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EP1701124A1 - Echangeur de chaleur à lamelles et une ailette de lamelle appropriée - Google Patents

Echangeur de chaleur à lamelles et une ailette de lamelle appropriée Download PDF

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Publication number
EP1701124A1
EP1701124A1 EP06001939A EP06001939A EP1701124A1 EP 1701124 A1 EP1701124 A1 EP 1701124A1 EP 06001939 A EP06001939 A EP 06001939A EP 06001939 A EP06001939 A EP 06001939A EP 1701124 A1 EP1701124 A1 EP 1701124A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
heating
lamellae
heat transfer
lamella
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.)
Granted
Application number
EP06001939A
Other languages
German (de)
English (en)
Other versions
EP1701124B1 (fr
Inventor
Ceslovas Kizlauskas
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.)
Kelvion Refrigeration GmbH
Original Assignee
Kueba Kaltetechnik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Kueba Kaltetechnik GmbH filed Critical Kueba Kaltetechnik GmbH
Publication of EP1701124A1 publication Critical patent/EP1701124A1/fr
Application granted granted Critical
Publication of EP1701124B1 publication Critical patent/EP1701124B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2215/00—Fins
    • F28F2215/10—Secondary fins, e.g. projections or recesses on main 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
    • F28F2275/00—Fastening; Joining
    • F28F2275/12—Fastening; Joining by methods involving deformation of the elements
    • F28F2275/125—Fastening; Joining by methods involving deformation of the elements by bringing elements together and expanding

