U.S. patent application number 12/994193 was filed with the patent office on 2011-04-28 for heat exchanger and air conditioner provided with heat exchanger.
This patent application is currently assigned to Mitsubishi Electric Corporation. Invention is credited to Akira Ishibashi, Sangmu Lee, Takuya Matsuda.
Application Number | 20110094258 12/994193 |
Document ID | / |
Family ID | 41433964 |
Filed Date | 2011-04-28 |
United States Patent
Application |
20110094258 |
Kind Code |
A1 |
Lee; Sangmu ; et
al. |
April 28, 2011 |
HEAT EXCHANGER AND AIR CONDITIONER PROVIDED WITH HEAT EXCHANGER
Abstract
A heat exchanger provided with a plurality of plate-like fins 2
arranged in parallel with a predetermined interval and a plurality
of flat-shaped heat transfer pipes 3 inserted in a direction
orthogonal to said plate-like fins 2 and through which a
refrigerant flows, in which said heat transfer pipe 3 has an
outside shape with a flat outer face arranged along an air flow
direction and a section substantially in an oval shape and first
and second refrigerant flow passages 31a, 31b made of two symmetric
and substantially D-shaped through holes having a bulkhead 32
between the two passages inside, which is bonded to said plate-like
fin 2 by expanding diameters of said first and second refrigerant
flow passages 31a, 31b by a pipe-expanding burette ball.
Inventors: |
Lee; Sangmu; (Tokyo, JP)
; Ishibashi; Akira; (Tokyo, JP) ; Matsuda;
Takuya; (Tokyo, JP) |
Assignee: |
Mitsubishi Electric
Corporation
Chiyoda-ku
JP
|
Family ID: |
41433964 |
Appl. No.: |
12/994193 |
Filed: |
May 8, 2009 |
PCT Filed: |
May 8, 2009 |
PCT NO: |
PCT/JP2009/058685 |
371 Date: |
November 23, 2010 |
Current U.S.
Class: |
62/498 ;
165/181 |
Current CPC
Class: |
F28F 1/40 20130101; F28F
1/12 20130101; F25B 1/005 20130101; F28F 1/325 20130101; F28F 1/10
20130101; F28F 1/405 20130101; F28D 1/0478 20130101; B21D 53/08
20130101; F28F 1/022 20130101; F28F 2275/125 20130101; Y10T
29/49373 20150115 |
Class at
Publication: |
62/498 ;
165/181 |
International
Class: |
F25B 1/00 20060101
F25B001/00; F28F 1/12 20060101 F28F001/12 |
Foreign Application Data
Date |
Code |
Application Number |
Jun 19, 2008 |
JP |
2008-160060 |
Claims
1. A heat exchanger provided with a plurality of plate-like fins
arranged in parallel with a predetermined interval and a plurality
of flat-shaped heat transfer pipes inserted in a direction
orthogonal to said plate-like fins and through which a refrigerant
flows, wherein said heat transfer pipes have an outside shape with
a flat outer face arranged along an air flow direction and a
section substantially in an oval shape and first and second
refrigerant flow passages made of two symmetric and substantially
D-shaped through holes having a bulkhead between the two passages
inside, which are bonded to said plate-like fin by expanding
diameters of said first and second refrigerant flow passages by a
pipe-expanding burette ball.
2. The heat exchanger according to claim 1, wherein a flow passage
of one of or both of said first and second refrigerant flow
passages has a plurality of protruding strips extending in an axial
direction on an inner wall face.
3. The heat exchanger according to claim 2, wherein said plurality
of protruding strips are formed at a required height so that their
distal ends are brought into contact with a circular outer
circumferential face of the pipe-expanding burette ball.
4. The heat exchanger according to claim 2, wherein a height of the
protruding strip after pipe expansion is approximately 0.1 to 0.3
mm.
