U.S. patent application number 11/736724 was filed with the patent office on 2007-11-01 for heat exchanger.
This patent application is currently assigned to SHOWA DENKO K.K.. Invention is credited to Hironaka Sasaki.
Application Number | 20070251682 11/736724 |
Document ID | / |
Family ID | 38542544 |
Filed Date | 2007-11-01 |
United States Patent
Application |
20070251682 |
Kind Code |
A1 |
Sasaki; Hironaka |
November 1, 2007 |
HEAT EXCHANGER
Abstract
A gas cooler includes paired header tanks, and a plurality of
parallel flat tubes disposed between the header tanks. Each header
tank is configured such that an outside plate, an inside plate, and
an intermediate plate are brazed together in layers. When the
height of each flat tube is represented by T (mm), the distance
between each of the opposite longitudinal end surfaces of each flat
tube and an outer surface of the corresponding intermediate plate
is represented by L (mm), and the width of each communication hole
of the intermediate plate is represented by W (mm), relations
L.gtoreq.0.7 T and 1.1 T.ltoreq.W.ltoreq.2.5 T are satisfied. This
gas cooler can minimize an increase in pressure loss when
supercritical refrigerant flows from the flat tubes into first
refrigerant flow sections of the outside plate and flows from the
first refrigerant flow sections into the flat tubes.
Inventors: |
Sasaki; Hironaka;
(Oyama-shi, JP) |
Correspondence
Address: |
OBLON, SPIVAK, MCCLELLAND, MAIER & NEUSTADT, P.C.
1940 DUKE STREET
ALEXANDRIA
VA
22314
US
|
Assignee: |
SHOWA DENKO K.K.
Tokyo
JP
|
Family ID: |
38542544 |
Appl. No.: |
11/736724 |
Filed: |
April 18, 2007 |
Current U.S.
Class: |
165/153 ;
165/176; 165/178 |
Current CPC
Class: |
F28F 9/0221 20130101;
F28F 9/0278 20130101; F28D 1/05391 20130101; F28F 9/0246 20130101;
F28D 1/0391 20130101; F28F 9/0224 20130101; F25B 39/00 20130101;
F28F 1/022 20130101; F28D 2021/0073 20130101 |
Class at
Publication: |
165/153 ;
165/178; 165/176 |
International
Class: |
F28D 1/02 20060101
F28D001/02 |
Foreign Application Data
Date |
Code |
Application Number |
Apr 28, 2006 |
JP |
2006-124789 |
Claims
1. A heat exchanger comprising a pair of header tanks disposed
apart from each other and each having at least one header section;
and a plurality of flat tubes disposed in parallel between the two
header tanks and having opposite end portions connected to the
respective header tanks, wherein each of the two header tanks is
configured such that an outside plate, an inside plate, and an
intermediate plate intervening between the outside and inside
plates are brazed together in layers; the outside plate has at
least one outwardly bulging portion extending in the longitudinal
direction of the header tank and having an opening closed by the
intermediate plate, the interior of the outwardly bulging portion
serving as a first refrigerant flow section; the inside plate has a
plurality of tube insertion holes in the form of through-holes
formed in a region corresponding to the outwardly bulging portion
and spaced apart from one another along the longitudinal direction
of the inside plate; opposite end portions of the flat tubes are
inserted through the respective tube insertion holes of the inside
plates of the two header tanks, and are brazed to the inside
plates; the intermediate plate has communication holes in the form
of through-holes formed for allowing the tube insertion holes of
the inside plate to communicate with the first refrigerant flow
section of the outside plate, the communication holes communicating
with one another via communication portions, each of which is
formed between adjacent communication holes of the intermediate
plate; the communication portions and portions of the communication
holes which correspond to the communication portions form a second
refrigerant flow section in the intermediate plate, the second
refrigerant flow section communicating with the first refrigerant
flow section of the outside plate and allowing refrigerant to flow
therethrough in the longitudinal direction of the header tank; the
header section is formed by portions of the three plates which
constitute the corresponding header thank and which correspond to
the outwardly bulging portion; and the longitudinal opposite ends
of the flat tubes are positioned within the second refrigerant flow
sections of the intermediate plates of the two header tanks,
wherein when the height of each flat tube is represented by T (mm),
the distance between each of the opposite longitudinal end surfaces
of each flat tube and an outer surface of the corresponding
intermediate plate is represented by L (mm), and the width of each
communication hole of the intermediate plate is represented by W
(mm), relations L.gtoreq.0.7 T and 1.1 T.ltoreq.W.ltoreq.2.5 T are
satisfied.
2. A heat exchanger according to claim 1, wherein a relation
L.ltoreq.2.5 T is satisfied.
3. A heat exchanger according to claim 1 or 2, wherein the first
header tank includes a plurality of header sections arranged in the
longitudinal direction of the header tank; the second header tank
includes a header section(s), the number of which is one fewer than
the number of the header sections of the first header tank and
which faces adjacent two header sections of the first header tank;
a header section at one end portion of the first header thank is an
inlet header section having a refrigerant inlet, and a header
section at the other end portion of the first header thank is an
outlet header section having a refrigerant outlet.
4. A heat exchanger according to claim 3, wherein the first header
tank includes two header sections, and the second header tank
includes a single header section.
Description
BACKGROUND OF THE INVENTION
[0001] The present invention relates to a heat exchanger, and more
particularly to a heat exchanger that can be favorably used as a
gas cooler or an evaporator of a supercritical refrigeration cycle
in which a CO.sub.2 (carbon dioxide) refrigerant or a like
supercritical refrigerant is used.
[0002] Herein and in the appended claims, the term "supercritical
refrigeration cycle" means a refrigeration cycle in which a
refrigerant on the high-pressure side is in a supercritical state;
i.e., assumes a pressure in excess of a critical pressure. The term
"supercritical refrigerant" means a refrigerant used in a
supercritical refrigeration cycle.
[0003] The applicant of the present application has proposed a heat
exchanger for use in a supercritical refrigeration cycle (refer to
Japanese Patent Application Laid-Open (kokai) No. 2005-300135). The
proposed heat exchanger includes a pair of header tanks disposed
apart from each other and each having at least one header section;
and a plurality of flat tubes disposed in parallel between the two
header tanks and having opposite end portions connected to the
respective header tanks. Each of the two header tanks is configured
such that an outside plate, an inside plate, and an intermediate
plate intervening between the outer and inside plates are brazed
together in layers. The outside plate has at least one outwardly
bulging portion extending in the longitudinal direction of the
header tank and having an opening closed by the intermediate plate.
