CN110662937A - Plate heat exchanger - Google Patents

Plate heat exchanger Download PDF

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Publication number
CN110662937A
CN110662937A CN201780091159.0A CN201780091159A CN110662937A CN 110662937 A CN110662937 A CN 110662937A CN 201780091159 A CN201780091159 A CN 201780091159A CN 110662937 A CN110662937 A CN 110662937A
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China
Prior art keywords
heat transfer
portions
convex
strips
concave
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Granted
Application number
CN201780091159.0A
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Chinese (zh)
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CN110662937B (en
Inventor
田中信雄
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Hisaka Works Ltd
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Hisaka Works Ltd
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Publication of CN110662937A publication Critical patent/CN110662937A/en
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Publication of CN110662937B publication Critical patent/CN110662937B/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/02—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the heat-exchange media travelling at an angle to one another
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

In a heat transfer plate of a plate heat exchanger, a first surface (Sa1) of a heat transfer portion is opposed to a first surface of a heat transfer portion of adjacent parallel heat transfer plates, a second surface which is a rear surface of the first surface (Sa1) is opposed to a second surface of the heat transfer portion of the adjacent parallel heat transfer plates, a first flow path is formed between the first surfaces (Sa1), and a second flow path is formed between the second surfaces. The first surface (Sa1) of the heat transfer portion includes a plurality of first convex strips (230), a barrier convex strip (231) which is lower than the first convex strips and extends in the direction intersecting the first convex strips, and a plurality of first concave strips (220) formed between adjacent first convex strips, and the second surface of the heat transfer portion includes a plurality of second concave strips which are in a front-back relationship with the first convex strips. The first convex strips (230) of the adjacent heat transfer plates are positioned between the first convex strips (230) of the opposite heat transfer plates, and the blocking convex strips (231) of the adjacent heat transfer plates are crossed and butted with the first convex strips (230) of the opposite heat transfer plates.

Description

Plate heat exchanger
Technical Field
The present invention relates to a plate heat exchanger used as a condenser or an evaporator.
Background
Conventionally, a plate heat exchanger includes a plurality of heat transfer plates. The plurality of heat transfer plates each include a heat transfer portion. The heat transfer portion has a first face and a second face in a first direction. Specifically, the heat transfer portion includes: a first surface formed with convex strips and concave strips; and a second surface facing the opposite side relative to the first surface, wherein the second surface is provided with concave strips which are in a surface-interior relationship with the convex strips of the first surface and convex strips which are in a surface-interior relationship with the concave strips of the first surface.
In each of the first and second surfaces of the heat transfer portion, the ridges intersect a center line of the heat transfer portion (hereinafter referred to as a "longitudinal center line") extending in a second direction orthogonal to the first direction. The convex strip is formed on the whole length of the heat transfer part in a third direction, and the third direction is orthogonal to the first direction and the second direction.
The plurality of heat transfer plates are overlapped in the first direction. That is, each of the plurality of heat transfer plates has a first surface of its own heat transfer portion facing a first surface of a heat transfer portion of a heat transfer plate arranged adjacent to one side in the first direction. The plurality of heat transfer plates have second surfaces of their own heat transfer portions facing second surfaces of the heat transfer portions of the heat transfer plates arranged adjacent to each other on the other side in the first direction.
In this state, the convex strips of the heat transfer portions of the adjacent heat transfer plates are crossed and abutted against each other, and a space is formed between the heat transfer portions of the adjacent heat transfer plates by the concave strips of the heat transfer portions. That is, the first flow path through which the first fluid flows in the second direction is formed between the first surfaces of the heat transfer portions of the adjacent heat transfer plates. In addition, a second flow path through which a second fluid flows in a second direction is formed between the second surfaces of the heat transfer portions of the adjacent heat transfer plates. In the plate heat exchanger, the first fluid in the first flow path and the second fluid in the second flow path exchange heat with each other through a heat transfer portion that separates the first flow path and the second flow path (see, for example, patent document 1).
Therefore, such a plate heat exchanger is sometimes used as a condenser, which is a device for condensing a second fluid in a second flow path by heat exchange between the first fluid in a first flow path and the second fluid in the second flow path. Further, such a plate heat exchanger may be used as an evaporator that evaporates a second fluid in a second flow path by exchanging heat between a first fluid in a first flow path and the second fluid in the second flow path.
However, when the conventional plate heat exchanger is used as a condenser or an evaporator, there is a limit in improving heat transfer performance in terms of a relationship with the characteristics of the second fluid to be condensed or evaporated.
Specifically, the ridges of the heat transfer portion are formed across the longitudinal center line of the heat transfer portion and over the entire length of the heat transfer portion in the third direction. Therefore, the ridges of the heat transfer portion increase the flow resistance of each of the first flow path and the second flow path.
Generally, a fluid that does not undergo a phase change (a fluid that is a single-phase fluid) is used as the first fluid. Therefore, the increase in the flow resistance of the first flow path increases the chance of thermally affecting the heat transfer portion. Therefore, the increase in the flow resistance of the first flow path becomes a factor for improving the heat transfer performance.
The second fluid is a fluid that undergoes a phase change such as freon (a fluid that is a two-phase flow containing a liquid and a gas). Accordingly, a liquid film of the second fluid is formed on the second surface of the heat transfer portion defining the second flow path. Therefore, in order to improve the heat conduction 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 portion.
However, since the ridges of the heat transfer portion are formed across the longitudinal center line of the heat transfer portion over the entire length of the heat transfer portion in the third direction, the ridges of the heat transfer portion interfere with the flow of the second fluid in the second flow path. That is, since the convex strip located on the second surface of the heat transfer portion is formed so as to intersect (cross) the flow of the second fluid in the second flow path, the resistance to the flow of the second fluid in the second flow path increases.
Therefore, in the conventional plate heat exchanger, there is a limit in increasing the flow velocity of the second fluid in the second flow channel, and the flow of the liquid film of the second fluid formed on the second surface of the heat transfer portion cannot be sufficiently disturbed.
Therefore, in the conventional plate heat exchanger, there is a limit to improve the heat transfer performance of the second fluid flowing through the second flow passage with respect to the heat transfer portion.
Documents of the prior art
Patent document
Patent document 1: japanese unexamined patent publication No. 2001-99588
Disclosure of Invention
Problems to be solved by the invention
Accordingly, an object of the present invention is to provide a plate heat exchanger capable of improving heat conduction performance of a second fluid with respect to a heat transfer portion, wherein the second fluid changes phase by heat exchange with a first fluid.
Means for solving the problems
The plate heat exchanger of the present invention comprises a plurality of heat transfer plates each including a heat transfer portion overlapping in a first direction, the heat transfer portion having a first surface and a second surface, wherein the first surface has ridges and grooves formed therein, the second surface faces the opposite side to the first surface and has grooves in a front-back relationship with the ridges of the first surface and ridges in a front-back relationship with the grooves of the first surface, the plurality of heat transfer plates have the first surface of their own heat transfer portion opposed to the first surface of the heat transfer portion of the heat transfer plates arranged adjacent to one side in the first direction, and the second surface of their own heat transfer portion opposed to the second surface of the heat transfer portion of the heat transfer plates arranged adjacent to the other side in the first direction, and a first flow path for allowing a 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 a second flow path for circulating a second fluid in a second direction is formed between the second surfaces of the heat transfer portions of the adjacent heat transfer plates, each of the heat transfer portions of the adjacent heat transfer plates includes a plurality of first convex strips as convex strips formed on the first surface, the plurality of first convex strips are arranged at intervals in a direction intersecting with the first direction and the second direction, the plurality of first convex strips extend in the second direction or a synthetic direction including a component of the second direction, respectively, each of the heat transfer portions of the adjacent heat transfer plates includes a plurality of first concave strips as concave strips formed on the first surface, the plurality of first concave strips are formed between the first convex strips adjacent in the direction intersecting with the first direction and the second direction, and a plurality of second concave strips in a front-back relationship with the first convex strips are formed on the second surface, the heat transfer portion of at least one of the heat transfer plates of the adjacent heat transfer plates includes at least one convex strip for blocking as convex strip formed on the first surface, the first ribs are formed on the first surface, and extend in a direction intersecting the first ribs, and each of the first ribs of the adjacent heat transfer plates is located between the first ribs of the opposite heat transfer plate, and the first ribs of at least one of the heat transfer plates intersect and abut the first ribs of the opposite heat transfer plate.
In one aspect of the present invention, it is preferable that at least one of the adjacent heat transfer plates includes a plurality of barrier ribs as the ribs formed on the first surface, and the plurality of barrier ribs are arranged at intervals in the second direction.
As another aspect of the present invention, each of the heat transfer portions of the adjacent heat transfer plates may include a plurality of second ridges as ridges formed on the second surface, the second ridges of the adjacent heat transfer plates being in a front-back relationship with the first ridges, and the second ridges of the adjacent heat transfer plates may overlap with the second ridges of the opposite heat transfer plates and may contact top portions of the second ridges of the opposite heat transfer plates.
The stopper rib may have at least one curved ridge portion including a pair of inclined ridge portions each having a base end and a tip end located on the opposite side of the base end, the pair of inclined ridge portions being inclined toward opposite directions to each other with respect to a center line extending in the second direction or an imaginary line parallel to the center line, and the tip ends of the pair of inclined ridge portions being connected to each other.
Preferably, each of the heat transfer portions of the adjacent heat transfer plates includes a barrier rib having curved ridges, and the curved ridges of the barrier ribs of the adjacent heat transfer plates are formed by being curved in opposite directions to each other.
Drawings
Fig. 1 is a perspective view of a plate heat exchanger according to a 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 of a flow path including a first fluid and a 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 the flow paths of the first fluid in the first flow path and the second fluid in the second flow path of the plate heat exchanger according to the first embodiment.
Fig. 8 is a schematic partial sectional view of the plate heat exchanger according to the first embodiment as viewed from the second direction.
Fig. 9 is a sectional view IX-IX of fig. 8, which is a sectional view illustrating the flow of the fluid in the first flow path and the second flow path.
Fig. 10 is a cross-sectional view taken along line X-X in fig. 8, and is a cross-sectional view illustrating the flow of fluid in the first flow path and the second flow path.
Fig. 11 is a diagram showing the flow of the first fluid in the first flow path in the plate heat exchanger according to the first embodiment.
Fig. 12 is a diagram showing the flow of the second fluid in the second flow path in the plate heat exchanger according to the first embodiment.
Fig. 13 is an exploded perspective view of a plate heat exchanger according to a second embodiment of the present invention, and is an exploded perspective view of a flow path including a first fluid and a second fluid.
Fig. 14 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 first 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 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 first 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 the flow paths of the first fluid in the first flow path and the second fluid in the second flow path of the plate heat exchanger according to the second embodiment.
Fig. 19 is a schematic partial sectional view of the plate heat exchanger according to the second embodiment as viewed from the second direction.
Fig. 20 is a cross-sectional view XX-XX in fig. 19, which is a cross-sectional view illustrating the flow of the fluid in the first flow path and the second flow path.
Fig. 21 is a sectional view taken along line XXI-XXI in fig. 19, and is a sectional view illustrating the flow of fluid in the first channel and the second channel.
Fig. 22 is a sectional view XXII to XXII in fig. 19, and is a sectional view in which the flow of the fluid in the first channel and the second channel is described.
Fig. 23 is a view showing the flow of the first fluid in the first flow path in the plate heat exchanger according to the second embodiment.
Fig. 24 is a diagram showing the flow of the second fluid in the second flow path in the plate heat exchanger according to the second embodiment.
Fig. 25 is a schematic partial sectional view of a plate heat exchanger according to another embodiment of the present invention, as viewed from a second direction.
Fig. 26 is a schematic partial sectional view of a plate heat exchanger according to another embodiment of the present invention, as viewed from a second direction.
Fig. 27 is a schematic partial sectional view of a plate heat exchanger according to still another embodiment of the present invention, as viewed from a 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.
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 in a plate heat exchanger according to still another embodiment of the present invention.
Detailed Description
Hereinafter, a plate heat exchanger according to a first embodiment of the present invention will be described with reference to the drawings.
As shown in fig. 1 and 2, a plate heat exchanger (hereinafter, simply referred to as "heat exchanger" in the present embodiment) 1 of the first embodiment includes three or more heat transfer plates 2 and 3.
