U.S. patent application number 16/065935 was filed with the patent office on 2019-01-10 for plate heat exchanger.
The applicant listed for this patent is HISAKA WORKS, LTD.. Invention is credited to Nobuo TANAKA.
Application Number | 20190011193 16/065935 |
Document ID | / |
Family ID | 59312157 |
Filed Date | 2019-01-10 |
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United States Patent
Application |
20190011193 |
Kind Code |
A1 |
TANAKA; Nobuo |
January 10, 2019 |
PLATE HEAT EXCHANGER
Abstract
Plate heat exchanger includes heat transfer plates each
including heat transfer portion with 1st surface and 2nd surface,
heat transfer portions stacked in 1st direction, 1st channel for
circulating 1st medium in 2nd direction orthogonal to 1st direction
formed between opposed 1st surfaces, and 2nd channel for
circulating 2nd medium in 2nd direction formed between opposed 2nd
surfaces. Each heat transfer portion includes barrier ridges on 1st
surface that extend in direction crossing 2nd direction, divides
heat transfer portion into divided areas in 2nd direction, and
crosses and abuts against ridges of 1st surface of opposed heat
transfer portion. Each heat transfer portion includes 2nd flow
channel forming valleys on 2nd surface arranged at intervals in 3rd
direction orthogonal to both 1st and 2nd directions in each divided
area from its one end to its other end in 2nd direction.
Inventors: |
TANAKA; Nobuo;
(Higashi-Osaka-shi, JP) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
HISAKA WORKS, LTD. |
Osaka-shi |
|
JP |
|
|
Family ID: |
59312157 |
Appl. No.: |
16/065935 |
Filed: |
November 17, 2016 |
PCT Filed: |
November 17, 2016 |
PCT NO: |
PCT/JP2016/084040 |
371 Date: |
June 25, 2018 |
Current U.S.
Class: |
1/1 |
Current CPC
Class: |
F28F 3/048 20130101;
F28F 3/046 20130101; F28F 3/08 20130101; F28F 2215/10 20130101;
F28F 3/12 20130101; F28F 3/00 20130101; F28D 9/02 20130101; F28D
9/0037 20130101; F28D 9/005 20130101 |
International
Class: |
F28D 9/00 20060101
F28D009/00; F28F 3/08 20060101 F28F003/08; F28F 3/12 20060101
F28F003/12 |
Foreign Application Data
Date |
Code |
Application Number |
Jan 13, 2016 |
JP |
2016-004234 |
Claims
1. 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 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 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, and wherein the heat transfer portion of at least
one of each adjacent heat transfer plates comprises: as the ridges
formed on the first surface, at least one barrier ridge that
crosses a centerline extending in the second direction of the heat
transfer portion and is formed over the entire length in a third
direction orthogonal to the first direction and the second
direction of the heat transfer portion, and that divides the heat
transfer portion into two or more divided areas in the second
direction, the at least one barrier ridge crossing and abutting
against the ridges formed on the first surface of the heat transfer
portion of the opposed heat transfer plate aligned adjacently, and
as the valleys formed on the second surface, a plurality of second
flow channel forming valleys constituting part of the second flow
channel, the plurality of second 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 one end to an other end
in the second direction of each corresponding one of the two or
more divided areas.
2. The plate heat exchanger according to claim 1, wherein each of
the heat transfer portions of the each adjacent heat transfer
plates comprises: 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 wherein the first flow channel side ridges in
the mutually corresponding divided areas of the adjacent heat
transfer plates are arranged with a clearance therebetween.
3. The plate heat exchanger according to claim 2, wherein a
projected amount of the at least one barrier ridge in the first
direction is set to be larger than a projected amount of the first
flow channel side ridges in the first direction.
4. The plate heat exchanger according to claim 2, wherein the
plurality of first flow channel side ridges in the mutually
corresponding divide areas of the each adjacent heat transfer
plates are arranged while being displaced with each other in the
third direction.
