EP0253167B1 - Heat-exchanger, more particularly evaporator for refrigerant - Google Patents

Heat-exchanger, more particularly evaporator for refrigerant Download PDF

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Publication number
EP0253167B1
EP0253167B1 EP87109108A EP87109108A EP0253167B1 EP 0253167 B1 EP0253167 B1 EP 0253167B1 EP 87109108 A EP87109108 A EP 87109108A EP 87109108 A EP87109108 A EP 87109108A EP 0253167 B1 EP0253167 B1 EP 0253167B1
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EP
European Patent Office
Prior art keywords
pipe
flat
pipes
widened
region
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.)
Expired
Application number
EP87109108A
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German (de)
French (fr)
Other versions
EP0253167A1 (en
Inventor
Dieter Dipl.-Ing. Bauer
Wolfgang Hesse
Werner Oelichmann
Herbert Schrade
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.)
Mahle Behr GmbH and Co KG
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Behr GmbH and Co KG
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Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Priority to AT87109108T priority Critical patent/ATE43707T1/en
Publication of EP0253167A1 publication Critical patent/EP0253167A1/en
Application granted granted Critical
Publication of EP0253167B1 publication Critical patent/EP0253167B1/en
Expired legal-status Critical Current

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Classifications

    • 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
    • F28D1/053—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 straight
    • F28D1/0535—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 straight the conduits having a non-circular cross-section
    • F28D1/05358—Assemblies of conduits connected side by side or with individual headers, e.g. section type radiators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C37/00—Manufacture of metal sheets, bars, wire, tubes or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape
    • B21C37/06—Manufacture of metal sheets, bars, wire, tubes or like semi-manufactured products, not otherwise provided for; Manufacture of tubes of special shape of tubes or metal hoses; Combined procedures for making tubes, e.g. for making multi-wall tubes
    • B21C37/15—Making tubes of special shape; Making tube fittings
    • B21C37/22—Making finned or ribbed tubes by fixing strip or like material to tubes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
    • B21D53/08—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of both metal tubes and sheet metal
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/025—Tubular elements of cross-section which is non-circular with variable shape, e.g. with modified tube ends, with different geometrical features
    • 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
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0221—Header boxes or end plates formed by stacked elements
    • 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