The interior of the outwardly bulging portion serves as a first
refrigerant flow section. The inside plate has a plurality of tube
insertion holes in the form of through-holes formed in a region
corresponding to the outwardly bulging portion and spaced apart
from one another along the longitudinal direction thereof. Opposite
end portions of the flat tubes are inserted through the respective
tube insertion holes of the inside plates of the two header tanks,
and are brazed to the inside plates. The intermediate plate has
communication holes in the form of through-holes formed for
allowing the tube insertion holes of the inside plate to
communicate with the first refrigerant flow section of the outside
plate. The communication holes communicate with one another via
communication portions, each of which is formed between adjacent
communication holes of the intermediate plate. The communication
portions and portions of the communication holes which correspond
to the communication portions form a second refrigerant flow
section in the intermediate plate. The second refrigerant flow
section communicates with the first refrigerant flow section of the
outside plate and allows refrigerant to flow therethrough in the
longitudinal direction of the header tank. The header section is
formed by portions of the three plates which constitute the
corresponding header thank and which correspond to the outwardly
bulging portion. The width of the second refrigerant flow section
of the intermediate plate is smaller than that of the first
refrigerant flow section of the outside plate. The longitudinal
opposite ends of the flat tubes are positioned within the second
refrigerant flow sections of the intermediate plates; i.e., at
thicknesswise intermediate portions of the intermediate plates.
[0004] In the heat exchanger described in the above-mentioned
publication, supercritical refrigerant flows from each flat tube
into the first refrigerant flow section of the outside plate of
each header tank as follows. That is, at a portion of each flat
tube which faces the second refrigerant flow section of the
intermediate plate, the supercritical refrigerant flows directly
into the second refrigerant flow section, and then flows into the
first refrigerant flow section via the second refrigerant flow
section. Meanwhile, at portions of each flat tube which face the
inner surface of the outside plate, the supercritical refrigerant
first flows into the corresponding communication hole of the
intermediate plate, flows within the communication hole in the
longitudinal direction thereof to enter the second refrigerant flow
section, and then flows into the first refrigerant flow section via
the second refrigerant flow section.
[0005] Further, in the heat exchanger described in the
above-mentioned publication, the supercritical refrigerant flows
from the first refrigerant flow section of the outside plate of
each header tank to each flat tube as follows. That is, at a
portion of each flat tube which faces the second refrigerant flow
section of the intermediate plate, the supercritical refrigerant
flows from the first refrigerant flow section directly into the
flat tube via the second refrigerant flow section. Meanwhile, at
portions of each flat tube which face the inner surface of the
outside plate, the supercritical refrigerant first flows from the
first refrigerant flow section into the second refrigerant flow
section, and then flows within the communication hole in the
longitudinal direction thereof to enter the flat tube.
[0006] At the portions of each flat tube which face the inner
surface of the outside plate, pressure loss unavoidably increases
for both the case where the supercritical refrigerant flows from
the flat tube into the first refrigerant flow section of the
outside plate of the header tank and the case where the
supercritical refrigerant flows from the first refrigerant flow
section of the outside plate of the header tank into the flat tube.
As a result, the performance of the heat exchanger
deteriorates.
SUMMARY OF THE INVENTION
[0007] An object of the present invention is to solve the above
problem and to provide a heat exchanger which can minimize an
increase in pressure loss at the time when supercritical
refrigerant flows from each flat tube into a first refrigerant flow
section of an outside plate and when the supercritical refrigerant
flows from the first refrigerant flow section of the outside plate
into the flat tube.
[0008] To fulfill the above object, the present invention comprises
the following modes.
[0009] 1) A heat exchanger comprising a pair of header tanks
disposed apart from each other and each having at least one header
section; and a plurality of flat tubes disposed in parallel between
the two header tanks and having opposite end portions connected to
the respective header tanks, wherein each of the two header tanks
is configured such that an outside plate, an inside plate, and an
intermediate plate intervening between the outside and inside
plates are brazed together in layers; the outside plate has at
least one outwardly bulging portion extending in the longitudinal
direction of the header tank and having an opening closed by the
intermediate plate, the interior of the outwardly bulging portion
serving as a first refrigerant flow section; the inside plate has a
plurality of tube insertion holes in the form of through-holes
formed in a region corresponding to the outwardly bulging portion
and spaced apart from one another along the longitudinal direction
of the inside plate; opposite end portions of the flat tubes are
inserted through the respective tube insertion holes of the inside
plates of the two header tanks, and are brazed to the inside
plates; the intermediate plate has communication holes in the form
of through-holes formed for allowing the tube insertion holes of
the inside plate to communicate with the first refrigerant flow
section of the outside plate, the communication holes communicating
with one another via communication portions, each of which is
formed between adjacent communication holes of the intermediate
plate; the communication portions and portions of the communication
holes which correspond to the communication portions form a second
refrigerant flow section in the intermediate plate, the second
refrigerant flow section communicating with the first refrigerant
flow section of the outside plate and allowing refrigerant to flow
therethrough in the longitudinal direction of the header tank; the
header section is formed by portions of the three plates which
constitute the corresponding header thank and which correspond to
the outwardly bulging portion; and the longitudinal opposite ends
of the flat tubes are positioned within the second refrigerant flow
sections of the intermediate plates of the two header tanks,
wherein when the height of each flat tube is represented by T (mm),
the distance between each of the opposite longitudinal end surfaces
of each flat tube and an outer surface of the corresponding
intermediate plate is represented by L (mm), and the width of each
communication hole of the intermediate plate is represented by W
(mm), relations L.gtoreq.0.7 T and 1.1 T.ltoreq.W.ltoreq.2.5 T are
satisfied.
[0010] 2) A heat exchanger according to par. 1), wherein a relation
L.ltoreq.2.5 T is satisfied.
[0011] 3) A heat exchanger according to par. 1 or 2), wherein the
first header tank includes a plurality of header sections arranged
in the longitudinal direction of the header tank; the second header
tank includes a header section(s), the number of which is one fewer
than the number of header sections of the first header tank and
which face adjacent two header sections of the first header tank; a
header section at one end portion of the first header thank is an
inlet header section having a refrigerant inlet, and a header
section at the other end portion of the first header thank is an
outlet header section having a refrigerant outlet.
[0012] 4) A heat exchanger according to par. 3), wherein the first
header tank includes two header sections, and the second header
tank includes a single header section.