5. The plate heat exchanger according to claim 1, wherein each of
the heat transfer portions of the each adjacent heat transfer
plates comprises: 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 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 are in contact with each other.
6. The plate heat exchanger according to claim 1, wherein each of
the heat transfer portions of the each adjacent heat transfer
plates comprises: 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 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
are arranged with a clearance therebetween.
7. The plate heat exchanger according to claim 6, wherein the
plurality of second flow channel side ridges in the mutually
corresponding divided areas of the each adjacent heat transfer
plates are arranged while being displaced in the third
direction.
8. The plate heat exchanger according to claim 1, wherein the at
least one barrier ridge includes two or more barrier ridges
provided at intervals in the second direction, and the two or more
barrier ridges divide each corresponding one of the heat transfer
portions into three or more divided areas.
9. The plate heat exchanger according to claim 1, wherein the
barrier ridge comprises at least one bent ridge portion that
comprises 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.
10. The plate heat exchanger according to claim 9, wherein each of
the heat transfer portions of the each adjacent heat transfer
plates includes the barrier ridge having the bent ridge portion,
and the bent ridge portions of the barrier ridges of the each
adjacent heat transfer plates are bent in directions completely
opposite to each other and comprise the inclined ridge portions of
the bent ridge portions opposed to each other crossing and abutting
against each other.
11. The plate heat exchanger according to claim 1, wherein the
barrier ridge extends straightforwardly in the third direction.
12. The plate heat exchanger according to claim 11, wherein each of
the heat transfer portions of the each adjacent heat transfer
plates includes the barrier ridge extending in the third direction,
and the barrier ridges of the each adjacent heat transfer plates
are arranged while being displaced with each other in the second
direction.
Description
CROSS-REFERENCE TO RELATED APPLICATION
[0001] This application claims priority to Japanese Patent
Application No. 2016-004234, the disclosure of which is
incorporated herein by reference in its entirety.
FIELD
[0002] The present invention relates to a plate heat exchanger that
is used as a condenser and an evaporator.
BACKGROUND
[0003] Plate heat exchangers have been conventionally provided. A
plate heat exchanger is a type of heat exchanger configured to
exchange heat between a first fluid medium and a second fluid
medium.
[0004] 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.
[0005] On each of the first surface and the second surface of the
heat transfer portion, 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.
[0006] 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.
With this configuration, 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
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. Also, 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.
[0007] In the plate heat exchanger configured as above, 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. As a result, 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).
[0008] 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 channel and the second fluid medium within the second
flow channels.
[0009] However, 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.
[0010] 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 flow
resistance of both the first flow channels and the second flow
channels.
[0011] Generally, 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.
[0012] 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 for the second fluid medium. As
a result, 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. 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 surface of the heat transfer portion.
[0013] However, 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.
[0014] 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
surface of the heat transfer portion.
[0015] 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
[0016] Patent Literature 1: JP 2001-099588 A
SUMMARY
Technical Problem
[0017] 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
[0018] 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 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, and wherein the heat transfer portion of at least
one of each adjacent heat transfer plates includes: as the ridges
formed on the first surface, at least one barrier ridge that
crosses a centerline extending in the second direction of the heat
transfer portion and is formed over the entire length in a third
direction orthogonal to the first direction and the second
direction of the heat transfer portion, and that divides the heat
transfer portion into two or more divided areas in the second
direction, the at least one barrier ridge crossing and abutting
against the ridges formed on the first surface of the heat transfer
portion of the opposed heat, transfer plate aligned adjacently and
as the valleys formed on the second surface, a plurality of second
flow channel forming valleys constituting part of the second flow
channel, the plurality of second 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 one end to an other end
in the second direction of each corresponding one of the two or
more divided areas.
[0019] It is preferable that 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.
[0020] In this case, 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.
[0021] It is preferable that 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.
[0022] It is preferable that 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.
[0023] It is preferable that 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.
[0024] In this case, 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.
[0025] It is preferable that 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.
[0026] 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.
[0027] It is preferable that 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.
[0028] The barrier ridge may extend straightforwardly in the third
direction.
