US20020003035A1 - Heat exchanger with small-diameter refrigerant tubes - Google Patents
Heat exchanger with small-diameter refrigerant tubes Download PDFInfo
- Publication number
- US20020003035A1 US20020003035A1 US09/897,143 US89714301A US2002003035A1 US 20020003035 A1 US20020003035 A1 US 20020003035A1 US 89714301 A US89714301 A US 89714301A US 2002003035 A1 US2002003035 A1 US 2002003035A1
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- heat exchanger
- air guide
- rows
- offset surfaces
- refrigerant tubes
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- 239000003507 refrigerant Substances 0.000 title claims abstract description 64
- 238000000034 method Methods 0.000 claims abstract description 6
- 230000008569 process Effects 0.000 claims abstract description 6
- 238000003825 pressing Methods 0.000 claims abstract description 5
- 230000000630 rising effect Effects 0.000 claims description 6
- 230000006872 improvement Effects 0.000 abstract description 3
- 238000004519 manufacturing process Methods 0.000 abstract description 3
- 230000001965 increasing effect Effects 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 238000007792 addition Methods 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/24—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely
- F28F1/32—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending transversely the means having portions engaging further tubular elements
- F28F1/325—Fins with openings
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S165/00—Heat exchange
- Y10S165/454—Heat exchange having side-by-side conduits structure or conduit section
- Y10S165/50—Side-by-side conduits with fins
- Y10S165/501—Plate fins penetrated by plural conduits
- Y10S165/502—Lanced
- Y10S165/503—Angled louvers
Definitions
- the present invention relates to a heat exchanger with small-diameter refrigerant tubes and, more particularly, to a heat exchanger designed such that the number, shape and dimension of vertical slits formed on its air guide fins are optimally designed to be compatible with the small-diameter refrigerant tubes.
- FIG. 1 is a perspective view of a conventional heat exchanger.
- FIG. 2 is a perspective view of a conventional air guide fin for such heat exchangers.
- FIG. 3 is a sectional view of the conventional air guide fin taken along the line A-A of FIG. 2.
- the conventional heat exchanger comprises a plurality of refrigerant tubes 1 and a plurality of air guide fins 3 .
- the refrigerant tubes 1 form a refrigerant passage of the heat exchanger, while the air guide fins 3 are vertically arranged at regular intervals, with the linear parts of the refrigerant tubes 1 passing through the fins 3 .
- the air guide fins 3 secure the heat exchange surface for allowing heat transfer between refrigerant and atmospheric air, and improve heat exchange efficiency of the heat exchanger.
- the entire refrigerant tubes 1 are arranged relative to the air guide fins 3 to form two vertical rows of tubes: left- and right-hand vertical rows of tubes 1 a and 1 b as best seen in FIG. 1.
- Each of the air guide fins 3 thus has two vertical rows of tube-fitting openings 20 for allowing an installation of the tubes 1 a and 1 b.
- each of the air guide fins 3 is typically provided with a plurality of vertical slits 10 for allowing air to pass through and enhancing the heat exchange efficiency of the heat exchanger.
- each air guide fin 3 is pressed at regularly spaced positions to form a plurality of offset surfaces 10 a such that the offset surfaces 10 a are alternately offset in opposite directions as best seen in FIG. 3.
- Two air guide openings are thus formed between opposite side edges of each offset surface 10 a and the land surface of the fin 3 , and allow air to smoothly pass through to improve heat exchange effect of the heat exchanger.
- a set of vertical slits 10 are each vertically formed on the fin 3 at a position between two tube-fitting openings 20 of each vertical row of openings 20 through a pressing process.
- six rows of vertical slits 10 are arranged in a transverse direction of the fin 3 at a position between the two tube-fitting openings 20 .
- the slits 10 are formed by the air guide openings, each of which is defined between opposite side edges of each of the offset surfaces loa and the land surface of the air guide fin 3 .
- the first, third and fifth rows of slits 11 , 13 and 15 are formed by the upward offset surfaces 11 a , 13 a and 15 a
- the second, fourth and sixth rows of slits 12 , 14 and 16 are formed by the downward offset surfaces 12 a , 14 a and 16 a
- the terms “upward offset” and “downward offset” are defined from FIG. 3 for ease of description.
- the first row of slits 11 comprise three unit slits vertically spaced apart from each other
- the second and sixth rows of slits 12 and 16 each comprise two unit slits vertically spaced apart from each other.
