same shape, and the same displacement direction (displacement in the X-axis direction). Further, each configuration of the second region T2 of the first surface S1 viewed from the first surface S1 side in the X-axis direction and the first region T1 of the second surface S2 viewed from the second surface S2 side in the X-axis direction. Each configuration has the same arrangement, the same shape, and the same displacement direction. In FIGS. 5 to 9, each configuration in the first region T1 of the first surface S1 and the same configuration when viewed from the X-axis direction are designated by the same reference numerals, and each configuration in the first region T1 of the first surface S1 is assigned. For configurations in which only the displacement directions in the X-axis direction and the X-axis direction are different, a code in which r is added to the end of the code of the corresponding configuration in the first region T1 of the first surface S1 is used.

As shown in FIGS. 5 to 8, each of the pair of dam portions 32 has a flow of fluids A and B from the communication hole 311 toward the main heat transfer regions 300a and 300b along the first surface S1 or the second surface S2. At the site where the flow of fluids A and B from the main heat transfer regions 300a and 300b toward the communication hole 311 is focused in the Y-axis direction along the first surface S1 or the second surface S2. is there. The surface on the first surface S1 side of each weir portion 32 is the first weir portion heat transfer region 320a, and the surface on the second surface S2 side of each weir portion 32 is the second weir portion heat transfer region 320b. .. That is, the region (part) corresponding to each weir portion 32 of the first surface S1 and the second surface S2 of the heat transfer plate 3 is the weir portion heat transfer region (first weir portion heat transfer region 320a, second weir). Partial heat transfer region 320b).

Specifically, each weir portion 32 is a triangular portion having a boundary with the main heat transfer portion 30 as the base and an intermediate position between the two communication holes 311a and 311b of the communication portion 31 as the apex. The weir portion 32 has a plurality of convex portions 92a (9a) and a plurality of concave portions 92b (9b) on both sides (weir portion heat transfer region) 320a and 320b, respectively. The plurality of convex portions 92a and the plurality of concave portions 92b have dimensions in the Y-axis direction of the main heat transfer regions 300a and 300b, the distance from the communication hole 311 to the main heat transfer regions 300a and 300b, and the fluid A for heat exchange. The arrangement and the form are set according to the type of B and the like, and the shape and the arrangement are not limited to those shown in FIGS. 5 to 8. Also in the weir portion 32, heat exchange between the fluids flowing between the first flow path Ra and the second flow path Rb (between the first fluid A and the second fluid B) formed on the boundary of the heat transfer plate 3 Is done.

The pair of guide notches 33 are arranged at the center of the heat transfer plate 3 in the Y-axis direction at each end in the Z-axis direction. The pair of guide notches 33 of the present embodiment have a line-symmetrical shape with the horizontal center line CL2 as the axis of symmetry.

As shown in FIG. 12, each of the plurality of gaskets 4 communicates between the flow path defining portion 41 that defines the flow paths Ra and Rb between the heat transfer plates 3 and the communication holes 311 of the adjacent heat transfer plates 3. It has an annular portion 42 and a connecting portion 43 that connects the flow path defining portion 41 and the annular portion 42. The gasket 4 of the present embodiment has one flow path defining portion 41, two annular portions 42, and four connecting portions 43.

The flow path defining portion 41 corresponds to the main heat transfer regions 300a and 300b of the main heat transfer portion 30, the pair of weir portions 32, and the communication portions 31a and 31b when viewed from the X-axis direction (in the present embodiment). In the example, it is a portion surrounding the two communication holes 311 (located on the same side with respect to the vertical center line CL1).

Each of the two annular portions 42 is a portion surrounding the communication hole 311 located outside the flow path defining portion 41 when viewed from the X-axis direction. The annular portion 42 has a semicircular first arc portion 421 arranged in the inner portion 351 of the first arrangement portion 35 and a semicircular second arc portion 352 arranged in the outer portion 352 of the first arrangement portion 35. It has a site 422 and. The annular portion 42 of the present embodiment is composed of a first arc portion 421 and a second arc portion 422, and has a circular shape when viewed from the X-axis direction.

The first arc portion 421 includes a central portion 4211 extending in an arc shape, a first outer portion 4212a extending from the central portion 4211 toward the radial inner side (center side) of the annular portion 42, and an annular portion 42 from the central portion 4211. It has a second outer portion 4212b that extends radially outward. The central portion 4211, the first outer portion 4212a, and the second outer portion 4212b are integrated. The thickness dimension (dimension in the X-axis direction) of each of the outer portions 4212a and 4212b gradually decreases as the distance from the central portion 4211 increases (see FIG. 14).

Each of the four connecting portions 43 connects the boundary portion between the first arc portion 421 and the second arc portion 422 in the annular portion 42 and the flow path demarcating portion 41. Each connecting portion 43 of the present embodiment is linear.

In the gasket 4 configured as described above, the cross-sectional (cross-sectional) shape of the first arc portion 421 of the annular portion 42 and the portion arranged in the second arrangement portion 37 of the heat transfer plate 3 in the flow path defining portion 41. The cross-sectional (cross-sectional) shape of the (widening portion) 411 includes other portions (flow path defining portion 41 (remaining portion excluding the widening portion 411), the second arc portion 422 of the annular portion 42, and each connecting portion 43. ) Is different from the cross-sectional (cross-sectional) shape. The details are as follows.

The cross-sectional shape of the other portions (flow path defining portion 41 (excluding widening portion 411), second arc portion 422 of the annular portion 42, and each connecting portion 43) is a flat octagon (see FIG. 13).

In the cross-sectional shape of the first arc portion 421, the central portion 4211 has a shape (flat octagonal shape) corresponding to the other portion, as shown in FIG. Further, the first outer portion 4212a and the second outer portion 4212b are located at both ends of the central portion 4211 (both ends in the radial direction of the annular portion 42) from positions central to the end in the X-axis direction in the radial direction, respectively. It is extending. The first outer portion 4212a and the second outer portion 4212b have a so-called tapered shape in which the dimension (thickness dimension) in the X-axis direction gradually decreases as the distance from the central portion 4211 increases.