5. A heat exchanger provided with a plurality of plate-like fins
arranged in parallel with a predetermined interval and a plurality
of flat-shaped heat transfer pipes inserted in a direction
orthogonal to said plate-like fins and through which a refrigerant
flows, wherein said heat transfer pipes have an outside shape with
a flat outer face arranged along an air flow direction and a
section substantially in an oval shape and first and second
refrigerant flow passages made of two symmetric and substantially
D-shaped through holes having a bulkhead between the two passages
inside, and one of or both of said first and second refrigerant
flow passages have a plurality of protruding strips extending in an
axial direction on an inner wall face of the flow passage.
6. The heat exchanger according to claim 5, wherein said
refrigerant flow passage on which said plurality of protruding
strips are provided is constituted so that a distance between a
predetermined point at the center part of said refrigerant flow
passage and each of distal end portions of said plurality of
protruding strips in the section becomes substantially equal.
7. The heat exchanger according to claim 5, wherein a plurality of
refrigerant circuits are constituted in a column direction using
said heat transfer pipe whose intermediate portion is given bending
work, and refrigerant outlet portions of said first and second
refrigerant flow passages of one of adjacent heat transfer pipes
and refrigerant inlet portions of said first and second refrigerant
flow passages of the other heat transfer pipe are connected to each
other by two return bend pipes in a cross state.
8. The heat exchanger according to claim 5, wherein a plurality of
refrigerant circuits are constituted in a column direction using
said heat transfer pipe whose intermediate portion is given bending
work, and refrigerant outlet portions of said first and second
refrigerant flow passages of one of adjacent heat transfer pipes
and refrigerant inlet portions of said first and second refrigerant
flow passages of the other heat transfer pipe are connected to each
other by a single return bend pipe so that the refrigerants are
mixed.
9. An air conditioner provided with a refrigerating cycle in which
a compressor, a condenser, a throttle device, and an evaporator are
sequentially connected by piping, wherein a refrigerant is used as
an operating fluid and the heat exchanger according to claim 1 is
used as said evaporator or condenser.
10. The air conditioner according to claim 9, wherein any of a HC
single refrigerant or a mixed refrigerant containing HC, R32,
R410A, R407C, carbon dioxide is used as a refrigerant.
11. The heat exchanger according to claim 3, wherein a height of
the protruding strip after pipe expansion is approximately 0.1 to
0.3 mm.
12. The heat exchanger according to claim 6, wherein a plurality of
refrigerant circuits are constituted in a column direction using
said heat transfer pipe whose intermediate portion is given bending
work, and refrigerant outlet portions of said first and second
refrigerant flow passages of one of adjacent heat transfer pipes
and refrigerant inlet portions of said first and second refrigerant
flow passages of the other heat transfer pipe are connected to each
other by two return bend pipes in a cross state.
13. The heat exchanger according to claim 6, wherein a plurality of
refrigerant circuits are constituted in a column direction using
said heat transfer pipe whose intermediate portion is given bending
work, and refrigerant outlet portions of said first and second
refrigerant flow passages of one of adjacent heat transfer pipes
and refrigerant inlet portions of said first and second refrigerant
flow passages of the other heat transfer pipe are connected to each
other by a single return bend pipe so that the refrigerants are
mixed.
14. An air conditioner provided with a refrigerating cycle in which
a compressor, a condenser, a throttle device, and an evaporator are
sequentially connected by piping, wherein a refrigerant is used as
an operating fluid and the heat exchanger according to claim 5 is
used as said evaporator or condenser.
15. The air conditioner according to claim 14, wherein any of a HC
single refrigerant or a mixed refrigerant containing HC, R32,
R410A, R407C, carbon dioxide is used as a refrigerant.
Description
TECHNICAL FIELD
[0001] The present invention relates to a heat exchanger and an air
conditioner provided with this heat exchanger.
BACKGROUND ART
[0002] A prior-art heat exchanger constituting an air conditioner
includes a heat exchanger called fin-tube heat exchanger. This heat
exchanger is constituted by plate-like fins arranged with a certain
interval and through which gas (air) flows and a flat-shaped heat
transfer pipe inserted orthogonally into the plate-like fins and
through which a refrigerant flows, and a plurality of protruding
strips are provided in the axial direction on an inner face of the
heat transfer pipe (See Patent Document 1, for example). Also, a
heat exchanger having a flat-shaped heat transfer pipe in a
multi-hole structure or a heat exchanger having a plurality of
slits provided in a plate-like fin by cutting are included. The
slit group is provided so that a side end portion of the slit
opposes a flow direction of air, and it is described that by
thinning a speed boundary layer and a temperature boundary layer of
the air flow at the side end portion of the slit, heat transfer is
promoted and heat exchange capacity is increased (See Patent
Document 2, for example).