[0013] According to the heat exchanger of par. 1), when the height
of each flat tube is represented by T (mm), the distance between
each of the opposite longitudinal end surfaces of each flat tube
and an outer surface of the corresponding intermediate plate is
represented by L (mm), and the width of each communication hole of
the intermediate plate is represented by W (mm), the relations
L.gtoreq.0.7 T and 1.1 T.ltoreq.W.ltoreq.2.5 T are satisfied.
Therefore, it is possible to minimize an increase in pressure loss
at the time when supercritical refrigerant first flows from
portions of each flat tube which face the inner surface of the
outside plate first into the corresponding communication hole of
the intermediate plate, flows within the communication hole in the
longitudinal direction thereof to enter the second refrigerant flow
section, and then flows into the first refrigerant flow section via
the second refrigerant flow section. Further, it is possible to
minimize an increase in pressure loss at the time when the
supercritical refrigerant first flows from the first refrigerant
flow section into the second refrigerant flow section, flows within
the communication hole in the longitudinal direction thereof, and
then flow into portions of each flat tube which face the inner
surface of the outside plate. Accordingly, deterioration in the
performance of the heat exchanger can be suppressed. In addition,
since a decrease in the joint area between the outside plate and
the intermediate plate can be minimized, a drop in the withstanding
pressure of the header tanks can be suppressed.
BRIEF DESCRIPTION OF THE DRAWINGS
[0014] FIG. 1 is a perspective view showing the overall
construction of a gas cooler to which the heat exchanger according
to the present invention is applied;
[0015] FIG. 2 is a fragmentary view in vertical section showing the
gas cooler of FIG. 1 as it is seen frontward from rear;
[0016] FIG. 3 is a perspective view showing a first header tank of
the gas cooler of FIG. 1;
[0017] FIG. 4 is an enlarged view in section taken along line A-A
of FIG. 2;
[0018] FIG. 5 is an enlarged view in section taken along line B-B
of FIG. 2;
[0019] FIG. 6 is an enlarged view in section taken along line C-C
of FIG. 5;
[0020] FIG. 7 is an exploded perspective view showing the first
header tank of the gas cooler of FIG. 1;
[0021] FIG. 8 is an exploded perspective view showing a second
header tank of the gas cooler of FIG. 1;
[0022] FIG. 9 is a cross-sectional view showing a flat tube of the
gas cooler of FIG. 1;
[0023] FIG. 10 is a fragmentary enlarged view of FIG. 9;
[0024] FIG. 11 is a view showing a method of manufacturing the flat
tube shown in FIG. 9;
[0025] FIG. 12 is a diagram showing the flow of a refrigerant
through the gas cooler of FIG. 1;
[0026] FIG. 13 is a graph sowing results of Test Example 1; and
[0027] FIG. 14 is a graph sowing results of Test Example 2.
DESCRIPTION OF THE PREFERRED EMBODIMENT
[0028] An embodiment of the present invention will next be
described in detail with reference to the drawings. This embodiment
is implemented by applying a heat exchanger according to the
present invention to a gas cooler of a supercritical refrigeration
cycle.
[0029] In the following description, the upper, lower, left-hand,
and right-hand sides of FIGS. 1 and 2 will be referred to as
"upper," "lower," "left," and "right," respectively. Also, the
downstream side of flow (represented by arrow X in FIG. 1) of air
through air-passing clearances between adjacent flat tubes will be
referred to as the "front," and the opposite side as the
"rear."
[0030] Further, in the following description, the term "aluminum"
encompasses aluminum alloys in addition to pure aluminum.
[0031] FIGS. 1 and 2 show the overall construction of a gas cooler
to which the heat exchanger according to the present invention is
applied. FIGS. 3 to 8 show the configuration of essential portions
of the gas cooler. FIGS. 9 and 10 show a flat tube. FIG. 11 shows a
method of manufacturing the flat tube. FIG. 12 shows the flow of a
refrigerant through the gas cooler of FIG. 1.
[0032] With reference to FIG. 1, a gas cooler 1 of a supercritical
refrigeration cycle wherein a supercritical refrigerant, such as
CO.sub.2, is used includes two header tanks 2 and 3 extending
vertically and spaced apart from each other in the left-right
direction; a plurality of flat tubes 4 arranged in parallel between
the two header tanks 2 and 3 and spaced apart from one another in
the vertical direction in such a manner that the width direction of
the flat tubes 4 coincides with the front-rear direction;
corrugated fins 5 arranged in respective air-passing clearances
between adjacent flat tubes 4 and at the outside of the upper-end
and lower-end flat tubes 4 and each brazed to the adjacent flat
tubes 4 or to the upper-end or lower-end flat tube 4; and side
plates 6 of aluminum arranged externally of and brazed to the
respective upper-end and lower-end corrugated fins 5. In the case
of this embodiment, the header tank 2 at the right will be referred
to as the "first header tank," and the header tank 3 at the left as
the "second header tank."
[0033] As shown in FIGS. 2 to 7, the first header tank 2 is
configured such that an outside plate 7, an inside plate 8, and an
intermediate plate 9 intervening between the outside plate 7 and
the inside plate 8 are brazed together in layers. The outside plate
7 and the inside plate 8 are each formed from a brazing sheet
having a brazing material layer on each of opposite sides; herein,
an aluminum brazing sheet. The intermediate plate 9 is formed from
a bare metal material; herein, a bare aluminum material. The first
header tank 2 is configured such that an inlet header section 10A
and an outlet header section 10B are arranged in the vertical
direction.
[0034] The outside plate 7 has a plurality of; herein, two,
dome-like outwardly bulging portions 11A and 11B spaced apart from
each other in the vertical direction. The outwardly bulging
portions 11A and 11B have the same bulging height, length, and
width. In the outside plate 7, a peripheral portion around a
leftward-facing opening of each of the outwardly bulging portions
11A and 11B is brazed to the intermediate plate 9, whereby the
intermediate plate 9 covers the leftward-facing openings of the
outwardly bulging portions 11A and 11B. As a result, the interiors
of the outwardly bulging portions 11A and 11B serve as first
refrigerant flow sections 11a and 11b whose upper and lower ends
are closed and through which refrigerant flows in the vertical
direction.
