EP3647710A1

EP3647710A1 - Plate type heat exchanger

Info

Publication number: EP3647710A1
Application number: EP17910745.3A
Authority: EP
Inventors: Nobuo Tanaka
Original assignee: Hisaka Works Ltd
Current assignee: Hisaka Works Ltd
Priority date: 2017-05-25
Filing date: 2017-05-25
Publication date: 2020-05-06
Anticipated expiration: 2037-05-25
Also published as: JPWO2018216165A1; CN110691954A; JP6799680B2; CN110691954B; EP3647710A4; EP3647710B1; WO2018216165A1

Abstract

Provided in the present invention is a plate heat exchanger capable of improving performance for transferring heat to heat transfer portions within a flow channel through which a second fluid medium that causes phase change as a result of its heat exchange with a first fluid medium is circulated. In the present invention, a first flow channel through which the first fluid medium is circulated is formed between first surfaces of each two adjacent heat transfer plates, and a second flow channel through which the second fluid medium is circulated is formed between second surfaces of each two adjacent heat transfer plates. Each of the first surfaces of the heat transfer portions includes a plurality of first ridges arranged at intervals from each other, a barrier ridge that is lower than the first ridges and extends in a direction intersecting with the first ridges, and a plurality of first valleys each formed between each two adjacent first ridges. Each of the second surfaces of the heat transfer portions includes a plurality of second valleys being in a front-back relationship with the first ridges. The barrier ridge on each of the two adjacent heat transfer plates has a longitudinal dimension set to be shorter than the entire length in a third direction of the heat transfer portion, and the barrier ridge on one of the two adjacent heat transfer plates is arranged at a position displaced in at least one of a second direction or the third direction, and crosses and abuts against the first ridges of the opposed heat transfer plate.

Description

FIELD

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

BACKGROUND

Conventionally, 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 and a second surface in a first direction. Specifically, the heat transfer portion has the first surface on which ridges and valleys are formed, and the 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.
On each of the first surface and the second surface of the heat transfer portion, the ridges intersect with a centerline (hereinafter referred to as vertical centerline) of the heat transfer portion extending in a second direction orthogonal to the 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.
In this state, the ridges on the heat transfer portions of each two adjacent heat transfer plates cross and abut against each other, and the valleys on the heat transfer portions form spaces between the heat transfer portions of each two adjacent heat transfer plates. That is, a first flow channel for circulating a 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. Also, a second flow channel for circulating a 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. With this configuration, the plate heat exchanger enables heat exchange between the first fluid medium within the first flow channels and the second fluid medium within the second flow channels, through the heat transfer portions that separate the first flow channels and the second flow channels (see, for example, Patent Literature 1).
There are some cases where 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. There are also other cases where 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 channels and the second fluid medium within the second flow channels.
However, the conventional plate heat exchanger, when 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 subjected to condensation or evaporation.
Specifically, 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 circulating resistance of both the first flow channels and the second flow channels.
Generally, a fluid medium that does not cause phase change (a fluid medium having single-phase flow) is employed as the first fluid medium. Therefore, increase in the circulating 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 circulating resistance in the first flow channels consequently becomes a factor for improved heat exchange performance.
In contrast, a fluid medium that causes phase change (a fluid medium having two-phase flow that contains liquid and gas), such as fluorocarbons, is employed as the second fluid medium. As a result, liquid film of the second fluid medium is formed on the second surfaces of the heat transfer portions that define the second flow channels. For the purpose of improving the heat transfer performance, therefore, it is necessary to increase the velocity of the second fluid medium and disturb flow of the liquid film formed on the second surfaces of the heat transfer portions.
However, since 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 in the third direction of the heat transfer portion, the ridges on the heat transfer portions 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 to cross (intersect with) the flow of the second fluid medium within the second flow channels, and thereby increase the circulating resistance of the second fluid medium within the second flow channels.
Therefore, 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 surfaces of the heat transfer portions.
Hence, 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.

CITATION LIST

Patent Literature

Patent Literature 1: JP 2001-99588 A

SUMMARY

Technical Problem

It is therefore an object of the present invention to provide a plate heat exchanger capable of improving performance for transferring, to the heat transfer portions, heat of the second fluid medium that causes the phase change as a result of its heat exchange with the first fluid medium.

Solution to Problem

A plate heat exchanger of the present invention includes 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 one of the plurality of heat transfer plates adjacent to the each 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 one of the plurality of heat transfer plates adjacent to the each 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 two of the plurality of heat transfer plates, and a second flow channel through which a second fluid medium is circulated in the second direction is formed between the second surfaces of the heat transfer portions of each adjacent heat transfer plates, wherein each of the heat transfer portions of each adjacent two of the plurality of heat transfer plates includes: as the ridges formed on the first surface, a plurality of first ridges arranged at intervals from each other in a direction intersecting with the first direction and the second direction, the plurality of first ridges extending in the second direction or in a synthetic direction that has a component in the second direction, and at least one barrier ridge that is lower than the plurality of first ridges formed on the first surface, the at least one barrier ridge extending in a direction intersecting with the plurality of first ridges; as the valleys formed on the first surface, a plurality of first valleys each formed between each adjacent two of the plurality of first ridges in the direction intersecting with the first direction and the second direction; and, as the valleys formed on the second surface, a plurality of second valleys being in a front-back relationship with the plurality of first ridges, wherein each of the plurality of first ridges of one of each adjacent two of the plurality of heat transfer plates is located between each adjacent two of the plurality of first ridges of the opposed heat transfer plate, wherein the at least one barrier ridge on each of each adjacent two of the plurality of heat transfer plates has a longitudinal dimension set to be shorter than the entire length in a third direction of the heat transfer portion, the third direction being orthogonal to the first direction and the second direction, and wherein the at least one barrier ridge on one of each adjacent two of the plurality of heat transfer plates is arranged at a position displaced in at least one of the second direction and the third direction from the at least one barrier ridge on the opposed heat transfer plate, and crosses and abuts against the plurality of first ridges of the opposed heat transfer plate.
According to one aspect of the present invention, the configuration may be such that each of the heat transfer portions of each adjacent two of the plurality of heat transfer plates includes a plurality of barrier ridges, and the plurality of barrier ridges are aligned at intervals from each other in the second direction.
According to another aspect of the present invention, it is preferable that the heat transfer portion of one heat transfer plate out of each adjacent two of the plurality of heat transfer plates have at least one row constituted by a plurality of barrier ridges arranged at intervals from each other in the second direction, the heat transfer portion of the other heat transfer plate out of the each adjacent two of the plurality of heat transfer plates have at least two rows each constituted by a plurality of barrier ridges arranged at intervals from each other in the second direction, and each of the at least one row on the one heat transfer plate out of the each adjacent two of the plurality of heat transfer plates be positioned between each adjacent two of the at least two rows on the other heat transfer plate out of the each adjacent two of the plurality of heat transfer plates.
In this case, it is preferable that each of the plurality of barrier ridges constituting the at least one row on the one heat transfer plate out of the each adjacent two of the plurality of heat transfer plates be positioned between each adjacent two of the plurality of barrier ridges constituting each of the at least two rows on the other heat transfer plate out of the each adjacent two of the plurality of heat transfer plates.
According to another aspect of the present invention, each of the at least one barrier ridge may extend straight in the third direction.
According to still another aspect of the present invention, it is preferable that each of the heat transfer portions of each adjacent two of the plurality of heat transfer plates include, as the ridges formed on the second surface, a plurality of second ridges being in a front-back relationship with the plurality of first valleys, and that the plurality of second ridges of one of each adjacent two of the plurality of heat transfer plates be overlapped with the plurality of second ridges of the opposed heat transfer plate and be in contact with top ends of the plurality of second ridges of the opposed heat transfer plate.

