US20190011193A1 - Plate heat exchanger - Google Patents

Plate heat exchanger Download PDF

Info

Publication number
US20190011193A1
US20190011193A1 US16/065,935 US201616065935A US2019011193A1 US 20190011193 A1 US20190011193 A1 US 20190011193A1 US 201616065935 A US201616065935 A US 201616065935A US 2019011193 A1 US2019011193 A1 US 2019011193A1
Authority
US
United States
Prior art keywords
heat transfer
flow channel
ridges
portions
ridge
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US16/065,935
Other languages
English (en)
Inventor
Nobuo Tanaka
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hisaka Works Ltd
Original Assignee
Hisaka Works Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hisaka Works Ltd filed Critical Hisaka Works Ltd
Assigned to HISAKA WORKS, LTD. reassignment HISAKA WORKS, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TANAKA, NOBUO
Publication of US20190011193A1 publication Critical patent/US20190011193A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • 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
    • F28D9/0031—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
    • F28D9/0037—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 conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • 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
    • 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
    • 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
    • F28F3/048—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 ribs integral with the element or local variations in thickness of the element, e.g. grooves, microchannels
    • 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
    • F28F3/08—Elements constructed for building-up into stacks, e.g. capable of being taken apart for cleaning
    • 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
    • F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main fins

Definitions

  • the present invention relates to a plate heat exchanger that is used as a condenser and an evaporator.
  • a plate heat exchanger is a type of heat exchanger configured to exchange heat between a first fluid medium and a second fluid medium.
  • the plate heat exchanger includes a plurality of heat transfer plates.
  • Each of the plurality of heat transfer plates includes a heat transfer portion.
  • the heat transfer portion has a first surface on which ridges and valleys are formed, and a second surface that faces an opposite side to the first surface and on which valleys each serving as the back of each corresponding one of the ridges on the first surface and ridges located on the back of the respective valleys on the first surface are formed.
  • the ridges cross a centerline (hereinafter referred to as vertical centerline) that extends in a second direction orthogonal to a first direction.
  • the ridges are formed over the entire length of the heat transfer portion in a third direction orthogonal to both the first direction and the second direction.
  • the plurality of heat transfer plates are stacked on each other in the first direction. That is, each of the plurality of heat transfer plates has the first surface of its heat transfer portion opposed to the first surface of the heat transfer portion of each adjacent heat transfer plate aligned on one side of the first direction. Each of the plurality of heat transfer plates has the second surface of its heat transfer portion opposed to the second surface of the heat transfer portion of the adjacent heat transfer plate aligned on the other side of the first direction.
  • the ridges on the heat transfer portions of each two adjacent heat transfer plates cross and abut against each other. With this configuration, the valleys on the heat transfer portions form spaces between the heat transfer portions of each two adjacent heat transfer plates.
  • a first flow channel for circulating the first fluid medium in the second direction is formed between the first surfaces of the heat transfer portions of each two adjacent heat transfer plates.
  • a second flow channel for circulating the second fluid medium in the second direction is formed between the second surfaces of the heat transfer portions of each two adjacent heat transfer plates.
  • the first fluid medium is circulated through the first flow channels in the second direction.
  • the second fluid medium is circulated through the second flow channels in the second direction.
  • the plate heat exchanger of this type is used as a condenser that is configured to condense the second fluid medium within the second flow channels through the heat exchange between the first fluid medium within the first flow channels and the second fluid medium within the second flow channels.
  • the plate heat exchanger of this type is used as an evaporator that is configured to evaporate the second fluid medium within the second flow channels through the heat exchange between the first fluid medium within the first flow channel and the second fluid medium within the second flow channels.
  • the conventional plate heat exchanger if used as the condenser or the evaporator, has a limit in improving heat exchange performance due to the characteristics of the second fluid medium, which is the medium to be condensed or evaporated.
  • the ridges on each of the heat transfer portions are formed crossing the vertical centerline of the heat transfer portion and extending over the entire length of the heat transfer portion in the third direction. This configuration causes the ridges of the heat, transfer portion to increase flow resistance of both the first flow channels and the second flow channels.
  • a fluid medium that does not cause phase change (a fluid medium having single-phase flow) is employed for the first fluid medium. Therefore, increase in the flow resistance in the first flow channels causes the heat transfer portions to be more likely to be subjected to thermal influences. The increase in the flow resistance in the first flow channels consequently becomes a factor for improved heat exchange performance.
  • a fluid medium that causes phase change (a fluid medium having two-phase flow that contains liquid and gas), such as fluorocarbons, is employed for the second fluid medium.
  • a fluid medium having two-phase flow that contains liquid and gas such as fluorocarbons
  • liquid film of the second fluid medium is formed on each of the second surfaces of the heat transfer portions that define the second flow channels.
  • the ridges on each the heat transfer portions are formed crossing the vertical centerline of the heat transfer portion and extending over the entire length of the heat transfer portion in the third direction.
  • This configuration causes the ridges on the heat transfer portions to block flow of the second fluid medium within the second flow channels. That is, the ridges on the second surfaces of the heat transfer portions are formed so as to cross the flow of the second fluid medium within the second flow channels, and therefore increase the flow resistance of the second fluid medium within the second flow channels.
  • the conventional plate heat exchanger has a limit in increasing the velocity of the second fluid medium within the second flow channels; and thus cannot sufficiently disturb the flow of the liquid film of the second fluid medium formed on the second surface of the heat transfer portion.
  • the conventional plate heat exchanger has a limit in improving the performance for transferring, to the heat transfer portion, heat of the second fluid medium that is circulated through the second flow channels.
  • the present invention features a plurality of heat transfer plates each including a heat transfer portion having a first surface on which ridges and valleys are formed, and a second surface that is opposed to the first surface and on which valleys being in a front-back relationship with the ridges of the first surface and ridges being in a front-back relationship with the valleys of the first surface are formed, the plurality of heat transfer plates respectively having the heat transfer portions stacked on each other in a first direction, wherein the first surface of the heat transfer portion of each of the plurality of heat transfer plates is arranged opposed to the first surface of the heat transfer portion of an adjacent heat transfer plate on one side in the first direction, and the second surface of the heat transfer portion of each of the plurality of heat transfer plates is arranged opposed to the second surface of the heat transfer portion of an adjacent heat transfer plate on an other side in the first direction, wherein a first flow channel through which a first fluid medium is circulated in a second direction orthogonal to the first direction is formed between the first surfaces of the heat transfer portions of each adjacent heat
