EP1625340A1 - Ailette d'echangeur de chaleur, echangeur de chaleur, condenseurs et evaporateurs - Google Patents

Ailette d'echangeur de chaleur, echangeur de chaleur, condenseurs et evaporateurs

Info

Publication number
EP1625340A1
EP1625340A1 EP04733971A EP04733971A EP1625340A1 EP 1625340 A1 EP1625340 A1 EP 1625340A1 EP 04733971 A EP04733971 A EP 04733971A EP 04733971 A EP04733971 A EP 04733971A EP 1625340 A1 EP1625340 A1 EP 1625340A1
Authority
EP
European Patent Office
Prior art keywords
louvers
louver
air
heat
heat exchanger
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP04733971A
Other languages
German (de)
English (en)
Other versions
EP1625340A4 (fr
Inventor
Shinobu c/o Oyama Regional Office YAMAUCHI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Resonac Holdings Corp
Original Assignee
Showa Denko KK
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Showa Denko KK filed Critical Showa Denko KK
Publication of EP1625340A1 publication Critical patent/EP1625340A1/fr
Publication of EP1625340A4 publication Critical patent/EP1625340A4/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins
    • F28F1/128—Fins with openings, e.g. louvered fins
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B39/00—Evaporators; Condensers
    • 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
    • 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
    • F28F1/30—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 being attachable to the element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities

Definitions

  • the present invention relates to a heat exchanger such as a car air- conditioning condenser or evaporator for use in car air-conditioning refrigeration cycles as a car air-conditioning apparatus for example. It also relates to a fin for use in heat exchangers (hereinafter referred to as "heat exchanger fin”) such as a louver fin or a corrugated fin to be equipped to the aforementioned apparatuses.
  • a heat exchanger such as a car air- conditioning condenser or evaporator for use in car air-conditioning refrigeration cycles as a car air-conditioning apparatus for example.
  • heat exchanger fin a fin for use in heat exchangers
  • a heat exchanger such as an evaporator or a condenser for use in car air- conditioning refrigeration cycles includes a heat exchanging tube through which refrigerant passes and a heat exchanger fin disposed perpendicular to the longitudinal direction of the heat exchanging tube, so that heat exchanging is performed between the ambient air and the refrigerant passing through the heat exchanging tube via the fin.
  • louver fin As a heat exchanger fin, depending on the usage and/or required performance, a louver fin, an offset fin, a pin fin and the like has been commonly used.
  • a louver fin type heat exchanger as shown in Fig. 11 , a plurality of louver fins 50 arranged in parallel to the introduction direction X of the air A are arranged in parallel with each other at certain intervals in the direction perpendicular to the air introduction direction X, thereby forming an air passages 60 between the adjacent louver fins 50.
  • Each louver fin 50 is provided with a plurality of cut-and-bent louvers 51 arranged in the longitudinal direction (air introduction direction) of the air passage 60.
  • the air A introduced in each air passage 60 passes through the louver gaps each formed between the adjacent louvers 51 of each louver fin 50 along the louvers 51 , thereby exchanging heat between the air A and the refrigerant passing through the heat exchanging tube (not shown).
  • the smaller louver pitch may cause clogging of sand and/or bridging of condensed water between the adjacent louvers 51 , preventing the air A passing through the air passage 60 from being introduced into the louver gaps each formed between the adjacent louvers 51.
  • This causes the bypass flow of the air A, i.e., the air flow passing through the fin spaces each formed between the adjacent louver fins 50 without being introduced into the louver gaps, resulting in a deterioration of the heat transfer rate.
  • the present invention has the following features.
  • a heat exchanger fin comprising: a heat transfer plate disposed in parallel to a heat medium introduction direction and provided with a plurality louvers arranged at certain intervals in the heat medium introduction direction, said plurality of louvers being formed by cutting and bending said heat transfer plate so that the heat medium is passed while being guided by said plurality of louvers, wherein said plurality of louvers include plural kinds of louvers different in louver width, said louver width being defined by a length of said louver along which the heat medium passes, and wherein said plural kinds of louvers different in louver width are disposed in a mixed arrangement along the heat medium introduction direction.
  • the heat medium such as air will be assuredly introduced into the gaps each formed between the adjacent louvers to flow smoothly along each louver, resulting in improved heat transfer rate by preventing generation of bypass flow of the heat medium.
  • the present invention can be preferably employed as corrugated fins or plate fins.
  • the heat transfer rate can be further improved.
  • said heat transfer plate is disposed between said pair of heat exchanging tubes arranged in parallel with each other at a certain distance to exchange heat between air as a heat medium passing through said pair of heat exchanging tubes and refrigerant passing through said heat exchanging tube.
  • the present invention can be preferably employed in tube type heat exchangers.
  • the present invention can be preferably employed in condensers.
  • the present invention can be preferably employed in evaporators.
  • a louver fin comprising: a heat transfer plate disposed in parallel to a heat medium introduction direction and provided with a plurality louvers arranged at certain intervals in the heat medium introduction direction, said plurality of louvers being formed by cutting and bending said heat transfer plate so that the heat medium is passed while being guided by said plurality of louvers, wherein said plurality of louvers include plural kinds of louvers different in louver width, said louver width being defined by a length of said louver along which the heat medium passes, and wherein said plural kinds of louvers different in louver width are disposed in a mixed arrangement along the heat medium introduction direction.
  • the heat medium such as air will be assuredly introduced in between louvers to flow smoothly along each louver, enabling improvement of the heat transfer rate by preventing generation of bypass flow.
