JPWO2018216166A1 - Plate heat exchanger - Google Patents

Abstract

The heat transfer plate of the plate heat exchanger is such that the first surface (Sa1) of the heat transfer section faces the first surface of the heat transfer section of the heat transfer plates arranged next to each other, and A certain second surface is opposed to the second surface of the heat transfer portion in the heat transfer plate arranged next to each other on the other side, a first flow path is formed between the first surfaces (Sa1), and a second flow path is provided between the second surfaces. To form. The first surface (Sa1) of the heat transfer section includes a plurality of first ridges (230), a barrier ridge (231) lower than the first ridge and extending in a direction intersecting the first ridge, And a plurality of first concave stripes (220) formed between the adjacent first convex stripes, and the second surface of the heat transfer portion has a plurality of second concave stripes in front and back relation with the first convex stripe. Including. The first ridges (230) of the adjacent heat transfer plates are located between the first ridges (230) of the partner heat transfer plate, and the barrier ridges (231) of the adjacent heat transfer plates are Cross abut with the first ridge (230) of the heat transfer plate.

Description

  The present invention relates to a plate heat exchanger used as a condenser or an evaporator.

  Conventionally, the plate heat exchanger includes a plurality of heat transfer plates. Each of the plurality of heat transfer plates includes a heat transfer section. The heat transfer section has a first surface and a second surface in the first direction. Specifically, the heat transfer portion is a concave surface that faces the first surface on which the convex stripes and concave stripes are formed, and faces the opposite side to the first surface, and is in a front-back relationship with the convex stripes on the first surface. And a concave surface of the first surface and a second surface having a convex stripe in a front-back relationship.

  On each of the first surface and the second surface of the heat transfer section, the ridge intersects with a center line (hereinafter, referred to as a vertical center line) of the heat transfer section that extends in the second direction orthogonal to the first direction. The ridge is formed over the entire length of the heat transfer section in the third direction orthogonal to each of the first direction and the second direction.

  The plurality of heat transfer plates are stacked in the first direction. That is, each of the plurality of heat transfer plates causes the first surface of the heat transfer portion thereof to face the first surface of the heat transfer portion of the heat transfer plate arranged next to each other on one side in the first direction. In addition, each of the plurality of heat transfer plates causes the second surface of the heat transfer section of itself to face the second surface of the heat transfer section of the heat transfer plate that is arranged next to the other side of the first direction.

  In this state, the ridges of the heat transfer portions of the adjacent heat transfer plates intersect each other, and the recessed ridges of the heat transfer portion form a space between the heat transfer portions of the adjacent heat transfer plates. That is, the first flow path that allows the first fluid to flow in the second direction is formed between the first surfaces of the heat transfer portions of the adjacent heat transfer plates. Moreover, the second flow path that allows the second fluid to flow in the second direction is formed between the second surfaces of the heat transfer portions of the adjacent heat transfer plates. Along with this, the plate heat exchanger exchanges heat between the first fluid in the first flow path and the second fluid in the second flow path via the heat transfer section that partitions the first flow path and the second flow path. (For example, see Patent Document 1).

  By the way, this type of plate heat exchanger is a condenser for condensing the second fluid in the second flow path by heat exchange between the first fluid in the first flow path and the second fluid in the second flow path. May be used as. In addition, this type of plate heat exchanger is an evaporator that evaporates the second fluid in the second flow path by heat exchange between the first fluid in the first flow path and the second fluid in the second flow path. Sometimes used as.

  However, in the conventional plate heat exchanger, when used as a condenser or an evaporator, there is a limit in improving heat transfer performance in relation to the characteristics of the second fluid to be condensed or evaporated. .

  More specifically, the ridges of the heat transfer section are formed across the entire length of the heat transfer section in the third direction across the longitudinal center line of the heat transfer section. Therefore, the ridges of the heat transfer section increase the flow resistance of each of the first flow path and the second flow path.

  In general, a fluid that does not cause a phase change (a fluid that becomes a single-phase flow) is used as the first fluid. Therefore, the increase in the flow resistance of the first flow path increases the chances of thermally affecting the heat transfer section. Therefore, the increase in the flow resistance of the first flow path becomes a factor that enhances the heat transfer performance.

  On the other hand, as the second fluid, a fluid that causes a phase change such as Freon (a fluid that becomes a two-phase flow containing a liquid and a gas) is used. Along with this, a liquid film of the second fluid is formed on the second surface of the heat transfer section that defines the second flow path. Therefore, in order to improve the heat transfer performance, it is necessary to increase the flow velocity of the second fluid and disturb the flow of the liquid film formed on the second surface of the heat transfer section.

  However, since the ridges of the heat transfer section are formed over the entire length of the heat transfer section in the third direction across the longitudinal center line of the heat transfer section, the ridges of the heat transfer section are Obstruct the flow of the second fluid in the passage. That is, since the ridge on the second surface of the heat transfer section is formed so as to cross (intersect) the flow of the second fluid in the second flow path, Increase the flow resistance of the two fluids.

  Therefore, in the conventional plate heat exchanger, there is a limit in increasing the flow velocity of the second fluid in the second flow passage, and the liquid film of the second fluid formed on the second surface of the heat transfer section is limited. The flow cannot be sufficiently disturbed.

  Therefore, in the conventional plate heat exchanger, there is a limit in improving the heat transfer performance of the second fluid flowing through the second flow path to the heat transfer section.

Japanese Patent Laid-Open No. 2001-99588

  Therefore, it is an object of the present invention to provide a plate heat exchanger capable of improving the heat transfer performance of the second fluid that changes in phase by heat exchange with the first fluid, to the heat transfer section.

  The plate heat exchanger of the present invention has a first surface on which ridges and recesses are formed, and a concave surface which faces the opposite side to the first surface and which is in a front-back relationship with the ridges on the first surface. A heat transfer plate including a heat transfer portion having a strip and a recessed surface of the first surface and a second surface having a convex strip in a front-back relationship, each heat transfer portion being superposed in the first direction. A plurality of heat transfer plates, and each of the plurality of heat transfer plates has a first surface of its own heat transfer section and a first surface of the heat transfer section in the heat transfer plate arranged next to each other on one side in the first direction. While facing each other, the second surface of its own heat transfer portion is opposed to the second surface of the heat transfer portion of the heat transfer plate arranged next to the other side in the first direction, and the first fluid is orthogonal to the first direction. The first flow path that circulates in two directions is formed between the first surfaces of the heat transfer portions of the adjacent heat transfer plates, and the second fluid flows in the second direction. The second flow path to be circulated is formed between the second surfaces of the heat transfer parts of the adjacent heat transfer plates, and each heat transfer part of the adjacent heat transfer plates is a ridge formed on the first surface. A plurality of first ridges arranged at intervals in a direction intersecting the one direction and the second direction, each of the plurality of first ridges extending in the second direction or a composite direction including the second direction as a component. As a concave stripe formed on the first surface, including a plurality of stripes, a plurality of first concave stripes formed between adjacent first convex stripes in a direction intersecting the first direction and the second direction, and As the recess formed on the two surfaces, a plurality of second recesses having a front and back relationship with the first protrusion are included, and the heat transfer portion in at least one of the heat transfer plates adjacent to each other is , A barrier lower than the first ridge formed on the first surface as the ridge formed on the first surface The first ridge of each of the adjacent heat transfer plates, which includes at least one barrier ridge extending in a direction intersecting with the first ridge, and the first ridge of each of the adjacent heat transfer plates is a first ridge of the other heat transfer plate. Located between them, the barrier ribs of at least one of the heat transfer plates and the first ribs of the other heat transfer plate intersect with each other.

  As one aspect of the present invention, at least one of the heat transfer plates adjacent to each other has a plurality of barriers arranged at intervals in the second direction as ridges formed on the first surface. It is preferable to include a convex ridge.

  As another aspect of the present invention, each heat transfer portion of the adjacent heat transfer plates includes a plurality of second ridges in front and back relation with the first ridge, as the ridges formed on the second surface. The second convex ridges of the adjacent heat transfer plates may overlap with the second convex ridges of the partner heat transfer plate and may be in contact with the claw portions of the second convex ridges of the partner heat transfer plate.

  The barrier rib has at least one bent rib, and the bent rib is a pair of inclined ribs each having a base end and a tip opposite to the base end. It may include a pair of inclined ridges that are inclined in opposite directions to each other with respect to a center line extending in two directions or an imaginary line parallel to the center line, and their tips are connected to each other.

  Each heat transfer portion of the adjacent heat transfer plates includes a barrier ridge having a bent ridge, and the bent ridges of the barrier ridges of the adjacent heat transfer plates are formed by bending in opposite directions to each other. Is preferably provided.

FIG. 1 is a perspective view of a plate heat exchanger according to the first embodiment of the present invention. FIG. 2 is an exploded perspective view of the plate heat exchanger according to the first embodiment, and is an exploded perspective view including the flow paths of the first fluid and the second fluid. FIG. 3 is a view of the heat transfer plate (first heat transfer plate) of the plate heat exchanger according to the first embodiment as viewed from the first surface side. FIG. 4 is a view of the heat transfer plate (first heat transfer plate) of the plate heat exchanger according to the first embodiment as viewed from the second surface side. FIG. 5 is a view of the heat transfer plate (second heat transfer plate) of the plate heat exchanger according to the first embodiment as viewed from the first surface side. FIG. 6 is a view of the heat transfer plate (second heat transfer plate) of the plate heat exchanger according to the first embodiment as viewed from the second surface side. FIG. 7 is a schematic diagram showing a flow path of the first fluid in the first flow path and a flow path of the second fluid in the second flow path of the plate heat exchanger according to the first embodiment. FIG. 8 is a schematic partial cross-sectional view of the plate heat exchanger according to the first embodiment as seen from the second direction. FIG. 9 is a cross-sectional view taken along the line IX-IX of FIG. 8, and is a cross-sectional view additionally showing the flow of fluid in the first flow path and the second flow path. FIG. 10 is a cross-sectional view taken along line XX of FIG. 8 and is a cross-sectional view additionally showing the flow of fluid in the first flow path and the second flow path. FIG. 11: is a figure which shows the flow of the 1st fluid in the 1st flow path in the plate-type heat exchanger which concerns on 1st embodiment. FIG. 12: is a figure which shows the flow of the 2nd fluid in the 2nd flow path in the plate-type heat exchanger which concerns on 1st embodiment. FIG. 13 is an exploded perspective view of the plate heat exchanger according to the second embodiment of the present invention, and is an exploded perspective view including the flow paths of the first fluid and the second fluid. FIG. 14: is the figure which looked at the heat transfer plate (1st heat transfer plate) of the plate heat exchanger which concerns on 2nd embodiment from the 1st surface side. FIG. 15 is a view of the heat transfer plate (first heat transfer plate) of the plate heat exchanger according to the second embodiment as viewed from the second surface side. FIG. 16: is the figure which looked at the heat transfer plate (2nd heat transfer plate) of the plate heat exchanger which concerns on 2nd embodiment from the 1st surface side. FIG. 17 is a view of the heat transfer plate (second heat transfer plate) of the plate heat exchanger according to the second embodiment as viewed from the second surface side. FIG. 18 is a schematic diagram showing a flow path of the first fluid in the first flow path and a flow path of the second fluid in the second flow path of the plate heat exchanger according to the second embodiment. FIG. 19 is a schematic partial cross-sectional view of the plate heat exchanger according to the second embodiment as seen from the second direction. 20 is a cross-sectional view taken along the line XX-XX of FIG. 19, and is a cross-sectional view additionally showing the flow of fluid in the first flow path and the second flow path. FIG. 21 is a cross-sectional view taken along the line XXI-XXI of FIG. 19, showing the flow of the fluid in the first channel and the second channel. 22 is a cross-sectional view taken along the line XXII-XXII in FIG. 19 and is a cross-sectional view additionally showing the flow of the fluid in the first flow passage and the second flow passage. FIG. 23: is a figure which shows the flow of the 1st fluid in the 1st flow path in the plate-type heat exchanger which concerns on 2nd embodiment. FIG. 24: is a figure which shows the flow of the 2nd fluid in the 2nd flow path in the plate heat exchanger which concerns on 2nd embodiment. FIG. 25 is a schematic partial cross-sectional view of the plate heat exchanger according to another embodiment of the present invention as seen from the second direction. FIG. 26 is a schematic partial cross-sectional view of the plate heat exchanger according to another embodiment of the present invention as seen from the second direction. FIG. 27 is a schematic partial cross-sectional view of the plate heat exchanger according to still another embodiment of the present invention as seen from the second direction. FIG. 28 is a schematic diagram showing a flow path of a first fluid in a first flow path and a flow path of a second fluid in a second flow path of a plate heat exchanger according to still another embodiment of the present invention. Is. FIG. 29 is a schematic diagram showing a flow path of a first fluid in a first flow path and a flow path of a second fluid in a second flow path of a plate heat exchanger according to still another embodiment of the present invention. Is.

  Hereinafter, a plate heat exchanger according to a first embodiment of the present invention will be described with reference to the accompanying drawings.

  As shown in FIGS. 1 and 2, a plate heat exchanger (hereinafter, simply referred to as a heat exchanger in the present embodiment) 1 according to the first embodiment includes three or more heat transfer plates 2 and 3.

  The three or more heat transfer plates 2 and 3 are stacked in the first direction. In the present embodiment, the three or more heat transfer plates 2 and 3 include two types of heat transfer plates. The two types of heat transfer plates 2 and 3 are alternately arranged in the first direction.

  Along with this, as shown in FIG. 2, the heat exchanger 1 has a first flow path Ra through which the first fluid A flows and a second flow path B through which the second fluid B flows, with the heat transfer plates 2 and 3 as boundaries. The flow paths Rb are formed alternately in the first direction.

  Here, the two types of heat transfer plates 2 and 3 will be specifically described. The two types of heat transfer plates 2 and 3 have common points and different points. First, the common points between the two types of heat transfer plates 2 and 3 will be described.