  • each of the heat transfer portions of the each adjacent heat transfer plates include: the at least one barrier ridge and the second flow channel forming valleys, as the valleys formed on the first surface, a plurality of first flow channel forming valleys constituting part of the first flow channel, the plurality of first flow channel forming valleys being arranged at intervals from each other in the third direction in each of the two or more divided areas from the one end to the other end in the second direction of each corresponding one of the two or more divided areas, and as the ridges formed on the first surface, a plurality of first flow channel side ridges each formed in the third direction between each adjacent first flow channel forming valleys, the first flow channel side ridges each extending from the one end to the other end in the second direction of each corresponding one of the two or more divided areas, and that the first flow channel side ridges in the mutually corresponding divided areas of the adjacent heat transfer plates be arranged with a clearance therebetween.
  • a projected amount of the at least one barrier ridge in the first direction may be set to be larger than a projected amount of the first flow channel side ridges in the first direction.
  • the plurality of first flow channel side ridges in the mutually corresponding divide areas of the each adjacent heat transfer plates be arranged while being displaced with each other in the third direction.
  • each of the heat transfer portions of the each adjacent heat transfer plates include: the at least one barrier ridge and the second flow channel forming valleys, and as the ridges formed on the second surface, a plurality of second flow channel side ridges each formed in the third direction between each adjacent second flow channel forming valleys, the second flow channel side ridges each extending from the one end to the other end of the divided area in the second direction, and that top ends of the second flow channel side ridges in the mutually corresponding divided areas of each adjacent heat transfer plates with the second surfaces of the heat transfer portions opposed to each other be in contact with each other.
  • each of the heat transfer portions of the each adjacent heat transfer plates include: the at least one barrier ridge and the second flow channel forming valleys, and as the ridges formed on the second surface, a plurality of second flow channel side ridges each formed in the third direction between each adjacent second flow channel forming valleys, the second flow channel side ridges each extending from the one end to the other end in the second direction of each corresponding one of the two or more divided areas, and that the second flow channel side ridges in the mutually corresponding divided areas of the each adjacent heat transfer plates with the second surfaces of the heat, transfer portions opposed to each other be arranged with a clearance therebetween.
  • the plurality of second flow channel side ridges in the mutually corresponding divided areas of the each adjacent heat transfer plates may be arranged while being displaced in the third direction.
  • the at least one barrier ridge include two or more harrier ridges provided at intervals in the second direction, and that the two or more barrier ridges divide each corresponding one of the heat transfer portions into three or more divided areas.
  • the barrier ridge may include at least one bent ridge portion that includes a pair of inclined ridge portions each having a proximal end and a distal end on an opposite side of the proximal end, the pair of inclined ridge portions being inclined in directions opposite to each other with respect to the centerline extending in the second direction or a virtual line parallel to the centerline, and having the distal ends thereof connected to each other.
  • each of the heat transfer portions of the each adjacent heat transfer plates include the barrier ridge having the bent ridge portion, and that the bent ridge portions of the barrier ridges of the each adjacent heat transfer plates be bent in directions completely opposite to each other and includes the inclined ridge portions of the bent ridge portions opposed to each other crossing and abutting against each other.
  • the barrier ridge may extend straightforwardly in the third direction.
  • Each of the heat transfer portions of the each adjacent heat transfer plates may include the barrier ridge extending in the third direction, and the barrier ridges of the each adjacent heat transfer plates may be arranged while being displaced with each other in the second direction.
  • FIG. 1 is a perspective view of a plate heat exchanger according to one embodiment of the present invention.
  • FIG. 2 is an exploded perspective view of the plate heat exchanger according to the embodiment, which includes circulation routes of a first fluid medium and a second fluid medium.
  • FIG. 3 is a view of a heat transfer plate (first heat transfer plate) of the plate heat exchanger according to the embodiment, as seen from its 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 embodiment, as seen from its second surface side.
  • FIG. 5 is a view of a heat transfer plate (second heat transfer plate) of the plate heat exchanger according to the embodiment, as seen from its 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 embodiment, as seen from its second surface side.
  • FIG. 7 is a view showing flows of the first fluid medium within a first flow channel in the plate heat exchanger according to the embodiment.
  • FIG. 8 is a schematic partial cross-sectional view of the plate heat exchanger according to the embodiment, showing a cross section taken along ridges on a second flow channel side thereof as seen from a third direction with the first flow channels mainly shown.
  • FIG. 9 is a view showing flows of the second fluid medium within the second flow channel in the plate heat exchanger according to the embodiment.
  • FIG. 10 is a schematic partial cross-sectional view of the plate heat exchanger according to the embodiment, showing a cross section taken along ridges on a first flow channel side thereof, as seen from the third direction with the second flow channels mainly shown.
  • FIG. 11 is a schematic diagram showing a circulation route of the first fluid medium through the first flow channels and a circulation route of the second fluid medium through the second flow channels of the plate heat exchanger according to the embodiment.
  • FIG. 12 is a view of a heat transfer plate (first heat transfer plate) of a plate heat exchanger according to another embodiment of the present invention, as seen from its first surface side.
  • FIG. 13 is a view of the heat transfer plate (first heat transfer plate) of the plate heat exchanger according to the other embodiment, as seen from its second surface side.
  • FIG. 14 is a view of a heat transfer plate (second heat, transfer plate) of the plate heat exchanger according to the other embodiment, as seen from its first surface side.
  • FIG. 15 is a view of the heat transfer plate (second heat transfer plate) of the plate heat exchanger according to the other embodiment, as seen from its second surface side.
  • FIG. 16 is a schematic diagram showing a circulation route of the first fluid medium through first flow channels and a circulation route of the second fluid medium through second flow channels, of a plate heat exchanger according to still another embodiment of the present invention.
  • FIG. 17 is a schematic diagram showing a circulation route of the first fluid medium through first flow channels and a circulation route of the second fluid medium through second flow channels, of a plate heat exchanger according to still another embodiment of the present invention.
  • a plate heat exchanger 1 includes a plurality of heat transfer plates 2 , 3 . That is, the plate heat exchanger 1 includes at least three heat transfer plates 2 , 3 . In this embodiment, the plate heat exchanger 1 includes more than three heat transfer plates 2 , 3 . Further, in this embodiment, the plurality of heat transfer plates 2 , 3 include two kinds of heat transfer plates. Accordingly, in the following description, one kind of the heat transfer plate 2 out of the two kinds of heat transfer plates 2 , 3 is referred to as a first heat transfer plate, and the other kind of the heat transfer plate 3 out of the two kinds of the heat transfer plates 2 , 3 is referred to as a second heat transfer plate. However, the first heat transfer plate 2 and the second heat transfer plate 3 have a common configuration; therefore, for the sake of describing the common configuration, the first heat transfer plate 2 and the second heat transfer plate 3 are collectively referred to as the heat transfer plates 2 , 3 .
  • the heat transfer plates 2 , 3 respectively include heat transfer portions 20 , 30 that respectively have first surfaces Sa 1 , Sb 1 and second surfaces Sa 2 , Sb 2 facing opposite to the first surfaces Sa 1 , Sb 1 , and annular fitting portions 21 , 31 that respectively extend from the entire outer peripheral edges of the heat transfer portions 20 , 30 while having surfaces extending in a direction intersecting with the surfaces of the heat transfer portions 20 , 30 .
