JP2022147760A - Plate type heat exchanger - Google Patents

Abstract

To provide a plate type heat exchanger with high heat exchange efficiency, in which a fluid is easily integrated to a fin body of an inner fin.SOLUTION: A plate type heat exchanger comprises: a plurality of heat transfer plates that have plate parts and peripheral wall parts, and which form channels for flowing a fluid in a first direction to a space surrounded by the peripheral wall parts between the plate parts by being laminated; and a plurality of inner fins 60 and 70 that are arranged on the inside of the channel of each heat transfer plate, which are disposed on fin body parts 61 and 71 having a plurality of fins, and at end parts of the fin body parts 61 and 71, orthogonal to the first direction and placed in a second direction parallel to the plate parts, and which have flange parts 62 and 72 placed at positions away from the plate parts forming the channels in which the fins body parts 61 and 71 are arranged. Each heat transfer plate has a protrusion that protrudes to one surface side from the plate part that the heat transfer plate itself has, and closes a gap between the flange parts 62 and 72 of the inner fin arranged in its own channel.SELECTED DRAWING: Figure 7

Description

The present disclosure relates to plate heat exchangers.

A plate heat exchanger has a plurality of heat transfer plates stacked at regular intervals. The plate heat exchanger exchanges heat by alternately flowing two fluids between the heat transfer plates. In such a plate-type heat exchanger, inner fins, which are not integrated with the heat transfer plates but are manufactured as separate parts, are sometimes provided on the heat transfer plates in order to improve heat exchange efficiency.

For example, Patent Document 1 discloses a plate-type heat exchanger that includes a heat transfer plate having a rectangular flow path formed in the center in the longitudinal direction, and inner fins placed in the flow path of the heat transfer plate. disclosed.

In the plate-type heat exchanger described in Patent Document 1, the heat transfer plate has a positioning projection and the inner fin has a positioning recess in order to prevent the inner fins from being displaced. The position of the inner fin with respect to the heat transfer plate is determined by fitting the positioning recess of the inner fin to the positioning protrusion of the heat transfer plate.

JP 2019-78441 A

In the plate-type heat exchanger described in Patent Document 1, the positioning protrusion is provided near the inner wall in the lateral direction of the flow path formed in the heat transfer plate. On the other hand, the positioning concave portion is provided at the fin end portion of the fin main body portion in the lateral direction where the inner fin has a corrugated fin main portion portion which is rectangular in plan view as a whole. As a result, when the recess for positioning is fitted to the protrusion for positioning, a gap is generated between the inner wall of the flow path in the lateral direction and the fin end portion of the fin main body where the recess for positioning is located.

In this state, when the fluid flows through the flow path of the heat transfer plate, the gap between the inner wall of the flow path in the lateral direction and the fin end portion of the fin main body having the concave portion for positioning is formed. pressure loss is also reduced. This makes it easier for the fluid to flow through the gap than through the fin main body. As a result, the amount of fluid flowing through the fin bodies is relatively reduced, and the heat exchange efficiency of the plate heat exchanger is lowered.

The present disclosure has been made to solve the above problems, and an object of the present disclosure is to provide a plate-type heat exchanger in which fluid is easily collected in the fin main body of the inner fins and the heat exchange efficiency is high.

To achieve the above object, a plate heat exchanger according to the present disclosure includes multiple heat transfer plates and multiple inner fins. The plurality of heat transfer plates includes a plate portion having inlet/outlet holes formed at both ends in the first direction and a peripheral wall portion provided on one surface side of the plate portion and surrounding the outer circumference of the plate portion. and are stacked with the plate portions facing each other with one surface facing the same direction, so that the space surrounded by the peripheral wall portion between the plate portions is filled with the fluid in the first direction. form a path. In addition, the plurality of inner fins are disposed inside the flow paths of the respective heat transfer plates, and the fin body portion having the plurality of fins and the second direction perpendicular to the first direction and parallel to the plate portion of the fin body portion have the plurality of fins. It has a collar portion located at the end in the direction and spaced apart from the plate portion forming the flow path in which the fin body portion is arranged. Then, the heat transfer plate has a convex portion that protrudes from its own plate portion toward one surface side and closes the gap with the collar portion of the inner fin arranged in its own flow path.

According to the configuration of the present disclosure, the convex portion of the heat transfer plate protrudes from the plate portion of the heat transfer plate itself to one surface side, and is the flange of the inner fin arranged in the flow path of the heat transfer plate itself. close the gap between the Therefore, it is difficult for the fluid to flow through the gap between the flange portion of the inner fin and the plate portion. As a result, the fluid is more likely to concentrate in the fin body than in the flange of the inner fin, and the heat exchange efficiency of the plate heat exchanger is high.

A perspective view of a plate heat exchanger according to Embodiment 1 of the present disclosure 1 is an exploded perspective view of a plate heat exchanger according to Embodiment 1 of the present disclosure; FIG. FIG. 2 is a perspective view of inner fins provided on a first heat transfer plate included in a plate heat exchanger according to Embodiment 1 of the present disclosure; FIG. 2 is a front view of a first heat transfer plate provided with inner fins included in the plate heat exchanger according to Embodiment 1 of the present disclosure; Sectional view of the first heat transfer plate without the first protrusion and the second heat transfer plate without the second protrusion, which are laminated with inner fins attached. Sectional view of a laminate included in a plate heat exchanger according to Embodiment 1 of the present disclosure Enlarged view of the VII region shown in FIG. Front view of a first heat transfer plate included in a plate heat exchanger according to Embodiment 1 of the present disclosure Front view of a second heat transfer plate included in a plate heat exchanger according to Embodiment 1 of the present disclosure Front view of a laminate included in a plate heat exchanger according to Embodiment 2 of the present disclosure Front view of a first heat transfer plate included in a plate heat exchanger according to Embodiment 2 of the present disclosure Front view of a second heat transfer plate included in a plate heat exchanger according to Embodiment 2 of the present disclosure

Hereinafter, plate heat exchangers according to embodiments of the present disclosure will be described in detail with reference to the drawings. In addition, the same code|symbol is attached|subjected to the same or equivalent part in the figure. In the orthogonal coordinate system XYZ shown in the figure, the horizontal direction is The X axis is the vertical direction, the Z axis is the vertical direction, and the Y axis is the direction perpendicular to the X and Z axes. Hereinafter, description will be made with reference to this coordinate system as appropriate.

(Embodiment 1)
The plate heat exchanger according to Embodiment 1 is a plate heat exchanger in which two types of heat transfer plates having inner fins fitted in flow paths are alternately laminated. In this plate heat exchanger, the heat transfer plate is provided with a protrusion that closes the gap in order to prevent the fluid from flowing into the gap between the end of the inner fin and the bottom wall of the flow path. First, the overall configuration of the plate heat exchanger will be described with reference to FIGS. 1 and 2. FIG.

FIG. 1 is a perspective view of a plate heat exchanger 1A according to Embodiment 1. FIG. FIG. 2 is an exploded perspective view of the plate heat exchanger 1A. In addition, in FIG. 2, in order to facilitate understanding, only outlines of the inner fins 60 and 70, the first heat transfer plate 10, and the second heat transfer plate 20 are shown, and the detailed structure is omitted.