Three or more heat transfer plates 2, 3 are superposed in the first direction. In the present embodiment, two types of heat transfer plates are included in the three or more heat transfer plates 2 and 3. The two types of heat transfer plates 2, 3 are alternately arranged in the first direction.
Accordingly, as shown in fig. 2, 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 are alternately formed in the first direction in the heat exchanger 1 with the heat transfer plates 2 and 3 as boundaries.
Here, the two heat transfer plates 2 and 3 will be specifically described. The two heat transfer plates 2, 3 have the same points and different points. First, the same points of the two heat transfer plates 2 and 3 will be described.
As shown in fig. 3 to 6, the heat transfer plates 2 and 3 include heat transfer portions 20 and 30 and annular fitting portions 21 and 31, wherein the heat transfer portions 20 and 30 include first surfaces Sa1 and Sb1 and second surfaces Sa2 and Sb2, the second surfaces Sa2 and Sb2 face opposite directions with respect to the first surfaces Sa1 and Sb1, and the annular fitting portions 21 and 31 extend from the entire circumferential direction of the outer peripheral edges of the heat transfer portions 20 and 30 in a direction intersecting the surfaces of the heat transfer portions 20 and 30.
The heat transfer portions 20, 30 have a thickness in the first direction. Accordingly, the first faces Sa1, Sb1 and the second faces Sa2, Sb2 of the heat transfer portions 20, 30 are aligned in the first direction. The heat transfer portions 20 and 30 are defined in an outline by 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 and extending in a third direction orthogonal to the first direction and the second direction and connected to the pair of long sides. That is, the outer shape of the heat transfer portions 20 and 30 as viewed in the first direction is a rectangle having long sides in the second direction.
The heat transfer portions 20 and 30 have one end portion and the other end portion located on the opposite side of the one end portion in the second direction. The heat transfer portions 20 and 30 have at least two openings 200, 201, 202, 203, 300, 301, 302, and 303 at one end portion and the other end portion in the second direction, respectively. In the present embodiment, the heat transfer portions 20 and 30 have two openings 200, 203, 300, and 303 at one end in the second direction, and two openings 201, 202, 301, and 302 at the other end in the second direction.
The two openings 200, 203, 300, 303 located at one end portion of the heat transfer portions 20, 30 in the second direction are juxtaposed in the third direction. In addition, the two openings 201, 202, 301, 302 located at the other end portions of the heat transfer portions 20, 30 in the second direction are juxtaposed in the third direction.
The peripheries of the openings 200, 300 located on one side of one end portion in the second direction and the peripheries of the openings 201, 301 located on the other end portion in the heat transfer portions 20, 30 are recessed on the first surfaces Sa1, Sb1 sides. Accordingly, the peripheries of the openings 200 and 300 located at one end and the peripheries of the openings 201 and 301 located at the other end of the heat transfer portions 20 and 30 bulge out on the second surfaces Sa2 and Sb2 sides.
The amount of swelling of the peripheries of the openings 200, 300 on the one side of the one end portion and the openings 201, 301 on the other end portion of the heat transfer portions 20, 30 toward the second surfaces Sa2, Sb2 side is set so as to be able to contact the peripheries of the openings 200, 201, 300, 301 (the openings 200, 300 on the one side of the one end portion and the openings 201, 301 on the other end portion) of the heat transfer portions 20, 30 of the heat transfer plates 2, 3 arranged adjacent to each other in the first direction.
In contrast, the peripheries of the openings 203, 303 on the other side of the one end portion and the peripheries of the openings 202, 302 on the other side of the other end portion in the second direction of the heat transfer portions 20, 30 are recessed on the second surface Sa2, Sb2 side. Accordingly, the peripheries of the openings 203, 303 on the other side of the one end portion and the peripheries of the openings 202, 302 on the other side of the other end portion in the second direction in the heat transfer portions 20, 30 bulge out on the first surfaces Sa1, Sb1 side.
The amount of bulging of the periphery of the other side opening 203, 303 at the one end portion in the second direction and the periphery of the other side opening 202, 302 at the other end portion in the heat transfer portion 20, 30 to the first surface Sa1, Sb1 side is set so as to be able to contact the periphery (bulged portion) of the openings 202, 203, 302, 303 (the other side opening 202, 302 at the one end portion and the other side opening 203, 303 at the other end portion) of the heat transfer portions 20, 30 of the heat transfer plates 2, 3 arranged adjacent to each other in the first direction. In fig. 3 to 6, in order to clarify the concave-convex relationship of each of the first faces Sa1, Sb1 and the second faces Sa2, Sb2, the regions recessed around the openings 200, 201, 202, 203, 300, 301, 302, 303 and the bottom portions of the concave ridges 22, 32 described later are marked with dots.
In the present embodiment, the openings 200 and 300 of the heat transfer portions 20 and 30 on the one side of the one end portion in the second direction and the openings 201 and 301 on the other end portion are diagonally positioned in accordance with the relationship with the state in which the heat transfer plates 2 and 3 are overlapped. In the heat transfer portions 20 and 30, the openings 203 and 303 on the other side of one end in the second direction are diagonally positioned from the openings 202 and 302 on the other side of the other end.
Concave stripes 22, 32 and convex stripes 23, 33 are formed on the first faces Sa1, Sb1 and the second faces Sa2, Sb2 of the heat transfer sections 20, 30, respectively. The heat transfer sections 20 and 30 have a plurality of (a plurality of) concave stripes 22 and 32 and convex stripes 23 and 33 on the first faces Sa1 and Sb1 and the second faces Sa2 and Sb2, respectively.
More specifically, the heat transfer plates 2 and 3 are formed by press-forming a metal plate. Accordingly, the concave stripes 22, 32 formed on the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 and the convex stripes 23, 33 formed on the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 are in a front-back relationship with each other. The convex strips 23, 33 formed on the first surfaces Sa1, Sb1 of the heat transfer units 20, 30 and the concave strips 22, 32 formed on the second surfaces Sa2, Sb2 of the heat transfer units 20, 30 are in a front-back relationship. That is, the concave stripes 22, 32 formed on the first surfaces Sa1, Sb1 of the heat transfer sections 20, 30 are formed at positions corresponding to the convex stripes 23, 33 formed on the second surfaces Sa2, Sb2 of the heat transfer sections 20, 30 by deformation of the metal plate accompanying press forming. Further, the convex strips 23, 33 formed on the first surfaces Sa1, Sb1 of the heat transfer sections 20, 30 are formed at positions corresponding to the concave strips 22, 32 formed on the second surfaces Sa2, Sb2 of the heat transfer sections 20, 30 by deformation of the metal plates accompanying press forming.
As shown in fig. 3 and 5, the heat transfer portions 20 and 30 include, as the concave stripes 22 and 32 formed on the first surfaces Sa1 and Sb1, a plurality of first concave stripes 220 and 320 extending in the second direction and arranged at intervals in the third direction. Further, as the convex strips 23, 33 formed on the first faces Sa1, Sb1, the heat transfer portions 20, 30 include a plurality of first convex strips 230, 330, and the plurality of first convex strips 230, 330 extend in the second direction between the first concave strips 220, 320 adjacent in the third direction. That is, in the first faces Sa1, Sb1 of the heat transfer portions 20, 30, the first concave stripes 220, 320 and the first convex stripes 230, 330 are alternately arranged in the third direction.
The heat transfer portions 20 and 30 include at least one rib 231 and 331 for blocking, as the ribs 23 and 33 formed on the first faces Sa1 and Sb1, the rib 231 and 331 for blocking having a height lower than the first ribs 230 and 330 formed on the first faces Sa1 and Sb1 and extending in a direction intersecting the plurality of first ribs 230 and 330.
The widths of the first concave strips 220, 320 in the third direction and the widths of the first convex strips 230, 330 in the third direction are the same or substantially the same. The inner surface defining the first concave strip 220, 320 is continuous with the outer surface defining the first convex strip 230, 330. Thereby, the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 are formed in a wavy shape undulating in the first direction.
On the premise of this, in the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30, the boundary between a specific first concave stripe 220, 320 of the plurality of first concave stripes 220, 320 and a specific first convex stripe 230, 330 of the plurality of first convex stripes 230, 330, that is, the first convex stripe 230, 330 adjacent to the specific first concave stripe 220, 320, is located on the longitudinal center line CL.
That is, the specific first concave stripes 220, 320 or the specific first convex stripes 230, 330 are arranged to be shifted from the longitudinal centerline CL in the third direction by the following distance: 1/4 indicating the interval between the adjacent first convex strips 230, 330 with one first concave strip 220, 320 therebetween, or 1/4 indicating the interval between the adjacent first concave strips 220, 320 with one first convex strip 230, 330 therebetween.
In the present embodiment, the first surfaces Sa1, Sb1 of the heat transfer units 20, 30 have a plurality of stopper ribs 231, 331. The plurality of stopper ribs 231 and 331 are arranged at intervals in the second direction. As described above, the plurality of barrier ribs 231 and 331 are lower in height than the first ribs 230 and 330, respectively. Specifically, the amount of projection of the blocking ribs 231, 331 from an imaginary plane (an imaginary plane developed in the second direction and the third direction) passing through the tops of the plurality of second ribs 233, 333 described later formed on the second surfaces Sa2, Sb2 is smaller than the amount of projection of the first ribs 230, 330. Accordingly, the top portions of the barrier ribs 231 and 331 are located on the second surface side in the first direction with respect to the top portions of the first ribs 230 and 330. That is, the top of the barrier ribs 231, 331 is located between the top of the first ribs 230, 330 and the bottom of the first concave ribs 220, 320.
As will be described in detail later, in the present embodiment, in a state where the plurality of heat transfer plates 2 and 3 are stacked, the first ridges 230 and 330 of the other heat transfer plate 2 and 3 of the adjacent heat transfer plates 2 and 3 are present between the first ridges 230 and 330 (the first concave stripes 220 and 320) of the one heat transfer plate 2 and 3 of the adjacent heat transfer plates 2 and 3.
Accordingly, the interval (distance) between the top of the first protrusion 230, 330 and the top of the stopper protrusion 231, 331 in the first direction is set to: the first ridges 230, 330 of one of the heat transfer plates 2, 3 and the first grooves 220, 320 of the other heat transfer plate 2, 3 are spaced apart from each other so as to ensure the flow of the first fluid a.
Specifically, in the present embodiment, the plurality of first concave stripes 220, 320 are set to have the same width, and the plurality of first convex stripes 230, 330 are set to have the same width in the heat transfer plates 2, 3. In each of the heat transfer plates 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.
Accordingly, if the first convex stripes 230, 330 of one heat transfer plate 2, 3 of the adjacent heat transfer plates 2, 3 are too close to the first concave stripes 220, 320 of the other heat transfer plate 2, 3 of the adjacent heat transfer plates 2, 3, the gaps between both sides in the width direction of the first convex stripes 230, 330 and both sides in the width direction of the first concave stripes 220, 320 disappear or become extremely narrow compared to the gaps formed between the tops of the first convex stripes 230, 330 and the bottoms of the first concave stripes 220, 320.
Therefore, in the present embodiment, the interval (distance) between the top of the first convex stripes 230, 330 and the top of the stopper convex stripes 231, 331 in the first direction is set so that the intervals between both sides in the width direction of the first convex stripes 230, 330 and both sides in the width direction of the first concave stripes 220, 320 are intervals at which the flow of the first fluid a can be ensured.
In the present embodiment, the barrier ribs 231 and 331 intersect the plurality of first ribs 230 and 330 and the first concave ribs 220 and 320. In the present embodiment, the barrier ribs 231, 331 are formed over the entire length of the heat transfer portions 20, 30 in the third direction.
In the present embodiment, the stopper ribs 231 and 331 have at least one curved convex strip portion 232 and 332. The curved raised strip portions 232 and 332 include a pair of inclined raised strip portions 232a, 232b, 332a, and 332b, the pair of inclined raised strip portions 232a, 232b, 332a, and 332b each have a base end and a tip end located on the opposite side of the base end, and are inclined in opposite directions with respect to the longitudinal center line CL, and the tip ends of the pair of inclined raised strip portions are connected to each other. In the present embodiment, the barrier ribs 231 and 331 have one curved convex strip portion 232 and 332.
In the present embodiment, the base ends of the pair of inclined raised strips 232a, 232b, 332a, 332b constituting the curved raised strips 232, 332 are located at the end edges of the heat transfer portions 20, 30 in the third direction.