- the slits 10 When the slits 10 are formed on each of the air guide fins 3 as described above, the slits 10 reduce the thickness of the thermal boundary layer inside the atmospheric air flowing along the fins 3 , thus increasing the average heat transfer coefficient of air, and improving heat exchange operational performance of the heat exchanger.
- the conventional heat exchanger is designed to use refrigerant tubes 1 having an outer diameter of 7 mm or 9.52 mm.
- refrigerant tubes 1 having an outer diameter of 7 mm or 9.52 mm are so-called “small-diameter refrigerant tubes” in the specification.
- the heat exchange efficiency of the air guide fins 3 may be deteriorated since the heat exchange surface area of each fin 3 is reduced due to a reduction in the width of the fin 3 .
- such deterioration in the heat exchange efficiency of the fins 3 may be overcome by increasing the number of the air guide fins 3 per unit length of the refrigerant tubes 1 to compensate for the reduction in the heat exchange surface area of the fins 3 .
- an air guide fin which is preferably used in a heat exchanger having small-diameter refrigerant tubes, and of which the slits are appropriately arranged, shaped and sized to be compatible with the small-diameter refrigerant tubes.
- an object of the present invention is to provide a heat exchanger with small-diameter refrigerant tubes, of which the number, shape and dimension of vertical slits formed on the air guide fins are optimally designed to be compatible with the small-diameter refrigerant tubes, and which thus minimizes its airside pressure loss, in addition to accomplishing an improvement in the heat transfer efficiency of the fins.
- the present invention provides a heat exchanger, comprising a plurality of air guide fins securing a heat exchange surface for allowing heat transfer between refrigerant and atmospheric air and assembled with each other by one or more vertical rows of refrigerant tubes passing through the air guide fins, wherein each of said refrigerant tubes is a small-diameter tube having an outer diameter of not larger than 6 mm; and four rows of offset surfaces vertically formed on each of said air guide fins at a position between two tubes of each vertical row of refrigerant tubes through a pressing process such that the four rows of offset surfaces are arranged along a transverse direction of said fin, with four rows of vertical slits each formed by two air guide openings defined between opposite side edges of each of said offset surfaces and the land surface of the air guide fin.
- FIG. 1 is a perspective view of a conventional heat exchanger
- FIG. 2 is a perspective view of a conventional air guide fin for such heat exchangers
- FIG. 3 is a sectional view of the conventional air guide fin taken along the line A-A of FIG. 2;
- FIG. 4 is a plan view of an air guide fin included in a heat exchanger with small-diameter refrigerant tubes in accordance with the preferred embodiment of the present invention
- FIG. 5 is a sectional view of the air guide f in taken along the line B-B of FIG. 4;
- FIG. 6 is an enlarged plan view of the air guide f in of this invention.
- FIG. 7 is a sectional view of the air guide fin taken along the line C-C of FIG. 4;
- FIG. 8 is a sectional view of the air guide fin taken along the line D-D of FIG. 4;
- FIG. 9 is a plan view of an air guide fin having two rows of small-diameter refrigerant tubes in accordance with the present invention.
- FIG. 4 is a plan view of an air guide fin included in a heat exchanger with small-diameter refrigerant tubes in accordance with the preferred embodiment of the present invention.
- FIG. 5 is a sectional view of the air guide fin taken along the line B-B of FIG. 4.
- FIG. 6 is an enlarged plan view of the air guide fin of this invention.
- FIG. 7 is a sectional view of the air guide fin taken along the line C-C of FIG. 4.
- FIG. 8 is a sectional view of the air guide fin taken along the line D-D of FIG. 4.
- FIG. 9 is a plan view of an air guide fin having two rows of small-diameter refrigerant tubes according to this invention.
- the heat exchanger comprises a plurality of vertical rows of refrigerant tubes 51 and a plurality of air guide fins 53 .
- the refrigerant tubes 51 form a refrigerant passage of the heat exchanger, while the air guide fins 53 are vertically arranged at regular intervals, with the linear parts of the refrigerant tubes 51 passing through the fins 53 .
- the air guide fins 53 secure the heat exchange surface for allowing heat transfer between refrigerant and atmospheric air, and improve heat exchange efficiency of the heat exchanger.
- each of the refrigerant tubes 51 is a small-diameter tube having an outer diameter of not larger than 6 mm.
