U.S. patent application number 13/317740 was filed with the patent office on 2012-05-03 for heat exchanger and fin for the same.
This patent application is currently assigned to SAMSUNG ELECTRONICS CO., LTD.. Invention is credited to Hayase Gaku, Young Min Kim, Kang Tae Seo.
Application Number | 20120103583 13/317740 |
Document ID | / |
Family ID | 45001646 |
Filed Date | 2012-05-03 |
United States Patent
Application |
20120103583 |
Kind Code |
A1 |
Kim; Young Min ; et
al. |
May 3, 2012 |
Heat exchanger and fin for the same
Abstract
A heat exchanger having a structure in which micro-channel tubes
are respectively fitted into both sides of corresponding flat fins
for heat exchange, thereby achieving enhancements in drainage and
heat transfer performance. The heat exchanger includes a first
header connected with an inflow tube and an outflow tube, a second
header spaced apart from the first header by a desired distance and
arranged parallel to the first header, a plurality of flat
micro-channel tubes arranged in a front row and a rear row between
the first header and the second header, and a plurality of plate
type fins. Each of the micro-channel tubes includes micro-channels.
Each of the fins includes slots arranged in a front row and a rear
row to respectively fit the front row and rear row micro-channel
tubes into the slots.
Inventors: |
Kim; Young Min; (Suwon-si,
KR) ; Gaku; Hayase; (Seongnam-si, KR) ; Seo;
Kang Tae; (Suwon-si, KR) |
Assignee: |
SAMSUNG ELECTRONICS CO.,
LTD.
Suwon-si
KR
|
Family ID: |
45001646 |
Appl. No.: |
13/317740 |
Filed: |
October 27, 2011 |
Current U.S.
Class: |
165/173 ;
165/181 |
Current CPC
Class: |
F28D 1/05391 20130101;
F28F 1/325 20130101; F28F 2215/12 20130101 |
Class at
Publication: |
165/173 ;
165/181 |
International
Class: |
F28F 9/02 20060101
F28F009/02; F28F 1/10 20060101 F28F001/10 |
Foreign Application Data
Date |
Code |
Application Number |
Oct 28, 2010 |
KR |
10-2010-0106368 |
Claims
1. A heat exchanger comprising: a first header connected with an
inflow tube and an outflow tube; a second header spaced apart from
the first header by a defined distance and arranged parallel to the
first header; a plurality of micro-channel tubes arranged in a
front row and a rear row between the first header and the second
header, each of the micro-channel tubes comprising a plurality of
micro-channels; and a plurality of plate type fins, each of the
plate type fins comprising slots arranged in a front row and a rear
row to respectively receive the front row and rear row of the
micro-channel tubes.
2. The heat exchanger according to claim 1, wherein each of the
plate type fins comprises louvers or slits formed between
vertically adjacent ones of the slots.
3. The heat exchanger according to claim 2, wherein the louvers
have a pitch LP satisfying a range of about 0.8
mm.ltoreq.Lp.ltoreq.1.2 mm.
4. The heat exchanger according to claim 2, wherein a clearance D1
between each slot and each louver or slit adjacent to each other
satisfies a range of about 0 mm<D1.ltoreq.1 mm.
5. The heat exchanger according to claim 2, wherein a clearance D2
between the front row and rear row slots satisfies a range of about
D2.gtoreq.2 mm.
6. The heat exchanger according to claim 2, wherein a ratio R
between an air-side heat transfer area A and a refrigerant-side
heat transfer area C defined by equations below satisfies a range
of about 2.5 mm.ltoreq.R.ltoreq.3.5 mm: A=((Lf.times.Wf)-(sum of
slot areas per fin)).times.2.times.total number of fins,
C=(Wc+Hc).times.2.times.Lt.times.(total number of micro-channels
per micro-channel tube).times.(total number of micro-channel
tubes), and R=A/C, where Lf represents an overall height of each
fin, Wf represents a width of each fin, We represents a width of
each micro-channel, Hc represents a height of each micro-channel,
and Lt represents a length of each micro-channel tube.