BRIEF DESCRIPTION OF THE 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 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 schematic view showing the circulation route of the first fluid medium in first flow channels and the circulation route of the second fluid medium in second flow channels, of 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, as seen from a second direction thereof.
Fig. 9 is a cross-sectional view taken along line IX-IX in Fig. 8, with an illustration of flows of the fluid media in the first flow channels and the second flow channels.
Fig. 10 is a cross-sectional view taken along line X-X in Fig. 8, with an illustration of the flows of the fluid media in the first flow channels and the second flow channels.
Fig. 11 is a cross-sectional view taken along line XI-XI in Fig. 8, with an illustration of the flows of the fluid media in the first flow channels and the second flow channels.
Fig. 12 is a view showing the flows of the first fluid medium within the first flow channel in the plate heat exchanger according to the embodiment.
Fig. 13 is a view showing the flows of the second fluid medium within the second flow channel in the plate heat exchanger according to the embodiment.
Fig. 14 is a schematic partial cross-sectional view of a plate heat exchanger according to another embodiment of the present invention, as seen from a second direction thereof.
Fig. 15 is a schematic partial cross-sectional view of a plate heat exchanger according to still another embodiment of the present invention, as seen from a second direction thereof.
Fig. 16 is a schematic partial cross-sectional view of a plate heat exchanger according to still another embodiment of the present invention, as seen from a second direction thereof.
Fig. 17 is a schematic view showing a circulation route of a first fluid medium in first flow channels and a circulation route of a second fluid medium in second flow channels, of a plate heat exchanger according to still another embodiment of the present invention.
Fig. 18 is a schematic view showing a circulation route of a first fluid medium in first flow channels and a circulation route of a second fluid medium in second flow channels, of a plate heat exchanger according to still another embodiment of the present invention.