Definitions

  • the invention relates to a blade for a fin heat exchanger with a plurality of parallel blades for heat exchange with a side of the slats flowing gaseous medium, a fin heat exchanger with a plurality of such fins and a use of the fin heat exchanger.
  • finned heat exchangers a number of generally metallic fins are arranged parallel to each other and is penetrated by one or more heat transfer tubes.
  • a finned heat exchanger is z. B. used for cooling or heating gaseous media, in particular of air.
  • Such a plate heat exchanger for cooling gaseous media is z. B. described in DE 197 09 176 A1.
  • a coolant flows through the heat transfer tube in cooling operation, while the medium to be cooled flows through the free space between the slats.
  • the cooled heat transfer tube cools the fins, which in turn absorb heat from the flowing gaseous medium.
  • the flow of the gaseous medium is substantially laminar. Accordingly, directly at the fins, the flow rate of the medium is zero or only very low and the heat transfer limited.
  • a better heat exchange is achieved by turbulent flow.
  • the slat is partially slotted and bent tab-like outwards on the slots.
  • the flow of the gaseous medium breaks off at the slot and, as start-up flow, first has to rest against the lamellar surface. Especially in the area of this start-up flow, the highest local heat transfers are achieved.
  • frost can deposit on the lamellar surface, which adds the slats to the slats.
  • frequent defrosting operations are therefore necessary to remove the frost.
  • slotted lamellae which are used for heating a gaseous medium, can become clogged with dirt. These heat exchangers must then be cleaned consuming.
  • the object of the present invention is to provide a fin for a fin heat exchanger and a fin heat exchanger, with the help of this disadvantage of the prior art can be avoided and allow efficient heat exchange.
  • a lamella according to the invention has an embossing which has a serrated profile in the flow direction of the gaseous medium, the is shaped so that at the tips of the teeth a stall occurs to produce a turbulent flow pattern.
  • the jagged profile may have different configurations. Particularly effective and easy to produce is an at least partially periodic profile, which also simplifies the installation of the individual fins of a fin heat exchanger.
  • the period P and the embossed height PH measured between two oppositely pointing tips of the serrated profile are in a predetermined relationship to one another.
  • the quotient between imprint height and period is advantageously between 0.2 and 0.25. This area ensures that the "valleys" between two points are not so deep that too much dead space is created, in which no flow occurs.
  • the flanks of the tines are steep enough to ensure the torrential flow at the tines.
  • a lamellar heat exchanger with lamellae according to the invention is particularly efficient if the imprint height PH is greater than 2 mm, in particular in a range between 2.2 mm and 2.4 mm. This measure of embossing height is particularly effective in forming turbulent flow, especially at a typical gaseous medium flow rate of 1.5 to 3.5 m / s.
  • a plate heat exchanger according to the invention is characterized by a plurality of lamellae arranged in parallel in accordance with the invention and has, inter alia, the advantages already described with reference to the individual lamellae.
  • Laminated heat exchangers can be interspersed by heat transfer tubes, the heat with the lamellae exchange these z. B. to cool. It may be a single heat transfer tube z. B. serpentine is guided by the slats or to a plurality of parallel, individual heat transfer tubes. Likewise, individual heat transfer tubes may be connected outside of the parallel slats by corresponding connections to a serpentine tube. In the present text these are Alternatives include when generally speaking of heat transfer tubes.
  • the inventive design of the slat shape can be used in fin heat exchangers, in which the heat transfer tubes are guided in a rectangular grid or offset from one another by the slats.
  • the heat transfer tubes are arranged offset to one another such that three adjacent passages for heat transfer tubes form an approximately isosceles triangle.
  • the ratio of the diameter of a heat transfer tube or a passage provided therefor to the length of a limb of the triangle e.g. between 0.25 and 0.33 are chosen.
  • heaters for defrosting the fins there may be provided heaters for defrosting the fins.
  • heating rod tubes or heating rods can be guided by the slats. Through heating pipes, a hot medium can be sent to defrost the slats.
  • Heating rods can be used for the same purpose e.g. be electrically heated.
  • heating rod tubes are used for the simple introduction of heating elements.
  • the heating rod tubes, heating tubes or heating rods between each two heat transfer tubes whose connecting line is oblique to the flow direction In the production of such a finned heat exchanger The slat can be easily cut to the desired size.
  • a fin heat exchanger according to the invention for cooling, in particular of air, since it can be particularly easy to frost formation.
  • Fig. 1 the detail of a disk set of a fin heat exchanger is shown, which will be described below using the example of an air cooler.
  • the disk pack consists of a large number of disks, of which only three are shown here.
  • air is passed through the finned heat exchanger, which cools at the fins 1, 3, 5.
  • These are interspersed with heat transfer tubes that dissipate heat from the fins and give off to a coolant flowing in the tubes.
  • the heat transfer tubes are not shown in FIG. 1 for the sake of clarity.
  • up-facing teeth 9 are not necessarily all provided with a reference numeral.
  • the individual lamellae are embossed.
  • the embossing is periodic at least insofar that always three prongs 9 are arranged directly next to each other.
  • Between the in Fig. 1 upwardly pointing serrations 9 are down-facing spikes 11.
  • Only between individual up-facing spikes is a narrow horizontal Area 12 in the field of Edelstab be Replacementen 17 (see Fig. 3), for example, to facilitate the drainage of condensation from the lamella.
  • FIG. 2 shows a lateral plan view of the section of the lamella block.
  • FIG. The distance between two upwardly pointing serrations 9 is designated as period P.
  • the spacing of the lamellae is designated A, while the embossing height, which indicates the height between an upwardly pointing and a downwardly pointing tip, is designated by PH. 13 denotes the example of the tine 10, the formation of turbulent flow, which is generated by the tearing of the flow at the top of the adjacent tine 10.
  • Fig. 3 shows the top view of a lamella, here also the passages 15 for the heat transfer tubes and bushings 17 are shown for Schustabrohre.
  • the heat transfer tubes 15 are guided through the heat transfer tube bushings, which are to remove heat in the described cooling operation of the slats.
  • the flare-free bushings for the Schustabrohre Schustabrohre are also performed in a manner not shown, which have been pressed by internal expansion after pushing through the slats.
  • By Schustabrohre 17 heating elements can be easily inserted, with the help of the lamella z. B. can be defrosted to remove frost.
  • the heat transfer tubes are pressed by internal expansion in the openings of the slats.
  • the heat transfer tube ducts 15 are arranged in a grid such that three adjacent heat transfer tubes form an isosceles triangle.
  • the ratio of the diameter of a heat transfer tube or passage 15 to the length of a leg of the triangle is e.g. between 0.25 and 0.33.
  • the Schustabrohr be arrangementen 17 are each between two heat transfer tube ducts 15th
  • the design of the plate heat exchanger with serrated lamellae has proven to be particularly favorable for so-called offset systems in which the individual heat transfer tube bushings as shown in Fig. 3 are not arranged in a rectangular grid. In contrast to an aligned arrangement here the formation of a turbulent flow is further supported.
  • FIG. 4 shows a side view in the viewing direction IV, as indicated in FIG. 3.
  • the bushings 17 for the heating elements have no Aufbördelept.
  • the flanges of the heat transfer tube bushings 15 are designated 16.
  • An inventive plate heat exchanger is z. B. used as an air cooler.
  • coolant is conveyed in a conventional manner.
  • the air to be cooled 7 is sent between the slats through the disk pack.
  • the air flow is deflected and breaks off at the tips. This results in a turbulent flow 13, which is exemplified at a tine 10 of the blade 3 in Fig. 2.
  • the turbulent air flow must first rest against the lamellar surface. Heat is transferred very effectively during this approach.
  • the generation of the turbulent air flow 13 prevents the formation of a laminar flow, which would be very inefficient for heat transfer, because directly on the blade itself a standing air layer would be present.
  • the embossing height is selected for an air velocity of 1.5 to 3.5 m / s, for example, between 2.2 mm to 2.4 mm and the fin spacing between 3 mm and 8 mm.
  • the period is chosen such that the quotient between imprint height and period lies between 0.2 and 0.25.
  • the particular configuration of the lamellae according to the invention and of the lamellar heat exchanger according to the invention ensures optimal formation of turbulent flow on the lamellar surface, without the risk that, as in the prior art, slits in the lamellae are added by frost. Therefore, the system according to the invention allows effective operation over longer periods of time and reduces the necessary number of defrosting operations.
  • the appropriate selection of the dimensions of the embossed lamella leads to a particularly effective heat exchange between the lamella and the flowing medium.
  • the heating rod tubes or heating tubes can be compressed by widening in the openings 17. So can be achieved with compressed tubes during heating a higher fin temperature at the same time lower surface temperature of the Edelstabrohres or heating tube. As a result, undesired vapor formation on the heating rod tube or heating tube during defrosting is reduced.