[0035] A refrigerant inlet 12 is formed in a crest portion of the
upper outwardly bulging portion 11A of the outside plate 7. An
inlet member 13 of a metal; herein, a bare aluminum material,
having a refrigerant inflow channel 14 in communication with the
refrigerant inlet 12 is brazed to the outer surface of the
outwardly bulging portion 11A by use of the brazing material on the
outer surface of the outside plate 7. A refrigerant outlet 15 is
formed in a crest portion of the lower outwardly bulging portion
11B. An outlet member 16 of a metal; herein, a bare aluminum
material, having a refrigerant outflow channel 17 in communication
with the refrigerant outlet 15 is brazed to the outer surface of
the outwardly bulging portion 11B by use of the brazing material on
the outer surface of the outside plate 7. The outside plate 7 is
formed, by press work, from an aluminum brazing sheet having a
brazing material layer on each of opposite sides.
[0036] A plurality of tube insertion holes 18 elongated in the
front-rear direction are formed through the inside plate 8 and are
vertically spaced apart from one another. An upper-half group of
tube insertion holes 18 are formed within a vertical range
corresponding to the upper outwardly bulging portion 11A of the
outside plate 7. Similarly, a lower-half group of tube insertion
holes 18 are formed within a vertical range corresponding to the
lower outwardly bulging portion 11B. The tube insertion holes 18
have a front-to-rear length slightly longer than the front-to-rear
width of the outwardly bulging portions 11A and 11B such that front
and rear end portions thereof project outward beyond the front and
rear ends, respectively, of the outwardly bulging portions 11A and
11B. Front and rear edge portions of the inside plate 8 have
integrally formed respective cover walls 19. The cover walls 19
project rightward such that their ends reach the outer surface of
the outside plate 7, and cover respective boundary portions between
the outside plate 7 and the intermediate plate 9 along the overall
length of the boundary portions. The cover walls 19 are brazed to
the front and rear side surfaces, respectively, of the outside
plate 7 and the intermediate plate 9. The projecting end of each of
the cover walls 19 has a plurality of integrally formed engaging
portions 21 which are vertically spaced apart from one another and
which are engaged with the outer surface of the outside plate 7.
The engaging portions 21 of the cover walls 19 are engaged with and
brazed to the outer surface of the outside plate 7. Notably, before
the three plates 7, 8, and 9 are layered, as indicated by a chain
line in FIG. 7, the engaging portions 21 are not bent and extend
straight from the cover walls 19. The straight engaging portions
before being bent are denoted by 21A.
[0037] A pair of projecting portions 26 are integrally formed on
the inside plate 8 at positions located at opposite sides of each
tube insertion hole 18 with respect to the tube-width direction
(vertical direction). The projecting portions 26 project outward
with respect to the left-right direction; i.e., toward the
intermediate plate 9, via inclined portions which are slightly
inclined toward the tube-insertion-hole-18 side and toward the
intermediate plate 9 (outward with respect to the left-right
direction). The projecting portions 26 are formed by bending
portions of the inside plate 8 corresponding to the opposite edges
of each tube insertion hole 18 outward with respect to the
left-right direction. The vertically outer surfaces of the
projecting portions 26 are inclined outward with respect to the
left-right direction and toward the tube-insertion-hole-18 side.
The inside plate 8 is formed, by press work, from an aluminum
brazing sheet having a brazing material layer on each of opposite
sides.
[0038] The intermediate plate 9 has communication holes 22 in the
form of through-holes for allowing the tube insertion holes 18 of
the inside plate 8 to communicate with the interiors of the
outwardly bulging portions 11A and 11B of the outside plate 7 and
in a number equal to the number of the tube insertion holes 18. The
communication holes 22 positionally coincide with the respective
tube insertion holes 18 of the inside plate 8. The width of the
communication holes 22 of the intermediate plate 9 with respect to
the vertical direction is greater than that of the tube insertion
holes 18 of the inside plate 8, except for the front and rear end
portions of the communication holes. The projecting portions 26 on
the upper and lower sides of each tube insertion hole 18 of the
inside palate 8 enter the corresponding communication hole 22.
Notably, the width of the front and rear end portions of each
communication hole 22 with respect to the vertical direction is
generally equal to that of each tube insertion hole 18. Stepped
portions 25 are formed on the peripheral wall surface of each
communication hole 22 of the intermediate plate 9 at opposite end
portions thereof with respect to the hole-length direction (front
and rear end portions). The stepped portions 25 are located at an
intermediate position with respect to the plate-thickness direction
of the intermediate plate 9, and project inward with respect to the
hole-length direction of the communication hole 22. An end surface
of the flat tube 4 abuts the stepped portions 25. The projecting
height of the stepped portion 25 of the intermediate plate 9 from
the peripheral wall surface of the communication hole 22 is
determined so as not to cover a refrigerant channel 4a, which will
be described later, of the flat tube 4. An upper-half group of tube
insertion holes 18 of the inside plate 8 communicate with a first
refrigerant flow section 11a within the upper outwardly bulging
portion 11A of the outside plate 7 via an upper-half group of
respective communication holes 22 of the intermediate plate 9.
Similarly, a lower-half group of tube insertion holes 18
communicate with a first refrigerant flow section 11b within the
lower outwardly bulging portion 11B of the outside plate 7 via a
lower-half group of respective communication holes 22 of the
intermediate plate 9. All of the communication holes 22 in
communication with the upper-side first refrigerant flow section
11a of the outside plate 7 communicate with one another via
communication portions 23, and all of the communication holes 22 in
communication with the lower-side first refrigerant flow section
11b of the outside plate 7 communicate with one another via the
communication portions 23. The communication portions 23 are formed
by cutting off central portions (with respect to the front-rear
direction) of portions of the intermediate plate 9 between the
adjacent communication holes 22. As a result, the communication
portions 23 which connect the connection holes 22 facing the first
refrigerant flow section 11a of the outside plate 7 and the central
portions (with respect to the front-rear direction) of the
communication holes 22 (portions of the communication holes 22
corresponding to the communication portions 23) form in the
intermediate plate 9 a second refrigerant flow section 9a which
communicates with the first refrigerant flow section 11a of the
outside plate 7 and through which refrigerant flows in the vertical
direction. Similarly, the communication portions 23 which connect
the connection holes 22 facing the first refrigerant flow section
11b of the outside plate 7 and the central portions (with respect
to the front-rear direction) of the communication holes 22
(portions of the communication holes 22 corresponding to the
communication portions 23) form in the intermediate plate 9 a
second refrigerant flow section 9b which communicates with the
first refrigerant flow section 11b of the outside plate 7 and
through which refrigerant flows in the vertical direction. The
right ends of the flat tubes 4 are positioned within the second
refrigerant flow sections 9a and 9b of the intermediate plate 9;
i.e., at a thicknesswise intermediate portion of the intermediate
plate 9. The intermediate plate 9 is formed, by press work, from a
bare aluminum material.