DESCRIPTION OF EMBODIMENTS

A description will be hereinafter made for a plate heat exchanger according to a first embodiment of the present invention with reference to the attached drawings.
As shown in Fig. 1 and Fig. 2, a plate heat exchanger 1 according to the first embodiment (hereinafter referred to simply as heat exchanger in this embodiment) includes three or more heat transfer plates 2, 3.
The three or more heat transfer plates 2, 3 are stacked on each other in a first direction. In the heat exchanger 1 according to this embodiment, the three or more heat transfer plates 2, 3 are composed of two kinds of heat transfer plates. The two kinds of heat transfer plates 2, 3 are arranged alternately in the first direction.
With this configuration, in the heat exchanger 1, first flow channels Ra through which a first fluid medium A is circulated and second flow channels Rb through which a second fluid medium B is circulated are alternately formed in the first direction with the heat transfer plates 2, 3 respectively interposed therebetween.
The two kinds of heat transfer plates 2, 3 will be specifically described. The two kinds of heat transfer plates 2, 3 have common features and different features. First, the common features of the two kinds of heat transfer plates 2, 3 will be described.
As shown in Fig. 3 to Fig. 6, the heat transfer plates 2, 3 respectively include heat transfer portions 20, 30 that respectively have first surfaces Sa1, Sb1 and second surfaces Sa2, Sb2 facing opposite to the first surfaces Sa1, Sb1, 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 the first direction. Accordingly, the first surfaces Sa1, Sb1 and the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 are aligned in the first direction. 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. In this embodiment, 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 Sa1, Sb1 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 Sa2, Sb2 side.
The projected amounts on the second surfaces Sa2, Sb2 sides of the area surrounding each of the one openings 200, 300 and the area surrounding each of the one openings 201, 301 in the other ends in the one ends in the second direction of the heat transfer portions 20, 30 are set so that these areas can respectively contact the corresponding areas respectively surrounding the openings 200, 201, 300, 301 (i.e., the one openings 200, 300 in the one ends and the one openings 201, 301 in the other ends) of the heat transfer portions 20, 30 of each two adjacent heat transfer plates 2, 3 aligned with each other in the first direction.
In contrast, 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 Sa2, Sb2 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 projected on the first surfaces Sa1, Sb1 side.
The projected amounts on the first surfaces Sa1, Sb1 sides of the area surrounding each of the other openings 203, 303 in the one ends and the 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 set so that these areas can respectively contact the corresponding areas respectively surrounding the openings 202, 203, 302, 303 (i.e., the other openings 202, 302 in the one ends and the other openings 203, 303 in the other ends) of the heat transfer portions 20, 30 of each two adjacent heat transfer plates 2, 3 aligned with each other in the first direction. In Fig. 3 to Fig. 6, 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 Sa1, Sb1 and the second surfaces Sa2, Sb2 to be distinguishable.
In this embodiment, 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 Sa1, Sb1 and the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30. Each of the first surfaces Sa1, Sb1 and the second surfaces Sa2, Sb2 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.
More specifically, 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 Sa1, Sb1 of the heat transfer portions 20, 30 are in a front-back relationship with the ridges 23, 33 formed on the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30. The ridges 23, 33 formed on the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 are in a front-back relationship with the valleys 22, 32 formed on the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30. That is, the deformation of the metal plate by press molding allows the valleys 22, 32 formed on the first surfaces Sa1, Sb1 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 Sa2, Sb2 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 Sa1, Sb1 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 Sa2, Sb2 of the heat transfer portions 20, 30.
As shown in Fig. 3 and Fig. 5, the heat transfer portion 20, 30 includes, as the valleys 22, 32 formed on the first surface Sa1, Sb1, a plurality of first valleys 220, 320 extending in the second direction and arranged 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 Sa1, Sb1, a plurality of first ridges 230, 330 each extending in the second direction between each two first valleys 220, 230 adjacent to each other in the third direction. That is, in the first surface Sa1, Sb1 of the heat transfer portion 20, 30, the first valleys 220, 320 and the first ridges 230, 330 are alternately arranged in the third direction.
Further, the heat transfer portion 20, 30 includes, as the ridges 23, 33 formed on the first surface Sa1, Sb1, at least one barrier ridge 231, 331 that is lower than the first ridges 230, 330 formed on the first surface Sa1, Sb1, the at least one barrier ridge 231, 331 extending in a direction intersecting with the plurality of first ridges 230, 330.
Each of the plurality of first valleys 220, 320 has the same or substantially the same width in the third direction as each of the plurality of first ridges 230, 330. The internal surfaces defining the first valleys 220, 320 are continuous with the external surfaces defining the first ridges 230, 330. With this configuration, the first surface Sa1, Sb1 of the heat transfer portion 20, 30 has a corrugated shape with projections and recesses aligned in the first direction.
Based on this, the boundary between a specific first valley 220, 320 out of the plurality of first valleys 220, 320 and a specific first ridge 230, 330 out of the plurality of first ridges 230, 330 that is adjacent to the specific first valley 220, 320 is located on the vertical centerline CL of the first surface Sa1, Sb1 of the heat transfer portion 20, 30.
That is, the specific first valley 220, 320 or the specific first ridge 230, 330 is arranged while being displaced in the third direction from the vertical centerline CL by one-fourth of the distance between adjacent first ridges 230, 330 with one first valley 220, 320 interposed therebetween, or the distance between each two adjacent first valleys 220, 320 with one first ridge 230, 330 interposed therebetween.
In this embodiment, the first surface Sa1,Sb1 of the heat transfer portion 20, 30 has a plurality of barrier ridges 231, 331. The plurality of barrier ridges 231, 331 are arranged at intervals from each other in the second direction. Each of the plurality of barrier ridges 231, 331 is lower than the first ridges 230, 330 as aforementioned. Specifically, the projected amount of the barrier ridges 231, 331 from a virtual plane (the virtual plane extending in the second direction and the third direction) passing through top ends of a plurality of second ridges 233, 333, which will be described later, formed on the second surface Sa2, Sb2 is smaller than that of the first ridges 230, 330. Accordingly, the top ends of the barrier ridges 231, 331 are located closer in the first direction to the second surface Sa2, Sb2 than the top ends of the first ridges 230, 330. That is, the top ends of the barrier ridges 231, 331 are located between the top ends of the first ridges 230, 330 and the bottom ends of the first valleys 220, 320.
As will be later described in details, in the state where the plurality of heat transfer plates 2, 3 are stacked on each other in this embodiment, each of the first ridges 230, 330 of one heat transfer plate 2, 3 of each two adjacent heat transfer plates 2, 3 is located between each two adjacent first ridges 230, 330 (i.e., located at positions corresponding to the first valleys 220, 320) of the other heat transfer plate 2, 3 of the each two adjacent heat transfer plates 2, 3.
Accordingly, the distance in the first direction between the top ends of the first ridges 230, 330 and the top ends of the barrier ridges 231, 331 is set so that the clearance between the first ridges 230, 330 of one heat transfer plate 2, 3 out of each two adjacent heat transfer plates 2, 3 and the first valleys 220, 320 of the other heat transfer plate 2, 3 can secure circulation of the first fluid medium A.
Specifically, in each of the heat transfer plates 2, 3 in this embodiment, the plurality of first valleys 220, 320 are set to have the same width and the plurality of first ridges 230, 330 are set to have the same width. In each of the heat transfer plates 2, 3, the first valleys 220, 320 and the first ridges 230, 330 are set to have substantially the same width.
Accordingly, if the first ridges 230, 330 of one heat transfer plate 2, 3 out of each two adjacent heat transfer plates 2, 3 are located too close to the first valleys 220, 320 of the other heat transfer plate 2, 3 out of the each two adjacent heat transfer plate 2, 3, the clearances between both sides in the width direction of the first ridges 230, 330 and both sides in the width direction of the first valleys 220, 320 will disappear, or become extremely narrow as compared with the clearances between the top ends of the first ridges 230, 330 and the bottom ends of the first valleys 220, 320.
Thus, in this embodiment, the distance in the first direction between the top ends of the first ridges 230, 330 and the top ends of the barrier ridges 231, 331 is set so that the clearances between the both sides in the width direction of each of the first ridges 230, 330 and the both sides in the width direction of each of the first valleys 220, 320 have a distance to secure circulation of the first fluid medium A.