  • a corrugated fin comprising: a plurality of heat transfer plates disposed in parallel to a heat medium introduction direction and arranged in parallel at certain intervals in a direction perpendicular to the heat medium introduction direction with adjacent heat transfer plates connected with each other, each of said plurality of heat transfer plates being provided with a plurality louvers arranged at certain intervals in the heat medium introduction direction, said plurality of louvers being formed by cutting and bending said heat transfer plate so that the heat medium is passed while being guided by said plurality of louvers, wherein said plurality of louvers include plural kinds of louvers different in louver width, said louver width being defined by a length of said louver along which the heat medium passes, and wherein said plural kinds of louvers different in louver width are disposed in a mixed arrangement.
  • the heat medium such as air will be assuredly introduced in between louvers to flow smoothly along each louver, enabling improvement of the heat transfer rate by preventing generation of bypass flow.
  • a heat exchanger comprising a plurality of heat exchanger fins disposed in parallel to an air introduction direction and arranged in parallel at certain intervals in a direction perpendicular to the air introduction direction, and a refrigerant passage through which refrigerant passes, each of said plurality of heat transfer plates being provided with a plurality louvers arranged at certain intervals in the air introduction direction, said plurality of louvers being formed by cutting and bending said heat exchanger fin so that the air is passed while being guided by said plurality of louvers to exchange heat between the air and the refrigerant, wherein said plurality of louvers include plural kinds of louvers different in louver width, said louver width being defined by a length of said louver along which the heat medium passes, and wherein said plural kinds of louvers different in louver width are disposed in a mixed arrangement.
  • the heat medium such as air will be assuredly introduced in between louvers to flow smoothly along each louver, enabling improvement of the heat transfer rate by preventing generation of bypass flow.
  • a heat exchanger comprising a pair of heat exchanging tubes disposed in parallel at a certain interval, and a plurality of heat exchanger fins each disposed in parallel to an air introduction direction and arranged in parallel with each other at certain intervals in a direction perpendicular to the air introduction direction, and each of said plurality of heat exchanger fins being provided with a plurality louvers arranged at certain intervals in the air introduction direction, said plurality of louvers being formed by cutting and bending said heat exchanger fin so that the air is passed while being guided by said plurality of louvers to exchange heat between the air and the refrigerant, wherein said plurality of louvers include plural kinds of louvers different in louver width, said louver width being defined by a length of said louver along which the air passes, and wherein said plural kinds of louvers different in louver width are disposed in a mixed arrangement.
  • the heat medium such as air will be assuredly introduced in between louvers to flow smoothly along each louver, enabling improvement of the heat transfer rate by preventing generation of bypass flow.
  • the present invention can be preferably employed in corrugated type heat exchangers.
  • a condenser comprising a plurality of heat exchanger fins disposed in parallel to an air introduction direction and arranged in parallel at certain intervals in a direction perpendicular to the air introduction direction, and a refrigerant passage through which refrigerant passes, each of said plurality of heat transfer plates being provided with a plurality louvers arranged at certain intervals in the air introduction direction, said plurality of louvers being formed by cutting and bending said heat exchanger fin so that the air is passed while being guided by said plurality of louvers to condense the refrigerant by exchange heat between the air and the refrigerant, wherein said plurality of louvers include plural kinds of louvers different in louver width, said louver width being defined by a length of said louver along which the heat medium passes, and wherein said plural kinds of louvers different in louver width are disposed in a mixed arrangement.
  • the heat medium such as air will be assuredly introduced in between louvers to flow smoothly along each louver, enabling improvement of the heat transfer rate by preventing generation of bypass flow.
  • a condenser comprising a pair of heat exchanging tubes disposed in parallel at a certain interval, and a plurality of heat exchanger fins each disposed in parallel to an air introduction direction and arranged in parallel with each other at certain intervals in a direction perpendicular to the air introduction direction, and each of said plurality of heat exchanger fins being provided with a plurality louvers arranged at certain intervals in the air introduction direction, said plurality of louvers being formed by cutting and bending said heat exchanger fin so that the air is passed while being guided by said plurality of louvers to condense refrigerant by exchanging heat between the air and the refrigerant, wherein said plurality of louvers include plural kinds of louvers different in louver width, said louver width being defined by a length of said louver along which the air passes, and wherein said plural kinds of louvers different in louver width are disposed in a mixed arrangement.