[0029] 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.
BRIEF DESCRIPTION OF DRAWINGS
[0030] FIG. 1 is a perspective view of a plate heat exchanger
according to one embodiment of the present invention.
[0031] 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.
[0032] 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.
[0033] 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.
[0034] 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.
[0035] 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.
[0036] 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.
[0037] 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.
[0038] 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.
[0039] 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.
[0040] 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.
[0041] 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.
[0042] 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.
[0043] 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.
[0044] 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.
[0045] 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.
[0046] 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.
DESCRIPTION OF EMBODIMENTS
[0047] Hereinafter, an embodiment of the present invention will be
described with reference to the attached drawings.
[0048] As shown in FIG. 1, 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.
[0049] First, the common configuration of the first heat transfer
plate 2 and the second heat transfer plate 3 will be described. As
shown in FIG. 2, 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.
[0050] The heat transfer portions 20, 30 have a thickness in a
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. 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.
[0051] 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.
[0052] 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.
[0053] 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 Sat,
Sb2 side.
[0054] A projected amount of the area surrounding each of the
openings 200, 201, 300, 301 that is projected on the second
surfaces Sa2, Sb2 side is set so that the area surrounding each of
the openings 200, 201, 300, 301 that is projected on the second
surfaces Sat, Sb2 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.
[0055] 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 projected on the first surfaces
Sa1, Sb1 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 Sa2, Sb2 side.
[0056] A projected amount of the area surrounding each of the
openings 202, 203, 302, 303 that is projected on the first surfaces
Sa1, Sb1 side is set so that the area surrounding each of the
openings 202, 203, 302, 303 that is projected on the first surfaces
Sa1, Sb1 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. In FIG. 3 and FIG. 4, 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.
[0057] 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.
[0058] 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.
[0059] 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.
[0060] As shown in FIG. 3 and FIG. 5, the heat transfer portion 20,
30 includes, as the ridges 23, 33 formed on the first surface Sa1,
Sb1, 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 Sa1, Sb1 of the opposed heat
transfer portion 20, 30.
[0061] The heat transfer portion 20, 30 includes, as the valleys
22, 32 formed on the first surface Sa1, Sb1, 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.
[0062] The heat transfer portion 20, 30 includes, as the ridges 23,
33 formed on the first surface Sa1, Sb1, 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.
[0063] In this embodiment, 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.
[0064] 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 232a, 232b, 332a, 332b each portion
having a proximal end and a distal end on the opposite side of the
proximal end, the pair of inclined ridge portions 232a, 232b, 332a,
332b 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. In this embodiment, the barrier
ridges 230, 330 have one bent ridge portion 232, 332.
[0065] In this embodiment, the proximal ends of the pair of
inclined ridge portions 232a, 232b, 332a, 332b 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.
[0066] In contrast, the distal ends of the pair of inclined ridge
portions 232a, 232b, 332a, 332b are located at the center (on the
vertical centerline CL) in the third direction of the heat transfer
portion 20, 30. With this, the distal ends of the pair of inclined
ridge portions 232a, 232b, 332a, 332b are connected in face-to-Pace
relationship.
[0067] This configuration allows the barrier ridge 230, 330 itself
to constitute the bent ridge portion 232, 332 in this embodiment.
The pair of inclined ridge portions 232a, 232b, 332a, 332b are
symmetrically arranged with reference to a virtual line that
extends in the second direction. That is, the pair of inclined
ridge portions 232a, 232b, 332a, 332b are inclined in a direction
completely opposite to each other. However, the pair of inclined
ridge portions 232a, 232b, 332a, 332b have the same inclination
angle with respect, to the vertical centerline CL extending in the
second direction.
[0068] 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 Sa1, Sb1 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.
[0069] 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. That is, 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. In contrast, 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.
[0070] In this embodiment, 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.
[0071] 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
5a2, Sb2, 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 Sa1, Sb1.