7. The heat exchanger according to claim 1, wherein welding
material, provided at inner sides of the slots arranged in each of
the first row and rear row in each fin, is used to permanently
attach the micro-channel tubes to the corresponding slots.
8. The heat exchanger according to claim 1, wherein openings
arranged in the form of a lattice between vertically adjacent ones
of the slots are formed at each of the fins.
9. The heat exchanger according to claim 8, wherein each of the
openings has a square shape.
10. The heat exchanger according to claim 1, wherein the first and
second headers extend vertically.
11. A fin assembly for a heat exchanger comprising: a plurality of
plate type fins into which micro-channel tubes are received,
wherein each of the plate type fins comprises slots arranged in a
front row and a rear row to receive the micro-channel tubes,
respectively, and louvers or slits formed between vertically
adjacent ones of the slots.
12. The fin assembly according to claim 11, wherein the louvers
have a pitch LP satisfying a range of about 0.8
mm.ltoreq.Lp.ltoreq.1.2 mm.
13. The fin assembly according to claim 11, wherein a clearance D1
between each slot and each louver or slit adjacent to each other
satisfies a range of about 0 mm<D1.ltoreq.1 mm.
14. The fin assembly according to claim 11, wherein a clearance D2
between the front row and rear row slots satisfies a range of about
D2.gtoreq.2 mm.
15. A fin assembly for a heat exchanger comprising: a plurality of
plate type fins into which flat micro-channel tubes are received,
wherein each of the plate type fins comprises slots arranged in a
front row and a rear row to receive the micro-channel tubes,
respectively, and openings arranged in a lattice form between the
vertically adjacent ones of the slots.
16. The fin assembly according to claim 15, wherein each of the
openings has a square shape.
17. The fin assembly according to claim 15, further comprising
welding wires installed at inner sides of the slots arranged in
each of the front row and rear row in each fin so that the
micro-channel tubes, which are respectively fitted into the
corresponding slots, are welded to the slots by the welding wires.
Description
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] This application claims the benefit of Korean Patent
Application No. 10-2010-106368 filed on Oct. 28, 2010 in the Korean
Intellectual Property Office, the disclosure of which is
incorporated herein by reference.
BACKGROUND
[0002] 1. Field
[0003] Embodiments of the present disclosure relate to a heat
exchanger of an air conditioner having a structure capable of
achieving enhancements in drainage and heat transfer
performance.
[0004] 2. Description of the Related Art
[0005] Heat exchangers, which implement one part of the
refrigeration cycle, are used in equipment such as air conditioners
and refrigerators. Heat exchangers include a plurality of fins for
heat exchange arranged to be spaced apart from one another, and a
plurality of refrigerant tubes, which is installed to come into
contact with the plural fins for heat exchange, to guide
refrigerant. In such a heat exchanger, air flowing into the heat
exchanger from the outside undergoes heat exchange while passing
through the fins for heat exchange, so that cooling operation or
heating operation is achieved.
[0006] Heat exchangers are classified into fin & tube type and
parallel flow type heat exchangers in accordance with shapes of the
fin and tube and coupling relations therebetween.
[0007] Conventionally, the fin & tube type heat exchanger has a
structure in which press-worked fins are layered, and a plurality
of circular tubes is then fitted between adjacent ones of the
layered fins through a press-fit process. On the other hand, the
parallel flow type heat exchanger has a structure in which a fin
having a corrugated shape is joined between flat elliptical tubes
through a brazing process.
[0008] In general, the parallel flow type-heat exchanger is
superior in terms of heat exchange efficiency, as compared to the
fin & tube type heat exchanger. However, drainage of condensed
water from the parallel flow type heat exchanger may be
troublesome.