The front ends of the pair of inclined ridges 232a, 232b, 332a, 332b are located at the center (on the longitudinal center line CL) of the heat transfer portions 20, 30 in the third direction. Thereby, the tip end portions of the pair of inclined raised strips 232a, 232b, 332a, 332b are connected in a state of being aligned with each other.
By having such a state, in the present embodiment, the stopper ridges 231 and 331 themselves constitute the curved ridge portions 232 and 332. The pair of inclined raised strips 232a, 232b, 332a, 332b are arranged symmetrically with respect to an imaginary line extending in the second direction. That is, the directions in which the pair of inclined raised strips 232a, 232b, 332a, 332b are inclined with respect to each other are diametrically opposite. However, the inclination angles of the pair of inclined convex portions 232a, 232b, 332a, 332b with respect to the longitudinal center line CL extending in the second direction are the same.
In this way, the barrier ribs 231, 331 are provided over the entire width of the heat transfer portions 20, 30 in the third direction. Accordingly, the first concave stripes 220, 320 and the first convex stripes 230, 330 on the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 are cut at a plurality of positions in the second direction. Accordingly, at least one end of the first concave stripe 220, 320 and the first convex stripe 230, 330 which are cut off is connected to the convex stripe 231, 331 for blocking.
In the present embodiment, the cut first concave stripes 220 and 320 are arranged in the second direction. Accordingly, the cut first ribs 230 and 330 are also aligned in the second direction.
As shown in fig. 4 and 6, the heat transfer portions 20 and 30 include a plurality of second concave stripes 221 and 321 as the concave stripes 22 and 32 formed on the second surfaces Sa2 and Sb2, and the plurality of second concave stripes 221 and 321 extend in the second direction and are arranged at intervals in the third direction. Further, as the convex strips 23 and 33 formed on the second surfaces Sa2 and Sb2, the heat transfer portions 20 and 30 include a plurality of second convex strips 233 and 333, and the plurality of second convex strips 233 and 333 are formed so as to extend in the second direction between the second concave strips 221 and 321 adjacent to each other in the third direction. That is, in the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30, the second concave stripes 221, 321 and the second convex stripes 233, 333 are alternately arranged in the third direction.
The heat transfer portions 20 and 30 include concave stripes (hereinafter, referred to as "back-side concave stripes") 222 and 322 as the concave stripes 22 and 32 formed on the second surfaces Sa2 and Sb2, and the concave stripes 222 and 322 are formed on the back sides of the barrier ribs 231 and 331 on the first surfaces Sa1 and Sb 1.
The second concave stripes 221, 321 are concave stripes 22, 32 formed on the back side of the first convex stripes 230, 330 on the first faces Sa1, Sb 1. Along with this, the second concave strips 221, 321 extend in the second direction. The second convex strips 233, 333 are convex strips 23, 33 formed on the back side of the first concave strips 220, 320 on the first faces Sa1, Sb 1. Accordingly, the second protrusions 233, 333 extend in the second direction.
The inner surfaces defining the second concave strips 221, 321 are continuous with the outer surfaces defining the second convex strips 233, 333. Thereby, the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 are formed in a wavy shape undulating in the first direction.
The back surface side concave strips 222, 322 and the barrier convex strips 231, 331 are formed in the same manner except that the concave-convex relationship is reversed. Therefore, the curved concave portions 223 and 323 are formed on the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30, the curved concave portions 223 and 323 include a pair of inclined concave portions 223a, 223b, 323a, and 323b, and the pair of inclined concave portions 223a, 223b, 323a, and 323b are the concave portions 22 and 32 formed on the back surfaces of the pair of inclined convex portions 232a, 232b, 332a, and 332 b.
In the present embodiment, the curved raised strips 232, 332 (the pair of inclined raised strips 232a, 232b, 332a, 332b) constitute the stopper ridges 231, 331. Therefore, the curved concave portions 223, 323 constitute the entirety of the back-side concave portions 222, 322 formed on the back sides of the convex ribs 231, 331 for stopper.
Accordingly, the second concave strips 221, 321 and the second convex strips 233, 333 are cut by the back-side concave strips 222, 322. Thereby, the cut second convex strips 233, 333 are connected to the back-side concave strips 222, 322. That is, the cut second concave strips 221, 321 are opened into the back-side concave strips 222, 322.
The common point of the two heat transfer plates 2 and 3 is as described above. Next, a difference between the two heat transfer plates 2 and 3 will be described.
As shown in fig. 3 and 5, the first ridges 230 on the first surface Sa1 of one of the two heat transfer plates 2, 3 (hereinafter referred to as "first heat transfer plate") 2 and the first ridges 330 on the first surface Sb1 of the other of the two heat transfer plates 2, 3 (hereinafter referred to as "second heat transfer plate") 3 are arranged so as to be offset in the third direction. That is, in a state where 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 face each other, the arrangement of the first concave stripes 220, 320 and the first convex stripes 230, 330 is set such that the first convex stripes 230 of the first heat transfer plate 2 correspond to the first concave stripes 320 of the second heat transfer plate 3, and the first convex stripes 330 of the second heat transfer plate 3 correspond to the first concave stripes 220 of the first heat transfer plate 2.
In the present embodiment, the dam ridges 231 of the first heat transfer plate 2 and the dam ridges 331 of the second heat transfer plate 3 are arranged in a state of being inverted with respect to an imaginary line extending in the third direction. That is, the inclination directions of the inclined ridges 232a, 232b of the dam ridges 231 of the first heat transfer plate 2 are opposite to the inclination directions of the inclined ridges 332a, 332b of the dam ridges 331 of the second heat transfer plate 3.
In the first heat transfer plate 2, as shown in fig. 3, the fitting portion 21 extends toward the first surface Sa1 of the heat transfer portion 20. In the second heat transfer plate 3, as shown in fig. 6, the fitting portion 31 extends toward the second surface Sb2 of the heat transfer portion 30.
The heat transfer plates 2 and 3 (the first heat transfer plate 2 and the second heat transfer plate 3) are as described above. As shown in fig. 2, the heat transfer plates 2 and 3 (the first heat transfer plate 2 and the second heat transfer plate 3) are stacked in the first direction. In the present embodiment, the first heat transfer plates 2 and the second heat transfer plates 3 are alternately stacked in the first direction. At this time, the plurality of heat transfer plates 2, 3 have the first surfaces Sa1, Sb1 of their own heat transfer portions 20, 30 facing the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 of the heat transfer plates 2, 3 arranged adjacent to each other on one side in the first direction, respectively. The plurality of heat transfer plates 2, 3 have the second surfaces Sa2, Sb2 of their own heat transfer portions 20, 30 facing the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the heat transfer plates 2, 3 arranged adjacent to each other on the other side in the first direction.
As a result, as shown in fig. 2 and 7, a first flow path Ra for flowing the first fluid a in the second direction and a second flow path Rb for flowing the second fluid B in the second direction are alternately formed with the heat transfer portions 20 and 30 of the heat transfer plates 2 and 3 as boundaries. That is, the first flow path Ra through which the first fluid a flows is formed between the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3, and the second flow path Rb through which the second fluid B flows is formed between the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3.
In this state, as shown in fig. 2, the openings 200, 201, 202, 203, 300, 301, 302, 303 located at the corresponding positions of the heat transfer portions 20, 30 are connected in the first direction. Further, the portions bulging toward the opposite side are in contact with the peripheries of the openings 200, 201, 202, 203, 300, 301, 302, 303 facing each other. Thus, a first inflow passage Pa1 for supplying the first fluid a to the first flow path Ra, a first outflow passage Pa2 for allowing the first fluid a to flow out from the first flow path Ra, a second inflow passage Pb1 for supplying the second fluid B to the second flow path Rb, and a second outflow passage Pb2 for allowing the second fluid B to flow out from the second flow path Rb are formed.
More specifically, when the plurality of heat transfer plates 2 and 3 are stacked, one first heat transfer plate 2 and one second heat transfer plate 3 are stacked in a state where the back side concave strips 222 and 322 face each other to form one set. When a plurality of such sets are overlapped, every other set is rotated by 180 degrees around an imaginary line extending in the first direction and overlapped. In this state, the fitting portions 21, 31 of one of the heat transfer plates 2, 3 (the first heat transfer plate 2 or the second heat transfer plate 3) adjacent in the first direction are fitted to the fitting portions 21, 31 of the other of the heat transfer plates 2, 3 (the first heat transfer plate 2 or the second heat transfer plate 3) adjacent in the first direction.
Thus, as shown in fig. 8 to 10, on the first faces Sa1, Sb1 sides of the adjacent heat transfer plates 2, 3, the first ridges 230 of the first heat transfer plate 2 (heat transfer portion 20) face the first grooves 320 of the second heat transfer plate (heat transfer portion 30), and the first grooves 220 of the first heat transfer plate 2 (heat transfer portion 20) face the first ridges 330 of the second heat transfer plate (heat transfer portion 30).
In the first heat transfer plate 2, the barrier ribs 231 are lower in height than the first ribs 230, and in the second heat transfer plate 3, the barrier ribs 331 are lower in height than the first ribs 330, so the barrier ribs 231 of the first heat transfer plate 2 cross and abut the first ribs 330 of the second heat transfer plate 3, and the barrier ribs 331 of the second heat transfer plate 3 cross and abut the first ribs 230 of the first heat transfer plate 2.
In the present embodiment, since the dam ridges 231 of the first heat transfer plate 2 and the dam ridges 331 of the second heat transfer plate 3 are provided in a state of being inverted with respect to the imaginary line extending in the third direction, the dam ridges 231 of the first heat transfer plate 2 and the dam ridges 331 of the second heat transfer plate 3 are arranged in a state of intersecting each other when viewed from the first direction as shown in fig. 11 in the state of being arranged as described above.
On the second surfaces Sa2, Sb2 sides of the adjacent heat transfer plates 2, 3, as shown in fig. 8 to 10, the second ridges 233 of the first heat transfer plate 2 (heat transfer portion 20) face the second ridges 333 of the second heat transfer plate (heat transfer portion 30), and the second concave ridges 221 of the first heat transfer plate 2 (heat transfer portion 20) face the second concave ridges 321 of the second heat transfer plate (heat transfer portion 30). That is, in the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 of the first heat transfer plate 2 and the second heat transfer plate 3, since the boundaries between the specific first concave strips 220, 320 of the plurality of first concave strips 220, 320 and the specific first convex strips 230, 330 of the plurality of first convex strips 230, 330 are located on the vertical center line CL, the tops of the first concave strips 230, 330 and the second convex strips 233, 333 of the adjacent heat transfer plates 2, 3 are opposed to each other by rotating the first heat transfer plate 2 and the second heat transfer plate 3 by 180 ° as described above, and the tops of the first concave strips 230, 330 and the specific first convex strips 230, 330 are adjacent to the specific first concave strips 220, 320. Further, the rear side concave strips 222, 322 of the adjacent heat transfer plates 2, 3 are opposed to each other (aligned state) when viewed from the first direction (see fig. 12).
As a result, as shown in fig. 2, a first flow path Ra for allowing the first fluid a to flow in a second direction orthogonal to the first direction is formed between the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3. Further, a second flow path Rb for allowing the second fluid B to flow 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.
As described above, the plurality of heat transfer plates 2 and 3 are overlapped in the first direction, and thus the openings 200, 201, 202, 203, 300, 301, 302, 303 located at the corresponding positions of the heat transfer portions 20 and 30 are connected in the first direction. Further, the portions bulging toward the opposite sides come into contact with the peripheries of the openings 200, 201, 202, 203, 300, 301, 302, and 303 facing each other. Thus, a first inflow passage Pa1 for supplying the first fluid a to the first flow passage Ra, a first outflow passage Pa2 for allowing the first fluid a to flow out from the first flow passage Ra, a second inflow passage Pb1 for supplying the second fluid B to the second flow passage Rb, and a second outflow passage Pb2 for allowing the second fluid B to flow out from the second flow passage Rb are formed.
In the heat exchanger 1 of the present embodiment, the portions of the adjacent heat transfer plates 2 and 3 that are in contact with each other are brazed to each other. Thereby, the plurality of heat transfer plates 2, 3 are integrally (mechanically) connected, and the facing surfaces (contact portions) of the adjacent heat transfer plates 2, 3 are sealed.
