EP1599698A1 - Wärmeübertragungslamelle, wärmetauscher, verdampfer und kondensator für eine autoklimaanlage - Google Patents

Wärmeübertragungslamelle, wärmetauscher, verdampfer und kondensator für eine autoklimaanlage

Info

Publication number
EP1599698A1
EP1599698A1 EP04704752A EP04704752A EP1599698A1 EP 1599698 A1 EP1599698 A1 EP 1599698A1 EP 04704752 A EP04704752 A EP 04704752A EP 04704752 A EP04704752 A EP 04704752A EP 1599698 A1 EP1599698 A1 EP 1599698A1
Authority
EP
European Patent Office
Prior art keywords
heat transfer
fin
heat
side edge
recited
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Withdrawn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
EP04704752A
Other languages
English (en)
French (fr)
Other versions
EP1599698A4 (de
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
Priority claimed from JP2003015045A external-priority patent/JP2004263881A/ja
Application filed by Showa Denko KK filed Critical Showa Denko KK
Publication of EP1599698A1 publication Critical patent/EP1599698A1/de
Publication of EP1599698A4 publication Critical patent/EP1599698A4/de
Withdrawn legal-status Critical Current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
    • F28F1/24—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

Definitions

  • HEAT TRENSFER FIN HEAT EXCHANGER
  • the present invention relates to a heat transfer fin for heat
  • ⁇ exchangers such as evaporators or condensers for use in car air-conditioners, and also relates to a heat exchanger, an evaporator for use in car air-conditioners or a condenser for use in car air-conditioners using such heat transfer fins.
  • an evaporator and the like for use in car air-condi ioners includes a plurality of heat exchanging tubes disposed in parallel with each other and a plurality of thin-plate like fins as heat transfer plates disposed between the adjacent heat exchanging tubes and arranged in parallel at certain intervals along the tube longitudinal direction.
  • an air passage is formed between adjacent fins, and heat exchanging is performed between the air passing through the air passage and the refrigerant passing through the heat exchanging tubes via the fins.
  • the windward side end face 101 is constituted as a nearly vertical surface against the air A passing through the air passage 110.
  • the air A collides with the windward side end face 101, turbulence of the air A occurs.
  • increasing the fin pitch causes increased turbulence of the air A, resulting in an increased pressure loss.
  • This increased pressure loss deteriorates the inhale amount of the air A and the inhale velocity of the air A, which in turn may result in deteriorated heat exchanging performance.
  • the heat exchanger having a larger pressure loss is lower in performance, and the heat exchanger having a smaller pressure loss is higher in performance and therefore excellent in heat exchanging performance.
  • Laid-open Patent Publication No.60-82786 discloses a fin-and-tube type heat exchanger in which the leeward side edge of the heat transfer fin is formed to be thin to decrease the pressure loss (see
  • the pressure loss can be decreased to some extent.
  • a further improvement of heat exchanging performance is required, and therefore a still further decreased pressure loss and improved heat transfer rate are desired.
  • the first aspect of the present invention employs the following structure (1).
  • a heat transfer fin comprising: a heat transfer plate for transferring heat of a heat transfer medium via the heat transfer plate, the heat transfer plate being disposed parallel or nearly parallel to a flowing direction of the heat transfer medium, wherein a heat transfer medium inlet side edge of the heat transfer plate is formed so as to become thinner toward an upstream side of a heat transfer medium flowing direction.
  • the heat transfer medium inlet side edge of the heat transfer plate is formed so as to become thinner toward an upstream side of a heat transfer medium flowing direction, the heat transfer medium flows smoothly along the external surface of the heat transfer plate without causing turbulence.
  • the flow resistance of the heat transfer medium decreases , causing a decreased pressure loss, which in turn results in an enhanced heat transfer rate.
  • excellent heat exchanging performance can be obtained.
  • the pressure loss can be further decreased, resulting in a further enhanced heat transfer rate.
  • the second aspect of the present invention employs the following structure (3) .
  • a heat transfer fin comprising: a plurality of heat transfer plates disposed in parallel with each other at certain intervals to form an air passage between adjacent heat transfer plates, whereby heat of air passing through the air passage is transferred via the heat transfer plates, wherein a windward side edge of the heat transfer plate is formed so as to become thinner toward a windward side of the air.
  • the third aspect of the present invention employs the following structure (6).
  • a heat transfer fin comprising: a plurality of heat transfer plates disposed between a pair of heat exchanging tubes arranged in parallel at a certain distance, the plurality of heat exchanging plates being disposed in parallel with each other at certain intervals along a longitudinal direction of the heat exchanging tube to form an air passage between adjacent heat transfer plates , whereby air passing through the air passage exchanges heat with refrigerant passing through the heat exchanging tubes, wherein a windward side edge of the heat transfer plate is formed so as to become thinner toward a windward side thereof .