SUMMARY
[0009] Therefore, it is an aspect of the present disclosure to
provide a fin micro-channel heat exchanger (FMC) having a structure
capable of achieving enhancements in drainage and heat transfer
performance.
[0010] It is another aspect of the present disclosure to provide a
model capable of achieving an optimal design of FMC.
[0011] Additional aspects of the disclosure will be set forth in
part in the description which follows and, in part, will be
apparent from the description, or may be learned by practice of the
disclosure.
[0012] In accordance with one aspect of the present disclosure, a
heat exchanger includes a first header connected with an inflow
tube and an outflow tube, a second header spaced apart from the
first header by a desired distance and arranged parallel to the
first header, a plurality of flat micro-channel tubes arranged in a
front row and a rear row between the first header and the second
header, and a plurality of plate type fins, each of the
micro-channel tubes includes micro-channels, and each of the fins
includes slots arranged in a front row and a rear row to
respectively fit the front row and rear row micro-channel tubes
into the slots.
[0013] Louvers or slits may be formed between vertically adjacent
ones of the slots in each of the fins.
[0014] The louvers may have a pitch LP satisfying a range of about
0.8 mm.ltoreq.Lp.ltoreq.1.2 mm.
[0015] A clearance D1 between each slot and each louver or slit
adjacent to each other may satisfy a range of about 0
mm<D1.ltoreq.1 mm.
[0016] A clearance D2 between the front row and rear row slots may
satisfy a range of about D2.gtoreq.2 mm.
[0017] A ratio R between an air-side heat transfer area A and a
refrigerant-side heat transfer area C defined by equations below
may satisfy a range of about 2.5 mm.ltoreq.R.ltoreq.3.5 mm:
A=((Lf.times.Wf)-(sum of slot areas per fin)).times.2.times.total
number of fins,
C=(Wc+Hc).times.2.times.Lt.times.(total number of micro-channels
per micro-channel tube).times.(total number of micro-channel
tubes), and
R=A/C,
where "Lf" represents an overall height of each fin, "Wf"
represents a width of each fin, "Wc" represents a width of each
micro-channel, "Hc" represents a height of each micro-channel, and
"Lt" represents a length of each micro-channel tube.
[0018] Openings arranged in the form of a lattice between
vertically adjacent ones of the slots may be formed at each of the
fins.
[0019] Each of the openings may have a square shape.
[0020] The first and second headers may extend vertically.
[0021] In accordance with another aspect of the present disclosure,
a fin assembly for a heat exchanger including a plurality of plate
type fins into which flat micro-channel tubes are fitted, wherein
each of the fins may include slots arranged in a front row and a
rear row to receive the micro-channel tubes, respectively, and
louvers or slits formed between vertically adjacent ones of the
slots.
[0022] The louvers may have a pitch LP satisfying a range of about
0.8 mm.ltoreq.Lp.ltoreq.1.2 mm.
[0023] A clearance D1 between each slot and each louver or slit
adjacent to each other may satisfy a range of about 0
mm.ltoreq.D1/1 mm.
[0024] A clearance D2 between the front row and rear row slots may
satisfy a range of about D2.gtoreq.2 mm.
[0025] In accordance with another aspect of the present disclosure,
a fin assembly for a heat exchanger including a plurality of plate
type fins into which flat micro-channel tubes are fitted, wherein
each of the fins may include slots arranged in a front row and a
rear row to receive the micro-channel tubes, respectively, and
openings arranged in a lattice form between the vertically adjacent
ones of the slots.
[0026] Each of the openings may have a square shape.
BRIEF DESCRIPTION OF THE DRAWINGS
[0027] These and/or other aspects of the disclosure will become
apparent and more readily appreciated from the following
description of the embodiments, taken in conjunction with the
accompanying drawings of which:
[0028] FIG. 1 is a perspective view illustrating an external
appearance of a heat exchanger according to an exemplary embodiment
of the present disclosure;
[0029] FIG. 2 is a top view schematically illustrating a fin
structure of the heat exchanger according to an exemplary
embodiment of the present disclosure;
[0030] FIG. 3 is a sectional view taken along line I-I of FIG.