PRIOR ARTS
[0003] [Patent Document 1] Japanese Unexamined Patent Application
Publication No. 11-94481 (FIGS. 1 to 3)
[0004] [Patent Document 2] Japanese Unexamined Patent Application
Publication No 2003-262485 (FIGS. 1 to 4)
SUMMARY OF INVENTION
Problems to be Solved by the Invention
[0005] In the heat exchanger of Patent Document 1, since the heat
transfer pipe is formed in a flat elliptic shape having a single
through hole through which a refrigerant flows, the heat transfer
pipe is expanded and deformed by a pressure inside the heat
transfer pipe during an operation of a refrigerating system, there
is a problem that close contact between the heat transfer pipe and
the plate-like fin is deteriorated.
[0006] With the purpose of improving performance of the heat
exchanger, the heat transfer pipe can be made into a multi-hole
structure and its size and diameter can be reduced as in Patent
Document 2. However, by reducing the size and diameter of the heat
transfer pipe, heat transfer rate in the pipe is increased while
pressure loss is increased, and they need to be optimized. Also,
the heat transfer pipe whose size and diameter are reduced is
advantageous in heat transfer performance, but there is a problem
that a cost for assembling or the like is increased since
manufacture of the heat transfer pipe and mounting between the heat
transfer pipe and the plate-like fin are carried out by
brazing.
[0007] The present invention was made in order to solve the above
problems and has an object to provide a heat exchanger and an air
conditioner provided with this heat exchanger in which ventilation
resistance is reduced and heat exchange capacity is increased by
using a heat transfer pipe in which deformation of the heat
transfer pipe caused by a pressure inside the heat transfer pipe
does not occur even if the heat transfer pipe is made flat, close
contact with the plate-like fin is favorable, assembling
performance is good, and heat transfer performance is
excellent.
Means for Solving the Problems
[0008] A heat exchanger according to the present invention is
provided with a plurality of plate-like fins arranged in parallel
with a predetermined interval and a plurality of flat-shaped heat
transfer pipes inserted in a direction orthogonal to the plate-like
fins and through which a refrigerant flows, and the heat transfer
pipe has an outside shape with a flat outer face arranged along an
air flow direction and a section substantially in an oval shape and
first and second refrigerant flow passages made of two symmetric
and substantially D-shaped through holes having a bulkhead between
the two passages inside, which is bonded to the plate-like fin by
expanding diameters of the first and second refrigerant flow
passages by a pipe-expanding burette ball.
Advantages
[0009] According to the present invention, since the bulkhead
partitioning the two refrigerant flow passages are provided inside
the flat-shaped heat transfer pipe, deformation of the heat
transfer pipe is not caused by a pressure inside the heat transfer
pipe even if the heat transfer pipe is made flat, and a heat
transfer pipe in which close contact with the plate-like fin is
favorable, assembling performance is good and heat transfer
performance is excellent can be obtained. Also, by using the
flat-shaped heat transfer pipe with excellent heat transfer
performance with reduced size and diameter, such a heat exchanger
can be obtained in which ventilation resistance is reduced and heat
exchange capacity is increased.
BRIEF DESCRIPTION OF DRAWINGS
[0010] FIG. 1 is a front view illustrating an outline of a heat
exchanger according to a first embodiment of the present
invention.
[0011] FIG. 2 is a front view of a heat transfer pipe of the first
embodiment.
[0012] FIG. 3 is an explanatory diagram of pipe-expanding means for
the heat transfer pipe in FIG. 2.
[0013] FIG. 4 is A-A sectional view of the pipe-expanding means in
FIG. 3.
[0014] FIG. 5 is a front view of a heat transfer pipe of a second
embodiment.
