U.S. patent application number 13/317602 was filed with the patent office on 2012-05-03 for heat exchanger.
This patent application is currently assigned to SAMSUNG ELECTRONICS CO., LTD.. Invention is credited to Hayase Gaku, Young Min Kim, Dong Ho Park, Kang Tae Seo.
Application Number | 20120103587 13/317602 |
Document ID | / |
Family ID | 44785705 |
Filed Date | 2012-05-03 |
United States Patent
Application |
20120103587 |
Kind Code |
A1 |
Park; Dong Ho ; et
al. |
May 3, 2012 |
Heat exchanger
Abstract
A heat exchanger includes a refrigerant pipe in which a
refrigerant flows and a heat exchanger fin coupled to the outer
circumference of the refrigerant pipe. The heat exchanger fin
includes a plate, a protrusion protruding from the plate, slits
disposed at opposite sides of the protrusion to guide air to the
protrusion, and a louver unit provided at the protrusion to perform
heat exchange with the air having passed through the slits.
Inventors: |
Park; Dong Ho; (Suwon-si,
KR) ; Gaku; Hayase; (Seongnam-si, KR) ; Seo;
Kang Tae; (Suwon-si, KR) ; Kim; Young Min;
(Suwon-si, KR) |
Assignee: |
SAMSUNG ELECTRONICS CO.,
LTD.
Suwon-si
KR
|
Family ID: |
44785705 |
Appl. No.: |
13/317602 |
Filed: |
October 24, 2011 |
Current U.S.
Class: |
165/181 |
Current CPC
Class: |
F25B 39/02 20130101;
F28F 2215/04 20130101; F28F 2215/08 20130101; F24F 1/18 20130101;
F28F 1/325 20130101; F28D 1/0477 20130101 |
Class at
Publication: |
165/181 |
International
Class: |
F28F 1/12 20060101
F28F001/12 |
Foreign Application Data
Date |
Code |
Application Number |
Oct 28, 2010 |
KR |
10-2010-0106371 |
Claims
1. A heat exchanger comprising: a refrigerant pipe in which a
refrigerant flows; and a heat exchanger fin coupled to an outer
circumference of the refrigerant pipe, wherein the heat exchanger
fin comprises a plate; a protrusion protruding from the plate;
slits disposed at opposite sides of the protrusion to guide air to
the protrusion; and a louver unit provided at the protrusion to
perform heat exchange with the air having passed through the
slits.
2. The heat exchanger according to claim 1, wherein the louver unit
comprises: first cutouts provided at the protrusion; and a
plurality of guide plates provided in parallel to each other so
that the guide plates are spaced apart from each other by the
respective first cutouts, the first cutouts and the guide plates
being alternately arranged.
3. The heat exchanger according to claim 2, wherein each of the
guide plates has a width of 0.5 mm to 3 mm.
4. The heat exchanger according to claim 2, wherein the protrusion
comprises first inclined surfaces inclined relative to the plate,
the guide plates are provided at the first inclined surfaces, and
an angle between the guide plates and the first inclined surfaces
is 10 to 60 degrees.
5. The heat exchanger according to claim 1, wherein each of the
slits comprises: second inclined surfaces inclined relative to the
plate; a top surface formed between the second inclined surfaces;
and a second cutout provided at a rear of the top surface.
6. The heat exchanger according to claim 5, wherein the top surface
has a width of 0.5 mm to 5 mm.
7. The heat exchanger according to claim 4, wherein the first
inclined surfaces are disposed at the plate symmetrically, a
distance between a line formed at a position where the first
inclined surfaces join each other and the plate constitutes a
height of the protrusion, and the protrusion has a height of 0.5 mm
to 4 mm.
8. The heat exchanger according to claim 4, wherein the first
inclined surfaces are disposed at the plate in a symmetrical
fashion, a distance between a flat surface connected between the
first inclined surfaces and the plate constitutes a height of the
protrusion, and the protrusion has a height of 0.5 mm to 4 mm.
9. The heat exchanger according to claim 1, wherein the heat
exchanger fin comprises a plurality of plates stacked at an
interval.