2;
[0031] FIG. 4 is a view schematically illustrating a fin structure
of the heat exchanger according to another exemplary embodiment of
the present disclosure;
[0032] FIG. 5 is a view schematically illustrating a fin structure
of the heat exchanger according to another exemplary embodiment of
the present disclosure;
[0033] FIG. 6 is a sectional view taken along line II-II of FIG.
5;
[0034] FIG. 7 is a view schematically illustrating a fin structure
of the heat exchanger according to another exemplary embodiment of
the present disclosure;
[0035] FIG. 8 is a view schematically illustrating a fin structure
of the heat exchanger according to another exemplary embodiment of
the present disclosure;
[0036] FIG. 9 is a sectional view taken along line III-III of FIG.
8;
[0037] FIG. 10 is a view schematically illustrating a fin structure
of the heat exchanger according to another exemplary embodiment of
the present disclosure;
[0038] FIG. 11 is a sectional view illustrating a cross section of
a micro-channel tube included in the heat exchanger according to an
exemplary embodiment of the present disclosure;
[0039] FIG. 12 is a graph illustrating variation in heat exchange
performance according to a ratio between an air-side heat transfer
area and a refrigerant-side heat transfer area;
[0040] FIGS. 13 and 14 are views explaining a method of joining the
tubes and fins for the heat exchanger according to an exemplary
embodiment of the present disclosure, respectively; and
[0041] FIG. 15 is a perspective view illustrating a fin structure
of the heat exchanger according to another exemplary embodiment of
the present disclosure.
DETAILED DESCRIPTION
[0042] Reference will now be made in detail to the embodiments of
the present disclosure, examples of which are illustrated in the
accompanying drawings, wherein like reference numerals refer to
like elements throughout.
[0043] Hereinafter, exemplary embodiments of the present disclosure
will be described with reference to the accompanying drawings.
[0044] FIG. 1 is a perspective view illustrating an external
appearance of a heat exchanger according to an exemplary embodiment
of the present disclosure.
[0045] Referring to FIG. 1, the heat exchanger 1 according to the
exemplary embodiment of the present disclosure includes a first
header 10, a second header 20, micro-channel tubes 30, and fins
40.
[0046] The first header 10 and the second header 20 extend
vertically while being spaced apart from each other by a desired
distance. Tube coupling portions (not shown) are formed at facing
walls of the first and second headers 10 and 20. Each tube coupling
portion is formed by cutting the corresponding header wall to a
size in accordance with a cross section of the corresponding
micro-channel tube 30 to couple the micro-channel tube 30 to the
tube coupling portion.
[0047] The first header 10 and the second header 20 include
respective front tanks 11 and 21 and respective rear tanks 12 and
22. The front tanks 11 and 21 and the rear tanks 12 and 22 are
partitioned by partition walls, respectively. Each of the front
tanks 11 and 21 and the rear tanks 12 and 22 may be further
vertically partitioned by baffles 13.
[0048] The micro-channel tubes 30 are installed between the first
and second headers 10 and 20, to guide refrigerant by communicating
the first header 10 with the second header 20.
[0049] Each of the micro-channel tubes 30 is a path through which
refrigerant passes. Refrigerant is compressed or expanded while
circulating in an air conditioner (not shown), so that cooling and
heating may be achieved.
[0050] The micro-channel tubes 30, which are vertically spaced
apart from one another by a desired clearance, are arranged in two
rows, namely, a front row and a rear row. That is, the
micro-channel tubes 30 include front row micro-channel tubes 31 and
rear row micro-channel tubes 32. Here, the front row and rear row
micro-channel tubes 31 and 32 are alternately arranged in a zigzag
formation. However, the front row and rear row micro-channel tubes
31 and 32 may be arranged to be horizontally aligned with each
other, as shown in FIG. 4.