As shown in FIGS. 1 and 2, the plate heat exchanger 1A includes a plurality of alternately stacked first heat transfer plates 10 and second heat transfer plates 20, and the stacked first heat transfer plates 10 and and side plates 40 and 50 that reinforce the second heat transfer plate 20 .

The first heat transfer plate 10 is a member having a channel through which the first fluid, which is one of the objects to be heat exchanged, flows. As shown in FIG. 2, the first heat transfer plate 10 includes a first plate portion 11 for forming the bottom of the flow channel, and a first peripheral wall portion 12 for forming the side wall of the flow channel. Prepare.

The first plate portion 11 is formed in a rectangular flat shape with rounded corners. And the board surface is turned to the front side. On the other hand, the first peripheral wall portion 12 extends from the edge portion of the first plate portion 11 to the front side, that is, in the +Y direction by a certain length. The first peripheral wall portion 12 surrounds the outer periphery of the first plate portion 11 . Furthermore, the first peripheral wall portion 12 is integrated with the first plate portion 11 by pressing a metal plate. With these configurations, the first plate portion 11 and the first peripheral wall portion 12 form a channel through which the first fluid flows.

2 is a schematic diagram, the first peripheral wall portion 12 is perpendicular to the first plate portion 11, but the actual first peripheral wall portion 12 slopes outward. Furthermore, a second peripheral wall portion 22 to be described later is also inclined to the outside of the second plate portion 21 .

In addition, when the first heat transfer plates 10 and the second heat transfer plates 20 are alternately laminated in the front-rear direction to form the laminate 30, the first plate portion 11 supplies the first fluid to the above-described flow path. In order to flow or to flow the second fluid through the channels of the second heat transfer plate 20, the first inlet hole 13, the first outlet hole 14, the second It has passage holes 15 and 16 . These first inflow hole 13 , first outflow hole 14 , and second passage holes 15 and 16 circularly pass through the first plate portion 11 .

To explain each hole, the first inlet hole 13 is formed in the first heat transfer plate 10 itself when the first heat transfer plate 10 and the second heat transfer plate 20 form the laminate 30. It is provided to allow the first fluid to flow from the flow path into the flow path of the first heat transfer plate 10 adjacent on the back side with the first heat transfer plate 10 and the second heat transfer plate 20 interposed therebetween. The first inflow hole 13 is connected to a first passage hole 23 (described later) of the second heat transfer plate 20 on the back side of the first heat transfer plate 10 in which the first inflow hole 13 is formed. It has a ring-shaped protrusion that surrounds and protrudes to the rear side.

Further, the first outflow hole 14 is formed in the first heat transfer plate 10 adjacent to the back side with the second heat transfer plate 20 interposed therebetween when the first heat transfer plate 10 and the second heat transfer plate 20 form the laminate 30 . It is provided for flowing out the first fluid from the flow path of the heat transfer plate 10 to the flow path of the first heat transfer plate 10 in which the first outlet hole 14 itself is formed. The first outflow hole 14 is connected to a later-described first passage hole 24 of the second heat transfer plate 20 on the back side of the first heat transfer plate 10 in which the first outflow hole 14 is formed. It has a ring-shaped protrusion that surrounds and protrudes to the rear side.

Furthermore, when the first heat transfer plate 10 and the second heat transfer plate 20 form the laminate 30, the second passage holes 15 and 16 are formed from the flow path of the second heat transfer plate 20 adjacent to the back side to the front side. It is provided for circulating the second fluid to the second heat transfer plate 20 adjacent to the side. The second passage holes 15 and 16 are connected to ring-shaped protrusions of a second inlet hole 25 and a second outlet hole 26, which will be described later, of the second heat transfer plate 20 adjacent on the front side thereof, and allow the second fluid to flow. For circulation, it has ring-shaped protrusions that protrude toward the front side and surround the second passage holes 15 and 16 respectively.

On the other hand, the second heat transfer plate 20 is a member having a channel through which the second fluid, which is another object of heat exchange, flows. As with the first heat transfer plate 10, the second heat transfer plate 20 includes a second plate portion 21 for forming the bottom of the flow channel, a second peripheral wall portion 22 for forming the side wall of the flow channel, Prepare.

The second plate portion 21 is formed in the same shape and size as the first plate portion 11 of the first heat transfer plate 10 . The second peripheral wall portion 22 is also formed in the same shape and size as the first peripheral wall portion 12 of the first heat transfer plate 10 . Then, the second plate portion 21 and the second peripheral wall portion 22 are integrally formed by press working, as in the case of the first heat transfer plate 10 . With these configurations, the second plate portion 21 and the second peripheral wall portion 22 form a channel through which the second fluid flows.

Further, the second plate portion 21 allows the second fluid to flow through the flow path formed by the second plate portion 21 itself when the first heat transfer plate 10 and the second heat transfer plate 20 form the laminate 30. or to allow the first fluid to flow through the channels of the first heat transfer plate 10, the first heat transfer plate 10 has the first inflow hole 13, the first outflow hole 14, the second passage holes 15, 16 and the front-back direction. First passage holes 23 and 24, a second inflow hole 25, and a second outflow hole 26 are provided at positions overlapping with . These first passage holes 23 , 24 , second inflow hole 25 , and second outflow hole 26 are the same as the first inflow hole 13 , first outflow hole 14 , and second passage holes 15 , 16 of the first heat transfer plate 10 . It is formed in a circular shape with a diameter and passes through the second plate portion 21 .

Each hole of the second plate portion 21 will be described. Each of the first passage holes 23 and 24 has a ring-shaped protrusion that protrudes to the front side and surrounds itself. When the first heat transfer plate 10 and the second heat transfer plate 20 form the laminate 30 , the first passage holes 23 and 24 are arranged such that the ring-shaped protrusions are aligned with the second heat transfer plate 20 . The first heat transfer plate 10 adjacent on the front side contacts and connects with the ring-shaped projections surrounding the above-described first inflow hole 13 and first outflow hole 14 . As a result, the first passage holes 23 and 24 allow the first fluid to flow in and out between the first inlet holes 13 and the first outlet holes 14 of the first heat transfer plate 10 adjacent on the front side. be. As a result, the first passage holes 23 and 24 allow the first fluid to flow from the flow path of the first heat transfer plate 10 adjacent on the back side to the flow path of the first heat transfer plate 10 adjacent on the front side. do.

In addition, the second inflow holes 25 have ring-shaped protrusions that protrude toward the rear side and surround themselves. Then, when the first heat transfer plate 10 and the second heat transfer plate 20 form the laminate 30, the ring-shaped protrusion is positioned at the first heat transfer plate 10 adjacent to the second heat transfer plate 20 on the back side. is connected in contact with the ring-shaped protrusion of the second passage hole 15 of . As a result, the second inflow hole 25 flows from the channel of the second heat transfer plate 20 in which it is formed through the second passage hole 15 of the first heat transfer plate 10 on the rear side. This allows the second fluid to flow into the channel of the second heat transfer plate 20 which is located on the rear side of the first heat transfer plate 10 .

Furthermore, like the second inflow hole 25, the second outflow hole 26 has ring-shaped protrusions that protrude toward the rear side and surround themselves. When the first heat transfer plate 10 and the second heat transfer plate 20 form the laminate 30 , the ring-shaped protrusion is the first heat transfer plate 10 adjacent to the second heat transfer plate 20 on the back side. It contacts and connects with the ring-shaped protrusion of the two-passage hole 16 . As a result, the second outflow hole 26 itself is formed from the flow path of the second heat transfer plate 20 on the back side of the first heat transfer plate 10 adjacent to the back side thereof. It is possible to cause the second fluid to flow out to the flow path of the second heat transfer plate 20 where it is located.