  As shown in FIGS. 3 to 6, the heat transfer plates 2 and 3 have a heat transfer section 20 having first surfaces Sa1 and Sb1 and second surfaces Sa2 and Sb2 opposite to the first surfaces Sa1 and Sb1. , 30 and annular fitting portions 21 and 31 extending from the entire outer peripheral edges of the heat transfer portions 20 and 30 in a direction that intersects the heat transfer portions 20 and 30 in a plane.

  The heat transfer parts 20 and 30 have a thickness in the first direction. Along with this, the first surfaces Sa1, Sb1 and the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30 are arranged in the first direction. The outer shapes (contours) of the heat transfer parts 20 and 30 are a pair of long sides extending in a second direction orthogonal to the first direction and a pair of short sides arranged at intervals in the second direction. Is defined by a pair of short sides extending in a third direction orthogonal to the first direction and the second direction and connecting a pair of long sides. That is, the outer shape of the heat transfer parts 20 and 30 when viewed from the first direction is a rectangular shape that is long in the second direction.

  The heat transfer parts 20 and 30 have one end in the second direction and the other end opposite to the one end. The heat transfer parts 20, 30 have at least two openings 200, 201, 202, 203, 300, 301, 302, 303 at one end and the other end in the second direction, respectively. In the present embodiment, the heat transfer parts 20, 30 have two openings 200, 203, 300, 303 at one end in the second direction and two openings 201, 202, 301 at the other end in the second direction. , 302.

  The two openings 200, 203, 300, 303 at one end of the heat transfer parts 20, 30 in the second direction are arranged in the third direction. Further, the two openings 201, 202, 301, 302 at the other ends of the heat transfer parts 20, 30 in the second direction are arranged in the third direction.

  The periphery of one opening 200, 300 at one end of the heat transfer portion 20, 30 in the second direction and the periphery of one opening 201, 301 at the other end are recessed on the first surface Sa1, Sb1 side. . Along with this, the periphery of one opening 200, 300 at one end in the second direction and the periphery of one opening 201, 301 at the other end of the heat transfer parts 20, 30 are on the second surface Sa2, Sb2 side. Bulges out.

  Amount of swelling to the second surface Sa2, Sb2 side around one opening 200, 300 at one end in the second direction and around one opening 201, 301 at the other end of the heat transfer section 20, 30. Are the openings 200, 201, 300, 301 of the heat transfer parts 20, 30 of the heat transfer plates 2, 3 arranged next to each other in the first direction (one opening 200, 300 at one end and one opening 201 at the other end). , 301) so that it can be contacted with the surroundings.

  On the other hand, the periphery of the other opening 203, 303 at one end of the heat transfer portion 20, 30 in the second direction and the periphery of the other opening 202, 302 at the other end are on the second surface Sa2, Sb2 side. Is dented at. Accordingly, the periphery of the other opening 203, 303 at one end of the heat transfer portion 20, 30 in the second direction and the periphery of the other opening 202, 302 at the other end are on the first surface Sa1, Sb1 side. Bulges out.

  Amount of swelling toward the first surface Sa1, Sb1 side around the other opening 203, 303 at one end in the second direction and the other opening 202, 302 at the other end of the heat transfer section 20, 30. Are the openings 202, 203, 302, 303 of the heat transfer portions 20, 30 of the heat transfer plates 2, 3 arranged next to each other in the first direction (the other opening 202, 302 at one end and the other opening at the other end). 203, 303) is set so as to be able to come into contact with the periphery (bulged portion). 3 to 6, the openings 200, 201, 202, 203, 300, 301, 302, 303 of the openings 200, 201, 202, 203, 300, 301, 302, 303 are formed in order to clarify the concave-convex relationship on each of the first surface Sa1, Sb1 and the second surface Sa2, Sb2. Dots are attached to the region that is recessed in the periphery and the bottom portions of the recesses 22 and 32 described below.

  In the present embodiment, in relation to the aspect in which the heat transfer plates 2 and 3 are overlapped, one opening 200, 300 at one end in the second direction and one opening at the other end in the heat transfer section 20, 30. 201 and 301 are in diagonal positions. Further, the other openings 203, 303 at one end of the heat transfer parts 20, 30 in the second direction and the other openings 202, 302 at the other end are at diagonal positions.

  Grooves 22, 32 and ridges 23, 33 are formed on the first surfaces Sa1, Sb1 and the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30, respectively. In each of the first surfaces Sa1 and Sb1 and the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30, there are a plurality (a large number) of the recessed ridges 22 and 32 and the protruding ridges 23 and 33, respectively.

  More specifically, the heat transfer plates 2 and 3 are formed by press forming a metal plate. Along with this, the concave stripes 22 and 32 formed on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 and the convex stripes 23 and 33 formed on the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30. And have a two-sided relationship. The convex stripes 23 and 33 formed on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 and the concave stripes 22 and 32 formed on the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30 are , There is a front and back relationship. That is, the recessed strips 22, 32 formed on the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 due to the deformation of the metal plate associated with the press forming are formed on the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30. It is formed at a position corresponding to the formed ridges 23 and 33. In addition, the ridges 23 and 33 formed on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 due to the deformation of the metal plate associated with the press forming are transferred to the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30. It is formed at a position corresponding to the formed concave lines 22 and 32.

  As shown in FIGS. 3 and 5, the heat transfer portions 20 and 30 are a plurality of first recessed strips 220 and 320 that extend in the second direction as the recessed strips 22 and 32 formed on the first surfaces Sa1 and Sb1. And includes a plurality of first recessed strips 220, 320 arranged at intervals in the third direction. Moreover, the heat transfer parts 20 and 30 are a plurality of first ridges 23 and 33 formed on the first surfaces Sa1 and Sb1 and extending in the second direction between the first ridges 220 and 320 adjacent in the third direction. Includes one ridge 230, 330. That is, on the first surfaces Sa1 and Sb1 of the heat transfer parts 20 and 30, the first concave stripes 220 and 320 and the first convex stripes 230 and 330 are alternately arranged in the third direction.

  Further, the heat transfer portions 20 and 30 are used as barrier ribs 23 and 33 formed on the first surfaces Sa1 and Sb1 for barriers lower than the first ribs 230 and 330 formed on the first surfaces Sa1 and Sb1. The ridges 231 and 331 include at least one barrier ridge 231 and 331 extending in a direction intersecting with the plurality of first ridges 230 and 330.

  The width in the third direction of each of the plurality of first concave stripes 220 and 320 and the width of each of the plurality of first convex stripes 230 and 330 in the third direction are the same or substantially the same. The inner surface defining the first concave stripes 220, 320 and the outer surface defining the first convex stripes 230, 330 are continuous. As a result, the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 are formed in a wavy shape that undulates in the first direction.

  On the premise of this, on the first surfaces Sa1 and Sb1 of the heat transfer parts 20 and 30, a specific first concave stripe 220, 320 of the plurality of first concave stripes 220, 320 and a plurality of first convex stripes 230 are provided. , 330 of the first first ridges 230, 330 adjacent to the first first ridges 230, 330 adjacent to the first first ridges 220, 320 of the first ridges 230, 330 of ing.

  That is, the specific first concave stripes 220, 320 or the specific first convex stripes 230, 330 are the intervals between the adjacent first convex stripes 230, 330 with one first concave stripe 220, 320 interposed therebetween, or The first concave stripes 230, 330 are sandwiched between the first concave stripes 220, 320, and the first concave stripes 220, 320 are arranged so as to be displaced from the vertical center line CL in the third direction by a distance ¼ of the distance between the adjacent first concave stripes 220, 320.

  In the present embodiment, the plurality of barrier ribs 231 and 331 are provided on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30, respectively. The plurality of barrier ribs 231 and 331 are arranged at intervals in the second direction. Each of the plurality of barrier ribs 231 and 331 is lower than the first ribs 230 and 330, as described above. Specifically, protrusion from a virtual surface (a virtual surface that spreads in the second direction and the third direction) that passes through the claws of a plurality of second protrusions 233 and 333 described below that are formed on the second surfaces Sa2 and Sb2. The amount of the barrier ribs 231 and 331 is smaller than that of the first ribs 230 and 330. Along with this, the claw portions of the barrier ribs 231 and 331 are located closer to the second surface in the first direction than the claw portions of the first ribs 230 and 330. That is, the claws of the barrier ribs 231, 331 are located between the claws of the first ribs 230, 330 and the bottoms of the first recesses 220, 320.

  Although details will be described later, in the present embodiment, the first ridges 230 of one of the heat transfer plates 2 and 3 adjacent to each other in the state where the plurality of heat transfer plates 2 and 3 are stacked. , 330 (first concave lines 220, 320), the first convex lines 230, 330 of the other heat transfer plates 2, 3 of the adjacent heat transfer plates 2, 3 are located.

  Accordingly, the distance (distance) between the claws of the first ridges 230 and 330 and the claws of the barrier ridges 231 and 331 in the first direction is one of the adjacent heat transfer plates 2 and 3. The distance between the first ridges 230 and 330 of the heat transfer plates 2 and 3 and the first ridges 220 and 320 of the other heat transfer plates 2 and 3 is such that the flow of the first fluid A can be secured. , Set.

  More specifically, in the present embodiment, in each of the heat transfer plates 2 and 3, the plurality of first recesses 220 and 320 are set to have the same width, and the plurality of first protrusions 230 and 330 have the same width. Is set to. In addition, in each heat transfer plate 2 and 3, the first concave stripes 220 and 320 and the first convex stripes 230 and 330 are set to have substantially the same width.

  Along with this, the first ridges 230 and 330 of the heat transfer plates 2 and 3 of one of the heat transfer plates 2 and 3 that are adjacent to each other cause the heat transfer plate 2 of the other of the heat transfer plates 2 and 3 that is adjacent to , 3 of the first concave stripes 220, 320 too close to each other, the gap between the both sides of the first convex stripes 230, 330 in the width direction and the both sides of the first concave stripes 220, 320 in the width direction disappears, or The gap between the claws of the first ridges 230 and 330 and the bottoms of the first ridges 220 and 320 is extremely narrow.

  Therefore, in the present embodiment, the distance between both sides in the width direction of the first ridges 230, 330 and the both sides in the width direction of the first ridges 220, 320 is the distance at which the fluidity of the first fluid A can be ensured. As described above, the distance (distance) between the claws of the first ridges 230 and 330 and the claws of the barrier ridges 231 and 331 in the first direction is set.

  In the present embodiment, the barrier ribs 231 and 331 intersect the plurality of first ribs 230 and 330 and the first recesses 220 and 320. In the present embodiment, the barrier ribs 231 and 331 are formed over the entire length of the heat transfer portions 20 and 30 in the third direction.

  In this embodiment, the barrier ribs 231 and 331 have at least one bent rib portion 232 or 332. The bent ridges 232, 332 are a pair of inclined ridges 232a, 232b, 332a, 332b each having a base end and a tip opposite to the base end, and are inclined with respect to the longitudinal centerline CL. It includes a pair of inclined ridges 232a, 232b, 332a, 332b which are inclined in opposite directions and whose tips are connected to each other. In the present embodiment, the barrier ribs 231 and 331 have one bent rib 232 and 332.

  In the present embodiment, the base ends of the pair of inclined ridges 232a, 232b, 332a, 332b forming the bent ridges 232, 332 are located on the edges of the heat transfer parts 20, 30 in the third direction. positioned.

  On the other hand, the tip ends of the pair of inclined ridges 232a, 232b, 332a, 332b are located at the centers (on the vertical center line CL) of the heat transfer parts 20, 30 in the third direction. As a result, the tip ends of the pair of inclined ridges 232a, 232b, 332a, 332b are connected in a mutually matched state.

  With such an aspect, in this embodiment, the barrier ribs 231 and 331 themselves form the bent ribs 232 and 332. The pair of inclined ridges 232a, 232b, 332a, 332b are arranged symmetrically with respect to an imaginary line extending in the second direction. That is, the inclination directions of the pair of inclined ridges 232a, 232b, 332a, 332b are opposite to each other. However, the inclination angles of the pair of inclined ridges 232a, 232b, 332a, 332b with respect to the vertical center line CL extending in the second direction are the same.

  In this way, the barrier ribs 231 and 331 are provided over the entire width of the heat transfer portions 20 and 30 in the third direction. Along with this, the first concave lines 220 and 320 and the first convex lines 230 and 330 on the first surfaces Sa1 and Sb1 of the heat transfer parts 20 and 30 are divided at a plurality of positions in the second direction. Along with this, at least one ends of the divided first concave lines 220 and 320 and the first convex lines 230 and 330 are connected to the barrier convex lines 231 and 331.

  In the present embodiment, the divided first concave lines 220 and 320 are aligned in the second direction. Along with this, the divided first ridges 230 and 330 are also aligned in the second direction.

  As shown in FIGS. 4 and 6, the heat transfer portions 20 and 30 are a plurality of second recessed strips 221 and 321 each extending in the second direction as the recessed strips 22 and 32 formed on the second surfaces Sa2 and Sb2. In addition, the plurality of second recessed strips 221 and 321 arranged at intervals in the third direction are included. In addition, the heat transfer portions 20 and 30 are formed as the convex stripes 23 and 33 formed on the second surfaces Sa2 and Sb2 and extend in the second direction between the second concave stripes 221 and 321 that are adjacent to each other in the third direction. A plurality of second ridges 233 and 333. That is, on the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30, the second concave stripes 221, 321 and the second convex stripes 233, 333 are alternately arranged in the third direction.

  Furthermore, the heat transfer parts 20 and 30 are recessed stripes 22 and 32 formed on the second surfaces Sa2 and Sb2, and are recessed stripes formed on the back side of the barrier ribs 231 and 331 on the first surfaces Sa1 and Sb1. It includes 222 and 322 (hereinafter referred to as the back side concave streaks).