- each of the air guide fins 53 is formed on each of the air guide fins 53 at a position between two tubes of each vertical row of refrigerant tubes 51 such that the slits 60 are arranged along a transverse direction of the fin 53 .
- the slits 60 are formed as follows. That is, four rows of offset surfaces 70 are vertically formed on each of the air guide fins 53 at a position between two tubes of each vertical row of refrigerant tubes 51 through a pressing process such that the four rows of offset surfaces 70 are arranged along a transverse direction of the fin 53 .
- the four rows of vertical slits 60 are each formed by two air guide openings defined between opposite side edges of each of the offset surfaces 70 and the land surface of the air guide fin 53 .
- the first row of slits 61 are formed by two air guide openings 61 a and 61 b defined between the opposite side edges of the offset surface 71 and the land surface of the air guide fin 53 as best seen in FIG. 5.
- the first and fourth rows of offset surfaces 71 and 74 each consist of two spaced unit offset surfaces, while the second and third rows of offset surfaces 72 and 73 each consist of a single unit offset surface.
- the entire offset surfaces 70 having the slits 60 are offset from the land surface of the air guide fin 53 in the same direction.
- the unidirectionally offset structure of the surfaces 70 is caused by the fact that it is almost impossible to provide sufficient gaps for effectively forming oppositely offset surfaces between the fins 53 since the fins 53 in the heat exchanger having the small-diameter tubes 51 are densely arranged to leave narrow gaps of a small pitch between them due to the reduced diameter of the tubes 51 .
- each of the unit offset surfaces 71 a , 71 b , 74 a and 74 b of the first and fourth rows of offset surfaces 71 and 74 forming the slits 61 and 64 is inclined to be close to a transverse center-line “CL1” of the offset surfaces 70 in a direction toward a longitudinal center-line “CL2” of the offset surfaces 70 .
- the unit offset surfaces 71 a , 71 b , 74 a and 74 b are inclined only at their outside ends, but are horizontal at their inside ends, thus forming trapezoidal profiles when seeing them in a plan view as shown in FIG. 6.
- the unit offset surfaces 71 a , 71 b , 74 a and 74 b may be inclined at their inside and outside ends to form parallelogrammic profiles.
- each of the second and third offset surfaces 72 and 73 forming the slits 62 and 63 are inclined to be close to the transverse center-line “CL1” in the direction toward the longitudinal center-line “CL2”, and so the second and third offset surfaces 72 and 73 thus form equiangular trapezoidal profiles.
- the four rows of offset surfaces 70 forming the slits 60 are symmetrically arranged on the basis of the longitudinal center-line “CL2”.
- the ends of the offset surfaces 70 with the slits 60 around each of the refrigerant tubes 51 form a trace circle “C”, which is concentric with the refrigerant tube 51 and has a diameter of not larger than two times the outer diameter of each of the refrigerant tubes 51 .
- the diameter of the trace circle “C” is limited to be not larger than two times the outer diameter of the refrigerant tube 51 , it is possible to maintain appropriate gaps between the ends of the slits 60 and the outer surfaces of the tubes 51 , in addition to securing desired sufficient lengths of the slits 60 .
- each of the offset surfaces 70 with the slits 60 comprises two rising parts 71 a ′ and 71 b ′, 72 ′, 73 ′ or 74 a ′ and 74 b ′ extending from the land surface of the fin 53 , and a horizontal part 71 a , 71 b , 72 , 73 , 74 a or 74 b extending between the two rising parts.
- the horizontal parts 71 a , 71 b , 72 , 73 , 74 a and 74 b of the offset surfaces 70 each form a desired slit 61 , 62 , 63 and 64 between it and the land surface of the fin 53 .
- Each of the two rising parts 71 a ′ and 71 b ′, 72 ′, 73 ′ or 74 a ′ and 74 b ′ is inclined at a predetermined angle of inclination relative to the land surface of the air guide fin 53 for accomplishing smooth flow of air in the slits 60 .
- the fourth row of offset surfaces 74 positioned at the outermost edge of the slit arrangement are spaced apart from the outside edge of the air guide fin 53 by a gap “Lt” of 0.5 mm or more in an effort to allow a precise formation of the offset surfaces 70 and the slits 60 and protect a press machine during a process of forming the offset surfaces 70 and the slits 60 .
- the four rows of offset surfaces 70 have the same width “Ws”, and are arranged at regular intervals.
- the present invention provides a heat exchanger with small-diameter refrigerant tubes.