A plurality of each of the first heat transfer plates 10 and the second heat transfer plates 20 having such a configuration face the surface with the first peripheral wall portion 12 or the surface with the second peripheral wall portion 22 facing the front. , are alternately laminated with a certain gap in the front-rear direction. As a result, the laminate 30 having the first plate portion 11 and the second plate portion 21 opposed to each other is formed. This laminate 30 is sandwiched between side plates 40 and 50 in order to increase its strength.

The side plate 40 is arranged on the front side of the laminate 30 to reinforce the laminate 30 . Specifically, in the laminate 30, the first heat transfer plate 10 is located on the frontmost side. The side plate 40 is formed in a rectangular shape with rounded corners that can be fitted into the space surrounded by the first peripheral wall portion 12 of the first heat transfer plate 10 . Then, it is fitted and joined to the space from the front side. As a result, the side plate 40 covers and closes the flow path from the front side and reinforces the laminate 30 .

In addition, the side plate 40 supplies and discharges the first fluid and the second fluid to and from the flow path of the first heat transfer plate 10 and the flow path of the second heat transfer plate 20 in the laminate 30. It has circular tubes 41-44 in the corners, upper right corner and lower right corner.

These circular tubes 41 to 44 overlap the first inlet hole 13, the first outlet hole 14, and the second passage holes 15 and 16 of the first heat transfer plate 10 described above in the front-rear direction. Also, the circular tubes 41 to 44 overlap the first passage holes 23 and 24, the second inlet hole 25, and the second outlet hole 26 of the second heat transfer plate 20 in the front-rear direction. As a result, the circular tubes 41-44 facilitate the flow of the first fluid and the second fluid into the respective holes. Alternatively, the first fluid and the second fluid are facilitated to flow out from each hole.

Of these circular tubes 41 to 44, the circular tubes 41 and 42 are connected to an external device (not shown) to supply and discharge the first fluid as indicated by arrows P shown in FIG. In addition, the circular tubes 43 and 44 supply and discharge the second fluid as indicated by arrows Q by being connected to another external device (not shown). This causes the first fluid and the second fluid to exchange heat.

On the other hand, the side plate 50 is formed to have the same shape and size as the second plate portion 21 of the second heat transfer plate 20 . In the laminate 30, the second heat transfer plate 20 is located on the rearmost side, and the side plate 50 is superimposed on the second plate portion 21 of the second heat transfer plate 20 from the rear side. , is joined to the second plate portion 21 . Thereby, the side plate 50 reinforces the laminate 30 .

In the plate heat exchanger 1A, as described above, the first heat transfer plates 10 and the second heat transfer plates 20 are alternately laminated to form the laminate 30 . Further, in the first heat transfer plate 10 and the second heat transfer plate 20, respective holes through which the first fluid and the second fluid flow in and out are formed at the four corners of the first plate portion 11 and the second plate portion 21. . Therefore, when the first fluid and the second fluid are supplied from the circular tubes 41 and 43 of the side plate 40 , the first fluid and the second fluid flow through the first heat transfer plate 10 and the second heat transfer plate 20 . It flows in the longitudinal direction of the first plate portion 11 and the second plate portion 21, that is, in the vertical direction. The channel of the first heat transfer plate 10 is blocked by the second plate portion 21 of the second heat transfer plate 20 adjacent in the front-rear direction. Also, the flow path of the second heat transfer plate 20 is blocked by the first plate portion 11 of the first heat transfer plate 10 adjacent in the front-rear direction. Therefore, the heat of the first fluid and the second fluid is transferred to the first plate portion 11 and the second plate portion 21 to perform heat exchange.

In this heat exchange, it is desirable that the heat transfer from the first fluid and the second fluid to the first heat transfer plate 10 and the second heat transfer plate 20 is high in order to increase the heat exchange efficiency. Therefore, inner fins 60 and 70 are provided in the flow paths of the first heat transfer plate 10 and the flow paths of the second heat transfer plate 20 in order to improve heat transfer.

Further, the first fluid and the second fluid are fluids having mutually different conditions such as temperature, phase, pressure, constituent substances, etc. For example, one is water and the other is a refrigerant. Therefore, it is desirable that the inner fins 60 and 70 have a shape and a size according to the characteristics of the first fluid and the second fluid to be heat-exchanged. Therefore, the inner fins 60 and 70 are provided with the first transmission fins 60 and 70 so that when the fluids flowing as the first fluid and the second fluid are changed, the shapes and sizes can be easily changed according to the characteristics of those fluids. It is not integrated with the heat plate 10 and the second heat transfer plate 20, but is manufactured as a separate component.

Next, the configuration of the inner fins 60, 70 will be described with reference to FIGS. 3 to 5 in addition to FIG.

FIG. 3 is a perspective view of the inner fins 60 provided on the first heat transfer plate 10 included in the plate heat exchanger 1A. FIG. 4 is a front view of the first heat transfer plate 10 provided with the inner fins 60, which is provided in the plate heat exchanger 1A. FIG. 5 shows the first heat transfer plate 10 without the first protrusion 17 and the second heat transfer plate 20 without the second protrusion 27, which are laminated with the inner fins 60 and 70 attached. is a cross-sectional view of.

3, only a part of the inner fin 60 is enlarged for easy understanding. Further, the plate surface of the first plate portion 11 is indicated by dotted lines to indicate the positional relationship. In FIG. 5 , for ease of understanding, the first heat transfer plate 10 and the second heat transfer plate 20 each show one laminate 30 .

As shown in FIG. 3, the inner fin 60 has a corrugated fin main body 61 and a flange extending rightward from the right end of the fin main body 61 in order to increase the contact area with the first fluid. 62; In addition, as shown in FIG. 4 , the inner fin 60 also has a flange portion 62 at the left end of the fin body portion 61 .

The fin main body 61 is formed in a shape called an offset fin, as shown in FIG. 3, in order to improve heat transfer efficiency. Specifically, the fin main body 61 has a constant width BW in the vertical direction, and has a plurality of corrugated bands 63 that undulate in the front-rear direction with a constant amplitude A1 and extend in the left-right direction with a constant wavelength L1. , are vertically arranged and connected. The amplitude A1 is the same as the depth of the channel in which the inner fins 60 are installed, that is, the depth in the Y direction. The tops 64 and bottoms 65 of the corrugated bands 63 adjacent to each other in the vertical direction are shifted by a certain distance, specifically, by half the wavelength L1. With such a configuration, the fin main body 61 rectifies the fluid in the vertical direction and enhances the efficiency of heat transfer from the fluid.

The fin body 61 also has flat corrugated tops 64 and bottoms 65 . Thereby, when installed in the channel, the contact area with the first plate portion 11 forming the channel is increased. Moreover, the contact area with the second plate portion 21 that covers the flow path from the front side is increased. As a result, heat transfer to the first heat transfer plate 10 and the second heat transfer plate 20 is enhanced.

At the right end of the fin body 61, each corrugated band 63 rises from the bottom 65 to the top 64 side. The right end of the fin main body 61 is connected to a flange 62 extending further to the right.