[0039] Respective portions of the three plates 7, 8, and 9 of the
first header tank 2 which correspond to the outwardly bulging
portions 11A and 11B form the inlet header section 10A and the
outlet header section 10B. The two first refrigerant flow sections
11a and 11b of the outside plate 7 and the two second refrigerant
flow sections 9a and 9b of the intermediate plate 9 form the
internal refrigerant flow spaces of the inlet header section 10A
and the outlet header section 10B.
[0040] The second header tank 3 has substantially the same
construction as the first header tank 2, and like members and
portions are designated by like reference numerals (see FIG. 2).
The two header tanks 2 and 3 are disposed such that the respective
inside plates 8 face each other.
[0041] As shown in FIGS. 1, 2, and 8, the outside plate 7 of the
second header tank 3 has dome-like outwardly bulging portions
provided in a number one fewer than the outwardly bulging portions
11A and 11B of the first header tank 2; herein, a single dome-like
outwardly bulging portion 24, which extends from an upper end
portion to a lower end portion of the outside plate 7 and is
opposed to the outwardly bulging portions 11A and 11B of the first
header tank 2. In the outside plate 7, a peripheral portion around
a rightward-facing opening of the outwardly bulging portion 24 is
brazed to the intermediate plate 9, whereby the intermediate plate
9 covers the rightward-facing opening of the outwardly bulging
portion 24. As a result, the interior of the outwardly bulging
portion 24 serves as a first refrigerant flow section 24a whose
upper and lower ends are closed and through which refrigerant flows
in the vertical direction. The outwardly bulging portion 24 has
neither a refrigerant inlet nor a refrigerant outlet.
[0042] All of the tube insertion holes 18 of the inside plate 8 of
the second header tank 3 are formed within a vertical range
corresponding to the outwardly bulging portion 24 of the outside
plate 7. All of the tube insertion holes 18 of the inside plate 8
communicate with the first refrigerant flow section 24a within the
outwardly bulging portion 24 of the outside plate 7 via all of the
communication holes 22 of the intermediate plate 9. All of the
communication holes 22 of the intermediate plate 9 communicate with
one another via communication portions 23, which are formed by
cutting off central portions (with respect to the front-rear
direction) of portions of the intermediate plate 9 between the
adjacent communication holes 22. As a result, the communication
portions 23 and the central portions (with respect to the
front-rear direction) of the communication holes 22 (portions of
the communication holes 22 corresponding to the communication
portions 23) form in the intermediate plate 9 a second refrigerant
flow section 9c which communicates with the refrigerant flow
section 24a of the outside plate 7 and through which refrigerant
flows in the vertical direction.
[0043] Respective portions of the three plates 7, 8, and 9 of the
second header tank 3 which correspond to the outwardly bulging
portion 24 form intermediate header sections 20, the number of
which is one fewer than the two header sections 10A and 10B of the
first header tank 2; here, a single intermediate header section 20,
in such a manner that the intermediate header section 20 faces the
two header sections 10A and 10B of the first header tank 2. The
refrigerant flow section 24a of the outside plate 7 and the second
refrigerant flow section 9c of the intermediate plate 9 form the
internal refrigerant flow space of the intermediate header section
20.
[0044] The remaining portion of the second header tank 3 has the
same structure as the first header tank 2, and like members and
portions are denoted by the same reference numerals.
[0045] Here, the tube height, which is the thickness of each flat
tube 4 as measured in the vertical direction, is represented by T
(mm); the distance between each of the opposite longitudinal end
surfaces of each flat tube 4 and the outer surface of the
corresponding intermediate plate 9 is represented by L (mm); and
the width of each communication hole 22 of the intermediate plate
9, except for the narrow portions at the front and rear ends
thereof, is represented by W (mm). The gas cooler 1 must satisfy
the relations L.gtoreq.0.7 T and 1.1 T.ltoreq.W.ltoreq.2.5 T (see
FIG. 6).
[0046] When L<0.7 T, the clearance between each of the opposite
ends of each flat tube 4 and the corresponding outside plate 7
becomes too small, so that the pressure loss increases at the inlet
header section 10A of the first header tank 2 and a lower half
portion of the intermediate header section 20 of the second header
tank 3. That is, at the inlet header section 10A of the first
header tank 2, the pressure loss increases when the supercritical
refrigerant flows from the first refrigerant flow section 11a into
the second refrigerant flow section 9a, flows within the
communication holes 22 in the longitudinal direction thereof, and
flows into the flat tubes 4 from portions of the first ends of the
flat tubes 4 facing the inner surface of the corresponding outside
plate 7. Similarly, at the lower half portion of the intermediate
header section 20 of the second header tank 3, the pressure loss
increases when the supercritical refrigerant flows from the first
refrigerant flow section 24a into the second refrigerant flow
section 9c, flows within the communication holes 22 in the
longitudinal direction thereof, and flows into the flat tubes 4
from portions of the second ends of the flat tubes 4 facing the
inner surface of the corresponding outside plate 7. When the
pressure loss increases, the performance of the gas cooler 1
deteriorates. Further, the pressure loss increases at the outlet
header section 10B of the first header tank 2 and an upper half
portion of the intermediate header section 20 of the second header
tank 3. That is, at the outlet header section 10B of the first
header tank 2, the pressure loss increases when the supercritical
refrigerant flows from the portions of the first ends of the flat
tubes 4 facing the inner surface of the corresponding outside plate
7 into the communication holes 22 of the intermediate plate 9,
flows within the communication holes 22 in the longitudinal
direction thereof to enter the second refrigerant flow section 9b,
and then flows into the first refrigerant flow section 11b via the
second refrigerant flow section 9b. Similarly, at the upper half
portion of the intermediate header section 20 of the second header
tank 3, the pressure loss increases when the supercritical
refrigerant flows from the portions of the second ends of the flat
tubes 4 facing the inner surface of the corresponding outside plate
7 into the communication holes 22 of the intermediate plate 9,
flows within the communication holes 22 in the longitudinal
direction thereof to enter the second refrigerant flow section 9c,
and then flows into the first refrigerant flow section 24a via the
second refrigerant flow section 9c. When the pressure loss
increases, the performance of the gas cooler 1 deteriorates.