10. A heat exchanger comprising a tube to guide a fluid and a heat
exchanger fin contacting the tube to perform heat exchange between
the fluid and external air, wherein the heat exchanger fin
comprises: location holes in which the tube is located in a
supported state; a protrusion provided between the location holes,
the protrusion protruding in an extension direction of the tube; a
slit disposed at a periphery of the protrusion to accelerate air
introduced to the protrusion; and a louver unit formed at the
protrusion to perform heat exchange between the air having passed
through the slit and the fluid.
11. The heat exchanger according to claim 10, wherein the louver
unit comprises: a plurality of guide plates provided in parallel to
each other so that the guide plates are spaced apart from each
other; and a plurality of first cutouts alternating with the guide
plates.
12. The heat exchanger according to claim 11, wherein the
protrusion comprises first inclined surfaces disposed symmetrically
to form a `V` shape, and the guide plates and the first cutouts are
provided at the first inclined surfaces.
13. The heat exchanger according to claim 12, wherein an angle
between the first inclined surfaces and the guide plates provided
at the first inclined surfaces is 10 to 60 degrees.
14. The heat exchanger according to claim 13, wherein each of the
guide plates has a width of 0.5 mm to 3 mm.
15. The heat exchanger according to claim 14, wherein the slit
comprises: second inclined surfaces protruding in an extension
direction of the tube; a top surface formed between the second
inclined surfaces; and a second cutout provided at a rear of the
top surface.
16. The heat exchanger according to claim 15, wherein the top
surface has a width of 0.5 mm to 5 mm.
17. The heat exchanger according to claim 11, wherein the
protrusion comprises: first inclined surfaces disposed
symmetrically; and a flat surface connected between the first
inclined surfaces, the guide plates and the first cutouts being
provided at the first inclined surfaces or the flat surface.
18. The heat exchanger according to claim 10, wherein the louver
unit comprises a plurality of guide plates spaced apart from each
other and a plurality of first cutouts alternating with the guide
plates, the protrusion comprises first inclined surfaces disposed
to form a `V` shape, and the guide plates and the first cutouts are
provided at the first inclined surfaces.
19. The heat exchanger according to claim 18, wherein the guide
plates are provided at the first inclined surfaces at varying
inclination angles relative to the first inclined surfaces.
20. The heat exchanger according to claim 18, wherein the inclined
surfaces are disposed to form a non-symmetrical `V` shape.
Description
CROSS-REFERENCE TO RELATED APPLICATIONS
[0001] This application claims the benefit of Korean Patent
Application No. 10-2010-0106371, 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 with an improved heat exchange structure.
[0004] 2. Description of the Related Art
[0005] A heat exchanger is mounted in devices operating based upon
a refrigeration cycle, such as air conditioners or refrigerators.
The heat exchanger includes a plurality of heat exchanger fins and
a refrigerant pipe extending through the heat exchanger fins to
guide a refrigerant. Contact area between the heat exchanger fins
and external air introduced to the heat exchanger is increased to
improve heat exchange efficiency between the refrigerant flowing in
the refrigerant pipe and the external air.
[0006] When the contact area between the heat exchanger fins and
external air contacting the heat exchanger fins is large or when
resistance applied to air contacting the heat exchanger fins is
small, heat exchange efficiency is increased. However, if the
contact area between the heat exchanger fins and air is too large,
large resistance is applied to air passing through the heat
exchanger fins. On the other hand, if the contact area is reduced
to lower resistance applied to air, heat exchange efficiency is
lowered. For this reason, it may be necessary to provide fins
having an optimal shape based on the heat exchanger employed.
[0007] For a heat exchanger used as an evaporator (that is, the
refrigeration cycle performs a heating operation), if outdoor
temperature is too low, the surface temperature of the heat
exchanger is lowered to below zero Celsius, and moisture contained
in outdoor air is attached to the surface of the cold heat
exchanger in a frozen state, thereby reducing heat exchange
efficiency of the heat exchanger.
SUMMARY
[0008] It is an aspect of the present disclosure to provide a heat
exchanger having a structure to effectively achieve heat exchange
between air and heat exchanger fins.
[0009] It is another aspect of the present disclosure to provide a
heat exchanger having a structure to restrain frost formation on
the surfaces of heat exchanger fins.
[0010] 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.