  • the heat transfer portions 20 , 30 have a thickness in a first direction. Accordingly, the first surfaces Sa 1 , Sb 1 and the second surfaces Sa 2 , Sb 2 of the heat transfer portions 20 , 30 are aligned in the first direction. As shown in FIG. 3 to FIG. 6 , the heat transfer portions 20 , 30 have an external form (contour) defined by a pair of long sides extending in a second direction orthogonal to the first direction, and a pair of short sides arranged with a distance from each other in the second direction while extending in a third direction orthogonal to the first direction and the second direction to connect the pair of long sides. That is, the heat, transfer portions 20 , 30 have an external form having a rectangular shape with the long sides extending in the second direction, when seen from the first direction.
  • Each of the heat transfer portions 20 , 30 has one end and the other end on the opposite side to the one end in the second direction.
  • the heat transfer portions 20 , 30 respectively have at least two openings 200 , 201 , 202 , 203 , 300 , 301 , 302 , 303 in each of the one ends and the other ends in the second direction.
  • the heat transfer portions 20 , 30 respectively have two openings 200 , 203 , 300 , 303 in the one ends in the second direction, and two openings 201 , 202 , 301 , 302 in the other ends in the second direction.
  • the two openings 200 , 203 , 300 , 303 in the one ends in the second direction of the heat transfer portions 20 , 30 are aligned in the third direction.
  • the two openings 201 , 202 , 301 , 302 in the other ends in the second direction of the heat transfer portions 20 , 30 are aligned in the third direction.
  • An area surrounding each of the one openings 200 , 300 in the one ends and an area surrounding each of the one openings 201 , 301 in the other ends in the second direction of the heat transfer portions 20 , 30 are recessed on the first surfaces Sa 1 , Sb 1 side. Accordingly, an area surrounding each of the one openings 200 , 300 in the one ends and an area surrounding each of the one openings 201 , 301 in the other ends in the second direction of the heat transfer portions 20 , 30 are projected on the second surfaces Sat, Sb 2 side.
  • a projected amount of the area surrounding each of the openings 200 , 201 , 300 , 301 that is projected on the second surfaces Sa 2 , Sb 2 side is set so that the area surrounding each of the openings 200 , 201 , 300 , 301 that is projected on the second surfaces Sat, Sb 2 side abut against the area surrounding each corresponding one of the openings 200 , 201 , 300 , 301 (the one openings 200 , 300 in the one ends and the one openings 201 , 301 in the other ends) in the heat transfer portions 20 , 30 of each adjacent heat transfer plates 2 , 3 .
  • an area surrounding each of the other openings 203 , 303 in the one ends and an area surrounding each of the other openings 202 , 302 in the other ends in the second direction of the heat transfer portions 20 , 30 are projected on the first surfaces Sa 1 , Sb 1 side. Accordingly, an area surrounding each of the other openings 203 , 303 in the one ends and an area surrounding each of the other openings 202 , 302 in the other ends in the second direction of the heat transfer portions 20 , 30 are recessed on the second surfaces Sa 2 , Sb 2 side.
  • a projected amount of the area surrounding each of the openings 202 , 203 , 302 , 303 that is projected on the first surfaces Sa 1 , Sb 1 side is set so that the area surrounding each of the openings 202 , 203 , 302 , 303 that is projected on the first surfaces Sa 1 , Sb 1 side abut the area surrounding each corresponding one of the openings 202 , 203 , 302 , 303 (the other openings 202 , 302 in the one ends and the other openings 203 , 303 in the other ends) in the heat transfer portions 20 , 30 of each adjacent heat transfer plates 2 , 3 .
  • recessed areas out of the areas each surrounding the openings 200 , 201 , 202 , 203 , 300 , 301 , 302 , 303 , and bottom parts of valleys 22 , 32 , which will be described later, are shown in stippling to allow the relationship between the projected portions and the recessed portions of the first surfaces Sa 1 , Sb 1 and the second surfaces Sa 2 , Sb 2 to be distinguishable.
  • the one openings 200 , 300 in the one ends and the one openings 201 , 301 in the other ends in the second direction of the heat transfer portions 20 , 30 are located diagonal to each other, due to the configuration in which the heat transfer plates 2 , 3 are stacked on each other.
  • the other openings 203 , 303 in the one ends and the other openings 202 , 302 in the other ends in the second direction of the heat transfer portions 20 , 30 are also located diagonal to each other.
  • the valleys 22 , 32 and ridges 23 , 33 are respectively formed on each of the first surfaces Sa 1 , Sb 1 and the second surfaces Sa 2 , Sb 2 of the heat transfer portions 20 , 30 .
  • Each of the first surfaces Sa 1 , Sb 1 and the second surfaces Sa 2 , Sb 2 of the heat, transfer portions 20 , 30 has a plurality (a large number) of valleys 22 , 32 and a plurality (a large number) of ridges 23 , 33 .
  • each of the heat transfer plates 2 , 3 is formed by press molding of a metal plate. Accordingly the valleys 22 , 32 formed on the first surfaces Sa 1 , Sb 1 of the heat transfer portions 20 , 30 are in a front-back relationship with the ridges 23 , 33 formed on the second surfaces Sa 2 , Sb 2 of the heat transfer portions 20 , 30 . The ridges 23 , 33 formed on the first surfaces Sa 1 , Sb 1 of the heat transfer portions 20 , 30 are in a front-back relationship with the valleys 22 , 32 formed on the second surfaces Sa 2 , Sb 2 of the heat, transfer portions 20 , 30 .
  • the deformation of the metal plate by press molding allows the valleys 22 , 32 formed on the first surfaces Sa 1 , Sb 1 of the heat transfer portions 20 , 30 to be formed at positions corresponding to the positions of the ridges 23 , 33 formed on the second surfaces Sa 2 , Sb 2 of the heat transfer portions 20 , 30 . Also, the deformation of the metal plate by press molding allows the ridges 23 , 33 formed on the first surfaces Sa 1 , Sb 1 of the heat transfer portions 20 , 30 to be formed at positions corresponding to the positions of the valleys 22 , 32 formed on the second surfaces Sa 2 , Sb 2 of the heat, transfer portions 20 , 30 .
  • the heat transfer portion 20 , 30 includes, as the ridges 23 , 33 formed on the first surface Sa 1 , Sb 1 , at least one barrier ridge 230 , 330 that crosses a centerline CL extending in the second direction (hereinafter referred to as vertical centerline) and is formed over the entire length in the third direction, and that divides the heat transfer portion 20 , 30 into two or more divided areas Da, Db in the second direction, the barrier ridge 230 , 330 crossing and abutting against the ridge 23 , 33 formed on the first surface Sa 1 , Sb 1 of the opposed heat transfer portion 20 , 30 .
  • the heat transfer portion 20 , 30 includes, as the valleys 22 , 32 formed on the first surface Sa 1 , Sb 1 , a plurality of first flow channel forming valleys 220 , 320 that constitute part of a first flow channel Ra, the plurality of first flow channel forming valleys 220 , 320 being arranged in each of the two or more divided areas Da, Db from one end to the other end of the divided area Da, Db in the second direction at intervals from each other in the third direction.
  • the heat transfer portion 20 , 30 includes, as the ridges 23 , 33 formed on the first surface Sa 1 , Sb 1 , a plurality of first flow channel side ridges 231 , 331 formed by extending in the second direction between each adjacent first flow channel forming valleys 220 , 320 in the third direction.
  • two or more barrier ridges 230 , 330 are provided at intervals from each other in the second direction.
  • the two or more barrier ridges 230 , 330 divide the heat transfer portion 20 , 30 into three or more divided areas Da, Db.
  • the barrier ridges 230 , 330 include at least one bent ridge portion 232 , 332 .
  • the bent ridge portion 232 , 332 includes a pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b each portion having a proximal end and a distal end on the opposite side of the proximal end, the pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b being inclined in a direction opposite to each other with respect to the vertical centerline CL and having the distal ends thereof connected to each other.
  • the barrier ridges 230 , 330 have one bent ridge portion 232 , 332 .
  • the proximal ends of the pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b that constitute the bent ridge portion 232 , 332 are located on an end edge in the third direction of the heat transfer portion 20 , 30 .
  • the distal ends of the pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b are located at the center (on the vertical centerline CL) in the third direction of the heat transfer portion 20 , 30 .
  • the distal ends of the pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b are connected in face-to-Pace relationship.
  • the pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b are symmetrically arranged with reference to a virtual line that extends in the second direction. That is, the pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b are inclined in a direction completely opposite to each other. However, the pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b have the same inclination angle with respect, to the vertical centerline CL extending in the second direction.
