EP2843346B1 - Wärmetauscher mit gerippten röhren und herstellungsverfahren dafür - Google Patents

Wärmetauscher mit gerippten röhren und herstellungsverfahren dafür Download PDF

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Publication number
EP2843346B1
EP2843346B1 EP13781866.2A EP13781866A EP2843346B1 EP 2843346 B1 EP2843346 B1 EP 2843346B1 EP 13781866 A EP13781866 A EP 13781866A EP 2843346 B1 EP2843346 B1 EP 2843346B1
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EP
European Patent Office
Prior art keywords
fin
portions
tube
heat exchanger
fins
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Active
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EP13781866.2A
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English (en)
French (fr)
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EP2843346A4 (de
EP2843346A1 (de
Inventor
Toru Sukawa
Atsuo Okaichi
Kenji Nagoshi
Masaya Honma
Shuhei OHTSUBO
Shoichi Yokoyama
Masanobu Hirota
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Panasonic Corp
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Panasonic Corp
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Publication of EP2843346A4 publication Critical patent/EP2843346A4/de
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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
    • F28F17/00—Removing ice or water from heat-exchange apparatus
    • F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • 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
    • F25B39/02—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
    • F28D2021/0071—Evaporators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means

Definitions

  • the present invention relates to a fin-tube heat exchanger for exchanging heat with a gas and to a method of manufacturing the same.
  • a fin-tube heat exchanger of this kind includes a plurality of fins arrayed at predetermined intervals and a heat-transfer tube extending through the plurality of fins. Air (a gas) flows between the fins to exchange heat with a fluid in the heat-transfer tube.
  • a device such as, for example, an air conditioner or a water heater employing such a fin-tube heat exchanger is confronted with problems of increasing the power consumption and reducing the energy efficiency. Accordingly, it is preferred that the condensed water be quickly removed from the fin surfaces.
  • a hydrophilic film layer is formed on each fin surface to enhance the drainage property by reducing a contact angle with respect to the water adhering to the fin surface, thereby preventing the condensed water so generated from blocking the airflow path between the fins (see, for example, Document 1).
  • the hydrophilic film layer on the fin surface is irradiated with plasma to thereby form fine asperities to enhance the drainage property (see, for example, Document 2).
  • each fin is formed with a drainage slit to enhance the drainage property of the condensed water (see, for example, Document 3).
  • Fig. 10 depicts a configuration of a fin-tube heat exchanger as disclosed in Document 3.
  • a fin 131 has a drainage slit 116 defined therein so as to extend obliquely downwardly from a drain (condensed water 113) retention area positioned below a heat-transfer tube 121 along the surface of the fin 131.
  • the drainage slit 116 is intended to quickly discharge the condensed water 113 that accumulates in the drain retention area below the heat-transfer tube 121.
  • the present invention has been developed in view of the problems referred to above and is intended to provide a fin-tube heat exchanger that can enhance the drainage performance of the condensed water adhering to the fin surfaces using an inexpensive working process and is superior in energy efficiency.
  • the present invention is also intended to provide a method of manufacturing such a fin-tube exchanger.
  • the present invention is directed to a fin-tube heat exchanger comprising: a plurality of fins arrayed parallel to one another to form flow paths of a gas therebetween; and a heat-transfer tube extending through the plurality of fins to allow a fluid to flow through the heat-transfer tube for heat exchange with the gas; each of the fins comprising; a plurality of first inclined portions that incline with respect to a direction of airflow so as to form at least one ridge portion; a plurality of tube-surrounding portions located around the heat-transfer tube that extends through each of the fins at a first position and a second position spaced away from each other in a direction of gravitational force; and a plurality of second inclined portions that incline with respect to the direction of airflow, the second inclined portions connecting the tube-surrounding portions and the first inclined portions together, wherein each of the first inclined portions includes a groove portion defined in a surface thereof to connect the second inclined portion at the first position to the second inclined