Preferably, the upper limit of L is 2.5 T. Even when L>2.5 T,
the above-described effect of suppressing an increase in pressure
loss is almost the same, and in addition, it is necessary to
decrease the tube height T of the flat tubes 4 and/or increase the
thickness of the intermediate plate 9. When the tube height T of
the flat tubes 4 is decreased, an increase in the pressure loss of
the flat tubes 4 themselves may possibly become greater than the
degree of suppression of an increase in the pressure loss at the
time when the supercritical refrigerant flows from the first
refrigerant flow sections 11a and 24a into the flat tubes 4 and
when the supercritical refrigerant flows from the flat tubes 4 into
the first refrigerant flow sections 11b and 24a. When the thickness
of the intermediate plate 9 is increased, the sizes and weights of
the header tanks 2 and 3 increase.
[0047] W is preferably set to a large value, because when the value
of W is small, pressure loss changes sharply with a change in L and
when the value of W is large, pressure loss changes mildly with a
change in L. However, when the value of W is excessively large, the
joint area between the outer surface of the intermediate plate 9
and the inner surface of the outside plate 7 decreases, and the
withstanding pressure of the header tanks 2 and 3 decreases.
Further, when the value of W is excessively small, inserting the
flat tubes 4 into the communication holes 22 becomes difficult.
Accordingly, the width W of the communication holes 22 must be
chosen within the range of 1.1 T to 2.5 T.
[0048] The first and second header tanks 2 and 3 are manufactured
as follows. That is, after the three plates 7, 8, and 9 are stacked
in layers, the straight engagement portions 21A are bent to form
the engagement portions 21, which are engaged with the outside
plate 7 so as to form a provisionally fixed assembly. After that,
the provisionally fixed assembly is heated to a predetermined
temperature so as to braze the three plates 7, 8, and 9 together by
use of the brazing material layers of the outside plate 7 and the
inside plate 8, braze the cover walls 19 to the front and rear end
surfaces of the intermediate plate 9 and the outside plate 7, and
further braze the engagement portions 21 to the outside plate 7.
Thus are manufactured the two header tanks 2 and 3.
[0049] As shown in FIGS. 9 and 10, each flat tube 4 includes
mutually opposed flat upper and lower walls 31 and 32 (a pair of
flat walls); front and rear side walls 33 and 34 which extend over
front and rear side ends, respectively, of the upper and lower
walls 31 and 32; and a plurality of reinforcement walls 35 which
are provided at predetermined intervals between the front and rear
side walls 33 and 34 and extend longitudinally and between the
upper and lower walls 31 and 32. By virtue of this structure, the
flat tube 4 internally has a plurality of refrigerant channels 4a
arranged in the width direction thereof.
[0050] The front side wall 33 has a dual structure and includes an
outer side-wall-forming elongated projection 36 which is integrally
formed with the front side end of the upper wall 31 in a downward
raised condition and extends along the entire height of the flat
tube 4; an inner side-wall-forming elongated projection 37 which is
located inside the outer side-wall-forming elongated projection 36
and is integrally formed with the upper wall 31 in a downward
raised condition; and an inner side-wall-forming elongated
projection 38 which is integrally formed with the front side end of
the lower wall 32 in an upward raised condition. The outer
side-wall-forming elongated projection 36 is brazed to the two
inner side-wall-forming elongated projections 37 and 38 and the
lower wall 32 while a lower end portion thereof is engaged with a
front side edge portion of the lower surface of the lower wall 32.
The two inner side-wall-forming elongated projections 37 and 38 are
brazed together while butting against each other. The rear side
wall 34 is integrally formed with the upper and lower walls 31 and
32. A projection 38a is integrally formed on the tip end face of
the inner side-wall-forming projection 38 of the lower wall 32 and
extends in the longitudinal direction of the inner
side-wall-forming projection 38 along the entire length thereof. A
groove 37a is formed on the tip end face of the inner
side-wall-forming elongated projection 37 of the upper wall 31 and
extends in the longitudinal direction of the inner
side-wall-forming elongated projection 37 along the entire length
thereof. The projection 38a is press-fitted into the groove
37a.
[0051] The reinforcement walls 35 are formed such that
reinforcement-wall-forming elongated projections 40 and 41, which
are integrally formed with the upper wall 31 in a downward raised
condition, and reinforcement-wall-forming elongated projections 42
and 43, which are integrally formed with the lower wall 32 in an
upward raised condition, are brazed together while the
reinforcement-wall-forming elongate projections 40 and 41 butt
against the reinforcement-wall-forming elongated projections 43 and
42, respectively. The upper wall 31 has the
reinforcement-wall-forming elongated projections 40 and 41, which
are of different projecting heights and are arranged alternately in
the front-rear direction. The lower wall 32 has the
reinforcement-wall-forming elongated projections 42 and 43, which
are of different projecting heights and are arranged alternately in
the front-rear direction. The reinforcement-wall-forming elongated
projections 40 of a long projecting height of the upper wall 31 and
the respective reinforcement-wall-forming elongated projections 43
of a short projecting height of the lower wall 32 are brazed
together. The reinforcement-wall-forming elongated projections 41
of a short projecting height of the upper wall 31 and the
respective reinforcement-wall-forming elongated projections 42 of a
long projecting height of the lower wall 32 are brazed together.
Hereinafter, the reinforcement-wall-forming elongated projections
40 and 42 of a long projecting height of the upper and lower walls
31 and 32 are called the first reinforcement-wall-forming elongated
projections. Similarly, the reinforcement-wall-forming elongated
projections 41 and 43 of a short projecting height of the upper and
lower walls 31 and 32 are called the second
reinforcement-wall-forming elongated projections. A groove 44 (45)
is formed on the tip end face of the second
reinforcement-wall-forming elongated projection 41 (43) of the
upper wall 31 (lower wall 32) and extends in the longitudinal
direction of the second reinforcement-wall-forming elongated
projection 41 (43) along the entire length thereof. A tip end
portion of the first reinforcement-wall-forming elongated
projection 42 (40) of the lower wall 32 (upper wall 31) is fitted
into the groove 44 (45) of the second reinforcement-wall-forming
elongated projection 41 (43) of the upper wall 31 (lower wall 32).
While tip end portions of the first reinforcement-wall-forming
elongated projections 40 and 42 of the upper and lower walls 31 and
32, respectively, are fitted into the respective grooves 45 and 44,
the reinforcement-wall-forming elongated projections 40 and 43 are
brazed together, and the reinforcement-wall-forming elongated
projections 41 and 42 are brazed together.