  The second concave stripes 221 and 321 are concave stripes 22 and 32 formed on the back side of the first convex stripes 230 and 330 on the first surfaces Sa1 and Sb1. Along with this, the second recessed strips 221 and 321 extend in the second direction. The second ridges 233, 333 are the ridges 23, 33 formed on the back side of the first ridges 220, 320 on the first surfaces Sa1, Sb1. Along with this, the second ridges 233 and 333 extend in the second direction.

  The inner surface that defines the second concave stripes 221 and 321 and the outer surface that defines the second convex stripes 233 and 333 are continuous. As a result, the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30 are formed in a wavy shape undulating in the first direction.

  The back side concave lines 222 and 322 are formed in the same form as that of the barrier convex lines 231 and 331 except that the concave-convex relationship is reversed. Therefore, the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30 have a pair of slanted recesses 22 and 32 formed on the back sides of the pair of slanted projections 232a, 232b, 332a, 332b. Bent concave line parts 223 and 323 including the line parts 223a, 223b, 323a and 323b are formed.

  In the present embodiment, the bent ridges 232 and 332 (the pair of inclined ridges 232a, 232b, 332a, 332b) configure the barrier ridges 231 and 331. Therefore, the bent groove portions 223 and 323 configure the entire back side groove portions 222 and 322 formed on the back side of the barrier ribs 231 and 331.

  Along with this, the second recessed strips 221 and 321 and the second projected strips 233 and 333 are divided by the back side recessed strips 222 and 322. As a result, the divided second ridges 233 and 333 are connected to the rear concave ridges 222 and 322. That is, the divided second recessed strips 221 and 321 are open toward the inside of the back side recessed strips 222 and 322.

  The common points between the two types of heat transfer plates 2 and 3 are as described above. Next, the difference between the two types of heat transfer plates 2 and 3 will be described.

  As shown in FIG. 3 and FIG. 5, a first ridge 230 on the first surface Sa1 of one of the two types of heat transfer plates 2 and 3 (hereinafter referred to as the first heat transfer plate) 2 , The first ridge 330 on the first surface Sb1 of the other heat transfer plate (hereinafter referred to as the second heat transfer plate) 3 of the two kinds of heat transfer plates 2 and 3 is displaced in the third direction. Are placed. That is, the first surface Sa1 of the heat transfer portion 20 of the first heat transfer plate 2 and the first surface Sb1 of the heat transfer portion 30 of the second heat transfer plate 3 are opposed to each other in the first heat transfer plate 2 The one convex line 230 corresponds to the first concave line 320 of the second heat transfer plate 3, and the first convex line 330 of the second heat transfer plate 3 corresponds to the first concave line 220 of the first heat transfer plate 2. As described above, the arrangement of the respective first concave stripes 220 and 320 and the first convex stripes 230 and 330 is set.

  In this embodiment, the barrier ribs 231 of the first heat transfer plate 2 and the barrier ribs 331 of the second heat transfer plate 3 are reversed from each other with respect to an imaginary line extending in the third direction. It is provided in. That is, the inclined direction of the inclined convex portions 232a, 232b of the barrier ribs 231 of the first heat transfer plate 2 and the inclined direction of the inclined convex portions 332a, 332b of the barrier ribs 331 of the second heat transfer plate 3 Is the exact opposite.

  Then, in the first heat transfer plate 2, as shown in FIG. 3, the fitting portion 21 extends to the first surface Sa1 side of the heat transfer portion 20. On the other hand, in the second heat transfer plate 3, as shown in FIG. 6, the fitting portion 31 extends to the second surface Sb2 side of the heat transfer portion 30.

  Each of the plurality of heat transfer plates 2 and 3 (first heat transfer plate 2 and second heat transfer plate 3) is as described above. Each of the plurality of heat transfer plates 2 and 3 (first heat transfer plate 2 and second heat transfer plate 3) is superposed in the first direction as shown in FIG. 2. In this embodiment, the first heat transfer plate 2 and the second heat transfer plate 3 are alternately stacked in the first direction. At this time, each of the plurality of heat transfer plates 2 and 3 transfers heat in the heat transfer plates 2 and 3 in which the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 of the heat transfer plates 2 and 3 are arranged next to each other on one side in the first direction. The first surfaces Sa1 and Sb1 of the portions 20 and 30 are opposed to each other. In addition, each of the plurality of heat transfer plates 2 and 3 has the second surface Sa2 and Sb2 of its own heat transfer parts 20 and 30 arranged next to each other on the other side in the first direction. The second surfaces Sa2 and Sb2 of 20, 30 are opposed to each other.

  As a result, as shown in FIGS. 2 and 7, the first flow passage Ra that allows the first fluid A to flow in the second direction and the second flow passage Rb that allows the second fluid B to flow in the second direction have the heat transfer plate 2 , 3 are alternately formed with the heat transfer parts 20 and 30 as boundaries. That is, the first flow path Ra that circulates the first fluid A is formed between the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3, and the second fluid B circulates. The second flow path Rb is formed between the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3.

  Further, in this state, as shown in FIG. 2, the openings 200, 201, 202, 203, 300, 301, 302, 303 at corresponding positions of the heat transfer parts 20, 30 are continuous in the first direction. In addition, portions around the openings 200, 201, 202, 203, 300, 301, 302, 303 facing each other and bulging toward the other side are in contact with each other. Thereby, the first inflow passage Pa1 for supplying the first fluid A to the first flow passage Ra, the first outflow passage Pa2 for flowing out the first fluid A from the first flow passage Ra, and the second fluid B for the second flow passage Rb. And a second outflow passage Pb2 for flowing out the second fluid B from the second flow passage Rb.

  More specifically, when stacking a plurality of heat transfer plates 2 and 3, one first heat transfer plate 2 and one second heat transfer plate 3 are made to face each other with their back side concaves 222 and 322 facing each other. It is set in a stacked state and overlapped. When superposing a plurality of sets, every other set is rotated by 180 degrees around an imaginary line extending in the first direction and is superposed. In this state, the fitting portions 21 and 31 of one of the heat transfer plates 2 and 3 (first heat transfer plate 2 or second heat transfer plate 3) of the heat transfer plates 2 and 3 that are adjacent to each other in the first direction are Of the heat transfer plates 2 and 3 adjacent to each other in the first direction are externally fitted to the fitting portions 21 and 31 of the other heat transfer plate 2 and 3 (the first heat transfer plate 2 or the second heat transfer plate 3). It

  As a result, as shown in FIGS. 8 to 10, on the first surfaces Sa1 and Sb1 sides of the adjacent heat transfer plates 2 and 3, the first protrusions 230 of the first heat transfer plate 2 (heat transfer section 20) are The first recessed ridge 220 of the first heat transfer plate 2 (heat transfer part 20) faces the first recessed ridge 320 of the second heat transfer plate (heat transfer part 30), and the second heat transfer plate (heat transfer part 20). 30) facing the first ridge 330.

  In the first heat transfer plate 2, the barrier ribs 231 are lower than the first ribs 230, and in the second heat transfer plate 3, the barrier ribs 331 are lower than the first ribs 330. The barrier ridges 231 of the heat plate 2 cross-abut with the first ridges 330 of the second heat transfer plate 3, and the barrier ridges 331 of the second heat transfer plate 3 intersect the first heat transfer plate 2. It intersects with the first ridge 230.

  In the present embodiment, the barrier ridges 231 of the first heat transfer plate 2 and the barrier ridges 331 of the second heat transfer plate 3 are provided in an inverted manner with respect to an imaginary line extending in the third direction. Therefore, in the state of being arranged as described above, as shown in FIG. 11, the barrier ribs 231 of the first heat transfer plate 2 and the barrier ribs 331 of the second heat transfer plate 3 are They are arranged in an intersecting manner when viewed from the direction.

  On the other hand, on the second surface Sa2, Sb2 side of the adjacent heat transfer plates 2, 3, as shown in FIG. 8 to FIG. 10, the second ridge 233 of the first heat transfer plate 2 (heat transfer part 20) is The second recess 221 of the first heat transfer plate 2 (heat transfer part 20) faces the second protrusion 333 of the second heat transfer plate (heat transfer part 30). It faces the second groove 321 of the portion 30). That is, in the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 of the first heat transfer plate 2 and the second heat transfer plate 3, respectively, a specific first concave portion of the plurality of first concave grooves 220 and 320 is formed. First ridges 230, 330 adjacent to the first ridges 220, 320 and a particular first ridge 230, 330 of the plurality of first ridges 230, 330. Since the boundary with is located on the vertical center line CL, as described above, by rotating the first heat transfer plate 2 and the second heat transfer plate 3 by 180 °, the adjacent heat transfer plates 2, 3 The second ridges 233, 333 of the above are opposed to each other, and the ridges of the two are brought into contact with each other. Further, the back side recessed lines 222 and 322 of the heat transfer plates 2 and 3 which are adjacent to each other when viewed from the first direction are in a state of facing each other (matching state) (see FIG. 12).

  Thereby, as shown in FIG. 2, the first surfaces of the heat transfer portions 20 and 30 of the heat transfer plates 2 and 3 in which the first flow paths Ra for circulating the first fluid A in the second direction orthogonal to the first direction are adjacent to each other. It is formed between Sa1 and Sb1. Further, the second flow path Rb for circulating the second fluid B in the second direction is formed between the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3.

  Then, as described above, the plurality of heat transfer plates 2 and 3 are overlapped in the first direction, so that the openings 200, 201, 202, 203, 300, 301, at the corresponding positions of the heat transfer parts 20 and 30 are formed. 302 and 303 are connected in the first direction. In addition, portions around the openings 200, 201, 202, 203, 300, 301, 302, 303 facing each other and bulging toward the other side are in contact with each other. Thereby, the first inflow passage Pa1 for supplying the first fluid A to the first flow passage Ra, the first outflow passage Pa2 for flowing out the first fluid A from the first flow passage Ra, and the second fluid B for the second flow passage Rb. And a second outflow passage Pb2 for flowing out the second fluid B from the second flow passage Rb.

  In the heat exchanger 1 according to this embodiment, the contacting portions of the adjacent heat transfer plates 2 and 3 are brazed to each other. As a result, the plurality of heat transfer plates 2 and 3 are integrally (mechanically) connected, and the opposing surfaces (contact portions) of the adjacent heat transfer plates 2 and 3 are sealed.

  The heat exchanger 1 according to this embodiment is as described above. The first fluid A flows into the plurality of first flow paths Ra from the first inflow passage Pa1 as shown in FIGS. 2, 7, and 11. The first fluid A flows in the second direction in each of the plurality of first flow paths Ra and flows out to the first outflow path Pa2. On the other hand, the second fluid B flows into the plurality of second flow paths Rb from the second inflow path Pb1 as shown in FIGS. 2, 7, and 12. The second fluid B flows in the second direction in each of the plurality of second flow paths Rb and flows out to the second outflow path Pb2.

  In the present embodiment, as shown in FIG. 11, the first fluid A flows in the first flow path Ra with a diagonal line connecting the diagonals of the heat transfer parts 20, 30 as the center. On the other hand, as shown in FIG. 12, the second fluid B is a diagonal line that connects the diagonals of the heat transfer portions 20 and 30 in the second flow path Rb, and is a diagonal line that is the center of the flow of the first fluid A. Circulates around a different diagonal line.

  At this time, the first fluid A flowing through the first flow channel Ra and the second fluid B flowing through the second flow channel Rb are the heat transfer plates 2 and 3 (that partition the first flow channel Ra from the second flow channel Rb). Heat is exchanged via the heat transfer parts 20, 30). Accordingly, the second fluid B is condensed or evaporated in the process of flowing in the second direction in the second flow path Rb.

  As described above, the heat exchanger 1 according to the present embodiment is opposite to the first surfaces Sa1 and Sb1 on which the convex stripes 23 and 33 and the concave stripes 22 and 32 are formed and the first surfaces Sa1 and Sb1. The ridges 23 and 32 facing the side and having a front and back relationship with the ridges 23 and 33 of the first surfaces Sa1 and Sb1 and the ridge 23 having a front and back relationship with the recesses 22 and 32 of the first surfaces Sa1 and Sb1. , 33 having the second surfaces Sa2, Sb2 formed thereon, the heat transfer plates 2, 3 including a plurality of heat transfer parts 20, 30 stacked in the first direction. Heat transfer plates 2 and 3, and each of the plurality of heat transfer plates 2 and 3 has the first surfaces Sa1 and Sb1 of its own heat transfer portions 20 and 30 arranged next to each other on one side in the first direction. When facing the first surfaces Sa1 and Sb1 of the heat transfer parts 20 and 30 in the plates 2 and 3, In addition, the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30 of their own face the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30 in the heat transfer plates 2, 3 arranged next to each other on the other side in the first direction. The first flow path Ra that allows the first fluid A to flow in the second direction orthogonal to the first direction is formed between the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3. In addition, the second flow path Rb that allows the second fluid B to flow in the second direction is formed between the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3, and the adjacent flow paths Rb and The heat transfer parts 20 and 30 of the heat plates 2 and 3 are arranged at intervals in the direction intersecting the first direction and the second direction as the ridges 23 and 33 formed on the first surfaces Sa1 and Sb1. A plurality of first ridges 230 and 330, each of which is in the second direction or A direction that intersects the first direction and the second direction as the recessed ridges 22 and 32 formed on the first surfaces Sa1 and Sb1 while including the plurality of first ridges 230 and 330 extending in the composite direction including the direction as a component. And the plurality of first concave stripes 220, 320 formed between the adjacent first convex stripes 230, 230, 330, 330, and as the concave stripes 22, 32 formed on the second surfaces Sa2, Sb2. The heat transfer part in the heat transfer plates 2 and 3 of at least one of the adjacent heat transfer plates 2 and 3 including the plurality of second recessed parts 221 and 321 that are in front and back relation with the one ridge 230 and 330. The ribs 20 and 30 are, as the ribs 23 and 33 formed on the first surfaces Sa1 and Sb1, the barrier ribs 231 and 331 lower than the first ribs 230 and 330 formed on the first surfaces Sa1 and Sb1. And the first ridge 230 , 330 including at least one barrier ridge 231 or 331 extending in a direction intersecting with the heat transfer plates 2 and 3, the first ridges 230 and 330 of the adjacent heat transfer plates 2 and 3 of the heat transfer plates 2 and 3, respectively. Located between the first ridges 230 and 330, the barrier ridges 231 and 331 of at least one of the heat transfer plates 2 and 3 and the first ridges 230 and 330 of the partner heat transfer plates 2 and 3 Are crossing each other.