- the number of the vertical slits formed on each air guide fin is reduced, in addition to changing the shape and dimension of the slits so as to allow the slits to be compatible with the small-diameter refrigerant tubes. Therefore, the air guide fins of the heat exchanger are optimally compatible with the small-diameter refrigerant tubes.
- the heat exchanger is thus reduced in its production cost, accomplishes the recent trend of compactness, and minimizes its air-side pressure loss, in addition to accomplishing an improvement in its heat exchange operational performance due to its enhanced heat transfer efficiency. This heat exchanger is also improved in its productivity.
Abstract
Description
- 1. Field of the Invention
- The present invention relates to a heat exchanger with small-diameter refrigerant tubes and, more particularly, to a heat exchanger designed such that the number, shape and dimension of vertical slits formed on its air guide fins are optimally designed to be compatible with the small-diameter refrigerant tubes.
- 2. Description of the Prior Art
- FIG. 1 is a perspective view of a conventional heat exchanger. FIG. 2 is a perspective view of a conventional air guide fin for such heat exchangers. FIG. 3 is a sectional view of the conventional air guide fin taken along the line A-A of FIG. 2.
- As shown in FIG. 1, the conventional heat exchanger comprises a plurality of
refrigerant tubes 1 and a plurality ofair guide fins 3. Therefrigerant tubes 1 form a refrigerant passage of the heat exchanger, while theair guide fins 3 are vertically arranged at regular intervals, with the linear parts of therefrigerant tubes 1 passing through thefins 3. The air guide fins 3 secure the heat exchange surface for allowing heat transfer between refrigerant and atmospheric air, and improve heat exchange efficiency of the heat exchanger. - In the conventional heat exchanger, the
entire refrigerant tubes 1 are arranged relative to theair guide fins 3 to form two vertical rows of tubes: left- and right-hand vertical rows oftubes air guide fins 3 thus has two vertical rows of tube-fitting openings 20 for allowing an installation of thetubes - As shown in FIGS. 2 and 3, each of the
air guide fins 3 is typically provided with a plurality ofvertical slits 10 for allowing air to pass through and enhancing the heat exchange efficiency of the heat exchanger. - In order to form the
slits 10 on eachair guide fin 3, thefin 3 is pressed at regularly spaced positions to form a plurality ofoffset surfaces 10 a such that theoffset surfaces 10 a are alternately offset in opposite directions as best seen in FIG. 3. Two air guide openings are thus formed between opposite side edges of eachoffset surface 10 a and the land surface of thefin 3, and allow air to smoothly pass through to improve heat exchange effect of the heat exchanger. - In a detailed description with reference to FIGS. 2 and 3, a set of
vertical slits 10 are each vertically formed on thefin 3 at a position between two tube-fitting openings 20 of each vertical row ofopenings 20 through a pressing process. In such a case, six rows ofvertical slits 10 are arranged in a transverse direction of thefin 3 at a position between the two tube-fitting openings 20. Theslits 10 are formed by the air guide openings, each of which is defined between opposite side edges of each of the offset surfaces loa and the land surface of theair guide fin 3. - Of the six rows of
vertical slits 10, the first, third and fifth rows ofslits upward offset surfaces slits downward offset surfaces slits 11 comprise three unit slits vertically spaced apart from each other, while the second and sixth rows ofslits - When the
slits 10 are formed on each of theair guide fins 3 as described above, theslits 10 reduce the thickness of the thermal boundary layer inside the atmospheric air flowing along thefins 3, thus increasing the average heat transfer coefficient of air, and improving heat exchange operational performance of the heat exchanger. - The conventional heat exchanger is designed to use
refrigerant tubes 1 having an outer diameter of 7 mm or 9.52 mm. In recent years, it is desired to reduce the outer diameter of therefrigerant tubes 1 in an effort to accomplish a preferable reduction in both the production cost and air-side pressure loss of heat exchangers. Therefrigerant tubes 1 having such a reduced outer diameter are so-called “small-diameter refrigerant tubes” in the specification. - When a heat exchanger uses a plurality of small-diameter refrigerant tubes having a reduced outer diameter in place of
conventional refrigerant tubes 1 having an outer diameter of 7 mm or 9.52 mm, it is necessary to optimally design the arrangement and shape of both theair guide fins 3 and theslits 10 so as to allow thefins 3 and theslits 10 to be compatible with the small-diameter tubes 1. - When a heat exchanger is fabricated using the small-