  • the heat transfer fin as recited in the aforementioned Item (6) wherein the plurality of heat transfer plates are disposed independently as plate fins.
  • the heat transfer fin as recited in the aforementioned Item (6 ) wherein the plurality of heat transfer plates are connected such that adjacent heat transfer fins are connected to form a corrugated fin.
  • the heat transfer fin as recited in the aforementioned Item (6) wherein the plurality of heat transfer plates are integral skived fins formed by skiving a surface of the heat exchanging tube.
  • the fourth aspect of the present invention employs the following structure (16).
  • a heat transfer fin comprising: a heat transfer plate disposed parallel or nearly parallel to a heat transfer medium passing direction, the heat transfer plate being providedwith a plurality of louvers at certain intervals along the heat transfer medium passing direction to transfer heat of the heat transfer medium via the heat transfer plate, wherein a heat transfer medium inlet side edge of the louver is formed so as to become thinner toward an upstream side of the heat transfer medium passing direction.
  • the heat transfer medium inlet side edge of the louver is formed so as to become thinner toward an upstream side of a heat transfer medium flowing direction, the heat transfer medium flows smoothly along the external surface of the louver without causing turbulence.
  • the flow resistance of the heat transfer medium decreases, causing a decreased pressure loss, which in turn results in an enhanced heat transfer rate.
  • excellent heat exchanging performance can be obtained.
  • the fifth aspect of the present invention employs the following structure (18).
  • a heat transfer fin comprising: a plurality of heat transfer plates disposed in parallel with each other at certain intervals to form an air passage between adjacent heat transfer plates, the heat transfer plate being provided with a plurality of louvers at certain intervals along the air passage to transfer heat of air passing through the air passage via the heat transfer plate, wherein a windward side edge of the louver is formed so as to become thinner toward an upstream side of the air.
  • the sixth aspect of the present invention employs the following structure (20).
  • a heat transfer fin comprising: a plurality of heat transfer plates disposed between a pair of heat exchanging tubes arranged in parallel at a certain distance, the plurality of heat transfer plates being disposed in parallel with each other at certain intervals along a longitudinal direction of the heat exchanging tube to form an air passage between adjacent heat transfer plates, and the heat transfer plate being provided with a plurality of louvers at certain intervals along the air passage, whereby air passing through the air passage exchanges heat with refrigerant passing through the heat exchanging tubes, wherein a windward side edge of the louver is formed so as to become thinner toward a windward side of the air.
  • the seventh aspect of the present invention employs the following structure (28).
  • a heat transfer fin comprising: a heat transfer plate disposed parallel or nearly parallel to a heat transfer medium passing direction, the heat transfer plate being providedwith a plurality of louvers at certain intervals along the heat transfer medium passing direction to transfer heat of the heat transfer medium via the heat transfer plate, wherein a heat transfer medium inlet side edge of the heat transfer plate and that of the louver are respectively formed so as to become thinner toward an upstream side of the heat transfer medium passing direction.
  • the heat transfer medium inlet side edge of the heat transfer plate and that of the louver are respectively formed so as to become thinner toward an upstream side of a heat transf r medium flowing direction, the heat transfer medium flows smoothly along the external surface of the heat transfer plate and that of the louver without causing turbulence.
  • the flow resistance of the heat transfer medium decreases, causing a decreased pressure loss, which in turn results in an enhanced heat transfer rate.
  • excellent heat exchanging performance can be obtained.
  • the eighth aspect of the present invention employs the following structure (30).
  • a heat transfer fin comprising: a plurality of heat transfer plates disposed in parallel with each other at certain intervals to form an air passage between adjacent heat transfer plates, the heat transfer plate being provided with a plurality of louvers at certain intervals along the air passage to transfer heat of air passing through the air passage via the heat transfer plate, wherein a windward side edge of the heat transfer plate and that of the louver are respectively formed so as to become thinner toward an upstream side of the air.
  • the ninth aspect of the present invention employs the following structure (32).