  According to the heat exchanger 1 configured as described above, as shown in FIGS. 9 and 10, the barrier is provided at an intermediate position of the first flow passage Ra formed between the first surfaces Sa1 and Sb1 of the adjacent heat transfer portions 20 and 30. The projecting ridges 231 and 331 exist in a state of protruding toward the heat transfer parts 20 and 30 of the other party. Along with this, the barrier ribs 231 and 331 impede the flow of the first fluid A in the first flow channel Ra and increase the flow resistance of the first fluid A in the first flow channel Ra.

  Particularly, according to the heat exchanger 1 according to the present embodiment, the first ridges 230 and 330 of the adjacent heat transfer plates 2 and 3 are the first ridges 230 and 330 of the opposite heat transfer plates 2 and 3, respectively. The barrier ribs 231 and 331 located between the heat transfer plates 2 and 3 (barrier ribs 231 and 331 lower than the first ribs 230 and 330) and the heat transfer plates 2 and 3 of the other party. The first ridges 230 and 330 are cross-butted.

  Therefore, the interval between the first surfaces Sa1 and Sb1 of the adjacent heat transfer plates 2 and 3 becomes narrow. That is, the heat transfer plates 2 and 3 defining the first flow path Ra are brought closer to each other by the protrusion amount of the barrier ribs 231 and 331 being smaller than the protrusion amount of the first ribs 230 and 330. As a result, the flow passage width of the first flow passage Ra becomes narrower, and as a result, the flow resistance of the first fluid A in the first flow passage Ra increases.

  Therefore, the heat exchanger 1 according to the present embodiment increases the flow resistance of the first fluid A as a result of the existence of the barrier ribs 231 and 331 and the channel width of the first channel Ra, resulting in the first fluid A. The number of opportunities for heat to affect the heat transfer parts 20, 30 increases, and the heat transfer performance to the second fluid B side is improved.

  On the other hand, on the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30 of the heat transfer plates 2 and 3, a plurality of second recessed stripes 221 and 321 having a front and back relationship with the first protruding stripes 230 and 330. Is formed, and since the concave ridges having a front and back relationship with the convex ridges 231 and 331 for the barrier of the first surfaces Sa1 and Sb1 are formed, between the second surfaces Sa2 and Sb2 of the adjacent heat transfer plates 2 and 3. There is nothing that becomes a flow resistance of the second fluid B in the second flow path Rb formed in. Therefore, the flow resistance of the second fluid B in the second flow path Rb is reduced, and the flow velocity of the second fluid B can be increased.

  As a result, even if a fluid that causes a phase change (a fluid that becomes a two-phase flow containing a liquid and a gas) is adopted as the second fluid B, the flow velocity of the second fluid B causes the fluid to flow on the surfaces of the heat transfer portions 20 and 30. The flow of the liquid film of the second fluid B formed on the surface is disturbed.

  Therefore, in the heat exchanger 1 configured as described above, the heat transfer performance of the second fluid B flowing through the second flow path Rb to the heat transfer portions 20, 30 (on the side of the first fluid A) is enhanced.

  In this embodiment, as shown in FIGS. 9 to 11, at least one of the heat transfer plates 2 and 3 adjacent to each other has a ridge formed on the first surfaces Sa1 and Sb1. Since the plurality of barrier ribs 231 and 331 arranged at intervals in the second direction are included as 23 and 33, depending on the number of the plurality of barrier ribs 231 and 331 in the first channel Ra. Therefore, the flow resistance of the first fluid A can be increased.

  In addition, in the present embodiment, the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3 are the first ridges 220 and 320 as the ridges 23 and 33 formed on the second surfaces Sa2 and Sb2. The second convex ridges 233, 333 of the adjacent heat transfer plates 2, 3 include a plurality of second convex ridges 233, 333 having a front and back relationship with each other. Since it overlaps with the strips 233 and 333 and is in contact with the crests of the second convex strips 233 and 333 of the heat transfer plates 2 and 3 of the other side, the flow pressure of the first fluid A flowing in the first flow channel Ra is Even if it acts on the heat transfer parts 20 and 30, the heat transfer parts 20 and 30 are not expanded. Therefore, the space forming the second flow path Rb is secured, and the smoothness of the circulation of the second fluid B is secured.

  In the present embodiment, the barrier ridges 231 and 331 have at least one bending ridge portion 232 and 332, and each of the bending ridge portions 232 and 332 is a base end and a tip opposite to the base end. And a pair of inclined ridges 232a and 232b each having an angle of inclination with respect to a center line extending in the second direction or an imaginary line parallel to the center line and having their tips connected to each other. It includes a pair of inclined ridges 232a and 232b that are formed.

  As a result, not only the barrier ribs 231 and 331 become the flow resistance of the first fluid A, but also the bent ribs 232 and 332 of the barrier ribs 231 and 331 (the pair of inclined ribs 232a, 232a, 232b, 332a, 332b) causes the first fluid A to diffuse in the first channel Ra. Therefore, the area | region which contributes to heat transfer in the heat transfer parts 20 and 30 increases. This improves the heat transfer performance of the first fluid A in the first flow channel Ra.

  In particular, the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3 include barrier ribs 231 and 331 having bent protrusion portions 232 and 332, respectively, and the barriers of the heat transfer plates 2 and 3 that are adjacent to each other. The bent ridges 232 and 332 of the projecting ridges 231 and 331 are formed by bending diametrically opposite to each other.

  Therefore, the inclined ridge portions 232a, 232b, 332a, 332b of the bent ridge portions 232, 332 are in a state where they intersect with each other (see FIG. 11). Along with this, the flow resistance of the first fluid A in the first flow channel Ra increases, and the diffusion effect of the first fluid A also increases. This improves the heat transfer performance of the first fluid A in the first flow channel Ra.

  Next, a plate heat exchanger according to the second embodiment of the present invention will be described. In the present embodiment, configurations that are the same as or equivalent to the configurations in the first embodiment have the same names as the configurations in the first embodiment and are given the same reference numerals.

  The plate type heat exchanger according to the second embodiment (hereinafter, simply referred to as heat exchanger in the present embodiment) includes three or more heat transfer plates 2 and 3, as shown in FIG. 13.

  The three or more heat transfer plates 2 and 3 are stacked in the first direction. In the heat exchanger 1 according to this embodiment, the three or more heat transfer plates 2 and 3 include two types of heat transfer plates. The two types of heat transfer plates 2 and 3 are alternately arranged in the first direction.

  Along with this, the heat exchanger 1 has a first flow path Ra through which the first fluid A flows and a second flow path Rb through which the second fluid B flows, with the heat transfer plates 2 and 3 as a boundary. They are formed alternately in one direction.

  Here, the two types of heat transfer plates 2 and 3 will be specifically described. The two types of heat transfer plates 2 and 3 have common points and different points. First, the common points between the two types of heat transfer plates 2 and 3 will be described.

  As shown in FIGS. 14 to 17, the heat transfer plates 2 and 3 have a heat transfer portion 20 having first surfaces Sa1 and Sb1 and second surfaces Sa2 and Sb2 opposite to the first surfaces Sa1 and Sb1. , 30 and annular fitting portions 21 and 31 extending from the entire outer peripheral edges of the heat transfer portions 20 and 30 in a direction that intersects the heat transfer portions 20 and 30 in a plane.

  The heat transfer parts 20 and 30 have a thickness in the first direction. Along with this, the first surfaces Sa1, Sb1 and the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30 are arranged in the first direction. The outer shapes (contours) of the heat transfer parts 20 and 30 are a pair of long sides extending in a second direction orthogonal to the first direction and a pair of short sides arranged at intervals in the second direction. Is defined by a pair of short sides extending in a third direction orthogonal to the first direction and the second direction and connecting a pair of long sides. That is, the outer shape of the heat transfer parts 20 and 30 when viewed from the first direction is a rectangular shape that is long in the second direction.

  The heat transfer parts 20 and 30 have one end in the second direction and the other end opposite to the one end. The heat transfer parts 20, 30 have at least two openings 200, 201, 202, 203, 300, 301, 302, 303 at one end and the other end in the second direction, respectively. In the present embodiment, the heat transfer parts 20, 30 have two openings 200, 203, 300, 303 at one end in the second direction and two openings 201, 202, 301 at the other end in the second direction. , 302.

  The two openings 200, 203, 300, 303 at one end of the heat transfer parts 20, 30 in the second direction are arranged in the third direction. Further, the two openings 201, 202, 301, 302 at the other ends of the heat transfer parts 20, 30 in the second direction are arranged in the third direction.

  The periphery of one opening 200, 300 at one end of the heat transfer portion 20, 30 in the second direction and the periphery of one opening 201, 301 at the other end are recessed on the first surface Sa1, Sb1 side. . Along with this, the periphery of one opening 200, 300 at one end in the second direction and the periphery of one opening 201, 301 at the other end of the heat transfer parts 20, 30 are on the second surface Sa2, Sb2 side. Bulges out.

  Amount of swelling to the second surface Sa2, Sb2 side around one opening 200, 300 at one end in the second direction and around one opening 201, 301 at the other end of the heat transfer section 20, 30. Are the openings 200, 201, 300, 301 of the heat transfer parts 20, 30 of the heat transfer plates 2, 3 arranged next to each other in the first direction (one opening 200, 300 at one end and one opening 201 at the other end). , 301) so that it can be contacted with the surroundings.

  On the other hand, the periphery of the other opening 203, 303 at one end of the heat transfer portion 20, 30 in the second direction and the periphery of the other opening 202, 302 at the other end are on the second surface Sa2, Sb2 side. Is dented at. Accordingly, the periphery of the other opening 203, 303 at one end of the heat transfer portion 20, 30 in the second direction and the periphery of the other opening 202, 302 at the other end are on the first surface Sa1, Sb1 side. Bulges out.

  Amount of swelling toward the first surface Sa1, Sb1 side around the other opening 203, 303 at one end in the second direction and the other opening 202, 302 at the other end of the heat transfer section 20, 30. Are the openings 202, 203, 302, 303 of the heat transfer portions 20, 30 of the heat transfer plates 2, 3 arranged next to each other in the first direction (the other opening 202, 302 at one end and the other opening at the other end). 203, 303) is set so as to be able to come into contact with the periphery (bulged portion). 14 to 17, the openings 200, 201, 202, 203, 300, 301, 302, 303 of the openings 200, 201, 202, 203, 300, 301, 302, 303 are formed in order to clarify the concave-convex relationship on each of the first surface Sa1, Sb1 and the second surface Sa2, Sb2. Dots are attached to the region that is recessed in the periphery and the bottom portions of the recesses 22 and 32 described below.

  In the present embodiment, in relation to the aspect in which the heat transfer plates 2 and 3 are overlapped, one opening 200, 300 at one end in the second direction and one opening at the other end in the heat transfer section 20, 30. 201 and 301 are in diagonal positions. Further, the other openings 203, 303 at one end of the heat transfer parts 20, 30 in the second direction and the other openings 202, 302 at the other end are at diagonal positions.

  Grooves 22, 32 and ridges 23, 33 are formed on the first surfaces Sa1, Sb1 and the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30, respectively. In each of the first surfaces Sa1 and Sb1 and the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30, there are a plurality (a large number) of the recessed ridges 22 and 32 and the protruding ridges 23 and 33, respectively.

  More specifically, the heat transfer plates 2 and 3 are formed by press forming a metal plate. Along with this, the concave stripes 22 and 32 formed on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 and the convex stripes 23 and 33 formed on the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30. And have a two-sided relationship. The convex stripes 23 and 33 formed on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 and the concave stripes 22 and 32 formed on the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30 are , There is a front and back relationship. That is, the recessed strips 22, 32 formed on the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 due to the deformation of the metal plate associated with the press forming are formed on the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30. It is formed at a position corresponding to the formed ridges 23 and 33. In addition, the ridges 23 and 33 formed on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 due to the deformation of the metal plate associated with the press forming are transferred to the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30. It is formed at a position corresponding to the formed concave lines 22 and 32.

  As shown in FIGS. 14 and 16, the heat transfer portions 20 and 30 are a plurality of first recessed stripes 220 and 320 that extend in the second direction as the recessed stripes 22 and 32 formed on the first surfaces Sa1 and Sb1. And includes a plurality of first recessed strips 220, 320 arranged at intervals in the third direction. Moreover, the heat transfer parts 20 and 30 are a plurality of first ridges 23 and 33 formed on the first surfaces Sa1 and Sb1 and extending in the second direction between the first ridges 220 and 320 adjacent in the third direction. Includes one ridge 230, 330. That is, on the first surfaces Sa1 and Sb1 of the heat transfer parts 20 and 30, the first concave stripes 220 and 320 and the first convex stripes 230 and 330 are alternately arranged in the third direction.

  Further, the heat transfer portions 20 and 30 are used as barrier ribs 23 and 33 formed on the first surfaces Sa1 and Sb1 for barriers lower than the first ribs 230 and 330 formed on the first surfaces Sa1 and Sb1. The ridges 231 and 331 include at least one barrier ridge 231 and 331 extending in a direction intersecting with the plurality of first ridges 230 and 330.

  The width in the third direction of each of the plurality of first concave stripes 220 and 320 and the width of each of the plurality of first convex stripes 230 and 330 in the third direction are the same or substantially the same. The inner surface defining the first concave stripes 220, 320 and the outer surface defining the first convex stripes 230, 330 are continuous. As a result, the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 are formed in a wavy shape that undulates in the first direction.

