EP1518084B1 - Stacked panel-shaped heat transmitter - Google Patents

Stacked panel-shaped heat transmitter Download PDF

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Publication number
EP1518084B1
EP1518084B1 EP03760681A EP03760681A EP1518084B1 EP 1518084 B1 EP1518084 B1 EP 1518084B1 EP 03760681 A EP03760681 A EP 03760681A EP 03760681 A EP03760681 A EP 03760681A EP 1518084 B1 EP1518084 B1 EP 1518084B1
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EP
European Patent Office
Prior art keywords
height
panel
type
heat exchanger
section
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 - Lifetime
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EP03760681A
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German (de)
French (fr)
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EP1518084A1 (en
Inventor
Daniel Hendrix
Florian Moldovan
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Mahle Behr GmbH and Co KG
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Behr GmbH and Co KG
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    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
    • F28D9/005—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another the plates having openings therein for both heat-exchange media
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/916—Oil cooler

Definitions

  • the invention relates to a plate heat exchanger in stack construction according to the preamble of claim 1 and known from DE-A 195 11 991 of the Applicant.
  • Plate heat exchangers in stack construction are known, for. Example by DE-A 43 14 808 and DE-A 197 50 748, in each case by the Applicant.
  • this known type of heat exchanger basically the same plates of a single type are used to achieve a high number of identical parts. This results in the media involved in the heat exchange, z. As oil and coolant same channel height, d. H. the same flow cross-section. The different heat transfer conditions of the different media can by different, d. H. adapted turbulence inserts are encountered between the plates.
  • different plate types ie of two types are used, so that results in about twice the channel height as for the coolant channels for the flow channels through which charge air flows.
  • the two different types of plates have perpendicular to the plate bottom established, provided with a shoulder edges, which stacking these plates serve the circumferential paragraphs as a support and stop surface for adjacent plates.
  • the plate edges are soldered together in the overlapping, vertically positioned areas - this requires a defined, relatively narrow tolerance gap, otherwise the soldering is not tight. In this respect, this design is characterized by an increased production and cost.
  • the edges of both the first and the second plate type are inclined relative to the plate bottom, ie with a flank angle ⁇ , which allows easy stacking of the plates. Due to the taper of the edges or flanks compensation of manufacturing inaccuracies by elastic deformation is possible.
  • the edge formation according to the invention of the second plate type achieves a flow channel with a larger channel height. This happens because the edge region of the second plate type has a first and a third flank section as well as a middle or second section extending perpendicularly to the plate plate, which is decisive for the channel height.
  • the plates are made by deep drawing, in several steps - so far, the production cost is relatively low.
  • the plates of the first and second types are stacked in an alternating order, so that in each case one channel alternates less with a channel of greater height.
  • z. B. two or more channels are acted upon in parallel by a flow medium.
  • the edge of the first plate type has an insertion flank with a larger flank angle than the flank section adjoining the plate bottom.
  • the second plate type is also provided with a Ein 1500flanke, which also brings the aforementioned advantages of improved assembly and soldering with it.
  • means for generating turbulence for example, turbulence inserts or turbulence sheets, nubs, beads, etc., are arranged between the plates and soldered to these in the flow channels.
  • turbulence inserts for example, turbulence inserts or turbulence sheets, nubs, beads, etc.
  • the turbulence inserts define by their height the distance of the plates and thus the channel height.
  • Fig. 1 shows a section along the plane II (Fig. 2) by a plate heat exchanger 1
  • the left side L shows a training in the prior art according to DE-A 195 11 991 of the Applicant and its right half R