Definitions

  • the invention relates to a heat exchanger, in particular a refrigerant evaporator according to the preamble of claim 1.
  • Heat exchangers of this type have already been proposed by the applicant's older DE application P 35 02 619.7.
  • Heat exchangers of this type have the advantage that, in contrast to heat exchangers with disk-shaped heat exchange bodies, the flat tubes do not have to be soldered or glued over their entire length, but only at their ends and at the connection openings, so that a significant simplification of manufacture can be achieved. Since in the proposed designs the flat tubes lie directly against one another with widened end parts, the arrangement of separate connecting tube sockets is also superfluous.
  • each flat tube extends to the narrow longitudinal sides in the shape of an ogive to the bends on the longitudinal edges of the flat tube, so that it is then possible to extend the widened part over the entire tube width .
  • Due to the pointed arch-shaped extension of the expansion towards the end regions the pipe material is stretched less there than in the middle of the parallel pipe walls. Overstretching with the risk of crack formation is therefore avoided.
  • This configuration then makes it possible in a simple manner to insert turbulence inserts with the width of the flat tubes axially into the open tubes and then to fix them in a known manner. It is also advantageous that no deformation occurs in the narrow end areas, where the weld seam is generally located. This measure enables a higher heat exchange performance compared to pipes in which the turbulence insert does not fill the full pipe width.
  • the expanded part extends only over part of the width of the flat tubes, but then a certain trick must be provided to provide the full-width turbulence insert in the flat tube.
  • the turbulence insert is first inserted in a zigzag-shaped corrugated shape into the central region of an oval tube and that this tube is then pressed in parallel and permanently deformed in the region in which the turbulence insert is seated to an extent that the turbulence insert presses out of its corrugated shape into a flat, elongated shape.
  • the flat tube is therefore only finished after inserting a turbulence insert.
  • This method has proven to be very beneficial. It has the advantage that the turbulence insert used in this way is also fixed in the flat tube after the deformation of the plate-shaped central part of the initially oval tube.
  • FIG. 1 to 3 show a heat exchanger (1) which is constructed from a plurality of flat tubes (2) which are placed directly next to one another and with their axes (5) aligned parallel to one another.
  • the flat tubes (2) are placed next to one another with widened parts (2a, 2b) provided at the ends and take up heat exchange fins (3) between them, which for better heat dissipation of the in the drawing plane in Fig. 1 on the flat tubes (2nd ) flowing past serve a heat exchange medium, especially air.
  • the widened part (2a) or (2b) of the flat tubes (2) is closed in the exemplary embodiment by caps (10) inserted on the end face. These caps are in the lower two tubes of FIG. 3rd omitted. It can be seen that the middle part (2c) of the flat tubes (2) is considerably narrower than the widened part (2a) and that the flat tubes provided with parallel walls have bends (8) in the area of their longitudinal edges, each of which extends into the parallel walls ( 4) pass over. It can also be seen from the figures that the widened part (2a) or analogously (2b) has openings (6, 6 ') in the parallel wall parts (4').
  • Fig. 2 shows that the parallel walls (4 ') of the expanded part (2a) run approximately in the area between the boundary lines (11) and that from these boundary lines to the outside, where less material is deformed by the ogival shape, expedient end wall parts (12) which run obliquely outwards remain, while in the area between the boundary lines (11) there is a lower lying area.
  • This configuration ensures that even in the middle area, ie. H. in the area of the walls (4 ') the material stretch can be kept within the permissible range.
  • FIG. 4 to 7 show another embodiment of a flat tube for a refrigerant evaporator, which is also provided with a turbulence insert (70), but is produced in a different way.
  • the end regions of a flat tube are not widened, but instead, as the upper part of FIG. 4, a tube (20 ') with an oval cross section is selected as the starting material, the walls (40) of which are at a distance (b) from one another .
  • This oval tube has the length (B ').
  • a turbulence insert (70 ') in corrugated or zigzag shape is now inserted into an oval tube (20') designed in this way.
  • This turbulence insert (70 ') has an overall length which is dimensioned such that it corresponds to the length (B) of the deformed part after the deformation of the tube (20') described below.
  • This turbulence insert (70 ') with the length (B) is therefore, as the upper part of FIG. 4 shows, first inserted axially into the tube (20), to the extent that it occupies the area (21) (see FIG 5 and 6), which is then to be deformed. Once this has been done, this central region (21) is pressed together by rolling or pressing, in such a way that in this region the tube (20 ') receives the thickness (d) and the width (B).
  • This flat tube (20) designed in this way therefore has widened end regions which do not have the full width (B).
  • the turbulence insert (70) over the full length of the width (B), which, due to the deformation process, both assumes its extended position according to FIG. 4 and is secured axially in this position.
  • the parts (20a) and (20b) remaining as a result of this deformation process and widened with respect to the region (21) can be provided with openings similar to the openings (6) of the embodiment in FIGS. 1 to 3. In the exemplary embodiment, however, they are each provided with two openings (60) and (60 '), which, when placed one against the other, establish the connection between the individual flat tubes (20).
  • outlets (61) projecting outward at the openings (60) are produced, for example, by a suitable stamping process.
  • This embodiment then has the advantage that only one type of flat tube (20) is required to build a flat tube evaporator or flat tube heat exchanger, which are soldered to one another.
  • the nozzles (61) are dimensioned so that they fit into the openings (60 ').
  • the open pipe ends are closed by inserted caps (10).

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

Abstract

1. Heat exchanger, particularly a cooling medium evaporator, consisting of a plurality of flat pipes parallel with one another, but arranged with a space between them and joined together, between which pipes a plurality of fins have been fitted to increase the heat exchange surface, said pipes being provided at both their end regions with a widened part of the pipe wall, being laid by means of this part directly on a corresponding part of the adjacent pipe and connected therewith, particularly by soldering, there being provided in each widened part, transversally to the longitudinal axis of the flat pipes, connection openings with the adjacent flat pipe or to the adjacent group of pipes, characterized in that the widened part (2a, 2b) of each flat pipe (2) extends over the entire width of the pipe, but, towards the narrow longitudinal sides (2') runs in the form of a pointed arch into the arc-shaped parts (8) of the flat pipe, and in that, in the region (20, 21) of each flat pipe (2, 20) lying between the widened parts (2a, 2b, 20a, 20b) of the pipe wall (4) turbulence inserts (7, 70) are provided which fill up the entire pipe width (B).

Description

Die Erfindung betrifft einen Wärmetauscher, insbesondere einen Kältemittel-Verdampfer nach dem Oberbegriff des Patentanspruchs 1.The invention relates to a heat exchanger, in particular a refrigerant evaporator according to the preamble of claim 1.