  On the premise of this, on the first surfaces Sa1 and Sb1 of the heat transfer parts 20 and 30, a specific first concave stripe 220, 320 of the plurality of first concave stripes 220, 320 and a plurality of first convex stripes 230 are provided. , 330 of the first first ridges 230, 330 adjacent to the first first ridges 230, 330 adjacent to the first first ridges 220, 320 of the first ridges 230, 330 of ing.

  That is, the specific first concave stripes 220, 320 or the specific first convex stripes 230, 330 are the intervals between the adjacent first convex stripes 230, 330 with one first concave stripe 220, 320 interposed therebetween, or The first concave stripes 230, 330 are sandwiched between the first concave stripes 220, 320, and the first concave stripes 220, 320 are arranged so as to be displaced from the vertical center line CL in the third direction by a distance ¼ of the distance between the adjacent first concave stripes 220, 320.

  In the present embodiment, the plurality of barrier ribs 231 and 331 are provided on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30, respectively. The plurality of barrier ribs 231 and 331 are arranged at intervals in the second direction. Each of the plurality of barrier ribs 231 and 331 is lower than the first ribs 230 and 330, as described above. Specifically, protrusion from a virtual surface (a virtual surface that spreads in the second direction and the third direction) that passes through the claws of a plurality of second protrusions 233 and 333 described below that are formed on the second surfaces Sa2 and Sb2. The amount of the barrier ribs 231 and 331 is smaller than that of the first ribs 230 and 330. Along with this, the claw portions of the barrier ribs 231 and 331 are located closer to the second surface in the first direction than the claw portions of the first ribs 230 and 330. That is, the claws of the barrier ribs 231, 331 are located between the claws of the first ribs 230, 330 and the bottoms of the first recesses 220, 320.

  Although details will be described later, in the present embodiment, the first ridges 230 of one of the heat transfer plates 2 and 3 adjacent to each other in the state where the plurality of heat transfer plates 2 and 3 are stacked. , 330 (positions corresponding to the first recessed strips 220, 320), the first ridges 230, 330 of the other heat transfer plate 2, 3 of the adjacent heat transfer plates 2, 3 are located.

  Accordingly, the distance (distance) between the claws of the first ridges 230 and 330 and the claws of the barrier ridges 231 and 331 in the first direction is one of the adjacent heat transfer plates 2 and 3. The distance between the first ridges 230 and 330 of the heat transfer plates 2 and 3 and the first ridges 220 and 320 of the other heat transfer plates 2 and 3 is such that the flow of the first fluid A can be secured. , Set.

  More specifically, in the present embodiment, in each of the heat transfer plates 2 and 3, the plurality of first recesses 220 and 320 are set to have the same width, and the plurality of first protrusions 230 and 330 have the same width. Is set to. In addition, in each heat transfer plate 2 and 3, the first concave stripes 220 and 320 and the first convex stripes 230 and 330 are set to have substantially the same width.

  Along with this, the first ridges 230 and 330 of the heat transfer plates 2 and 3 of one of the heat transfer plates 2 and 3 that are adjacent to each other cause the heat transfer plate 2 of the other of the heat transfer plates 2 and 3 that is adjacent to , 3 of the first concave stripes 220, 320 too close to each other, the gap between the both sides of the first convex stripes 230, 330 in the width direction and the both sides of the first concave stripes 220, 320 in the width direction disappears, or The gap between the claws of the first ridges 230 and 330 and the bottoms of the first ridges 220 and 320 is extremely narrow.

  Therefore, in the present embodiment, the distance between both sides in the width direction of the first ridges 230, 330 and the both sides in the width direction of the first ridges 220, 320 is the distance at which the fluidity of the first fluid A can be ensured. As described above, the distance (distance) between the claws of the first ridges 230 and 330 and the claws of the barrier ridges 231 and 331 in the first direction is set.

  In the present embodiment, the barrier ribs 231 and 331 intersect the plurality of first ribs 230 and 330 and the first recesses 220 and 320. In this embodiment, the barrier ribs 231 and 331 extend in the third direction. The barrier ribs 231 and 331 are set to a length shorter than the total length of the heat transfer portions 20 and 30 in the third direction. That is, the number of the first ridges 230, which is smaller than the total number of the plurality of first ridges 230, 330 and the first ridges 220, 320 arranged along the entire length of the heat transfer parts 20, 30 in the third direction. The length is set to intersect with 330 and the first recessed strips 220 and 320.

  More specifically, the length of the barrier ribs 231 and 331 in the extending direction (longitudinal direction) is set to ½ or less of the total length of the heat transfer portions 20 and 30 in the third direction. In the present embodiment, the length in the extending direction (longitudinal direction) of the barrier ribs 231 and 331 is set to 1/3 or less of the total length of the heat transfer portions 20 and 30 in the third direction.

  As described above, the length of the barrier ribs 231 and 331 in the extending direction (longitudinal direction) is set to be ⅓ or less of the total length of the heat transfer portions 20 and 30 in the third direction. On the first surfaces Sa1 and Sb1 of 20, 30, a plurality of rows of barrier ridges 231 and 331 arranged at intervals in the second direction are provided at intervals in the third direction. That is, the plurality of barrier ribs 231 and 331 are arranged in a matrix on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30.

  The numbers and positions of the barrier ribs 231 and 331 in each row correspond to each other. Along with this, the corresponding barrier ridges 231 and 331 in different rows are aligned in the third direction.

  Here, the spacing between the rows of the adjacent barrier ridges 231 and 331 (the spacing between the adjacent barrier ridges 231 and 331 in the third direction) is the direction in which the single barrier ridges 231 and 331 extend (longitudinal direction). ) Is less than or equal to the length. In the present embodiment, the spacing between the rows of the adjacent barrier ridges 231 and 331 (the spacing between the adjacent barrier ridges 231 and 331 in the third direction) is the direction in which the single barrier ridges 231 and 331 extend. It is set smaller than the length (longitudinal direction).

  As described above, the length of the barrier ribs 231 and 331 in the extending direction (longitudinal direction) is 1/3 or less of the total length of the heat transfer portions 20 and 30 in the third direction (1/2 or less in the present embodiment). ), The first concave lines 220, 320 and the first convex lines 230, 330 on the first surfaces Sa1, Sb1 of the heat transfer parts 20, 30 are continuous in the second direction, And those divided at a plurality of positions in the second direction by the barrier ribs 231 and 331. At least one ends of the divided first concave lines 220 and 320 and the first convex lines 230 and 330 are connected to the barrier convex lines 231 and 331.

  In the present embodiment, the divided first concave lines 220 and 320 are aligned in the second direction. Along with this, the divided first ridges 230 and 330 are also aligned in the second direction.

  As shown in FIGS. 15 and 17, the heat transfer parts 20 and 30 are a plurality of second recessed strips 221 and 321 each extending in the second direction as the recessed strips 22 and 32 formed on the second surfaces Sa2 and Sb2. In addition, the plurality of second recessed strips 221 and 321 arranged at intervals in the third direction are included. In addition, the heat transfer portions 20 and 30 are formed as the convex stripes 23 and 33 formed on the second surfaces Sa2 and Sb2 and extend in the second direction between the second concave stripes 221 and 321 that are adjacent to each other in the third direction. A plurality of second ridges 233 and 333. That is, on the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30, the second concave stripes 221, 321 and the second convex stripes 233, 333 are alternately arranged in the third direction.

  Furthermore, the heat transfer parts 20 and 30 are recessed stripes 22 and 32 formed on the second surfaces Sa2 and Sb2, and are recessed stripes formed on the back side of the barrier ribs 231 and 331 on the first surfaces Sa1 and Sb1. It includes 222 and 322 (hereinafter referred to as the back side concave streaks).

  The second concave stripes 221 and 321 are concave stripes 22 and 32 formed on the back side of the first convex stripes 230 and 330 on the first surfaces Sa1 and Sb1. Along with this, the second recessed strips 221 and 321 extend in the second direction. The second ridges 233, 333 are the ridges 23, 33 formed on the back side of the first ridges 220, 320 on the first surfaces Sa1, Sb1. Along with this, the second ridges 233 and 333 extend in the second direction.

  The inner surface that defines the second concave stripes 221 and 321 and the outer surface that defines the second convex stripes 233 and 333 are continuous. As a result, the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30 are formed in a wavy shape undulating in the third direction.

  The back side concave lines 222 and 322 are formed in the same form as that of the barrier convex lines 231 and 331 except that the concave-convex relationship is reversed.

  In this embodiment, the back recessed lines 222 and 322 intersect the plurality of second protruding lines 233 and 333 and the second recessed lines 221 and 321. In this embodiment, the back recessed lines 222, 322 are set to a length shorter than the total length of the heat transfer parts 20, 30 in the third direction. That is, the number of the second ridges 233 is smaller than the total number of the plurality of second ridges 233 and 333 and the second ridges 221 and 321 arranged along the entire length of the heat transfer portions 20 and 30 in the third direction. The length is set to intersect with 333 and the second recesses 221 and 321.

  More specifically, the length in the extending direction (longitudinal direction) of the back recessed lines 222, 322 is set to ½ or less of the total length of the heat transfer parts 20, 30 in the third direction. In the present embodiment, the length in the extending direction (longitudinal direction) of the back side recessed lines 222, 322 is set to 1/3 or less of the total length of the heat transfer parts 20, 30 in the third direction.

  As described above, the length of the back side recessed lines 222, 322 in the extending direction (longitudinal direction) is set to ⅓ or less of the total length of the heat transfer units 20, 30 in the third direction. , 30 on the second surfaces Sa2, Sb2, a plurality of rows of back side recessed lines 222, 322 arranged at intervals in the second direction are provided at intervals in the third direction. That is, on the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30, a plurality of back recessed lines 222, 322 are arranged in a matrix.

  The numbers and positions of the back side concave lines 222 and 322 in each row correspond. Along with this, the corresponding back recessed lines 222 and 322 in different rows are aligned in the third direction.

  Here, the interval between the rows of the back side recesses 222, 322 adjacent to each other (the interval between the back side recesses 222, 322 adjacent in the third direction) is the length in the extending direction (longitudinal direction) of the single back side recesses 222, 322. Is set below. In the present embodiment, the spacing between the rows of the back side recesses 222 and 322 that are adjacent to each other (the spacing between the back side recesses 222 and 322 that are adjacent in the third direction) is the direction in which the single back side recesses 222 and 322 extend (longitudinal direction). ) Is set smaller than the length.

  In this way, the length in the extending direction (longitudinal direction) of the back side recessed lines 222, 322 is 1/3 or less of the total length of the heat transfer parts 20, 30 in the third direction (1/2 or less in the present embodiment). The second concave lines 221 and 321 and the second convex lines 233 and 333 on the second surfaces Sa2 and Sb2 of the heat transfer parts 20 and 30 are continuous in the second direction and the back side. It is divided by the concave lines 222 and 322 at a plurality of positions in the second direction. At least one ends of the divided second concave lines 221 and 321 and the second convex lines 233 and 333 are connected to the back side concave lines 222 and 322. That is, the divided second recessed strips 221 and 321 are open toward the inside of the back side recessed strips 222 and 322.

  In this embodiment, the divided second recessed strips 221 and 321 are aligned in the second direction. Along with this, the divided second ridges 233 and 333 are also aligned in the second direction.

  The common points between the two types of heat transfer plates 2 and 3 are as described above. Next, the difference between the two types of heat transfer plates 2 and 3 will be described.

  As shown in FIG. 14 and FIG. 16, the first ridge 230 on the first surface Sa1 of the heat transfer plate (hereinafter, referred to as the first heat transfer plate) 2 of one of the two types of heat transfer plates 2 and 3. , The first ridge 330 on the first surface Sb1 of the other heat transfer plate (hereinafter referred to as the second heat transfer plate) 3 of the two kinds of heat transfer plates 2 and 3 is displaced in the third direction. Are placed. That is, the first surface Sa1 of the heat transfer portion 20 of the first heat transfer plate 2 and the first surface Sb1 of the heat transfer portion 30 of the second heat transfer plate 3 are opposed to each other in the first heat transfer plate 2 The one convex line 230 corresponds to the first concave line 320 of the second heat transfer plate 3, and the first convex line 330 of the second heat transfer plate 3 corresponds to the first concave line 220 of the first heat transfer plate 2. As described above, the arrangement of the respective first concave stripes 220 and 320 and the first convex stripes 230 and 330 is set.

  Then, in the present embodiment, the first heat transfer plate 2 and the second heat transfer plate 3 have different numbers and arrangements of the barrier ribs 231 and 331 on the first surfaces Sa1 and Sb1. That is, in the first heat transfer plate 2 and the second heat transfer plate 3, the number of rows of the barrier ribs 231 and 331 on the first surfaces Sa1 and Sb1 and the arrangement of the barrier ribs 231 and 331 in each row are determined. Different.

  Specifically, in the first surface Sa1 of the first heat transfer plate 2, in the first surface Sb1 of the second heat transfer plate 3 rather than the number of rows of the barrier ribs 231 arranged in the third direction at intervals. The number of rows of the barrier ribs 331 arranged at intervals in the third direction is smaller by one row. In addition, the number of barrier ribs 231 in each row on the first surface Sb1 of the second heat transfer plate 3 is greater than the number of barrier ribs 231 in each row on the first surface Sa1 of the first heat transfer plate 2. There is one less.

  Along with this, the positions of the rows of the barrier ribs 231 on the first surface Sa1 of the first heat transfer plate 2 are the positions between the rows of the barrier ribs 331 on the first surface Sb1 of the second heat transfer plate 3. Correspondingly, the positions of the rows of the convex ridges 331 for barrier on the first surface Sb1 of the second heat transfer plate 3 correspond to the positions between the rows of the convex ridges 231 for barrier of the first surface Sa1 of the first heat transfer plate 2. is doing. In addition, the barrier ribs 231 on each row of the first surface Sa1 of the first heat transfer plate 2 are arranged between the barrier ribs 331 on each row of the first surface Sb1 of the second heat transfer plate 3 (in the second direction. Corresponding to the intermediate position between the adjacent barrier ribs 331), the barrier ribs 331 in each row of the first surface Sb1 of the second heat transfer plate 3 correspond to the first surface Sa1 of the first heat transfer plate 2. It corresponds to between the barrier ribs 231 in a row (the intermediate position between the barrier ribs 231 adjacent in the second direction).