  • the present invention can provide a fin-tube heat exchanger that can enhance the drainage performance of the condensed water adhering to the fin surfaces using an inexpensive working process and is superior in energy efficiency.
  • a first aspect of the invention is directed to a fin-tube heat exchanger comprising: a plurality of fins arrayed parallel to one another to form flow paths of a gas therebetween; and a heat-transfer tube extending through the plurality of fins to allow a fluid to flow through the heat-transfer tube for heat exchange with the gas; each of the fins comprising; a plurality of first inclined portions that incline with respect to a direction of airflow so as to form at least one ridge portion; a plurality of tube-surrounding portions located around the heat-transfer tube that extends through each of the fins at a first position and a second position spaced away from each other in a direction of gravitational force; and a plurality of second inclined portions that incline with respect to the direction of airflow, the second inclined portions connecting the tube-surrounding portions and the first inclined portions together, wherein each of the first inclined portions includes a groove portion defined in a surface thereof to connect the second inclined portion at the first position to the second inclined portion at the
  • This configuration can efficiently introduce condensed water downwardly in the direction of gravitational force through the groove portion from the second inclined portion where the condensed water mainly accumulates (or from the tube-surrounding portion through the second inclined portion). That is, the condensed water accumulating on the second inclined portion at the first position can be efficiently introduced to another second inclined portion at the second position, which is positioned downwardly of the first position in the direction of gravitational force, through the groove portion. Accordingly, a fin-tube heat exchanger can be provided that can enhance the drainage performance of the condensed water adhering to the fin surfaces and restrain a bridge from being generated between adjacent fins and is superior in energy efficiency. Also, the groove portion can be formed through a comparatively simple working process, thus making it possible to restrain an increase in manufacturing cost associated with the formation of the groove portion.
  • a second aspect of the invention is directed to a fin-tube heat exchanger according to the first aspect, wherein the groove portion has an opening of a width dimension of 2 mm or less.
  • This configuration creates the effect of the capillary action between the groove portion and the condensed water to thereby further efficiently discharge the condensed water.
  • a third aspect of the invention is directed to a fin-tube heat exchanger according to the first or second aspect, wherein in each of the fins, the ridge portion defined by the first inclined portions has a ridge line extending in the direction of gravitational force, and the groove portion extends in the direction of gravitational force.
  • This configuration can efficiently discharge the condensed water, which has entered the groove portion, downwardly in the direction of gravitational force.
  • a fourth aspect of the invention is directed to a fin-tube heat exchanger according to any one of the first to third aspects, wherein each of the fins comprises a base material and a coating formed on a surface of the base material, and the coating comprises a hydrophilic layer.
  • the condensed water accumulating on the tube-surrounding portion or the second inclined portion spreads flatly along the fin surface, thereby making it possible to further restrain the generation of the bridge and easily introduce the condensed water to the groove portion.
  • a fifth aspect of the invention is directed to a method of manufacturing the fin-tube heat exchanger according to fourth aspect, comprising: forming the hydrophilic layer on the base material; and subsequently shaping each of the fins by shaping the first inclined portions, the second inclined portions and the groove portion at the same time using the base material.