In this embodiment, the barrier ridges 231, 331 intersect with the plurality of first ridges 230, 330 and the plurality of first valleys 220, 320. In this embodiment, the barrier ridges 231, 331 extend in the third direction. The barrier ridges 231, 331 are set to have a length shorter than the entire length in the third direction of the heat transfer portion 20, 30. That is, the length is set so that each of the barrier ridges 231, 331 intersects with the first ridges 230, 330 and the first valleys 220, 320, the number of which is smaller than the total number of the plurality of first ridges 230, 330 and the plurality of first valleys 220, 320 aligned with each other over the entire length in the third direction of the heat transfer portion 20, 30.
More specifically, the length in the extending direction (longitudinal direction) of the barrier ridge 231, 331 is set to 1/2 or less of the entire length in the third direction of the heat transfer portion 20, 30. In this embodiment, the length in the extending direction (longitudinal direction) of the barrier ridge 231, 331 is set to 1/3 or less of the entire length in the third direction of the heat transfer portion 20, 30.
Since the length in the extending direction (longitudinal direction) of each of the barrier ridges 231, 331 is set to 1/3 or less of the entire length in the third direction of the heat transfer portion 20, 30, as described above, a plurality of rows each constituted by the plurality of barrier ridges 231, 331 aligned at intervals from each other in the second direction are provided at intervals from each other in the third direction on the first surface Sa1, Sb1 of the heat transfer portion 20, 30. That is, the plurality of barrier ridges 231, 331 are arranged in a matrix form on the first surface Sa1, Sb1 of the heat transfer portion 20, 30.
The number and positions of the barrier ridges 231, 331 in each of the rows correspond to each other. Thus, those barrier ridges 231, 331 corresponding to each other between the different rows are aligned with each other in the third direction.
Here, the distance between each two adjacent rows of the barrier ridges 231, 331 (i.e., the distance between the barrier ridges 231, 331 adjacent to each other in the third direction) is set to be equal to or less than the length in the extending direction (longitudinal direction) of each of the barrier ridges 231, 331. In this embodiment, the distance between each two adjacent rows of the barrier ridges 231, 331 (i.e., the distance between the barrier ridges 231, 331 adjacent to each other in the third direction) is set to be shorter than the length in the extending direction (longitudinal direction) of each of the barrier ridges 231, 331.
Since the length in the extending direction (longitudinal direction) of each of the barrier ridges 231, 331 is set to 1/3 or less (1/2 or less in this embodiment) of the entire length in the third direction of the heat transfer portion 20, 30, as described above, some of the first valleys 220, 320 and the first ridges 230, 330 on the first surface Sa1, Sa2 of the heat transfer portion 20, 30 are continuous in the second direction while the remaining ones are divided at a plurality of places in the second direction by the barrier ridges 231, 331. At least one end of each of the divided first valleys 220, 320 and at least one end of each of the divided first ridges 230, 330 are joined to a corresponding one of the barrier ridges 231, 331.
In this embodiment, the divided first valleys 220, 320 are aligned with each other in the second direction. Accordingly, the divided first ridges 230, 330 are also aligned with each other in the second direction.
As shown in Fig. 4 and Fig. 6, the heat transfer portion 20, 30 includes, as the valleys 22, 32 formed on the second surface Sa2, Sb2, a plurality of second valleys 221, 321 extending in the second direction and arranged 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 Sa2, Sb2, a plurality of second ridges 233, 333 each extending in the second direction between each two second valleys 221, 231 adjacent to each other in the third direction. That is, in the second surface Sa2, Sb2 of the heat transfer portion 20, 30, the second valleys 221, 321 and the second ridges 233, 333 are alternately arranged in the third direction.
Further, the heat transfer portion 20, 30 includes, as the valleys 22, 32 formed on the second surface Sa2, Sb2, valleys (hereinafter referred to as back side valleys) 222, 322 formed respectively on the back sides of the barrier ridges 231, 331 on the first surface Sa1, Sb1.
The second valleys 221, 321 are the valleys 22, 32 formed on the back sides of the first ridges 230, 330 on the first surface Sa1, Sb1. Thus, the second valleys 221, 321 extend in the second direction. The second ridges 233, 333 are the ridges 23, 33 formed on the back sides of the first valleys 220 and 320 on the first surface Sa1, Sb1. Thus, the second ridges 233, 333 extend in the second direction.
The internal surfaces defining the second valleys 221, 321 are continuous with the external surfaces defining the second ridges 233, 333. With this configuration, the second surface Sa2, Sb2 of the heat transfer portion 20, 30 has a corrugated shape with projections and recesses in the third direction.
The back side valleys 222, 322 are formed in the same pattern as the barrier ridges 231, 331 except that they have a reversed concavo-convex relationship.
In this embodiment, the back side valleys 222, 322 intersect with the plurality of second ridges 233, 333 and the plurality of second valleys 221, 321. In this embodiment, the back side valleys 222, 322 are set to have a length shorter than the entire length in the third direction of the heat transfer portion 20, 30. That is, the length is set so that each of the back side valleys 222, 322 intersects with the second ridges 233, 333 and the second valleys 221, 321, the number of which is smaller than the total number of the plurality of second ridges 233, 333 and the plurality of second valleys 221, 321 aligned with each other over the entire length in the third direction of the heat transfer portion 20, 30.
More specifically, the length in the extending direction (longitudinal direction) of the back side valley 222, 322 is set to 1/2 or less of the entire length in the third direction of the heat transfer portion 20, 30. In this embodiment, the length in the extending direction (longitudinal direction) of the back side valley 222, 322 is set to 1/3 or less of the entire length in the third direction of the heat transfer portion 20, 30.
Since the length in the extending direction (longitudinal direction) of each of the back side valleys 222, 322 is set to 1/3 or less of the entire length in the third direction of the heat transfer portion 20, 30, as described above, a plurality of rows each constituted by the plurality of back side valleys 222, 322 aligned at intervals from each other in the second direction are provided at intervals from each other in the third direction on the second surface Sa2, Sb2 of the heat transfer portion 20, 30. That is, the plurality of back side valleys 222, 322 are arranged in a matrix form on the second surface Sa2, Sb2 of the heat transfer portion 20, 30.
The number and positions of the back side valleys 222, 322 in each of the rows correspond to each other. Thus, those back side valleys 222, 322 corresponding to each other between the different rows are aligned with each other in the third direction.
Here, the distance between each two adjacent rows of the back side valleys 222, 322 (i.e., the distance between the back side valleys 222, 322 adjacent to each other in the third direction) is set to be equal to or less than the length in the extending direction (longitudinal direction) of each of the back side valleys 222, 322. In this embodiment, the distance between each two adjacent rows of the back side valleys 222, 322 (i.e., the distance between the back side valleys 222, 322 adjacent to each other in the third direction) is set to be shorter than the length in the extending direction (longitudinal direction) of each of the back side valleys 222, 322.
Since the length in the extending direction (longitudinal direction) of each of the back side valleys 222, 322 is set to 1/3 or less (1/2 or less in this embodiment) of the entire length in the third direction of the heat transfer portion 20, 30, as described above, some of the second valleys 221, 321 and the second ridges 233, 333 on the second surface Sa2, Sa2 of the heat transfer portion 20, 30 are continuous in the second direction while the remaining ones are divided at a plurality of places in the second direction by the back side valleys 222, 322. At least one end of each of the divided second valleys 221, 321 and at least one end of each of the divided second ridges 233, 333 are joined to a corresponding one of the back side valleys 222, 322. That is, the divided second valleys 221, 321 are open to the inside of the back side valleys 222, 322.
In this embodiment, the divided second valleys 221, 321 are aligned with each other in the second direction. Accordingly, the divided second ridges 233, 333 are also aligned with each other in the second direction.
The common features of the two kinds of heat transfer plates 2, 3 have been described as above. Next, the different features between the two kinds of heat transfer plates 2, 3 will be described.
As shown in Fig. 3 and Fig. 5, the first ridges 230 on the first surface Sa1 of one heat transfer plate (hereinafter referred to as first heat transfer plate) 2 out of the two kinds of heat transfer plates 2, 3 are arranged while being positionally displaced in the third direction from the first ridges 330 on the first surface Sb1 of the other heat transfer plate (hereinafter referred to as second heat transfer plate) 3 out of the two kinds of heat transfer plates 2, 3. That is, in the state where the first surface Sa1 of the heat transfer portion 20 of the first heat transfer plate 2 is opposed to the first surface Sb1 of the heat transfer portion 30 of the second heat transfer plate 3, the first valleys 220, 320 and the first ridges 230, 330 are respectively arranged so that the first ridges 230 of the first heat transfer plate 2 are opposed to the first valleys 320 of the second heat transfer plate 3 and that the first ridges 330 of the second heat transfer plate 3 are opposed to the first valleys 220 of the first heat transfer plate 2.