[0015] FIG. 6 is a diagram illustrating a relation between a height
of a protruding strip and a heat exchange rate after pipe
expansion.
[0016] FIG. 7 is a front view of a heat transfer pipe of a third
embodiment.
[0017] FIG. 8 is an explanatory diagram of pipe-expanding means for
the heat transfer pipe in FIG. 7.
[0018] FIG. 9 is B-B sectional view f the pipe-expanding means in
FIG. 8.
[0019] FIG. 10 is a front view of a heat transfer pipe of a fourth
embodiment.
[0020] FIGS. 11 are explanatory views of a prior-art fin-tube heat
exchanger.
[0021] FIG. 12 is a front view illustrating an outline of a heat
exchanger according to a fifth embodiment.
[0022] FIG. 13 is a front view illustrating an outline of a heat
exchanger according to a sixth embodiment.
MODES FOR CARRYING OUT THE INVENTION
[0023] Embodiments of the present invention will be described below
referring to the attached drawings.
First Embodiment
[0024] FIG. 1 is a front view illustrating an outline of a heat
exchanger according to a first embodiment of the present invention.
In FIG. 1, reference numeral 1 denotes a heat exchanger constituted
by a plurality of plate-like fins 2 arranged in parallel with a
predetermined interval and a plurality of flat-shaped heat transfer
pipes 3 inserted in a direction orthogonal to the plate-like fins 2
and bonded to the plate-like fins 2 by pipe expansion (also called
diameter expansion). The plate-like fins 2 are made of a metal
plate such as copper or copper alloy or aluminum or aluminum alloy
(similarly in the other embodiments) and provided in parallel with
an air flow direction A and with a predetermined interval in a
perpendicular direction (depth direction) in the figure. On the
plate-like fin 2, the flat-shaped heat transfer pipes 2, which will
be described later, are provided in plural stages and in one row or
more in a direction (vertical direction in the figure)
perpendicular to the air flow direction A. Moreover, a plurality of
slits 4 are provided in the plate-like fin 2 by cutting between
each stage of the flat-shaped heat transfer pipes 3. The slit 4 is,
as shown in Patent Document 2, provided so that a side end portion
of the slit 4 opposes the air flow direction A, and by thinning a
speed boundary layer and a temperature boundary layer of the air
flow at the side end portion, such an advantage is provided that
heat transfer is promoted and heat exchange capacity is
increased.
[0025] The heat transfer pipe 3 is formed such that, as shown in
FIG. 2, the pipe is elongated along the air flow direction A, upper
and lower outer faces 3a, 3b are flat and a section is
substantially in an oval shape (or flat elliptic shape). That is,
the upper and lower outer faces 3a and 3b are flat and side faces
3c, 3d on an upwind side and a downwind side have a flat outside
shape forming a semicircle. This flat-shaped heat transfer pipe 3
is made of a metal material such as copper or copper alloy or
aluminum or aluminum alloy and the like and formed by an extrusion
material (similarly in the other embodiments). Inside the heat
transfer pipe 3, first and second refrigerant flow passages 31a,
31b made of two symmetric substantially D-shaped through holes are
provided on both sides in the horizontal direction (hereinafter
referred to as width direction) in the figure in parallel with the
axial direction having a bulkhead 32 between them. That is, the
heat transfer pipe 3 has a flat and substantially D-shaped two-hole
structure.
[0026] A radius r after diameter expansion (which will be described
later) of the first, second refrigerant flow passages 31a, 31b made
of such substantially D-shaped through holes is 1 to 3 mm. That is
because if the radius r is less than 1 mm, an increase amount of
pressure loss becomes larger than an increase amount of heat
transfer rate, which results in lowered heat exchange performance.
On the other hand, if the radius r exceeds 3 mm, not only that an
inter-pipe refrigerant flow velocity is slowed and the heat
exchange performance is lowered but that a height (thickness) H and
a width W of the flat-shaped heat transfer pipe 3 are increased and
the pressure loss of the air flow is increased. Thus, the radius r
after the diameter expansion of the first, second refrigerant flow
passages 31a, 31b is set at 1 to 3 mm (the same applies to the
radius r of the refrigerant flow passage in the other
embodiments).