Wärmetauscher dieser Art sind durch die ältere DE-Anmeldung P 35 02 619.7 der Anmelderin bereits vorgeschlagen worden. Wärmetauscher dieser Art weisen den Vorteil auf, daß im Gegensatz zu Wärmetauschern mit scheibenförmigen Wärmetauschkörpern die Flachrohre nicht über ihre gesamte Länge, sondern nur an ihren Enden und an den Verbindungsöffnungen verlötet oder verklebt werden müssen, so daß eine bedeutende Herstellungsvereinfachung erzielt werden kann. Da bei den vorgeschlagenen Bauarten die Flachrohre unmittelbar mit aufgeweiteten Endteilen aneinander anliegen, ist auch die Anordnung gesonderter Verbindungsrohrstutzen überflüssig.Heat exchangers of this type have already been proposed by the applicant's older DE application P 35 02 619.7. Heat exchangers of this type have the advantage that, in contrast to heat exchangers with disk-shaped heat exchange bodies, the flat tubes do not have to be soldered or glued over their entire length, but only at their ends and at the connection openings, so that a significant simplification of manufacture can be achieved. Since in the proposed designs the flat tubes lie directly against one another with widened end parts, the arrangement of separate connecting tube sockets is also superfluous.

Nachteilig ist in gewisser Hinsicht bei solchen Wärmetauscherbauarten jedoch, daß sich die Aufweitungen an den Rohrenden nicht über die ganze Rohrbreite erstrecken lassen, weil bei der Herstellung einer solchen Aufweitung Risse durch Materialüberstreckung, insbesondere im Bereich der bogenförmigen Wände an den Längskanten der Flachrohre ergeben. Das führt dazu, daß bei den bekannten Bauarten innerhalb der Flachrohre keine Einsätze vorgesehen werden können, wie sie beispielsweise von Ölkühlern in der Form von Turbulenzeinlagen bekannt sind. Die nicht über die ganze Breite durchgehende Aufweitung bei den vorgeschlagenen Wärmetauschern würde nur das Einschieben von Turbulenzeinlagen erlauben, die nur einen Teil der Rohrbreite ausfüllen. Das Wärmeaustauschmittel würde in einem solchen Fall an den Turbulenzeinlagen außen vorbeiströmen, so daß der den Wärmeübergang verbessernde Effekt einer Turbulenzeinlage nicht erfüllt wäre.In some respects, however, it is disadvantageous with such types of heat exchanger that the widenings at the pipe ends cannot extend over the entire pipe width, because in the production of such a widening cracks result from material overstretching, in particular in the region of the arcuate walls on the longitudinal edges of the flat pipes. The result of this is that, in the known designs, no inserts can be provided within the flat tubes, as are known, for example, from oil coolers in the form of turbulence inserts. The widening which is not continuous over the entire width in the case of the proposed heat exchangers would only allow the insertion of turbulence inserts which only fill part of the tube width. In such a case, the heat exchange medium would flow past the turbulence inserts, so that the effect of a turbulence insert improving the heat transfer would not be fulfilled.

Es ist daher die Aufgabe der Erfindung, Wärmetauscher der eingangs genannten Art so auszubilden, daß in dem zwischen den aufgeweiteten Teilen der Rohre liegenden Bereich Turbulenzeinlagen vorgesehen werden können, welche die gesamte Rohrbreite ausfüllen.It is therefore the object of the invention to design heat exchangers of the type mentioned at the outset in such a way that turbulence inserts which fill the entire pipe width can be provided in the region lying between the widened parts of the pipes.

Dies kann gemäß dem Patentanspruch 1 dadurch erreicht werden, daß der aufgeweitete Teil jedes Flachrohres sich zu den schmalen Längsseiten hin spitzbogenförmig zu den Krümmungsbogen an den Längskanten des Flachrohres hin erstreckt, so daß es dann möglich ist, den aufgeweiteten Teil über die gesamte Rohrbreite zu erstrecken. Durch das spitzbogenförmige Auslaufen der Ausweitung zu den Endbereichen hin wird dort das Rohrmaterial weniger gestreckt als in der Mitte der parallelen Rohrwände. Ein Überstrecken mit der Gefahr der Rißbildung unterbleibt daher. Durch diese Ausgestaltung wird es dann in einfacher Weise möglich, Turbulenzeinlagen mit der Breite der Flachrohre axial in die offenen Rohre einzuschieben und dann in bekannter Weise zu fixieren. Vorteilhaft ist auch, daß in den schmalen Endbereichen, wo im allgemeinen die Schweißnaht liegt, keine Verformung auftritt. Durch diese Maßnahme wird eine höhere Wärmetauschleistung gegenüber Rohren ermöglicht, bei denen die Turbulenzeinlage nicht die volle Rohrbreite ausfüllt.This can be achieved according to claim 1 in that the widened part of each flat tube extends to the narrow longitudinal sides in the shape of an ogive to the bends on the longitudinal edges of the flat tube, so that it is then possible to extend the widened part over the entire tube width . Due to the pointed arch-shaped extension of the expansion towards the end regions, the pipe material is stretched less there than in the middle of the parallel pipe walls. Overstretching with the risk of crack formation is therefore avoided. This configuration then makes it possible in a simple manner to insert turbulence inserts with the width of the flat tubes axially into the open tubes and then to fix them in a known manner. It is also advantageous that no deformation occurs in the narrow end areas, where the weld seam is generally located. This measure enables a higher heat exchange performance compared to pipes in which the turbulence insert does not fill the full pipe width.