  Then, in the first heat transfer plate 2, as shown in FIG. 14, the fitting portion 21 extends to the first surface Sa1 side of the heat transfer portion 20. On the other hand, in the second heat transfer plate 3, as shown in FIG. 17, the fitting part 31 extends to the second surface Sb2 side of the heat transfer part 30.

  Each of the plurality of heat transfer plates 2 and 3 (first heat transfer plate 2 and second heat transfer plate 3) is as described above. Each of the plurality of heat transfer plates 2 and 3 (first heat transfer plate 2 and second heat transfer plate 3) is superposed in the first direction as shown in FIG. 13. In this embodiment, the first heat transfer plate 2 and the second heat transfer plate 3 are alternately stacked in the first direction. At this time, each of the plurality of heat transfer plates 2 and 3 transfers heat in the heat transfer plates 2 and 3 in which the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 of the heat transfer plates 2 and 3 are arranged next to each other on one side in the first direction. The first surfaces Sa1 and Sb1 of the portions 20 and 30 are opposed to each other. In addition, each of the plurality of heat transfer plates 2 and 3 has the second surface Sa2 and Sb2 of its own heat transfer parts 20 and 30 arranged next to each other on the other side in the first direction. The second surfaces Sa2 and Sb2 of 20, 30 are opposed to each other.

  As a result, as shown in FIGS. 13 and 18, the heat transfer plate 2 includes the first flow passage Ra that allows the first fluid A to flow in the second direction and the second flow passage Rb that allows the second fluid B to flow in the second direction. , 3 are alternately formed with the heat transfer parts 20 and 30 as boundaries. That is, the first flow path Ra that circulates the first fluid A is formed between the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3, and the second fluid B circulates. The second flow path Rb is formed between the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3.

  Further, in this state, as shown in FIG. 13, the openings 200, 201, 202, 203, 300, 301, 302, 303 at corresponding positions of the heat transfer parts 20, 30 are continuous in the first direction. In addition, portions around the openings 200, 201, 202, 203, 300, 301, 302, 303 facing each other and bulging toward the other side are in contact with each other. Thereby, the first inflow passage Pa1 for supplying the first fluid A to the first flow passage Ra, the first outflow passage Pa2 for flowing out the first fluid A from the first flow passage Ra, and the second fluid B for the second flow passage Rb. And a second outflow passage Pb2 for flowing out the second fluid B from the second flow passage Rb.

  More specifically, when stacking the plurality of heat transfer plates 2 and 3, one first heat transfer plate 2 and one second heat transfer plate 3 are stacked to form a set. When superposing a plurality of sets, every other set is rotated by 180 degrees around an imaginary line extending in the first direction and is superposed. In this state, the fitting portions 21 and 31 of one of the heat transfer plates 2 and 3 (first heat transfer plate 2 or second heat transfer plate 3) of the heat transfer plates 2 and 3 that are adjacent to each other in the first direction are Of the heat transfer plates 2 and 3 adjacent to each other in the first direction are externally fitted to the fitting portions 21 and 31 of the other heat transfer plate 2 and 3 (the first heat transfer plate 2 or the second heat transfer plate 3). It

  Thereby, as shown in FIGS. 19 to 22, the first protrusions 230 of the first heat transfer plate 2 (heat transfer section 20) on the first surfaces Sa1 and Sb1 sides of the adjacent heat transfer plates 2 and 3 are The first recessed ridge 220 of the first heat transfer plate 2 (heat transfer part 20) faces the first recessed ridge 320 of the second heat transfer plate (heat transfer part 30), and the second heat transfer plate (heat transfer part 20). 30) facing the first ridge 330.

  In the first heat transfer plate 2, the barrier ribs 231 are lower than the first ribs 230, and in the second heat transfer plate 3, the barrier ribs 331 are lower than the first ribs 330. The barrier ridges 231 of the heat plate 2 cross-abut with the first ridges 330 of the second heat transfer plate 3, and the barrier ridges 331 of the second heat transfer plate 3 intersect the first heat transfer plate 2. It intersects with the first ridge 230.

  On the other hand, on the second surface Sa2, Sb2 side of the adjacent heat transfer plates 2 and 3, the second ridge 233 of the first heat transfer plate 2 (heat transfer section 20) has the second heat transfer plate (heat transfer plate). The second recessed portion 221 of the first heat transfer plate 2 (heat transfer portion 20) faces the second protruding portion 333 of the portion 30) and the second recessed portion 321 of the second heat transfer plate (heat transfer portion 30). To face. That is, in the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 of the first heat transfer plate 2 and the second heat transfer plate 3, respectively, a specific first concave portion of the plurality of first concave grooves 220 and 320 is formed. First ridges 230, 330 adjacent to the first ridges 220, 320 and a particular first ridge 230, 330 of the plurality of first ridges 230, 330. Since the boundary with is located on the vertical center line CL, as described above, by rotating the first heat transfer plate 2 and the second heat transfer plate 3 by 180 °, the adjacent heat transfer plates 2, 3 The second ridges 233, 333 of the above are opposed to each other, and the ridges of the two are brought into contact with each other.

  As a result, as shown in FIG. 13, the first surfaces of the heat transfer portions 20 and 30 of the heat transfer plates 2 and 3 adjacent to each other in the first flow passage Ra that allows the first fluid A to flow in the second direction orthogonal to the first direction. It is formed between Sa1 and Sb1. Further, the second flow path Rb for circulating the second fluid B in the second direction is formed between the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3.

  Then, as described above, the plurality of heat transfer plates 2 and 3 are overlapped in the first direction, so that the openings 200, 201, 202, 203, 300, 301, at the corresponding positions of the heat transfer parts 20 and 30 are formed. 302 and 303 are connected in the first direction. In addition, portions around the openings 200, 201, 202, 203, 300, 301, 302, 303 facing each other and bulging toward the other side are in contact with each other. Thereby, the first inflow passage Pa1 for supplying the first fluid A to the first flow passage Ra, the first outflow passage Pa2 for flowing out the first fluid A from the first flow passage Ra, and the second fluid B for the second flow passage Rb. And a second outflow passage Pb2 for flowing out the second fluid B from the second flow passage Rb.

  In the heat exchanger 1 according to this embodiment, the contacting portions of the adjacent heat transfer plates 2 and 3 are brazed to each other. As a result, the plurality of heat transfer plates 2 and 3 are integrally (mechanically) connected, and the opposing surfaces (contact portions) of the adjacent heat transfer plates 2 and 3 are sealed.

  The heat exchanger 1 according to this embodiment is as described above. The first fluid A flows into the plurality of first flow paths Ra from the first inflow path Pa1 as shown in FIGS. 13, 18, and 23. The first fluid A flows in the second direction in each of the plurality of first flow paths Ra and flows out to the first outflow path Pa2. On the other hand, the second fluid B flows into the plurality of second flow passages Rb from the second inflow passage Pb1 as shown in FIGS. 13, 18, and 24. The second fluid B flows in the second direction in each of the plurality of second flow paths Rb and flows out to the second outflow path Pb2.

  In the present embodiment, as shown in FIG. 23, the first fluid A circulates in the first flow passage Ra with a diagonal line connecting the diagonals of the heat transfer portions 20, 30 as the center. On the other hand, as shown in FIG. 24, the second fluid B is a diagonal line that connects the diagonals of the heat transfer portions 20 and 30 in the second flow path Rb, and is a diagonal line that is the center of the flow of the first fluid A. Circulates around a different diagonal line.

  At this time, the first fluid A flowing through the first flow channel Ra and the second fluid B flowing through the second flow channel Rb are the heat transfer plates 2 and 3 (that partition the first flow channel Ra from the second flow channel Rb). Heat is exchanged via the heat transfer parts 20, 30). Accordingly, the second fluid B is condensed or evaporated in the process of flowing in the second direction in the second flow path Rb.

  As described above, the heat exchanger 1 according to the present embodiment is opposite to the first surfaces Sa1 and Sb1 on which the convex stripes 23 and 33 and the concave stripes 22 and 32 are formed and the first surfaces Sa1 and Sb1. The ridges 23 and 32 facing the side and having a front and back relationship with the ridges 23 and 33 of the first surfaces Sa1 and Sb1 and the ridge 23 having a front and back relationship with the recesses 22 and 32 of the first surfaces Sa1 and Sb1. , 33 having the second surfaces Sa2, Sb2 formed thereon, the heat transfer plates 2, 3 including a plurality of heat transfer parts 20, 30 stacked in the first direction. Heat transfer plates 2 and 3, and each of the plurality of heat transfer plates 2 and 3 has the first surfaces Sa1 and Sb1 of its own heat transfer portions 20 and 30 arranged next to each other on one side in the first direction. When facing the first surfaces Sa1 and Sb1 of the heat transfer parts 20 and 30 in the plates 2 and 3, In addition, the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30 of their own face the second surfaces Sa2, Sb2 of the heat transfer parts 20, 30 in the heat transfer plates 2, 3 arranged next to each other on the other side in the first direction. The first flow path Ra that allows the first fluid A to flow in the second direction orthogonal to the first direction is formed between the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3. In addition, the second flow path Rb that allows the second fluid B to flow in the second direction is formed between the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3, and the adjacent flow paths Rb and The heat transfer parts 20 and 30 of the heat plates 2 and 3 are arranged at intervals in the direction intersecting the first direction and the second direction as the ridges 23 and 33 formed on the first surfaces Sa1 and Sb1. A plurality of first ridges 230 and 330, each of which is in the second direction or A direction that intersects the first direction and the second direction as the recessed ridges 22 and 32 formed on the first surfaces Sa1 and Sb1 while including the plurality of first ridges 230 and 330 extending in the composite direction including the direction as a component. And the plurality of first concave stripes 220, 320 formed between the adjacent first convex stripes 230, 230, 330, 330, and as the concave stripes 22, 32 formed on the second surfaces Sa2, Sb2. The heat transfer part in the heat transfer plates 2 and 3 of at least one of the adjacent heat transfer plates 2 and 3 including the plurality of second recessed parts 221 and 321 that are in front and back relation with the one ridge 230 and 330. The ribs 20 and 30 are, as the ribs 23 and 33 formed on the first surfaces Sa1 and Sb1, the barrier ribs 231 and 331 lower than the first ribs 230 and 330 formed on the first surfaces Sa1 and Sb1. And the first ridge 230 , 330 including at least one barrier ridge 231 or 331 extending in a direction intersecting with the heat transfer plates 2 and 3, the first ridges 230 and 330 of the adjacent heat transfer plates 2 and 3 of the heat transfer plates 2 and 3, respectively. Located between the first ridges 230 and 330, the barrier ridges 231 and 331 of at least one of the heat transfer plates 2 and 3 and the first ridges 230 and 330 of the partner heat transfer plates 2 and 3 Are crossing each other.

  According to the heat exchanger 1 configured as described above, as shown in FIGS. 20 to 22, the barrier is provided at an intermediate position of the first flow path Ra formed between the first surfaces Sa1 and Sb1 of the adjacent heat transfer portions 20 and 30. The projecting ridges 231 and 331 exist in a state of protruding toward the heat transfer parts 20 and 30 of the other party. Along with this, the barrier ribs 231 and 331 impede the flow of the first fluid A in the first flow channel Ra and increase the flow resistance of the first fluid A in the first flow channel Ra.

  Particularly, according to the heat exchanger 1 according to the present embodiment, the first ridges 230 and 330 of the adjacent heat transfer plates 2 and 3 are the first ridges 230 and 330 of the opposite heat transfer plates 2 and 3, respectively. The barrier ribs 231 and 331 located between the heat transfer plates 2 and 3 (barrier ribs 231 and 331 lower than the first ribs 230 and 330) and the heat transfer plates 2 and 3 of the other party. The first ridges 230 and 330 are cross-butted.

  Therefore, the interval between the first surfaces Sa1 and Sb1 of the adjacent heat transfer plates 2 and 3 becomes narrow. That is, the heat transfer plates 2 and 3 defining the first flow path Ra are brought closer to each other by the protrusion amount of the barrier ribs 231 and 331 being smaller than the protrusion amount of the first ribs 230 and 330. As a result, the flow passage width of the first flow passage Ra becomes narrower, and as a result, the flow resistance of the first fluid A in the first flow passage Ra increases.

  Therefore, the heat exchanger 1 according to the present embodiment increases the flow resistance of the first fluid A as a result of the existence of the barrier ribs 231 and 331 and the channel width of the first channel Ra, resulting in the first fluid A. The number of opportunities for heat to affect the heat transfer parts 20, 30 increases, and the heat transfer performance to the second fluid B side is improved.

  On the other hand, on the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30 of the heat transfer plates 2 and 3, a plurality of second recessed stripes 221 and 321 having a front and back relationship with the first protruding stripes 230 and 330. Is formed, and since the concave ridges having a front and back relationship with the convex ridges 231 and 331 for the barrier of the first surfaces Sa1 and Sb1 are formed, between the second surfaces Sa2 and Sb2 of the adjacent heat transfer plates 2 and 3. There is nothing that becomes a flow resistance of the second fluid B in the second flow path Rb formed in. Therefore, the flow resistance of the second fluid B in the second flow path Rb is reduced, and the flow velocity of the second fluid B can be increased.

  As a result, even if a fluid that causes a phase change (a fluid that becomes a two-phase flow containing a liquid and a gas) is adopted as the second fluid B, the flow velocity of the second fluid B causes the fluid to flow on the surfaces of the heat transfer portions 20 and 30. The flow of the liquid film of the second fluid B formed on the surface is disturbed.

  Therefore, in the heat exchanger 1 configured as described above, the heat transfer performance of the second fluid B flowing through the second flow path Rb to the heat transfer portions 20, 30 (on the side of the first fluid A) is enhanced.