[0052] The flat tube 4 is manufactured by use of a tube-forming
metal sheet 50 as shown in FIG. 11(a). The tube-forming metal sheet
50 is formed, by rolling, from an aluminum brazing sheet having a
brazing material layer on each of opposite sides. The tube-forming
metal sheet 50 includes a flat upper-wall-forming portion 51
(flat-wall-forming portion); a flat lower-wall-forming portion 52
(flat-wall-forming portion); a connection portion 53 connecting the
upper-wall-forming portion 51 and the lower-wall-forming portion 52
and adapted to form the rear side wall 34; the inner
side-wall-forming elongated projections 37 and 38, which are
integrally formed with the side ends of the upper-wall-forming and
lower-wall-forming portions 51 and 52 opposite the connection
portion 53 in an upward raised condition and which are adapted to
form an inner portion of the front side wall 33; an outer
side-wall-forming-elongated-projection forming portion 54, which
extends outward from the side end of the upper-wall-forming portion
51 opposite the connection portion 53; and a plurality of
reinforcement-wall-forming elongated projections 40, 41, 42, and
43, which are integrally formed with the upper-wall-forming and
lower-wall-forming portions 51 and 52 in an upward raised condition
and which are arranged at predetermined intervals in the width
direction of the tube-forming metal sheet 50. The first
reinforcement-wall-forming elongated projections 40 of the
upper-wall-forming portion 51 and the second
reinforcement-wall-forming elongated projections 43 of the
lower-wall-forming portion 52 are located symmetrically with
respect to the centerline of the width direction of the connection
portion 53. Similarly, the second reinforcement-wall-forming
elongated projections 41 of the upper-wall-forming portion 51 and
the first reinforcement-wall-forming elongated projections 42 of
the lower-wall-forming portion 52 are located symmetrically with
respect to the centerline of the width direction of the connection
portion 53. The projection 38a is formed on the tip end face of the
inner side-wall-forming elongated projection 38 of the
lower-wall-forming portion 52, and the groove 37a is formed on the
tip end face of the inner side-wall-forming elongated projection 37
of the upper-wall-forming portion 51. The groove 44 (45), into
which a tip end portion of the first reinforcement-wall-forming
elongated projection 42 (40) of the lower-wall-forming portion 52
(upper-wall-forming portion 51) is fitted, is formed on the tip end
face of the second reinforcement-wall-forming elongated projection
41 (43) of the upper-wall-forming portion 51 (lower-wall-forming
portion 52).
[0053] The inner side-wall-forming elongated projections 37 and 38
and the reinforcement-wall-forming elongated projections 40, 41,
42, and 43 are integrally formed, by rolling, on one side of the
aluminum brazing sheet whose opposite sides are clad with a brazing
material, whereby a brazing material layer (not shown) is formed on
the opposite side surfaces and tip end faces of the inner
side-wall-forming elongated projections 37 and 38 and the
reinforcement-wall-forming elongated projections 40, 41, 42, and
43; on the peripheral surfaces of the grooves 44 and 45 of the
second reinforcement-wall-forming elongated projections 41 and 43;
and on the vertically opposite surfaces of the upper-wall-forming
and lower-wall-forming portions 51 and 52 and the outer
side-wall-forming-elongated-projection forming portion 54.
[0054] The tube-forming metal sheet 50 is gradually folded at
opposite side edges of the connection portion 53 by a roll forming
process (see FIG. 11(b)) until a hairpin form is assumed. The inner
side-wall-forming elongated projections 37 and 38 are caused to
butt against each other; tip end portions of the first
reinforcement-wall-forming elongated projections 40 and 42 are
fitted into the respective grooves 45 and 44 of the second
reinforcement-wall-forming elongated projections 43 and 41; and the
projection 38a is press-fitted into the groove 37a.
[0055] Next, the outer side-wall-forming-elongated-projection
forming portion 54 is folded along the outer surfaces of the inner
side-wall-forming elongated projections 37 and 38, and a tip end
portion thereof is deformed so as to be engaged with the
lower-wall-forming portion 52, thereby yielding a folded member 55
(see FIG. 11(c)).
[0056] Subsequently, the folded member 55 is heated at a
predetermined temperature so as to braze together tip end portions
of the inner side-wall-forming elongated projections 37 and 38; to
braze together tip end portions of the first and second
reinforcement-wall-forming elongated projections 40 and 43; to
braze together tip end portions of the first and second
reinforcement-wall-forming elongated projections 42 and 41; and to
braze the outer side-wall-forming-elongated-projection forming
portion 54 to the inner side-wall-forming elongated projections 37
and 38 and to the lower-wall-forming portion 52. Thus is
manufactured the flat tube 4.
[0057] While opposite end portions of the flat tubes 4 are inserted
through the respective tube insertion holes 18 of the inside plates
8 and into the respective communication holes 22 of the
intermediate plates 9 of the header tanks 2 and 3, and end surfaces
of the opposite end portions abut the respective stepped portions
25 of the intermediate plates 9, the opposite end portions of the
flat tubes 4 are brazed to the respective peripheral wall surfaces
of the tube insertion holes 18 of the inside plates 8 and to the
respective peripheral wall surfaces of the front and rear narrow
end portions of the communication holes 22 of the intermediate
plates 9 by utilization of the brazing material layers of the
inside plates 8 and the brazing material layers of the tube-forming
metal sheets 50.
[0058] Accordingly, right end portions of an upper-half group of
flat tubes 4 are connected to the first header tank 2 so as to
communicate with the interior of the upper outwardly bulging
portion 11A, and left end portions are connected to the second
header tank 3 so as to communicate with the interior of the
outwardly bulging portion 24. Also, right end portions of a
lower-half group of flat tubes 4 are connected to the first header
tank 2 so as to communicate with the interior of the lower
outwardly bulging portion 11B, and left end portions are connected
to the second header tank 3 so as to communicate with the interior
of the outwardly bulging portion 24.
[0059] Each of the corrugated fins 5 is made in a wavy form from a
brazing sheet; herein, an aluminum brazing sheet, having a brazing
material layer on each of opposite sides.