The flange portion 62 is a portion that is formed to provide a cutting allowance when manufacturing the inner fin 60 . That is, the inner fins 60 are formed by pressing a metal plate, and the flange portion 62 is a cutting allowance when cutting off the inner fins 60 produced from the pressed metal plate after press working. It is a flat plate-like portion set to provide. In this specification, the fin body 61 is referred to as a flange 62 because of the shape of the fin main body 61 that covers the bottom of the flow path in an eave-like manner from a position away from the bottom of the flow path.

The flange portion 62 is located at a position where the top portion 64 and the bottom portion 65 of the vertically adjacent corrugated band 63 are shifted in the left-right direction by a predetermined distance, and the bottom portion 65 at the rightmost end thereof is separated from the bottom portion 65 by a predetermined length FL1. It extends straight to the right. The length FL1 of the flange portion 62 is longer than the fin pitch P1 due to manufacturing restrictions. For example, the length FL1 of the flange portion 62 is 2 to 3 mm when the fin pitch P1 is 2 mm. The brim portion 62 is connected to each band 63 described above.

The flange portion 62 is also provided at the left end of the fin body portion 61, as shown in FIG. As shown in FIG. 5, the band 63 of the fin body 61 also rises from the bottom 65 toward the top 64 at the left end of the flange 62, and the flange 62 extends leftward from the left end of the raised band 63. there is Its shape is bilaterally symmetrical with the flange portion 62 at the right end shown in FIG. Therefore, detailed description is omitted.

5, the inner fin 70 includes a fin body portion 71 having the same configuration as the fin body portion 61 and having a shape called an offset fin. The fin main body 71 differs from the first fluid in the pressure, flow velocity, and other conditions of the second fluid, so that the corrugated amplitude A2 and the wavelength L2 differ from those of the fin main body 61. For example, the corrugated amplitude A2 and wavelength L2 are larger than those of the fin body 61 .

Further, the inner fin 70 has a flange portion 72 having the same configuration as the flange portion 62 at the left end of the fin body portion 71 . Also, although not shown, a flange portion 72 is also provided at the right end. The length FL2 of these flanges 72 in the horizontal direction differs from that of the flange 62 because the corrugated amplitude A2 and the wavelength L2 of the fin body 71 are different from those of the fin body 61 of the inner fin 60. is shorter than the length FL1 of the flange portion 62 .

As shown in FIGS. 2 and 4, the inner fins 60 and 70 are formed in a rectangular shape as a whole when viewed from the front. The rectangular shape is the area between the first inlet hole 13 and the first outlet hole 14 of the channel of the first heat transfer plate 10, or the area from the second inlet hole 25 of the channel of the second heat transfer plate 20. It has a rectangular shape that can be fitted in the area up to the second outflow hole 26 . For example, the inner fins 60 and 70 have a longitudinal length of about 400 mm and a lateral length of 45 to 195 mm. Inner fins 60 and 70 are nested in these areas in the orientation described above. The inner fins 60 and 70 bring the corrugated top portion 64 and bottom portion 65 into contact with the first plate portion 11 and the second plate portion 21, respectively. As a result, heat transfer is enhanced when the first fluid and the second fluid flow through the channels of the first heat transfer plate 10 and the second heat transfer plate 20 .

As mentioned above, the collar 62 of the inner fin 60 is on the top 64 side of the corrugation, not on the bottom 65 side. The same applies to the flange portion 72 of the inner fin 70 . Therefore, when the inner fins 60 and 70 are installed in the channels of the first heat transfer plate 10 and the second heat transfer plate 20, as shown in FIG. A gap 2 is generated between the first plate portion 11 forming the . Similarly, a gap 3 is formed between the flange portion 72 of the inner fin 70 and the second plate portion 21 forming the bottom of the flow path.

Further, the gap 2 between the flange portion 62 of the inner fin 60 and the first plate portion 11 is such that the length FL1 of the flange portion 62 in the lateral direction is larger than the fin pitch P1, as described above. Between the corrugated tops 64 or bottoms 65 are larger than the fin spaces 5 for the flow of the first fluid. Further, the gap 2 extends in the vertical direction like the fin space 5 for flowing the first fluid of the fin main body 61, that is, in the Z direction in which the first fluid flows. As a result, the gap 2 has a smaller pressure loss than the fin main body 61 when the first fluid flows through the flow path, and the first fluid flows easily. This makes it easier for the first fluid to concentrate in the gap 2 . As a result, the amount of the first fluid flowing through the fin main body 61 is reduced, and the heat exchange efficiency is lowered.

The same applies to the gap 3 between the flange portion 72 of the inner fin 70 and the second plate portion 21, and the second fluid tends to concentrate in the gap 3 as well. As a result, the flow rate of the second fluid also decreases in the fin body portion 71 of the inner fin 70, resulting in a decrease in heat exchange efficiency.

Therefore, in the plate heat exchanger 1A, the first heat transfer plate 10 and the second heat transfer plate 20 are provided with the first protrusion and the second protrusion that close the gap 2 described above. Next, with reference to FIGS. 6 and 7, the first and second protrusions of the first heat transfer plate 10 and the second heat transfer plate 20 and their associated configurations will be described.

FIG. 6 is a cross-sectional view of a laminate 30 included in the plate heat exchanger 1A. FIG. 7 is an enlarged view of the VII region shown in FIG. FIG. 8 is a front view of the first heat transfer plate 10. FIG. FIG. 9 is a front view of the second heat transfer plate 20. FIG.

6 and 7 show an example in which two first heat transfer plates 10 and two second heat transfer plates 20 are stacked for easy understanding. Inner fins 60 and 70 are installed only on one first heat transfer plate 10 and one second heat transfer plate 20 among them. Furthermore, FIG. 6 shows a cross section when it is assumed that the laminated body 30 is cut at the position of the VI-VI cutting line shown in FIGS. In addition, in FIG. 8, the positions of the inner fins 60 and the positions of the second protrusions 27 on the second heat transfer plate 20 are indicated by dotted lines in order to indicate the positional relationship. Similarly, in FIG. 9, the positions of the inner fins 70 and the positions of the first projections 17 on the first heat transfer plate 10 are indicated by dotted lines.

As shown in FIGS. 6 and 7, the first heat transfer plate 10 and the second heat transfer plate 20 are provided with first protrusions 17 and second protrusions 27 protruding into the channels, respectively.

The first convex portion 17 is provided at a corner portion formed by the left and right ends of the first plate portion 11 and the first peripheral wall portion 12 in the channel of the first heat transfer plate 10 where the inner fins 60 are arranged. ing. Similarly, the second convex portion 27 is formed at the corner portion formed by the left and right ends of the second plate portion 21 and the second peripheral wall portion 22 of the channel of the second heat transfer plate 20 where the inner fins 70 are arranged. is provided. As shown in FIG. 7 , in a cross-sectional view of the flow channel, that is, in an XY cross-sectional view, the first convex portion 17 has a longitudinal side connected to the first peripheral wall portion 12 and a lateral side. It has a rectangular shape whose sides are connected to the first plate portion 11, and the second convex portion 27 has an arc shape extending from the second peripheral wall portion 22 to the second plate portion 21, that is, a fan shape obtained by dividing a semicircle into two.