[0072] The heat transfer portion 20, 30 include, as the valleys 22,
32 formed on the second surface Sa2, Sb2, 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. Further, the heat transfer portion 20, 30
includes, as the ridges 23, 33 formed on the second surface Sa2,
Sb2, 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.
[0073] 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. On the second surface Sa2,
Sb2 of the heat transfer portion 20, 30, therefore, a bent valley
portion 223, 323 that includes a pair of inclined valley portions
223a, 223b, 323a, 323b is formed, which is the valley 22, 32 formed
on the back side of each pair of inclined ridge portions 232a,
232b, 332a, 332b.
[0074] In this embodiment, the bent ridge portion 232, 332 (the
pair of inclined ridge portions 232a, 232b, 332a, 332b) constitutes
the barrier ridge 230, 330. Thus, 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.
[0075] 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 Sa1, Sb1. 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. Here, "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. In this embodiment,
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.
[0076] With this configuration, 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.
With this configuration, the second surface Sa2, Sb2 (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.
[0077] 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.
[0078] 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 Sa2, Sb2 are opposed to each other while
their first surfaces Sa1, Sb1 are opposed to each other. As shown
in FIG. 3, therefore, 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.
[0079] 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.
[0080] With this configuration, 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.
[0081] In this embodiment, as shown in FIG. 7, the plurality of
heat transfer plates 2, 3 are stacked on each other so that the
distal ends of the inclined ridge portions 232a, 232b 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 332a, 332b 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.
[0082] That is, as shown in FIG. 7 and FIG. 8, 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 232a
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 332a 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 232b
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 332b constituting the barrier
ridge 330 (the bent ridge portion 332) of each of the second heat
transfer plates 3.
[0083] In this embodiment, as shown in FIG. 2, 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. When a plurality of
pairs are stacked, 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 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.
[0084] As shown in FIG. 7, 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
Sa1, Sb1 of the heat transfer portions 20, 30 opposed to each other
are arranged to overlap each other when seen from the first
direction. As shown in FIG. 8, 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
Sa1, Sb1 on the heat transfer portions 20, 30 opposed to each other
are located at intervals from each other.
[0085] As shown in FIG. 9, the second flow channel side ridges 233,
333 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 second surfaces
Sa2, Sb2 of the heat transfer portions 20, 30 opposed to each other
are arranged to overlap each other when seen from the first
direction. As shown in FIG. 10, each adjacent heat transfer plates
2, 3 (the first heat transfer plate 2 and the second heat transfer
plate 3) with the second surfaces Sa2, Sb2 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.
[0086] 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 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
Sa2, Sb2 of the heat transfer portions 20, 30 of each adjacent heat
transfer plates 2, 3.
[0087] 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 abut each
other. This configuration forms a first inflow channel Pa1 for
supplying the first fluid medium A into the first flow channels Ra,
a first outflow channel Pa2 for causing the first fluid medium A to
flow out of the first flow channels Ra, a second inflow channel Pb1
for supplying the second fluid medium B into the second flow
channels Rb, and a second outflow channel Pb2 for causing the
second fluid medium B to flow out of the second flow channels
Rb.
[0088] In the plate heat exchanger 1 according to this embodiment,
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.
[0089] The plate heat exchanger 1 according to this embodiment has
been described as above. As shown in FIG. 2, FIG. 7, and FIG. 11,
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. 9, and FIG. 11, the
second fluid medium B flows from the second inflow channel Pb1 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
Pb2.
[0090] In this embodiment, as shown in FIG. 7, 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. 9, 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.
[0091] 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.