[0060] The gas cooler 1 is manufactured by the steps of: preparing
the aforementioned two provisionally fixed assemblies to be
manufactured into the header tanks 2 and 3, a plurality of the
aforementioned folded members 55, and a plurality of corrugated
fins 5; arranging the two provisionally fixed assemblies in such a
manner as to be spaced apart from each other with the inside plates
8 facing each other; arranging alternately the folded members 55
and the corrugated fins 5; inserting opposite end portions of the
folded members 55 through the respective tube insertion holes 18 of
the inside plates 8 and into the respective communication holes 22
of the intermediate plates 9 of the two provisionally fixed
assemblies, and causing the end surfaces of the opposite end
portions to abut the respective stepped portions 25 of the
intermediate plate 9; arranging the side plates 6 externally of the
respective opposite-end corrugated fins 5; arranging the inlet
member 13 and the outlet member 16 on the outwardly bulging
portions 11A and 11B, respectively, of the outside plate 7 used to
form the first header tank 2; and brazing necessary portions of the
provisionally fixed assemblies as mentioned above to thereby form
the header tanks 2 and 3, brazing necessary portions of the folded
members 55 as mentioned above to thereby form the flat tubes 4,
brazing the flat tubes 4 to the header tanks 2 and 3, brazing the
corrugated fins 5 to the flat tubes 4, brazing the side plates 6 to
the respective corrugated fins 5, and brazing the inlet member 13
and the outlet member 16 to the outwardly bulging portions 11A and
11B, respectively.
[0061] The gas cooler 1, together with a compressor, an evaporator,
a pressure-reducing device, and an intermediate heat exchanger for
performing heat exchange between refrigerant from the gas cooler
and refrigerant from the evaporator, constitutes a supercritical
refrigeration cycle. The refrigeration cycle is installed in a
vehicle, for example, in an automobile, as a car air
conditioner.
[0062] As shown in FIG. 12, in the gas cooler 1 described above,
CO.sub.2 from a compressor flows through the refrigerant inflow
channel 14 of the inlet member 13 and enters the first refrigerant
flow section 11a of the upper outwardly bulging portion 11A of the
first header tank 2 through the refrigerant inlet 12. Then, the
CO.sub.2 dividedly flows into the refrigerant channels 4a of all
the flat tubes 4 in communication with the upper outwardly bulging
portion 11A via the upper-side second refrigerant flow section 9a
and the communication holes 22 of the intermediate plate 9. The
CO.sub.2 in the refrigerant channels 4a flows leftward through the
refrigerant channels 4a and enters the first refrigerant flow
section 24a of the outwardly bulging portion 24 of the second
header tank 3. The CO.sub.2 in the first refrigerant flow section
24a of the outwardly bulging portion 24 flows downward through the
first refrigerant flow section 24a and through the second
refrigerant flow section 9c of the intermediate plate 9; dividedly
flows into the refrigerant channels 4a of all the flat tubes 4 in
communication with the lower outwardly bulging portion 11B via the
second refrigerant flow section 9c and the communication holes 22;
flows rightward through the refrigerant channels 4a; and enters the
first refrigerant flow section 11b of the lower outwardly bulging
portion 11B via the lower-side second refrigerant flow section 9b
and the communication holes 22 of the intermediate plate 9 of the
first header tank 2. Subsequently, the CO.sub.2 flows out of the
gas cooler 1 via the refrigerant outlet 15 and the refrigerant
outflow channel 17 of the outlet member 16. While flowing through
the refrigerant channels 4a of the flat tubes 4, the CO.sub.2 is
subjected to heat exchange with the air flowing through the
air-passing clearances in the direction of arrow X shown in FIGS. 1
and 12, thereby being cooled.
[0063] Next, there will be described text examples performed by use
of the above-described gas cooler 1.
TEST EXAMPLE 1
[0064] Three types of gas coolers 1 which differ in the width W of
the communication holes 22 of the intermediate plate 9 were
prepared, and, while the distance L between each of the opposite
longitudinal end surfaces of each flat tube 4 and the inner surface
of the corresponding outside plate 7 was changed to various values,
the relation between the above-described distance L and pressure
loss was investigated for the gas cooler 1 of each type. Notably,
the gas coolers 1 are identical in terms of the dimensions of the
components and portions, other than the distance L. FIG. 13 shows
the results of the test.
[0065] The results shown in FIG. 13 demonstrate that in each gas
cooler 1, an increase in pressure loss can be suppressed when the
relation L.ltoreq.0.7 T is satisfied, where T represents the tube
height in mm of the flat tubes 4. Further, the results demonstrate
that the smaller the width W of the communication holes 22 of the
intermediate plate 9, the greater the degree to which a change in
pressure loss with a change in L becomes sharp, and the greater the
width W, the greater the degree to which a change in pressure loss
with a change in L becomes mild.
TEST EXAMPLE 2
[0066] Gas coolers 1 were fabricated, while the width W of the
communication holes 22 of the intermediate plate 9 was changed to
various values, and the relation between the width W and the
withstanding pressure of the header tanks 2 and 3 was investigated.
The gas coolers 1 are identical in terms of the dimensions of the
components and portions, other than the width W. FIG. 14 shows the
results of the test.
[0067] The results shown in FIG. 14 demonstrate that the
withstanding pressure of the header tanks 2 and 3 increases when
W.ltoreq.2.5 T.
[0068] In the above-described embodiment, the heat exchanger of the
present invention is applied to a gas cooler of a supercritical
refrigeration cycle. However, the heat exchanger of the present
invention may be applied to an evaporator of the above-mentioned
supercritical refrigeration cycle. This evaporator, together with a
compressor, a gas cooler, a pressure-reducing device, and an
intermediate heat exchanger for performing heat exchange between
refrigerant from the gas cooler and refrigerant from the
evaporator, constitutes a supercritical refrigeration cycle which
uses a supercritical refrigerant such as CO.sub.2. This
refrigeration cycle is installed in a vehicle, for example, in an
automobile, as a car air conditioner.
[0069] In the above-described embodiment, each of the header tanks
2 and 3 is formed by stacking three types of plates; i.e., the
outside plate 7, the inside plate 8, and the intermediate plate 9,
one sheet each. However, the present invention is not limited
thereto, and two or more intermediate plates 9 may be stacked.
[0070] Although CO.sub.2 is used as a supercritical refrigerant of
a supercritical refrigeration cycle in the above-described
embodiments, the refrigerant is not limited thereto, but ethylene,
ethane, nitrogen oxide, or the like may be alternatively used.
[0071] The above-described embodiment uses, for forming the flat
tube 4, a folded member 55 which is formed by bending a
tube-forming metal sheet in the form of an aluminum brazing sheet
having a brazing material layer on each of opposite sides. However,
the present invention is not limited thereto. For example, an
aluminum extrudate having a brazing material layer on its outer
surface may be used to form the flat tube 4.
* * * * *