  In this embodiment, as shown in FIG. 20 to FIG. 23, at least one of the heat transfer plates 2 and 3 adjacent to each other has at least one heat transfer plate formed on the first surfaces Sa1 and Sb1. Since the plurality of barrier ribs 231 and 331 arranged at intervals in the second direction are included as 23 and 33, depending on the number of the plurality of barrier ribs 231 and 331 in the first channel Ra. Therefore, the flow resistance of the first fluid A can be increased.

  In addition, in the present embodiment, the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3 are the first ridges 220 and 320 as the ridges 23 and 33 formed on the second surfaces Sa2 and Sb2. The second convex ridges 233, 333 of the adjacent heat transfer plates 2, 3 include a plurality of second convex ridges 233, 333 having a front and back relationship with each other. Since it overlaps with the strips 233 and 333 and is in contact with the crests of the second convex strips 233 and 333 of the heat transfer plates 2 and 3 of the other side, the flow pressure of the first fluid A flowing in the first flow channel Ra is Even if it acts on the heat transfer parts 20 and 30, the heat transfer parts 20 and 30 are not expanded. Therefore, the space forming the second flow path Rb is secured, and the smoothness of the circulation of the second fluid B is secured.

  In the present embodiment, on the first surfaces Sa1 and Sb1 of the heat transfer parts 20 and 30, a plurality of barrier ribs 231 and 331 extending in the third direction are arranged at intervals in the second direction, and a plurality of barrier ribs are formed. Since the ridges 231 and 331 are shorter than the total length of the heat transfer parts 20 and 30 in the third direction, the first fluid A causes the barrier ridges 231 and 331 to become resistance in the first flow path Ra. Try to avoid distribution. As a result, the first fluid A diffuses in the first flow channel Ra. Therefore, the area | region which contributes to heat transfer in the heat transfer parts 20 and 30 increases. This improves the heat transfer performance of the first fluid A in the first flow channel Ra.

  In particular, barrier ribs 231 and 331 are provided on the first surfaces Sa1 and Sb1 of the adjacent heat transfer plates 2 and 3, respectively, and the barrier ribs 231 and 331 of the adjacent heat transfer plates 2 and 3 are the first Since the first flow path Ra is disposed at the position shifted in the two directions, the first flow path Ra is not closed by the barrier ribs 231 and 331, and the diffusibility of the first fluid A in the first flow path Ra is enhanced.

  Further, a plurality of barrier ribs 231 and 331 are arranged in a matrix on each of the first surfaces Sa1 and Sb1 of the adjacent heat transfer plates 2 and 3, and the barrier ribs 231 of the adjacent heat transfer plates 2 and 3 are arranged. , 331 are arranged at positions displaced from each other in the second direction and the third direction, the first flow path Ra is not closed by the barrier ribs 231 and 331, and the first fluid in the first flow path Ra is prevented. The diffusivity of A is further enhanced.

  The present invention is not limited to any of the above-mentioned embodiments, and it goes without saying that appropriate changes can be made without departing from the scope of the present invention.

  In each of the above-described embodiments, the adjacent heat transfer plates 2 and 3 (the first heat transfer plate 2 and the second heat transfer plate 3) are barrier ridges 231 as ridges on the first surfaces Sa1 and Sb1. , 331, but is not limited to this. For example, only one of the heat transfer plates 2 and 3 adjacent to each other (the first heat transfer plate 2 and the second heat transfer plate 3) is convex on the first surfaces Sa1 and Sb1. The ribs may include barrier ribs 231 and 331.

  In each of the above-described embodiments, the joints of the second ridges 233 and 333 of the adjacent heat transfer plates 2 and 3 (the first heat transfer plate 2 and the second heat transfer plate 3) are contacted or connected to each other. Not limited to. For example, the claw portions of the second ridges 233 and 333 of the adjacent heat transfer plates 2 and 3 (the first heat transfer plate 2 and the second heat transfer plate 3) are separated from each other in the first direction or the second direction. Good. However, in order to obtain rigidity that can counter the rise in the flow pressure in the first flow path Ra and the like, as in the above embodiment, the adjacent heat transfer plates 2 and 3 (the first heat transfer plate 2 and the second heat transfer plate 2) are provided. It is preferable that the ridges of the second ridges 233 and 333 of the plate 3) contact or be connected to each other.

  In each of the above-described embodiments, the first concave stripes 220 and 320, the first convex stripes 230 and 330, the second concave stripes 221 and 321, and the second convex stripes 233 and 333 are formed to extend straight in the second direction. However, it is not limited to this. For example, assuming that the second recessed lines 221 and 321 are continuous with the back side recessed lines 222 and 322, a combined direction including the second direction as a component (direction inclined with respect to an imaginary line extending in the second direction). ) May be extended to. However, in order to increase the flow velocity of the second fluid B, the inclination component (angle) with respect to the virtual line extending in the second direction may be smaller than the inclination component (angle) with respect to the virtual line extending in the third direction. It is a condition.

  In each of the above embodiments, two or more barrier ribs 231 and 331 are provided at intervals in the second direction, but the invention is not limited to this. For example, one barrier ridge 231, 331 may be provided for one heat transfer part 20, 30. Moreover, in the said 2nd embodiment, with respect to the 1st surface Sa1 and Sb1 of the heat transfer parts 20 and 30, the row | line | column of the some convex ribs 231 and 331 for barriers which space | intervaled in the 2nd direction was set to the 3rd direction. Two or more rows are provided at intervals, but the invention is not limited to this. For example, a row of a plurality of barrier ridges 231 and 331 may be provided on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 at intervals in the second direction. Furthermore, in the second embodiment, the plurality of barrier ribs 231 and 331 spaced in the second direction are aligned in the second direction with respect to the first surfaces Sa1 and Sb1 of the heat transfer units 20 and 30. , But is not limited to this. For example, the plurality of barrier ribs 231 and 331 arranged at intervals in the second direction may be arranged so as to be displaced in the third direction.

  In each of the above embodiments, the plurality of barrier ribs 231 and 331 formed on the first surfaces Sa1 and Sb1 of the heat transfer parts 20 and 30 have the same shape, but the invention is not limited thereto. For example, a plurality of barrier ribs 231 and 331 having different shapes may be formed on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30.

  In each of the above-described embodiments, the width dimensions (dimensions in the direction orthogonal to the longitudinal direction) of the first concave stripes 220, 320 and the first convex stripes 230, 330 are set to be the same, but the present invention is not limited to this. For example, as shown in FIGS. 25 to 27, the width dimensions of the first concave stripes 220 and 320 may be set larger than the width dimensions of the first convex stripes 230 and 330. Specifically, as shown in FIG. 25, the radius of curvature of the first recessed ridges 220, 320 is set to the first radius, assuming that the first recessed ridges 220, 320 and the first ridges 230, 330 are formed in an arc cross section. It may be set to be larger than the radius of curvature of the one ridge 230, 330. Further, as shown in FIGS. 26 and 27, the bottoms of the first recessed strips 220 and 320 are formed flat so that the width dimension of the first recessed strips 220 and 320 is smaller than the width dimension of the first protruding strips 230 and 330. It may be set large. In this case, as shown in FIG. 26, the first ridges 230 and 330 may have an arcuate cross section, or, as shown in FIG. 27, the ridges of the first ridges 230 and 330 may have a flat shape. By doing so, the first ridges 230, 330 of the heat transfer plates 2, 3 of the other party cross-butt against the barrier ridges 231, 331 lower than the first ridges 230, 330, Even when the first ridges 230, 330 approach or enter the first ridges 220, 320, there is an extreme gap between the first ridges 220, 320 and the first ridges 230, 330. The flowability of the first fluid A is ensured without forming a narrowed portion.

  In each of the above embodiments, the first flow path Ra directly connects the first inflow path Pa1 and the first outflow path Pa2, and the second flow path Rb directly connects the second inflow path Pb1 and the second outflow path Pb2. However, it is not limited to this. For example, as shown in FIGS. 28 and 29, at least two second flow paths Rb are communicated with each other by a connection flow path PJ extending in the first direction at a position different from the second inflow path Pb1 and the second outflow path Pb2. The second flow path Rb located in the uppermost stream of the flow path of the second fluid B including the flow path PJ is connected to the second inflow path Pb1, and the most downstream of the flow path of the second fluid B including the connection flow path PJ. The second flow path Rb located at may be connected to the second outflow path Pb2.

  More specifically, the branch reference space Ds1 is formed between the heat transfer plates 2 and 3 adjacent to each other at an intermediate position in the stacking direction (first direction) of the heat transfer plates 2 and 3. On the premise of this, the second flow path Rb on the one side of the branch reference space Ds1 in the first direction and the branch reference space Ds1 are connected via the connection flow path PJ, and in the first direction from the branch reference space Ds1. Alternatively, the second flow path Rb on the other side and the branch reference space Ds1 may be connected via the connection flow path PJ. With this configuration, the distribution path of the second fluid B is at least one first system S1 that is continuous from the branch reference space Ds1 on one side in the first direction, and on the other side in the first direction from the branch reference space Ds1. It is branched into at least one continuous second system S2.

  Moreover, when the distribution path of the second fluid B includes the first system S1 and the second system S2, at least one second system located at an intermediate position in the first direction in each of the first system S1 and the second system S2. The branch reference space (between the heat transfer plates 2 and 3 that defines the second flow path Rb that is the flow path Rb and is directly or indirectly connected to the upstream branch reference space Ds1 via the connection flow path PJ ( The downstream reference space (Ds2) may be formed. In this case, the second flow path Rb on one side of the branch reference space Ds2 in the first direction and the downstream branch reference space Ds2 are connected via the connection flow path PJ, and the branch reference space Ds2 in the first direction. The second flow path Rb on the other side of the branch flow path and the branch reference space Ds2 on the downstream side are connected via the connection flow path PJ. As a result, the distribution path of the second fluid B in each of the first system S1 and the second system S2 further branches into at least two systems S1a, S1b, S2a, S2b, and the most of the systems S1a, S1b, S2a, S2b. The downstream second flow path Rb is connected to the second outflow path Pb2. In addition, the 2nd flow path Rb (the 2nd flow path Rb connected to the 2nd outflow path Pb2) in the most downstream in each system | strain S1a, S1b, S2a, S2b is not limited to one, and even if there is more than one. Good.

  In the first embodiment, the barrier ribs 231 and 331 having the bent ribs 232 and 332 are formed over the entire length of the heat transfer portions 20 and 30 in the third direction, but the present invention is not limited thereto. For example, the barrier ribs 231 and 331 may include a plurality (two or more) of bent rib portions 232 and 332. Further, the barrier ribs 231 and 331 may have a curved shape when viewed from the first direction. Further, the barrier ribs 231 and 331 may be formed in a corrugated shape in which a plurality of curved portions are connected when viewed from the first direction.

  Further, the barrier ribs 231 and 331 that are linear over the entire length may be formed over the entire length in the third direction of the heat transfer portions 20 and 30. However, when the barrier ribs 231 and 331 are provided on both of the adjacent heat transfer plates 2 and 3, the barrier ribs 231 of one of the heat transfer plates 2 and 3 that are adjacent to each other are provided. 331 is displaced in the second direction with respect to the barrier ribs 231 and 331 of the other heat transfer plate 2 or 3 of the adjacent heat transfer plates 2 and 3. By doing so, it is possible to prevent the barrier ribs 231 and 331 from contacting each other over the entire length and closing the first flow path Ra, and also to achieve the same operation and effect as the above embodiment. You can

In the second embodiment, each of the plurality of barrier ribs 231 and 331 extends straight in the third direction, but the present invention is not limited to this. For example, each of the plurality of barrier ribs 231 and 331 may include the bent ribs 232 and 332 as in the first embodiment.
In this case, the barrier ribs 231 and 331 of the adjacent heat transfer plates 2 and 3 may intersect with each other when viewed from the first direction.

  In the second embodiment, the barrier ribs 231 and 331 are provided to intersect the plurality of first ribs 230 and 330, but the invention is not limited to this. The barrier ribs 231 and 331 may extend in a direction intersecting with the first ribs 230 and 330. That is, the ribs 231 and 331 for partition walls extend in a direction intersecting with the first ribs 230 and 330 (the claw portion (ridge line) of the ribs 231 and 331 for partition wall intersects with the first ribs 230 and 330. It is formed to be extremely short on the assumption that it extends in the direction) and intersects only the single first ridge 230, 330, or between the adjacent first ridges 230, 230, 330, 330 (the single first ridge 230, 330). It may be present in one recessed line 220, 320).

  1 ... Plate heat exchanger (heat exchanger), 2 ... 1st heat transfer plate (heat transfer plate), 3 ... 2nd heat transfer plate (heat transfer plate), 20, 30 ... Heat transfer part, 21, 31 ... Fitting part, 22, 32 ... Recessed line, 23, 33 ... Convex line, 200, 201, 202, 203, 300, 301, 302, 303 ... Opening, 220, 320 ... First recessed line, 221, 321 ... Second groove, 222, 322 ... Back groove, 223, 323 ... Bent groove, 223a, 223b, 323a, 323b ... Inclined groove, 230, 330 ... First ridge, 231, 331 ... For barrier Ridge, 232, 332 ... bent ridge, 232a, 232b, 332a, 332b ... inclined ridge, 233, 333 ... second ridge, A ... first fluid, B ... second fluid, CL ... longitudinal center Line, Pa1 ... first inflow path, Pa2 ... first outflow path, Pb1 Second inlet passage, Pb2 ... second outlet channel, Ra ... first passage, Rb ... second channel, Sa1, Sb1 ... first surface, Sa2, Sb2 ... second surface

As another aspect of the present invention, each heat transfer portion of the adjacent heat transfer plates includes a plurality of second ridges in front and back relation with the first ridge, as the ridges formed on the second surface. The second ridges of the adjacent heat transfer plates may overlap the second ridges of the partner heat transfer plate and may be in contact with the tops of the second ridges of the partner heat transfer plate.