[0011] In accordance with one aspect of the present disclosure, a
heat exchanger includes a refrigerant pipe in which a refrigerant
flows and a heat exchanger fin coupled to the outer circumference
of the refrigerant pipe, wherein the heat exchanger fin includes a
plate, a protrusion protruding from the plate, slits disposed at
opposite sides of the protrusion to guide air to the protrusion,
and a louver unit provided at the protrusion to perform heat
exchange with the air having passed through the slits.
[0012] The louver unit may include first cutouts provided at the
protrusion and a plurality of guide plates provided in parallel to
each other so that the guide plates are spaced apart from each
other by the respective first cutouts, the first cutouts and the
guide plates being alternately arranged.
[0013] Each of the guide plates may have a width of 0.5 mm to 3
mm.
[0014] The protrusion may include first inclined surfaces inclined
relative to the plate, the guide plates may be provided at the
first inclined surfaces, and the angle between the guide plates and
the first inclined surfaces may be 10 to 60 degrees.
[0015] Each of the slits includes second inclined surfaces inclined
relative to the plate, a top surface formed between the second
inclined surfaces, and a second cutout provided at the rear of the
top surface.
[0016] The top surface may have a width of 0.5 mm to 5 mm.
[0017] The first inclined surfaces may be disposed at the plate in
a symmetrical fashion, the distance between a line formed at the
position where the first inclined surfaces join each other and the
plate may constitute a height of the protrusion, and the protrusion
may have a height of 0.5 mm to 4 mm.
[0018] The first inclined surfaces may be disposed at the plate in
a symmetrical fashion, the distance between a flat surface
connected between the first inclined surfaces and the plate may
constitute a height of the protrusion, and the protrusion may have
a height of 0.5 mm to 4 mm.
[0019] The heat exchanger fin may include a plurality of plates
stacked at an interval.
[0020] In accordance with another aspect of the present disclosure,
a heat exchanger includes a tube to guide a fluid and a heat
exchanger fin contacting the tub to perform heat exchange between
the fluid and external air, wherein the heat exchanger fin includes
location holes in which the tube is located in a supported state, a
protrusion provided between the location holes, the protrusion
protruding in the extension direction of the tube, a slit disposed
at the periphery of the protrusion to accelerate air introduced to
the protrusion, and a louver unit formed at the protrusion to
perform heat exchange between the air having passed through the
slit and the fluid.
[0021] The louver unit may include a plurality of guide plates
provided in parallel to each other so that the guide plates are
spaced apart from each other and a plurality of first cutouts
alternating with the guide plates.
[0022] The protrusion may include first inclined surfaces disposed
in a symmetrical fashion to form a `V` shape, and the guide plates
and the first cutouts may be provided at the first inclined
surfaces.
[0023] The angle between the first inclined surfaces and the guide
plates provided at the first inclined surfaces may be 10 to 60
degrees.
[0024] Each of the guide plates may have a width of 0.5 mm to 3
mm.
[0025] The slit may include second inclined surfaces protruding in
the extension direction of the tube, a top surface formed between
the second inclined surfaces, and a second cutout provided at the
rear of the top surface.
[0026] The top surface may have a width of 0.5 mm to 5 mm.
[0027] The protrusion may include first inclined surfaces disposed
in a symmetrical fashion and a flat surface connected between the
first inclined surfaces, the guide plates and the first cutouts
being provided at the first inclined surfaces or the flat
surface.
BRIEF DESCRIPTION OF THE DRAWINGS
[0028] 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:
[0029] FIG. 1 is a perspective view illustrating a heat exchanger
according to an embodiment of the present disclosure;
[0030] FIG. 2 is a perspective view illustrating part of a heat
exchanger fin of FIG. 1;
[0031] FIG. 3 is a front view of FIG. 2;
[0032] FIG. 4 is a sectional view taken along line I-I of FIG.
3;
[0033] FIG. 5 is an enlarged sectional view illustrating part of
FIG. 4;
[0034] FIG. 6 is a view illustrating air flow around the heat
exchanger fin of FIG. 3;
[0035] FIG. 7 is a sectional view taken along line II-II of FIG.
6;
[0036] FIG. 8 is a table illustrating heat exchange efficiency of
the heat exchanger fin of FIG. 3;
[0037] FIG. 9 is a front view illustrating a conventional fin;
[0038] FIG. 10 is a sectional view taken along line A-A of FIG.