Bei einer anderen Ausführungsform gemäß dem Patentanspruch 4 ist es auch möglich, daß sich der aufgeweitete Teil nur über einen Teil der Breite der Flachrohre erstreckt, wobei dann allerdings ein gewisser Kniff vorgesehen werden muß, um die Turbulenzeinlage in voller Breite in dem Flachrohr vorzusehen. Dies wird dadurch erreicht, daß die Turbulenzeinlage zunächst in zick-zack-förmig gewellter Form in den mittleren Bereich eines ovalen Rohres eingeschoben wird und daß dieses Rohr dann in dem Bereich, in dem die Turbulenzeinlage sitzt, parallel zusammengedrückt und bleibend verformt wird, und zwar in einem Ausmaß, daß sich die Turbulenzeinlage aus ihrer gewellten Form in eine flache gestreckte Form drückt. Bei dieser Methode wird daher das Flachrohr erst nach dem Einsetzen einer Turbulenzeinlage fertiggestellt. Diese Methode hat sich als sehr vorteilhaft erwiesen. Sie bringt den Vorteil mit sich, daß die so eingesetzte Turbulenzeinlage nach der Verformung des plattenförmigen Mittelteiles des zunächst ovalen Rohres auch in dem Flachrohr fixiert ist.In another embodiment according to claim 4, it is also possible that the expanded part extends only over part of the width of the flat tubes, but then a certain trick must be provided to provide the full-width turbulence insert in the flat tube. This is achieved in that the turbulence insert is first inserted in a zigzag-shaped corrugated shape into the central region of an oval tube and that this tube is then pressed in parallel and permanently deformed in the region in which the turbulence insert is seated to an extent that the turbulence insert presses out of its corrugated shape into a flat, elongated shape. With this method, the flat tube is therefore only finished after inserting a turbulence insert. This method has proven to be very beneficial. It has the advantage that the turbulence insert used in this way is also fixed in the flat tube after the deformation of the plate-shaped central part of the initially oval tube.

In der nachfolgenden Beschreibung werden an Hand der Zeichnungen zwei Ausführungsbeispiele der Erfindung beschrieben. Es zeigen:

  • Fig. 1 einen schematischen Längsschnitt durch einen Kältemittel-Verdampfer, der aus unmittelbar aneinandergesetzten Flachrohren aufgebaut ist,
  • Fig. 2 die Seitenansicht des Kältemittel-Verdampfers der Fig. 1 in einer Teilansicht in Richtung des Pfeiles II,
  • Fig. 3 die Draufsicht auf den Kältemittel-Verdampfer der Fig. 1 in Richtung des Pfeiles 111, wobei nur ein Teil der oberen Stirnenden der Rohre in offenem Zustand gezeigt ist,
  • Fig. 4 die schematische Darstellung des Herstellungsvorganges für ein Flachrohr, bei dem die Turbulenzeinlage vor dem Verformen des Mittelteiles eingesetzt ist,
  • Fig. 5 die teilweise aufgeschnittene Seitenansicht eines nach dem in Fig. 4 skizzierten Verfahren hergestellten Flachrohres,
  • Fig. 6 einen Teilschnitt durch das Flachrohr der
  • Fig. 5 längs der Linie VI-VI und
  • Fig. 7 die Draufsicht auf das Rohr der Fig. 5 in Richtung des Pfeiles VII.
In the following description, two exemplary embodiments of the invention are described with reference to the drawings. Show it:
  • 1 shows a schematic longitudinal section through a refrigerant evaporator which is constructed from flat tubes placed directly next to one another,
  • 2 shows the side view of the refrigerant evaporator of FIG. 1 in a partial view in the direction of arrow II,
  • 3 shows the top view of the refrigerant evaporator of FIG. 1 in the direction of arrow 111, only part of the upper end faces of the tubes being shown in the open state,
  • 4 shows the schematic representation of the manufacturing process for a flat tube, in which the turbulence insert is inserted before the deformation of the central part,
  • 5 shows the partially cut-away side view of a flat tube produced by the method outlined in FIG. 4,
  • Fig. 6 shows a partial section through the flat tube of the
  • Fig. 5 along the line VI-VI and
  • Fig. 7 is a plan view of the tube of FIG. 5 in the direction of arrow VII.