diameter refrigerant tubes 1 and theair guide fins 3 without changing the arrangement and shape of thefins 3, it is almost impossible to form theslits 10 on thefins 3 since the widths of theslits 10 are extremely reduced as the width of thefins 3 is reduced due to the reduced outer diameter of therefrigerant tubes 1. - In the case of using such small-
diameter refrigerant tubes 1 in a heat exchanger, the heat exchange efficiency of theair guide fins 3 may be deteriorated since the heat exchange surface area of eachfin 3 is reduced due to a reduction in the width of thefin 3. In the prior art, such deterioration in the heat exchange efficiency of thefins 3 may be overcome by increasing the number of theair guide fins 3 per unit length of therefrigerant tubes 1 to compensate for the reduction in the heat exchange surface area of thefins 3. However, when a plurality of slits having the same arrangement and shape as those of theconventional slits 10 are formed onsuch fins 3, the air-side pressure loss of the heat exchanger is extremely increased to undesirably eliminate the advantages expected from the use of the small-diameter tubes as the refrigerant tubes. - That is, when a heat exchanger is fabricated using such small-
diameter refrigerant tubes 1 while densely arranging theair guide fins 3 each having the six rows ofvertical slits 10 in a conventional manner, thefins 3 undesirably increase resistance against air to overload a blower fan, thus damaging or breaking the blower fan. - Therefore, it is necessary to propose an air guide fin, which is preferably used in a heat exchanger having small-diameter refrigerant tubes, and of which the slits are appropriately arranged, shaped and sized to be compatible with the small-diameter refrigerant tubes.
- Accordingly, the present invention has been made keeping in mind the above problems occurring in the prior art, and an object of the present invention is to provide a heat exchanger with small-diameter refrigerant tubes, of which the number, shape and dimension of vertical slits formed on the air guide fins are optimally designed to be compatible with the small-diameter refrigerant tubes, and which thus minimizes its airside pressure loss, in addition to accomplishing an improvement in the heat transfer efficiency of the fins.
- In order to accomplish the above object, the present invention provides a heat exchanger, comprising a plurality of air guide fins securing a heat exchange surface for allowing heat transfer between refrigerant and atmospheric air and assembled with each other by one or more vertical rows of refrigerant tubes passing through the air guide fins, wherein each of said refrigerant tubes is a small-diameter tube having an outer diameter of not larger than 6 mm; and four rows of offset surfaces vertically formed on each of said air guide fins at a position between two tubes of each vertical row of refrigerant tubes through a pressing process such that the four rows of offset surfaces are arranged along a transverse direction of said fin, with four rows of vertical slits each formed by two air guide openings defined between opposite side edges of each of said offset surfaces and the land surface of the air guide fin.
- The above and other objects, features and other advantages of the present invention will be more clearly understood from the following detailed description taken in conjunction with the accompanying drawings, in which:
- FIG. 1 is a perspective view of a conventional heat exchanger;
- FIG. 2 is a perspective view of a conventional air guide fin for such heat exchangers;
- FIG. 3 is a sectional view of the conventional air guide fin taken along the line A-A of FIG. 2;
- FIG. 4 is a plan view of an air guide fin included in a heat exchanger with small-diameter refrigerant tubes in accordance with the preferred embodiment of the present invention;
- FIG. 5 is a sectional view of the air guide f in taken along the line B-B of FIG. 4;
- FIG. 6 is an enlarged plan view of the air guide f in of this invention;
- FIG. 7 is a sectional view of the air guide fin taken along the line C-C of FIG. 4;
- FIG. 8 is a sectional view of the air guide fin taken along the line D-D of FIG. 4; and
- FIG. 9 is a plan view of an air guide fin having two rows of small-diameter refrigerant tubes in accordance with the present invention.
- Reference now should be made to the drawings, in which the same reference numerals are used throughout the different drawings to designate the same or similar components.
- FIG. 4 is a plan view of an air guide fin included in a heat exchanger with small-diameter refrigerant tubes in accordance with the preferred embodiment of the present invention. FIG. 5 is a sectional view of the air guide fin taken along the line B-B of FIG. 4. FIG. 6 is an enlarged plan view of the air guide fin of this invention. FIG. 7 is a sectional view of the air guide fin taken along the line C-C of FIG. 4. FIG. 8 is a sectional view of the air guide fin taken along the line D-D of FIG. 4. FIG. 9 is a plan view of an air guide fin having two rows of small-diameter refrigerant tubes according to this invention.