[0027] Subsequently, an example of a diameter expansion procedure
of the first, second refrigerant flow passages 31a, 31b of the
above flat-shaped heat transfer pipe 3 and a mounting procedure to
a mounting hole (long hole) 22 provided in the plate-like fin 2
will be described.
[0028] As shown in FIG. 3, the long-hole mounting hole 22 is
provided in a fin collar portion 21 of the pressed plate-like fin
2, and each of the plate-like fins 2 is held by a jig (riot shown)
or the like with the fin collar portion 21 aligned in the same
direction. The above-mentioned flat-shaped heat transfer pipe 3 is
inserted into the mounting hole 22 of each of the plate-like fins
2, and then, using a pipe expanding device using a pair of
pipe-expanding burette balls 100 made of a metal material such as a
super hard alloy or the like and having the same sectional shape
(substantially D-shaped, see FIG. 4) as the first, second
refrigerant flow passages 31a, 31b, the pair of pipe expanding
burette balls 100 are pushed into the first, second refrigerant
flow passages 31a, 31b by a mechanical method or a fluid pressure.
Then, the first, second refrigerant flow passages 31a, 31b are
diameter-expanded at the same time, and the heat transfer pipe 3 is
sequentially bonded to each of the plate-like fins 2 and integrally
fixed.
[0029] In this case, a thickness t2 of the bulkhead 32 of the
first, second refrigerant flow passages 31a, 31b is preferably
formed thicker about 1.5 times a thickness t1 of the first, second
refrigerant flow passages 31a, 31b. As a result, pressure capacity
of the flat-shaped heat transfer pipe 3 can be increased.
[0030] As mentioned above, according to the heat transfer pipe of
this embodiment, since the pressure capacity of the flat-shaped
heat transfer pipe 3 can be maintained by the bulkhead 32 provided
between the first, second flow passages 31a, 31b, the flat-shaped
heat transfer pipe 3 is not deformed by the pressure inside the
heat transfer pipe and the close contact with the plate-like fin 2
can be kept favorable. Thus, the heat transfer pipe with excellent
heat transfer performance can be obtained. Also, since the
flat-shaped heat transfer pipe 3 is bonded to the plate-like fin 2
by pipe expansion, assembling is far easier than brazing.
Therefore, a manufacturing cost can be lowered. Moreover, an
interval between the plate-like fins 2 can be kept constant by the
fin collar portion 21 in the same direction and close contact
between the flat-shaped heat transfer pipe 3 and the plate-like fin
2 is favorable, the heat exchanger in which the ventilation
resistance is reduced and heat exchange capacity can be increased
can be obtained even if the heat transfer pipe is made flat and the
size and diameter are reduced.
Second Embodiment
[0031] FIG. 5 is a front view illustrating a flat-shaped heat
transfer pipe of a second embodiment. The heat transfer pipe 3 of
this embodiment has, as in the case of FIG. 2, the first, second
refrigerant flow passages 31a, 31b made of through holes having
substantially a D-shaped section provided on both sides in the
width direction. On inner wall faces of the first, second
refrigerant flow passages 31a, 31b, respectively, a plurality of
protruding strips 33 having a substantially square section (its
distal end portion is in a slightly rounded shape) are provided in
the axial direction with a constant height and interval.
[0032] The above flat-shaped heat transfer pipe 3 is inserted into
the mounting hole 22 of the plate-like fin 2 according to the
above-mentioned procedure and fixed to the plate-like fin 2 by
expanding the diameters of the first, second refrigerant flow
passages 31a, 31b through each protruding strip 33 using the
pipe-expanding burette balls 100 having the same sectional shape
(substantially D-shape) as above.
[0033] As shown in FIG. 6, in the flat-shaped heat transfer pipe 3
of this embodiment, the higher a height h (protruding length) of
the protruding strip 33 after pipe expansion is, the higher the
heat transfer rate becomes since a contact area is increased.