  • the heat medium such as air will be assuredly introduced in between louvers to flow smoothly along each louver, enabling improvement of the heat transfer rate by preventing generation of bypass flow.
  • the present invention can be preferably employed in corrugated type heat exchangers.
  • a condenser for use in car air-conditioning refrigeration cycles comprising: a plurality of heat exchanger fins disposed in parallel to an air introduction direction and arranged in parallel at certain intervals in a direction perpendicular to the air introduction direction; and a refrigerant passage through which refrigerant passes, wherein each of said plurality of heat transfer plates is provided with a plurality louvers arranged at certain intervals in the air introduction direction, said plurality of louvers being formed by cutting and bending said heat exchanger fin so that the air is passed while being guided by said plurality of louvers to condense the refrigerant by exchange heat between the air and the refrigerant, and wherein said plurality of louvers include plural kinds of louvers different in louver width, said louver width being defined by a length of said louver along which the heat medium passes, and wherein said plural kinds of louvers different in louver width are disposed in a mixed arrangement.
  • the heat medium such as air will be assuredly introduced in between louvers to flow smoothly along each louver, enabling improvement of the heat transfer rate by preventing generation of bypass flow.
  • a condenser for use in car air-conditioning refrigeration cycles comprising: a pair of heat exchanging tubes disposed in parallel at a certain interval; and a plurality of heat exchanger fins each disposed in parallel to an air introduction direction and arranged in parallel with each other at certain intervals in a direction perpendicular to the air introduction direction, wherein each of said plurality of heat exchanger fins is provided with a plurality louvers arranged at certain intervals in the air introduction direction, said plurality of louvers being formed by cutting and bending said heat exchanger fin so that the air is passed while being guided by said plurality of louvers to condense refrigerant by exchanging heat between the air and the refrigerant, wherein said plurality of louvers include plural kinds of louvers different in louver width, said louver width being defined by a length of said louver along which the air passes, and wherein said plural kinds of louvers different in louver width are disposed in a mixed arrangement.
  • the heat medium such as air will be assuredly introduced in between louvers to flow smoothly along each louver, enabling improvement of the heat transfer rate by preventing generation of bypass flow.
  • An evaporator comprising a plurality of heat exchanger fins disposed in parallel to an air introduction direction and arranged in parallel at certain intervals in a direction perpendicular to the air introduction direction, and a refrigerant passage through which refrigerant passes, each of said plurality of heat transfer plates being provided with a plurality louvers arranged at certain intervals in the air introduction direction, said plurality of louvers being formed by cutting and bending said heat exchanger fin so that the air is passed while being guided by said plurality of louvers to evaporate the refrigerant by exchange heat between the air and the refrigerant, wherein said plurality of louvers include plural kinds of louvers different in louver width, said louver width being defined by a length of said louver along which the heat medium passes, and wherein said plural kinds of louvers different in louver width are disposed in a mixed arrangement.
  • An evaporator comprising a pair of heat exchanging tubes disposed in parallel at a certain interval, and a plurality of heat exchanger fins each disposed in parallel to an air introduction direction and arranged in parallel with each other at certain intervals in a direction perpendicular to the air introduction direction, and each of said plurality of heat exchanger fins being provided with a plurality louvers arranged at certain intervals in the air introduction direction, said plurality of louvers being formed by cutting and bending said heat exchanger fin so that the air is passed while being guided by said plurality of louvers to evaporate refrigerant by exchanging heat between the air and the refrigerant, wherein said plurality of louvers include plural kinds of louvers different in louver width, said louver width being defined by a length of said louver
  • the heat medium such as air will be assuredly introduced in between louvers to flow smoothly along each louver, enabling improvement of the heat transfer rate by preventing generation of bypass flow.
  • louvers include wide louvers each having a wide louver width and narrow louvers each having a narrow louver width, wherein said wide louvers and said narrow louvers are disposed in a mixed arrangement.
  • the present invention can be preferably employed in corrugated type evaporators.