The height at which the first convex portion 17 and the second convex portion 27 protrude into the flow channel is +Y The heights H1 and H2 in the Y direction from the surface are smaller than the heights of the flanges 62 and 72 of the inner fins 60 and 70 by the thicknesses T1 and T2 of the flanges 62 and the clearance required for brazing. For example, the heights H1 and H2 of the first convex portion 17 and the second convex portion 27 in the Y direction are 0.4 to 4.0 mm. As a result, the first protrusion 17 and the second protrusion 27 are close to the flanges 62 and 72 to a distance that enables brazing. Collar portions 62 and 72 are brazed to the tips thereof.

In addition, the lateral widths of the first protrusion 17 and the second protrusion 27, that is, the widths W1 and W2 in the X direction are larger than the lateral lengths FL1 and FL2 of the flanges 62 and 72 of the inner fin 60. The variations in manufacturing and assembly are only small. For example, the widths W1 and W2 of the first protrusion 17 and the second protrusion 27 in the X direction are set to be 1.3 to 2.4 mm.

By being formed in such a size, the first protrusion 17 and the second protrusion 27 close most of the gaps 2 and 3 shown in FIG. 5 below the flanges 62 and 72. . As a result, the first fluid and the second fluid are prevented from flowing into these gaps 2 and 3 .

Further, as shown in FIG. 8, the first convex portion 17 extends from the left wall and the right wall of the first peripheral wall portion 12 of the first heat transfer plate 10 toward the right or left flow path in a front view. It has the shape of a protruding long and narrow rectangle. Similarly, as shown in FIG. 9, the second convex portion 27 extends from the left wall and the right wall of the second peripheral wall portion 22 of the second heat transfer plate 20 toward the right or left flow path in a front view. It has the shape of a protruding long and narrow rectangle. As a result, the first convex portion 17 and the second convex portion 27 are arranged along the first peripheral wall portion 12 of the first heat transfer plate 10 and the second peripheral wall portion 22 of the second heat transfer plate 20 to form the above-described flange portion. The gaps between 62 and 72 and the first plate portions 11 and 12 are closed. Then, the first fluid and the second fluid are suppressed from flowing into these gaps.

Furthermore, the positions of the first protrusion 17 and the second protrusion 27 are shifted in the vertical direction as shown in FIGS. 8 and 9 .

To explain the reason for the positional deviation, the first heat transfer plate 10 and the second heat transfer plate 20 are formed by pressing a metal plate to form the first protrusion 17 and the second protrusion 27. However, as a result of being formed in the pressing process, the corner portions of the first plate portion 11 and the second plate portion 21 are formed by bending toward the channel side, that is, toward the front side. As a result, as shown in FIG. 7, the recess of the space S1 is formed on the back side of the first convex portion 17 . Further, a recess of the space S2 is formed on the back side of the second convex portion 27 .

As a result, at the location where the first convex portion 17 is formed, the second fluid flowing through the flow path of the second heat transfer plate 20 on the back side flows into the space S1 on the back side of the first convex portion 17, The second fluid flows through the space S1 in the vertical direction, that is, in the Z direction. Also, at the location where the second convex portion 27 is formed, the first fluid flowing through the flow path of the first heat transfer plate 10 on the back side flows into the space S2 behind the second convex portion 27, Fluid flows in the Z direction through the space S2. Therefore, if the first convex portion 17 and the second convex portion 27 overlap in the front-rear direction, that is, in the Y direction, the gap shown in FIG. 2 and 3 are blocked, the first fluid and the second fluid flow in the Z direction through the space S2 and the space S1 shown in FIG. decrease.

On the other hand, if the first convex portion 17 and the second convex portion 27 do not overlap in the Y direction and are shifted in the Z direction, the space S1 is formed at the location in the Z direction where the first convex portion 17 is formed. Although the second fluid flows in, the first protrusion 17 is not formed at another location in the Z direction where the second protrusion 27 is formed. The second fluid never flows. Furthermore, since the second protrusion 27 closes the gap 3 , the second fluid is less likely to flow through the gap 3 . Thereby, the second fluid can be concentrated in the fin body portion 71 of the inner fin 70 . In addition, the first fluid flows into the space S2 at another location in the Z direction where the second convex portion 27 is formed. As a result of the absence of the portion 27, the space S2 itself does not exist and the first fluid does not flow into the space S2. Since the first protrusion 17 itself closes the gap 2 , the first fluid is less likely to flow through the gap 2 . As a result, the first fluid can be concentrated in the fin body portion 61 of the inner fin 60 .

Therefore, in order to prevent the first fluid and the second fluid from flowing through the spaces S1 and S2 in the Z direction at the same location in the Z direction, the first convex portion 17 and the second convex portion 27 are arranged as described above. The position is shifted in the Z direction.

The first convex portion 17 and the second convex portion 27 are shaped and arranged as described above, and are further brazed to the collar portions 62, 72 of the inner fins 60, 70 on the +Y side thereof. Thereby, the first convex portion 17 and the second convex portion 27 fix the inner fins 60 and 70 . As described above, the first convex portion 17 and the second convex portion 27 are located between the flange portion 62 of the inner fin 60 and the first plate portion 11, and the gap 2 shown in FIG. and the gap 3 of the second plate portion 21 are closed. As a result, the first convex portion 17 and the second convex portion 27 prevent the pressure loss in the gaps 2 and 3 from becoming smaller than the pressure loss in the fin body portions 61 and 71 . The gaps 2 and 3 are made difficult for the first fluid and the second fluid to flow. As a result, the first convex portion 17 and the second convex portion 27 suppress the amount of the first fluid and the second fluid flowing through the fin body portions 61 and 71 from decreasing, thereby increasing the heat exchange efficiency. there is

The first heat transfer plate 10 and the second heat transfer plate 20 of the plate heat exchanger 1A according to Embodiment 1 described above are examples of the heat transfer plate referred to in this specification. The first plate portion 11, the second plate portion 21, the first peripheral wall portion 12, and the second peripheral wall portion 22 are examples of the plate portion and the peripheral wall portion. The first fluid and the second fluid are examples of fluids. The corrugated top portion 64 and bottom portion 65 of the fin body portions 61 and 71 are examples of a plurality of fins that the fin body portions 61 and 71 have.

Also, the first inflow hole 13, the first outflow hole 14, the second inflow hole 25, and the second outflow hole 26 are examples of the inflow/outflow holes referred to in this specification. Here, the first inflow hole 13, the first outflow hole 14, the second inflow hole 25, and the second outflow hole 26 are switched between an external device that supplies the first fluid and the second fluid, and another external device. It can vary and in that case may be referred to as first outlet, first inlet, second outlet, second inlet.

Furthermore, the vertical direction, which is the direction in which the first fluid and the second fluid flow, that is, the Z direction is an example of the first direction in this specification, and the horizontal direction orthogonal thereto, that is, the X direction is It is an example of the second direction. Also, the first convex portion 17 and the second convex portion 27 are examples of convex portions. The front surface side of the first plate portion 11 and the second plate portion 21 from which the first convex portion 17 and the second convex portion 27 protrude is an example of one surface from which the convex portion protrudes.

As described above, in the plate heat exchanger 1A according to Embodiment 1, the first heat transfer plate 10 protrudes from the first plate portion 11 toward the flow path side, and the first plate portion 11 and the flange portion 62 It has a first protrusion 17 that closes the gap 2 therebetween. Therefore, it is difficult for the first fluid to flow into the gap 2 between the first plate portion 11 and the flange portion 62 . As a result, in the plate heat exchanger 1</b>A, the first fluid is more likely to concentrate in the fin main body portion 61 than in the flange portion 62 . Moreover, the heat exchange efficiency of the plate heat exchanger 1A is high.