In den Fig. 1 bis 3 ist ein Wärmetauscher (1) gezeigt, der aus mehreren unmittelbar aneinandergesetzten und mit ihren Achsen (5) parallel zueinander ausgerichteten Flachrohren (2) aufgebaut ist. Die Flachrohre (2) sind mit aufgeweiteten, jeweils an den Enden vorgesehenen Teilen (2a, 2b) aneinandergesetzt und nehmen zwischen sich Wärmetauschrippen (3) auf, die für eine bessere Wärmeabgabe des in Fig. 1 in die Zeichenebene hinein an den Flachrohren (2) vorbeiströmenden einen Wärmetauschmediums, insbesondere Luft, dienen.1 to 3 show a heat exchanger (1) which is constructed from a plurality of flat tubes (2) which are placed directly next to one another and with their axes (5) aligned parallel to one another. The flat tubes (2) are placed next to one another with widened parts (2a, 2b) provided at the ends and take up heat exchange fins (3) between them, which for better heat dissipation of the in the drawing plane in Fig. 1 on the flat tubes (2nd ) flowing past serve a heat exchange medium, especially air.

Der aufgeweitete Teil (2a) bzw. (2b) der Flachrohre (2) ist beim Ausführungsbeispiel durch stirnseitig eingesetzte Kappen (10) verschlossen. Diese Kappen sind bei den unteren beiden Rohren der Fig. 3 weggelassen. Man erkennt, daß der mittlere Teil (2c) der Flachrohre (2) wesentlich schmäler ist als der aufgeweitete Teil (2a) und daß die mit parallelen Wänden versehenen Flachrohre im Bereich ihrer Längskanten Krümmungsbogen (8) besitzen, die jeweils in die parallelen Wände (4) übergehen. Aus den Fig. ist auch zu erkennen, daß der aufgeweitete Teil (2a) bzw. analog (2b) Öffnungen (6, 6') in den parallelen Wandteilen (4') besitzt. Diese parallelen Wandteile (4') gehen nach unten zu den Wänden (4) in einen Übergangsbereich (9) über, der etwa senkrecht, sowohl auf den Wänden (4') als auch auf den Wänden (4) steht. Dieser Übergangsbereich (9) wird zu den beiden Längskanten der Rohre, d. h. jeweils zu den Rohrbogen (8) hin kleiner, was dadurch bewirkt wird, daß die zunächst parallelen Wände (4') zu den Rohrbögen (8) hin spitzbogenförmig verlaufen. Die Materialdehnung beim Aufweiten der Teile (2a, 2b) wird daher zu den Bereichen der Rohrbögen (8) hin immer kleiner und im Bereich der Rohrbögen (8) zu Null. Durch diese spitzbogenförmige Aufweitung, die mit entsprechenden Werkzeugen vorgenommen werden kann, kann die Gefahr einer Rißbildung im Bereich der Rohrbögen vollkommen vermieden werden. Die Rohre lassen sich, wie Fig. 3 zeigt, gut aneinandersetzen und bieten den Vorteil, daß eine Turbulenzeinlage (7) mit der gesamten Breite (B) der Flachrohre (2) axial in die Flachrohre eingeschoben und dann verankert werden kann.The widened part (2a) or (2b) of the flat tubes (2) is closed in the exemplary embodiment by caps (10) inserted on the end face. These caps are in the lower two tubes of FIG. 3rd omitted. It can be seen that the middle part (2c) of the flat tubes (2) is considerably narrower than the widened part (2a) and that the flat tubes provided with parallel walls have bends (8) in the area of their longitudinal edges, each of which extends into the parallel walls ( 4) pass over. It can also be seen from the figures that the widened part (2a) or analogously (2b) has openings (6, 6 ') in the parallel wall parts (4'). These parallel wall parts (4 ') go down to the walls (4) into a transition area (9) which is approximately vertical, both on the walls (4') and on the walls (4). This transition area (9) becomes smaller towards the two longitudinal edges of the pipes, ie towards the pipe bends (8), which is caused by the fact that the initially parallel walls (4 ') run towards the pipe bends (8) in the shape of an ogive. The material expansion when the parts (2a, 2b) expand is therefore becoming ever smaller towards the areas of the pipe bends (8) and zero in the area of the pipe bends (8). By means of this pointed arch-shaped widening, which can be carried out with appropriate tools, the risk of crack formation in the area of the pipe bends can be completely avoided. The tubes can, as Fig. 3 shows, put together well and offer the advantage that a turbulence insert (7) with the entire width (B) of the flat tubes (2) can be inserted axially into the flat tubes and then anchored.