In this embodiment, the first heat transfer plate 2 and the second heat transfer plate 3 are different from each other in the number and arrangement pattern of the barrier ridges 231, 331 on the first surfaces Sa1, Sb1. That is, the first heat transfer plate 2 and the second heat transfer plate 3 are different from each other in the number of rows of the barrier ridges 231, 331 on the first surfaces Sa1, Sb1 and the arrangement pattern of the barrier ridges 231, 331 in each of the rows.
Specifically, the number of rows of the barrier ridges 331 arranged at intervals from each other in the third direction on the first surface Sb1 of the heat transfer plate 3 is smaller by one than the number of rows of the barrier ridges 231 arranged at intervals from each other in the third direction on the first surface Sa1 of the heat transfer plate 2. Further, the number of barrier ridges 231 in each of the rows on the first surface Sb1 of the second heat transfer plate 3 is smaller by one than the number of barrier ridges 231 in each of the rows on the first surface Sa1 of the first heat transfer plate 2.
Accordingly, the position of each of the rows of the barrier ridges 231 on the first surface Sa1 of the first heat transfer plate 2 corresponds to the position between each two adjacent rows of the barrier ridges 331 on the first surface Sb1 of the second heat transfer plate 3, and the position of each of the barrier ridges 331 on the first surface Sb1 of the second heat transfer plate 3 corresponds to the position between each two adjacent rows of the barrier ridges 231 on the first surface Sa1 of the first heat transfer plate 2. The position of each of the barrier ridges 231 in each of the rows on the first surface Sa1 of the first heat transfer plate 2 corresponds to the position between each two adjacent barrier ridges 331 in each of the rows on the first surface Sb1 of the second heat transfer plate 3 (i.e., the intermediate position between each two adjacent barrier ridges 331 in the second direction), and the position of each of the barrier ridges 331 in each of the rows on the first surface Sb1 of the second heat transfer plate 3 corresponds to the position between each two adjacent barrier ridges 231 in each of the rows on the first surface Sa1 of the first heat transfer plate 2 (i.e., the intermediate position between each two adjacent barrier ridges 231 in the second direction).
As shown in Fig. 3, each of the first heat transfer plates 2 includes the fitting portion 21 projecting on the first surface Sa1 side of the heat transfer portion 20. In contrast, as shown in Fig. 6, each of the second heat transfer plates 3 includes the fitting portion 31 projecting on the second surface Sb2 side of the heat transfer portion 30.
Each of the plurality of heat transfer plates 2, 3 (the first heat transfer plates 2 and the second heat transfer plates 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. In this embodiment, the first heat transfer plates 2 and the second heat transfer plates 3 are alternately stacked on each other in the first direction. At this time, each of the plurality of heat transfer plates 2, 3 has the first surface Sa1, Sb1 of its heat transfer portion 20, 30 opposed to the first surface Sa1, Sb1 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 Sa2, Sb2 of its heat transfer portion 20, 30 opposed to the second surface Sa2, Sb2 of the heat transfer portion 20, 30 of the adjacent heat transfer plate 2, 3 on the other side in the first direction.
With this configuration, as shown in Fig. 2 and Fig. 7, the first channels Ra through which the first fluid medium A is circulated in the second direction and the second flow channels Rb through which the second fluid medium B is circulated in the second direction are alternately formed with the heat transfer portions 20, 30 of the heat transfer plates 2, 3 respectively interposed therebetween. That is, each of the first flow channels Ra through which the first fluid medium A is circulated is formed between the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 of each two adjacent heat transfer plates 2, 3, and each of the second flow channels Ra through which the second fluid medium B is circulated is formed between the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of each two adjacent heat transfer plates 2, 3.
In this state, 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, as shown in Fig. 2. The areas respectively surrounding the openings 200, 201, 202, 203, 300, 301, 302, 303 that are opposed to and projected toward each other contact each other. This configuration forms the first inflow channel Pa1 for supplying the first fluid medium A into the first flow channels Ra, the first outflow channel Pa2 for causing the first fluid medium A to flow out of the first flow channels Ra, the second inflow channel Pb 1 for supplying the second fluid medium B into the second flow channels Rb, and the second outflow channel Pb2 for causing the second fluid medium B to flow out of the second flow channels Rb.
More specifically, when the plurality of heat transfer plates 2, 3 are stacked on each other, 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. When a plurality of pairs are stacked on each other, every other pair is turned 180 degrees upside down about a virtual line extending in the first direction. In this state, 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 over 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.
Thus, as shown in Fig. 8 to Fig. 11, on the first surfaces Sa1, Sb1 sides of each two adjacent heat transfer plates 2, 3, the first ridges 230 of the first heat transfer plate 2 (heat transfer portion 20) are opposed to the first valleys 320 of the second heat transfer plate 3 (heat transfer portion 30), and the first valleys 220 of the first heat transfer plate 2 (heat transfer portion 20) are opposed to the first ridges 330 of the second heat transfer plate 3 (heat transfer portion 30).
On the first heat transfer plate 2, the barrier ridges 231 are lower than the first ridges 230, and on the second heat transfer plate 3, the barrier ridges 331 are lower than the first ridges 330; thus, the barrier ridges 231 of the first heat transfer plate 2 cross and abut against the first ridges 330 of the second heat transfer plate 3, and the barrier ridges 331 of the second heat transfer plate 3 cross and abut against the first ridges 230 of the first heat transfer plate 2.
In contrast, on the second surfaces Sa2, Sb2 sides of each two adjacent heat transfer plates 2, 3, the second ridges 233 of the first heat transfer plate 2 (heat transfer portion 20) are opposed to the second ridges 333 of the second heat transfer plate 3 (heat transfer portion 30), and the second valleys 221 of the first heat transfer plate 2 (heat transfer portion 20) are opposed to the second valleys 321 of the second heat transfer plate 3 (heat transfer portion 30). That is, on the first surface Sa1, Sb1 of the heat transfer portion 20, 30 of each of the first heat transfer plate 2 and the second heat transfer plate 3, the boundary between a specific first valley 220, 320 out of the plurality of first valleys 220, 320 and a specific first ridge 230, 330 out of the plurality of first ridges 230, 330 that is adjacent to the specific first valley 220, 320 is located on the vertical centerline CL. Thus, turning the first heat transfer plates 2 and the second heat transfer plates 3 180° upside down as aforementioned causes the second ridges 233, 333 of each two adjacent heat transfer plates 2, 3 to be opposed to each other and causes their top ends to be in contact with each other.
With this configuration, as shown in Fig. 2, 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 Sa1, Sb1 of the heat transfer portions 20, 30 of each two 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 formed between the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of each two adjacent heat transfer plates 2, 3.
Further, as described above, 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 contact each other. This configuration forms the first inflow channel Pa1 for supplying the first fluid medium A into the first flow channels Ra, the first outflow channel Pa2 for causing the first fluid medium A to flow out of the first flow channels Ra, the second inflow channel Pb 1 for supplying the second fluid medium B into the second flow channels Rb, and the second outflow channel Pb2 for causing the second fluid medium B to flow out of the second flow channels Rb.
In the heat exchanger 1 according to this embodiment, the contacted portions between each two 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 (contacted portions) of the adjacent heat transfer plates 2, 3 to be sealed.
The heat exchanger 1 according to this embodiment has been described as above. As shown in Fig. 2, Fig. 7, and Fig. 12, the first fluid medium A flows from the first inflow channel Pa1 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 Pa2. In contrast, as shown in Fig. 2, Fig. 7, and Fig. 13, 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 plurality of second flow channels Rb in the second direction, and flows out to the second outflow channel Pb2.
In this embodiment, as shown in Fig. 12, 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. As shown in Fig. 13, in contrast, 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.
At this time, 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. As a result, 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.