9;
[0039] FIG. 11 is a front view illustrating a heat exchanger
according to another embodiment of the present disclosure;
[0040] FIG. 12 is a front view illustrating a heat exchanger
according to another embodiment of the present disclosure;
[0041] FIG. 13 is a sectional view taken along line III-III of FIG.
12;
[0042] FIG. 14 is a front view illustrating a heat exchanger
according to another embodiment of the present disclosure;
[0043] FIG. 15 is a sectional view taken along line IV-IV of FIG.
14;
[0044] FIG. 16 is a front view illustrating a heat exchanger
according to another embodiment of the present disclosure;
[0045] FIG. 17 is a sectional view taken along line V-V of FIG.
16;
[0046] FIG. 18 is a front view illustrating a heat exchanger
according to yet another embodiment of the present disclosure;
and
[0047] FIG. 19 is a sectional view taken along line VI-VI of FIG.
18.
DETAILED DESCRIPTION
[0048] 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.
[0049] FIG. 1 is a perspective view illustrating a heat exchanger
according to an embodiment of the present disclosure.
[0050] As shown in FIG. 1, a heat exchanger 10 includes a
refrigerant pipe 20, in which a refrigerant flows, and heat
exchanger fins 30 coupled to the outer circumference of the
refrigerant pipe 20.
[0051] The refrigerant pipe 20 is configured in the shape of a
hollow tube in which the refrigerant flows. The refrigerant pipe 20
is lengthened to increase heat exchange area between the
refrigerant flowing in the refrigerant pipe 20 and external air.
However, it may be difficult to extend the refrigerant pipe 20 in
one direction due to spatial restrictions. Consequently, the
refrigerant pipe 20 is repeatedly bent at opposite ends of the heat
exchanger 10 in opposite directions to efficiently increase heat
exchange area per unit volume.
[0052] The refrigerant flowing in the refrigerant pipe 20 is formed
by mixing different Freon products exhibiting different properties.
For example, R-134a and R410A may be used.
[0053] The refrigerant may be phase changed (compressed) from a gas
state to a liquid state to perform heat exchange with external air.
On the other hand, the refrigerant may be phase changed (expanded)
from a liquid state to a gas state to perform heat exchange with
external air. When the refrigerant is phase changed from a gas
state to a liquid state, the heat exchanger 10 is used as a
condenser. When the refrigerant is phase changed from a liquid
state to a gas state, the heat exchanger 10 is used as an
evaporator.
[0054] The refrigerant, flowing in the refrigerant pipe 20, is
compressed or expanded to discharge heat to the surroundings or to
absorb heat from the surroundings. The heat exchanger fins 30 are
coupled to the refrigerant pipe 20 so that the refrigerant
efficiently discharges or absorbs heat during compression or
expansion.
[0055] The heat exchanger fins 30 are disposed at a predetermined
interval in the direction in which the refrigerant pipe 20
extends.
[0056] The heat exchanger fins 30 may be made of various metal
materials, such as aluminum, exhibiting high thermal conductivity.
The heat exchanger fins 30 are coupled to the outer circumference
of the refrigerant pipe 20 in a contact state to increase contact
area between the refrigerant pipe 20 and external air.
[0057] The interval between the heat exchanger fins 30 may be
reduced to increase the number of the heat exchanger fins 30. If
the interval between the heat exchanger fins 30 is too small,
however, the heat exchanger fins 30 may act as resistance to air F
introduced to the heat exchanger 10, as shown in FIG. 1, resulting
in pressure loss. For this reason, the interval between the heat
exchanger fins 30 may be properly adjusted.
[0058] FIG. 2 is a perspective view illustrating part of one of the
heat exchanger fins of FIG. 1, FIG. 3 is a front view of FIG. 2,
FIG. 4 is a sectional view taken along line I-I of FIG. 3, and FIG.
5 is an enlarged sectional view illustrating part of FIG. 4.
[0059] As shown in FIGS. 2 to 5, the heat exchanger fin 30 includes
a plate 40, a protrusion 70 protruding from the plate 40, slits 50
provided at opposite sides of the protrusion 70, and a louver unit
60 provided at the protrusion 70.
[0060] The plate 40 is made of an aluminum alloy. The plate 40 is
thin. The plate 40 includes location holes 32, through which the
refrigerant pipe 20 extends in a contact state.