Fig. 2 zeigt, daß die parallelen Wände (4') des aufgeweiteten Teiles (2a) in etwa im Bereich zwischen den Grenzlinien (11) verlaufen und daß von diesen Grenzlinien aus nach außen, wo durch die spitzbogenförmige Ausbildung weniger Material verformt wird, zweckmäßig auch schräg nach außen oben verlaufende Stirnwandteile (12) verbleiben, während in dem Bereich zwischen den Grenzlinien (11) ein tiefer liegender Bereich vorhanden ist. Diese Ausgestaltung sorgt dafür, daß auch im mittleren Bereich, d. h. im Bereich der Wandungen (4') die Materialstreckung im zulässigen Rahmen gehalten werden kann.Fig. 2 shows that the parallel walls (4 ') of the expanded part (2a) run approximately in the area between the boundary lines (11) and that from these boundary lines to the outside, where less material is deformed by the ogival shape, expedient end wall parts (12) which run obliquely outwards remain, while in the area between the boundary lines (11) there is a lower lying area. This configuration ensures that even in the middle area, ie. H. in the area of the walls (4 ') the material stretch can be kept within the permissible range.

Die Fig. 4 bis 7 zeigen eine andere Ausführungsform eines Flachrohres für einen Kältemittel-Verdampfer, das ebenfalls mit einer Turbulenzeinlage (70) versehen ist, aber auf andere Weise hergestellt wird. Bei dieser Ausführungsform werden die Endbereiche eines Flachrohres nicht aufgeweitet, sondern es wird, wie der obere Teil der Fig. 4 zeigt, als Ausgangsmaterial ein Rohr (20') mit ovalem Querschnitt gewählt, dessen Wandungen (40) den Abstand (b) zueinander aufweisen. Dieses ovale Rohr hat die Länge (B'). In ein so ausgestaltetes ovales Rohr (20') wird nun eine Turbulenzeinlage (70') in gewellter oder Zick-Zack-Form eingelegt. Diese Turbulenzeinlage (70') weist insgesamt eine Länge auf, die so bemessen ist, daß sie nach der im folgenden beschriebenen Verformung des Rohres (20') der Länge (B) des verformten Teiles entspricht. Diese Turbulenzeinlage (70') mit der Länge (B) wird daher zunächst, wie der obere Teil der Fig. 4 zeigt, axial in das Rohr (20) eingeschoben, und zwar so weit, daß sie den Bereich (21) einnimmt (s. Fig. 5 und 6), der anschließend verformt werden soll. Ist dies geschehen, so wird dieser mittlere Bereich (21) durch Walzen oder Pressen zusammengedrückt, und zwar so, daß in diesem Bereich das Rohr (20') die Stärke (d) erhält und die Breite (B) aufweist. Dieses so ausgebildete Flachrohr (20) besitzt daher aufgeweitete Endbereiche, die nicht die volle Breite (B) besitzen. In dem Bereich (21) aber sitzt über die volle Länge der Breite (B) die Turbulenzeinlage (70), die durch den Verformungsvorgang sowohl ihre gestreckte Lage gemäß Fig. 4 einnimmt, als auch axial in dieser Lage gesichert ist. Die durch diesen Verformungsvorgang verbleibenden und gegenüber dem Bereich (21) aufgeweiteten Teile (20a) und (20b) können mit Öffnungen ähnlich den Öffnungen (6) der Ausführungsform der Fig. 1 bis 3 versehen sein. Sie sind beim Ausführungsbeispiel jedoch jeweils mit zwei Öffnungen (60) bzw. (60') versehen, die beim Aneinandersetzen die Verbindung zwischen den einzelnen Flachrohren (20) herstellen. Beim Ausführungsbeispiel ist außerdem noch dafür gesorgt, daß an den Öffnungen (60) nach außen vorstehende Stutzen (61) vorhanden sind, die beispielsweise durch einen geeigneten Ausprägevorgang hergestellt werden. Diese Ausführungsform weist dann den Vorteil auf, daß nur eine Sorte von Flachrohren (20) zum Aufbau eines Flachrohrverdampfers oder Flachrohrwärmetauschers nötig ist, die untereinander verlötet werden. Die Stutzen (61) sind dabei so bemessen, daß sie in die Öffnungen (60') hereinpassen. Die offenen Rohrenden werden, wie auch bei anderen Ausführungsformen, durch eingesetzte Kappen (10) verschlossen.4 to 7 show another embodiment of a flat tube for a refrigerant evaporator, which is also provided with a turbulence insert (70), but is produced in a different way. In this embodiment, the end regions of a flat tube are not widened, but instead, as the upper part of FIG. 4, a tube (20 ') with an oval cross section is selected as the starting material, the walls (40) of which are at a distance (b) from one another . This oval tube has the length (B '). A turbulence insert (70 ') in corrugated or zigzag shape is now inserted into an oval tube (20') designed in this way. This turbulence insert (70 ') has an overall length which is dimensioned such that it corresponds to the length (B) of the deformed part after the deformation of the tube (20') described below. This turbulence insert (70 ') with the length (B) is therefore, as the upper part of FIG. 4 shows, first inserted axially into the tube (20), to the extent that it occupies the area (21) (see FIG 5 and 6), which is then to be deformed. Once this has been done, this central region (21) is pressed together by rolling or pressing, in such a way that in this region the tube (20 ') receives the thickness (d) and the width (B). This flat tube (20) designed in this way therefore has widened end regions which do not have the full width (B). In the region (21), however, sits the turbulence insert (70) over the full length of the width (B), which, due to the deformation process, both assumes its extended position according to FIG. 4 and is secured axially in this position. The parts (20a) and (20b) remaining as a result of this deformation process and widened with respect to the region (21) can be provided with openings similar to the openings (6) of the embodiment in FIGS. 1 to 3. In the exemplary embodiment, however, they are each provided with two openings (60) and (60 '), which, when placed one against the other, establish the connection between the individual flat tubes (20). In the case of the exemplary embodiment, it is also ensured that outlets (61) projecting outward at the openings (60) are produced, for example, by a suitable stamping process. This embodiment then has the advantage that only one type of flat tube (20) is required to build a flat tube evaporator or flat tube heat exchanger, which are soldered to one another. The nozzles (61) are dimensioned so that they fit into the openings (60 '). As in other embodiments, the open pipe ends are closed by inserted caps (10).