[0092] As just described, the 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 Sat, 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 an adjacent 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 an adjacent 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 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 heat transfer plates 2, 3, and wherein the heat
transfer portion 20, 30 of at least one of each adjacent heat
transfer plates 2, 3 includes: as the ridges 23, 33 formed on the
first surface Sa1, Sb1, at least one barrier ridge 230, 330 that
crosses a centerline (vertical centerline) CL extending in the
second direction of the heat transfer portion 20, 30 and is formed
over the entire length in a third direction orthogonal to the first
direction and the second direction of the heat transfer portion 20,
30, and that divides the heat transfer portion 20, 30 into two or
more divided areas Da, Db in the second direction, the at least one
barrier ridge 230, 330 crossing and abutting against the ridges 23,
33 formed on the first surface Sa1, Sb1 of the heat transfer
portion 20, 30 of the opposed heat transfer plate 2, 3, and as the
valleys 22, 32 formed on the second surface Sa2, Sb2, a plurality
of second flow channel forming valleys 221, 321 constituting part
of the second flow channel Rb, the plurality of second flow channel
forming valleys 221, 321 being arranged at intervals from each
other in the third direction in each of the two or more divided
areas Da, Db from one end to an other end in the second direction
of each corresponding one of the two or more divided areas Da,
Db.
[0093] According to the plate heat exchanger 1 configured as above,
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 Sa1, Sb1 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. As a
result, 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.
[0094] The valleys 22, 32 on the first surface Sa1, Sb1 are in a
front-back relationship with the ridges 23, 33 on the second
surface Sa2, Sb2, and the ridges 23, 33 on the first surface Sa1,
Sb1 are in a front-back relationship with the valleys 22, 32 on the
second surface Sa2, Sb2. Accordingly the back side valleys 222, 322
corresponding to the barrier ridges 230, 330 are formed on the
second surface 5a2, Sb2 of the heat transfer portion 20, 30. That
is, 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 Sa2, Sb2
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
Sa2, Sb2 side.
[0095] 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. As a result, 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.
[0096] 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, Thus, 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.
[0097] 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.
[0098] Consequently, 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).
[0099] In this embodiment, 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 Sa1, Sb1, 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 Sa1, Sb1, 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, 331 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 Da, Db, and the
first flow channel side ridges 231, 331 in the mutually
corresponding divided areas Da, Db of the adjacent heat transfer
plates 2, 3 are arranged with a clearance therebetween (see FIG.
8). With this configuration, the inside of each of the first flow
channel Ra is not completely closed but fluidity of the first fluid
medium A is secured within the first flow channels Ra while the
circulating resistance of the first fluid medium A is also applied
to the inside of each of the first flow channels Ra.
[0100] Particularly in this embodiment, 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. As a
result, the entire areas or the substantially entire areas of the
first surfaces Sa1, Sb1 of the heat transfer portions 20, 30
contribute to heat transfer.
[0101] 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
Sa2, Sb2, 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 Sa2, Sb2 of the heat transfer
portions 20, 30 opposed to each other are in contact with each
other (see FIG. 10). 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.
[0102] Further, 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.
[0103] The barrier ridge 230, 330 includes at least one bent ridge
portion 232, 332 that includes a pair of inclined ridge portions
232a, 232b, 332a, 332b each having a proximal end and a distal end
on an opposite side of the proximal end, the pair of inclined ridge
portions 232a, 232b, 332a, 332b 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). Accordingly not only do the entire barrier ridges 230,
330 crossing the first flow channel Ra cause the flow resistance to
the first fluid medium A, but also the bent ridge portion 232, 332
(the pair of inclined ridge portions 232a, 232b, 332a, 332b) 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.
[0104] 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 232a, 232b, 332a, 332b 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.
[0105] It is a matter of course that the present invention is not
limited to the aforementioned embodiment, but various modifications
can be made without departing from the gist of the present
invention.
[0106] The aforementioned embodiment was described by taking, for
example, the cases where, as the adjacent heat transfer plates 2,
3, two kinds of heat transfer plates 2, 3 (the first heat transfer
plate 2 and the second heat transfer plate 3) are provided and 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. For example, 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.
[0107] The aforementioned embodiment was described by taking, for
example, the case where the second flow channel forming valleys
221, 321 extend straightforwardly in the second direction, without
limitation thereto. For example, 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. However, in
order to increase the velocity of the second fluid medium B, 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.
[0108] 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. For example, 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.
[0109] The aforementioned embodiment was described by taking, for
example, the case where each adjacent heat transfer plates 2, 3
with the second surfaces Sa2, Sb2 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. For
example, 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 Sa2, Sb2 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.