However, if the height h of the protruding strip 33 after the pipe
expansion exceeds 0.3 mm, the increase amount of pressure loss
becomes larger than the increase amount of the heat transfer rate,
and as a result, the heat exchange rate is lowered. On the other
hand, if the height h of the protruding strip 33 after the pipe
expansion is less than 0.1 mm, the heat transfer rate is not
improved. Thus, in the flat-shaped heat transfer pipe 3 of this
embodiment, the height h (protruding length) of the protruding
strip 33 after the pipe expansion is preferably approximately 0.1
to 0.3 mm. The sectional shape of the protruding strip 33 is not
limited to a square, but any appropriate sectional shape such as
triangle, trapezoid, semicircle and the like can be employed.
Third Embodiment
[0034] FIG. 7 is a front view illustrating a flat-shaped heat
transfer pipe of a third embodiment. The heat transfer pipe 3 of
this embodiment has, similarly to FIG. 2, the first and second
refrigerant flow passages 31a, 31b made of through holes having
sections substantially in the D-shape provided on both sides in the
width direction. On the inner wall faces of the first, second
refrigerant flow passages 31a, 31b, a plurality of protruding
strips 33, 34 having a predetermined height and interval and
sections substantially in a square shape (the distal end portions
are in a slightly rounded shape) are provided in the axial
direction. The protruding strip 34 is provided at corner portions
of the bulkhead 32 and further at a required height h so that
distal ends of the protruding strips 33, 34 are brought into
contact with a circle with a radius R, that is, an outer
circumferential face (See FIG. 9) of a circle of the pipe-expanding
burette ball 100.
[0035] In other words, the first, second refrigerant flow passages
31a, 31b on which the plurality of protruding strips 33, 34 are
provided are constituted so that a distance from predetermined
points at the center parts of the refrigerant flow passages in the
section (O1, O2 in FIG. 7) to each of the distal end portions of
the plurality of the protruding strips 33, 34 becomes substantially
equal. The points O1, O2 are points matching the centers of the
pipe-expanding burette balls 100 when the pipe is expanded.
[0036] This flat-shaped heat transfer pipe 3 is inserted into the
mounting hole 22 of the plate-like fin 2 as shown in FIG. 8
according to the above-mentioned procedure and fixed to the
plate-like fin 2 by expanding the diameters of the first, second
refrigerant flow passages 31a, 31b through each protruding strip
33, 34 using pipe-expanding burette balls 41 having a circular
section. In this case, the height h (protruding length) of the
protruding strip 33 is preferably approximately 0.1 to 0.3 mm. By
using the pipe-expanding burette ball 100 having the circular outer
circumferential face, the pipe-expanding burette ball can be easily
positioned. The sectional shape of the protruding strips 33, 34 is
not limited to a square, but any appropriate sectional shape such
as triangle, trapezoid, semicircle and the like can be
employed.
Fourth Embodiment
[0037] FIG. 10 is a front view illustrating a flat-shaped heat
transfer pipe of a fourth embodiment. The heat transfer pipe 3 of
this embodiment has the first refrigerant flow passage 31a in the
same shape as that of the first embodiment and the second
refrigerant flow passage 31b in the same shape as that of the third
embodiment. It is needless to say that the combination may be
opposite.
[0038] This flat-shaped heat transfer 3 is inserted into the
mounting hole 21 of the plate-like fin 2 according to the
above-mentioned procedure and fixed to the plate-like fin 2 by
expanding the diameter of the first refrigerant flow passage 31a
using the pipe-expanding burette ball 41 having a substantially
D-shaped section and by expanding the diameter of the second
refrigerant flow passage 31b using the pipe-expanding burette ball
41 having a circular section. In this case, the height h
(protruding length) of the protruding strip 33 is preferably
approximately 0.1 to 0.3 mm. The sectional shape of the protruding
strip 33 is not limited to a square, but any appropriate sectional
shape such as triangle, trapezoid, semicircle and the like can be
employed.