[0051] Meanwhile, an inflow tube 14 into which refrigerant flows
and an outflow tube 15 from which heat-exchanged refrigerant while
passing through the micro-channel tubes 30 is discharged are
connected to the first header 10. The inflow and outflow tubes 14
and 15 may be respectively connected to lower and upper sides of
the first header 10, in order to prevent accumulation of
refrigerant droplets caused by gravity, even if refrigerant flowing
into the first header 10 has both a gas phase and a liquid
phase.
[0052] FIG. 2 is a top view schematically illustrating a fin
structure of the heat exchanger according to an exemplary
embodiment of the present disclosure. FIG. 3 is a sectional view
taken along line I-I of FIG. 2.
[0053] A structure of fins and tubes for the heat exchanger
according to the exemplary embodiments of the present disclosure
will be described with reference to FIGS. 2 and 3.
[0054] Referring to FIGS. 2 and 3, a fin body 43 in each fin 40 is
formed to have a plate shape with a certain width Wf and height Hf.
The fin body 43 may be a rectangular thin plate.
[0055] Each fin 40 is installed to come into contact with the
corresponding micro-channel tubes 30, and may be formed as widely
as possible so that the section thereof to radiate or absorb heat
becomes wider.
[0056] Heat of refrigerant flowing inside the micro-channel tubes
30 is transferred to air flowing around the fins 40 via the
micro-channel tubes 30 and fins 40, thereby easily radiating heat
to the outside.
[0057] On the contrary, even when heat of air flowing around the
fins 40 is transferred to refrigerant via the fins 40 and
micro-channel tubes 30, the heat is also radiated to the outside in
the same way as described above.
[0058] Meanwhile, front row slots 44 and rear row slots 45 are
formed at each of the fins 40 so that the front row and rear row
micro-channel tubes 31 and 32 are fitted into the front row slots
44 and the rear row slots 45, respectively. In each fin 40, collars
47 perpendicular to the fin body 43 are formed respectively at
peripheral areas of the front row and rear row slots 44 and 45 to
easily fit the front row and rear row micro-channel tubes 31 and 32
into the corresponding front row and rear row slots 44 and 45
respectively, thereby securing a desired joining force.
[0059] The fins 40 are arranged to be evenly spaced in parallel
with a flow direction of air. Thus, air may execute heat exchange
while naturally flowing along surfaces of the fins 40 without
greatly undergoing resistance caused by the fins 40.
[0060] When the front row and rear row micro-channel tubes 31 and
32 are arranged in a zigzag formation, the front row and rear row
slots 44 and 45 of each fin 40 are also arranged in a zigzag
formation. However, when the front row and rear row micro-channel
tubes 31 and 32 are arranged to be horizontally aligned with each
other, as shown in FIG. 4, the front row and rear row slots 44 and
45 of each fin 40 are also arranged to be horizontally aligned with
each other, of course.
[0061] In each fin 40, front row and rear row louvers 41 and 42 are
formed between the vertically adjacent slots 44 and between the
vertically adjacent slots 45 respectively, to enhance heat transfer
efficiency by increasing a contact area with air.
[0062] The louvers 41 are formed between the vertically adjacent
front row slots 44, and the louvers 42 are formed between the
vertically adjacent rear row slots 45.
[0063] In each fin 40, the front row louvers 41 and the rear row
louvers 42 are symmetrically arranged in a width direction of the
fin 40, and each of the front row louvers 41 and the rear row
louvers 42 is formed so that a portion of the fin body 43 is
slightly bent from a plane of the fin 40 in an upward or downward
direction to be inclined at a desired angle. Accordingly, air
flowing along the fins 40 is dispersed by the louvers 41 and 42,
and growth of a boundary layer is restrained, so that heat exchange
efficiency may be enhanced.