As described above, a plate heat exchanger 1 according to this embodiment includes a plurality of heat transfer plates 2, 3 each including a heat transfer portion 20, 30 having a first surface Sa1, Sb1 on which ridges 23, 33 and valleys 22, 32 are formed, and a second surface Sa2, Sb2 that is opposed to the first surface Sa1, Sb1 and on which valleys 22, 32 being in a front-back relationship with the ridges 23, 33 of the first surface Sa1, Sb1 and ridges 23, 33 being in a front-back relationship with the valleys 22, 32 of the first surface Sa1, Sb1 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 Sa1, Sb1 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 Sa1, Sb1 of the heat transfer portion 20, 30 of one of the plurality of heat transfer plates 2, 3 adjacent to the each heat transfer plate 2, 3 on one side in the first direction, and the second surface Sa2, Sb2 of the heat transfer portion 20, 30 of each of the plurality of heat transfer plates 2, 3 is arranged opposed to the second surface Sa2, Sb2 of the heat transfer portion 20, 30 of one of the plurality of heat transfer plates 2, 3 adjacent to the each heat transfer plate 2, 3 on an other side in the first direction, wherein a first flow channel Ra through which a first fluid medium A is circulated 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 each adjacent two of the plurality of heat transfer plates 2, 3, and a second flow channel Rb through which a second fluid medium B is circulated in the second direction is formed between the second surfaces Sa2, Sb2 of the heat transfer portions 20, 30 of each adjacent two of the plurality of heat transfer plates 2, 3, wherein each of the heat transfer portions 20, 30 of each adjacent two of the plurality of heat transfer plates 2, 3 includes: as the ridges 23, 33 formed on the first surface Sa1, Sb1, a plurality of first ridges 230, 330 arranged at intervals from each other in a direction intersecting with the first direction and the second direction, the plurality of first ridges 230, 330 extending in the second direction or in a synthetic direction that has a component in the second direction, and at least one barrier ridge 231, 331 that is lower than the plurality of first ridges 230, 330 formed on the first surface Sa1, Sb1, the at least one barrier ridge 231, 331 extending in a direction intersecting with the plurality of first ridges 230, 330; as the valleys 22, 32 formed on the first surface Sa2, Sb2, a plurality of first valleys 220, 320 each formed between each adjacent two of the plurality of first ridges 230, 330 in the direction intersecting with the first direction and the second direction; and, as the valleys 22, 32 formed on the second surface Sa2, Sb2, a plurality of second valleys 221, 321 being in a front-back relationship with the plurality of first ridges 230, 330, wherein each of the plurality of first ridges 230, 330 of one of each adjacent two of the plurality of heat transfer plates 2, 3 is located between each adjacent two of the plurality of first ridges 230, 330 of the opposed heat transfer plate 2, 3, wherein the at least one barrier ridge 231, 331 on each of each adjacent two of the plurality of heat transfer plates 2, 3 has a longitudinal dimension set to be shorter than the entire length in a third direction of the heat transfer portion 20, 30, the third direction being orthogonal to the first direction and the second direction, and wherein the at least one barrier ridge 231, 331 on one of each adjacent two of the plurality of heat transfer plates 2, 3 is arranged at a position displaced in at least one of the second direction and the third direction from the at least one barrier ridge 231, 331 on the opposed heat transfer plate 2, 3, and crosses and abuts against the plurality of first ridges 230, 330 of the opposed heat transfer plate 2, 3.
According to the heat exchanger 1 configured as above, the longitudinal dimension of each of the at least one barrier ridge 231, 331 on each of each adjacent two of the plurality of heat transfer plates 2, 3 is set to be shorter than the entire length in the third direction of the heat transfer portion 20, 30, and each of the at least one barrier ridges 231, 331 on one of each adjacent two of the plurality of heat transfer plates 2, 3 is arranged at a position displaced in at least one of the second direction and the third direction from each of the at least one barrier ridge 23, 331 on the opposed heat transfer plate 2, 3. Thus, each of the at least one barrier ridge 231, 331 on one of each adjacent two of the plurality of heat transfer plates 2, 3 does not coincide with (is not overlapped with) each of the at least one barrier ridge 231, 331 on the opposed heat transfer plate 2, 3. As a result, the first flow channel Ra is formed while communicating in the second direction.
As shown in Fig. 9 to Fig. 11, each of the at least one barrier ridge 231, 331 is projected toward the opposed heat transfer portion 20, 30 at an intermediate position of the first flow channel Ra formed between the first surfaces Sa1, Sb1 of each two adjacent heat transfer portions 20, 30. This configuration allows each of the at least one barrier ridge 231, 331 to block circulation of the first fluid medium A through the first flow channel Ra to thereby increase the circulating resistance of the first fluid medium A through the first flow channel Ra.
In particular, according to the heat exchanger 1 of this embodiment, each of the first ridges 230, 330 of each two adjacent heat transfer plates 2, 3 is located between each two adjacent first ridges 230, 330 of the opposed heat transfer plate 2,3, and each of the at least one barrier ridge 231, 331 (each of the at least one barrier ridge 231, 331 lower than the first ridges 230, 330) of the heat transfer plate 2, 3 crosses and abuts against the first ridges 230, 330 of the opposed heat transfer plate 2, 3.
This configuration makes small a clearance between the first surfaces Sa1, Sb1 of each two adjacent heat transfer plates 2, 3. That is, the projected amount of each of the at least one barrier ridge 231, 331 is smaller than the projected amount of the first ridges 230, 330, and consequently the heat transfer plates 2, 3 defining each of the first flow channels Ra are arranged close to each other. This configuration narrows the width of the first flow channel Ra to thereby increase the circulating resistance of the first fluid medium A through the first flow channel Ra.
Thus, in the heat exchanger 1 according to this embodiment, the circulating resistance of the first fluid medium A is increased by each of the at least one barrier ridge 231, 331 and the narrowed width of the first flow channel Ra; consequently, the first fluid medium A becomes more likely to cause the heat transfer portions 20, 30 to be subjected to thermal influences, thereby improving the performance of transferring heat to the second fluid medium B.
In contrast, on the second surfaces Sa2, Sb2 of the respective heat transfer plates 2, 3, the plurality of second valleys 221, 321 being in a front-back relationship with the first ridges 230, 330 are formed, and the valleys being in a front-back relationship with the barrier ridges 231, 331 of the first surfaces Sa1, Sb1 are formed; thus, nothing causes an increase in the circulating resistance of the second fluid medium B in the second flow channel Rb formed between the second surfaces Sa2, Sb2 of each two adjacent heat transfer plates 2, 3. 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.
As a result, 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.
Consequently, the 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).
In this embodiment, each of the heat transfer portions 20, 30 of each adjacent two of the plurality of heat transfer plates 2, 3 includes a plurality of barrier ridges 231, 331, and the plurality of barrier ridges 231, 331 are aligned at intervals from each other in the second direction. This configuration can increase the circulation resistance at a plurality of places (i.e., the places at which the plurality of barrier ridges 231, 331 are located) within the first flow channel Ra. As a result, the first fluid medium A becomes more likely to cause the heat transfer portions 20, 30 to be subjected to thermal influences, thereby improving the performance of transferring heat to the second fluid medium B.
In particular, in this embodiment, the heat transfer portion 20 of one heat transfer plate 2 out of each adjacent two of the plurality of heat transfer plates 2, 3 has at least one row (two rows in this embodiment) constituted by a plurality of barrier ridges 231 arranged at intervals from each other in the second direction, the heat transfer portion 30 of the other heat transfer plate 3 out of the each adjacent two of the plurality of heat transfer plates 2, 3 has at least two rows (three rows in this embodiment) each constituted by a plurality of barrier ridges 331 arranged at intervals from each other in the second direction, and each of the at least one row on the one heat transfer plate 2 out of the each adjacent two of the plurality of heat transfer plates 2, 3 is positioned between each adjacent two of the at least two rows on the other heat transfer plate 3 out of the each adjacent two of the plurality of heat transfer plates 2, 3. This configuration causes the first fluid medium A to be diffused within the entire first flow channel Ra. Accordingly, the areas contributing to heat transfer in the heat transfer portions 20, 30 are increased, which consequently improves heat transfer performance of the first fluid medium A within the first flow channel Ra.
In particular, since each of the plurality of barrier ridges 231 constituting the at least one row on the one heat transfer plate 2 out of the each adjacent two of the plurality of heat transfer plates 2, 3 is positioned between each adjacent two of the plurality of barrier ridges 331 constituting each of the at least two rows on the other heat transfer plate 3 out of the each adjacent two of the plurality of heat transfer plates 2, 3, the first fluid medium A circulating through the first flow channel Ra is diffused around each of the plurality of barrier ridges 231, 331 as it flows downstream. This configuration causes the first fluid medium A to be diffused within the entire first flow channel Ra, and accordingly, the areas contributing to heat transfer in the heat transfer portions 20, 30 are increased. This consequently improves heat transfer performance of the first fluid medium A within the first flow channel Ra.
Each of the at least one barrier ridge 231, 331 extends straight in the third direction, and thus extends in a direction orthogonal to a direction in which the first fluid medium A is circulated within the first flow channel Ra. With this configuration, the first fluid medium A becomes more likely to collide with each of the at least one barrier ridge 231, 331, which not only increases the circulating resistance but causes the first flow medium A to be efficiently diffused in the third direction.