More specifically, as shown in FIG. 15, in the first arc portion 421, the central portion 4211 is in contact with the bottom wall portion 3511 of the inner portion 351 of the first arrangement portion 35 in a state where no elastic force in the X-axis direction is generated. In this state, a gap α is formed between the first outer side portion 4212a and each first side wall portion 3512, and between the second outer portion 4212b and each second side wall portion 3513. In the plate laminated portion 2 of the present embodiment, the facing surface of the first outer side portion 4212a with the first side wall portion 3512 and the first side wall portion 3512 are substantially parallel to each other in a state where the gap α is generated, and the second outer side portion 2 The surface of the portion 4212b facing the second side wall portion 3513 and the second side wall portion 3513 are substantially parallel to each other.

Then, in a state where the gasket 4 is sandwiched between the heat transfer plates 3 with sufficient force and the fluids A and B can flow through the flow paths Ra and Rb, as shown in FIG. 16, the cross section of the first arc portion 421 is cross-sectional. The shape is such that the central portion 4211 and each bottom wall portion 3511 are in contact with each other in a state where the elastic force Ef1 in the X-axis direction is generated, and the first outer portion 4212a and each first side wall portion 3512 are in contact with each other and the second outer side. The portion 4212b and each second side wall portion 3513 are in contact with each other.

In the first outer portion 4212a and the second outer portion 4212b of the present embodiment, an elastic force Ef2 in the X-axis direction is generated, respectively. At this time, the elastic force Ef1 in the X-axis direction (force in the direction of widening the distance between the bottom wall portions 3511) generated in the central portion 4211 is generated in each of the first outer portion 4212a and the second outer portion 4212b. The elastic force in the X-axis direction (force in the direction of widening the distance between the first side wall portion 3512 and the second side wall portion 3513) is larger than Ef2.

Further, as shown in FIGS. 9 and 12, the cross-sectional shape of the widening portion 411 in the flow path defining portion 41 is the main body portion 412 having a shape corresponding to the cross section of the central portion 4211 of the first arc portion 421 and the first outer side. Includes an extension portion 413 having a shape corresponding to the cross section of the portion 4212a or the second outer portion 4212b. Also in this widening portion 411, the widening portion 411 is sandwiched between the heat transfer plates 3 (specifically, the second arrangement portion 37) with sufficient force, and the fluids A and B can flow through the flow paths Ra and Rb. In the state, the elastic force in the X-axis direction generated in the main body portion 421 (the force in the direction of widening the interval between the second flat portions 371) is the elastic force in the X-axis direction generated in the extension portion 413 (third). It is larger than the force in the direction of widening the distance between the side wall portions 372).

In the plate laminated portion 2 having the heat transfer plate 3 and the gasket 4 configured as described above, as shown in FIG. 4, a plurality of heat transfer plates 3 are stacked in the X-axis direction in a state of being inverted every other heat transfer plate 3. ing. At this time, the plurality of gaskets 4 are arranged (sandwiched) between the heat transfer plates 3, but the plurality of gaskets 4 are also arranged between the heat transfer plates 3 in a state of being inverted every other one. Has been done. In the plate laminated portion 2 of the present embodiment, the reversal of the heat transfer plate 3 is performed with the horizontal center line CL2 as the rotation axis, and the reversal of the gasket 4 extends in the Z-axis direction at the center in the Y-axis direction. This is done with the center line CL3 (see FIG. 12) as the axis of rotation.

By superimposing a plurality of heat transfer plates 3 in the X-axis direction with the gasket 4 sandwiched between the heat transfer plates 3 in this way, each heat transfer plate 3 in the plate laminated portion 2 (heat exchanger 1). A first flow path Ra that allows the first fluid A to flow in the Z-axis direction and a second flow path Rb that allows the second fluid B to flow in the Z-axis direction are alternately formed with the plate 3 as a boundary. That is, in the plurality of heat transfer plates 3 stacked in the X-axis direction, the first flow path Ra is formed between the first surfaces S1 of the adjacent heat transfer plates 3, and the second surface of the adjacent heat transfer plates 3 is formed. A second flow path Rb is formed between S2.

Further, in the plate laminated portion 2, the corresponding communication holes 311b of the plurality of heat transfer plates 3 are connected to each other in the X-axis direction, so that a pair of first series passages Ra1 and Ra2 communicating only with the first flow path Ra are formed. At the same time, the corresponding communication holes 311a of the plurality of heat transfer plates 3 are connected to each other in the X-axis direction, so that a pair of second communication passages Rb1 and Rb2 communicating only with the second flow path Rb are formed. One of the pair of first series passages Ra1 and Ra2 causes the first fluid A to flow into each first passage Ra, and the other first series passage Ra2 allows the first fluid A to flow. It flows out from each first flow path Ra. Further, one of the pair of second passages Rb1 and Rb2, the second passage Rb1, causes the second fluid B to flow into each second passage Rb, and the other second passage Rb2 is the second fluid. B is allowed to flow out from each second flow path Rb.

In the plate laminated portion 2 of the present embodiment, a portion (alternate region portion) 20 in which the fluids A and B flow from the respective flow paths Ra1 and Rb1 to the respective flow paths Ra and Rb, and each communication passage from the respective flow paths Ra and Rb. The portion (alternate region portion) 20 where the fluids A and B flow out to Ra2 and Rb2 has the same configuration.

In the alternating region portion 20, as shown in FIGS. 9 and 10, a sandwiching region 21 in which the gasket 4 is sandwiched in the X-axis direction and a flow path region 22 through which fluids A and B can flow are interposed via a heat transfer plate 3. It is formed alternately.

In each sandwiching region 21, the first regions T1 on the first surface S1 side of the communication portion 31 or the second regions T2 on the second surface S2 side face each other, and the inner portions 351 of the first arrangement portion 35 face each other. As a result, it is formed between the inner parts 351. A gasket 4 (first arc portion 421 of the annular portion 42) is sandwiched between the inner portions 351 (holding region 21).