[0064] In each fin 40, the clearance D1 between each slot 44 or 45
and each louver 41 or 42 may be 1 mm or less, in order to prevent
an increase in air-side pressure loss and a deterioration in heat
transfer performance due to formation of water droplets at lower
ends of the micro-channel tubes 30. In accordance with such a
structure, condensed water may be smoothly drained to lower ends of
the fins 40 by capillary action.
[0065] In each fin 40, drainage performance may be enhanced when
the clearance D2 between the front row slots 44 into which the
front row micro-channel tubes 31 are respectively fitted and the
rear row slots 45 into which the rear row micro-channel tubes 32
are respectively fitted may be 2 mm or more.
[0066] Drainage performance may be enhanced when the pitch LP of
the louvers 41 and 42 satisfies a range of 0.8
mm.ltoreq.Lp.ltoreq.1.2 mm.
[0067] FIG. 5 is a view schematically illustrating a fin structure
of the heat exchanger according to another exemplary embodiment of
the present disclosure. FIG. 6 is a sectional view taken along line
II-II of FIG. 5. FIG. 7 is a view schematically illustrating a fin
structure of the heat exchanger according to another exemplary
embodiment of the present disclosure.
[0068] In each fin 40 for the heat exchanger, instead of the
louvers 41 and 42, slits 46a and 46b may be formed between
vertically adjacent slots 44 and between vertically adjacent slots
45, respectively. The slits 46a are formed between the vertically
adjacent front row slots 44, and the slits 46b are formed between
the vertically adjacent rear row slots 45. Air is changed into
turbulent air while flowing into openings of the slits 46a and 46b,
and the turbulent air circulates around the micro-channel tubes 30,
and thus heat exchange efficiency may be improved.
[0069] In the present embodiments, front row slots 44 and rear row
slots 45 of each fin 40 may be arranged in a zigzag formation or to
be horizontally aligned with each other.
[0070] FIG. 8 is a view schematically illustrating a fin structure
of the heat exchanger according to another exemplary embodiment of
the present disclosure. FIG. 9 is a sectional view taken along line
III-III of FIG. 8. FIG. 10 is a view schematically illustrating a
fin structure of the heat exchanger according to another exemplary
embodiment of the present disclosure.
[0071] As shown in FIGS. 8 to 10, louvers 41 and 42 and slits 46a
and 46b in each fin 40 may also be formed together, and front row
slots 44 and rear row slots 45 in each fin 40 may be arranged in a
zigzag formation or to be horizontally aligned with each other.
Since the remaining components are the same as those according to
another exemplary embodiment of the present disclosure, no
description will be given.
[0072] Meanwhile, as shown in FIG. 11, each of the micro-channel
tubes 30 has a flat shape, and a plurality of micro-channels 33 is
formed in the micro-channel tube 30 to guide refrigerant in the
micro-channel tube 30.
[0073] Although each of the micro-channel tubes 30 may have a
circular shape in a cross section, the micro-channel tube 30 may
have a flat shape to expand a heat transfer area.
[0074] FIG. 12 is a graph illustrating variation in heat exchange
performance according to a ratio between an air-side heat transfer
area and a refrigerant-side heat transfer area. In the graph, the
x-axis refers to the ratio R between the air-side heat transfer
area A and the refrigerant-side heat transfer area C, whereas the
y-axis refers to the quantity of heat per frontal area Q/FA, heat
transfer capacity per frontal area HA/FA, and pressure loss per
unit length dP/L (however, numerical values of the y-axis are
relative values).
[0075] In the heat exchanger including the fins 40 and
micro-channel tubes 30 having the structure as described above,
performance characteristics according to the ratio R between the
air-side heat transfer area A and the refrigerant-side heat
transfer area C may be varied.