The heat exchanger 1 of the present embodiment is as described above. As shown in fig. 2, 7, and 11, the first fluid a flows from the first inflow passage Pa1 into the plurality of first passages Ra. The first fluid a flows in the second direction through each of the plurality of first flow paths Ra, and flows out to the first outflow path Pa 2. As shown in fig. 2, 7, and 12, the second fluid B flows from the second inflow path Pb1 into the plurality of second flow paths Rb. The second fluid B flows in the second direction through each of the plurality of second channels Rb and flows out to the second outflow channel Pb 2.
In the present embodiment, as shown in fig. 11, the first fluid a flows through the first flow path Ra around a diagonal line connecting the opposite corners of the heat transfer portions 20 and 30. As shown in fig. 12, the second fluid B flows through the second channel Rb around a diagonal line connecting the opposite corners of the heat transfer units 20 and 30, that is, another diagonal line different from the diagonal line serving as the center of flow of the first fluid a.
At this time, the first fluid a flowing through the first flow path Ra and the second fluid B flowing through the second flow path Rb exchange heat via the heat transfer plates 2 and 3 (heat transfer portions 20 and 30) that separate the first flow path Ra and the second flow path Rb. Thereby, the second fluid B is condensed or evaporated while flowing in the second direction in the second flow path Rb.
As described above, the heat exchanger 1 according to the present embodiment includes the heat transfer plates 2 and 3, the heat transfer plates 2 and 3 include the heat transfer portions 20 and 30, the heat transfer portions 20 and 30 overlap each other in the first direction, the heat transfer portions 20 and 30 include the first surfaces Sa1, Sb1 and the second surfaces Sa2 and Sb2, the first surfaces Sa1 and Sb1 have the convex strips 23 and 33 and the concave strips 22 and 32 formed thereon, the second surfaces Sa2 and Sb2 face the opposite sides of the first surfaces Sa1 and Sb1 and have the concave strips 22 and 32 and the convex strips 23 and 33 formed thereon, the concave strips 22 and 32 and the convex strips 23 and 33 of the first surfaces Sa1 and Sb1 are in front-back relation to each other, the convex strips 23 and 33 and the concave strips 22 and 32 of the first surfaces Sa1 and Sb1 are in front-back relation to each other, and the plurality of the heat transfer plates 2 and 3 have the first surfaces Sa 34 and Sb 85 of the heat transfer portions 20 and 30 and the first surfaces Sa 20 and Sb 3638 of the adjacent heat transfer plates 393 on one side in the first direction and the adjacent side of the first surfaces Sa2 and, Sb1 are opposed to each other, the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the heat transfer plates 2, 3 are opposed to the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the heat transfer plates 2, 3 arranged adjacent to each other on the other side in the first direction, a first flow path Ra for allowing the first fluid a to flow in the second direction orthogonal to the first direction is formed between the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3, a second flow path Rb for allowing the second fluid B to flow 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, each of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3 includes a plurality of first ridges 230, 330 as the ridges 23, 33 formed on the first surfaces Sa1, Sb1, the plurality of first ridges 230, 330 are arranged at intervals in a direction intersecting the first direction and the second direction, the plurality of first ridges 230, 330 are arranged at intervals, and the second ridges 230, and the first ridges are arranged at intervals, 330 extend in the second direction or in a combined direction including components of the second direction, and as the concave stripes 22, 32 formed on the first faces Sa1, Sb1, the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3 include a plurality of first concave stripes 220, 320, the plurality of first concave stripes 220, 320 are formed between the first convex stripes 230, 330, the first convex stripes 230, 330 are adjacent in a direction intersecting the first direction and the second direction, and as the concave stripes 22, 32 formed on the second faces Sa2, Sb2, the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3 include a plurality of second concave stripes 221, 321 in a front-back relationship with the first convex stripes 230, 330, and the heat transfer portions 20, 30 of at least one of the heat transfer plates 2, 3 of the adjacent heat transfer plates 2, 3 include at least one blocking convex stripe 231, 331 as the convex stripe Sb 23, Sb 23 formed on the first faces 1, Sb1, The stopper ribs 231 and 331 are lower in height than the first ribs 230 and 330 formed on the first surfaces Sa1 and Sb1, extend in a direction intersecting the first ribs 230 and 330, the first ribs 230 and 330 of the adjacent heat transfer plates 2 and 3 are positioned between the first ribs 230 and 330 of the opposite heat transfer plates 2 and 3, and the stopper ribs 231 and 331 of at least one of the heat transfer plates 2 and 3 are in cross abutment with the first ribs 230 and 330 of the opposite heat transfer plates 2 and 3.
According to the heat exchanger 1 having the above-described configuration, as shown in fig. 9 and 10, the blocking ridges 231 and 331 are present at the intermediate positions of the first flow paths Ra formed between the first surfaces Sa1 and Sb1 of the adjacent heat transfer portions 20 and 30 so as to protrude toward the heat transfer portions 20 and 30 of the opposite side. Accordingly, the barrier ribs 231 and 331 obstruct the flow of the first fluid a in the first flow path Ra, and increase the flow resistance of the first fluid a in the first flow path Ra.
In particular, according to the heat exchanger 1 of the present embodiment, the first ribs 230, 330 of the adjacent heat transfer plates 2, 3 are positioned between the first ribs 230, 330 of the opposite heat transfer plates 2, 3, and the blocking ribs 231, 331 of the heat transfer plates 2, 3 (the blocking ribs 231, 331 having a height lower than the first ribs 230, 330) are in cross-abutment with the first ribs 230, 330 of the opposite heat transfer plates 2, 3.
Therefore, the interval between the first surfaces Sa1, Sb1 of the adjacent heat transfer plates 2, 3 is narrowed. That is, the heat transfer plates 2 and 3 defining the first flow paths Ra are brought into close proximity to each other by the amount of projection of the blocking ridges 231 and 331 being smaller than the amount of projection of the first ridges 230 and 330. Accordingly, the flow path width of the first flow path Ra is narrowed, and as a result, the flow resistance of the first fluid a in the first flow path Ra is increased.
Therefore, in the heat exchanger 1 of the present embodiment, the flow resistance of the first fluid a is increased by the presence of the stopper ribs 231 and 331 and the flow path width of the first flow path Ra, and as a result, the chance of the first fluid a thermally affecting the heat transfer portions 20 and 30 is increased, and the heat conduction performance to the second fluid B side is improved.
On the other hand, since the plurality of second concave stripes 221, 321 in a front-back relationship with the first convex stripes 230, 330 and the concave stripes in a front-back relationship with the blocking convex stripes 231, 331 of the first surfaces Sa1, Sb1 are formed in the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the heat transfer plates 2, 3, there is no structure in the second flow path Rb formed between the second surfaces Sa2, Sb2 of the adjacent heat transfer plates 2, 3, which becomes a flow resistance of the second fluid B. 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.
Thus, even if a fluid that undergoes a phase change (a fluid of a two-phase flow including a liquid and a gas) is used as the second fluid B, the flow of the liquid film of the second fluid B formed on the surface of the heat transfer portions 20 and 30 is disturbed by the flow velocity of the second fluid B.
Therefore, in the heat exchanger 1 configured as described above, the heat conduction performance of the second fluid B flowing through the second flow path Rb with respect to the heat transfer portions 20 and 30 (the first fluid a side) is improved.
In the present embodiment, as shown in fig. 9 to 11, at least one of the heat transfer plates 2, 3 adjacent to each other includes the plurality of barrier ribs 231, 331 as the ribs 23, 33 formed on the first surfaces Sa1, Sb1, and the plurality of barrier ribs 231, 331 are arranged at intervals in the second direction, so that the flow resistance of the first fluid a can be increased in the first flow path Ra in accordance with the number of the plurality of barrier ribs 231, 331.
In the present embodiment, each of the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3 includes, as the ridges 23 and 33 formed on the second surfaces Sa2 and Sb2, a plurality of second ridges 233 and 333 that are in a front-back relationship with the first concave strips 220 and 320, and each of the second ridges 233 and 333 of the adjacent heat transfer plates 2 and 3 overlaps with the second ridge 233 and 333 of the opposite heat transfer plate 2 and 3 and contacts with the top of the second ridge 233 and 333 of the opposite heat transfer plate 2 and 3, and therefore, even when the flow pressure of the first fluid a flowing through the first flow path Ra acts on the heat transfer portion 20 or 30, the heat transfer portion 20 or 30 is not expanded. Therefore, a space constituting the second flow path Rb can be secured, and the smoothness of the flow of the second fluid B can be secured.
In the present embodiment, the stopper convex strips 231 and 331 have at least one curved convex strip portion 232 and 332, the curved convex strip portions 232 and 332 include a pair of inclined convex strip portions 232a and 232b, the pair of inclined convex strip portions 232a and 232b have a base end and a tip end located on the opposite side of the base end, are inclined in the opposite directions with respect to a center line extending in the second direction or an imaginary line parallel to the center line, and have tip ends connected to each other.
Thus, not only the entire barrier ribs 231 and 331 serve as the flow resistance of the first fluid a, but also the curved convex ridges 232 and 332 (the pair of inclined convex ridges 232a, 232b, 332a, and 332b) included in the barrier ribs 231 and 331 cause the first fluid a to diffuse in the first flow path Ra. Therefore, the area of the heat transfer portions 20, 30 that contributes to heat transfer increases. This improves the heat transfer performance of the first fluid a in the first flow path Ra.
In particular, the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3 respectively include the stopper ridges 231 and 331 having the curved convex portions 232 and 332, and the curved convex portions 232 and 332 of the stopper ridges 231 and 331 of the adjacent heat transfer plates 2 and 3 are formed by being curved in the opposite direction to each other.
Therefore, the inclined ridges 232a, 232b, 332a, 332b of the curved ridges 232, 332 intersect with each other (see fig. 11). Accordingly, the flow resistance of the first fluid a in the first flow path Ra increases, and the diffusion effect of the first fluid a improves. This improves the heat transfer performance of the first fluid a in the first flow path Ra.
Next, a plate heat exchanger according to a second embodiment of the present invention will be described. In the present embodiment, the same or equivalent structure as that of the first embodiment is given the same name as that of the first embodiment, and the same reference numerals are given thereto.
The plate heat exchanger according to the second embodiment (hereinafter, simply referred to as "heat exchanger") includes three or more heat transfer plates 2 and 3 as shown in fig. 13.
Three or more heat transfer plates 2, 3 are superposed in the first direction. The heat exchanger 1 of the present embodiment includes two types of heat transfer plates among the three or more heat transfer plates 2 and 3. The two types of heat transfer plates 2, 3 are alternately arranged in the first direction.
Accordingly, in the heat exchanger 1, the first flow path Ra through which the first fluid a flows and the second flow path Rb through which the second fluid B flows are alternately formed in the first direction with the heat transfer plates 2 and 3 as boundaries.
Here, the two heat transfer plates 2 and 3 will be specifically described. The two heat transfer plates 2, 3 have the same points and different points. First, the same points of the two heat transfer plates 2 and 3 will be described.
As shown in fig. 14 to 17, the heat transfer plates 2 and 3 include heat transfer portions 20 and 30, and annular fitting portions 21 and 31, wherein the heat transfer portions 20 and 30 include first surfaces Sa1 and Sb1 and second surfaces Sa2 and Sb2 facing opposite directions from the first surfaces Sa1 and Sb1, and the fitting portions 21 and 31 extend from the entire circumferential direction of the outer peripheral edges of the heat transfer portions 20 and 30 in a direction intersecting the surfaces of the heat transfer portions 20 and 30.
The heat transfer portions 20, 30 have a thickness in the first direction. Accordingly, the first faces Sa1, Sb1 and the second faces Sa2, Sb2 of the heat transfer portions 20, 30 are aligned in the first direction. The outer shape (contour) of the heat transfer portions 20, 30 is defined by a pair of long sides extending in a second direction orthogonal to the first direction and a pair of short sides; the pair of short sides are arranged at intervals in the second direction, and extend in a third direction orthogonal to the first direction and the second direction, respectively, and are connected to the pair of long sides. That is, the outer shape of the heat transfer portions 20 and 30 as viewed in the first direction is a rectangle having long sides in the second direction.
The heat transfer portions 20 and 30 have one end portion and the other end portion located on the opposite side of the one end portion in the second direction. Heat transfer portions 20 and 30 have at least two openings 200, 201, 202, 203, 300, 301, 302, and 303 at one end portion and the other end portion in the second direction, respectively. In the present embodiment, the heat transfer portions 20 and 30 have two openings 200, 203, 300, and 303 at one end in the second direction, and two openings 201, 202, 301, and 302 at the other end in the second direction.