  • a projected amount in the first direction of the barrier ridges 230 , 330 is set to be larger than that of the first flow channel side ridges 231 , 331 . Accordingly, top ends of the barrier ridges 230 , 330 are positioned outwardly of the top ends of the first flow channel side ridges 231 , 331 .
  • This configuration allows only the barrier ridges 230 , 330 out of the ridges 23 formed on the first surface Sa 1 , Sb 1 of the heat transfer portion 20 , 30 to contact the heat transfer portion 20 , 30 of the opposed heat transfer plate 2 , 3 . That is, the first flow channel side ridges 231 , 331 are formed to have a lower height than the barrier ridges 230 , 330 so that they do not contact the opposed heat transfer plate 2 , 3 .
  • the first flow channel forming valleys 220 , 320 and the first flow channel side ridges 231 , 331 formed in each of the divided areas Da, Db are formed over the entire length in the second direction of the divided areas Da, Db. Accordingly, at least one end of each of the first flow channel forming valleys 220 , 320 and at least one end of each of the first flow channel side ridges 231 , 331 are joined to a corresponding one of the barrier ridges 230 , 330 that define the divided areas Da, Db.
  • the one ends of the first flow channel forming valleys 220 , 320 and the first flow channel side ridges 231 , 331 respectively are joined to one of each pair of barrier ridges 230 , 330 that define the divided areas Da, Db.
  • the other ends of the first flow channel forming valleys 220 , 320 and the first flow channel side ridges 231 , 331 are joined to the other one of each pair of barrier ridges 230 , 330 that define the divided areas Da, Db.
  • the plurality of first flow channel forming valleys 220 , 320 formed in each of the two or more divided areas Da, Db are aligned with each other in the second direction. That is, the first flow channel forming valleys 220 , 320 formed in the two or more divided areas Da, Db correspond in the number and arrangement to each other. Accordingly, the first flow channel side ridges 231 , 331 formed in the two or more divided areas Da, Db also correspond in the number and arrangement to each other.
  • the heat transfer portion 20 , 30 includes, as the valleys 22 , 32 formed on the second surface 5 a 2 , Sb 2 , valleys (hereinafter referred to as back side valleys) 222 , 322 formed respectively on the back sides of the barrier ridges 230 , 330 on the first surface Sa 1 , Sb 1 .
  • the heat transfer portion 20 , 30 include, as the valleys 22 , 32 formed on the second surface Sa 2 , Sb 2 , a plurality of second flow channel forming valleys 221 , 321 that constitute part of a second flow channel Rb, the plurality of second flow channel forming valleys 221 , 321 being arranged in each of the two or more divided areas Da, Db from one end to the other end of the divided area Da, Db in the second direction at intervals from each other in the third direction.
  • the heat transfer portion 20 , 30 includes, as the ridges 23 , 33 formed on the second surface Sa 2 , Sb 2 , a plurality of second flow channel side ridges 233 , 333 formed in the third direction between each adjacent second flow channel forming valleys 221 , 321 , the second flow channel side ridges 233 , 333 each extending from one end to the other end in the second direction of the divided area Da, Db.
  • the back side valleys 222 , 322 are formed in the same pattern as the barrier ridges 230 , 330 except that they have a reversed concavo-convex relationship.
  • a bent valley portion 223 , 323 that includes a pair of inclined valley portions 223 a , 223 b , 323 a , 323 b is formed, which is the valley 22 , 32 formed on the back side of each pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b.
  • the bent ridge portion 232 , 332 (the pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b ) constitutes the barrier ridge 230 , 330 .
  • the bent valley portion 223 , 323 constitutes each of the entire back side valleys 222 , 322 formed on the back side of each of the barrier ridges 230 , 330 .
  • the second flow channel forming valleys 221 , 321 are the valleys 22 , 32 formed on the back sides of the first flow channel side ridges 231 , 331 on the first surface Sa 1 , Sb 1 .
  • the second flow channel forming valleys 221 , 321 are herein described specifically. As described above, the second flow channel forming valleys 221 , 321 extend from one end to the other end in the second direction of each of the divided areas Da, Db.
  • “extend from one end to the other end in the second direction” means that the second flow channel forming valleys 221 , 321 extend from one end to the other end in the second direction of each of the divided areas Da, Db at a smaller angle with respect to the virtual line extending in the second direction than an inclination angle with respect to a virtual line extending in the third direction.
  • the second flow channel forming valleys 221 , 321 extend in the second direction. That is, in this embodiment, the second flow channel forming valleys 221 , 321 extend at an angle of 0 degree with respect to the virtual line extending in the second direction and an angle of 90 degrees with respect to the virtual line extending in the third direction.
  • the second flow channel side ridges 233 , 333 each being formed between each adjacent second flow channel forming valleys 221 , 321 also extend in the second direction.
  • the internal surfaces that define the second flow channel forming valleys 221 , 321 are continuous with the external surfaces that define the second flow channel side ridges 233 , 333 .
  • the second surface Sa 2 , Sb 2 (the divided areas Da, Db) of the heat transfer portion 20 , 30 has a corrugated shape with projections and recesses aligned in the third direction.
  • the second flow channel forming valleys 221 , 321 and the second flow channel side ridges 233 , 333 are formed over the entire length in the second direction of each of the divided areas Da, Db.
  • the second flow channel forming valleys 221 , 321 are thus continuous with the back side valleys 222 , 322 formed on the backs of the barrier ridges 230 , 330 that define the divided areas Da, Db in which the second flow channel forming valleys 221 , 321 themselves are formed. That is, each of the second flow channel forming valleys 221 , 321 is open to the inside of a corresponding one of the back side valleys 222 , 322 .
  • the first heat transfer plates 2 and the second heat transfer plates 3 respectively include the heat transfer portions 20 , 30 configured as above.
  • the first heat transfer plates 2 and the second heat transfer plates 3 are stacked on each other so that their second surfaces Sa 2 , Sb 2 are opposed to each other while their first surfaces Sa 1 , Sb 1 are opposed to each other.
  • each of the first heat transfer plates 2 includes the fitting portion 21 projecting on the first surface Sa 1 side of the heat transfer portion 20 .
  • each of the second heat transfer plates 3 includes the fitting portion 31 projecting on the second surface Sb 2 side of the heat transfer portion 30 .
  • Each of the plurality of heat transfer plates 2 , 3 has been described as above.
  • the plurality of heat transfer plates 2 , 3 (the first heat, transfer plates 2 and the second heat transfer plates 3 ) are stacked on each other in the first direction, as shown in FIG. 2 .
  • the first heat transfer plates 2 and the second heat transfer plates 3 are alternately stacked on each other in the first direction.
  • each of the plurality of heat transfer plates 2 , 3 has the first surface Sa 1 , Sb 1 of its heat transfer portion 20 , 30 opposed to the first surface Sa 1 , Sb 1 of the heat transfer portion 20 , 30 of the adjacent heat, transfer plate 2 , 3 on one side in the first direction. Further, each of the plurality of heat transfer plates 2 , 3 has the second surface Sa 2 , Sb 2 of its heat transfer portion 20 , 30 opposed to the second surface Sa 2 , Sb 2 of the heat transfer portion 20 , 30 of the adjacent heat transfer plate 2 , 3 on the other side in the first direction.
  • the plurality of heat transfer plates 2 , 3 are stacked on each other so that the distal ends of the inclined ridge portions 232 a , 232 b of the barrier ridge(s) 230 (the bent ridge portion(s) 232 ) of each of the first heat transfer plates 2 are located closer to one end in the second direction of the heat transfer portion 20 than the proximal ends thereof, whereas the distal ends of the inclined ridge portions 332 a , 332 b of the barrier ridge(s) 330 (the bent ridge portion(s) 332 ) of each of the second heat, transfer plates 3 are located closer to the other end in the second direction of the heat transfer portion 30 than the proximal ends thereof.
  • the first heat transfer plates 2 and the second heat transfer plates 3 are stacked alternately on each other so that one inclined ridge portion 232 a constituting the barrier ridge 230 (the bent ridge portion 232 ) of each of the first heat transfer plates 2 crosses and abuts against one inclined ridge portion 332 a constituting the barrier ridge 330 (the bent ridge portion 332 ) of each of the second heat transfer plates 3 , and that the other inclined ridge portion 232 b constituting the barrier ridge 230 (the bent ridge portion 232 ) of each of the first heat transfer plates 2 crosses and abuts against the other inclined ridge portion 332 b constituting the barrier ridge 330 (the bent ridge portion 332 ) of each of the second heat transfer plates 3 .