  • a heat transfer fin comprising: a plurality of heat transfer plates disposed between a pair of heat exchanging tubes arranged in parallel at a certain distance, the plurality of heat exchanging plates being disposed in parallel with each other at certain intervals along a longitudinal direction of the heat exchanging tube to form an air passage between adjacent heat transfer plates, the heat transfer plate being provided with a plurality of louvers at certain intervals along the air passage, whereby air passing through the air passage exchanges heat with refrigerant passing through the heat exchanging tubes, wherein a windward side edge of the heat transfer plate and that of the louver are respectively formed so as to become thinner toward a windward side of the air.
  • the tenth aspect of the present invention employs the following structure (34).
  • the tenth aspect of the present invention is directed to an inner fin or the like to be disposed within a heat exchanging tube.
  • this heat transfer plate since the refrigerant inlet side edge of the heat transfer plate is formed so as to become thinner toward an upstream side of a refrigerant passing direction, the refrigerant flows smoothly along the external surface of the heat transfer plate without causing turbulence. Thus, the flow resistance of the refrigerant decreases, causing a decreased pressure loss, which in turn results in an enhanced heat transfer rate. As a result, excellent heat exchanging performance can be obtained.
  • the eleventh aspect of the present invention employs the following structure (36).
  • (36) A heat transfer fin disposed in a heat exchanging tube through which refrigerant passes, the heat transfer fin comprising a plurality of heat transfer plates arranged parallel to a refrigerant passing direction, the heat transfer plates being provided with openings in a zigzag form to transfer heat of the refrigerant via the heat transfer plates, wherein a side edge of the opening of the heat transfer plate facing an upstream side of the refrigerant passing direction is formed so as to become thinner toward the upstream side of the refrigerant passing direction.
  • the twelfth aspect of the present invention employs the following structure (38).
  • the heat transfer fins according to the first to twelfth aspects of the present invention can be preferably applied to heat exchangers, evaporators for use in car air-conditioners, or evaporators for use in car air-conditioners, as shown in the following structures (41) to (43).
  • a condenser for use in car air-conditioners the condenser being equipped with a heat transfer fin as recited in any one of the aforementioned Items (1) to (40).
  • FIG. 1 is a schematic partially broken perspective view showing a fin portion and therearound of an evaporator 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.
  • Fig.3 is an enlarged cross-sectional view showing the portion surrounded by the dashed line in Fig. 2.
  • Fig.4 is an enlarged cross-sectional view showing a windward side edge of a heat transfer plate/louver of a heat transfer fin according to a first modification of the present invention.
  • Fig. 5 is an enlarged cross-sectional view showing a windward side edge of a heat transfer plate/louver of a heat transfer fin according to a second modification of the present invention.
  • Fig. 6 is an enlarged cross-sectional view showing a windward side edge of a heat transfer plate/louver of a heat transfer fin according to a third modification of the present invention.
  • Fig. 7 is an enlarged cross-sectional view showing a windward side edge of a heat transfer plate/louver of a heat transfer fin according to a fourth modification of the present invention.
  • Fig. 8 is a graph showing the relationship of the pressure drop and the heat transfer rate with respect to the face velocity of evaporators according to Example 1 and Comparative Example 1.
  • Fig. 9 is a graph showing the relationship of the pressure drop and the heat transfer rate with respect to the face velocity of evaporators according to Example 2 and Comparative Example 1.
  • Fig. 10 is a graph showing the relationship of the pressure drop and the heat transfer rate with respect to the face velocity of evaporators according to Example 3 and Comparative Example 1.
  • Fig. 11 is a graph showing the relationship of the pressure drop and the heat transfer rate with respect to the face velocity of evaporators according to Example 1 and Comparative Example 2.
  • Fig. 12 is a graph showing the relationship of the pressure drop and the heat transfer rate with respect to the face velocity of evaporators according to Example 4 and Comparative Example 2.
  • Fig. 10 is a graph showing the relationship of the pressure drop and the heat transfer rate with respect to the face velocity of evaporators according to Example 3 and Comparative Example 1.
  • Fig. 11 is a graph showing the relationship of the pressure drop and the heat transfer rate with respect to the face velocity of evaporators according to Example 1 and Comparative Example 2.
  • Fig.14 is a cross-sectional view showing a windward side edge of a louver of a corrugated fin for conventional evaporators .
  • Fig. 1 is a schematic partially broken perspective view showing a fin portion and therearound of an evaporator for use in car air-conditioners according to an embodiment of the present invention.