[0039] According to this embodiment, the first embodiment and the
third embodiment are applied in combination to the first, second
refrigerant flow passages 31a, 31b, and the effect substantially
similar to these embodiments can be obtained. That is, the
flat-shaped heat transfer pipe 3 is not deformed by the pressure
inside the heat transfer pipe, and close contact with the
plate-like fin 2 can be maintained favorable. Thus, the heat
transfer pipe having excellent heat transfer performance can be
obtained. Also, since the flat-shaped heat transfer pipe 3 is
bonded to the plate-like fin 2 by pipe expansion, assembling is far
easier than brazing. Therefore, a manufacturing cost can be
reduced. Moreover, since each of the plate-like fins 2 can be
maintained with a constant interval by the fin collar portion 21 in
the same direction and close contact between the flat-shaped heat
transfer pipe 3 and the plate-like fin 2 is favorable, even if the
heat transfer pipe is made flat or reduced in size and diameter, a
heat exchanger in which ventilation resistance is reduced and heat
exchange capacity can be increased can be obtained.
[0040] Also, if the plurality of protruding strips 33, 34 are
provided on the inner wall face of the refrigerant flow passage
31b, either of the refrigerant flow passages, a contact area with
the refrigerant is increased, and since the height h of the
protruding strip 33 is set at approximately 0.1 to 0.3 mm, a
pressure inside the flow passage is not increased but the heat
transfer performance can be further improved.
Fifth Embodiment
[0041] FIGS. 11 are explanatory diagrams illustrating a prior-art
fin-tube heat exchanger, in which FIG. 11A shows a front face side,
and FIG. 11B shows a back face side of a heat transfer pipe
connected state. FIG. 12 is a front view of a heat exchanger
according to a fifth embodiment;
[0042] First, FIG. 11 will be described. The heat transfer pipe is
given bending work in a hairpin state with a predetermined bending
pitch at its intermediate portion so as to manufacture a plurality
of hairpin pipes 51, and then, the plurality of hairpin pipes 51
are inserted from the back face side into plate-like fins 2
arranged in parallel with each other with a predetermined interval.
Then, the heat transfer pipe is expanded by a mechanical method or
a liquid-pressure pipe expanding method and the plate-like fin 2
and the heat transfer pipe are bonded together. Subsequently, using
a plurality of return bend pipes 5 given bending work with
predetermined length and pitch, the return bend pipe 5 having a
braze ring on its outer face is attached to a pipe end of the
adjacent hairpin pipe 51 after pipe expansion, and the both pipes
are heated and brazed by a burner so as to manufacture a heat
exchanger 50.
[0043] Subsequently a flow of refrigerant of the prior-art fin-tube
heat exchanger 50 will be described, The refrigerant enters from an
inlet pipe 52, flows out from "a" on the front face side to "b" on
the back face side, flows in from "c" through the hairpin pipe 51
and flows out to "d" on the front face side, passes through the
return bend pipe 5 on the front face side, and flows into the
hairpin pipe 51 in the subsequent stage from "e". As mentioned
above, the refrigerant fluidizes downward through the heat transfer
pipe as
a.fwdarw.b.fwdarw.c.fwdarw.d.fwdarw.e.fwdarw.f.fwdarw.g.fwdarw. . .
. , and the refrigerant finally flows out of a flow-out pipe 53 on
the lower stage. During that period, heat exchange is performed
with air passing between the plate-like fins 2.
[0044] On the other hand, with regard to the heat exchanger 1 of
this embodiment, as shown in FIG. 12, explaining arrangement of the
heat transfer pipe 3 on the right side in the figure (a part of the
intermediate part of the arrangement of the right and left heat
transfer pipes is assumed to be shown), for example, a plurality of
hairpin pipes 30 are manufactured by applying bending work to the
transfer pipe 3 at the intermediate part with predetermined bending
pitch and then, the plurality of hairpin pipes 30 are inserted into
the plate-like fins 2 arranged in parallel with each other with a
predetermined interval from the back face side. Then, the heat
transfer pipe 3 is expanded by the mechanical method or liquid
pressure pipe expansion method as mentioned above, and the
plate-like fin and the heat transfer pipe 3 are bonded together.