In the present embodiment, the plurality of barrier ribs 231 and 331 are provided on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30, respectively. The plurality of barrier ribs 231 and 331 are arranged at intervals in the second direction. Each of the plurality of barrier ribs 231 and 331 is lower than the first ribs 230 and 330, as described above. Specifically, a protrusion from a virtual surface (a virtual surface that spreads in the second direction and the third direction) that passes through the tops of a plurality of second protrusions 233 and 333 described below that are formed on the second surfaces Sa2 and Sb2. The amount of the barrier ribs 231 and 331 is smaller than that of the first ribs 230 and 330. Accordingly, the tops of the barrier ribs 231 and 331 are located closer to the second surface in the first direction than the tops of the first ribs 230 and 330. That is, the tops of the barrier ribs 231 and 331 are located between the tops of the first ribs 230 and 330 and the bottoms of the first recesses 220 and 320.

Accordingly, the distance (distance) between the tops of the first ridges 230 and 330 and the tops of the barrier ridges 231 and 331 in the first direction is one of the adjacent heat transfer plates 2 and 3. The distance between the first ridges 230 and 330 of the heat transfer plates 2 and 3 and the first ridges 220 and 320 of the other heat transfer plates 2 and 3 is such that the flow of the first fluid A can be secured. , Set.

Along with this, the first ridges 230 and 330 of the heat transfer plates 2 and 3 of one of the heat transfer plates 2 and 3 that are adjacent to each other cause the heat transfer plate 2 of the other of the heat transfer plates 2 and 3 that is adjacent to each other. , 3 of the first concave stripes 220, 320 too close to each other, the gap between the both sides of the first convex stripes 230, 330 in the width direction and the both sides of the first concave stripes 220, 320 in the width direction disappears, or The gap between the top of the first ridges 230 and 330 and the bottom of the first ridges 220 and 320 is extremely narrow.

Therefore, in the present embodiment, the distance between both sides in the width direction of the first ridges 230, 330 and the both sides in the width direction of the first ridges 220, 320 is the distance at which the fluidity of the first fluid A can be ensured. Thus, the distance (distance) between the tops of the first protrusions 230 and 330 and the tops of the barrier protrusions 231 and 331 in the first direction is set.

On the other hand, on the second surface Sa2, Sb2 side of the adjacent heat transfer plates 2, 3, as shown in FIG. 8 to FIG. 10, the second ridge 233 of the first heat transfer plate 2 (heat transfer part 20) is The second recess 221 of the first heat transfer plate 2 (heat transfer part 20) faces the second protrusion 333 of the second heat transfer plate (heat transfer part 30). It faces the second groove 321 of the portion 30). That is, in the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 of the first heat transfer plate 2 and the second heat transfer plate 3, respectively, a specific first concave portion of the plurality of first concave grooves 220 and 320 is formed. First ridges 230, 330 adjacent to the first ridges 220, 320 and a particular first ridge 230, 330 of the plurality of first ridges 230, 330. Since the boundary with is located on the vertical center line CL, as described above, by rotating the first heat transfer plate 2 and the second heat transfer plate 3 by 180 °, the adjacent heat transfer plates 2, 3 The second ridges 233, 333 of the above are opposed to each other, and their tops are brought into contact with each other. Further, the back side recessed lines 222 and 322 of the heat transfer plates 2 and 3 which are adjacent to each other when viewed from the first direction are in a state of facing each other (matching state) (see FIG. 12).

In addition, in the present embodiment, the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3 are the first ridges 220 and 320 as the ridges 23 and 33 formed on the second surfaces Sa2 and Sb2. The second convex ridges 233, 333 of the adjacent heat transfer plates 2, 3 include a plurality of second convex ridges 233, 333 having a front and back relationship with each other. Since it overlaps with the strips 233, 333 and is in contact with the tops of the second convex strips 233, 333 of the heat transfer plates 2, 3 of the other side, the flow pressure of the first fluid A flowing in the first flow channel Ra is Even if it acts on the heat transfer parts 20 and 30, the heat transfer parts 20 and 30 are not expanded. Therefore, the space forming the second flow path Rb is secured, and the smoothness of the circulation of the second fluid B is secured.

In the present embodiment, the plurality of barrier ribs 231 and 331 are provided on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30, respectively. The plurality of barrier ribs 231 and 331 are arranged at intervals in the second direction. Each of the plurality of barrier ribs 231 and 331 is lower than the first ribs 230 and 330, as described above. Specifically, a protrusion from a virtual surface (a virtual surface that spreads in the second direction and the third direction) that passes through the tops of a plurality of second protrusions 233 and 333 described below that are formed on the second surfaces Sa2 and Sb2. The amount of the barrier ribs 231 and 331 is smaller than that of the first ribs 230 and 330. Accordingly, the tops of the barrier ribs 231 and 331 are located closer to the second surface in the first direction than the tops of the first ribs 230 and 330. That is, the tops of the barrier ribs 231 and 331 are located between the tops of the first ribs 230 and 330 and the bottoms of the first recesses 220 and 320.

Accordingly, the distance (distance) between the tops of the first ridges 230 and 330 and the tops of the barrier ridges 231 and 331 in the first direction is one of the adjacent heat transfer plates 2 and 3. The distance between the first ridges 230 and 330 of the heat transfer plates 2 and 3 and the first ridges 220 and 320 of the other heat transfer plates 2 and 3 is such that the flow of the first fluid A can be secured. , Set.

Along with this, the first ridges 230 and 330 of the heat transfer plates 2 and 3 of one of the heat transfer plates 2 and 3 that are adjacent to each other cause the heat transfer plate 2 of the other of the heat transfer plates 2 and 3 that is adjacent to each other. , 3 of the first concave stripes 220, 320 too close to each other, the gap between the both sides of the first convex stripes 230, 330 in the width direction and the both sides of the first concave stripes 220, 320 in the width direction disappears, or The gap between the top of the first ridges 230 and 330 and the bottom of the first ridges 220 and 320 is extremely narrow.

Therefore, in the present embodiment, the distance between both sides in the width direction of the first ridges 230, 330 and the both sides in the width direction of the first ridges 220, 320 is the distance at which the fluidity of the first fluid A can be ensured. Thus, the distance (distance) between the tops of the first protrusions 230 and 330 and the tops of the barrier protrusions 231 and 331 in the first direction is set.

On the other hand, on the second surface Sa2, Sb2 side of the adjacent heat transfer plates 2 and 3, the second ridge 233 of the first heat transfer plate 2 (heat transfer section 20) has the second heat transfer plate (heat transfer plate). The second recessed portion 221 of the first heat transfer plate 2 (heat transfer portion 20) faces the second protruding portion 333 of the portion 30) and the second recessed portion 321 of the second heat transfer plate (heat transfer portion 30). To face. That is, in the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 of the first heat transfer plate 2 and the second heat transfer plate 3, respectively, a specific first concave portion of the plurality of first concave grooves 220 and 320 is formed. First ridges 230, 330 adjacent to the first ridges 220, 320 and a particular first ridge 230, 330 of the plurality of first ridges 230, 330. Since the boundary with is located on the vertical center line CL, as described above, by rotating the first heat transfer plate 2 and the second heat transfer plate 3 by 180 °, the adjacent heat transfer plates 2, 3 The second ridges 233, 333 of the above are opposed to each other, and their tops are brought into contact with each other.

In addition, in the present embodiment, the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3 are the first ridges 220 and 320 as the ridges 23 and 33 formed on the second surfaces Sa2 and Sb2. The second convex ridges 233, 333 of the adjacent heat transfer plates 2, 3 include a plurality of second convex ridges 233, 333 having a front and back relationship with each other. Since it overlaps with the strips 233, 333 and is in contact with the tops of the second convex strips 233, 333 of the heat transfer plates 2, 3 of the other side, the flow pressure of the first fluid A flowing in the first flow channel Ra is Even if it acts on the heat transfer parts 20 and 30, the heat transfer parts 20 and 30 are not expanded. Therefore, the space forming the second flow path Rb is secured, and the smoothness of the circulation of the second fluid B is secured.

In each of the above-described embodiments, the tops of the second ridges 233 and 333 of the adjacent heat transfer plates 2 and 3 (the first heat transfer plate 2 and the second heat transfer plate 3) are in contact with or connected to each other. Not limited to. For example, the tops of the second ridges 233 and 333 of the adjacent heat transfer plates 2 and 3 (the first heat transfer plate 2 and the second heat transfer plate 3) are separated from each other in the first direction or the second direction. Good. However, in order to obtain rigidity that can counter the rise in the flow pressure in the first flow path Ra and the like, as in the above embodiment, the adjacent heat transfer plates 2 and 3 (the first heat transfer plate 2 and the second heat transfer plate 2) are provided. The tops of the second ridges 233 and 333 of the plate 3) are preferably in contact with or connected to each other.

In each of the above-described embodiments, the width dimensions (dimensions in the direction orthogonal to the longitudinal direction) of the first concave stripes 220 and 320 and the first convex stripes 230 and 330 are set to be the same, but the present invention is not limited thereto. For example, as shown in FIGS. 25 to 27, the width dimensions of the first concave stripes 220 and 320 may be set larger than the width dimensions of the first convex stripes 230 and 330. Specifically, as shown in FIG. 25, the radius of curvature of the first recessed ridges 220, 320 is set to the first radius, assuming that the first recessed ridges 220, 320 and the first ridges 230, 330 are formed in an arc cross section. It may be set to be larger than the radius of curvature of the one ridge 230, 330. Further, as shown in FIGS. 26 and 27, the bottoms of the first recessed strips 220 and 320 are formed flat so that the width dimension of the first recessed strips 220 and 320 is smaller than the width dimension of the first protruding strips 230 and 330. It may be set large. In this case, as shown in FIG. 26, the first ridges 230 and 330 may have an arcuate cross section, or as shown in FIG. 27, the tops of the first ridges 230 and 330 may have a flat shape. By doing this, the first protrusions 230, 330 of the heat transfer plates 2, 3 of the other party cross-butt against the barrier protrusions 231, 331 lower than the first protrusions 230, 330. Even when the first ridges 230, 330 approach or enter the first ridges 220, 320, there is an extreme gap between the first ridges 220, 320 and the first ridges 230, 330. The flowability of the first fluid A is ensured without forming a narrowed portion.

In the second embodiment, the barrier ribs 231 and 331 are provided to intersect the plurality of first ribs 230 and 330, but the invention is not limited to this. The barrier ribs 231 and 331 may extend in a direction intersecting with the first ribs 230 and 330. That is, the ribs for partition wall 231 and 331 extend in a direction intersecting with the first ribs 230 and 330 (the tops (ridge lines) of the ribs for partition wall 231 and 331 intersect the first ribs 230 and 330). It is formed to be extremely short on the assumption that it extends in the direction) and intersects only the single first ridge 230, 330, or between the adjacent first ridges 230, 230, 330, 330 (the single first ridge 230, 330). It may be present in one recessed line 220, 320).

Claims (5)

The first surface on which the ridges and the ridges are formed, and the recessed ridges facing the opposite side to the first surface and having a front and back relationship with the ridges on the first surface and the ridges and the front and back of the first surface A heat transfer plate including a heat transfer part having a second surface on which a ridge is formed, each heat transfer part comprising a plurality of heat transfer plates superposed in a first direction,
Each of the plurality of heat transfer plates makes the first surface of its own heat transfer section face the first surface of the heat transfer section of the heat transfer plate arranged next to one side in the first direction, and The second surface of the second surface of the heat transfer plate in the heat transfer plate next to each other on the other side of the first direction,
A first flow path that allows the first fluid to flow in a second direction orthogonal to the first direction is formed between the first surfaces of the heat transfer portions of the adjacent heat transfer plates, and causes the second fluid to flow in the second direction. A second flow path is formed between the second surfaces of the heat transfer parts of the adjacent heat transfer plates,
Each heat transfer portion of the adjacent heat transfer plates is a plurality of first ridges arranged at intervals in a direction intersecting the first direction and the second direction as a ridge formed on the first surface. And includes a plurality of first ridges each extending in a second direction or a composite direction including the second direction as a component, and as a ridge formed on the first surface, intersects the first direction and the second direction. A plurality of first concave lines formed between the first convex lines adjacent to each other in the direction of, and as a concave line formed on the second surface, a plurality of second concave lines having a front and back relationship with the first convex line. Including articles,
The heat transfer portion of at least one heat transfer plate of the adjacent heat transfer plates is a barrier formed on the first surface and is lower than the first protrusion formed on the first surface. A ridge, including at least one barrier ridge extending in a direction intersecting with the first ridge,
The first ridges of the adjacent heat transfer plates are located between the first ridges of the other heat transfer plate, and the barrier ridges of at least one of the heat transfer plates and the other heat transfer plate of the other party. The first ridge is cross-collision,
Plate heat exchanger. At least one of the adjacent heat transfer plates has a plurality of barrier ribs arranged at intervals in the second direction as the ribs formed on the first surface.
The plate heat exchanger according to claim 1. Each heat transfer portion of the adjacent heat transfer plate includes a plurality of second ridges in front and back relation with the first ridge, as the ridges formed on the second surface.
Each of the second ridges of the adjacent heat transfer plates overlaps with the second ridge of the partner heat transfer plate and is in contact with the second ridge of the partner heat transfer plate.
The plate heat exchanger according to claim 1. The barrier rib has at least one bent rib portion,
The bent ridge portions are a pair of inclined ridge portions each having a base end and a tip opposite to the base end, and are center lines extending in the second direction or virtual lines parallel to the center line. With respect to each other, including a pair of inclined ridges, which are inclined in opposite directions and whose tips are connected to each other.
The plate heat exchanger according to any one of claims 1 to 3. Each heat transfer portion of the adjacent heat transfer plates includes a barrier rib having a bent rib.
The bent ridges of the barrier ribs of the adjacent heat transfer plates are formed by bending diametrically opposite each other.
The plate heat exchanger according to claim 4.

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