  • each of the first heat transfer plates 2 and each of the second heat transfer plates 3 are stacked on each other to form a pair while their back side valleys 222 , 322 are opposed to each other.
  • every other pair is turned 180 degrees upside down about a virtual line extending in the first direction.
  • the fitting portion 21 , 31 of one heat transfer plate 2 , 3 (the first heat transfer plate 2 or the second heat transfer plate 3 ) out of the heat transfer plates 2 , 3 adjacent to each other in the first direction is fitted onto the fitting portion 21 , 31 of the other heat transfer plate 2 , 3 (the first heat transfer plate 2 or the second heat transfer plate 3 ) out of the heat transfer plates 2 , 3 adjacent to each other in the first direction.
  • the first flow channel side ridges 231 , 331 in the mutually corresponding divided areas Da, Db of each adjacent heat transfer plates 2 , 3 (the first heat transfer plate 2 and the second heat transfer plate 3 ) with their first surfaces Sa 1 , Sb 1 of the heat transfer portions 20 , 30 opposed to each other are arranged to overlap each other when seen from the first direction.
  • the first flow channel side ridges 231 , 331 in the mutually corresponding divided areas Da, Db of each adjacent heat transfer plates 2 , 3 (the first heat transfer plate 2 and the second heat transfer plate 3 ) with their first surfaces Sa 1 , Sb 1 on the heat transfer portions 20 , 30 opposed to each other are located at intervals from each other.
  • each adjacent heat transfer plates 2 , 3 (the first heat transfer plate 2 and the second heat transfer plate 3 ) with their second surfaces Sa 2 , Sb 2 of the heat transfer portions 20 , 30 opposed to each other are arranged to overlap each other when seen from the first direction.
  • each adjacent heat transfer plates 2 , 3 (the first heat transfer plate 2 and the second heat transfer plate 3 ) with the second surfaces Sa 2 , Sb 2 of the heat transfer portions 20 , 30 opposed to each other have the top ends of the second flow channel side ridges 233 , 333 in the mutually corresponding divided areas Da, Db contacting each other.
  • the first flow channel Ra through which the first fluid medium A is circulated in the second direction orthogonal to the first direction is formed between the first surfaces Sa 1 , Sb 1 of the heat transfer portions 20 , 30 of each adjacent heat transfer plates 2 , 3 .
  • the second flow channel Rb through which the second fluid medium B is circulated in the second direction is also formed between the second surfaces Sa 2 , Sb 2 of the heat transfer portions 20 , 30 of each adjacent heat transfer plates 2 , 3 .
  • the plurality of heat transfer plates 2 , 3 are stacked on each other in the first direction so that the openings 200 , 201 , 202 , 203 , 300 , 301 , 302 , 303 located in the corresponding positions of the heat transfer portions 20 , 30 are lined up in the first direction.
  • the areas respectively surrounding the openings 200 , 201 , 202 , 203 , 300 , 301 , 302 , 303 that are opposed to and projected toward each other abut each other.
  • This configuration forms a first inflow channel Pa 1 for supplying the first fluid medium A into the first flow channels Ra, a first outflow channel Pa 2 for causing the first fluid medium A to flow out of the first flow channels Ra, a second inflow channel Pb 1 for supplying the second fluid medium B into the second flow channels Rb, and a second outflow channel Pb 2 for causing the second fluid medium B to flow out of the second flow channels Rb.
  • the abutted portions between the adjacent heat transfer plates 2 , 3 are brazed together.
  • This configuration allows the plurality of heat transfer plates 2 , 3 to be integrally (mechanically) connected to each other, and an interface between the opposed surfaces (abutted portions) of the adjacent heat transfer plates 2 , 3 to be sealed.
  • the plate heat exchanger 1 has been described as above.
  • the first fluid medium A flows from the first inflow channel Pa 1 into the plurality of first flow channels Ra.
  • the first fluid medium A is circulated through each of the first flow channels Ra in the second direction, and flows out to the first outflow channel Pa 2 .
  • the second fluid medium B flows from the second inflow channel Pb 1 into the plurality of second flow channels Rb.
  • the second fluid medium B is circulated through each of the second flow channels Rb in the second direction, and flows out to the second outflow channel Pb 2 .
  • the first fluid medium A is circulated through each of the first flow channels Ra with a diagonal line connecting opposing corners of the heat transfer portion 20 , 30 as a center of flow.
  • the second fluid medium B is circulated through each of the second flow channels Rb with another diagonal line connecting opposing corners of the heat transfer portion 20 , 30 as a center of flow, which is different from the diagonal line being the center of the flow of the first fluid medium A.
  • the first fluid medium A that is circulated through the first flow channels Ra and the second fluid medium B that is circulated through the second flow channels Rb exchange heat via the heat transfer plates 2 , 3 (the heat transfer portions 20 , 30 ) that separate the first flow channels Ra and the second flow channels Rb.
  • the second fluid medium B is condensed or evaporated in the course of being circulated through the second flow channels Rb in the second direction.
  • the plate heat exchanger 1 includes: a plurality of heat transfer plates 2 , 3 each including a heat transfer portion 20 , 30 having a first surface Sa 1 , Sb 1 on which ridges 23 , 33 and valleys 22 , 32 are formed, and a second surface Sat, Sb 2 that is opposed to the first surface Sa 1 , Sb 1 and on which valleys 22 , 32 being in a front-back relationship with the ridges 23 , 33 of the first surface Sa 1 , Sb 1 and ridges 23 , 33 being in a front-back relationship with the valleys 22 , 32 of the first surface Sa 1 , Sb 1 are formed, the plurality of heat transfer plates 2 , 3 respectively having the heat transfer portions 20 , 30 stacked on each other in a first direction, wherein the first surface Sa 1 , Sb 1 of the heat transfer portion 20 , 30 of each of the plurality of heat transfer plates 2 , 3 is arranged opposed to the first surface Sa 1 , Sb 1 of the heat transfer
  • the barrier ridges 230 , 330 are projected toward the opposed heat transfer portion 20 , 30 at intermediate positions of the first flow channel Ra formed between the first surfaces Sa 1 , Sb 1 of each adjacent heat transfer portions 20 , 30 (see FIG. 8 ).
  • This configuration allows the barrier ridges 230 , 330 to block circulation of the first fluid medium A through the first flow channels Ra to thereby increase the circulating resistance of the first fluid medium A through the first flow channels Ra.
  • the first fluid medium A is more likely to thermally influence the heat transfer portions 20 , 30 , which consequently enhances heat transfer performance to the second fluid medium B side.
  • the valleys 22 , 32 on the first surface Sa 1 , Sb 1 are in a front-back relationship with the ridges 23 , 33 on the second surface Sa 2 , Sb 2
  • the ridges 23 , 33 on the first surface Sa 1 , Sb 1 are in a front-back relationship with the valleys 22 , 32 on the second surface Sa 2 , Sb 2
  • the back side valleys 222 , 322 corresponding to the barrier ridges 230 , 330 are formed on the second surface 5 a 2 , Sb 2 of the heat transfer portion 20 , 30 .
  • the back side valleys 222 , 322 crossing a centerline (vertical centerline) CL that extends in the second direction of the heat transfer portion 20 , 30 are formed on the second surface Sa 2 , Sb 2 of the heat transfer portion 20 , 30 .
  • This configuration allows the back side valley(s) 222 , 322 to divide the heat transfer portion 20 , 30 into two or more divided areas Da, Db on the second surface Sa 2 , Sb 2 side.
  • the plurality of second flow channel forming valleys 221 , 321 extend from one end to the other end in the second direction of each of the divided areas Da, Db in which they are located.
  • the plurality of second flow channel forming valleys 221 , 321 are continuous with the back side valleys 222 , 322 (the valleys 22 , 32 corresponding to the barrier ridges 230 , 330 ) that define the divided areas Da, Db in which they are located.
  • the second flow channel Rb has nothing that blocks circulation of the second fluid medium B (i.e. that crosses the flow channel) over the entire length in the second direction.
  • the second flow channel forming valleys 221 , 321 extend from one end to the other end in the second direction of each of the divided areas Da, Db,