The two openings 200, 203, 300, 303 located at one end of the heat transfer portions 20, 30 in the second direction are juxtaposed in the third direction. The two openings 201, 202, 301, 302 located at the other end portions of the heat transfer portions 20, 30 in the second direction are juxtaposed in the third direction.
The peripheries of the openings 200 and 300 located at one end and the peripheries of the openings 201 and 301 located at the other end of the heat transfer units 20 and 30 in the second direction are recessed toward the first surfaces Sa1 and Sb 1. Accordingly, the peripheries of the openings 200 and 300 located at one end and the peripheries of the openings 201 and 301 located at the other end of the heat transfer units 20 and 30 in the second direction bulge toward the second surfaces Sa2 and Sb 2.
The amount of projection of the peripheries of the openings 200, 300 on the one side of the one end portion and the openings 201, 301 on the other end portion of the heat transfer portions 20, 30 toward the second surfaces Sa2, Sb2 is set so as to be able to contact the peripheries of the openings 200, 201, 300, 301 (the openings 200, 300 on the one side of the one end portion and the openings 201, 301 on the other end portion) of the heat transfer portions 20, 30 of the heat transfer plates 2, 3 arranged adjacent to each other in the first direction.
On the other hand, the peripheries of the openings 203 and 303 on the other side of one end and the peripheries of the openings 202 and 302 on the other side of the other end of the heat transfer units 20 and 30 in the second direction are recessed on the second surfaces Sa2 and Sb2 sides. Accordingly, the peripheries of the openings 203 and 303 on the other side of one end and the peripheries of the openings 202 and 302 on the other side of the other end of the heat transfer portions 20 and 30 in the second direction bulge out toward the first surfaces Sa1 and Sb 1.
The amount of bulging of the periphery of the other side opening 203, 303 of one end portion of the heat transfer portion 20, 30 in the second direction and the periphery of the other side opening 202, 302 of the other end portion toward the first surface Sa1, Sb1 side is set so as to be able to contact the periphery (bulged portion) of the periphery (of the openings 202, 203, 302, 303 of the heat transfer portions 20, 30 (of the other side opening 202, 302 of one end portion and the other side opening 203, 303 of the other end portion) of the heat transfer portions 20, 3 arranged adjacent to each other in the first direction. In fig. 14 to 17, in order to clarify the concave-convex relationship between the first surfaces Sa1, Sb1 and the second surfaces Sa2, Sb2, the regions recessed around the openings 200, 201, 202, 203, 300, 301, 302, 303 and the bottoms of the concave stripes 22, 32 described later are marked with dots.
In the present embodiment, the openings 200 and 300 located on one side of one end portion of the heat transfer portions 20 and 30 in the second direction and the openings 201 and 301 located on the other end portion are located at diagonal positions in accordance with the relationship with the state where the heat transfer plates 2 and 3 are superimposed. Further, the opening 203, 303 on the other side of one end portion of the heat transfer portion 20, 30 in the second direction and the opening 202, 302 on the other side of the other end portion are located at diagonal positions.
The first faces Sa1, Sb1 and the second faces Sa2, Sb2 of the heat transfer portions 20, 30 are respectively formed with concave stripes 22, 32 and convex stripes 23, 33. The first faces Sa1, Sb1 and the second faces Sa2, Sb2 of the heat transfer portions 20, 30 have a plurality of (a plurality of) concave stripes 22, 32 and convex stripes 23, 33, respectively.
More specifically, the heat transfer plates 2 and 3 are formed by press forming a metal plate. Accordingly, the concave stripes 22, 32 formed on the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 and the convex stripes 23, 33 formed on the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 are in a front-back relationship with each other. The convex strips 23, 33 formed on the first surfaces Sa1, Sb1 of the heat transfer units 20, 30 and the concave strips 22, 32 formed on the second surfaces Sa2, Sb2 of the heat transfer units 20, 30 are in a front-back relationship. That is, the concave portions 22 and 32 formed on the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30 are formed at positions corresponding to the convex portions 23 and 33 formed on the second surfaces Sa2 and Sb2 of the heat transfer portions 20 and 30 by deformation of the metal plate in accordance with press forming. Further, the convex strips 23, 33 formed on the first surfaces Sa1, Sb1 of the heat transfer sections 20, 30 are formed at positions corresponding to the concave strips 22, 32 formed on the second surfaces Sa2, Sb2 of the heat transfer sections 20, 30 by deformation of the metal plate accompanying press forming.
As shown in fig. 14 and 16, the heat transfer portions 20 and 30 include, as the concave stripes 22 and 32 formed on the first faces Sa1 and Sb1, a plurality of first concave stripes 220 and 320 extending in the second direction, respectively, and the plurality of first concave stripes 220 and 320 are arranged at intervals in the third direction. Further, the heat transfer portions 20 and 30 have a plurality of first ridges 230 and 330 as the ridges 23 and 33 formed on the first faces Sa1 and Sb1, and the plurality of first ridges 230 and 330 extend in the second direction between the first concave stripes 220 and 320 adjacent to each other in the third direction. That is, in the first faces Sa1, Sb1 of the heat transfer portions 20, 30, the first concave stripes 220, 320 and the first convex stripes 230, 330 are alternately arranged in the third direction.
The heat transfer portions 20 and 30 have at least one rib 231 and 331 for blocking, which is the rib 23 and 33 formed on the first face Sa1 and Sb1, and the rib 231 and 331 for blocking is lower in height than the first ribs 230 and 330 formed on the first face Sa1 and Sb1 and extends in a direction intersecting the plurality of first ribs 230 and 330.
The widths of the first concave strips 220, 320 in the third direction and the widths of the first convex strips 230, 330 in the third direction are the same or substantially the same. The inner surface defining the first concave strip 220, 320 is continuous with the outer surface defining the first convex strip 230, 330. Thereby, the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 are formed in a wavy shape undulating in the first direction.
On the premise of this, in the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30, the boundaries between the specific first concave stripes 220, 320 of the plurality of first concave stripes 220, 320 and the specific first convex stripes 230, 330 of the plurality of first convex stripes 230, 330 are located on the longitudinal center line CL, and the specific first convex stripes 230, 330 are the first convex stripes 230, 330 adjacent to the specific first concave stripes 220, 320.
That is, the specific first concave stripes 220, 320 or the specific first convex stripes 230, 330 are arranged to be offset from the longitudinal centerline CL in the third direction by the following distances: the distance 1/4 between the first convex strips 230, 330 adjacent to each other across one first concave strip 220, 320 or the distance 1/4 between the first concave strips 220, 320 adjacent to each other across one first convex strip 230, 330.
In the present embodiment, the heat transfer units 20 and 30 have the plurality of stopper ribs 231 and 331 on the first surfaces Sa1 and Sb 1. The plurality of stopper ribs 231 and 331 are arranged at intervals in the second direction. As described above, the plurality of barrier ribs 231 and 331 are lower in height than the first ribs 230 and 330, respectively. Specifically, the amount of projection of the blocking ribs 231, 331 from an imaginary plane (an imaginary plane developed in the second direction and the third direction) passing through the tops of the plurality of second ribs 233, 333 described later formed on the second surfaces Sa2, Sb2 is smaller than the amount of projection of the first ribs 230, 330. Accordingly, the top portions of the barrier ribs 231 and 331 are located on the second surface side in the first direction with respect to the top portions of the first ribs 230 and 330. That is, the top of the barrier ribs 231, 331 is located between the top of the first ribs 230, 330 and the bottom of the first concave ribs 220, 320.
In the present embodiment, the first ridges 230, 330 of the other heat transfer plate 2, 3 of the adjacent heat transfer plates 2, 3 are positioned between the first ridges 230, 330 of the one heat transfer plate 2, 3 of the adjacent heat transfer plates 2, 3 (positions corresponding to the first concave ridges 220, 320) in a state where the plurality of heat transfer plates 2, 3 are stacked.
Accordingly, the distance (distance) between the top of the first convex rib 230, 330 and the top of the stopper convex rib 231, 331 in the first direction is set so that the distance between the first convex rib 230, 330 of one heat transfer plate 2, 3 and the first concave rib 220, 320 of the other heat transfer plate 2, 3 of the adjacent heat transfer plates 2, 3 is a distance at which the first fluid a can be ensured to flow.
Specifically, in the present embodiment, the plurality of first concave stripes 220, 320 are set to have the same width, and the plurality of first convex stripes 230, 330 are set to have the same width in the heat transfer plates 2, 3. In each of the heat transfer plates 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.
Accordingly, if the first convex rib 230, 330 of one heat transfer plate 2, 3 of the adjacent heat transfer plates 2, 3 is too close to the first concave rib 220, 320 of the other heat transfer plate 2, 3 of the adjacent heat transfer plates 2, 3, the gap between both sides in the width direction of the first convex rib 230, 330 and both sides in the width direction of the first concave rib 220, 320 disappears or becomes extremely narrow compared to the gap formed between the top of the first convex rib 230, 330 and the bottom of the first concave rib 220, 320.
Therefore, in the present embodiment, the interval (distance) between the top of the first convex stripes 230, 330 and the top of the stopper convex stripes 231, 331 in the first direction is set so that the interval between both sides in the width direction of the first convex stripes 230, 330 and both sides in the width direction of the first concave stripes 220, 320 becomes an interval at which the flow of the first fluid a can be ensured.
In the present embodiment, the barrier ribs 231 and 331 intersect the plurality of first ribs 230 and 330 and the first concave ribs 220 and 320. In the present embodiment, the barrier ribs 231 and 331 extend in the third direction. The length of the stopper ribs 231 and 331 is set to be shorter than the entire length of the heat transfer portions 20 and 30 in the third direction. That is, the length of the barrier ribs 231, 331 is set to a length that intersects with the first ribs 230, 330 and the first concave stripes 220, 320, the number of which is less than the total number of the plurality of first ribs 230, 330 and the first concave stripes 220, 320 arranged over the entire length of the heat transfer portions 20, 30 in the third direction.
More specifically, the length of the barrier ribs 231 and 331 in the extending direction (longitudinal direction) is set to be equal to or less than 1/2 of the total length of the heat transfer portions 20 and 30 in the third direction. In the present embodiment, the length of the barrier ribs 231, 331 in the extending direction (longitudinal direction) is set to be equal to or less than 1/3 of the total length of the heat transfer portions 20, 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 equal to or less than 1/3 of the total length of the heat transfer unit 20 and 30 in the third direction, and accordingly, in the first surface Sa1 and Sb1 of the heat transfer unit 20 and 30, a plurality of barrier ribs 231 and 331 arranged at intervals in the second direction are arranged in a plurality of rows at intervals in the third direction. That is, in the first surfaces Sa1, Sb1 of the heat transfer units 20, 30, the plurality of barrier ribs 231, 331 are arranged in a matrix.
The number and positions of the barrier ribs 231, 331 in each row correspond to each other. Accordingly, the barrier ribs 231 and 331 corresponding to different rows are aligned in a row in the third direction.
Here, the interval between the rows of the adjacent barrier ribs 231, 331 (the interval between the barrier ribs 231, 331 adjacent in the third direction) is set to be equal to or less than the length of the extending direction (longitudinal direction) of the single barrier rib 231, 331. In the present embodiment, the interval between the rows of the adjacent barrier ribs 231, 331 (the interval between the barrier ribs 231, 331 adjacent in the third direction) is set to be smaller than the length of the single barrier rib 231, 331 in the extending direction (longitudinal direction).
As described above, the length of the barrier ribs 231, 331 in the extending direction (longitudinal direction) is set to be equal to or less than 1/3 (equal to or less than 1/2 in the present embodiment) of the entire length of the heat transfer unit 20, 30 in the third direction, and accordingly, the first concave stripes 220, 320 and the first convex stripes 230, 330 continuous in the second direction and the first concave stripes 220, 320 and the first convex stripes 230, 330 cut at a plurality of positions in the second direction by the barrier ribs 231, 331 are included in the first concave stripes 220, 320 and the first convex stripes 230, 330 on the first surface Sa1, Sb1 of the heat transfer unit 20, 30. At least one end of the first concave strips 220, 320 and the first convex strips 230, 330 which are cut off is connected with the convex strips 231, 331 for stopping.
In the present embodiment, the cut first concave stripes 220 and 320 are arranged in the second direction. Accordingly, the cut first ribs 230 and 330 are also aligned in the second direction.