[0061] Each of the location holes 32 contacts the outer
circumference of the refrigerant pipe 20 to support the refrigerant
pipe 20. Each of the location holes 32 is formed in a shape
corresponding to the outer circumference of the refrigerant pipe 20
to surround the refrigerant pipe 20.
[0062] As shown in FIG. 2, each of the location holes 32 protrudes
frontward and rearward from the plate 40 to stably support the
refrigerant pipe 20 and to increase contact area between the
refrigerant pipe 20 and the heat exchanger fin 30 so that heat
exchange is smoothly achieved.
[0063] The protrusion 70 protrudes frontward from the plate 40.
[0064] The protrusion 70 includes first inclined surfaces 72
disposed at a predetermined angle relative to the plate 40. The
first inclined surfaces 72 are disposed on the plate 40 in a
symmetrical fashion to form a `V` shape.
[0065] The first inclined surfaces 72 guide air, passing through
the slits 50, to the louver unit 60. That is, air, accelerated
while passing through the slits 50, naturally flows along the first
inclined surfaces 72 so that speed of the air is not reduced. The
air flowing along the first inclined surfaces 72 contacts the
louver unit 60 to perform heat exchange with the refrigerant
flowing in the refrigerant pipe 20, thereby increasing heat
transfer efficiency.
[0066] As previously described, the first inclined surfaces 72 are
disposed on the plate 40 in a symmetrical fashion to form a `V`
shape. A contact line 74 is formed vertically at a position where
the first inclined surfaces 72 join each other. The distance
between the contact line 74 and the plate 40 constitutes a height H
of the protrusion 70.
[0067] If the height H of the protrusion 70 is increased, the area
of the first inclined surfaces 72 increases, thereby increasing the
contact area between the first inclined surfaces 72 and external
air. If the height H of the protrusion 70 is excessively increased,
however, the first inclined surfaces 72 act as resistance to
external air. As a result, the speed of air is reduced and pressure
of the air is reduced (pressure loss), thereby reducing heat
transfer efficiency. The height H of the protrusion 70 is 0.5 mm to
4.0 mm.
[0068] Meanwhile, the first inclined surfaces 72 may be disposed on
the plate in a non-symmetrical fashion, which will be described in
detail below in connection with a heat exchanger fin 300 according
to another embodiment of the present disclosure.
[0069] The slits 50 are disposed at opposite sides of the
protrusion 70.
[0070] The slits 50 prevent moisture contained in external air from
being attached to the surface of the heat exchanger fin 30. Also,
the slits accelerate external air introduced to the heat exchanger
10 and guide the external air to the protrusion 70 and the louver
unit 60. Each of the slits 50 includes second inclined surfaces 52
inclined relative to the plate 40, a top surface 54 provided
between the second inclined surfaces 52, and a second cutout 56
provided at the rear of the top surface 54.
[0071] The second inclined surfaces 52 protrude from the plate 40
so that the second inclined surfaces 52 are disposed at a
predetermined angle relative to the plate 40 to define a space, in
which external air flows, between the plate 40 and the top surface
54.
[0072] The top surface 54 is formed in an approximately trapezoidal
shape. The top surface 54 is disposed between the second inclined
surfaces 52. Air, passing through each of the slits 50, is divided
by the top surface 54 and flows along the front and rear of the top
surface 54, resulting in turbulent flow. As a result, the air is
further accelerated.
[0073] The top surface 54 may be formed in other shapes. For
example, the top surface 54 may be formed in the shape of a
triangle, a semicircle, an arc or a quadrangle. Even if the top
surface 54 is formed in any one of the above-specified shapes, the
same effect in that air, passing through each of the slits 50, is
divided by the top surface 54 is achieved.
[0074] An edge 58 is formed between top surface 54 and each of the
second inclined surfaces 52. The edge 58 prevents frost formation.
Frost formation is a phenomenon in which moisture contained in
external air is attached to the surface of the heat exchanger fin
30 in a frozen state. Frost is formed at a flat surface on which
more than a predetermined amount of moisture is easily collected.
More than a predetermined amount of moisture is prevented from
being collected by the provision of the edge 58, thereby preventing
or retarding frost formation.
[0075] The second cutout 56 is provided at the rear of the top
surface 54 to guide external air, introduced to the heat exchanger
10, to the louver unit 60 and to minimize resistance applied to the
air flowing along the top surface 54.