Moreover, in the hairpin pipe 30, pipe ends of the heat transfer
pipe 3 on the second stage and the heat transfer pipe 3 on the
third stage are connected by two return bend pipes 5a, 5b made of a
metal material of aluminum or aluminum alloy and the like in a
cross state. That is, the first refrigerant flow passage 31a on the
upwind side of the heat transfer pipe 3 on the second stage and the
second refrigerant flow passage 31b on the downwind side of the
heat transfer pipe 3 on the third stage are connected by the return
bend pipe 5a, and the second refrigerant flow passage 31b on the
downwind side on the heat transfer pipes 3 on the second stage and
the first refrigerant flow passage 31a on the upwind side of the
heat transfer pipe 3 on the third stage are connected by the return
bend pipe 5b. The heat transfer pipe 3 on the third stage and on
the fourth stage, not shown, are constituted as hairpin pipes 30,
and the heat transfer pipes on the fourth stage and the fifth
stage, not shown, are connected by the return bend pipes similarly
to the above in a cross state. The heat exchanger 1 of this
embodiment has a plurality of refrigerant circuits constituted in
the column direction as above.
[0045] In the heat exchanger 1 of this embodiment, the refrigerant
separately flows into the first, second refrigerant flow passages
31a, 31b of the heat transfer pipe 3 on the first stage,
respectively, at the same time The refrigerant flowing into the
first refrigerant flow passage 31a of the heat transfer pipe 3 on
the first stage flows out of the first refrigerant flow passage 31a
of the heat transfer pipe 3 on the second stage through the hairpin
pipe 30 and flows into the second refrigerant flow passage 31b of
the heat transfer pipe 3 on the third stage further through the
return bend pipe 5a. On the other hand, the refrigerant flowing
into the second refrigerant flow passage 31b of the heat transfer
pipe 3 on the first stage flows out of the second refrigerant flow
passage 31b of the heat transfer pipe 3 on the second stage through
the hairpin pipe 30 and flows into the first refrigerant flow
passage 31a of the heat transfer pipe 3 on the third stage further
through the return bend pipe 5b.
[0046] Therefore, according to the heat exchanger 1 of this
embodiment, since the refrigerant fluidizes alternately in a cross
state by the return bend pipes 5a, 5b, the heat exchange capacity
on the upwind side and the heat exchange capacity on the downwind
side can be well-balanced, and a heat exchanger with high
efficiency can be obtained.
Sixth Embodiment
[0047] FIG. 13 is a front view illustrating an outline of a heat
exchanger according to a sixth embodiment. This embodiment is
different from the fifth embodiment only in that the pipe ends of
the heat transfer pipes 3 on the second stage and the third stage
in the adjacent hairpin pipes 30 are connected by a return bend
pipe 5c having a single flow passage so that the refrigerants are
mixed.
[0048] As a result, a mass ratio of a gas phase and a liquid phase
becomes the same at outlet sides of the plurality of refrigerant
circuits of the heat transfer pipe and it enters the refrigerant
inlet portion of the heat transfer pipe on the subsequent stage,
the heat exchange capacity on the upwind side and the heat exchange
capacity on the downwind side can be well-balanced, and a heat
exchanger with high efficiency can be obtained.
[0049] Also, the heat exchanger 1 constituted by using the
flat-shaped heat transfer pipe 3 of each of the above embodiments
can be used, in a refrigerating cycle circuit constituted by
sequentially connecting compressor, condenser, throttle device,
evaporator by piping, as the condenser or evaporator using a HC
single refrigerant of a mixed refrigerant containing HC or a
refrigerant of any of R32, R410A, R407C, carbon dioxide and the
like as an operating fluid.
REFERENCE NUMERALS
[0050] 1 heat exchanger [0051] 2 plate-like fin [0052] 3 heat
transfer pipe [0053] 4 slit [0054] 5, 5a, 5b, 5c return bend pipe
[0055] 21 fin collar portion [0056] 22 mounting hole [0057] 30
hairpin pipe [0058] 31a first refrigerant flow passage [0059] 31b
second refrigerant flow passage [0060] 32 bulkhead [0061] 33, 34
protruding strip [0062] 100 pipe-expanding burette ball
* * * * *