  • the first inclined portions, the second inclined portions and the groove portion of each fin are shaped at the same time, thus making it possible to provide a fin-tube heat exchanger that is superior in energy efficiency while restraining the manufacturing cost without addition of a new working process.
  • Fig. 1 depicts a perspective view of a fin-tube heat exchanger according to a first embodiment of the present invention.
  • the fin-tube heat exchanger 100 according to the first embodiment includes a plurality of fins 1 arrayed parallel to one another at predetermined intervals to form flow paths of air A (a gas) and a heat-transfer tube 21 extending through these fins 1.
  • the fin-tube heat exchanger is configured to exchange heat between a medium B flowing through the heat-transfer tube 21 and the air A flowing along surfaces of the fins 1.
  • a refrigerant such as, for example, carbon dioxide or hydrofluorocarbon is employed as the medium B.
  • the heat-transfer tube 21 may be made up of only one tube or branched into a plurality of tubes.
  • Figs. 2A , 2B and 2C depict a detailed configuration of each fin 1 according to the first embodiment.
  • the fin 1 is formed with at least one ridge portion 3 that appears with respect to a direction of airflow S.
  • the fin 1 has two ridge portions 3 with respect to the direction of airflow S and, as shown in a cross-sectional view of Fig. 2B , the fin 1 is formed as a corrugated fin having a cross-sectional shape generally in the form of an M.
  • the fin 1 is provided with a plurality of tube-surrounding portions 5, a plurality of first inclined portions 6 that incline with respect to the direction of airflow S so as to form the ridge portions 3, and a plurality of second inclined portions 7 that connect the tube-surrounding portions 5 and the first inclined portions 6 together.
  • the two ridge portions 3 and a hollow portion 4 positioned therebetween are formed by alternately connecting the first inclined portions 6 having different inclined angles with respect to the direction of airflow S.
  • ridge lines of the ridge portions 3 and the hollow portion 4 are formed so as to extend along the direction of gravitational force.
  • Each tube-surrounding portion 5 is an annular portion disposed so as to surround an associated heat-transfer tube 21 at a location where the heat-transfer tube 21 penetrates the fin 1.
  • the tube-surrounding portion 5 is formed as a plane or planar surface extending along the direction of airflow S.
  • the heat-transfer tube 21 penetrates each fin 1 at a plurality of locations spaced away from one another in the direction of gravitational force.
  • the tube-surrounding portions 5 are provided at the locations where the heat-transfer tube 21 penetrates the fin 1.
  • Each second inclined portion 7 is a portion provided around one of the tube-surrounding portions 5. As shown in Fig. 2C , each planar tube-surrounding portion 5 and each first inclined portion 6 having an inclined surface are connected to each other by one of the second inclined portions 7 having an inclined surface. Accordingly, as shown in Fig. 2C , a hollowed region surrounded by the inclined surfaces of the second inclined portions 7 is formed around the location where the heat-transfer tube 21 penetrates the fin 1. The hollowed region is a region where condensed water is apt to accumulate.
  • the fin 1 according to the first embodiment has a plurality of recessed groove portions 8 defined therein to discharge condensed water that has accumulated on the second inclined portions 7.
  • the recessed groove portions 8 are formed in the surfaces of a pair of first inclined portions 6, which form the hollow portion 4, so as to extend in the direction of gravitational force.
  • Each of the groove portions 8 is formed in the vicinity of the hollow portion 4 along an associated one of the ridge portions 3 and the hollow portion 4.
  • each groove portion 8 is formed so as to extend in the direction of gravitational force to connect the hollow regions that are adjacent to each other in the direction of gravitational force and each surrounded by the second inclined portion 7.
  • the groove portion 8 is such that at least a portion of a hollow cross-sectional surface thereof is open into the second inclined portion 7 at a connecting portion with the second inclined portion 7.
  • a metal having a water contact angle of 30 degrees or less be used. Also, an oxide layer or corrosion product is formed on the metal if the metal is exposed to air or moisture and, accordingly, in a surface treatment of a base material of the fin 1, a hydrophilic coating is preferably formed on respective surfaces of the base material.