Further, in each flow path region 22, the second regions T2 on the first surface S1 side of the communication portion 31 or the first regions T1 on the second surface S2 side face each other, and the inner portions 351r of the first arrangement portion 35r face each other. Are formed between the inner portions 351r by facing each other. The flow path region 22 formed between the inner portions 351r constitutes a part of the flow paths Ra and Rb formed between the heat transfer plates 3. That is, the flow path region 22 is included in the flow paths Ra and Rb.

The alternating region portion 20 on the side where the fluids A and B flow into the flow paths Ra and Rb from the communication passages Ra1 and Rb1 in the plate laminated portion 2 is configured as described above, so that the first series passage Ra1 can be used. The first fluid A flows into the first flow path Ra through the flow path region 22 included in each first flow path Ra (that is, the inflow into the second flow path Rb is between the inner portions 351 (sandwich area 21). It is blocked by the gasket 4 sandwiched between them). Further, the second fluid B flows from the second passage Rb1 through the flow path region 22 included in each second flow path Rb into the second flow path Rb (that is, the inflow into the first flow path Ra). It is blocked by the gasket 4 sandwiched between the inner portions 351 (holding area 21).

On the other hand, in the alternating region portion 20 on the side where the fluids A and B flow out from the flow paths Ra and Rb in the plate laminated portion 2 to the communication passages Ra2 and Rb2, the fluids A and B are configured as described above. Flow out from each first flow path Ra through the flow path region 22 included in the first flow path Ra to the first series passage Ra 2. Further, each second flow path Rb flows out to the second continuous passage Rb2 through the flow path region 22 included in the second flow path Rb.

In the outer peripheral portion of the plate laminated portion 2, the portion (same region portion) 25 in which the flow paths Ra and Rb formed between the heat transfer plates 3 are sealed by the gasket 4 is, for example, as shown in FIG. In addition, sandwiching regions 26 are formed via the heat transfer plate 3 in the X-axis direction. Here, the angle θ5 of the wall portion 3012a with respect to the top portion 3012b of the uneven portion 3012 in the arrangement portion 301 of the main heat transfer portion 30 is about 135 ° ≦ θ5 ≦ about 145 °.

Each sandwiching region 26 of the same region portion 25 is formed between the arrangement portions 301 and the outer portion 352 by overlapping the arrangement portions 301 of the main heat transfer portion 30 and the outer portions 352 of the first arrangement portion 35. ing. A gasket 4 (flow path defining portion 41 or annular portion 42) is sandwiched between the arrangement portions 301 and the outer portion 352.

Returning to FIGS. 1, 2, and 4, each of the pair of frames 5a and 5b is a thick plate-shaped member having a shape corresponding to the heat transfer plate 3 when viewed from the X-axis direction.

One of the frames 5a of the pair of frames 5a and 5b has a rectangular thick plate shape that is long in the Z-axis direction, and each communication hole 311 of the heat transfer plate 3 (each communication passage Ra1, Ra2, Rb1, Rb2). Has a plurality of (four in the example of the present embodiment) through holes 51 penetrating in the X-axis direction at positions corresponding to the above. Further, one frame 5a has a plurality of notches 52 arranged at both ends in the Y-axis direction at intervals in the Z-axis direction.

Further, the other frame 5b of the pair of frames 5a and 5b has a rectangular thick plate shape that is long in the Z-axis direction, and a plurality of notches arranged at both ends in the Y-axis direction at intervals in the Z-axis direction. It has a part 53. Each of the plurality of notch portions 53 is arranged at a position (position overlapping when viewed from the X-axis direction) corresponding to each notch portion 52 of one frame 5a.

Each of the guide portions 6 has a pair of guide bars 61 extending in the X-axis direction. The guide portion 6 of the present embodiment also has a support member 62 that maintains a distance between the ends of the pair of guide bars 61.

The pair of guide bars 61 extend parallel to each other from both ends of one frame 5a in the Z-axis direction. These pair of guide bars 61 guide the other frame 5b in a state (posture) parallel to the one frame 5a so that they can be brought into contact with each other in the X-axis direction. Further, each of the pair of guide bars 61 is fitted into the guide notches 33 at both ends in the Z-axis direction of the heat transfer plate 3 to guide each heat transfer plate 3 to the arrangement position.

The support member 62 extends in the Z-axis direction, and by connecting the ends of the pair of guide bars 61 (the ends on the opposite side to the end connected to one frame 5a), the ends are connected to each other. Maintain the interval.

Each of the plurality of tightening members 7 has a bolt 71 extending in the X-axis direction and a nut 72 screwing with the bolt 71. Each tightening member 7 is fitted into the corresponding notches 52 and 53 of the pair of frames 5a and 5b (overlapping when viewed from the X-axis direction), and the pair of frames is in a direction in which the distance in the X-axis direction becomes smaller. Tighten 5a and 5b. By tightening the pair of frames 5a and 5b by the plurality of tightening members 7, the gaskets 4 arranged between the heat transfer plates 3 are sandwiched with sufficient force, whereby the gaskets 4 are formed between the heat transfer plates 3. Each of the flow paths Ra and Rb becomes liquid-tight.

In the heat exchanger 1 configured as described above, when the first fluid A is supplied to one first series passage Ra1 and the second fluid B is supplied to one second series passage Rb1, the second fluid B is supplied. One fluid A flows into each first flow path Ra from one first series passage Ra1, and second fluid B flows into each second flow path Rb from one second continuous passage Rb1.

As a result, in the heat exchanger 1, the first fluid A flows in the first flow path Ra in the Z-axis direction, and the second fluid B flows in the second flow path Rb in the Z-axis direction. Specifically, the first fluid A passes (circulates) between the first surfaces S1 from one end to the other end in the Z-axis direction in the first flow path Ra, and the second fluid B passes through the second flow path. In Rb, it passes (circulates) between the second surfaces S2 from the other end in the Z-axis direction toward one end side. At this time, the first fluid A and the second fluid B exchange heat via the heat transfer plate 3 (mainly the main heat transfer portion 30) between the first flow path Ra and the second flow path Rb.

Then, as shown in FIG. 4, the first fluid A that has completed heat exchange flows out from each first passage Ra to the other first series passage Ra2, and is discharged to the outside through the first series passage Ra2. Further, the second fluid B that has completed heat exchange flows out from each second passage Rb to the other second passage Rb2, and is discharged to the outside through the second passage Rb2.

In the above heat exchanger 1, in the plate laminated portion 2, each heat transfer constituting the alternating region portion (the portion where the fluids A and B flow from the communication passages Ra1 and Rb1 to the respective flow paths Ra and Rb) 20 on the inflow side. The parts of the plate 3 (alternate region constituent parts: in the example of the present embodiment, the hole peripheral portion 36, the inner portion 351 of the first arrangement portion 35, and the connecting portion 38) are as shown in FIGS. 9 and 10. The hole peripheral portion (first portion) 36 along the virtual surface V orthogonal to the X-axis direction and the hole extending from the hole peripheral portion 36 and away from the heat transfer plate (counterpart plate) 3 adjacent to each other in the X-axis direction. Each has a first side wall portion (second portion) 3512 that forms a sandwiching region 21 with the mating plate 3 by bending with respect to the peripheral edge portion 36. The angle θ1 of the first side wall portion 3512 with respect to the hole peripheral edge portion 36 is a portion (same region constituent portion) of each heat transfer plate 3 constituting the same region portion 25 in the outer peripheral portion of the plate laminated portion 2, for example, FIG. As shown in 11, the wall portion of the uneven portion 3012 with respect to the top portion of the concave-convex portion 3012 of the arrangement portion 301 of the main heat transfer portion 30 (the portion along the virtual surface V in the portion constituting the arrangement portion 301: the third portion) 3012b. It is larger than the angle θ5 of 3012a (a portion extending from the top 3012b and bending with respect to the top 3012b in a direction away from the mating plate 3 to form a sandwiching region 26 with the mating plate 3: a fourth portion).

As described above, the angle (first angle) θ1 of the first side wall portion 3512 with respect to the hole peripheral edge portion 36 is, for example, the angle (first angle) of the wall portion 3012a with respect to the top portion 3012b of the uneven portion 3012 in the arrangement portion 301 of the main heat transfer portion 30. By being larger than the second angle) θ5, the fluids A and B are in the flow path region 22 (between the heat transfer plates 3) of the alternating region portion 20 as compared with the configuration in which the first angle θ1 is the same as the second angle θ5. Pressure loss (flow resistance) when passing through the formed flow paths Ra and Rb) in the direction in which the hole peripheral edge portion 36 and the first side wall portion 3512 are aligned is suppressed.

Further, also in the alternating region portion (alternate region portion on the outflow side) 20 where the fluids A and B flow out from the flow paths Ra and Rb to the communication passages Ra2 and Rb2, the perimeter of the hole in the alternating region component of each heat transfer plate 3 The angle (first angle) θ1 of the first side wall portion 3512 with respect to the portion 36 is the angle of the wall portion 3012a with respect to the top portion 3012b in the same region portion 25 (for example, the uneven portion 3012 of the arrangement portion 301 of the main heat transfer portion 30). By being larger than the second angle) θ5, the fluids A and B are in the flow path region 22 (between the heat transfer plates 3) of the alternating region portion 20 as compared with the configuration in which the first angle θ1 is the same as the second angle θ5. Pressure loss (flow resistance) when passing through the formed flow paths Ra and Rb) in the direction in which the hole peripheral edge portion 36 and the first side wall portion 3512 are aligned is suppressed. The first angle θ1 of the present embodiment is preferably 145 ° ≦ θ1 ≦ 170 °, more preferably 150 ° ≦ θ1 ≦ 160 °, based on the flow analysis described later.

Further, in the heat exchanger 1 of the present embodiment, the alternating region constituents of the heat transfer plates 3 constituting the alternating region portion 20 are aligned with the hole peripheral portion 36 in the direction from the hole peripheral portion 36 toward the first side wall portion 3512. The connecting portion (fifth portion) 38 arranged at intervals and along the virtual surface V and the connecting portion 38 extending from the connecting portion 38 toward the hole peripheral portion 36 and bending away from the mating plate 3 with respect to the connecting portion 38. It has a second side wall portion (sixth portion) 3513 that forms a sandwiching region 21 with the mating plate 3. The angle θ2 of the second side wall portion 3513 with respect to the connecting portion 38 is, for example, the wall of the uneven portion 3012 with respect to the top portion 3012b of the concave-convex portion 3012 at the portion constituting the arrangement portion 301 of the main heat transfer portion 30 shown in FIG. The angle θ5 of the portion 3012a is larger. Therefore, in each of the alternating region portions 20 on the inflow side and the outflow side, the pressure loss when the fluids A and B pass through the flow path region 22 in the direction in which the hole peripheral portion 36 and the first side wall portion 3512 are aligned is more effective. It is suppressed to. The second angle θ2 of the present embodiment is also preferably 145 ° ≦ θ2 ≦ 170 °, more preferably 150 ° ≦ θ2 ≦ 160 °, based on the flow analysis described later.

Further, in the heat exchanger 1 of the present embodiment, the portion (first arc portion) 421 arranged in the sandwiching region 21 in the gasket 4 is the heat transfer plate 3 as shown in FIGS. 12 and 14 to 16. The central portion 4211 and the central portion 4211 sandwiched between the bottom wall portion (seventh portion) 3511 of the first arrangement portion 35 and the mating plate 3 (in the example of the present embodiment, the bottom wall portion 3511 of the mating plate 3). The first outer portion 4212a, which is adjacent to the heat transfer plate 3 and is sandwiched between the first side wall portion 3512 of the heat transfer plate 3 and the mating plate (in the example of the present embodiment, the first side wall portion 3512 of the mating plate 3). A second outer side adjacent to the central portion 4211 and sandwiched between the second side wall portion 3513 of the heat transfer plate 3 and the mating side plate (in the example of the present embodiment, the second side wall portion 3513 of the mating plate 3). It has a site 4212b and. Then, in a state of being sandwiched between the heat transfer plate 3 and the mating plate 3, the elastic force Ef1 in the X-axis direction at the central portion 4211 is in the X-axis direction at the first outer portion 4212a and the second outer portion 4212b. It is larger than the elastic force Ef2.

According to such a configuration, the first side wall portion 3512 and the second side wall portion 3513 are pushed toward the flow path region 22 side in the X-axis direction by the first outer side portion 4212a and the second outer side portion 4212b (particularly, the alternating region constituent portion (particularly). , While preventing a decrease in the airtightness between the alternating region constituent portion and the gasket 4 (first arc portion 421) due to deformation (see FIG. 17) of the inner portion 351) of the first arrangement portion 35, the first It is possible to prevent the portions 3512 and 3513 from being deformed by the force applied to the side wall portion 3512 and the second side wall portion 3513 from the flow path region 22 side in the X-axis direction. The details are as follows. In FIG. 17, in order to make it easier to understand the deformation of the alternating region constituent portion of the heat transfer plate 3, the deformation is exaggerated and the description of the gasket 4 is omitted.

When the elastic force Ef2 in the X-axis direction at the first outer portion 4212a and the second outer portion 4212b is larger than the elastic force Ef1 in the X-axis direction at the central portion 4211, the first side wall portion 3512 and the second side wall portion 3513 are on the first outer side. Pushed by the portion 4212a and the second outer portion 4212b, the alternating region constituent portion of the heat transfer plate 3 (particularly, the inner portion 351 of the first arrangement portion 35) is deformed so as to bend (see FIG. 17). When such deformation occurs, the airtightness between the alternating region constituent portion (inner portion 351) and the gasket 4 (first arc portion 421) tends to decrease.

However, like the heat exchanger 1 of the present embodiment, the elastic force Ef1 in the X-axis direction at the central portion 4211 is made larger than the elastic force Ef2 in the X-axis direction at the first outer portion 4212a and the second outer portion 4212b. Therefore, the deformation of the alternating region constituent portion (inner portion 351) of the heat transfer plate 3 is suppressed, and the central portion 4211 is sufficiently adhered to the bottom wall portion 3511, whereby the deterioration of the airtightness can be prevented.

Moreover, according to the heat exchanger 1 of the present embodiment, the angle θ1 of the first side wall portion 3512 with respect to the hole peripheral edge portion 36 and the angle θ2 of the second side wall portion 3513 with respect to the connection portion 38 are the arrangement portions of the main heat transfer portion 30, respectively. Since the angle θ5 (see FIG. 11) of the wall portion 3012a with respect to the top portion 3012b of the uneven portion 3012 in 301 is larger, the first side wall portion 3512 and the second side wall portion 3513 when the fluids A and B flow between the heat transfer plates 3 and the like. The portions 3512 and 3513 are easily deformed with respect to the force from the flow path region 22 side (force in the X-axis direction) applied to the flow path region 22, but even if the force from the flow path region 22 side is applied, the first side wall portion 3512 Since the second side wall portion 3513 is supported by the first outer portion 4212a and the second outer portion 4212b, deformation of the portions 3512 and 3513 can be prevented.

Further, in the heat exchanger 1 of the present embodiment, the alternating region portion 20 is the hole peripheral portion 36 in the peripheral portion of one of the first and second continuous passages Ra1 and Rb1 in the plate laminated portion 2 in the direction away from the communication hole 311. And the first side wall portion 3512 are arranged so as to be arranged in order. According to such a configuration, it is possible to suppress the pressure loss at the portion immediately after the inflow from the respective communication passages Ra1 and Ra2 to the first flow path Ra or the second flow path Rb (alternate region portion 20 on the inflow side). ..

Further, in the alternating region portion 20 of the heat exchanger 1 of the present embodiment, in the heat transfer plate pair (two heat transfer plates 3 adjacent to each other in the X-axis direction) forming the sandwiching region 21, the hole peripheral portions 36 are connected to each other. In the heat transfer plate pair forming the flow path region 22, the hole peripheral portions 36 face each other at intervals in the X-axis direction. The alternating region portion 20 is arranged so that the hole peripheral portion 36 of the alternating region constituent portion in each heat transfer plate 3 faces the communication passages Ra1, Ra2, Rb1, and Rb2, and the communication passages Ra1, Ra2, and Rb1. It extends (circumferentially) along the periphery of Rb2 (see FIG. 10). In this way, in the heat exchanger 1, the inlet (at the alternating area portion 20) when the fluids A and B flow into the respective flow paths Ra and Rb (inter-plate flow paths) from the first or second communication passages Ra1 and Rb1. Since the portion where the hole peripheral portions 36 are spaced apart from each other in the X-axis direction: the entrance of the flow path region 22) extends along the peripheral edges of the first or second continuous passages Ra1 and Rb1, the opening area of the entrance. (Cross-sectional area of the flow path) is sufficiently secured. As a result, pressure loss at the inlet is suppressed.

Further, in the heat exchanger 1 of the present embodiment, the annular portion 42 of the gasket 4 includes the first arc portion (the portion arranged in the sandwiching region 21) 421 and with respect to the circular communication hole 311. It is arranged at a position eccentric to the alternating region portion 20 side. By arranging the annular portion 42 at a position eccentric to the alternating region portion 20 side with respect to the communication hole 311 in this way, the peripheral edge of the communication hole 311 on the alternating region portion 20 side and the annular portion 42 (specifically, the first arc). The distance from the part 421) becomes wider. Therefore, it becomes easy to form (arrange) a portion where the hole peripheral portions 36 of the alternating region portion 20 are spaced apart from each other. Moreover, while securing a region for forming a portion in which the hole peripheral portions 36 of the alternating region portion 20 are spaced apart from each other, a portion in which the corresponding portion (annular portion) 42 of the gasket 4 is formed into an annular shape is not provided. As a result, the sealing property at the site is stabilized.

Here, in order to confirm the effect, a flow analysis in the heat exchanger 1 of the above embodiment was performed. In this flow analysis, the physical property value of water at 45 ° C. is used as the fluid, the angle θ1 of the first side wall portion with respect to the hole peripheral portion and the angle θ2 of the second side wall portion with respect to the connection portion are set to be the same angle, and these angles θ1. The analysis was performed under the conditions that the angle θ2 was changed from 135 ° to 172 ° by about 5 °. The result is shown in FIG. The pressure drop reduction rate in FIG. 18 is obtained based on the case where the angle θ1 and the angle θ2 are 135 °.

From the result of this flow analysis, the angle θ1 and the angle θ2 in the alternating region constituent portion of the heat transfer plate 3 (the portion of the heat transfer plate 3 constituting the alternating region portion 20) are the same region constituent portion of the heat transfer plate 3 (same). Angle θ5 of the heat transfer plate 3 constituting the region portion 25 (in the example of the above embodiment, the angle θ5 of the wall portion 3012a with respect to the top portion 3012b of the uneven portion 3012 in the arrangement portion 301 of the main heat transfer portion 30: FIG. 11 It was confirmed that the pressure loss was effectively reduced when it was larger than (see). In addition, in the part (same area constituent part) of each heat transfer plate 3 constituting the same area part 25 of the plate laminated part 2 of the said embodiment, the top (virtual) of the concavo-convex part 3012 in the arrangement part 301 of the main heat transfer part 30. A portion along the surface V) 3012a with respect to the wall portion 3012a (a portion extending from the top 3012b and bending with respect to the top 3012b in a direction away from the mating plate 3 to form a sandwiching region 26 with the mating plate 3). ) Is about 135 ° ≦ θ5 ≦ about 145 °.

Further, from the results of the flow analysis shown in FIG. 18, when the angle θ5 of the same region component of the heat transfer plate 3 is 135 ° ≦ θ5 ≦ 145 °, the angle θ1 of the alternating region component of the heat transfer plate 3 and When the angle θ2 is 145 ° ≤ θ1 ≤ 170 ° (the range surrounded by the broken line in FIG. 18), a good result (pressure loss reduction rate) is obtained, and when 150 ° ≤ θ1 ≤ 160 °, a better result (pressure loss) is obtained. It was confirmed that the rate of decrease) was obtained.

The plate heat exchanger of the present invention is not limited to the above embodiment, and it goes without saying that various modifications can be made without departing from the gist of the present invention. For example, the configuration of one embodiment can be added to the configuration of another embodiment, and a part of the configuration of one embodiment can be replaced with the configuration of another embodiment. In addition, some of the configurations of certain embodiments can be deleted.

In the plate laminated portion 2 of the heat exchanger 1 of the above embodiment, the alternating region portion 20 is arranged around the communication passages Ra1, Ra2, Rb1 and Rb2 (arranged so as to face the communication passages Ra1, Ra2, Rb1 and Rb2). However, it is not limited to this configuration. For example, the alternating region portion 20 is located at an intermediate position between the passages Ra and Rb (between one passage Ra1 and Rb1 in the plate laminated portion 2 and the other passages Ra2 and Rb2, that is, the respective passages Ra1 and Ra2. , Rb1 and Rb2).

Further, in the alternating region portion 20 of the plate laminated portion 2 of the above embodiment, the angle θ1 of the first side wall portion 3512 with respect to the hole peripheral edge portion 36 and the angle θ2 of the second side wall portion 3513 with respect to the connecting portion 38 are the same. Moreover, the angle θ5 of the wall portion 3012a with respect to the top portion 3012b in the same region portion 25 (for example, the uneven portion 3012 of the arrangement portion 301 of the main heat transfer portion 30) is larger than, but is not limited to this configuration.

For example, the angle θ1 of the first side wall portion 3512 with respect to the hole peripheral edge portion 36 and the angle θ2 of the second side wall portion 3513 with respect to the connecting portion 38 are a portion along the virtual surface V in the same region portion 25 and an extension from the portion. And the angle formed by the portion forming the sandwiching region 26 with the counterpart plate 3 by bending with respect to the portion in the direction away from the counterpart plate 3 (in the example of the above embodiment, the main heat transfer portion 30). The angle of the wall portion 3012a with respect to the top portion 3012b of the uneven portion 3012 of the arrangement portion 301) is larger than θ5, but the angles do not have to be the same.

Further, only one of the angle θ1 of the first side wall portion 3512 with respect to the hole peripheral edge portion 36 and the angle θ2 of the second side wall portion 3513 with respect to the connecting portion 38 is along the virtual surface V in the same region portion 25. An angle formed by a portion and a portion forming a sandwiching region 26 between the portion and the counterpart plate 3 by bending with respect to the portion in a direction extending from the portion and away from the counterpart plate 3 (example of the above embodiment). Then, the angle of the wall portion 3012a with respect to the top portion 3012b of the uneven portion 3012 of the arrangement portion 301 of the main heat transfer portion 30) may be larger than θ5. Even with this configuration, the fluids A and B are in the direction in which the hole peripheral portion 36 and the first side wall portion 3512 are aligned with each other in the flow path region 22 (flow paths Ra and Rb formed between the heat transfer plates 3) of the alternating region portion 20. Pressure loss when passing through is suppressed.

Further, in the first arrangement portion 35 of the heat transfer plate 3 of the above embodiment, the configuration is different between the inner portion 351 and the outer portion 352, but the configuration is not limited to this. The outer portion 352 may have the same configuration as the inner portion 351, that is, the bottom wall portion 3511 and the first and second side wall portions 3512 and 3513 may be provided. In this case, in the annular portion 42 of the gasket 4, it is preferable that the second arc portion 422 has the same configuration as the first arc portion 421, that is, the central portion 4211 and the first and second outer portions 4212a and 4212b.

Further, in the gasket 4 of the above embodiment, the central portion 4211 and the first and second outer portions 4212a and 4212b are integrated, but the present invention is not limited to this configuration. In the gasket 4, the central portion 4211, the first outer portion 4212a, and the second outer portion 4212b may be separate bodies. In this case, the central portion 4211 and the first and second outer portions 4212a and 4212b may be connected by adhesion, welding, adhesion or the like.

Further, in the widening portion 411 of the flow path defining portion 41, the main body portion 412 and the extension portion 413 may be separate bodies. In this case as well, the main body portion 412 and the extension portion 413 may be connected by adhesion, welding, attachment, or the like.

Further, the first arc portion 421 of the gasket 4 of the above embodiment has a central portion 4211 and first and second outer portions 4212a and 4212b, but is not limited to this configuration. The first arc portion 421 may have only the central portion 4211, or may have the central portion 4211 and one of the first outer portion 4212a and the second outer portion 4212b.

Further, in the alternating region portion 20 of the plate laminated portion 2 of the above embodiment, the gasket 4 is sandwiched between the heat transfer plates 3 due to the cross-sectional shape of the gasket 4 (see FIG. 14), and the fluid A is inserted into the flow paths Ra and Rb. , B is in a state where it can be distributed, so that the elastic force Ef1 in the X-axis direction at the central portion 4211 is larger than the elastic force Ef2 in the X-axis direction at the first outer portion 4212a and the second outer portion 4212b. That is, due to the difference in the amount of compression in the X-axis direction of each part 4211, 4212a, 4212b when the gasket 4 is sandwiched between the heat transfer plates 3 and the fluids A and B can flow through the flow paths Ra and Rb. The elastic force Ef1 in the X-axis direction at the central portion 4211 is made larger than the elastic force Ef2 in the X-axis direction at the first outer portion 4212a and the second outer portion 4212b, but the present invention is not limited to this configuration. For example, by using different materials in the central portion 4211 and the first and second outer portions 4212a and 4212b, the elastic force Ef1 in the X-axis direction in the central portion 4211 can be reduced to the first outer portion 4212a and the second outer portion 4212a. The elastic force Ef2 in the X-axis direction at the portion 4212b may be larger than the elastic force Ef2.

Further, also in the widening portion 411 of the flow path defining portion 41, not only the difference in the amount of compression depending on the cross-sectional shape but also the difference in the amount of compression depending on the cross-sectional shape and the difference in the material cause at least one of the differences between the heat transfer plates 3 (second arrangement). When sandwiched between the portions 37) with sufficient force, the elastic force in the X-axis direction (direction to widen the distance between the second arrangement portions 37) generated in the main body portion 412 is generated in the extension portion 413 in the X-axis direction (third portion 37). It may be configured to be larger than the elastic force (in the direction of widening the distance between the two arrangement portions 37).

Further, in the alternating region portion 20 of the plate laminated portion 2 of the above embodiment, each cross-sectional shape of the hole peripheral portion 36, the connecting portion 38, the first side wall portion 3512, and the second side wall portion 3513 extends straight (FIG. 9), but the configuration is not limited to this. For example, the cross-sectional shape of the first side wall portion 3512, the second side wall portion 3513, or the like may be curved and extended as shown in FIG. In this case, for example, as the angle θ1 of the first side wall portion 3512 with respect to the hole peripheral edge portion 36, the angle formed by the hole peripheral portion 36 and the tangent line L1 at the boundary portion between the hole peripheral edge portion 36 and the hole peripheral edge portion 36 of the first side wall portion 3512 is used. As the angle θ2 of the second side wall portion 3513 with respect to the connection portion 38, the angle formed by the connection portion 38 and the tangent line L2 at the boundary portion between the connection portion 38 and the connection portion 38 of the second side wall portion 3513 may be used.

The specific shapes of the communication hole 311 of the heat transfer plate 3 and the annular portion 42 of the gasket 4 are not limited. The communication hole 311 and the annular portion 42 may have a shape other than a circle such as an ellipse or a polygon.

Further, in the plate laminated portion 2 of the above embodiment, the annular portion 42 of the gasket 4 is arranged at a position eccentric to the communication hole 311 on the alternating region portion 20 side, but the configuration is not limited to this. For example, the annular portion 42 may be arranged in a state where the circular communication hole 311 and the center of the annular portion 42 are aligned with each other.

1 ... Plate type heat exchanger, 2 ... Plate laminated part, 20 ... Alternating region part, 21, 26 ... Holding area, 22 ... Channel area, 25 ... Same area part, 3 ... Heat transfer plate (counterpart plate), 30 ... Main heat transfer part, 300a ... First main heat transfer region (main heat transfer region), 300b ... Second main heat transfer region (main heat transfer region), 301 ... Arrangement part, 3011 ... Flat part, 3012 ... Concavo-convex part , 3012a ... wall part (fourth part), 3012b ... top (third part), 31, 31a, 31b ... communication part, 311, 311a, 311b ... communication hole, 32 ... weir part, 320a ... first weir part transmission Heat region (heat transfer region of the weir), 320b ... Second heat transfer region of the weir (heat transfer region of the weir), 35, 35r ... First arrangement, 351, 351r ... Inner part, 3511 ... Bottom wall (first) Seven parts), 3512, 3512r ... First side wall part (second part), 3513, 3513r ... Second side wall part (sixth part), 3514, 3514r ... Support part, 352, 352r ... Outer part, 3521 ... First Flat portion, 3522, 3522r ... Width direction defining portion, 36, 36r ... Hole peripheral portion (first portion), 37, 37r ... Second arrangement portion, 371 ... Second flat portion, 372, 372r ... Third side wall portion, 373, 373r ... 4th side wall, 38, 38r ... Connection (fifth part), 4 ... Gasket, 41 ... Flow path demarcation part, widening part ... 411, Main body part ... 412, Extension part ... 413, 42 ... Circular portion, 421 ... First arc portion, 4211 ... Central portion, 4212a ... First outer portion, 4212b ... Second outer portion, 422 ... Second arc portion, 43 ... Connection portion, 5a, 5b ... Frame, 51 ... Penetration Holes, 52, 53 ... Notches, 6 ... Guides, 61 ... Guide bars, 62 ... Support members, 7 ... Tightening members, 71 ... Bolts, 72 ... Nuts, 9a, 91a, 92a ... Convex parts, 9b, 91b , 92b ... concave, 100 ... plate type heat exchanger, 110 ... heat transfer plate, 111, 112, 113, 114 ... communication holes, 115, 116 ... concave, 120a, 120b ... gasket, 121a ... first flow path forming portion, 121b ... Second flow path forming portion, 122a ... First annular portion, 122b ... Second annular portion, 123a ... First connecting portion, 123b ... Second connecting portion, A ... First fluid (fluid), B ... Second Fluid (fluid), C1 ... 1st flow path (flow path), C2 ... 2nd flow path (flow path), CL1 ... vertical center line of heat transfer plate, CL2 ... horizontal center line of heat transfer plate, CL3 ... gasket Center line, Ef1, Ef2 ... elastic force, L1, L2 ... tangent line, Ra ... first flow path (flow path), Ra1, Ra2 ... first series passage ( (Communication passage), Rb ... Second flow path (flow path), Rb1, Rb2 ... Second communication passage (communication passage), S1 ... First surface, S2 ... Second surface, T1 ... First region, T2 ... Second Area, V ... virtual surface, α ... gap