  • An evaporator for use in car air-conditioning refrigeration cycles comprising: a plurality of heat exchanger fins disposed in parallel to an air introduction direction and arranged in parallel at certain intervals in a direction perpendicular to the air introduction direction; and a refrigerant passage through which refrigerant passes, wherein each of said plurality of heat transfer plates is provided with a plurality louvers arranged at certain intervals in the air introduction direction, said plurality of louvers being formed by cutting and bending said heat exchanger fin so that the air is passed while being guided by said plurality of louvers to evaporate the refrigerant by exchange heat between the air and the refrigerant, and wherein said plurality of louvers include plural kinds of louvers different in louver width, said louver width being defined by a length of said louver along which the heat medium passes, and wherein said plural kinds of louvers different in louver width are disposed in a mixed arrangement.
  • the heat medium such as air will be assuredly introduced in between louvers to flow smoothly along each louver, enabling improvement of the heat transfer rate by preventing generation of bypass flow.
  • An evaporator for use in car air-conditioning refrigeration cycles comprising: a pair of heat exchanging tubes disposed in parallel at a certain interval; and a plurality of heat exchanger fins each disposed in parallel to an air introduction direction and arranged in parallel with each other at certain intervals in a direction perpendicular to the air introduction direction, wherein each of said plurality of heat exchanger fins is provided with a plurality louvers arranged at certain intervals in the air introduction direction, said plurality of louvers being formed by cutting and bending said heat exchanger fin so that the air is passed while being guided by said plurality of louvers to evaporate refrigerant by exchanging heat between the air and the refrigerant, wherein said plurality of louvers include plural kinds of louvers different in louver width, said louver width being defined by a length of said louver along which the air passes, and wherein said plural kinds of louvers different in louver width are disposed in a mixed arrangement.
  • the heat medium such as air will be assuredly introduced in between louvers to flow smoothly along each louver, enabling improvement of the heat transfer rate by preventing generation of bypass flow.
  • Fig. 1 is a perspective cut-out explanatory view partially showing a fin and its vicinity of a heat exchanger according to an embodiment of the present invention.
  • Fig. 2 is an enlarged cross-sectional view taken along the line P-P in Fig. 1 and showing the louver fin of the aforementioned embodiment.
  • Fig. 3 is an enlarged cross-sectional view showing the fin portion of the heat exchanger according to the aforementioned embodiment.
  • Figs. 4(a) to 4(e) show partial cross-sectional views of louver fins according to modified embodiments of the present invention.
  • Fig. 5 is a graph showing the relationship between the front wind velocity and the heat transfer rate in the evaporators of Examples 1 to 5 and Comparative Example 1.
  • Fig. 6 is a graph showing the relationship between the front wind velocity and the heat transfer rate in the evaporators of Examples 6 and 7 and Comparative Example 2.
  • Fig. 7 is a graph showing the relationship between the louver angle and the heat transfer rate at the front wind velocity of 1 m/s in the evaporators of Examples 8 and 9 and Comparative Example 3.
  • Fig. 8 is a graph showing the relationship between the louver angle and the heat transfer rate at the front wind velocity of 2 m/s in the evaporators of Examples 8 and 9 and Comparative Example 3.
  • Fig. 9 is a graph showing the relationship between the fin pitch and the heat transfer rate at the front wind velocity of 1 m/s in the evaporators of Examples 9 and 10 and Comparative Example 4.
  • Fig. 10 is a graph showing the relationship between the fin pitch and the heat transfer rate at the front wind velocity of 2 m/s in the evaporators of Examples 10 and 11 and Comparative Example 4.
  • Fig. 11 is a cross-sectional view showing a part of louver fins of a conventional heat exchanger.
  • Fig. 1 is a perspective cut-out explanatory view partially showing a fin and its vicinity of a heat exchanger such as an evaporator for use in car air-conditioners according to an embodiment of the present invention
  • Fig. 2 is an enlarged cross- sectional view showing the louver fin applied to the heat exchanger of the aforementioned embodiment
  • Fig. 3 is an enlarged cross-sectional view of the front portions of the fins of the heat exchanger according to the aforementioned embodiment.
  • a plurality of flat heat exchanging tubes 1 and 2 each extending in the direction perpendicular to the air introduction direction X (Le ⁇ ., the up-and-down direction) are arranged in parallel with each other at certain intervals along the right-and-left direction of the heat exchanger in two rows.
  • a corrugated fin 3 Disposed between the adjacent heat exchanging tubes 1 and 1 (2 and 2) arranged in the widthwise direction of the heat exchanger is a corrugated fin 3.
  • the corrugated fin 3 is provided with a plurality of thin louver fins 4 as heat transfer plates extending in the front-and-rear direction and arranged in the up-and- down direction at certain intervals with their sides connected alternatively to thereby form a meandering shape. Between the adjacent louver fins 4 of the corrugated fin 3, an air passage 6 extending in the front-and-rear direction is formed, so that the air A as heat medium will be introduced into each air passage 6 from the front side of the heat exchanger during the operation.
  • Each louver fin 4 is provided with a plurality of louvers 5 formed by cutting and bending a certain region of the louver fin at certain intervals in the front-and-rear direction.
  • the air A entered into the air passages 6 will be guided by the louvers 5 into the louver gaps each formed between the adjacent louvers 5, so that heat exchanging is performed between the air A and the refrigerant passing through the heat exchanging tubes 1 via the fin.
  • the aforementioned plurality of louvers 5 in each louver fin 4 includes wide louvers 5a each having a large louver width and narrow louvers 5b each having a small louver width, and the wide louver and the narrow louver are disposed alternatively.
  • louver width of the wide louver 5a when the louver width of the wide louver 5a is represented as "Lwl,” it is preferable to set the width Lwl to 0.8 to 1.3 mm. It is more preferable to set the lower limit to 0.85 mm or more and the upper limit to 1.2 mm or less. Further, when the louver width of the narrow louver 5b is represented as "Lws,” it is preferable to set the width Lws to 0.1 to 0.6 mm. It is more preferable to set the lower limit to 0.15 mm or more.
  • Too small or too large louver width Lwl or Lws causes a deterioration of the heat transfer rate of the louver fin 4 because of the generated bypass flow of the air or the increased pressure loss, resulting in deteriorated heat exchanging performance. Furthermore, in this embodiment, it is preferable to set the ratio Lws/Lwl of the louver width "Lws" of the narrow louver 5b to the louver width Lwl of the wide louver 5a to 0.1 to 0.7. It is more preferable to set the lower limit to 0.3 or more.
  • the angle La of each louver 5 (louver angle) with respect to the louver fin 4 as a heat transfer plate is set to be almost constant. It is preferable to set the louver angle La to 22 to 36° . More preferably, the lower limit and the upper limit are set to 24° or more and 32° or less, respectively.
  • Too small or too large louver angle La causes a deterioration of the heat transfer rate of the louver fin because of the generated bypass flow of the air or the increased pressure loss, resulting in deteriorated heat exchanging performance.
  • the distance between the adjacent louver fins 4 and 4, i.e., the fin pitch Fp is preferably set to 1 to 2 mm. More preferably, the upper limit is set to 1.6 mm or less.
  • too small or too large fin pitch Fp causes a deterioration of the heat transfer rate of the louver fin 4 because of the generated bypass flow of the air or the increased pressure loss, resulting in deteriorated heat exchanging performance.
  • the ratio Fp/Lwl of the fin pitch Fp to the louver width Lwl of the wide louver 5a is preferably set to 1 or more. If this ratio is too small or too large, the heat transfer rate may deteriorate because of the generated bypass flow of the air or the increased pressure loss, resulting in deteriorated heat exchanging performance.
  • the plurality of louvers 5 include three or more kinds of louvers different in width
  • the plurality of louvers 5 of each louver fin 4 include wide louvers 5a and narrow louvers 5b arranged alternatively, the air A entered into the air passages 6 will be guided by the louvers 5 into the louver gaps each formed between the adjacent louvers 5, thereby causing the air A to smoothly flow along each louver 5. This improves the heat transfer rate by preventing the generation of bypass flow of the air A, resulting in excellent heat exchanging performance.
  • the plurality of louvers 5 of each louver fin 4 include two kinds of louvers, wide louvers 5a and narrow louvers 5b, arranged alternatively, in the present invention, the kind of louver or the arrangement thereof are not limited to the above.
  • the plurality of louvers may include one or plural wide louvers and one or plural narrow louvers arranged alternatively.
  • the present invention covers various embodiments so long as the plurality of louvers include two or more kinds of louvers different in louver width arranged in a mixed manner.
  • the narrow louvers 5b are arranged between the wide louvers 5a as shown in Fig. 4(b); one or more narrow louvers 5b and one or more wide louvers 5a are arranged alternatively as shown in Figs. 4(c) to 4(e); and the wide louvers 5a and the narrow louvers 5b are arranged randomly.
  • the present invention is not limited to it, but can also be applied to a heat exchanger such as a condenser or a heater core.
  • the heat exchanger is not limited to a heat exchanger for use in car air-conditioners, but can be used as a heat exchanger for use in room air-conditioners, refrigerators, another refrigeration apparatuses or heaters.
  • the explanation is directed to the case in which the present invention is applied to corrugated fins, the present invention is not limited to it, but can also be applied to plate fins in which adjacent heat transfer fins are disposed independently.
  • the present invention is not limited to it, but can be applied to a fin for transferring heat by heat medium other than air.
  • Lwl width of wide louver (mm)
  • Lws width of narrow louver (mm)
  • the evaporator of Example 1 was provided with corrugated fins having a plurality of louver fins each including wide louvers and narrow louvers arranged alternatively.
  • the louver width Lwl of the wide louver was 1.1 mm
  • the louver width Lws of the narrow louver was 0.167 mm
  • the louver angle La was 26°
  • the fin pitch Fp was 1.3 mm
  • the louver width ratio Lws/Lwl was 0.152.