  • a base material 9 having a coating 10 on respective surfaces thereof is used.
  • the coating 10 is made up of a corrosion-resistant layer 10a, a hydrophilic layer 10b laminated on the corrosion-resistant layer 10a, and a lubricant layer 10c laminated on the hydrophilic layer 10b.
  • a ferrous material, a copper material or an aluminum material can be used for the base material 9.
  • the corrosion-resistant layer 10a is formed through a chromate-phosphate treatment, while an inorganic (liquid glass-based or boehmite-based) layer, an organic resin-based layer, or an organic-inorganic composite layer can be used as the hydrophilic layer 10b.
  • an inorganic (liquid glass-based or boehmite-based) layer, an organic resin-based layer, or an organic-inorganic composite layer can be used as the hydrophilic layer 10b.
  • a silica/resin-based composite layer that is an organic-inorganic composite layer and has been formed through a chemical conversion treatment is used as the hydrophilic layer 10b.
  • the lubricant layer 10c is intended to enhance the lubricating property when the fin material is pressed into the fin 1. If a water-soluble layer is used as the lubricant layer 10c, it readily disappears in the presence of condensed water generated on the fin 1. Accordingly, the hydrophilic property of the hydrophilic layer 10b is not lowered by the lubricant layer 10c formed thereon.
  • the condensed water spreads flatly along the fin surfaces, thus making it possible to restrain a bridge from being generated between adjacent fins land to readily lead the condensed water to the groove portions 8 in a manner explained later.
  • Fig. 4 is a top plan view of a fin 1 having no groove portions 8 in a fin-tube heat exchanger according to a comparative example of the first embodiment.
  • the same component parts other than the groove portions 8 as those in the fin 1 according to the first embodiment are designated by the same reference numbers and explanation thereof is omitted.
  • condensed water 13 generated particularly around the heat-transfer tube 21 flows gradually downwardly along the surface of the fin 1 in the direction of gravitational force. This condensed water cannot climb over the ridge portion 3 positioned at the boundary with the first inclined portion 6 and gradually accumulates on the tube-surrounding portion 5 and the second inclined portion 7.
  • the amount of accumulated condensed water increases and a bridge is generated between adjacent fins 1 to block a space between them.
  • the airflow resistance increases and the heat-transfer area of the fin to be utilized for heat exchange with air reduces, thereby giving rise to a reduction in energy efficiency.
  • FIG. 5 An operation of discharging the condensed water in the fin 1 according to the first embodiment is explained hereinafter with reference to Fig. 5 .
  • Fig. 5(a), (b), (c) and (d) are shown in order of time from the left.
  • the accumulated condensed water is introduced into and passes through the groove portions 8, which are respectively connected to lower portions of the second inclined portions 7 in the direction of gravitational force, and is then introduced to the second inclined portions 7 at the second position P2 adjacent to the first position P1 in the direction of gravitational force.
  • Such a condensed water-introducing action of the groove portions 8 conveys the condensed water 13 from the tube-surrounding portion 5 and the second inclined portions 7 both positioned at an upper portion (position P1) in the direction of gravitational force to the next tube-surrounding portion 5 and the next second inclined portions 7 both positioned at a lower portion (position P2) in the direction of gravitational force ( Fig. 5(c) ).
  • the condensed water-introducing action of the groove portions 8 is repeatedly conducted to thereby convey the condensed water 13 further downwardly ( Fig. 5(d) ).
  • the condensed water-introducing action of the groove portions 8 can rapidly discharge the condensed water 13 accumulating on the tube-surrounding portion 5 and the second inclined portions 7, thus making it possible to dramatically enhance the drainage performance of the fin 1.
  • the groove portions 8 have been described as being formed so as to connect the second inclined portions 7 adjacent to each other in the direction of gravitational force, the groove portions 8 may be at least held in contact with the second inclined portions 7 formed at a lower portion of the heat-transfer tube 21 in the direction of gravitational force to introduce the condensed water accumulating on the second inclined portions 7 downwardly in the direction of gravitational force.