Further, in the plate-type heat exchanger 1A, the second heat transfer plate 20 protrudes from the second plate portion 21 toward the flow path, and closes the gap 3 between the second plate portion 21 and the flange portion 72. It has a convex portion 27 . Therefore, as in the case of the first heat transfer plate 10 , the second fluid is less likely to flow into the gap 3 between the second plate portion 21 and the flange portion 72 , and the first fluid flows into the fin body portion 71 rather than into the flange portion 72 . are easily aggregated. The heat exchange efficiency of the plate heat exchanger 1A is high.

The first convex portion 17 and the second convex portion 27 do not overlap in the stacking direction of the first heat transfer plate 10 and the second heat transfer plate 20, and are misaligned. By bending the plate surfaces of the first heat transfer plate 10 and the second heat transfer plate 20, the first convex portion 17 and the second convex portion 27 are formed, and have a convex shape on one surface and a concave shape on the other surface. , the first fluid and the second fluid may pass through the recessed portion and flow. , the first fluid and the second fluid are prevented from flowing through the recessed portion.

The first convex portion 17 is formed at the corner portion formed by the first plate portion 11 and the first peripheral wall portion 12 of the first heat transfer plate 10, and is along the first peripheral wall portion 12. The strength of the heat exchanger 1A is high. Similarly, the second convex portion 27 is formed at the corner portion formed by the second plate portion 21 and the second peripheral wall portion 22 of the second heat transfer plate 20, and is along the second peripheral wall portion 22, so that the plate The strength of the type heat exchanger 1A is high.

(Modification)
In Embodiment 1, flanges 62 and 72 of inner fins 60 and 70 are brazed to first protrusion 17 and second protrusion 27 . However, the first protrusion 17 and the second protrusion 27 are not limited to this. In the plate heat exchanger 1A, the first heat transfer plate 10 and the second heat transfer plate 20 are laminated, and the adjacent first heat transfer plate 10 and the second heat transfer plate 20 are brazed. However, the flanges 62, 72 of the inner fins 60, 70 may not be brazed to the first protrusion 17 and the second protrusion 27, as long as sufficient mechanical strength can be obtained by the brazing.

For example, when the longitudinal direction of the first heat transfer plate 10 and the second heat transfer plate 20 is 100 to 800 mm, the width direction thereof is 50 to 200 mm, and the plate thickness is 0.2 mm, the first heat transfer plate Since the plates are sufficiently thick relative to the size of the plate 10 and the second heat transfer plate 20, the mechanical strength of the plate heat exchanger 1A is high. With such a size, the adjacent first heat transfer plate 10 and second heat transfer plate 20 are brazed to obtain sufficient mechanical strength. , 72 may not be brazed to the first protrusion 17 and the second protrusion 27 .

In Embodiment 1, the first convex portion 17 and the second convex portion 27 are close to the flange portions 62 and 72 to the extent that they can be joined. When not joined to the convex portion 17 and the second convex portion 27 , the first convex portion 17 and the second convex portion 27 are preferably in contact with the flange portions 62 and 72 .

(Embodiment 2)
In the plate heat exchanger 1A according to Embodiment 1, one first convex portion 17 and one second convex portion 27 are provided, but the first convex portion 17 and the second convex portion 27 are limited to this. not. A plurality of first protrusions 17 and second protrusions 27 may be provided.

A plate heat exchanger 1B according to Embodiment 2 includes a first heat transfer plate 80 provided with a plurality of first protrusions 87 and a second heat transfer plate 90 provided with a plurality of second protrusions 97. And prepare.

A plate heat exchanger 1B according to the second embodiment will be described below with reference to FIGS. 10 to 12. FIG. In the second embodiment, the configuration different from that of the first embodiment will be mainly described.

FIG. 10 is a front view of a laminate 35 included in the plate heat exchanger 1B according to Embodiment 2. FIG. FIG. 11 is a front view of the first heat transfer plate 80 included in the plate heat exchanger 1B. FIG. 12 is a front view of the second heat transfer plate 90 included in the plate heat exchanger 1B.

10, the laminate 35 in which the first heat transfer plate 80 and the second heat transfer plate 90 are alternately laminated in the order of the first heat transfer plate 80 and the second heat transfer plate 90 from the front side is shown. The figure seen from the front is shown. In order to facilitate understanding, the second convex portion 97 of the second heat transfer plate 90 is indicated by dotted lines. 10 and 12, the inner fins 60 and 70 are omitted in order to show the positional relationship between the first convex portion 87 and the second convex portion 97. As shown in FIG.

As shown in FIGS. 10 and 11, the first heat transfer plate 80 has a plurality of first protrusions 87 arranged along the left wall portion and the right wall portion of the first peripheral wall portion 82, respectively. there is

The plurality of first protrusions 87 are composed of a left wall portion of the first peripheral wall portion 82 in the upper region of the first heat transfer plate 80, a right wall portion of the first peripheral wall portion 82 in the upper region, The left wall portion of the first peripheral wall portion 82 located in the lower region of the first heat transfer plate 80 and the right wall portion of the first peripheral wall portion 82 located in the lower region are provided three each. These three first protrusions 87 are arranged vertically at a constant pitch P2.

Although not shown, each of the first convex portions 87 is formed by bending the first plate portion 81 toward the channel on the front side, like the first convex portion 17 of the first embodiment. Thereby, each of the first protrusions 87 protrudes into the flow path. The tip of the first convex portion 87 extends to the flange portion 62 of the inner fin 60 (not shown in FIGS. 10 and 11) and is joined to the flange portion 62 . The detailed shape of each of the first projections 87 and the relative position with respect to the flange portion 62 are the same as those of the first projections 17 of the first embodiment. Thereby, each of the first convex portions 87 closes the gap 2 between the flange portion 62 of the inner fin 60 and the first plate portion 81 . As a result, each of the first protrusions 87 prevents the first fluid from entering the gap 2 .

On the other hand, as shown in FIGS. 10 and 12, the second heat transfer plate 90 has a plurality of second projections 97 along the left wall portion and the right wall portion of the second peripheral wall portion 92, respectively. are arrayed.

The plurality of second protrusions 97 are the left wall portion of the second peripheral wall portion 92 in the upper region of the second heat transfer plate 90, the right wall portion of the second peripheral wall portion 92 in the upper region, the second The left wall portion of the second peripheral wall portion 92 in the lower region of the heat transfer plate 90 and the right wall portion of the second peripheral wall portion 92 in the lower region are provided with four of each. These four second protrusions 97 are arranged in the vertical direction at the same pitch P2 as the first protrusions 87 .

Furthermore, these four second protrusions 97 are vertically displaced from the three first protrusions 87 described above. Specifically, the vertical lengths of the first convex portion 87 and the second convex portion 97 described above are shorter than the pitch P2 described above. The first protrusion 87 is arranged in the center between the second protrusions 97 . As a result, the first protrusions 87 and the second protrusions 97 are alternately arranged in the vertical direction. As a result, as described in Embodiment 1, when the first convex portion 87 and the second convex portion 97 overlap in the front-rear direction, the first fluid and the second fluid flow into the first convex portion 87 and the second convex portion. This prevents the liquid from flowing vertically through the space 97 .