  • the second flow channel forming valleys 221 , 321 extend straightforwardly in the second direction, or extend while being inclined in the state where an inclination component (angle) with respect to a virtual line extending in the second direction is smaller than an inclination component (angle) with respect to a virtual line extending in the third direction.
  • This configuration allows the second flow channel forming valleys 221 , 321 to form space (part of the second flow channel Rb) corresponding to or substantially corresponding to the circulating direction of the second fluid medium B. Consequently, the circulating resistance of the second fluid medium B through the second flow channel Rb can be reduced to increase the velocity of the second fluid medium B.
  • liquid film of the second fluid medium B formed on the surfaces of the heat, transfer portions 20 , 30 is disturbed by the increased velocity of the second fluid medium B, even if a fluid medium that causes phase change (a fluid medium having two-phase flow that contains liquid and gas) is employed as the second fluid medium B.
  • a fluid medium that causes phase change a fluid medium having two-phase flow that contains liquid and gas
  • the plate heat exchanger 1 configured as above enhances heat transfer performance of the second fluid medium B circulated through the second flow channels Rb to the heat transfer portions 20 , 30 (the first fluid medium A side).
  • each of the heat transfer portions 20 , 30 of the each adjacent heat transfer plates 2 , 3 includes: the at least one barrier ridge 230 , 330 and the second flow channel forming valleys 221 , 321 , as the valleys 22 , 32 formed on the first surface Sa 1 , Sb 1 , a plurality of first flow channel forming valleys 220 , 320 constituting part of the first flow channel Ra, the plurality of first flow channel forming valleys 220 , 320 being arranged at intervals from each other in the third direction in each of the two or more divided areas Da, Db from the one end to the other end in the second direction of each corresponding one of the two or more divided areas Da, Db, and as the ridges 23 , 33 formed on the first surface Sa 1 , Sb 1 , a plurality of first flow channel side ridges 231 , 331 each formed in the third direction between each adjacent first flow channel forming valleys 220 , 320 , the first flow channel side ridges 231
  • a projected amount of the at least one barrier ridge 230 , 330 in the first direction is set to be larger than a projected amount of the first flow channel side ridges 231 , 331 in the first direction. Accordingly, the barrier ridges 230 , 330 having a larger projected amount than the first flow channel side ridges 231 , 331 cross and abut against the ridges 23 , 33 of the opposed heat transfer plate 2 , 3 (the barrier ridges 230 , 330 or the first flow channel side ridges 231 , 331 ). As a result, the first flow channel side ridges 231 , 331 of the heat transfer portions 20 , 30 opposed to each other within the first flow channel Ra are not in contact with each other.
  • the first flow channel Ra is formed over the entire length in the third direction of the heat transfer portions 20 , 30 .
  • This configuration allows the first fluid medium A to spread in the third direction and be circulated in the second direction through the first flow channel Ra while causing the circulating resistance therewithin.
  • the entire areas or the substantially entire areas of the first surfaces Sa 1 , Sb 1 of the heat transfer portions 20 , 30 contribute to heat transfer.
  • Each of the heat transfer portions 20 , 30 of the each adjacent heat transfer plates 2 , 3 includes: the at least one barrier ridge 230 , 330 and the second flow channel forming valleys 221 , 321 , and as the ridges 23 , 33 formed on the second surface Sa 2 , Sb 2 , a plurality of second flow channel side ridges 233 , 333 each formed in the third direction between each adjacent second flow channel forming valleys 221 , 321 , the second flow channel side ridges 233 , 333 each extending from the one end to the other end of the divided area Da, Db in the second direction, and top ends of the second flow channel side ridges 233 , 333 in the mutually corresponding divided areas Da, Db of each adjacent heat transfer plates 2 , 3 with the second surfaces Sa 2 , Sb 2 of the heat transfer portions 20 , 30 opposed to each other are in contact with each other (see FIG.
  • This configuration prevents the heat transfer portions 20 , 30 from being expanded even if the fluid pressure of the first fluid medium A circulated through the first channel Ra acts on the heat transfer portions 20 , 30 . Therefore, the space constituting the second flow channel Rb is secured to ensure smooth circulation of the second fluid medium B.
  • the at least one barrier ridge 230 , 330 includes two or more barrier ridges 230 , 330 provided at intervals in the second direction, and the two or more barrier ridges 230 , 330 divide each corresponding one of the heat transfer portions 20 , 30 into three or more divided areas Da, Db (see FIG. 7 and FIG. 8 ). Accordingly, the barrier ridges 230 , 330 block circulation through the first flow channel Ra at a plurality of (two or more) positions within the first flow channel Ra. This increases the circulating resistance of the first fluid medium A within the first flow channel Ra, which consequently enhances heat, transfer performance of the first fluid medium A within the first flow channel Ra.
  • the barrier ridge 230 , 330 includes at least one bent ridge portion 232 , 332 that includes a pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b each having a proximal end and a distal end on an opposite side of the proximal end, the pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b being inclined in directions opposite to each other with respect to the centerline (vertical centerline) CL extending in the second direction or a virtual line parallel to the centerline (vertical centerline) CL, and having the distal ends thereof connected to each other (see FIG. 3 , FIG. 5 ; and FIG. 7 ).
  • the bent ridge portion 232 , 332 (the pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b ) of the barrier ridges 230 , 330 diffuses the first fluid medium A within the first flow channel Ra.
  • This increases the areas contributing to heat transfer in the heat transfer portions 20 , 30 , and consequently enhances heat transfer performance of the first fluid medium A within the first flow channel. Ra.
  • Each of the heat transfer portions 20 , 30 of the each adjacent heat transfer plates 2 , 3 includes the barrier ridge 230 , 330 having the bent ridge portion 232 , 332 , and the bent ridge portions 232 , 332 of the barrier ridges 230 , 330 of the each adjacent heat transfer plates 2 , 3 are bent in directions completely opposite to each other and include the inclined ridge portions 232 a , 232 b , 332 a , 332 b of the bent ridge portions 232 , 332 opposed to each other crossing and abutting against each other (see FIG. 7 ). Accordingly, the flow resistance of the first fluid medium A within the first flow channel Ra is increased and the diffusion effect of the first fluid medium A is also increased. As a result, heat transfer performance of the first fluid medium A within the first flow channel Ra is enhanced.
  • each of the adjacent heat transfer plates 2 , 3 includes the barrier ridges 230 , 330 and the second flow channel forming valleys 221 , 331 , without limitation thereto.
  • one of each adjacent heat transfer plates 2 , 3 may include the barrier ridges 230 , 330 and the second flow channel forming valleys 221 , 321 .
  • the second flow channel forming valleys 221 , 321 extend straightforwardly in the second direction, without limitation thereto.
  • the second flow channel forming valleys 221 , 321 may be inclined with respect to the virtual line extending in the second direction, with the prerequisite that they are continuous with the back side valleys 222 , 322 .
  • the second flow channel forming valleys 221 , 321 are required to be inclined, satisfying the condition that the inclination component (angle) with respect to the virtual line extending in the second direction is smaller than the inclination component (angle) with respect to the virtual line extending in the third direction.
  • the aforementioned embodiment was described by taking, for example, the case where two or more barrier ridges 230 , 330 are provided at intervals from each other in the second direction and divide the heat transfer portion 20 , 30 into three or more divided areas Da, Db, without limitation thereto.
  • one barrier ridge 230 , 330 may be provided on one heat transfer portion 20 , 30 and divides the heat transfer portion 20 , 30 into two divided areas Da, Db.
  • each adjacent heat transfer plates 2 , 3 with the second surfaces Sa 2 , Sb 2 of the heat transfer portions 20 , 30 opposed to each other have the top ends of the second flow channel side ridges 233 , 333 in the mutually corresponding divided areas Da, Db contacting each other, without limitation thereto.
  • the second flow channel side ridges 233 , 333 in the mutually corresponding divided areas Da, Db of each adjacent heat transfer plates 2 , 3 with the second surfaces Sa 2 , Sb 2 of the heat transfer portions 20 , 30 opposed to each other may be arranged with a clearance therebetween.