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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)
EP06001939.5A 2005-02-04 2006-01-31 Echangeur de chaleur à lamelles Active EP1701124B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005005293A DE102005005293A1 (de) 2005-02-04 2005-02-04 Lamellenwärmetauscher und Lamelle dafür

Publications (2)

Publication Number Publication Date
EP1701124A1 true EP1701124A1 (fr) 2006-09-13
EP1701124B1 EP1701124B1 (fr) 2017-11-08

Family

ID=36579256

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06001939.5A Active EP1701124B1 (fr) 2005-02-04 2006-01-31 Echangeur de chaleur à lamelles

Country Status (2)

Country Link
EP (1) EP1701124B1 (fr)
DE (1) DE102005005293A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014081101A (ja) * 2012-10-15 2014-05-08 Mitsubishi Electric Corp 冷却器および保冷庫

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2529215A (en) 1947-11-10 1950-11-07 Trane Co Heat exchanger
DE1751244A1 (de) * 1967-10-27 1971-06-09 Alfa Laval Ab Waermeaustauscher fuer den Waermeuebergang zwischen einer Fluessigkeit und einem Gas oder Luft
DE1751464A1 (de) 1967-06-08 1971-07-15 Air Preheater Waermetauscher-Baugruppe
US4449581A (en) * 1982-08-30 1984-05-22 Chromalloy American Corporation Heat exchanger fin element with dog-bone type pattern of corrugations
EP0469150A1 (fr) 1990-02-20 1992-02-05 Nauchno-Proidsvodstevennoe Obiedinenie Po Traktorostroeniju Ensemble de toles pour echangeur thermique a plaques et a tubes dote de canaux diffuseurs-convergents et matrice de rotor de fabrication des plaques dudit ensemble
WO1994027105A1 (fr) 1993-05-19 1994-11-24 Norsk Hydro A.S Echangeur de chaleur forme par assemblage mecanique, a pression interne elevee
DE19709176A1 (de) 1997-03-06 1998-09-17 Juergen Lessing Lamellenwärmetauscher
US5927393A (en) * 1997-12-11 1999-07-27 Heatcraft Inc. Heat exchanger fin with enhanced corrugations
US20020023744A1 (en) * 1999-12-10 2002-02-28 Kwang-Il Kim Manufacturing method for split heat exchanger having oval tubes in zigzag pattern
US20040251016A1 (en) 2003-05-28 2004-12-16 Sai Kee Oh Heat exchanger