In this embodiment, each of the heat transfer portions 20, 30 of each adjacent two of the plurality of heat transfer plates 2, 3 includes, as the ridges 23, 33 formed on the second surface Sa2, Sb2, a plurality of second ridges 233, 333 being in a front-back relationship with the plurality of first valleys 220, 320, and the plurality of second ridges 233, 333 of one of each adjacent two of the plurality of heat transfer plates 2, 3 are overlapped with the plurality of second ridges 233, 333 of the opposed heat transfer plate 2, 3 and are in contact with top ends of the plurality of second ridges 233, 333 of the opposed heat transfer plate 2, 3. 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 flow 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.
It is a matter of course that the present invention is not limited to any of the aforementioned embodiments, but various modifications can be made without departing from the gist of the present invention.
The aforementioned embodiment was described by taking, for example, the case where the top ends of the second ridges 233, 333 of each two 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, without limitation thereto. For example, the top ends of the second ridges 233, 333 of the each two adjacent heat transfer plates 2, 3 (the first heat transfer plate 2 and the second heat transfer plate 3) may be away from each other in the first direction or in the second direction. However, in order to achieve rigidity for withstanding, for example, an increase in the flow pressure within the first flow channel Ra, it is preferable that the top ends of the second ridges 233, 333 of each two adjacent heat transfer plates 2, 3 (the first heat transfer plate 2 and the second heat transfer plate 3) be in contact with or connected to each other, as in the cases of the aforementioned embodiments.
The aforementioned embodiment was described by taking, for example, the case where the first valleys 220, 320, the first ridges 230, 330, the second valleys 221, 321, and the second ridges 233, 333 extend straightforwardly in the second direction, without limitation thereto. For example, the second valleys 221, 321 may extend in a synthetic direction that has a component in the second direction (i.e., in a direction inclined relative to a virtual line extending in the second direction), with the prerequisite that they are continuous with the back side valleys 222, 322. However, in order to increase the velocity of the second fluid medium B, the back side valleys 222, 322 are required to be inclined, satisfying the condition that the inclination component (angle) relative to the virtual line extending in the second direction is smaller than the inclination component (angle) relative to the virtual line extending in the third direction.
The aforementioned embodiment was described by taking, for example, the case where each of the plurality of heat transfer plates 2, 3 has two or more barrier ridges 231, 331 at intervals from each other in the second direction, without limitation thereto. For example, one barrier ridge 231, 331 may be provided on one heat transfer portion 20, 30. The aforementioned second embodiment was described by taking, for example, the case where two or more rows each constituted by the plurality of barrier ridges 231, 331 arranged at intervals from each other in the second direction are provided at intervals from each other in the third direction, without limitation thereto. For example, the plurality of barrier ridges 231, 331 arranged at intervals from each other in the second direction to be aligned in one row may be provided on each of the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30. Further, the aforementioned second embodiment was described by taking, for example, the case where the plurality of barrier ridges 231, 331 arranged at intervals from each other in the second direction are lined up in the second direction on each of the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30, without limitation thereto. For example, the plurality of barrier ridges 231, 331 arranged at intervals from each other in the second direction may be arranged while being displaced from each other in the third direction.
The aforementioned embodiment was described by taking, for example, the case where the plurality of barrier ridges 231, 331 formed on the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30 are formed into the same shape, without limitation thereto. For example, the plurality of barrier ridges 231, 331 in different shapes may be formed on the first surfaces Sa1, Sb1 of the heat transfer portions 20, 30.
The aforementioned embodiment was described by taking, for example, the case where the first valleys 220, 320 and the first ridges 230, 330 are set to have the same width dimension (i.e., the dimension in the direction orthogonal to the longitudinal direction), without limitation thereto. For example, as shown in Fig. 14 to Fig. 16, the width dimension of the first valleys 220, 320 may be set to be larger than the width dimension of the first ridges 230, 330. Specifically, as shown in Fig. 14, the radius of curvature of the first valleys 220, 320 may be set to be larger than the radius of curvature of the first ridges 230, 330, with the prerequisite that the first valleys 220, 320 and the first ridges 230, 330 have an arc-shaped cross section. Further, as shown in Fig. 15 and Fig. 16, the first valleys 220, 320 may be formed to have a flat bottom and have a width dimension larger than the width dimension of the first ridges 230, 330. In this case, the first ridges 230, 330 may have an arc-shaped cross section as shown in Fig. 15, or may have a flat top end as shown in Fig. 16. This configuration allows the barrier ridges 231, 331 lower than the first ridges 230, 330 to cross and abut against the first ridges 230, 330 of the opposed heat transfer plate 2, 3. Thus, even if the first ridges 230, 330 are arranged to be close to or fit into the first valleys 220, 320, no extremely narrow clearance is formed between the first valleys 220, 320 and the first ridges 230, 330, thereby securing circulation of the fist fluid medium A.
The aforementioned embodiment was described by taking, for example, the case where the first flow channels Ra are directly communicated with the first inflow channel Pa1 and the first outflow channel Pa2 and the second flow channels Rb are directly communicated with the second inflow channel Pb1 and the second outflow channel Pb2, without limitation thereto. For example, as shown in Fig. 17 and Fig. 18, 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 Pb 1 and the second outflow channel Pb2 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 Pb1 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 Pb2.
More specifically, a branch reference space Ds1 is formed between two 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). Based on this, the configuration may be such that one of the second flow channels Rb located on one side in the first direction of the branch reference space Ds1 is connected to the branch reference space Ds1 via the connection flow channel PJ, and that one of the second flow channels Rb located on the other side in the first direction of the branch reference space Ds1 is connected to the branch reference space Ds1 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 S1 that is continuous on the one side in the first direction of the branch reference space Ds1 and at least one second system S2 that is continuous on the other side in the first direction of the branch reference space Ds1.
In the case where the circulation route of the second fluid medium B includes the first system S1 and the second system S2, each of the first system S1 and the second system S2 may have a branch reference space (branch reference space on the downstream side) Ds2 formed between two 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 Ds1 upstream thereof via the connection flow channel PJ. In this case, the second flow channel Rb located on one side in the first direction of the branch reference space Ds2 is connected to the branch reference space Ds2 on the downstream side via the connection flow channel PJ, and the second flow channel Rb located on the other side in the first direction of the branch reference space Ds2 is connected to the branch reference space Ds2 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 S1 and the second system S2 to be further branched into at least two systems S1a, S1b, S2a, S2b, and the second flow channel Rb located most downstream of each of the systems S1a, S1b, S2a, S2b to be connected to the second outflow channel Pb2. Note that there may be one or more second flow channels Rb located most downstream of each of the systems S1a, S1b, S2a, S2b (the second flow channels Rb connected to the second outflow channel Pb2).
The aforementioned embodiment was described by taking, for example, the case where the plurality of barrier ridges 231, 331 extend straight in the third direction, without limitation thereto. For example, the plurality of barrier ridges 231, 331 may include the bent ridge portion 232, 332, similar to the first embodiment. In this case, the barrier ridges 231, 331 of each two adjacent heat transfer plates 2, 3 may intersect with each other when seen from the first direction.
The aforementioned embodiment was described by taking, for example, the case where the barrier ridges 231, 331 are provided while intersecting with the plurality of first ridges 230, 330, without limitation thereto. The barrier ridges 231, 331 may extend in a direction intersecting with the first ridges 230, 330. That is, each of the barrier ridges 231, 331 may be so short that it intersects only with a single first ridge 230, 330, or lies between each two adjacent first ridges 230, 330 (i.e., within a single first valley 220, 320), with the prerequisite that the barrier ridges 231, 331 extend in a direction intersecting with the first ridges 230, 330 (i.e., the top ends (ridge lines) of the barrier ridges 231, 331 extend in a direction intersecting with the first ridges 230, 330).