As shown in fig. 15 and 17, the heat transfer portions 20 and 30 include a plurality of second concave stripes 221 and 321 extending in the second direction as the concave stripes 22 and 32 formed on the second surfaces Sa2 and Sb2, respectively, and the plurality of second concave stripes 221 and 321 are arranged at intervals in the third direction. Further, the heat transfer portions 20 and 30 include, as the convex strips 23 and 33 formed on the second surfaces Sa2 and Sb2, a plurality of second convex strips 233 and 333, and the plurality of second convex strips 233 and 333 are formed to extend in the second direction between the second concave strips 221 and 321 adjacent to each other in the third direction. That is, in the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30, the second concave stripes 221, 321 and the second convex stripes 233, 333 are alternately arranged in the third direction.
The heat transfer units 20 and 30 include concave stripes (hereinafter, referred to as "back-side concave stripes") 222 and 322 on the back side of the barrier ribs 231 and 331 formed on the first surfaces Sa1 and Sb1 as the concave stripes 22 and 32 formed on the second surfaces Sa2 and Sb 2.
The second concave stripes 221, 321 are concave stripes 22, 32 formed on the back side of the first convex stripes 230, 330 on the first faces Sa1, Sb 1. Along with this, the second concave strips 221, 321 extend in the second direction. The second convex strips 233, 333 are convex strips 23, 33 formed on the back side of the first concave strips 220, 320 on the first faces Sa1, Sb 1. Accordingly, the second protrusions 233, 333 extend in the second direction.
The inner surfaces defining the second concave strips 221, 321 are continuous with the outer surfaces defining the second convex strips 233, 333. Thereby, the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 are formed in a wavy shape undulating in the third direction.
The back surface side concave strips 222, 322 and the barrier convex strips 231, 331 are formed in the same manner except that the concave-convex relationship is reversed.
In the present embodiment, the back-side concave strips 222, 322 intersect the plurality of second convex strips 233, 333 and the second concave strips 221, 321. In the present embodiment, the length of the back surface side concave strips 222, 322 is set to be shorter than the entire length of the heat transfer portions 20, 30 in the third direction. That is, the length of the back-side concave strips 222, 322 is set to a length that intersects the number of the second convex strips 233, 333 and the second concave strips 221, 321 that is less than the total number of the plurality of second convex strips 233, 333 and the second concave strips 221, 321 that are arranged over the entire length of the heat transfer portions 20, 30 in the third direction.
More specifically, the length of the back-side concave strips 222, 322 in the extending direction (longitudinal direction) is set to be equal to or less than 1/2 of the total length of the heat transfer portions 20, 30 in the third direction. In the present embodiment, the length of the back-side concave strips 222, 322 in the extending direction (longitudinal direction) is set to be equal to or less than 1/3 of the total length of the heat transfer portions 20, 30 in the third direction.
As described above, the length of the back-side concave strips 222, 322 in the extending direction (longitudinal direction) is set to be equal to or less than 1/3 of the total length of the heat transfer unit 20, 30 in the third direction, and accordingly, a plurality of rows of the back-side concave strips 222, 322 arranged at intervals in the second direction are provided at intervals in the third direction on the second surface Sa2, Sb2 of the heat transfer unit 20, 30. That is, in the second surfaces Sa2, Sb2 of the heat transfer units 20, 30, the plurality of back surface side concave stripes 222, 322 are arranged in a matrix.
The number and position of the back side concave strips 222, 322 of each row correspond. Accordingly, the back-side concave stripes 222, 322 corresponding to different rows are aligned in a row in the third direction.
Here, the interval between the rows of the adjacent back-side concave strips 222, 322 (the interval between the adjacent back-side concave strips 222, 322 in the third direction) is set to be equal to or less than the length in the extending direction (longitudinal direction) of the single back-side concave strip 222, 322. In the present embodiment, the interval between the rows of adjacent back-side concave stripes 222, 322 (the interval between the back-side concave stripes 222, 322 adjacent in the third direction) is set smaller than the length of the single back-side concave stripe 222, 322 in the extending direction (longitudinal direction).
As described above, the length of the back-side concave strips 222, 322 in the extending direction (longitudinal direction) is set to be equal to or less than 1/3 (equal to or less than 1/2 in the present embodiment) of the total length of the heat transfer portions 20, 30 in the third direction, and along with this, the second concave strips 221, 321 and the second convex strips 233, 333 on the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 include ones that are continuous in the second direction and are cut at a plurality of positions in the second direction by the back-side concave strips 222, 322. At least one end of the second concave strips 221, 321 and the second convex strips 233, 333 which are cut off is connected to the back-side concave strips 222, 322. That is, the cut second concave strips 221, 321 are opened into the back-side concave strips 222, 322.
In the present embodiment, the cut second concave stripes 221 and 321 are arranged in the second direction. Accordingly, the cut second ridges 233, 333 are also aligned in the second direction.
The common point of the two heat transfer plates 2 and 3 is as described above. Next, the difference between the two heat transfer plates 2 and 3 will be described.
As shown in fig. 14 and 16, the first ridges 230 on the first surface Sa1 of one of the two heat transfer plates 2, 3 (hereinafter referred to as "first heat transfer plate") 2 are arranged to be offset from the first ridges 330 on the first surface Sb1 of the other of the two heat transfer plates 2, 3 (hereinafter referred to as "second heat transfer plate") 3 in the third direction. That is, in a state where 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 face each other, the arrangement of the first concave stripes 220, 320 and the first convex stripes 230, 330 is set such that the first convex stripes 230 of the first heat transfer plate 2 correspond to the first concave stripes 320 of the second heat transfer plate 3, and the first convex stripes 330 of the second heat transfer plate 3 correspond to the first concave stripes 220 of the first heat transfer plate 2.
In the present embodiment, the number and arrangement of the blocking ridges 231 and 331 on the first surfaces Sa1 and Sb1 are different between the first heat transfer plate 2 and the second heat transfer plate 3. That is, in the first heat transfer plate 2 and the second heat transfer plate 3, the number of rows of the blocking projections 231 and 331 on the first surface Sa1 and Sb1 is different from the arrangement of the blocking projections 231 and 331 in each row.
Specifically, in the first surface Sa1 of the first heat transfer plate 2, the number of rows of the blocking ridges 331 arranged at intervals in the third direction in the first surface Sb1 of the second heat transfer plate 3 is one less than the number of rows of the blocking ridges 231 arranged at intervals in the third direction. In addition, the number of the dam beads 231 in each row in the first surface Sb1 of the second heat transfer plate 3 is one less than the number of the dam beads 231 in each row in the first surface Sa1 of the first heat transfer plate 2.
Accordingly, the positions of the rows of the blocking ridges 231 of the first surface Sa1 of the first heat transfer plate 2 correspond to the positions between the rows of the blocking ridges 331 of the first surface Sb1 of the second heat transfer plate 3, and the positions of the rows of the blocking ridges 331 of the first surface Sb1 of the second heat transfer plate 3 correspond to the positions between the rows of the blocking ridges 231 of the first surface Sa1 of the first heat transfer plate 2. The dam beads 231 in each row of the first surface Sa1 of the first heat transfer plate 2 correspond to the dam beads 331 in each row of the first surface Sb1 of the second heat transfer plate 3 (intermediate positions of the adjacent dam beads 331 in the second direction), and the dam beads 331 in each row of the first surface Sb1 of the second heat transfer plate 3 correspond to the dam beads 231 in each row of the first surface Sa1 of the first heat transfer plate 2 (intermediate positions of the adjacent dam beads 231 in the second direction).
In the first heat transfer plate 2, as shown in fig. 14, the fitting portion 21 extends toward the first surface Sa1 of the heat transfer portion 20. In the second heat transfer plate 3, as shown in fig. 17, the fitting portion 31 extends toward the second surface Sb2 of the heat transfer portion 30.
The heat transfer plates 2 and 3 (the first heat transfer plate 2 and the second heat transfer plate 3) are as described above. As shown in fig. 13, the heat transfer plates 2 and 3 (the first heat transfer plate 2 and the second heat transfer plate 3) are stacked in the first direction. In the present embodiment, the first heat transfer plates 2 and the second heat transfer plates 3 are alternately stacked in the first direction. At this time, the plurality of heat transfer plates 2, 3 have the first surfaces Sa1, Sb1 of their own heat transfer portions 20, 30 facing the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 of the heat transfer plates 2, 3 arranged adjacent to each other on one side in the first direction, respectively. The plurality of heat transfer plates 2, 3 have the second surfaces Sa2, Sb2 of their own heat transfer portions 20, 30 facing the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the heat transfer plates 2, 3 arranged adjacent to each other on the other side in the first direction.
As a result, as shown in fig. 13 and 18, a first flow path Ra through which the first fluid a flows in the second direction and a second flow path Rb through which the second fluid B flows in the second direction are alternately formed between the heat transfer portions 20 and 30 of the heat transfer plates 2 and 3. That is, the first flow path Ra through which the first fluid a flows is formed between the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3, and the second flow path Rb through which the second fluid B flows is formed between the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3.
In this state, as shown in fig. 13, the openings 200, 201, 202, 203, 300, 301, 302, 303 at the corresponding positions in the heat transfer portions 20, 30 are connected in the first direction. Further, the portions bulging toward the opposite sides are in contact with the peripheries of the openings 200, 201, 202, 203, 300, 301, 302, 303 facing each other. As a result, a first inflow passage Pa1 for supplying the first fluid a to the first flow path Ra, a first outflow passage Pa2 for allowing the first fluid a to flow out from the first flow path Ra, a second inflow passage Pb1 for supplying the second fluid B to the second flow path Rb, and a second outflow passage Pb2 for allowing the second fluid B to flow out from the second flow path Rb are formed.
More specifically, when a plurality of heat transfer plates 2 and 3 are superposed, one first heat transfer plate 2 and one second heat transfer plate 3 are superposed to form a set. When a plurality of such sets are superposed, every other set is rotated by 180 degrees around an imaginary line extending in the first direction and superposed. In this state, the fitting portions 21, 31 of one of the heat transfer plates 2, 3 (the first heat transfer plate 2 or the second heat transfer plate 3) adjacent in the first direction are fitted to the fitting portions 21, 31 of the other of the heat transfer plates 2, 3 (the first heat transfer plate 2 or the second heat transfer plate 3) adjacent in the first direction.
As a result, as shown in fig. 19 and 22, on the first surfaces Sa1, Sb1 sides of the adjacent heat transfer plates 2, 3, the first ridges 230 of the first heat transfer plate 2 (heat transfer portion 20) face the first grooves 320 of the second heat transfer plate (heat transfer portion 30), and the first grooves 220 of the first heat transfer plate 2 (heat transfer portion 20) face the first ridges 330 of the second heat transfer plate (heat transfer portion 30).
In the first heat transfer plate 2, the barrier ribs 231 are lower in height than the first ribs 230, and in the second heat transfer plate 3, the barrier ribs 331 are lower in height than the first ribs 330, so the barrier ribs 231 of the first heat transfer plate 2 cross and abut the first ribs 330 of the second heat transfer plate 3, and the barrier ribs 331 of the second heat transfer plate 3 cross and abut the first ribs 230 of the first heat transfer plate 2.
On the second surfaces Sa2, Sb2 sides of the adjacent heat transfer plates 2, 3, the second ridges 233 of the first heat transfer plate 2 (heat transfer portion 20) face the second ridges 333 of the second heat transfer plate (heat transfer portion 30), and the second concave ridges 221 of the first heat transfer plate 2 (heat transfer portion 20) face the second concave ridges 321 of the second heat transfer plate (heat transfer portion 30). That is, in the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 of the first heat transfer plate 2 and the second heat transfer plate 3, the boundaries of the specific first concave strips 220, 320 of the plurality of first concave strips 220, 320 and the specific first convex strips 230, 330 of the plurality of first convex strips 230, 330 are located on the vertical center line CL, and therefore, as described above, the second convex strips 233, 333 of the adjacent heat transfer plates 2, 3 are opposed to each other by rotating the first heat transfer plate 2 and the second heat transfer plate 3 by 180 °, and the tops of the first convex strips 230, 330 adjacent to the specific first concave strips 220, 320 are brought into contact with each other.
As a result, as shown in fig. 13, a first flow path Ra for allowing the first fluid a to flow in a second direction orthogonal to the first direction is formed between the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3. Further, a second flow path Rb for allowing the second fluid B to flow 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.