  • the groove portions 8 are formed to avoid the ridge lines of the ridge portions 3 or the hollow portions 4 formed by the first inclined portions 6, but the groove portions may be formed on the ridge lines by further hollowing the ridge portions 3 or the hollow portions 4.
  • a width dimension L of an opening of each groove portion 8 is preferably 2 mm or less to make use of the capillary action and, in order to further enhance the effect of the capillary action, the width dimension L is preferably 0.5 mm or less.
  • each groove portion 8 as shown in Fig. 6 has inclined side surfaces 8a in consideration of a reduction in airflow resistance of air passing between the fins 1, as shown in Fig. 7 , the groove portion 8 may have vertically extending side surfaces 8a. Alternatively, the groove portion 8 may be sharpened downwardly (in the form of a V) so as to have opposite side surfaces 8a that meet at a bottom portion 8b.
  • the first inclined portions 6, the second inclined portions 7 and the groove portions 8 can be shaped at the same time by pressing a base material having coatings formed thereon. Accordingly, an inexpensive fin-tube heat exchanger that is superior in drainage property can be manufactured without addition of a new working process.
  • Fig. 8 is a top plan view of a fin of a fin-tube heat exchanger according to a second embodiment of the present invention.
  • the same component parts as those in the first embodiment referred to above are designated by the same reference numbers and explanation thereof is omitted.
  • the second embodiment differs from the first embodiment in that the groove portions 8 are provided in the vicinity of the ridge portions 3 of each fin 1.
  • each groove portion 8 is formed so as to connect two second inclined portions 7 adjacent to each other in the direction of gravitational force along one of the ridge portions 3 of the fin 1.
  • Fig. 9A is a top plan view of a corrugated fin of a fin-tube heat exchanger according to a third embodiment of the present invention.
  • Figs. 9B and 9C are cross-sectional views of the corrugated fin.
  • the same component parts as those in the first embodiment referred to above are designated by the same reference numbers and explanation thereof is omitted.
  • each fin 15 is formed as a corrugated fin having a cross-sectional shape generally in the form of an inverted V (that is, the fin 15 has only one ridge portion 3 formed thereon).
  • each groove portion 8 is formed so as to connect two second inclined portions 7 adjacent to each other in the direction of gravitational force along the ridge portion 3 of the fin 15.
  • a V-shaped corrugated fin can be formed so as to have a larger surface area than that of an M-shaped corrugated fin and is accordingly likely to have an increased heat exchanging performance.
  • the V-shaped corrugated fin is provided with the flat tube-surrounding portions 5 and the second inclined portions 7 both having larger areas as those of the M-shaped corrugated fin and, accordingly, the area where the condensed water 13 accumulates becomes large, thus posing a problem that the condensed water 13 is likely to accumulate.
  • the condensed water 13 can be smoothly introduced downwardly in the direction of gravitational force by providing the groove portions 8 in the manner as set forth in the third embodiment, thus making it possible to realize a V-shaped corrugate fin that has an enhanced heat exchanging performance and is superior in drainage performance.
  • the groove portions 8 have been described as extending in the direction of gravitational force, it is sufficient if the groove portions continuously have components directed downwardly in the direction of gravitational force.
  • the groove portions may be inclined or curved with respect to the direction of gravitational force.
  • the groove portions formed in the fin surfaces have been also described as being able to enhance the drainage property of the condensed water adhering to the fin surfaces, the groove portions can enhance the drainage property of a liquid adhering to the fin surfaces as well as the condensed water.
  • the heat medium may exchange heat with a gas passing through the fin-tube heat exchanger as well as the air.
  • the fin-tube heat exchanger according to the present invention has the groove portions formed in the fin surfaces to enhance the drainage property
  • the fin-tube heat exchanger according to the present invention can be utilized as a heat exchanger for use in an air conditioner, a water heater, a heating appliance or the like.