  • This configuration allows the second flow channel Rb to be formed continuously over the entire length in the second direction and the entire length in the third direction of the heat transfer portions 20 , 30 . Accordingly the circulating resistance of the second fluid medium B within the second flow channel Rb can be reduced to thereby further increase the velocity of the second fluid medium B.
  • the plurality of second flow channel side ridges 233 , 333 in the mutually corresponding divided areas Da, Db in each adjacent heat transfer plates 2 , 3 may be arranged while being displaced (for example, by 1 ⁇ 4 pitch) in the third direction.
  • This configuration avoids contact between the second flow channel side ridges 233 , 333 of the heat transfer portions 20 , 30 opposed to each other within the second flow channel Rb, and hence allows the second flow channel Rb to be continuous over the entire length in the second direction and the entire length in the third direction of the heat transfer portions 20 , 30 .
  • the circulating resistance of the second fluid medium B within the second flow channel Rb can be reduced to thereby further increase the velocity of the second fluid medium B.
  • the projected amount of the barrier ridges 230 , 330 is set to be larger than that of the first flow channel side ridges 231 , 331 so that the first flow channel side ridges 231 , 331 are configured not to be in contact with the opposed heat transfer portion 20 , 30 , without, limitation thereto.
  • the projected amount of the barrier ridges 230 , 330 may be set to be the same as the projected amount of the first flow channel side ridges 231 , 331 .
  • the plurality of first flow channel side ridges 231 , 331 in the mutually corresponding divided areas Da, Db in each adjacent heat transfer plates 2 , 3 with the first surfaces Sa 1 , Sb 1 of the heat transfer portions 20 , 30 opposed to each other may be arranged while being displaced (for example, by 1 ⁇ 4 pitch) in the third direction.
  • This configuration avoids contact between the first flow channel side ridges 231 , 331 of the heat transfer portions 20 , 30 opposed to each other within the first flow channel Ra.
  • the first flow channel Ra extends through the entirety in the second direction of the divide areas Da, Db of the heat transfer portions 20 , 30 .
  • the flow resistance of the first fluid medium A within the first flow channel Ra is increased due to the barrier ridges 230 , 330 crossing and abutting against each other, or the barrier ridges 230 , 330 crossing and abutting against the ridges 23 , 33 of the opposed heat, transfer portion 20 , 30 .
  • the barrier ridge 230 , 330 constitutes one bent ridge portion 232 , 332 including the pair of inclined ridge portions 232 a , 232 b , 332 a , 332 b , without limitation thereto.
  • the barrier ridges 230 , 330 may include a plurality of (two or more) bent ridge portions 232 , 332 .
  • the barrier ridges 230 , 330 may be formed into a curved shape when seen from the first direction.
  • the barrier ridges 230 , 330 may be formed into a corrugated shape with a plurality of curved portions joined to each other when seen from the first direction.
  • the aforementioned embodiment was described by taking, for example, the case where the plurality of barrier ridges 230 , 330 formed on the first surfaces Sa 1 , Sb 1 of the heat, transfer portions 20 , 30 are formed into the same pattern, without limitation thereto.
  • the plurality of barrier ridges 230 , 330 in a different pattern may be formed on the first surfaces Sa 1 , Sb 1 of the heat transfer portions 20 , 30 .
  • the different pattern means that the inclined ridge portions 232 a , 232 b , 332 a , 332 b have different inclination angles, the bent ridge portions 232 , 332 (the inclined ridge portions 232 a , 232 b , 332 a , 332 b ) have different inclination directions, or the barrier ridges 230 , 330 have different shapes when seen from the first direction, with the prerequisite that the barrier ridges 230 , 330 include the bent ridge portion(s) 232 , 332 .
  • the aforementioned embodiment was described by taking, for example, the case where the barrier ridges 230 , 330 including the bent ridge portions 232 , 332 are formed on each of the heat transfer portions 20 , 30 of each adjacent heat transfer plates 2 , 3 with the first surfaces Sa 1 , Sb 1 of the heat transfer portions 20 , 30 opposed to each other and the bent ridge portions 232 , 332 of the barrier ridges 230 , 330 of each adjacent heat transfer plates 2 , 3 are bent in a direction completely opposite to each other and have the inclined ridge portions 232 a , 232 b , 332 a , 332 b of the bent ridge portions 232 , 332 opposed to each other crossing and abutting against each other, without limitation thereto.
  • the barrier ridges 230 , 330 and the back side valleys 222 , 322 may extend straightforwardly in the third direction.
  • This configuration allows the barrier ridges 230 , 330 to cross the first flow channel Ra over the entire length of the first flow channel Ra, which increases the flow resistance of the first fluid medium A.
  • the first fluid medium A becomes more likely to cause the heat transfer portions 20 , 30 to be subjected to thermal influences, which consequently enhances heat transfer performance.
  • the configuration may be such that the barrier ridges 230 , 330 extending in the third direction are formed on each of the heat transfer portions 20 , 30 of each adjacent heat transfer plates 2 , 3 with the first surfaces Sa 1 , Sb 1 of the heat transfer portions 20 , 30 opposed to each other, and that the barrier ridges 230 , 330 of each of the adjacent heat transfer plates 2 , 3 are arranged while being displaced from each other in the second direction and cross and abut against the first flow channel side ridges 231 , 331 in each of the divided areas Da, Db of the opposed heat transfer portion 20 , 30 .
  • This configuration causes the barrier ridges 230 , 330 to block circulation through the first flow channel Ra at a plurality of (two or more) positions within the first flow channel Ra.
  • the circulating resistance of the first fluid medium A is increased within the first flow channel Ra, which consequently enhances heat transfer performance of the first fluid medium A within the first flow channel Ra.
  • At least two second flow channels Rb may be communicated with each other by a connection flow channel PJ that extends in the first direction at a position different from the second inflow channel Phi and the second outflow channel Pb 2 so that the second flow channel Rb located most upstream of the circulation route including the connection flow channel PJ of the second fluid medium B is connected to the second inflow channel Pb 1 and the second flow channel Rb located most downstream of the circulation route including the connection flow channel PJ of the second fluid medium B is connected to the second outflow channel Pb 2 .
  • a branch reference space Psi is formed between adjacent heat transfer plates 2 , 3 at an intermediate position in a direction in which the heat transfer plates 2 , 3 are stacked on each other (i.e. in the first direction).
  • the configuration may be such that one of the second flow channels Rb located on one side of the branch reference space Ds 1 is connected to the branch reference space Ds 1 via the connection flow channel PJ in the first direction, and that one of the second flow channels Rb located on the other side of the branch reference space Psi is connected to the branch reference space Psi via the connection flow channel PJ.
  • This configuration allows the circulation route of the second fluid medium B to be branched into at least one first system S 1 that is continuous on the one side of the branch reference space Psi in the first direction and at least one second system S 2 that is continuous on the other side of the branch reference space Psi in the first direction.
  • each of the first system S 1 and the second system S 2 may have a branch reference space (branch reference space on the downstream side) Ds 2 formed between adjacent heat transfer plates 2 , 3 that define at least one second flow channel Rb located at an intermediate position in the first direction and directly or indirectly connected to the branch reference space Ds 1 upstream thereof via the connection flow channel PJ.
  • branch reference space branch reference space on the downstream side
  • the second flow channel Rb located on one side of the branch reference space Ds 2 in the first direction is connected to the branch reference space Ds 2 on the downstream side via the connection flow channel PJ
  • the second flow channel Rb located on the other side of the branch reference space Ds 2 in the first direction is connected to the branch reference space Ds 2 on the downstream side via the connection flow channel PJ.
  • This configuration allows the circulation route of the second fluid medium B in each of the first system S 1 and the second system S 2 to be further branched into at least two systems S 1 a , S 1 b , S 2 a , S 2 b , and the second flow channel Rb located most downstream of each of the systems S 1 a , S 1 b , S 2 a , S 2 b to be connected to the second outflow channel Pb 2 .