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2530064A1 (de) * 1975-07-05 1977-01-27 Volkswagenwerk Ag Luftlamelle fuer einen leichtmetall- waermetauscher
WO1985002671A1 (fr) * 1983-12-07 1985-06-20 Licencia Találmányokat Értékesito^" Vállalat Procede et installation d'echange thermique recuperateur pour retirer des impuretes d'air chaud pollue, en particulier de gaz de fumees, et pour reduire la corrosion des cheminees
DE3409608A1 (de) * 1984-03-15 1985-09-19 Klöckner-Humboldt-Deutz AG, 5000 Köln Aus einzelnen platten zusammengesetztes netz eines kreuzstromwaermetauschers
DE8628175U1 (de) * 1986-10-22 1986-12-18 Thermal-Werke, Wärme-, Kälte-, Klimatechnik GmbH, 6909 Walldorf Lamelle
DE3918610A1 (de) * 1989-06-07 1990-12-13 Guentner Gmbh Hans Luftgekuehlter waermeaustauscher
FR2650382A1 (fr) * 1989-07-27 1991-02-01 Const Aero Navales Echangeur a plaques a circuits etanches
DE19813119A1 (de) * 1998-03-25 1999-10-07 Inst Energetik Und Umwelt Ggmb Turbulenzwärmerückgewinner und Anwendungen desselben
DE29916493U1 (de) * 1999-09-14 2000-04-06 FPL Wärmerückgewinnung-Lüftung GmbH, 38889 Blankenburg Vorrichtung für den Wärmetausch im Kreuzstromprinzip

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2529215A (en) 1947-11-10 1950-11-07 Trane Co Heat exchanger
DE1751464A1 (de) 1967-06-08 1971-07-15 Air Preheater Waermetauscher-Baugruppe
DE1751244A1 (de) * 1967-10-27 1971-06-09 Alfa Laval Ab Waermeaustauscher fuer den Waermeuebergang zwischen einer Fluessigkeit und einem Gas oder Luft
US4449581A (en) * 1982-08-30 1984-05-22 Chromalloy American Corporation Heat exchanger fin element with dog-bone type pattern of corrugations
EP0469150A1 (fr) 1990-02-20 1992-02-05 Nauchno-Proidsvodstevennoe Obiedinenie Po Traktorostroeniju Ensemble de toles pour echangeur thermique a plaques et a tubes dote de canaux diffuseurs-convergents et matrice de rotor de fabrication des plaques dudit ensemble
WO1994027105A1 (fr) 1993-05-19 1994-11-24 Norsk Hydro A.S Echangeur de chaleur forme par assemblage mecanique, a pression interne elevee
DE19709176A1 (de) 1997-03-06 1998-09-17 Juergen Lessing Lamellenwärmetauscher
US5927393A (en) * 1997-12-11 1999-07-27 Heatcraft Inc. Heat exchanger fin with enhanced corrugations
US20020023744A1 (en) * 1999-12-10 2002-02-28 Kwang-Il Kim Manufacturing method for split heat exchanger having oval tubes in zigzag pattern
US20040251016A1 (en) 2003-05-28 2004-12-16 Sai Kee Oh Heat exchanger

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014081101A (ja) * 2012-10-15 2014-05-08 Mitsubishi Electric Corp 冷却器および保冷庫

Also Published As

Publication number Publication date
EP1701124B1 (fr) 2017-11-08
DE102005005293A1 (de) 2006-08-10

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