- As shown in FIGS.4 to 6, the heat exchanger according to the present invention comprises a plurality of vertical rows of
refrigerant tubes 51 and a plurality ofair guide fins 53. Therefrigerant tubes 51 form a refrigerant passage of the heat exchanger, while theair guide fins 53 are vertically arranged at regular intervals, with the linear parts of therefrigerant tubes 51 passing through thefins 53. The air guide fins 53 secure the heat exchange surface for allowing heat transfer between refrigerant and atmospheric air, and improve heat exchange efficiency of the heat exchanger. In the heat exchanger of this invention, each of therefrigerant tubes 51 is a small-diameter tube having an outer diameter of not larger than 6 mm. In addition, four rows ofvertical slits 60 are formed on each of theair guide fins 53 at a position between two tubes of each vertical row ofrefrigerant tubes 51 such that theslits 60 are arranged along a transverse direction of thefin 53. - The
slits 60 are formed as follows. That is, four rows ofoffset surfaces 70 are vertically formed on each of theair guide fins 53 at a position between two tubes of each vertical row ofrefrigerant tubes 51 through a pressing process such that the four rows ofoffset surfaces 70 are arranged along a transverse direction of thefin 53. The four rows ofvertical slits 60 are each formed by two air guide openings defined between opposite side edges of each of theoffset surfaces 70 and the land surface of theair guide fin 53. For example, the first row ofslits 61 are formed by twoair guide openings offset surface 71 and the land surface of theair guide fin 53 as best seen in FIG. 5. Atmospheric air flow around thefins 53 under the guide of theslits 60, and so heat exchange effect of the heat exchanger is enhanced. Of the four rows of offsetsurfaces 70, the first and fourth rows of offsetsurfaces surfaces - In the present invention, the entire offset
surfaces 70 having theslits 60 are offset from the land surface of theair guide fin 53 in the same direction. The unidirectionally offset structure of thesurfaces 70 is caused by the fact that it is almost impossible to provide sufficient gaps for effectively forming oppositely offset surfaces between thefins 53 since thefins 53 in the heat exchanger having the small-diameter tubes 51 are densely arranged to leave narrow gaps of a small pitch between them due to the reduced diameter of thetubes 51. - As shown in FIG. 6, the outside end of each of the unit offset surfaces71 a, 71 b, 74 a and 74 b of the first and fourth rows of offset
surfaces slits - In the preferred embodiment of this invention, the unit offset surfaces71 a, 71 b, 74 a and 74 b are inclined only at their outside ends, but are horizontal at their inside ends, thus forming trapezoidal profiles when seeing them in a plan view as shown in FIG. 6. However, it should be understood that the unit offset surfaces 71 a, 71 b, 74 a and 74 b may be inclined at their inside and outside ends to form parallelogrammic profiles.
- The opposite ends of each of the second and third offset
surfaces slits surfaces surfaces 70 forming theslits 60 are symmetrically arranged on the basis of the longitudinal center-line “CL2”. - In addition, the ends of the offset surfaces70 with the
slits 60 around each of therefrigerant tubes 51 form a trace circle “C”, which is concentric with therefrigerant tube 51 and has a diameter of not larger than two times the outer diameter of each of therefrigerant tubes 51. - When the offset surfaces70 around each of the
refrigerant tubes 51 are designed to form such a trace circle “C”, it is possible to more effectively guide air to the outer surfaces of therefrigerant tubes 51, thus more effectively promoting heat transfer between the air and the sidewalls of thetubes 51. - In addition, when the diameter of the trace circle “C” is limited to be not larger than two times the outer diameter of the
refrigerant tube 51, it is possible to maintain appropriate gaps between the ends of theslits 60 and the outer surfaces of thetubes 51, in addition to securing desired sufficient lengths of theslits 60. - As shown in FIGS. 7 and 8, each of the offset surfaces70 with the
slits 60 comprises two risingparts 71 a′ and 71 b′, 72′, 73′ or 74 a′ and 74 b′ extending from the land surface of thefin 53, and ahorizontal part horizontal parts slit fin 53. Each of the two risingparts 71 a′ and 71 b′, 72′, 73′ or 74 a′ and 74 b′ is inclined at a predetermined angle of inclination relative to the land surface of theair guide fin 53 for accomplishing smooth flow of air in theslits 60. - In addition, the fourth row of offset
surfaces 74 positioned at the outermost edge of the slit arrangement are spaced apart from the outside edge of theair guide fin 53 by a gap “Lt” of 0.5 mm or more in an effort to allow a precise formation of the offset surfaces 70 and theslits 60 and protect a press machine during a process of forming the offset surfaces 70 and theslits 60. - The four rows of offset
surfaces 70 have the same width “Ws”, and are arranged at regular intervals. - In the heat exchanger of this invention, it is preferable to arrange two vertical rows of
refrigerant tubes 51 on theair guide tubes 53. - When the two vertical rows of
ref rigerant tubes 51 are arranged on theair guide tubes 53 as described above, it is preferable to form a zigzag arrangement of thetubes 51. - As described above, the present invention provides a heat exchanger with small-diameter refrigerant tubes. In the heat exchanger, the number of the vertical slits formed on each air guide fin is reduced, in addition to changing the shape and dimension of the slits so as to allow the slits to be compatible with the small-diameter refrigerant tubes. Therefore, the air guide fins of the heat exchanger are optimally compatible with the small-diameter refrigerant tubes. The heat exchanger is thus reduced in its production cost, accomplishes the recent trend of compactness, and minimizes its air-side pressure loss, in addition to accomplishing an improvement in its heat exchange operational performance due to its enhanced heat transfer efficiency. This heat exchanger is also improved in its productivity.
- Although a preferred embodiment of the present invention has been described for illustrative purposes, those skilled in the art will appreciate that various modifications, additions and substitutions are possible, without departing from the scope and spirit of the invention as disclosed in the accompanying claims.
Claims (9)
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
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KR1020000038505A KR100347894B1 (en) | 2000-07-06 | 2000-07-06 | Heat exchanger |
KR00-38505 | 2000-07-06 | ||
KR2000-38505 | 2000-07-06 |
Publications (2)
Publication Number | Publication Date |
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US20020003035A1 true US20020003035A1 (en) | 2002-01-10 |
US6431263B2 US6431263B2 (en) | 2002-08-13 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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US09/897,143 Expired - Lifetime US6431263B2 (en) | 2000-07-06 | 2001-07-03 | Heat exchanger with small-diameter refrigerant tubes |
Country Status (7)
Country | Link |
---|---|
US (1) | US6431263B2 (en) |
JP (2) | JP2002062076A (en) |
KR (1) | KR100347894B1 (en) |
CN (1) | CN1232794C (en) |
ES (1) | ES2223201B2 (en) |
IT (1) | ITRM20010385A1 (en) |
TW (1) | TW526323B (en) |
Cited By (7)
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US20070215330A1 (en) * | 2006-03-20 | 2007-09-20 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Heat exchanger |
US20090308585A1 (en) * | 2008-06-13 | 2009-12-17 | Goodman Global, Inc. | Method for Manufacturing Tube and Fin Heat Exchanger with Reduced Tube Diameter and Optimized Fin Produced Thereby |
US20100000726A1 (en) * | 2008-07-04 | 2010-01-07 | Sang Yeul Lee | Heat exchanger |
EP2447656A3 (en) * | 2010-10-28 | 2015-02-25 | Samsung Electronics Co., Ltd. | Heat Exchanger with louvered transversal fins |
US20190390922A1 (en) * | 2018-06-25 | 2019-12-26 | Getac Technology Corporation | Enhanced heat dissipation module, cooling fin struture and stamping method thereof |
US20220136784A1 (en) * | 2020-10-30 | 2022-05-05 | Asrock Inc. | Heat dissipation fin and heat dissipation module |
US11774187B2 (en) * | 2018-04-19 | 2023-10-03 | Kyungdong Navien Co., Ltd. | Heat transfer fin of fin-tube type heat exchanger |
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JP4610626B2 (en) * | 2008-02-20 | 2011-01-12 | 三菱電機株式会社 | Heat exchanger and ceiling-embedded air conditioner installed in ceiling-embedded air conditioner |
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US3397741A (en) * | 1966-02-21 | 1968-08-20 | Hudson Engineering Corp | Plate fin tube heat exchanger |
JPH0610591B2 (en) * | 1983-07-29 | 1994-02-09 | 三菱電機株式会社 | Heat exchanger |
JPS60188796A (en) * | 1984-03-09 | 1985-09-26 | Matsushita Electric Ind Co Ltd | Heat exchanger equipped with fin |
JPS616588A (en) * | 1984-06-20 | 1986-01-13 | Hitachi Ltd | Finned tube type heat exchanger |
JP2524812B2 (en) * | 1988-06-29 | 1996-08-14 | 三菱電機株式会社 | Heat exchanger |
JPH07109353B2 (en) * | 1989-02-01 | 1995-11-22 | 松下電器産業株式会社 | Heat exchanger with fins |
KR0155653B1 (en) * | 1995-01-23 | 1999-01-15 | 구자홍 | Fin & tube type heat exchanger |
JPH10132480A (en) * | 1996-10-31 | 1998-05-22 | Daikin Ind Ltd | Heat exchanger for air conditioner |
JP3292077B2 (en) * | 1997-01-30 | 2002-06-17 | 株式会社日立製作所 | Heat exchangers and air conditioners |
KR19990021475A (en) * | 1997-08-30 | 1999-03-25 | 윤종용 | Fin Heat Exchanger |
JPH11281282A (en) * | 1998-03-27 | 1999-10-15 | Sanyo Electric Co Ltd | Heat exchanger |
JP2001194084A (en) * | 1999-12-15 | 2001-07-17 | Lg Electronics Inc | Fin tube type heat exchanger |
-
2000
- 2000-07-06 KR KR1020000038505A patent/KR100347894B1/en not_active IP Right Cessation
-
2001
- 2001-07-02 JP JP2001201089A patent/JP2002062076A/en active Pending
- 2001-07-03 US US09/897,143 patent/US6431263B2/en not_active Expired - Lifetime
- 2001-07-03 IT IT2001RM000385A patent/ITRM20010385A1/en unknown
- 2001-07-05 ES ES200101567A patent/ES2223201B2/en not_active Expired - Fee Related
- 2001-07-05 CN CNB011200251A patent/CN1232794C/en not_active Expired - Fee Related
- 2001-07-06 TW TW090116556A patent/TW526323B/en active
-
2004
- 2004-11-22 JP JP2004006810U patent/JP3110196U/en not_active Expired - Lifetime
Cited By (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US20070215330A1 (en) * | 2006-03-20 | 2007-09-20 | Ishikawajima-Harima Heavy Industries Co., Ltd. | Heat exchanger |
US20090308585A1 (en) * | 2008-06-13 | 2009-12-17 | Goodman Global, Inc. | Method for Manufacturing Tube and Fin Heat Exchanger with Reduced Tube Diameter and Optimized Fin Produced Thereby |
US20100000726A1 (en) * | 2008-07-04 | 2010-01-07 | Sang Yeul Lee | Heat exchanger |
EP2447656A3 (en) * | 2010-10-28 | 2015-02-25 | Samsung Electronics Co., Ltd. | Heat Exchanger with louvered transversal fins |
US11774187B2 (en) * | 2018-04-19 | 2023-10-03 | Kyungdong Navien Co., Ltd. | Heat transfer fin of fin-tube type heat exchanger |
US20190390922A1 (en) * | 2018-06-25 | 2019-12-26 | Getac Technology Corporation | Enhanced heat dissipation module, cooling fin struture and stamping method thereof |
US10921066B2 (en) * | 2018-06-25 | 2021-02-16 | Getac Technology Corporation | Enhanced heat dissipation module, cooling fin structure and stamping method thereof |
US20220136784A1 (en) * | 2020-10-30 | 2022-05-05 | Asrock Inc. | Heat dissipation fin and heat dissipation module |
US11781818B2 (en) * | 2020-10-30 | 2023-10-10 | Asrock Inc. | Heat dissipation fin and heat dissipation module |
Also Published As
Publication number | Publication date |
---|---|
KR20020004530A (en) | 2002-01-16 |
ES2223201B2 (en) | 2006-03-16 |
ES2223201A1 (en) | 2005-02-16 |
KR100347894B1 (en) | 2002-08-09 |
ITRM20010385A0 (en) | 2001-07-03 |
ITRM20010385A1 (en) | 2002-01-07 |
JP2002062076A (en) | 2002-02-28 |
TW526323B (en) | 2003-04-01 |
CN1232794C (en) | 2005-12-21 |
US6431263B2 (en) | 2002-08-13 |
JP3110196U (en) | 2005-06-16 |
CN1332355A (en) | 2002-01-23 |
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