Landscapes

  • 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)
US16/065,935 2016-01-13 2016-11-17 Plate heat exchanger Abandoned US20190011193A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2016-004234 2016-01-13
JP2016004234 2016-01-13
PCT/JP2016/084040 WO2017122428A1 (fr) 2016-01-13 2016-11-17 Échangeur de chaleur à plaques

Publications (1)

Publication Number Publication Date
US20190011193A1 true US20190011193A1 (en) 2019-01-10

Family

ID=59312157

Family Applications (1)

Application Number Title Priority Date Filing Date
US16/065,935 Abandoned US20190011193A1 (en) 2016-01-13 2016-11-17 Plate heat exchanger

Country Status (5)

Country Link
US (1) US20190011193A1 (fr)
EP (1) EP3404350B1 (fr)
JP (1) JP6407454B2 (fr)
CN (1) CN108463683A (fr)
WO (1) WO2017122428A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PT3660437T (pt) 2018-11-29 2021-08-16 Alfa Laval Corp Ab Um permutador de placa de calor e uma placa de permuta de calor para tratar uma alimentação tal como água do mar
PL3660438T3 (pl) 2018-11-29 2021-09-13 Alfa Laval Corporate Ab Prezentowany wynalazek odnosi się do płytowego wymiennika ciepła, płyty wymiennika ciepła oraz metody obróbki podawanego materiału takiego jak woda morska
JP7300500B2 (ja) * 2019-04-23 2023-06-29 株式会社日阪製作所 プレート式熱交換器
JP7181241B2 (ja) * 2020-02-05 2022-11-30 株式会社日阪製作所 プレート式熱交換器
PL4015961T3 (pl) 2020-12-15 2023-07-10 Alfa Laval Corporate Ab Płyta wymiennika ciepła
JPWO2023127625A1 (fr) * 2021-12-28 2023-07-06

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4182411A (en) * 1975-12-19 1980-01-08 Hisaka Works Ltd. Plate type condenser
US4314605A (en) * 1976-02-28 1982-02-09 Hisaka Works Ltd. Condenser
JPH07260386A (ja) * 1994-03-28 1995-10-13 Hisaka Works Ltd プレート式熱交換器
JPH08101000A (ja) * 1994-09-30 1996-04-16 Hisaka Works Ltd プレート式熱交換器
US20060060339A1 (en) * 2004-09-09 2006-03-23 Toyoaki Matsuzaki Heat exchange unit

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB580368A (en) * 1944-01-01 1946-09-05 Separator Ab Improvements in or relating to plate heat exchangers
JPS5022503B1 (fr) * 1969-06-05 1975-07-31
JPS5652223B2 (fr) * 1973-09-13 1981-12-10
SE8306795D0 (sv) * 1983-12-08 1983-12-08 Alfa Laval Thermal Ab Vermevexlarplatta
JPS60162183A (ja) * 1984-02-01 1985-08-23 フオルケル・ハンネマン 熱交換器
JP3586581B2 (ja) * 1999-03-30 2004-11-10 株式会社日阪製作所 プレート式熱交換器
JP2001099588A (ja) 1999-09-29 2001-04-13 Hisaka Works Ltd プレート式熱交換器
JP2002107074A (ja) * 2000-09-29 2002-04-10 Sanyo Electric Co Ltd プレート型熱交換器及びそれを用いたヒートポンプ給湯機
FR2848292B1 (fr) * 2002-12-05 2005-03-04 Packinox Sa Plaque d'un echangeur thermique et echangeur thermique a plaques
DE10320812B4 (de) * 2003-05-08 2007-03-01 Gea Wtt Gmbh Plattenwärmeübertrager mit einwandigen und doppelwandigen Wärmeübertragerplatten
JP2006162154A (ja) * 2004-12-07 2006-06-22 Ebara Corp 積層プレート式吸収器、吸収式ヒートポンプ及び吸収式冷凍機
US20070169916A1 (en) * 2006-01-20 2007-07-26 Wand Steven M Double-wall, vented heat exchanger
EP2233873A1 (fr) * 2009-03-12 2010-09-29 Robert Bosch GmbH Échangeur thermique à plaques
FR2954480B1 (fr) * 2009-12-17 2012-12-07 Valeo Systemes Thermiques Plaque d'echangeur de chaleur, en particulier pour un condenseur de climatisation
SE534918C2 (sv) * 2010-06-24 2012-02-14 Alfa Laval Corp Ab Värmeväxlarplatta och plattvärmeväxlare
CN105008843B (zh) * 2013-03-29 2017-05-17 株式会社日阪制作所 板式热交换器
JP6552499B2 (ja) * 2013-12-10 2019-07-31 スウェップ インターナショナル アクティエボラーグ 改良された流れを有する熱交換器

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4182411A (en) * 1975-12-19 1980-01-08 Hisaka Works Ltd. Plate type condenser
US4314605A (en) * 1976-02-28 1982-02-09 Hisaka Works Ltd. Condenser
JPH07260386A (ja) * 1994-03-28 1995-10-13 Hisaka Works Ltd プレート式熱交換器
JPH08101000A (ja) * 1994-09-30 1996-04-16 Hisaka Works Ltd プレート式熱交換器
US20060060339A1 (en) * 2004-09-09 2006-03-23 Toyoaki Matsuzaki Heat exchange unit

Also Published As

Publication number Publication date
EP3404350A4 (fr) 2019-09-18
EP3404350A1 (fr) 2018-11-21
WO2017122428A1 (fr) 2017-07-20
JPWO2017122428A1 (ja) 2018-07-12
EP3404350B1 (fr) 2022-08-17
JP6407454B2 (ja) 2018-10-17
CN108463683A (zh) 2018-08-28

Similar Documents

Publication Publication Date Title
US20190011193A1 (en) Plate heat exchanger
US6823934B2 (en) Heat transfer plate and plate pack for use in a plate heat exchanger
JP2006214646A (ja) 熱交換用プレート
JP2020505574A (ja) 熱交換板および熱交換器
EP3647710B1 (fr) Échangeur de chaleur de type à plaques
JP4504092B2 (ja) プレート式熱交換器
EP3627087B1 (fr) Échangeur de chaleur de type à plaques
JP2004184075A (ja) 伝熱プレート及びプレート式熱交換器
JP5085723B2 (ja) プレート式熱交換器
KR20180115755A (ko) 판 열교환기를 위한 열교환기 판, 및 판 열교환기
US10281222B2 (en) Heat exchanger
JPH0579790A (ja) 熱交換器
JP7100074B2 (ja) プレート式熱交換器
JP2006064281A (ja) プレート式熱交換器
JP2008190786A (ja) プレート式熱交換器
EP3978856A1 (fr) Échangeur de chaleur à plaques et distributeur pour échangeur de chaleur à plaques
WO2020045595A1 (fr) Échangeur de chaleur à plaques
JP6281422B2 (ja) 積層型熱交換器
JP6235645B2 (ja) プレート式熱交換器
KR100819010B1 (ko) 열교환기
JP5933605B2 (ja) プレート式熱交換器
JP5244162B2 (ja) プレート式熱交換器
JP5557893B2 (ja) プレート式熱交換器
JP2019215096A (ja) 積層型熱交換器
JP2019070472A (ja) プレート式熱交換器

Legal Events

Date Code Title Description
AS Assignment

Owner name: HISAKA WORKS, LTD., JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:TANAKA, NOBUO;REEL/FRAME:046194/0493

Effective date: 20180228

STPP Information on status: patent application and granting procedure in general

Free format text: DOCKETED NEW CASE - READY FOR EXAMINATION

STPP Information on status: patent application and granting procedure in general

Free format text: NON FINAL ACTION MAILED

STPP Information on status: patent application and granting procedure in general

Free format text: RESPONSE TO NON-FINAL OFFICE ACTION ENTERED AND FORWARDED TO EXAMINER

STPP Information on status: patent application and granting procedure in general

Free format text: FINAL REJECTION MAILED

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION