EP2295919B1 - Lamelle und Wärmetauscher damit - Google Patents

Lamelle und Wärmetauscher damit Download PDF

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Publication number
EP2295919B1
EP2295919B1 EP10007986.2A EP10007986A EP2295919B1 EP 2295919 B1 EP2295919 B1 EP 2295919B1 EP 10007986 A EP10007986 A EP 10007986A EP 2295919 B1 EP2295919 B1 EP 2295919B1
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EP
European Patent Office
Prior art keywords
fin
circular arc
straight
segment
segments
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EP10007986.2A
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English (en)
French (fr)
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EP2295919A2 (de
EP2295919A3 (de
Inventor
Jiang Jianlong
Lin-Jie Huang
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.)
Sanhua Hangzhou Micro Channel Heat Exchanger Co Ltd
Danfoss AS
Original Assignee
Sanhua Holding Group Co Ltd
Sanhua Hangzhou Micro Channel Heat Exchanger Co Ltd
Danfoss AS
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Publication of EP2295919A3 publication Critical patent/EP2295919A3/de
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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
    • F28F1/126—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
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators

Definitions

  • the present invention relates to a fin and a heat exchanger having the same.
  • the headers of the heat exchanger of the parallel flow type are conventionally disposed horizontally and the tubes thereof are disposed vertically between the headers.
  • Fig. 10 is a structural schematic view of the conventional heat exchanger and Fig. 11 is an enlarged view of Portion G' in Fig. 10 .
  • the headers 3a' and 3b are disposed horizontally, parallel to and spaced from each other, and the tubes 2' are disposed vertically and parallel to each other between the headers 3a' and 3b', in which fins 1' are disposed between adjacent tubes 2' respectively.
  • the conventional disposition manners of the headers and tubes are not suitable for heat exchangers of some types such as prolate type (that is, heat exchanger having a length greater than a height thereof).
  • the headers should be very long such that the manufacturing costs thereof are high, and it is difficult to achieve a uniform distribution of the refrigerant. Since the headers do not participate ventilation and heat transfer, the longer the headers, the larger the area blocking the air flow, thus decreasing the effective heat-transfer area.
  • the tubes are short in length and large in number, that is, the number of the flow path of the refrigerant is large, so that the flow speed of the refrigerant in the tubes is low, thus causing poor heat-transfer performance.
  • the headers are disposed vertically and the tubes are disposed horizontally between the headers conventionally, thus decreasing the length of the headers, increasing the length of the tubes and decreasing the number of the tubes.
  • the conventional heat exchanger of prolate type with vertically disposed headers and horizontally disposed tubes employs conventional fins, there are some problems with the drainage of the condensation water. For example, as shown in Fig. 12 , if the air is blown along the direction D', due to the surface tension of the condensation water, most condensation water will be accumulated at the leeward side (i.e. region F' shown in Fig. 12 of the heat exchanger) and can be not drained smoothly.
  • EP 1 586 844 A1 discloses a fin having straight segments connected to each other along a longitudinal direction to form crests and troughs.
  • the straight segments comprise slots to accommodate tubes.
  • US 6 213 196 B1 shows a double heat exchanger for vehicle air conditioner having fins which are connected with bridges. Each fin has straight portions. A plurality of fins follows in longitudinal direction. These fins are connected by connecting portions.
  • US 2004/0206484 A1 shows two types of fins. In a first type wave crests and wave troughs of the fins are connected to tubes. In a second type the fin has slits in which the tubes are inserted.
  • US 5 787 972 A shows a heat exchanger fin having straight portions following each other in longitudinal directions. These straight portions are connected with connecting portions which have the same form over the entire width.
  • EP 1 832 832 A1 shows a heat exchanger having straight portions connected with arc shaped portions.
  • an object of the present invention is to provide a fin for a heat exchanger, in which the water drainage performance of the fin is improved.
  • an embodiment of the present invention provides a fin, as defined in claim 1.
  • each of the substantially-circular arc segments at least forming the wave troughs in the first end portion is divided into the first straight portion and the second straight portion, the first straight portion and the straight segment connected therewith may be in the same plane and the second straight portion and the straight segment connected therewith may be in the same plane as well, and when the fin is disposed between adjacent tubes of a heat exchanger, one end of the fin may be extended beyond the tubes in the lateral direction, so that the condensation water may easily flow downwardly along the first and second straight portions and the straight segments to drop off the fin and may not be accumulated on the fin, thus improving the water drainage performance of the fin.
  • each of the substantially-circular arc segments at least forming the wave troughs in the second end portion is separated from a substantially-circular arc segment of a corresponding intermediate portion via the longitudinal slot, and a top of each of the substantially-circular arc segments at least forming the wave troughs in the second end portion is formed with the lateral slot along the lateral direction such that each of the substantially-circular arc segments at least forming the wave troughs in the second end portion is divided into a first straight portion and a second straight portion separated from each other.
  • each of the substantially-circular arc segments at least forming the wave troughs in the second end portion is divided into the first straight portion and the second straight portion, the first straight portion and the straight segment connected therewith may be in the same plane and the second straight portion and the straight segment connected therewith may be in the same plane as well, and when the fin is disposed between adjacent tubes of a heat exchanger, the condensation water may easily flow downwardly along the first and second straight portions and the straight segments to drop off the fin and may not be accumulated on the fin, thus further improving the water drainage performance of the fin.
  • each of the substantially-circular arc segments forming the wave crests and wave troughs in the first and second end portions is separated from a substantially-circular arc segment of a corresponding intermediate portion via the longitudinal slot, and a top of each of the substantially-circular arc segments forming the wave crests and the wave troughs of the first and second end portions is formed with a lateral slot along the lateral direction such that each substantially-circular arc segment of the first and second end portions is divided into the first straight portion and the second straight portion separated from each other.
  • each of the substantially-circular arc segments forming the wave crests and wave troughs in the first and second end portions is divided into the first straight portion and the second straight portion, when the fin is disposed between adjacent tubes of the heat exchanger, the first and second end portions may be extended beyond the tubes in the lateral direction respectively, so that the condensation water may easily flow downwardly along the straight segments and the first and second straight portions to drop off the fin and may not be accumulated on the fin, thus further improving the water drainage performance of the fin.
  • a substantially-circular arc transition segment is connected between adjacent straight segment and substantially-circular, in which R> r, where R is a radius of the substantially-circular arc segment and r is a radius of the substantially-circular arc transition segment.
  • the radius R of the substantially-circular arc segment is larger than the radius r of the substantially-circular arc transition segment, when the fin is assembled and welded between adjacent tubes of the heat exchanger, the substantially-circular arc segment is easy to deform, whereas the straight segments and the substantially-circular arc transition segments substantially retain their shape respectively, so that the deformation of the fin is regular and easy to control, the fin is arranged uniformly in the heat exchanger, with a large heat-transfer coefficient, and the shape of the fin may meet the design requirements and be much more stable.
  • the radius ratio R/r of the radius R of the substantially-circular arc segment to the radius r of the substantially-circular arc transition segment is larger than 2. Therefore, the substantially-circular arc segment is easier to deform, so that the deformation of the fin is more regular and easier to control.
  • the central angle ⁇ of the substantially-circular arc segment is in a range of about 30° to about 170°. Therefore, the manufacture of the fin is more convenient.
  • each straight segment is formed with a window. Therefore, the heat-transfer coefficient may be further improved.
  • the window is formed by extending a portion of the straight segment away from a plane in which the straight segment is located.
  • an embodiment of the present invention provides a heat exchanger, comprising: a first header disposed vertically; a second header disposed vertically and spaced apart from the first header; a plurality of tubes, two ends of each flat tube being connected and communicated with the first and second headers respectively; and a plurality of fins, each of which is disposed between adjacent tubes, and a first end portion of each fin extended out from a first side of the adjacent tubes in a lateral direction, wherein each fin comprises: straight segments; and substantially-circular arc segments connected with the straight segments in turn along a longitudinal direction such that the substantially-circular arc segments form wave crests and wave troughs of the fin respectively, wherein the fin is divided in a lateral direction into a first end portion, a second end portion, and an intermediate portion between the first and second end portions, wherein each of the substantially-circular arc segments at least forming the wave troughs in the first end portion is separated from a substantially-circular
  • a second end portion of each fin is extended out from a second side opposite to the first side of the adjacent tubes in the lateral direction. Therefore, the water drainage performance of heat exchanger may be further improved and it is not necessary to consider the air blowing direction during mounting.
  • the heat exchanger according to the embodiment of the invention also has other advantages described above with reference to the fin.
  • relative terms such as “longitudinal”, “lateral”, “right”, “left”, “lower”, “upper”, “horizontal”, “vertical”, “above”, “below”, “up”, “top”, “bottom” as well as derivative thereof (e.g., “horizontally”, “vertically”, “downwardly”, “upwardly”, etc.) should be construed to refer to the orientation as then described or as shown in the drawings under discussion. These relative terms are for convenience of description and do not require that the present invention be constructed or operated in a particular orientation.
  • the fin 1 is substantially corrugated, and comprises straight segments 11, and substantially-circular arc segments 12 connected with the straight segments 11 in turn along a longitudinal direction B, in which the substantially-circular arc segments 12 form wave crests and wave troughs of the fin 1 respectively.
  • the fin 1 is divided in a lateral direction C into a first end portion 112, a second end portion 114, and an intermediate portion 113 between the first and second end portions 112, 114.
  • the width of the first end portion 112 in the lateral direction C is S1
  • the width of the second end portion 114 in the lateral direction C is S2.
  • S1, S2 and the width of the intermediate portion 113 in the lateral direction C may be determined according to the specific applications and may be not particularly limited in the present invention.
  • Each of the substantially-circular arc segments 12 at least forming the wave troughs in the first end portion 112 and a substantially-circular arc segment 12 of the corresponding intermediate portion 113, are split from each other in the up and down direction in Fig. 1 .
  • each of the substantially-circular arc segments 12 at least forming the wave troughs in the first end portion 112 is separated from a substantially-circular arc segment 12 of the corresponding intermediate portion 113 via a longitudinal slot 111 extended downwardly to the straight segments 11 as shown in Fig. 1 .
  • a lateral slot 110 is formed along the lateral direction C in a top of each of the substantially-circular arc segments 12 at least forming the wave troughs in the first end portion 112, and the lateral slot 110 is extended through the whole first end portion 112, such that each of the substantially-circular arc segments 12 at least forming the wave troughs in the first end portion 112 is divided into a first straight portion 12a and a second straight portion 12b separated from each other.
  • the first straight portion 12a and the straight segment 11 connected to the first straight portion 12a are in the same plane, and the second straight portion 12b and the straight segment 11 connected to the second straight portion 12b are in the same plane as well, as shown in Fig. 1 .
  • the substantially-circular arc segment 12 of the corresponding intermediate portion 113 is still substantially-circular arcuate.
  • the first end portion 112 of the fin 1 may be extended out from a first side of the adjacent tubes 2 (i.e. the right side in Fig. 8 ) along the lateral direction C, that is, the first end portion 112 of the fin 1 may be extended beyond the tubes 2 in the lateral direction C.
  • each of the substantially-circular arc segments 12 at least forming the wave troughs in the first end portion 112 is divided into the first straight portion 12a and the second straight portion 12b, the surface tension of the condensation water is destroyed, so that when the air is blown along a direction D, the condensation water may not be accumulated at Area F of the fin 1, and may easily flow downwardly along the straight segments 11, and the first and second straight portions 12a, 12b to drop off the fin 1, thus improving the water drainage performance of the fin 1.
  • each of the substantially-circular arc segments 12 at least forming the wave crests in the first end portion 112 is also divided into a first straight portion 12a and a second straight portion 12b via the longitudinal slot 111 and the lateral slot 110, such that when the fin 1 is disposed between adjacent tubes 2, the surface tension of the condensation water is destroyed by the first straight portion 12a and the second straight portion 12b, and the condensation water may easily flow downwardly along the first and second straight portions 12a, 12b of the substantially-circular arc segments 12 forming the wave crests, the straight segments 11, and the first and second straight portions 12a, 12b of the substantially-circular arc segments 12 forming the wave troughs, so as to drop off the fin 1, thus further reducing the possibility of the accumulating of the condensation water in Area F of the fin 1 and improving the water drainage performance of the fin 1.
  • each of the substantially-circular arc segments 12 at least forming the wave troughs in the second end portion 114 of the fin 1 is also divided into a first straight portion 12a and a second straight portion 12b via the longitudinal slot 111 and the lateral slot 110.
  • each of the substantially-circular arc segments 12 at least forming the wave crests in the second end portion 114 is also divided into a first straight portion 12a and a second straight portion 12b via the longitudinal slot 111 and the lateral slot 110.
  • the second end portion 114 may be extended out from a second side of the tubes 2 (i.e. the left side in Fig. 8 ) along the lateral direction C, that is, the second end portion 114 of the fin 1 may be extended beyond the tubes 2 in the lateral direction C. Because each of the substantially-circular arc segments 12 forming the wave troughs or both the wave troughs and the wave crests in the second end portion 114 is divided into the first straight portion 12a and the second straight portion 12b, the surface tension of the condensation water is destroyed. For example, when air is blown along a direction opposite to the direction D (i.e. the leftward direction in Fig.
  • the condensation water may not be accumulated in an area symmetrical to Area F of the fin 1, and may easily flow downwardly along the first and second straight portions 12a, 12b of the second end portion 114 and the straight segments 11 to drop off the fin 1, thus further improving the water drainage performance of the fin 1.
  • each of the substantially-circular arc segments 12 forming the wave troughs or both the wave troughs and the wave crests in both the first end portion 112 and the second end portion 114 of the fin 1 is divided into the first straight portion 12a and the second straight portion 12b, and when the fin 1 is disposed between adjacent tubes 2, both the first end portion 112 and the second end portion 114 are extended out from the two sides of the tubes 2 along the lateral direction C respectively, it is not necessary to consider the air blowing direction D during mounting, thus improving the mounting efficiency and the water drainage performance of the fin 1.
  • adjacent straight segment 11 and substantially-circular arc segment 12 are connected via a substantially-circular arc transition segment 13, in which R> r, where, R is a radius of the substantially-circular arc segment (its centre of circle is O1) and r is a radius of the substantially-circular arc transition segment (its centre of circle is 02).
  • each end of one substantially-circular arc segment 12 is connected with an end of one substantially-circular arc transition segment 13, and the other end of the substantially-circular arc transition segment 13 is connected with an end of another straight segment 11, and then the other end of the another straight segment 11 is connected with another substantially-circular arc transition segment 13, thus forming a substantially corrugated fin 1 extending along the longitudinal direction B.
  • two straight segment 11, two substantially-circular arc segment 12 and four substantially-circular arc transition segment 13 form one cycle of the fin 1, and one cycle length of the fin 1 is P.
  • the fin 1 may be made, for example, by rolling metal foil. It may be understood by those skilled in the art that the cycle number of the fin 1 may be determined based on specific requirements, and is not particularly limited in the invention.
  • the substantially-circular arc segment 12 is easier to deform so as to become straight and clings to the surface of the tubes 2, as shown in Fig. 5 and Fig. 9 , whereas the straight segments 11 and the substantially-circular arc transition segments 13 with a smaller radius keep their shape unchanged respectively.
  • the deformation of the substantially-circular arc segments 12 are regular, and the deformation of each of the substantially-circular arc segments 12 is uniform, so that the deformation of the fin 1 is regular and easy to control, the fin 1 is arranged uniformly in the heat exchanger, and the shape of the fin 1 may meet the design requirements and may be much more stable.
  • Areas A surrounded by two adjacent straight segments 11, the substantially-circular arc segments 12 becoming straight and the tubes 2 becomes substantially trapezoid and the shape of each of Areas A is uniform, as shown in Fig. 5 .
  • the heat exchanger of the embodiments of the present invention has an increased heat-transfer coefficient on the air blowing side, an improved heat-transfer performance and a much more regular and aesthetic appearance.
  • Areas A may be substantially rectangular or square after welding.
  • the radius ratio R/r of the radius R of the substantially-circular arc segment 12 to the radius r of the substantially-circular arc transition segment 13 is larger than 2, so that the substantially-circular arc segment 12 is easier to deform.
  • the larger the radius R the easier the deformation of the substantially-circular arc segment 12 is.
  • R may be 5 times larger than r, and if R is 1 mm, r is 0.2 mm.
  • the compressed distance of the substantially-circular arc segment 12 is N (i. e. the chordal height of the substantially-circular arc segment 12).
  • the compressed distance N is controlled within 0.01-0.1 mm, i.e. 0.01 mm ⁇ R ( 1-cos( ⁇ /2) ) ⁇ 0.1 mm, in which R is the radius of the substantially-circular arc segment 12, and ⁇ is the central angle of the substantially-circular arc segment 12.
  • the central angle ⁇ of the substantially-circular arc segment 12 is set in a range of about 30° to about 170°.
  • the straight segments 11 may be formed with a window 14, thus further improving the heat-transfer coefficient and the heat-transfer performance of the heat exchanger.
  • the window 14 may be formed by extending, such as punching, a middle portion 15 of the straight segment 11 away from the plane in which the straight segment 11 is located.
  • the window 14 may be also formed by cutting a slot in the straight segment 11, and then punching to turn the portion 15 of the straight segment 11 from the plane in which the straight segment 11 is located, so that the portion 15 may not be separated from the straight segment 11, thus further improving the heat-transfer coefficient and the heat-transfer performance.
  • the length L of the window 14 and the height H of the fin 1 satisfy the equation: 0.75 ⁇ L/H ⁇ 1.05, thus achieving better performance.
  • the length L is the length of the window 14 in the longitudinal direction (the direction indicated by Arrow Q in Fig. 3 ) of the straight segment 11
  • the height H is the height in the vertical direction (the up and down direction in Fig. 5 ) after formation of the fin 1, i.e. the distance between two parallel substantially-circular arc segment 12 in the up and down direction when the substantially-circular arc segment 12 becomes straight, as shown in Fig. 5 .
  • the heat exchanger according to the embodiment of the present invention comprises a first header 3a, a second header 3b, a plurality of tubes 2, and a plurality of fins 1.
  • the first header 3a is used as inlet header
  • the second header 3b is used as outlet header
  • the tube 2 may be a flat tube.
  • the first header 3a and the second header 3b are substantially disposed vertically, i.e. along the up and down direction in Fig. 6 .
  • the first header 3a and the second header 3b are substantially parallel with each other and spaced apart from each other by a predetermined distance.
  • the tubes 2 is disposed between the first header 3a and the second header 3b, and two ends of each flat tube 2 are connected and communicated with the first header 3a and the second header 3b respectively.
  • a plurality of micro-channels are formed in each flat tube 2, so that the heat exchanger according to the invention is referred as a micro-channel heat exchanger.
  • each fin 1 is disposed between adjacent tubes 2, and the first end portion 112 of each fin 1 may be extended out from a first side of the adjacent tubes 2 (i.e. the right side in Fig. 8 ) along the lateral direction C.
  • the substantially-circular arc segments 12 forming the wave troughs and the wave crests in the intermediate portion 113 of each fin 1 are pressed and flattened by the tubes 2, as shown in Fig. 9 . Because each of the substantially-circular arc segments 12 forming the wave troughs and the wave crests in the first end portion 112 are divided into the first straight portion 12a and the second straight portion 12b via the longitudinal slot 111 and the lateral slot 110, the surface tension of the condensation water is destroyed.
  • the condensation water may be not accumulated in Area F of the fin 1, and may easily flow downwardly along the straight segments 11, and the first and second straight portions 12a , 12b to drop off each fin 1, thus improving the water drainage performance of the heat exchanger.
  • each of the substantially-circular arc segments 12 forming the wave troughs and the wave crests in the second end portion 114 is also divided into the first straight portion 12a and the second straight portion 12b via the longitudinal slot 111 and the lateral slot 110, so that when blowing air along a direction opposite to the direction D, the condensation water may be not accumulated in an area (i.e. the left side in Fig. 8 ) symmetrical to the area F of the fin 1, and may easily flow downwardly along the first and second straight portions 12a, 12b of the second end portion 114, and the straight segments 11 to drop off the fin 1, thus further improving the water drainage performance of the heat exchanger, and it is not necessary to consider the direction D during mounting.
  • the substantially-circular arc segments 12 forming the wave troughs and the wave crests in the intermediate portion 113 of each fin 1 are pressed and flattened by the tubes 2 more easily, as shown in Figs. 8-9 and Fig. 5 , so that the shape of Areas A are regular, and the shape of Areas A is uniform.
  • the heat exchanger so manufactured has an increased heat-transfer coefficient, an improved heat-transfer performance and a much more regular and aesthetic appearance.
  • the heat exchanger according to the embodiment of the invention also has other advantages described with reference to the fin 1.
  • the heat exchanger according to embodiments of the invention has good water drainage performance, the condensation water does not tend to accumulate on the fin 1, and the fin 1 has a regular arrangement in the heat exchanger, an increased heat-transfer coefficient and a high heat-transfer performance.

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

Claims (13)

  1. Lamelle (1), aufweisend:
    gerade Segmente (11); und
    im Wesentlichen kreisbogenförmige Segmente (12), die entlang einer Längsrichtung derart abwechselnd mit den geraden Segmenten (11) verbunden sind, dass die im Wesentlichen kreisbogenförmigen Segmente (12) Wellenberge bzw. Wellentäler der Lamelle (1) bilden,
    wobei die Lamelle (1) in einer seitlichen Richtung in einen ersten Endabschnitt (112), einen zweiten Endabschnitt (114) und einen Zwischenabschnitt (113) zwischen den ersten und zweiten Endabschnitten (112, 114) geteilt ist, dadurch gekennzeichnet, dass im ersten Endabschnitt (112) Teilabschnitte, die jedem der im Wesentlichen kreisbogenförmigen Segmente (12) entsprechen, die wenigstens die Wellentäler bilden, von den im Wesentlichen kreisbogenförmigen Segmenten (12) eines entsprechenden Zwischenabschnitts (113) durch Längsschlitze (111) getrennt sind, und
    wobei ein oberes Ende jedes Teilabschnitts im ersten Endabschnitt, das dem oberen Ende jedes der im Wesentlichen kreisbogenförmigen Segmente entspricht, derart mit einem seitlichen Schlitz (110) entlang der seitlichen Richtung ausgebildet ist, dass jeder der Teilabschnitte im ersten Endabschnitt (112) in einen ersten geraden Abschnitt (12a) und einen zweiten geraden Abschnitt (12b) geteilt ist, die voneinander getrennt sind.
  2. Lamelle nach Anspruch 1, wobei im zweiten Endabschnitt (114) ein Teilabschnitt, der jedem der im Wesentlichen kreisbogenförmigen Segmente (12) entspricht, die wenigstens die Wellentäler bilden, von einem im Wesentlichen kreisbogenförmigen Segment (12) eines entsprechenden Zwischenabschnitts (113) durch den Längsschlitz (111) getrennt ist, und
    wobei ein oberes Ende jedes der Teilabschnitte im zweiten Endabschnitt (114) derart mit dem seitlichen Schlitz (110) entlang der seitlichen Richtung ausgebildet ist, dass jeder der Teilabschnitte im zweiten Endabschnitt (114) in einen ersten geraden Abschnitt (12a) und einen zweiten geraden Abschnitt (12b) geteilt ist, die voneinander getrennt sind.
  3. Lamelle nach Anspruch 2, wobei in den ersten und zweiten Endabschnitten (112, 114) ein Teilabschnitt, der jedem der im Wesentlichen kreisbogenförmigen Segmente (12) entspricht, welche die Wellenberge und Wellentäler bilden, von einem im Wesentlichen kreisbogenförmigen Segment (12) eines entsprechenden Zwischenabschnitts (113) durch den Längsschlitz (111) getrennt ist, und
    wobei ein oberes Ende jedes der Segmente der ersten und zweiten Endabschnitte (112, 114) derart mit einem seitlichen Schlitz (110) entlang der seitlichen Richtung ausgebildet ist, dass jedes Segment der ersten und zweiten Endabschnitte in den ersten geraden Abschnitt (12a) und den zweiten geraden Abschnitt (12b) geteilt ist, die voneinander getrennt sind.
  4. Lamelle nach einem der Ansprüche 1 bis 3, wobei ein im Wesentlichen kreisbogenförmiges Übergangssegment (13) zwischen einem benachbarten geraden Segment (11) und einem im Wesentlichen kreisbogenförmigen Segment (12) verbunden ist, wobei R > r, wobei R ein Radius des im Wesentlichen kreisbogenförmigen Segments (12) ist, und r ein Radius des im Wesentlichen kreisbogenförmigen Übergangssegments (13) ist.
  5. Lamelle nach Anspruch 4, wobei R/r > 2.
  6. Lamelle nach Anspruch 4, wobei 0 , 01 mm ≤ R ⁢ 1 - cos α / 2 ≤ 0 , 1 mm ,
    Figure imgb0003
     wobei α ein Mittelpunktswinkel des im Wesentlichen kreisbogenförmigen Segments ist.
  7. Lamelle nach Anspruch 4, wobei 2 * R * α * π / 180 / P ≥ 0 , 85 ,
    Figure imgb0004
     wobei:
    P eine Zykluslänge der Lamelle ist,
    α ein Mittelpunktswinkel des im Wesentlichen kreisbogenförmigen Segments ist, und
    n ein Umfangsverhältnis ist.
  8. Lamelle nach Anspruch 4, wobei 30° ≤ α ≤ 170°, wobei α ein Mittelpunktswinkel des im Wesentlichen kreisbogenförmigen Segments (12) ist.
  9. Lamelle nach Anspruch 4, wobei jedes gerade Segment mit einem Fenster (14) ausgebildet ist.
  10. Lamelle nach Anspruch 9, wobei das Fenster (14) durch Erweitern eines Abschnitts des geraden Segments (11) weg von einer Ebene ausgebildet ist, in welcher sich das gerade Segment (11) befindet.
  11. Lamelle nach Anspruch 9, wobei 0,85 ≤ L/H ≤ 1,05, wobei:
    L eine Länge des Fensters (14) ist, und
    H eine Höhe der Lamelle (1) in der vertikalen Richtung nach dem Verformen ist.
  12. Wärmetauscher, aufweisend:
    einen ersten Verteiler (3a), der vertikal angeordnet ist;
    einen zweiten Verteiler (3b), der vertikal und vom ersten Verteiler (3a) beabstandet angeordnet ist;
    eine Mehrzahl von Rohren (2), wobei zwei Enden jedes Flachrohrs (2) mit dem ersten bzw. zweiten Verteiler (3a, 3b) verbunden sind und in Kommunikation stehen; und
    eine Mehrzahl von Lamellen (1), die jeweils zwischen benachbarten Rohren angeordnet sind, wobei ein erster Endabschnitt (112) jeder Lamelle (1) von einer ersten Seite der benachbarten Rohre (2) in einer seitlichen Richtung nach außen erweitert ist, und wobei jede Lamelle (1) eine Lamelle (1) nach einem der Ansprüche 1 bis 10 ist.
  13. Wärmetauscher nach Anspruch 12, wobei ein zweiter Endabschnitt (114) jeder Lamelle (1) von einer zweiten Seite gegenüber der ersten Seite der benachbarten Rohre (2) in der seitlichen Richtung nach außen erweitert ist.
EP10007986.2A 2009-08-13 2010-07-30 Lamelle und Wärmetauscher damit Active EP2295919B1 (de)

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CN2009101623884A CN101619950B (zh) 2009-08-13 2009-08-13 翅片和具有该翅片的换热器

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CN101619950A (zh) 2010-01-06
CN101619950B (zh) 2011-05-04
US20110036550A1 (en) 2011-02-17
EP2295919A2 (de) 2011-03-16
EP2295919A3 (de) 2014-03-26

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