[0076] When the heat exchanger 10 is used as an evaporator to heat
a room, the refrigerant, flowing in the refrigerant pipe 20, is
expanded from a liquid state to a gas state to absorb heat from the
surroundings. As a result, the surface temperature of the
refrigerant pipe 20 is generally lowered to below zero degrees
Celsius. The second cutout 56 retards heat exchange between the
refrigerant pipe 20 and the corresponding slit 50, thereby
preventing frost formation.
[0077] The width D of the top surface 54 may be 0.5 to 5.0 mm in
consideration of resistance applied to air passing through the
corresponding slit 50.
[0078] The slits 50 are disposed at opposite sides of the
protrusion 70. At least two slits 50 may be disposed in the
vertical direction of the plate 40 so that the slits 50 are spaced
apart from each other.
[0079] When the slits are disposed in the vertical direction of the
plate 40 so that the slits 50 are spaced apart from each other, the
strength of the slits 50 and the plate 40 is higher than when the
slits are disposed without separation.
[0080] The louver unit 60 is provided at the protrusion 70.
[0081] The louver unit 60 includes guide plates 62 provided at the
first inclined surfaces 72 and first cutout 64 alternating with the
guide plates 62.
[0082] The guide plates 62 are disposed at a predetermined angle
relative to the first inclined surfaces 72. The guide plates 62 are
arranged in parallel to each other so that the guide plates 62 are
spaced apart from each other.
[0083] External air, accelerated after having passed through the
slits 50, flows along the first inclined surfaces 72 and contacts
the guide plates 62 to perform heat exchange with the guide plates
62. The guide plates 62 increase contact area between the heat
exchanger fin 30 and external air to increase heat exchange
efficiency.
[0084] When the pitch (width) P of each of the guide plates 62 is
small or when the inclination angle a between each of the guide
plates 62 and the first inclined angle 72 is small, contact area
between the heat exchanger fin 30 and external air increases. If
the pitch P is too small or the inclination angle a is too large,
however, speed of air passing through the louver unit 60 is reduced
by the guide plates 62, resulting in pressure loss. As a result,
overall heat exchange efficiency is lowered. Consequently, the
pitch P and the inclination angle a are properly adjusted. For
example, the pitch P may be 0.5 mm to 3.0 mm and the inclination
angle a may be 10 degrees to 60 degrees.
[0085] Also, the edge of each of the guide plates 62 prevents or
retards frost formation, as previously described.
[0086] The first cutouts 64 are provided at the first inclined
surfaces 72 so that the first cutouts 64 and the guide plates 62
are alternately disposed. The first cutouts 64 guide external air,
accelerated after having passed through the slits 50, to flow along
one side of each of the guide plates 62, thereby effectively
achieving heat transfer between the guide plates 62 and external
air.
[0087] FIG. 6 is a view illustrating air flow around the heat
exchanger fin of FIG. 3, and FIG. 7 is a sectional view taken along
line II-II of FIG. 6.
[0088] FIGS. 6 and 7 illustrate calculation results of air flow
around the heat exchanger fin 30 using computational fluid dynamics
(CFD). In the drawings, lines indicate air flow direction, and
lengths of the lines indicate air speed. Longer lengths of the
lines represent higher air speed.
[0089] As shown in FIGS. 6 and 7, air passing through the slits 50
of the heat exchanger fin 30 moves faster than air not passing
through the slits 50 since the air introduced into the slits 50 is
accelerated by the top surface 54 of each of the slits 50.
[0090] The air, accelerated by the slits 50, flows to the louver
unit 60 without reduction of air speed. As previously described,
the slits 50 accelerate air introduced into the slits 50 and guide
the introduced air to the louver unit 60.
[0091] The air flows on the surfaces of the guide plates 62 and
between the guide plates 62, i.e. at the first cutouts 64, at high
speed to perform heat exchange with the guide plates 62.
[0092] FIG. 8 is a table illustrating heat exchange efficiency of
the heat exchanger fin of FIG. 3. FIGS. 9 and 10 are a front view
and a sectional view illustrating a conventional fin compared with
the heat exchange efficiency of the heat exchanger fin of FIG.
3.
[0093] As shown in FIGS. 9 and 10, a conventional fin 1 is provided
at the middle thereof with silts 5 but does not include a
protrusion 70 and a louver unit 60, which are included in the heat
exchanger fin 30 of FIG. 3.