As described above, the plurality of heat transfer plates 2 and 3 are overlapped in the first direction, and thus the openings 200, 201, 202, 203, 300, 301, 302, 303 located at the corresponding positions of the heat transfer portions 20 and 30 are connected in the first direction. Further, the portions bulging toward the opposite sides are in contact with the peripheries of the openings 200, 201, 202, 203, 300, 301, 302, 303 facing each other. Thus, a first inflow passage Pa1 for supplying the first fluid a to the first flow path Ra, a first outflow passage Pa2 for allowing the first fluid a to flow out from the first flow path Ra, a second inflow passage Pb1 for supplying the second fluid B to the second flow path Rb, and a second outflow passage Pb2 for allowing the second fluid B to flow out from the second flow path Rb are formed.
In the heat exchanger 1 of the present embodiment, the portions of the adjacent heat transfer plates 2 and 3 that are in contact with each other are brazed to each other. Thereby, the plurality of heat transfer plates 2, 3 are integrally (mechanically) connected, and the facing surfaces (contact portions) of the adjacent heat transfer plates 2, 3 are sealed.
The heat exchanger 1 of the present embodiment is as described above. As shown in fig. 13, 18, and 23, the first fluid a flows from the first inflow passage Pa1 into the plurality of first passages Ra. The first fluid a flows through each of the plurality of first flow paths Ra in the second direction, and flows out to the first outflow path Pa 2. As shown in fig. 13, 18, and 24, the second fluid B flows from the second inflow passages Pb1 into the plurality of second passages Rb. The second fluid B flows in the second direction through each of the plurality of second channels Rb and flows out to the second outflow channel Pb 2.
In the present embodiment, as shown in fig. 23, the first fluid a flows through the first flow path Ra around a diagonal line connecting the opposite corners of the heat transfer portions 20 and 30. As shown in fig. 24, the second fluid B flows through the second channel Rb around another diagonal line that connects the opposite corners of the heat transfer units 20 and 30 and is different from the diagonal line that becomes the center of the flow of the first fluid a.
At this time, the first fluid a flowing through the first flow path Ra and the second fluid B flowing through the second flow path Rb exchange heat through the heat transfer plates 2 and 3 (heat transfer portions 20 and 30) that separate the first flow path Ra and the second flow path Rb. Thereby, the second fluid B is condensed or evaporated while flowing in the second direction in the second flow path Rb.
As described above, the heat exchanger 1 according to the present embodiment includes the heat transfer plates 2 and 3, the heat transfer plates 2 and 3 each having the heat transfer portions 20 and 30, the heat transfer portions 20 and 30 being overlapped with each other in the first direction, the heat transfer portions 20 and 30 having the first surfaces Sa1, Sb1 and the second surfaces Sa2 and Sb2, wherein the first surfaces Sa1 and Sb1 have the convex strips 23 and 33 and the concave strips 22 and 32 formed thereon, the second surfaces Sa 3 and Sb2 are directed to the opposite side with respect to the first surfaces Sa1 and Sb1, the concave strips 22 and 32 and the convex strips 23 and 33 are formed thereon, the concave strips 22 and 32 are in front-back relationship with the convex strips 23 and 33 of the first surfaces Sa1 and Sb1, the convex strips 23 and 33 are in front-back relationship with the concave strips 22 and 32 of the first surfaces Sa1 and Sb1, and the plurality of heat transfer plates 2 and 3 have the first surfaces Sa 34 and Sb 85 of the heat transfer portions 20 and Sb 30 and the first surfaces Sa 38 of the adjacent heat transfer plates 1 and 30 arranged on one side of the first direction, respectively, Sb1 are opposed to each other, the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the heat transfer plates 2, 3 are opposed to the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the heat transfer plates 2, 3 arranged adjacent to each other on the other side in the first direction, a first flow path Ra for allowing the first fluid a to flow in the second direction orthogonal to the first direction is formed between the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3, a second flow path Rb for allowing the second fluid B to flow 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, each of the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3 includes a plurality of first ridges 230, 330 as the ridges 23, 33 formed on the first surfaces Sa1, Sb1, the plurality of first ridges 230, 330 are arranged at intervals in a direction intersecting the first direction and the second direction, the plurality of first ridges 230, 330 are arranged at intervals, 330 extend in the second direction or in a combined direction including components of the second direction, and as the concave stripes 22, 32 formed on the first faces Sa1, Sb1, the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3 include a plurality of first concave stripes 220, 320, the plurality of first concave stripes 220, 320 are formed between the first convex stripes 230, 330, the first convex stripes 230, 330 are adjacent in a direction intersecting the first direction and the second direction, and as the concave stripes 22, 32 formed on the second faces Sa2, Sb2, the heat transfer portions 20, 30 of the adjacent heat transfer plates 2, 3 include a plurality of second concave stripes 221, 321 in a front-back relationship with the first convex stripes 230, 330, and the heat transfer portions 20, 30 of at least one of the heat transfer plates 2, 3 of the adjacent heat transfer plates 2, 3 include at least one blocking convex stripe 231, 331 as the convex stripe Sb 23, Sb 23 formed on the first faces 1, Sb1, The stopper ribs 231 and 331 are lower in height than the first ribs 230 and 330 formed on the first surfaces Sa1 and Sb1, extend in a direction intersecting the first ribs 230 and 330, the first ribs 230 and 330 of the adjacent heat transfer plates 2 and 3 are positioned between the first ribs 230 and 330 of the opposite heat transfer plates 2 and 3, and the stopper ribs 231 and 331 of at least one of the heat transfer plates 2 and 3 are in cross abutment with the first ribs 230 and 330 of the opposite heat transfer plates 2 and 3.
According to the heat exchanger 1 having the above-described configuration, as shown in fig. 20 to 22, the blocking ridges 231 and 331 are present in a state of protruding toward the heat transfer portions 20 and 30 of the opposite side at the intermediate positions of the first flow path Ra formed between the first surfaces Sa1 and Sb1 of the adjacent heat transfer portions 20 and 30. Accordingly, the barrier ribs 231 and 331 obstruct the flow of the first fluid a in the first flow path Ra, and increase the flow resistance of the first fluid a in the first flow path Ra.
In particular, according to the heat exchanger 1 of the present embodiment, the first ribs 230, 330 of the adjacent heat transfer plates 2, 3 are positioned between the first ribs 230, 330 of the opposite heat transfer plates 2, 3, and the blocking ribs 231, 331 of the heat transfer plates 2, 3 (the blocking ribs 231, 331 having a height lower than the first ribs 230, 330) are in cross-abutment with the first ribs 230, 330 of the opposite heat transfer plates 2, 3.
Therefore, the interval between the first surfaces Sa1, Sb1 of the adjacent heat transfer plates 2, 3 is narrowed. Namely, the following states are achieved: the heat transfer plates 2 and 3 defining the first flow path Ra are close to each other by the amount by which the blocking ribs 231 and 331 protrude less than the amount by which the first ribs 230 and 330 protrude. As a result, the flow path width of the first flow path Ra is reduced, and as a result, the flow resistance of the first fluid a in the first flow path Ra is increased.
Therefore, in the heat exchanger 1 of the present embodiment, the flow resistance of the first fluid a is increased by the presence of the stopper ribs 231 and 331 and the flow path width of the first flow path Ra, and as a result, the chance of the first fluid a thermally affecting the heat transfer portions 20 and 30 is increased, and the heat conduction performance toward the second fluid B side is improved.
On the other hand, since the plurality of second concave stripes 221, 321 that are in a front-back relationship with the first convex stripes 230, 330 are formed in the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of the heat transfer plates 2, 3, and the concave stripes that are in a front-back relationship with the stopper convex stripes 231, 331 of the first surfaces Sa1, Sb1 are formed, there is no structure that serves as flow resistance of the second fluid B in the second flow path Rb formed between the second surfaces Sa2, Sb2 of the adjacent heat transfer plates 2, 3. 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.
Thus, even if a fluid that undergoes a phase change (a fluid that becomes a two-phase flow including a liquid and a gas) is used as the second fluid B, the flow of the liquid film of the second fluid B formed on the surface of the heat transfer portions 20, 30 is disturbed by the flow velocity of the second fluid B.
Therefore, in the heat exchanger 1 configured as described above, the heat conduction performance of the second fluid B flowing through the second flow path Rb to the heat transfer portions 20 and 30 (the first fluid a side) is improved.
In the present embodiment, as shown in fig. 20 to 23, at least one of the heat transfer plates 2, 3 adjacent to each other includes the plurality of barrier ribs 231, 331 as the ribs 23, 33 formed on the first surfaces Sa1, Sb1, and the plurality of barrier ribs 231, 331 are arranged at intervals in the second direction, so that the flow resistance of the first fluid a can be increased in the first flow path Ra in accordance with the number of the plurality of barrier ribs 231, 331.
In the present embodiment, each of the heat transfer portions 20 and 30 of the adjacent heat transfer plates 2 and 3 includes, as the ridges 23 and 33 formed on the second surfaces Sa2 and Sb2, a plurality of second ridges 233 and 333 that are in a front-back relationship with the first concave strips 220 and 320, and each of the second ridges 233 and 333 of the adjacent heat transfer plates 2 and 3 overlaps with the second ridge 233 and 333 of the opposite heat transfer plate 2 and 3 and contacts with the top of the second ridge 233 and 333 of the opposite heat transfer plate 2 and 3, and therefore, even when the flow pressure of the first fluid a flowing through the first flow path Ra acts on the heat transfer portion 20 or 30, the heat transfer portion 20 or 30 is not expanded. Therefore, a space for forming the second channel Rb can be secured, and the second fluid B can be smoothly circulated.
In the present embodiment, the plurality of barrier ribs 231 and 331 extending in the third direction are disposed at intervals in the second direction in the first surfaces Sa1 and Sb1 of the heat transfer portions 20 and 30, and the plurality of barrier ribs 231 and 331 are shorter than the entire length of the heat transfer portions 20 and 30 in the third direction, so that the first fluid a flows through the first flow path Ra while avoiding the barrier ribs 231 and 331 which become resistance. Thereby, the first fluid a is diffused in the first flow path Ra. Therefore, the area of the heat transfer portions 20, 30 that contributes to heat transfer increases. This improves the heat transfer performance of the first fluid a in the first flow path Ra.
In particular, since the dam beads 231 and 331 are provided on the first surfaces Sa1 and Sb1 of the adjacent heat transfer plates 2 and 3, and the dam beads 231 and 331 of the adjacent heat transfer plates 2 and 3 are arranged at positions shifted in the second direction, the first flow path Ra is not blocked by the dam beads 231 and 331, and the diffusibility of the first fluid a in the first flow path Ra is improved.
Further, in the first surfaces Sa1, Sb1 of the adjacent heat transfer plates 2, 3, the plurality of barrier ribs 231, 331 are arranged in a matrix, and the barrier ribs 231, 331 of the adjacent heat transfer plates 2, 3 are arranged at positions shifted from each other in the second direction and the third direction, so that the first flow path Ra is not blocked by the barrier ribs 231, 331, and the diffusibility of the first fluid a in the first flow path Ra is further improved.
The present invention is not limited to any of the above embodiments, and it is needless to say that appropriate modifications can be added within a range not departing from the gist of the present invention.
In the above embodiments, the adjacent heat transfer plates 2 and 3 (the first heat transfer plate 2 and the second heat transfer plate 3) include the blocking ridges 231 and 331 as the ridges on the first surfaces Sa1 and Sb1, but are not limited thereto. For example, as the ridges on the first surfaces Sa1, Sb1, the blocking ridges 231, 331 may be included in only one of the heat transfer plates 2, 3 (the first heat transfer plate 2 and the second heat transfer plate 3) adjacent to each other.
In the above embodiments, the tops of the second ridges 233, 333 of the adjacent heat transfer plates 2, 3 (the first heat transfer plate 2 and the second heat transfer plate 3) are in contact with or connected to each other, but the present invention is not limited thereto. For example, the tops of the second ribs 233, 333 of the adjacent heat transfer plates 2, 3 (the first heat transfer plate 2 and the second heat transfer plate 3) may be separated from each other in the first direction or the second direction. However, in order to obtain rigidity against an increase in the flow pressure in the first flow path Ra or the like, it is preferable that the tops of the second ridges 233, 333 of the adjacent heat transfer plates 2, 3 (the first heat transfer plate 2 and the second heat transfer plate 3) contact or are connected to each other, as in the above-described embodiment.