[0110] In this case, 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. As a result, 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.
[0111] The aforementioned embodiment was described by taking, for
example, the case where 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. For example,
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.
[0112] In this case, 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
Sa1, Sb1 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. However, 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.
[0113] The aforementioned embodiment was described by taking, for
example, the case where the barrier ridge 230, 330 constitutes one
bent ridge portion 232, 332 including the pair of inclined ridge
portions 232a, 232b, 332a, 332b, without limitation thereto. For
example, the barrier ridges 230, 330 may include a plurality of
(two or more) bent ridge portions 232, 332. Further, the barrier
ridges 230, 330 may be formed into a curved shape when seen from
the first direction. Further, 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.
[0114] The aforementioned embodiment was described by taking, for
example, the case where the plurality of barrier ridges 230, 330
formed on the first surfaces Sa1, Sb1 of the heat, transfer
portions 20, 30 are formed into the same pattern, without
limitation thereto. For example, the plurality of barrier ridges
230, 330 in a different pattern may be formed on the first surfaces
Sa1, Sb1 of the heat transfer portions 20, 30. Here, the different
pattern means that the inclined ridge portions 232a, 232b, 332a,
332b have different inclination angles, the bent ridge portions
232, 332 (the inclined ridge portions 232a, 232b, 332a, 332b) 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.
[0115] 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 Sa1, Sb1 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 232a, 232b, 332a, 332b of the bent
ridge portions 232, 332 opposed to each other crossing and abutting
against each other, without limitation thereto. For example, as
shown in FIG. 12 to FIG. 15, 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. 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, which consequently enhances
heat transfer performance.
[0116] In this case, 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 Sa1, Sb1 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.
[0117] 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. As a
result, 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.
[0118] 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. 16 and FIG. 17, 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 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.
[0119] More specifically 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). Based on this,
the configuration may be such that one of the second flow channels
Rb located on one side of the branch reference space Ds1 is
connected to the branch reference space Ds1 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 S1 that is continuous on the one side of
the branch reference space Psi in the first direction and at least
one second system S2 that is continuous on the other side of the
branch reference space Psi in the first direction.
[0120] 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 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 of the branch reference
space Ds2 in the first direction 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 of the branch reference space Ds2 in the first direction 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).
REFERENCE SIGNS LIST
[0121] 1: Plate heat exchanger [0122] 2: First heat transfer plate
(heat transfer plate) [0123] 3: Second heat transfer plate (heat
transfer plate) [0124] 20, 30: Heat transfer portion [0125] 21, 31:
Fitting portion [0126] 22, 32: Valley [0127] 23, 33: Ridge [0128]
200, 201, 202, 203, 300, 301, 302, 303: Opening [0129] 220, 320:
First flow channel forming valley [0130] 221, 321: Second flow
channel forming valley [0131] 222, 322: Back side valley [0132]
223, 323: Bent valley portion [0133] 223a, 223b, 323a, 323b:
Inclined valley portion [0134] 230, 330: Barrier ridge [0135] 231,
331: First flow channel side ridge [0136] 232, 332: Bent ridge
portion [0137] 232a, 232b, 332a, 332b: Inclined ridge portion
[0138] 233, 333: Second flow channel side ridge [0139] A: First
fluid medium. [0140] B: Second fluid medium [0141] CL: Vertical
centerline (centerline) [0142] Da, Db: Divided area [0143] Ds1:
Branch reference space [0144] Ds2: Branch reference space [0145]
Pa1: First inflow channel [0146] Pa2: First outflow channel [0147]
Pb1: Second inflow channel [0148] Pb2: Second outflow channel
[0149] PJ: Connection flow channel [0150] Ra: First flow channel
[0151] Rb: Second flow channel [0152] S1: First system [0153] S2:
Second system [0154] S1a, S1b, S2a, S2b: System [0155] Sa1, Sb1:
First surface [0156] Sa2, Sb2: Second surface
* * * * *