  • Fig. 2 is a schematic cross-sectional view of a fin corresponding to a cross-section taken along the line P-P in Fig. 1.
  • the disposed direction of the heat exchanging tube 51 and 52 will be regarded as an up-an-down direction for easy understanding of the present invention.
  • a corrugated fin 53 Disposed between the heat exchanging tubes 51 and 52 adjacent in the widthwise direction of the evaporator is a corrugated fin 53.
  • the corrugated fin 53 is provided with a plurality of thin plate-like louver fins 54 as transfer plates extending in the fore and aft direction and disposed in parallel at certain intervals in the up-and-down direction.
  • the adjacent louver fins 54 are connected in turns to form a meandering shape.
  • an air passage 56 extending in the fore and aft direction is formed.
  • air A introduced from the front side of the evaporator passes through each air passage 56 and flows out of the rear side thereof.
  • Each louver fin 54 is providedwith a plurality of cut-and-bent louvers 55 at certain intervals in the fore and aft direction.
  • Fig.3 is an enlarged cross-sectional view showing the portion surrounded by the dashed line Q in Fig. 2.
  • Fig. 3 is an enlarged cross-sectional view of the front edge 55a of each louver 55 , i.e., the windward side edge (air inlet side edge) relative to the air A to be introduced into the air passing passage 56.
  • the windward edge 55a of the louver 55 is formed so as to become thinner toward the windward side.
  • the windward side edge 55a of the louver 55 is formed into a curved cross-sectional shape with a rounded tip end, or a semielliptic shape formed by dividing an ellipse along the minor axis .
  • the front edge 54a of the louver fin 54 which is a portion surrounded by the dashed line R in Fig. 2, i.e., the windward side edge (air inlet side edge) of the louver fin 54, is formed so as to become thinner toward the windward side as shown by the reference numeral in parentheses in Fig.3 in the same manner as the aforementioned windward side edge 55a of the louver 55.
  • air A is introduced into each air passage 56 from the front side of the evaporator and flows out of the rear side thereof.
  • the air A exchanges heat with the refrigerant passing through each heat exchanging tube 51 and 52 while passing through each air passage.
  • the air A to be introduced in the air passage 56 flows smoothly along the external surface of the windward side edge 55a of the louver 55 without causing air turbulence in stead of colliding against the windward side edge 55a because of the tapered semielliptic configuration thereof.
  • the air A flows smoothly along the external surface of the edge 54a without causing air turbulence.
  • the cross-sectional contour configuration of the front edge 54a/55a of the fin 54/louver 55 is formed into a semielliptic shape
  • the configuration is not limited to the above embodiments .
  • the cross-sectional contour configuration of the front edge can be a semicircular shape as shown in Fig. 4, an isosceles triangular shape with an acute front edge as shown in Fig. 5, a triangular shape with a single cut side as shown in Fig. 6, and a polygonal shape such as a trapezoidal shape with a tapered end portion as shown in Fig. 7.
  • the configuration can be any combination of the aforementioned shapes shown in Figs .3 to 7. In short, it can be acceptable so long as the front edge 54a/55a is formed so as to become thinner toward the tip end (windward side end) .
  • all of the louvers 55 are formed to have a tapered front edge 55a respectively.
  • at least one of the louvers 55 is formed to have a tapered front edge 55a.
  • both fins 54 and louvers 55 are formed to have a tapered front edge 54a and 55a respectively.
  • at least one of the fin front edge 54a and the louver front edge 55a is formed to have a tapered edge.
  • the explanation is directed to the case in which the present invention is applied to an evaporator.
  • the present invention is not limited to the above embodiments, and can be similarly applied to heat exchangers such as condensers, heater cores and radiators.
  • heat exchangers are not limited to heat exchanger for use in car air-conditioners, but can also be applied to heat exchangers for use in room air-conditioners, refrigerators, another refrigeration apparatuses, heaters, etc.
  • the explanation is directed to the case in which the present invention is applied to a corrugated fin as an example.
  • the present invention is not limited to the above embodiments, but can also be applied, for example, to plate fins as independent heat transfer plates to be disposed at certain intervals or skived fins formed by skiving an external peripheral wall(s) of a heat exchanging tube.
  • the explanation is directed to the case in which the present invention is applied to fins for transferring heat with air.
  • the present invention is not limited to the above embodiments , but can also be applied to any fins for transferring heat with another heat transfer medium such as refrigerant.
  • the refrigerant inlet side edge of the heat transfer plate (fin) to be disposed in a heat exchanging tube is formed so as to become thinner toward the upstream side of the refrigerant.
  • the present invention can be applied to offset fins with heat transfer medium mixing openings formed in summit and valley portions of a wavy heat transfer plate in a staggered manner. Furthermore, the side edge of the opening of the offset fin facing the upstream side of the heat transfer medium flowing direction among the peripheral edge of the opening can be formed so as to become thinner toward the upstream side.
  • the front side edge (upstream side edge with respect to the heat transfer medium flowing direction) of the fin (heat transfer plate) or its louver is formed into a tapered configuration.
  • the present invention is not limited to the above.
  • the rear side edge (the downstream side edge with respect to the heat transfer medium flowing direction, the heat transfer medium outlet side edge, or the leeward side edge) of the fin (heat transfer plate) or its louver can be formed so as to become thinner toward the rearward side (the downstream side, the outlet side or the leeward side) .
  • the side edge of the opening of the offset fin facing the downstream side of the heat transfer medium flowing direction among the peripheral edge of the opening can be formed so as to become thinner toward the downstream side.
  • Example 1 prepared was an evaporator provided with corrugated fins as shown in Fig. 3 in which the windward side edge of each fin and the windward side edge of each louver were respectively formed into a semielliptic configuration.
  • Comparative Example 1 prepared was an evaporator provided with conventional corrugated fins as shown in Fig. 14 in which the windward side edge of each fin and the windward side edge of each louver were respectively formed into a rectangular cross-sectional shape perpendicular to the air flow direction.
  • Example 1 the same measurements as in Example 1 were carried out.
  • Example 1 is excellent in performance at higher face velocity.
  • Example 2 prepared was an evaporator provided with corrugated fins as shown in Fig. 4 in which the windward side edge of each fin and the windward side edge of each louver were respectively formed into a semicircular cross-sectional shape.
  • Example 3 prepared was an evaporator provided with corrugated fins as shown in Fig. 5 in which the windward side edge of each fin and the windward side edge of each louver were respectively formed into an isosceles triangular cross-sectional shape.
  • Example 2 the same measurements as in Example 1 were carried out .
  • the measured results are shown in the graphs shown in Figs. 9 and 10.
  • Each of the graphs also shows the measured results of the evaporator of Comparative
  • Example 2 As shown in these graphs, the evaporator of Example 2 is smaller in pressure loss, higher in heat transfer rate and therefore excellent in heat exchanging performance as compared to Comparative Example 1. Furthermore, Example 3 is excellent in heat transfer rate especially at higher face velocity and therefore excellent in heat exchanging performance, though no superiority can be recognized in pressure loss .
  • Comparative Example 2 prepared was an evaporator provided with corrugated fins in which the windward side edge of each fin and the windward side edge of each louver were respectively formed into a rectangular cross-sectional shape (see Fig. 14), and the leeward side edges thereof were respectively formed into a semielliptic cross-sectional shape as shown in Fig. 3.
  • Example 1 Regarding this evaporator, the same measurements as in Example 1 were carried out. The measured results are shown by the dashed line in the graph shown in Fig. 11. In this graph, the solid lines denote the measured results of the evaporator of Example 1.
  • Example 4 prepared was an evaporator provided with corrugated fins in which the windward and leeward side edges of each fin and the windward and leeward side edges of each louver were respectively formed into a semielliptic cross-sectional shape as shown in Fig. 3.
  • Example 2 Regarding this evaporator, the same measurements as in Example 1 were carried out, and the measured results are shown in Fig. 12. In this graph, the dashed lines denote the measured results of the evaporator of Comparative Example 2.
  • FIG. 13 shows the measured results of Example 4 with solid lines and the measured results of Example 1 with dashed lines .
  • the graph reveals that the evaporator of Example 4 is slightly small in pressure loss and slightly higher in heat transfer rate as compared with Example 1.
  • forming both side edges of the fin/louver into a tapered end respectively enhances heat transferring performance as compared with the case in which only one windward side edge is formed into a tapered end.
  • a heat transfer medium inlet side edge of a heat transfer plate and/or its louver is formed into a tapered end, a heat transfer medium such as air can flow along the external periphery of the heat transfer plate and/or its louver, causing smooth flow without no turbulence. Accordingly, heat transfer medium flow resistance and pressure loss can be decreased, causing an enhanced heat transfer rate, which in turn results in excellent heat exchanging performance.
  • the present invention can be applied to, for example, a heat transfer fin for heat exchangers such as evaporators or condensers for use in car air-conditioners , and also relates to aheat exchanger, an evaporator for use in car air-conditioners or a condenser for use in car air-conditioners using such heat transfer fins .

Landscapes

  • Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP04704752A 2003-01-23 2004-01-23 Wärmeübertragungslamelle, wärmetauscher, verdampfer und kondensator für eine autoklimaanlage Withdrawn EP1599698A4 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
JP2003015045A JP2004263881A (ja) 2003-01-23 2003-01-23 伝熱フィン、熱交換器、カーエアコン用エバポレータ及びコンデンサ
JP2003015045 2003-01-23
US45452503P 2003-03-14 2003-03-14
US454525P 2003-03-14
PCT/JP2004/000623 WO2004065879A1 (en) 2003-01-23 2004-01-23 Heat transfer fin, heat exchanger, evaporator and condenser for use in car air-conditioner

Publications (2)

Publication Number Publication Date
EP1599698A1 true EP1599698A1 (de) 2005-11-30
EP1599698A4 EP1599698A4 (de) 2009-01-07

Family

ID=32775180

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04704752A Withdrawn EP1599698A4 (de) 2003-01-23 2004-01-23 Wärmeübertragungslamelle, wärmetauscher, verdampfer und kondensator für eine autoklimaanlage

Country Status (2)

Country Link
EP (1) EP1599698A4 (de)
WO (1) WO2004065879A1 (de)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9086243B2 (en) 2006-02-06 2015-07-21 Panasonic Intellectual Property Management Co., Ltd. Fin-tube heat exchanger
FR3166201A1 (fr) * 2024-09-09 2026-03-13 Claude Gerard Elément adapté pour former, entre deux plaques d’un échangeur thermique, des ailettes à bords d’attaque ou de fuite aminci(s), échangeur et procédé de fabrication correspondants

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07109355B2 (ja) * 1986-05-20 1995-11-22 日本パ−カライジング株式会社 アルミニウム製熱交換器及びその製造方法
JPH07218174A (ja) * 1994-02-04 1995-08-18 Mitsubishi Alum Co Ltd 放熱フィン
JP2000097589A (ja) * 1998-09-24 2000-04-04 Showa Alum Corp 熱交換器用チューブ
JP4358961B2 (ja) * 2000-03-02 2009-11-04 昭和電工株式会社 エバポレータ用フィン

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
No further relevant documents disclosed *
See also references of WO2004065879A1 *

Also Published As

Publication number Publication date
EP1599698A4 (de) 2009-01-07
WO2004065879A1 (en) 2004-08-05

Similar Documents

Publication Publication Date Title
US8276652B2 (en) High performance louvered fin for heat exchanger
US7882708B2 (en) Flat pipe-shaped heat exchanger
JP4117429B2 (ja) 熱交換器用フィン
CN103477177B (zh) 热交换器
US6213196B1 (en) Double heat exchanger for vehicle air conditioner
US7182128B2 (en) Heat exchanger tube having strengthening deformations
EP3018439B1 (de) Rippenrohrwärmetauscher
US6401809B1 (en) Continuous combination fin for a heat exchanger
CN208254300U (zh) 带有错位翅片的换热器盘管
US6170566B1 (en) High performance louvered fin for a heat exchanger
US20060266503A1 (en) Heat transfer fin, heat exchanger, evaporator and condenser for use in car air-conditioner
JPH10253276A (ja) 熱交換器
CN103890527B (zh) 翅片管热交换器
US20070051502A1 (en) Heat exchanger fin, heat exchanger, condensers, and evaporators
WO2006028253A1 (ja) 熱交換装置
JP2005106328A (ja) 熱交換装置
EP1625340A1 (de) Wärmetauscherrippe, wärmetauscher, kondensatoren und verdampfer
US5975200A (en) Plate-fin type heat exchanger
CN112888909A (zh) 热交换器和具有该热交换器的空气调节器
WO2005073655A1 (ja) 熱交換器及びこれを含む空調装置
EP1599698A1 (de) Wärmeübertragungslamelle, wärmetauscher, verdampfer und kondensator für eine autoklimaanlage
EP0803695A2 (de) Rippenplatten-Wärmetauscher
JP7006376B2 (ja) 熱交換器
EP3575728A1 (de) Kern eines wärmetauschers mit gewellten rippen
JP2009162433A (ja) 伝熱部材

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20050823

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20081205

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20090619