Claims (7)

1. Heat exchanger, particularly a cooling medium evaporator, consisting of a plurality of flat pipes parallel with one another, but arranged with a space between them and joined together, between which pipes a plurality of fins have been fitted to increase the heat exchange surface, said pipes being provided at both their end regions with a widened part of the pipe wall, being laid by means of this part directly on a corresponding part of the adjacent pipe and connected therewith, particularly by soldering, there being provided in each widened part, transversally to the longitudinal axis of the flat pipes, connection openings with the adjacent flat pipe or to the adjacent group of pipes, characterized in that the widened part (2a, 2b) of each flat pipe (2) extends over the entire width of the pipe, but, towards the narrow longitudinal sides (2') runs in the form of a pointed arch into the arc-shaped parts (8) of the flat pipe, and in that, in the region (20, 21) of each flat pipe (2, 20) lying between the widened parts (2a, 2b, 20a, 20b) of the pipe wall (4) turbulence inserts (7, 70) are provided which fill up the entire pipe width (B).
2. Heat exchanger according to Claim 1, characterized in that the region of the widened part (2a, 2b) which runs into the arc-shaped parts (8) is designed to be slightly crowned.
3. Heat exchanger according to Claim 1, characterized in that the wall of the widened part (2a, 2b) extends in the transition region (9) to the parallel pipe walls (4') substantially perpendicularly to said walls.
4. Heat exchanger, particularly a cooling medium evaporator, consisting of a plurality of flat pipes parallel with one another, but arranged with a space between them and joined together, between which pipes a plurality of fins gave been fitted to increase the heat exchange surface, said pipes being provided at both their end regions with a widened part of the pipe wall, being laid by means of this part directly on a corresponding part of the adjacent pipe and connected therewith, particularly by soldering, there being provided in each widened part, transversally to the longitudinal axis of the flat pipes, connection openings with the adjacent flat pipe or to the adjacent group of pipes, characterized in that the widened part (20a) corresponds to the cross- section of an oval pipe (20') the wall of which (40) is compressed to a smaller distance (d) in the region (21) between the widened ends (20a, 20b), and in that, in the compressed region, turbulence inserts (70) are provided which are pushed into the pipe (20') before compression and fill up the entire width of the compressed region.
5. Heat exchanger according to Claim 4, characterized in that the widened part (20a) of the flat pipe (20) extends only over one part of the width (B) of the flat pipe (20).
6. Method of manufacture of a heat exchanger according to Claim 1, characterized in that firstly the ends (2a, 2b) of the flat pipe (2) are widened and in that, subsequently, the turbulence insert (7) is introduced axially.
7. Method of manufacture of a heat exchanger according to Claim 1, characterized in that the turbulence insert (70) is pushed in waved form (70') into the centre region (21) of the oval pipe (20'), and in that the pipe (20'), in the region (21) in which the turbulence insert (70') is situated is then compressed in parallel and is permanently deformed until the turbulence insert (70) is pressed out of its waved form into a stretched shape.
EP87109108A 1986-07-09 1987-06-24 Heat-exchanger, more particularly evaporator for refrigerant Expired EP0253167B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87109108T ATE43707T1 (en) 1986-07-09 1987-06-24 HEAT EXCHANGER, ESPECIALLY REFRIGERANT EVAPORATORS.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19863622953 DE3622953A1 (en) 1986-07-09 1986-07-09 HEAT EXCHANGER, ESPECIALLY REFRIGERANT EVAPORATOR
DE3622953 1986-07-09