In the above embodiments, the first concave strips 220 and 320, the first convex strips 230 and 330, the second concave strips 221 and 321, and the second convex strips 233 and 333 are formed to extend straight in the second direction, but the present invention is not limited thereto. For example, the second concave stripes 221 and 321 may extend in a synthetic direction (a direction inclined with respect to a virtual line extending in the second direction) including the second direction component, on the assumption that they are continuous with the back-side concave stripes 222 and 322. However, in order to increase the flow velocity of the second fluid B, it is a condition that the inclination component (angle) with respect to the imaginary line extending in the second direction is smaller than the inclination component (angle) with respect to the imaginary line extending in the third direction.
In the above embodiments, the barrier ribs 231 and 331 are provided at intervals in the second direction, but the present invention is not limited thereto. For example, one barrier rib 231, 331 may be provided for one heat transfer unit 20, 30. In the second embodiment, the rows of the plurality of barrier ribs 231 and 331 spaced apart from each other in the second direction are provided in two or more rows spaced apart from each other in the third direction in the first surfaces Sa1 and Sb1 of the heat transfer units 20 and 30, but the present invention is not limited thereto. For example, a row of the plurality of barrier ribs 231 and 331 may be provided in the first faces Sa1 and Sb1 of the heat transfer units 20 and 30 at intervals in the second direction. In the second embodiment, the plurality of barrier ribs 231 and 331 spaced apart from each other in the second direction are arranged in the second direction on the first surfaces Sa1 and Sb1 of the heat transfer units 20 and 30, but the present invention is not limited thereto. For example, the plurality of barrier ribs 231 and 331 arranged at intervals in the second direction may be arranged at a position shifted in the third direction.
In the above embodiments, the plurality of barrier ribs 231 and 331 formed on the first surfaces Sa1 and Sb1 of the heat transfer units 20 and 30 have the same configuration, but the present invention is not limited thereto. For example, the plurality of barrier ribs 231 and 331 may be formed in different shapes on the first surfaces Sa1 and Sb1 of the heat transfer units 20 and 30.
In the above 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 thereto. For example, as shown in fig. 25 to 27, the width of the first concave strips 220 and 320 may be set larger than the width of the first convex strips 230 and 330. Specifically, as shown in fig. 25, assuming that the first concave stripes 220 and 320 and the first convex stripes 230 and 330 are formed to have circular arc-shaped cross sections, the radius of curvature of the first concave stripes 220 and 320 may be set larger than the radius of curvature of the first convex stripes 230 and 330. As shown in fig. 26 and 27, the bottom portions of the first concave stripes 220 and 320 may be formed flat, and the width of the first concave stripes 220 and 320 may be set larger than the width of the first convex stripes 230 and 330. In this case, as shown in fig. 26, the first ribs 230 and 330 may have an arc-shaped cross section, and as shown in fig. 27, the top portions of the first ribs 230 and 330 may be formed in a flat shape. In this way, even if the first convex strips 230 and 330 of the heat transfer plates 2 and 3 on the other side cross and abut against the stopper convex strips 231 and 331 having a height lower than the height of the first convex strips 230 and 330, and thereby the first convex strips 230 and 330 approach or enter the first concave strips 220 and 320, a portion having an extremely narrow interval is not formed between the first concave strips 220 and 320 and the first convex strips 230 and 330, and the flow property of the first fluid a can be ensured.
In each of the above embodiments, the first flow path Ra directly communicates the first inflow path Pa1 with the first outflow path Pa2, and the second flow path Rb directly communicates the second inflow path Pb1 with the second outflow path Pb2, but the present invention is not limited thereto. For example, as shown in fig. 28 and 29, at least two second flow paths Rb may be 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 at the most upstream of the flow path of the second fluid B including the connection flow path PJ being connected to the second inflow path Pb1, and the second flow path Rb located at the most downstream of the flow path of the second fluid B including the connection flow path PJ being connected to the second outflow path Pb 2.
More specifically, a branching reference space Ds1 is formed between the adjacent heat transfer plates 2, 3 at a position midway in the direction in which the heat transfer plates 2, 3 overlap (first direction). On the premise of this, the second flow path Rb located on the one side of the division reference space Ds1 in the first direction and the division reference space Ds1 may be connected via a connection flow path PJ, and the second flow path Rb located on the other side of the division reference space Ds1 in the first direction and the division reference space Ds1 may be connected via a connection flow path PJ. With this configuration, the flow path of the second fluid B is branched into at least one first system S1 that is continuous from the branched reference space Ds1 on one side in the first direction and at least one second system S2 that is continuous from the branched reference space Ds1 on the other side in the first direction.
In addition, when the flow path of the second fluid B includes the first system S1 and the second system S2, a branching reference space (a downstream-side branching reference space) Ds2 may be formed in each of the first system S1 and the second system S2, and the branching reference space Ds2 may be formed between the heat transfer plates 2 and 3 defining at least one second flow path Rb that is located at an intermediate position in the first direction and directly or indirectly connected to the upstream branching reference space Ds1 via a connection flow path PJ. In this case, the second flow path Rb on the one side of the branch reference space Ds2 in the first direction is connected to the downstream branch reference space Ds2 via a connection flow path PJ, and the second flow path Rb on the other side of the branch reference space Ds2 in the first direction is connected to the downstream branch reference space Ds2 via a connection flow path PJ. Thus, the flow path of the second fluid B in each of the first system S1 and the second system S2 is further branched into at least two systems S1a, S1B, S2a, and S2B, and the second flow path Rb located at the most downstream of the systems S1a, S1B, S2a, and S2B is connected to the second outflow Pb 2. The number of the second flow paths Rb (the second flow path Rb connected to the second outflow path Pb 2) located at the most downstream side in each of the systems S1a, S1b, S2a, and S2b is not limited to one, and may be plural.
In the first embodiment, the stopper ribs 231 and 331 having the curved convex ridges 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 of (two or more) curved ribs 232 and 332. The barrier ribs 231 and 331 may be formed in a curved shape when viewed from the first direction. The barrier ribs 231 and 331 may be formed in a wave shape in which a plurality of bent portions are connected when viewed from the first direction.
The stopper ribs 231 and 331 that are linear over the entire length may be formed over the entire length of the heat transfer portions 20 and 30 in the third direction. However, when the barrier ribs 231 and 331 are provided on both the adjacent heat transfer plates 2 and 3, the barrier ribs 231 and 331 of one of the adjacent heat transfer plates 2 and 3 are arranged offset from the barrier ribs 231 and 331 of the other of the adjacent heat transfer plates 2 and 3 in the second direction. With this configuration, the stopper ridges 231 and 331 can be prevented from coming into contact with each other over the entire length thereof to close the first flow path Ra, and the same operation and effect as those of the above embodiment can be achieved.
In the second embodiment, the plurality of barrier ribs 231 and 331 each extend straight in the third direction, but the present invention is not limited thereto. For example, as in the first embodiment, the plurality of stopper ribs 231 and 331 may include curved convex strip portions 232 and 332, respectively.
In this case, the blocking ridges 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 so as to intersect with the plurality of first ribs 230 and 330, but the present invention is not limited thereto. The barrier ribs 231, 331 may extend in a direction intersecting the first ribs 230, 330. That is, the barrier ribs 231, 331 are formed extremely short so as to extend in the direction intersecting the first ribs 230, 330 (the top portions (ridges) of the barrier ribs 231, 331 extend in the direction intersecting the first ribs 230, 330), and the barrier ribs 231, 331 may intersect only a single first rib 230, 330, or may be present between adjacent first ribs 230, 330 (within a single first concave stripe 220, 320).
Description of reference numerals
1 … plate heat exchanger, 2 … first heat transfer plate (heat transfer plate), 3 … second heat transfer plate (heat transfer plate), 20, 30 … heat transfer portion, 21, 31 … fitting portion, 22, 32 … concave bar, 23, 33 … convex bar, 200, 201, 202, 203, 300, 301, 302, 303 … opening, 220, 320 … first concave bar, 221, 321 … second concave bar, 222, 322 … back side concave bar, 223, 323 … curved concave bar, 223a, 223B, 323a, 323B 63 … inclined concave bar, 230, 330 … first convex bar, 231, 331 2 blocking convex bar, 232, 332 … curved convex bar, 232a, 232B, 332B … inclined convex bar, 233, 333 … second convex bar, a … first fluid, B … second fluid, CL 58 longitudinal centerline, 1 … first inflow path, 1 … first outflow path, 1 … Pb, 1 … first outflow path 1 … Ra, 1 … Pb1 … first outflow path, rb … second channel, Sa1, Sb1 … first surface, Sa2, Sb2 … second surface.

Claims (5)

1. A plate heat exchanger has a plurality of heat transfer plates including heat transfer portions overlapping in a first direction, the heat transfer portions having a first surface and a second surface, wherein the first surface has raised lines and recessed strips formed therein, the second surface faces an opposite side with respect to the first surface, and recessed strips in a surface-to-interior relationship with the raised lines of the first surface and raised lines in a surface-to-interior relationship with the recessed strips of the first surface are formed,
the plurality of heat transfer plates have first surfaces of their own heat transfer portions facing first surfaces of heat transfer portions of heat transfer plates arranged adjacently on one side in the first direction, and have second surfaces of their own heat transfer portions facing second surfaces of heat transfer portions of heat transfer plates arranged adjacently on the other side in the first direction,
a first flow path for circulating a first fluid 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 a second flow path for circulating a second fluid in the second direction is formed between the second surfaces of the heat transfer portions of the adjacent heat transfer plates,
each heat transfer portion of the adjacent heat transfer plates includes a plurality of first convex strips as convex strips formed on the first surface, the plurality of first convex strips are arranged at intervals in a direction intersecting with the first direction and the second direction, the plurality of first convex strips extend in the second direction or a composite direction including a component in the second direction, respectively, and each heat transfer portion of the adjacent heat transfer plates includes a plurality of first concave strips as concave strips formed on the first surface, the plurality of first concave strips are formed between the first convex strips adjacent in the direction intersecting with the first direction and the second direction, and the plurality of second concave strips which are in a front-back relationship with the first convex strips are included as concave strips formed on the second surface,
the heat transfer portion of at least one of the adjacent heat transfer plates includes at least one rib for blocking, which is lower in height than the first rib formed on the first surface and extends in a direction intersecting the first rib, as the rib formed on the first surface,
each first convex strip of the adjacent heat transfer plates is positioned between the first convex strips of the opposite heat transfer plate, and the blocking convex strip of at least one heat transfer plate is crossed and butted with the first convex strip of the opposite heat transfer plate.
2. The plate heat exchanger according to claim 1, wherein at least one of the adjacent heat transfer plates includes a plurality of ribs for blocking as the ribs formed on the first surface, and the plurality of ribs for blocking are arranged at intervals in the second direction.
3. The plate heat exchanger according to claim 1 or 2, wherein each of the heat transfer portions of the adjacent heat transfer plates includes a plurality of second convex ribs as convex ribs formed on the second surface in a back-and-forth relationship with the first concave ribs,
each second convex strip of the adjacent heat transfer plate is superposed with the second convex strip of the opposite heat transfer plate and is contacted with the top of the second convex strip of the opposite heat transfer plate.
4. The plate heat exchanger according to any of claims 1 to 3, wherein the barrier ribs have at least one curved rib portion,
the curved convex strip portion includes a pair of inclined convex strip portions each having a base end and a leading end located on the opposite side of the base end, the pair of inclined convex strip portions being inclined in opposite directions to each other with respect to a center line extending in the second direction or an imaginary line parallel to the center line, and the leading ends of the pair of inclined convex strip portions being connected to each other.
5. The plate heat exchanger according to claim 4, wherein each of the heat transfer portions of the adjacent heat transfer plates includes a stopper rib having a curved ridge portion,
the curved convex portions of the barrier ribs of the adjacent heat transfer plates are formed by being curved in the opposite direction to each other.
CN201780091159.0A 2017-05-25 2017-05-25 Plate heat exchanger Active CN110662937B (en)

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JP2021134987A (en) 2020-02-27 2021-09-13 三菱重工業株式会社 Heat exchange core and heat exchanger

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EP3627087A1 (en) 2020-03-25
JPWO2018216166A1 (en) 2020-04-23
JP6799681B2 (en) 2020-12-16
EP3627087A4 (en) 2021-01-20
EP3627087C0 (en) 2023-08-23
EP3627087B1 (en) 2023-08-23
CN110662937B (en) 2021-05-14

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