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

Claims (5)

  1. Rippenrohrwärmetauscher (100), enthaltend:
    eine Vielzahl an Rippen (1;15), welche parallel zueinander angeordnet sind, um Strömungspfade für ein Gas dazwischen zu bilden, und
    ein Wärmeübertragungsrohr (21), welches sich durch die Vielzahl an Rippen (1; 15) hindurch erstreckt, um einem das Wärmeübertragungsrohr (21) durchströmenden Fluid den Wärmetausch mit dem Gas zu ermöglichen;
    jede der Rippen (1;15) enthaltend:
    eine Vielzahl an ersten geneigten Abschnitten (6), welche relativ zur Strömungsrichtung des Gases geneigt sind, um mindestens ein Scheitelkammabschnitt (3) zu bilden;
    eine Vielzahl an rohrumgebenden Abschnitten (5), welche um das Wärmeübertragungsrohr (21) angeordnet sind, das sich durch jede der Rippen (1, 15) in einer ersten Position (P1) und einer zweiten Position (P2), die in Schwerkraftrichtung zueinander beabstandet sind, hindurch erstreckt; und
    eine Vielzahl an zweiten geneigten Abschnitten (7), welche relativ zur Strömungsrichtung des Gases geneigt sind, wobei die zweiten geneigten Abschnitte (7) die rohrumgebenden Abschnitte (5) mit den ersten geneigten Abschnitten (6) verbinden,
    dadurch gekennzeichnet, dass jeder der ersten geneigten Abschnitte (6) einen in seiner Oberfläche ausgebildeten Rinnenabschnitt (8) aufweist, um den zweiten geneigten Abschnitt (7) an der ersten Position (P1) mit dem zweiten geneigten Abschnitt (7) an der zweiten Position (P2) zu verbinden.
  2. Rippenrohrwärmetauscher nach Anspruch 1, wobei der Rinnenabschnitt (8) eine Öffnung mit einer Breitenabmessung von 2 mm oder weniger aufweist.
  3. Rippenrohrwärmetauscher nach Anspruch 1 oder 2, wobei in jeder der Rippen (1; 15), der Scheitelkammabschnitt (3), welcher durch die ersten geneigten Abschnitte (6) gebildet ist, eine sich in Richtung der Schwerkraft erstreckende Scheitelkammlinie aufweist, und sich der Rinnenabschnitt (8) entlang der Schwerkraftrichtung erstreckt.
  4. Rippenrohrwärmetauscher nach einem der Ansprüche 1 bis 3, wobei jede der Rippen (1; 15) ein Grundmaterial (9) und eine Beschichtung (10), die auf dem Grundmaterial (9) gebildet ist, aufweist, und die Beschichtung (10) eine hydrophile Schicht (10b) enthält.
  5. Fertigungsverfahren für den Rippenrohrwärmetauscher nach Anspruch 4, enthaltend:
    Bilden der hydrophilen Schicht (10b) auf dem Grundmaterial (9); und
    anschließendes Formen jeder der Rippen durch zeitgleiches Formen der ersten geneigten Abschnitte (6), der zweiten geneigten Abschnitte (7) und des Rinnenabschnitts (8) unter Verwendung des Grundmaterials (9).
EP13781866.2A 2012-04-23 2013-04-22 Wärmetauscher mit gerippten röhren und herstellungsverfahren dafür Active EP2843346B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2012097380 2012-04-23
PCT/JP2013/002710 WO2013161263A1 (ja) 2012-04-23 2013-04-22 フィンチューブ熱交換器とその製造方法

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EP2843346A1 EP2843346A1 (de) 2015-03-04
EP2843346A4 EP2843346A4 (de) 2015-06-03
EP2843346B1 true EP2843346B1 (de) 2018-12-26

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EP (1) EP2843346B1 (de)
JP (1) JP6128492B2 (de)
CN (1) CN103857974B (de)
WO (1) WO2013161263A1 (de)

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JP6449032B2 (ja) * 2015-01-28 2019-01-09 アクア株式会社 冷却器及びその製造方法並びにその冷却器を備えた冷蔵庫
CN106066133A (zh) * 2016-06-22 2016-11-02 上海和衡能源科技发展有限公司 单管翅片型热交换器及其组装
DE102017120124A1 (de) * 2017-09-01 2019-03-07 Miele & Cie. Kg Lamellenrohrwärmeübertrager
DE102017120123A1 (de) * 2017-09-01 2019-03-07 Miele & Cie. Kg Lamellenrohrwärmeübertrager
CN108613232A (zh) * 2018-05-28 2018-10-02 广东美的厨房电器制造有限公司 用于制冷烟机的换热器及具有其的制冷烟机
CN111981583B (zh) * 2020-08-14 2021-12-07 青岛海信日立空调系统有限公司 一种空调器室外机
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CN103857974B (zh) 2018-03-16
JPWO2013161263A1 (ja) 2015-12-21
EP2843346A4 (de) 2015-06-03
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JP6128492B2 (ja) 2017-05-17
WO2013161263A1 (ja) 2013-10-31
CN103857974A (zh) 2014-06-11

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