[0094] In the table of FIG. 8, wind speed indicates speed of
external air introduced to the fin, and fin pitch indicates the
distance between the respective fins. Smaller pitch means that a
larger number of fins may be disposed in a limited space.
[0095] As the result of a comparison of heat transfer efficiency
between the conventional fins and the inventive fins having the
same pitch (1.5 mm), the inventive fins have approximately 7.4% to
8.2% higher heat transfer efficiency in all wind speed sections
than the conventional fins.
[0096] Also, even when the pitch of the inventive fins is increased
from 1.5 mm to 1.7 mm, the inventive fins have higher heat transfer
efficiency than the conventional fins having a pitch of 1.5 mm.
This means that higher heat transfer efficiency is achieved using a
smaller number of inventive fins, thereby reducing material
costs.
[0097] FIGS. 11 to 19 are front views and sectional views
illustrating heat exchanger fins 200, 300, 400, 500 and 600
according to other embodiments of the present disclosure.
[0098] FIG. 11 illustrates a heat exchanger fin 200 according to
another embodiment of the present disclosure. A slit 250,
protruding frontward from the heat exchanger fin 200, is formed as
a single body.
[0099] FIGS. 12 and 13 illustrate a heat exchanger fin 300
according to another embodiment of the present disclosure. A
protrusion 370 of the heat exchanger fin 300 is formed in a
non-symmetrical shape. That is, first inclined surfaces 372a and
372b constituting the protrusion 370 are formed in a
non-symmetrical `V` shape.
[0100] An inclination angle .beta. between the first inclined
surface 372a and the front of a plate 40 is larger than an
inclination angle .beta.' between the first inclined surface 372b
and the front of the plate 40. Consequently, the area of the first
inclined surface 372a is smaller than that of the first inclined
surface 372b. Also, a contact line 374 at which the first inclined
surfaces 372a and 372b join each other deviates from the middle of
the plate 40.
[0101] FIGS. 14 and 15 illustrate a heat exchanger fin 400
according to another embodiment of the present disclosure. Guide
plates 462 provided at a louver unit 60 of the heat exchanger fin
400 have different inclination angles.
[0102] That is, the guide plates 462 may be provided at first
inclined surfaces 72 so that the guide plates 462 are at different
inclination angles relative to the first inclined surfaces 72.
[0103] FIGS. 16 and 17 illustrate a heat exchanger fin 500
according to another embodiment of the present disclosure. Slits
50, protruding frontward from the heat exchanger fin 500, are
provided at only one side of a protrusion 700.
[0104] In this case, the slits 50 are disposed at an external air
introduction side.
[0105] FIGS. 18 and 19 illustrate a heat exchanger fin 600
according to yet another embodiment of the present disclosure. A
protrusion 670 of the heat exchanger fin 600 includes a flat
surface 676.
[0106] The flat surface 676 is provided between first inclined
surfaces 672. The first inclined surfaces 672 may be symmetric with
respect to the flat surface 676. The distance between the flat
surface 676 and a plate 40 constitutes the height of the protrusion
670. The height of the protrusion 670 is 0.5 mm to 4.0 mm.
[0107] Guide plates 62 may be selectively provided at the first
inclined surfaces 672 or the flat surface 676. Alternatively, the
guide plates 62 may be provided at both the first inclined surfaces
672 and the flat surface 676.
[0108] At least two of the previous embodiments may be combined.
For example, when the embodiment of FIGS. 12 and 13 and the
embodiment of FIGS. 14 and 15 are combined, the guide plates 462
may be provided at the first inclined surfaces 372a and 372b of the
protrusion 370 formed in a non-symmetrical shape (characteristic of
the embodiment of FIG. FIGS. 12 and 13) so that the guide plates
462 are at different inclination angles to the first inclined
surfaces 372a and 372b (characteristic of the embodiment of FIGS.
14 and 15).
[0109] As is apparent from the above description, heat exchange
between air and the heat exchanger fins of the embodiments of the
present disclosure is effectively achieved, thereby improving heat
exchange efficiency.
[0110] Also, frost formation is restrained on the surfaces of the
heat exchanger fins, thereby improving heat exchange
efficiency.
[0111] 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.
* * * * *