Publications (2)

Publication Number Publication Date
EP0253167A1 EP0253167A1 (en) 1988-01-20
EP0253167B1 true EP0253167B1 (en) 1989-05-31

Family

ID=6304670

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Application Number Title Priority Date Filing Date
EP87109108A Expired EP0253167B1 (en) 1986-07-09 1987-06-24 Heat-exchanger, more particularly evaporator for refrigerant

Country Status (5)

Country Link
EP (1) EP0253167B1 (en)
JP (1) JPH0739914B2 (en)
AT (1) ATE43707T1 (en)
DE (2) DE3622953A1 (en)
ES (1) ES2008864B3 (en)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3900744A1 (en) * 1989-01-12 1990-07-26 Sueddeutsche Kuehler Behr HEAT EXCHANGER
JPH0346757U (en) * 1989-08-29 1991-04-30
FR2715216B1 (en) * 1994-01-20 1996-02-16 Valeo Thermique Moteur Sa Heat exchanger tube, process for its conformation and heat exchanger comprising such tubes.
FR2715217B1 (en) * 1994-01-20 1996-03-01 Valeo Thermique Moteur Sa Heat exchanger tube, in particular for a motor vehicle, process for its conformation and heat exchanger comprising such tubes.
DE19543986A1 (en) 1995-11-25 1997-05-28 Behr Gmbh & Co Heat exchanger and a method of manufacturing a heat exchanger
IT1291636B1 (en) * 1997-04-22 1999-01-19 Whirlpool Co MODULAR HEAT EXCHANGER PARTICULARLY FOR WASHING DRYERS AND SIMILAR MACHINES
DE19722097A1 (en) * 1997-05-27 1998-12-03 Behr Gmbh & Co Heat exchanger and heat exchanger arrangement for a motor vehicle
DE19723878B4 (en) * 1997-06-06 2007-10-25 Behr Gmbh & Co. Kg Heat exchanger
DE10138247A1 (en) * 2001-08-03 2003-02-13 Behr Gmbh & Co Heat exchanger arrangement used in motor vehicles comprises a heat exchanger having adjacent pipe ends designed and joined together to form a collector
CN106839854A (en) * 2017-01-26 2017-06-13 上海宝丰机械制造有限公司 Heat exchanger tube and the evaporative condenser including it

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2345331A (en) * 1942-04-18 1944-03-28 Morris Motors Ltd Heat interchange apparatus
DE2747275A1 (en) * 1977-10-21 1979-04-26 Volkswagenwerk Ag HEAT EXCHANGERS, IN PARTICULAR LIGHT METAL HEAT EXCHANGERS
US4269265A (en) * 1979-11-29 1981-05-26 Modine Manufacturing Company Tubular heat exchanger with turbulator
DE8126746U1 (en) * 1981-09-14 1982-02-25 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart FLAT TUBE HEAT EXCHANGER WITH TURBULEN INSERT
DE3502619A1 (en) * 1985-01-26 1986-07-31 Süddeutsche Kühlerfabrik Julius Fr. Behr GmbH & Co KG, 7000 Stuttgart HEAT EXCHANGER, ESPECIALLY REFRIGERANT EVAPORATOR

Also Published As

Publication number Publication date
EP0253167A1 (en) 1988-01-20
ES2008864B3 (en) 1989-08-16
JPS6317391A (en) 1988-01-25
DE3760214D1 (en) 1989-07-06
ATE43707T1 (en) 1989-06-15
DE3622953A1 (en) 1988-01-21
JPH0739914B2 (en) 1995-05-01

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