  • the louver width Lwl of the wide louver was set to 1.0 mm, and the louver width Lws of the narrow louver was set to 0.333 mm. The remaining dimensions were set to the same as those in Example 1.
  • the louver width ratio Lws/Lwl was 0.333.
  • the louver width Lwl of the wide louver was set to 1.0 mm, and the louver width Lws of the narrow louver was set to 0.5 mm.
  • the remaining dimensions were set to the same as those in Example 1.
  • the louver width ratio Lws/Lwl was 0.50.
  • the louver width- Lwl of the wide louver was set to 0.85 mm, and the louver width Lws of the narrow louver was set to 0.583 mm.
  • the remaining dimensions were set to the same as those in Example 1.
  • the louver width ratio Lws/Lwl was 0.686.
  • the louver width Lwl of the wide louver was set to 0.85 mm, and the louver width Lws of the narrow louver was set to 0.65 mm.
  • the remaining dimensions were set to the same as those in Example 1.
  • the louver width ratio Lws/Lwl was 0.765.
  • the corrugated fin had a plurality of louvers arranged at a constant louver width (louver pitch) of 0.75 mm.
  • the remaining dimensions were set to the same as those in Example 1.
  • each heat transfer rate with respect to the front wind velocity was measured by computer simulation. The results are shown in the graph of Fig. 5.
  • the evaporators of Examples 1 to 5 were higher than the evaporator of Comparative Example 1 in heat transfer rate by 10 to 20% at the entire front wind velocity region, and therefore excellent in heat exchanging performance.
  • the heat transfer rate was excellent.
  • Example 1 was higher than the evaporator of Example 2 in heat transfer rate.
  • Example 1 to 5 in each of Examples 1 to 4 in which the ratio Lws/Lwl of the louver width Lws of the narrow louver to the louver width Lwl of the wide louver was 0.1 to 0.7, the heat transfer rate was more stabilized than that of Example 5 in which the louver width ratio Lws/Lwl exceeded 0.7.
  • Example 2 to 4 in which the louver width ratio Lws/Lwl was 0.3 to 0.7 sufficient heat transfer rate was obtained at the entire front wind velocity region.
  • Lwl width of wide louver (mm)
  • Lws width of narrow louver (mm)
  • Lws/Lwl louver width ratio
  • Fp fin pitch (mm)
  • La louver angle (° )
  • Example 6 As shown in Table 2, the evaporator of Example 6 was prepared in the same manner as the aforementioned Example 2 except that the louver angle La was set to 28
  • Example 7 The evaporator of Example 7 was prepared in the same manner as the aforementioned Example 3 except that the louver angle La was set to 28° .
  • the evaporator of Comparative Example 2 was prepared in the same manner as the aforementioned Comparative Example 1 except that the louver angle La was set to 28° .
  • La is set to 28°
  • the evaporators of Examples 6 and 7 were higher than the evaporator of Comparative Example 2 in heat transfer rate at the entire front wind velocity region, and therefore excellent in heat exchanging performance.
  • the heat transfer rate was high.
  • each heat transfer rate with respect to the louver angle La in the state in which the front wind velocity was 1 m/s and 2m/s was measured by computer simulation.
  • Lwl width of wide louver (mm)
  • Lws width of narrow louver (mm)
  • Lws/Lwl louver width ratio
  • Fp fin pitch (mm)
  • La louver angle (° )
  • evaporators of Examples 10 and 11 and Comparative Example 4 were prepared in the same manner as in the aforementioned Examples 2 and 3 and Comparative Example 1 except that the fin pitch Fp was set to parameter. In each of these evaporators, each heat transfer rate with respect to the fin pitch Fp in the state where the front wind velocity was 1 m/s and 2m/s was measured by computer simulation. These results are shown in the graphs of Figs. 9 and 10.
  • the present invention can be applied to a heat exchanger such as a car air- conditioning condenser or evaporator, and also to a heat exchanger fin such as a louver fin or a corrugated fin to be equipped to the heat exchanger.
  • a heat exchanger such as a car air- conditioning condenser or evaporator
  • a heat exchanger fin such as a louver fin or a corrugated fin to be equipped to the heat exchanger.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne une ailette d'échangeur de chaleur permettant d'améliorer la vitesse de transfert de chaleur, tout en empêchant la génération d'un écoulement de dérivation de chaleur. L'invention concerne une ailette d'échangeur de chaleur, notamment une ailette de louvre (4) dotée d'une pluralité de louvres (5) agencés à certains intervalles dans la direction d'introduction X de l'air A, les louvres étant formés par la coupe et par la courbure de l'ailette d'échangeur de chaleur, de sorte que l'air A circule tandis qu'il est guidé par les louvres (5). La pluralité de louvres (5) comprend des louvres différents en ce qui concerne la largeur de louvre, la largeur de louvre étant définie par la longueur de louvre le long duquel circule le milieu de chauffe, un louvre large et un louvre étroit étant agencés de manière alternée.
EP04733971A 2003-05-19 2004-05-19 Ailette d'echangeur de chaleur, echangeur de chaleur, condenseurs et evaporateurs Withdrawn EP1625340A4 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP2003140400 2003-05-19
US47836003P 2003-06-16 2003-06-16
PCT/JP2004/007160 WO2004102102A1 (fr) 2003-05-19 2004-05-19 Ailette d'echangeur de chaleur, echangeur de chaleur, condenseurs et evaporateurs