REFERENCE SIGNS LIST

1: Plate heat exchanger (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: Valley
23, 33: Ridge
200, 201, 202, 203, 300, 301, 302, 303: Opening
220, 320: First valley
221, 321: Second valley
222, 322: Back side valley
230, 330: First ridge
231,331: Barrier ridge
233, 333: Second ridge
A: First fluid medium
B: Second fluid medium
CL: Vertical centerline
Pa1: First inflow channel
Pa2: First outflow channel
Pb1: Second inflow channel
Pb2: Second outflow channel
Ra: First flow channel
Rb: Second flow channel
Sa1, Sb1: First surface
Sa2, Sb2: Second surface

Claims

A plate heat exchanger comprising:
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 one of the plurality of heat transfer plates adjacent to the each 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 one of the plurality of heat transfer plates adjacent to the each 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 two of the plurality of heat transfer plates, and a second flow channel through which a second fluid medium is circulated in the second direction is formed between the second surfaces of the heat transfer portions of each adjacent two of the plurality of heat transfer plates,

wherein each of the heat transfer portions of each adjacent two of the plurality of heat transfer plates comprises:
as the ridges formed on the first surface, a plurality of first ridges arranged at intervals from each other in a direction intersecting with the first direction and the second direction, the plurality of first ridges extending in the second direction or in a synthetic direction that has a component in the second direction, and at least one barrier ridge that is lower than the plurality of first ridges formed on the first surface, the at least one barrier ridge extending in a direction intersecting with the plurality of first ridges;

as the valleys formed on the first surface, a plurality of first valleys each formed between each adjacent two of the plurality of first ridges in the direction intersecting with the first direction and the second direction; and

as the valleys formed on the second surface, a plurality of second valleys being in a front-back relationship with the plurality of first ridges,

wherein each of the plurality of first ridges of one of each adjacent two of the plurality of heat transfer plates is located between each adjacent two of the plurality of first ridges of the opposed heat transfer plate,

wherein the at least one barrier ridge on each of each adjacent two of the plurality of heat transfer plates has a longitudinal dimension set to be shorter than the entire length in a third direction of the heat transfer portion, the third direction being orthogonal to the first direction and the second direction, and

wherein the at least one barrier ridge on one of each adjacent two of the plurality of heat transfer plates is arranged at a position displaced in at least one of the second direction and the third direction from the at least one barrier ridge on the opposed heat transfer plate, and crosses and abuts against the plurality of first ridges of the opposed heat transfer plate.
The plate heat exchanger according to claim 1, wherein
each of the heat transfer portions of each adjacent two of the plurality of heat transfer plates comprises a plurality of barrier ridges, and the plurality of barrier ridges are aligned at intervals from each other in the second direction.
The plate heat exchanger according to claim 1, wherein
the heat transfer portion of one heat transfer plate out of each adjacent two of the plurality of heat transfer plates has at least one row constituted by a plurality of barrier ridges arranged at intervals from each other in the second direction,
the heat transfer portion of the other heat transfer plate out of the each adjacent two of the plurality of heat transfer plates have at least two rows each constituted by a plurality of barrier ridges arranged at intervals from each other in the second direction, and
each of the at least one row on the one heat transfer plate out of the each adjacent two of the plurality of heat transfer plates is positioned between each adjacent two of the at least two rows on the other heat transfer plate out of the each adjacent two of the plurality of heat transfer plates.
The plate heat exchanger according to claim 3, wherein
each of the plurality of barrier ridges constituting the at least one row on the one heat transfer plate out of the each adjacent two of the plurality of heat transfer plates is positioned between each adjacent two of the plurality of barrier ridges constituting each of the at least two rows on the other heat transfer plate out of the each adjacent two of the plurality of heat transfer plates.
The plate heat exchanger according to any one of claims 1 to 4, wherein
each of the at least one barrier ridge extends straight in the third direction.
The plate heat exchanger according to any one of claims 1 to 5, wherein
each of the heat transfer portions of each adjacent two of the plurality of heat transfer plates comprises, as the ridges formed on the second surface, a plurality of second ridges being in a front-back relationship with the plurality of first valleys, and
the plurality of second ridges of one of the each adjacent two of the plurality of heat transfer plates is overlapped with the plurality of second ridges of the opposed heat transfer plate and is in contact with top ends of the plurality of second ridges of the opposed heat transfer plate.