Although not shown, each of the second protrusions 97 is also formed by bending the second plate portion 91 toward the flow path on the front side in the same manner as the second protrusions 27 of the first embodiment. And it protrudes into the flow path. The tip of the second projection 97 extends to the flange portion 72 of the inner fin 70 (not shown in FIG. 12) and is joined to the flange portion 72 . The second convex portion 97 is also similar to the second convex portion 27 of the first embodiment in its detailed shape and position relative to the flange portion 72 . Thereby, each of the second convex portions 97 closes the gap 3 between the flange portion 72 of the inner fin 70 and the second plate portion 91 . As a result, each of the second protrusions 97 suppresses the entry of the second fluid into the gap 3 .

Among the plurality of second protrusions 97 , the highest or lowest second protrusion 97 is the highest or lowest of the plurality of first protrusions 87 . It is arranged above or below the one convex portion 87 . As a result, the uppermost or lowermost second convex portion 97 is more likely than the first convex portion 87 to be the first inflow hole 13, the first outflow hole 14, the second inflow hole 25, and the second outflow hole. closer to hole 26; As a result, when the second fluid has a greater influence on the heat exchange efficiency than the first fluid when entering the gap 3, the second convex portion 97 prevents the second fluid from entering the gap 3. It can be suppressed at a location closer to the inflow destination of the second fluid than the one convex portion 87 . Thereby, the heat exchange efficiency of the plate heat exchanger 1B can be improved.

For example, when the first fluid is water and the second fluid is a fluorocarbon refrigerant or a non-fluorocarbon refrigerant such as ammonia or carbon dioxide, the second fluid has a greater effect on exchange efficiency. The heat exchange efficiency of the plate heat exchanger 1B can be improved.

As described in the first embodiment, the first fluid is supplied from the circular pipe 41 at the corner of the lower region of the side plate 40, and the second fluid is supplied from the circular pipe 41 at the corner of the upper region on the opposite side. As a result of the feed from 43, the stack 35 is fed in a countercurrent manner with the first and second fluids flowing in opposite directions. For this reason, the uppermost second protrusion 97 among the plurality of second protrusions 97 is located above any first protrusion 87, that is, above any first protrusion 87 in the second inflow hole. 25 side. However, when the external equipment connected to the circular tubes 41 and 43 and another external equipment may reverse the flow of the first fluid and the second fluid, as in the second embodiment, a plurality of Of the second protrusions 97 , the lowest second protrusion 97 is positioned below any first protrusion 87 , that is, closer to the second outflow hole 26 than any first protrusion 87 . is desirable.

As described above, in the plate-type heat exchanger 1B according to Embodiment 2, the first heat transfer plate 80 includes a plurality of first heat transfer plates that block the gap 2 between the flange portion 62 of the inner fin 60 and the first plate portion 81. A convex portion 87 is provided. Further, the second heat transfer plate 90 includes a plurality of second protrusions 97 closing the gap 3 between the flange portion 72 of the inner fin 70 and the second plate portion 91 . As a result, it is possible to more effectively prevent the first fluid and the second fluid from flowing through these gaps 2 and 3 and lowering the heat exchange efficiency.

In addition, the plurality of first protrusions 87 and the plurality of second protrusions 97 do not overlap in the front-rear direction, that is, in the stacking direction of the laminate 35, but in the vertical direction, that is, the first fluid and the second fluid. is shifted in the direction of flow. By bending the first plate portion 81 and the second plate portion 91, the first convex portion 87 and the second convex portion 97 are formed. In the case of a convex shape on one side and a concave shape on the other side, the first fluid and the second fluid may flow through these concave portions, but the first convex portion 87 and the second convex portion 97 can suppress such flows of the first fluid and the second fluid, as in the first embodiment.

In the plate heat exchanger 1</b>B, one of the plurality of second protrusions 97 is positioned closer to the second inlet 25 than any of the first protrusions 87 . Also, the distance from the second protrusion 97 to the second inlet 25 is shorter than the distance from the first protrusion 87 to the first inlet 13 . When the first fluid or the second fluid flows through the gaps 2 and 3, the second fluid may have a greater influence on the heat exchange efficiency than the first fluid. In this case, it is possible to effectively prevent the second fluid from flowing into the gap 3 and reducing the heat exchange efficiency.

Although the plate heat exchangers 1A and 1B according to the embodiments of the present disclosure have been described above, the plate heat exchangers 1A and 1B are not limited to this.

In Embodiments 1 and 2, the plate heat exchangers 1A and 1B are such that the longitudinal direction of the first heat transfer plates 10 and 80 and the second heat transfer plates 20 and 90 is the up-down direction, and the width direction is the left-right direction. , are oriented in the direction in which they are stacked in the front-rear direction, but the orientation of the plate heat exchangers 1A and 1B is not limited to this. The orientations of the plate heat exchangers 1A and 1B of Embodiments 1 and 2 are merely for convenience of explanation. If each configuration of the plate heat exchangers 1A, 1B such as the first heat transfer plates 10, 80 and the second heat transfer plates 20, 90 has the positional relationship described above, the plate heat exchangers 1A, 1B can be arbitrarily oriented.

In Embodiments 1 and 2, the first protrusions 17 and 87 protrude to such an extent that they can be joined to the flange portion 62 of the inner fin 60 . Further, the second protrusions 27 and 97 protrude to such an extent that they can be joined to the flange portion 72 of the inner fin 70 . However, the first protrusions 17, 87 and the second protrusions 27, 97 are not limited to this. The first protrusions 17 and 87 and the second protrusions 27 and 97 extend from the first plate portions 11 and 81 and the second plate portions 21 and 91 to the first peripheral wall portions 12 and 82 and the second peripheral wall portions 22 and 92. gaps 2, 3 between flanges 62, 72 of inner fins 60, 70 arranged in flow paths formed by first plate portions 11, 81 and second plate portions 21, 91 and projecting to a certain surface side; All you have to do is block the

Here, blocking generally means not only eliminating gaps and holes, but also impeding passage and flow. Say.

Regarding the degree of closure of the gaps 2 and 3, it is sufficient that the gaps 2 and 3 are closed to such an extent that the pressure loss thereof is greater than or equal to the pressure loss of the fin main bodies 61 and 71. FIG. For example, when the gaps 2 and 3 are partially closed as a result of closing the gaps 2 and 3, the cross-sectional area of the unclosed space is the same as that of the adjacent top portions 64 of the fin body portions 61 and 71. or less than the cross-sectional area of the fin space 5 between the bottom portions 65 adjacent to each other.

Further, in the first and second embodiments, the first convex portions 17, 87 and the second convex portions 27, 97 are adjacent to the fin body portions 61, 71 of the inner fins 60, 70 in the left-right direction. A small space remains open. However, as described above, the gaps 2 and 3 between the flange portions 62 and 72 and the first plate portions 11 and 81 and the second plate portions 21 and 91 have a pressure greater than the pressure loss of the fin body portions 61 and 71. It suffices if it is blocked to the extent that it causes a loss. Therefore, the first protrusions 17, 87 and the second protrusions 27, 97 are adjacent to the fin body portions 61, 71 of the inner fins 60, 70 from the left and right directions, so that the minute space is completely closed. may be

The first protrusions 17, 87 and the second protrusions 27, 97 may also be adjacent to the first peripheral wall portions 12, 82 and the second peripheral wall portions 22, 92. , 82 and the second peripheral wall portions 22 and 92 with a small space therebetween. In that case, the gaps 2 and 3 are not completely closed, but the gaps 2 and 3 may be closed to such an extent that the pressure loss is equal to or greater than the pressure loss of the fin main bodies 61 and 71 .

In Embodiments 1 and 2, the first projections 17, 87 and the second projections 27, 97 are fan-shaped by dividing a rectangle into two semicircles in cross-sectional view of the channel. However, the first protrusions 17, 87 and the second protrusions 27, 97 are not limited to this. The first convex portions 17, 87 and the second convex portions 27, 97 are formed from the first plate portions 11, 81, the second plate portions 21, 91 to the first peripheral wall portions 12, 82, the second plate portions 21, 91, as described above. Collar portions 62, 72 of inner fins 60, 70 protruding toward the surface where the peripheral wall portions 22, 92 are present and arranged in the flow path formed by the first plate portions 11, 81 and the second plate portions 21, 91 As long as the gaps 2 and 3 are closed, the shape is arbitrary as long as this condition is satisfied. For example, the first protrusions 17, 87 and the second protrusions 27, 97 may be hemispherical, pyramidal, prismatic, cylindrical, or the like.

In Embodiments 1 and 2, the first protrusions 17, 87 and the second protrusions 27, 97 are formed by bending the plates forming the first heat transfer plates 10, 80 and the second heat transfer plates 20, 90. so that the side opposite to the protruding side is recessed. However, the first protrusions 17, 87 and the second protrusions 27, 97 are not limited to this. Since the first protrusions 17, 87 and the second protrusions 27, 97 only need to satisfy the above conditions, the sides opposite to the protruding sides of the first protrusions 17, 87 and the second protrusions 27, 97 are recessed. It may be flat instead of flat. For example, the first protrusions 17, 87 and the second protrusions 27, 97 are not formed by pressing the first heat transfer plates 10, 80 and the second heat transfer plates 20, 90. It may be formed by bonding a separately manufactured convex to the first heat transfer plate 10, 80 and the second heat transfer plate 20, 90, so that the side opposite to the protruding side is flat. .

In Embodiment 2, the first protrusions 87 and the second protrusions 97 are arranged at a constant pitch P2. However, the first convex portion 87 and the second convex portion 97 are not limited to this. The first convex portion 87 and the second convex portion 97 may not have the constant pitch P2. When the first protrusion 87 and the second protrusion 97 are formed by bending the plate and the side opposite to the protrusion side is recessed, the first protrusion 87 and the second protrusion 97 overlap in the stacking direction. All you have to do is

In Embodiments 1 and 2, the fin body portions 61 and 71 are corrugated. However, the fin body portions 61 and 71 are not limited to this. The fin body portions 61 and 71 are arranged in the flow paths of the first heat transfer plates 10 and 80 and the second heat transfer plates 20 and 90, respectively, and have a plurality of fins. shape is not limited. For example, the fin bodies 61 and 71 may be flat fins having a plurality of flat fins, or may be corrugated fins having a plurality of plate fins bent in a corrugated shape. Further, the fin body portions 61 and 71 may be pin-type fins having a plurality of pin-shaped fins.

In Embodiments 1 and 2, the first and second fluids flow in opposite directions in the plate heat exchangers 1A and 1B, but the first and second fluids flow in the same direction. may flow in a co-current fashion.

1A, 1B plate heat exchanger, 2, 3 gap, 5 fin space, 10 first heat transfer plate, 11 first plate portion, 12 first peripheral wall portion, 13 first inflow hole, 14 first outflow hole, 15 Second passage hole 16 Second passage hole 17 First protrusion 20 Second heat transfer plate 21 Second plate portion 22 Second peripheral wall portion 23, 24 First passage hole 25 Second inflow hole , 26 second outflow hole, 27 second protrusion, 30,35 laminate, 40 side plate, 41-44 circular tube, 50 side plate, 60 inner fin, 61 fin body, 62 flange, 63 band, 64 Top portion 65 Bottom portion 70 Inner fin 71 Fin body portion 72 Collar portion 80 First heat transfer plate 81 First plate portion 82 First peripheral wall portion 87 First protrusion 90 Second heat transfer plate , 91 second plate portion 92 second peripheral wall portion 97 second convex portion A1, A2 amplitude BW width FL1, FL2 length H1, H2 height L1, L2 wavelength P arrow P1 fin pitch , P2 pitch, Q arrow, S1, S2 space, T1, T2 thickness, W1, W2 width.

Claims (9)

A plate portion having inflow/outflow holes through which fluid flows in and out is formed at both ends in the first direction, and a peripheral wall portion provided on one surface side of the plate portion and surrounding an outer periphery of the plate portion, By stacking the plate portions facing each other with one surface facing the same direction, it is possible to flow the fluid in the first direction in the space surrounded by the peripheral wall portion between the plate portions. a plurality of heat transfer plates forming flow channels;
A fin body portion having a plurality of fins disposed inside the flow path of each of the heat transfer plates; and a second direction of the fin body portion orthogonal to the first direction and parallel to the plate portion. a plurality of inner fins provided at an end portion and having a collar portion located away from the plate portion forming the flow path in which the fin body portion is arranged;
with
The heat transfer plate has a convex portion which protrudes from the plate portion of itself to the one surface side and closes the gap between the flange portion of the inner fin arranged in the flow path of itself. ,
Plate heat exchanger. The convex portion has a gap between the fin body portion of the inner fin and the fin body portion of the plurality of fins that is equal to or less than the pitch of the fins in the second direction,
A plate heat exchanger according to claim 1. The convex portion is adjacent to the fin body portion of the inner fin in the second direction,
A plate heat exchanger according to claim 1. The flange portion of the inner fin extends in the first direction,
A plurality of the protrusions are provided on the heat transfer plate and are spaced apart from each other in the first direction,
A plate heat exchanger according to any one of claims 1 to 3. The convex portions are formed at regular intervals in the first direction,
A plate heat exchanger according to claim 4. The length of the protrusions in the first direction is less than or equal to the length of the gaps provided between the protrusions in the first direction.
A plate heat exchanger according to claim 5. The plurality of heat transfer plates are
at least one first heat transfer plate, wherein the fluid is a first fluid, and the protrusions are a plurality of first protrusions spaced apart from each other in the first direction;
At least one second heat transfer plate alternately stacked with the first heat transfer plates, wherein the fluid is the second fluid, and the protrusions are a plurality of second protrusions spaced apart from each other in the first direction. a heat plate;
Of the plurality of second protrusions, the second protrusion that is closest to the first direction side is the first heat transfer plate that is adjacent to the second heat transfer plate having the second protrusion. located on the first direction side of the first protrusion that is closest to the first direction side among the plurality of first protrusions that have the plurality of first protrusions,
the first fluid is water,
wherein the second fluid is a refrigerant;
A plate heat exchanger according to any one of claims 4 to 6. The convex portion and the convex portion provided on the heat transfer plate adjacent to the heat transfer plate having the convex portion in the stacking direction are displaced in the first direction,
A plate heat exchanger according to any one of claims 1 to 7. The convex portion protrudes toward the one surface by bending a portion of the plate portion.
A plate heat exchanger according to any one of claims 1 to 8.

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