[0076] The air-side heat transfer area A is defined by
A=((Lf.times.Wf)-(sum of slot areas per fin)).times.2.times. total
number of fins, where "Lf" represents the length (or height) of
each fin 40, and "Wf" represents the width of each fin 40. On the
other hand, the refrigerant-side heat transfer area C is defined by
C=(Wc+Hc).times.2.times.Lt.times.(total number of micro-channels
per micro-channel tube).times.(total number of micro-channel
tubes), where "Wc" represents the width of each micro-channel, "Hc"
represents the height of each micro-channel, and "Lt" represents
the length of each micro-channel tube. The ratio R is defined by
R=air-side heat transfer area A/refrigerant-side heat transfer area
C.
[0077] As shown in FIG. 12, pressure loss increases as the ratio R
between the air-side heat transfer area A and the refrigerant-side
heat transfer area C increases. Therefore, when the ratio R
satisfies a range of about 2.5.ltoreq.R.ltoreq.3.5, overall
performance characteristics may be optimized.
[0078] Conventionally, the ratio R between the air-side heat
transfer area A and the refrigerant-side heat transfer area C is
10.ltoreq.R.ltoreq.20 in the case of the fin & tube type heat
exchanger, whereas the ratio R is 3.ltoreq.R.ltoreq.4 in the case
of the parallel flow type heat exchanger.
[0079] Accordingly, the refrigerant-side heat transfer area C may
be increased, in order to obtain an optimal performance
characteristic.
[0080] FIGS. 13 and 14 are views explaining a method of joining the
tubes and fins for the heat exchanger according to an exemplary
embodiment of the present disclosure, respectively.
[0081] The joining of the micro-channel tubes 30 and fins 40 as
described above may be achieved by welding wires 50, in addition to
a brazing process conventionally used to join aluminum clad fins
and tubes.
[0082] When the welding wires 50 are respectively installed at
inner sides of the slots 44 and 45 in each fin 40 so that the front
row and rear row micro-channel tubes 31 and 32, which are
respectively fitted into the corresponding slots 44 and 45, are
welded to the slots 44 and 45 by the welding wires 50, as shown in
FIG. 13, the fin 40 and the front row and rear row micro-channel
tubes 31 and 32 may be welded and joined together while the melted
welding wires flow into the gaps between the micro-channel tubes
and the corresponding slots, as shown in FIG. 14. In accordance
with such a method, joining defects may be greatly resolved in
addition to easy welding.
[0083] FIG. 15 is a perspective view illustrating a fin structure
of the heat exchanger according to another exemplary embodiment of
the present disclosure.
[0084] In each plate type fin 140 for the heat exchanger into which
the flat micro-channel tubes are fitted, the fin 140 may include a
fin body 143, slots 145 alternatively arranged in a zigzag
formation to respectively fit the micro-channel tubes, and a
plurality of openings 148 arranged in a lattice form between the
vertically adjacent slots 145. Collars 147 may be formed
respectively around the slots 145 so as to easily attach the
micro-channel tubes to the slots 145 by fitting the micro-channel
tubes into the slots 145.
[0085] As shown in FIG. 15, air F flowing in a thickness direction
of the fins 140 may pass between a front surface and a rear surface
of each fin 140 through the openings 148 while flowing between the
fins 140. Further, since a plurality of fins 140 is layered, the
openings 148 arranged at corresponding positions between the
layered fins 140 may form a channel. Thus, a reduction in air-side
pressure loss and an enhancement in heat transfer performance may
be achieved.
[0086] As is apparent from the above description, in accordance
with aspects of the present disclosure, it may be possible to
provide a fin micro-channel heat exchanger having a structure
capable of achieving enhancements in drainage and heat transfer
performance.
[0087] Although a few embodiments of the present disclosure have
been shown and described, it would be appreciated by those skilled
in the art that changes may be made in these embodiments without
departing from the principles and spirit of the invention, the
scope of which is defined in the claims and their equivalents.
* * * * *