Claims (7)

A plate laminated portion having a plurality of heat transfer plates stacked in a predetermined direction and a plurality of gaskets sandwiched between the heat transfer plates to form a flow path through which a fluid can flow between the heat transfer plates. ,
The plate laminated portion is
An alternating region portion in which a holding region in which the gasket is sandwiched in the predetermined direction and a flow path region through which the fluid can flow are alternately formed via the heat transfer plate.
The sandwiching region has the same region portion formed via the heat transfer plate in the predetermined direction.
The alternating region constituent portion constituting the alternating region portion in the heat transfer plate is
The first part along the virtual plane orthogonal to the predetermined direction,
A second sandwiching region is formed between the first portion and the other plate by bending the first portion in a direction away from the mating plate, which is a heat transfer plate adjacent to the first portion and adjacent to the first portion. With the part,
The same region constituent portion constituting the same region portion in the heat transfer plate is
The third part along the virtual surface and
It has a fourth portion that extends from the third portion and bends with respect to the third portion in a direction away from the counterpart plate to form the sandwiching region with the counterpart plate.
The angle of the second portion with respect to the first portion in the cross section along the surface including the cross section of the gasket sandwiched in the sandwiching region of the alternating region constituent portion is the cross section of the gasket sandwiched in the sandwiching region of the same region constituent portion. A plate heat exchanger that is greater than the angle of the fourth portion with respect to the third portion in a cross section along a surface including the surface. The alternating region component of the heat transfer plate
A fifth portion arranged at a distance from the first portion and along the virtual surface in the direction from the first portion to the second portion,
A sixth portion that extends from the fifth portion toward the first portion and bends with respect to the fifth portion in a direction away from the mating plate to form a sandwiching region between the fifth portion and the mating plate. Have and
The angle of the sixth portion with respect to the fifth portion in the cross section along the surface including the cross section of the gasket sandwiched in the sandwiching region of the alternating region constituent portion is the cross section of the gasket sandwiched in the sandwiching region of the same region constituent portion. The plate heat exchanger according to claim 1, which is larger than the angle of the fourth portion with respect to the third portion in the cross section along the surface including the surface. The alternating region component of the heat transfer plate has a seventh portion that connects the tip of the second portion and the tip of the sixth portion and is along the virtual surface.
The portion of the gasket that is arranged in the sandwiching area is
A central portion sandwiched between the seventh portion and the mating plate,
A first outer portion adjacent to the central portion and sandwiched between the second portion and the mating plate,
It has a second outer portion that is adjacent to the central portion and is sandwiched between the sixth portion and the mating plate.
The plate heat exchanger according to claim 2, wherein the elastic force in the predetermined direction at the central portion is larger than the elastic force in the predetermined direction at the first outer portion and the second outer portion. The central portion, the first outer portion, and the second outer portion are integrated.
The portions arranged in the sandwiching region of the gasket are the first outer portion and the second portion when the central portion is in contact with the seventh portion in a state where the elastic force in the predetermined direction is not generated. In a state where the gasket is sandwiched between the heat transfer plates and the fluid can flow through the flow path, the predetermined state is formed. The central portion and the seventh portion are in contact with each other in a state where elastic force is generated in the direction, the first outer portion and the second portion are in contact with each other, and the second outer portion and the sixth portion are in contact with each other. The plate heat exchanger according to claim 3, which has a shape. Each of the plurality of heat transfer plates has a through hole and has a through hole.
The plate laminated portion has a communication passage formed by connecting the through holes in the predetermined direction.
The communication passage communicates with the flow path formed between the heat transfer plates, and communicates with the communication passage.
Any of claims 1 to 4, wherein the alternating region portion is arranged so that the first portion and the second portion are arranged in a direction away from the through hole at the peripheral edge portion of the communication passage in the plate laminated portion. The plate heat exchanger according to item 1. In the heat transfer plate pair forming the sandwiching region in the alternating region portion, the first portions face each other in an abutting state, and in the heat transfer plate pair forming the flow path region, the heat transfer plate pair is described. The first parts face each other at intervals in the predetermined direction,
The plate-type heat according to claim 5, wherein the alternating region portion is arranged so that the first portion of each alternating region component faces the communication passage and extends along the peripheral edge of the communication passage. Exchanger. The through hole of the heat transfer plate is circular and has a circular shape.
The gasket has an annular portion that surrounds the through hole and has an annular shape.
The plate heat exchanger according to claim 6, wherein the annular portion includes a portion arranged in the sandwiching region and is arranged at a position eccentric to the alternating region portion side with respect to the through hole.

Images