Publications (2)

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EP1625340A1 true EP1625340A1 (fr) 2006-02-15
EP1625340A4 EP1625340A4 (fr) 2009-01-21

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EP (1) EP1625340A4 (fr)
KR (1) KR20060012303A (fr)
AU (1) AU2004239162A1 (fr)
WO (1) WO2004102102A1 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100690891B1 (ko) * 2005-05-26 2007-03-09 엘지전자 주식회사 건조기용 열교환기 및 이를 이용한 응축식 건조기
KR100919390B1 (ko) 2006-02-13 2009-09-29 주식회사 엘지화학 수직 적층 구조의 중대형 전지모듈
US20070240865A1 (en) 2006-04-13 2007-10-18 Zhang Chao A High performance louvered fin for heat exchanger
FR2924491B1 (fr) * 2007-12-04 2009-12-18 Valeo Systemes Thermiques Intercalaire ondule muni de persiennes pour echangeur de chaleur
DE102009021179A1 (de) * 2009-05-13 2010-11-18 Behr Gmbh & Co. Kg Rippe für einen Wärmeübertrager
DE102009021177A1 (de) * 2009-05-13 2010-11-18 Behr Gmbh & Co. Kg Rippe für einen Wärmetauscher
KR101182129B1 (ko) 2009-10-13 2012-09-12 주식회사 엘지화학 구조적 안정성이 우수한 전지모듈
KR20110083017A (ko) 2010-01-13 2011-07-20 엘지전자 주식회사 열 교환기용 핀 및 이를 갖는 열 교환기
KR101230350B1 (ko) 2010-01-27 2013-02-06 주식회사 엘지화학 구조적 안정성이 우수한 전지팩
KR101231111B1 (ko) 2010-10-27 2013-02-07 주식회사 엘지화학 내구성이 향상된 전지팩
WO2012157857A2 (fr) 2011-05-19 2012-11-22 주식회사 엘지화학 Bloc-batterie présentant une excellente fiabilité structurelle
DE102014202788A1 (de) * 2013-12-19 2015-06-25 Robert Bosch Gmbh Wärmetauscher

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4693307A (en) * 1985-09-16 1987-09-15 General Motors Corporation Tube and fin heat exchanger with hybrid heat transfer fin arrangement
DE3050963C2 (fr) * 1980-04-30 1988-12-01 Nippondenso Co., Ltd., Kariya, Aichi, Jp
US5311935A (en) * 1992-01-17 1994-05-17 Nippondenso Co., Ltd. Corrugated fin type heat exchanger

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2568968Y2 (ja) * 1991-10-25 1998-04-22 昭和アルミニウム株式会社 熱交換器

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3050963C2 (fr) * 1980-04-30 1988-12-01 Nippondenso Co., Ltd., Kariya, Aichi, Jp
US4693307A (en) * 1985-09-16 1987-09-15 General Motors Corporation Tube and fin heat exchanger with hybrid heat transfer fin arrangement
US5311935A (en) * 1992-01-17 1994-05-17 Nippondenso Co., Ltd. Corrugated fin type heat exchanger

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2004102102A1 *

Also Published As

Publication number Publication date
WO2004102102A1 (fr) 2004-11-25
EP1625340A4 (fr) 2009-01-21
KR20060012303A (ko) 2006-02-07
AU2004239162A1 (en) 2004-11-25

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