  • the inventive design of Plate heat exchanger 1 reproduces.
  • This consists of two different types of plates, namely a plate 2 lesser height and a plate 3 of greater height.
  • Both plate types 2, 3 each have a flat bottom 2a, 3a and a raised edge 2b, 3b, which will be explained in more detail below with regard to its geometrical design.
  • the plates 2, 3 are stacked in a known manner and form flow channels 4 of height h and flow channels 5 of height H, ie with different channel height (H> h).
  • 5 turbulence inserts 6, 7 are arranged in the illustrated embodiment, which fill the channel cross-section and are soldered to the adjacent plate bottoms 2a, 3a.
  • the flow channels 4 are connected to a distribution channel 8 in connection, which is arranged in alignment with an inlet connection 9 for a first medium.
  • the flow channels 5 with the larger channel height H are connected to a distribution channel 10 in connection, which is arranged in alignment with an inlet connection 11 of a second medium.
  • the first medium which enters through the inlet nozzle 9 in the plate heat exchanger 1, is a coolant of a coolant circuit, not shown, of an internal combustion engine of a motor vehicle, while the second medium, which enters through the inlet nozzle 11 in the plate heat exchanger 1, which is compressed by a compressor, not shown and thus heated charge air, which is cooled in this plate heat exchanger by the coolant and then fed to the internal combustion engine, not shown.
  • the other components of this plate heat exchanger such as annular spacers 12 and 13 different height for the low flow channels. 4 and the higher flow channels 5, as well as a lower end plate 14 and an upper end plate 15 correspond to the known prior art.
  • Fig. 2 shows a view of the plate heat exchanger 1 according to FIG. 1 from above with a view of the charge air inlet nozzle 11 - the coolant inlet nozzle 9 is hidden and therefore shown in dashed lines.
  • a coolant outlet pipe 16 is further arranged, while a charge air outlet nozzle 17 by dashed lines (because hidden) is shown.
  • the charge air thus flows on the one hand diagonally from the inlet nozzle 11 through the flow channels 5 to the outlet nozzle 17 and the other from top to bottom through the plate heat exchanger 1.
  • the coolant from the inlet nozzle 9 also flows diagonally through the flow channels 4 to the outlet nozzle 16, but from bottom to top.
  • Other flow forms according to the mentioned prior art are possible.
  • All parts of the illustrated plate heat exchanger 1 are preferably made of an aluminum alloy, are solder-plated and are soldered together, as well as the conically shaped edge regions 2b with the edge regions 3b.
  • the conicity of these edge regions 2b, 3b will be described in more detail below.
  • Fig. 3 shows a sketch with a first plate 20 and a second plate 21, which are stacked in one another.
  • the plates 20, 21 each have a flat bottom 20a, 21a and obliquely erected peripheral edge portions 20b, 21b, which are inclined at an obtuse angle ⁇ relative to the bottoms 20a, 21a.
  • the obtuse angle ⁇ is composed of a sum of 90 ° plus an angle ⁇ .
  • the plates 20, 21 each have a wall thickness s in the bottom and edge region, the channel height between the plates 20, 21 is indicated by h.
  • the intersections of the drawn lines A, B, C as well as the intersections A, C, D each form right triangles.
  • the distance AC results as the sum of s plus h, while the distance AD corresponds to the wall thickness s.
  • This results in the following angular relationship: sin ⁇ s / (s + h); thus results from the choice of the wall thickness s and the channel height h of the so-called flank angle ⁇ .
  • the condition is that the point A is located vertically above the point C.
  • 21 results in a contact surface 22 between the outer surface of the edge region 21b and the inner surface of the edge region 20b. In this contact region 22, the discs are soldered together.
  • Fig. 4 shows in a schematic sketch the two plate types, ie a plate 23 of the first type, shown individually on the left side, and a plate 24 of the second type, shown individually on the right; the assembly of both plates 23, 24 is shown in the middle of Fig. 4, wherein a flow channel 25 of the height h (for the coolant) and a flow channel 26 of the height H (for the charge air) results.
  • the representation shows that H>h; the plates being chosen so that the ratio of the channel height H to the channel height h is in a range of 1.5 to 10, preferably in a range between 2 and 6.
  • the plates 23, 24 correspond to the plates 2, 3 in FIG. 1.
  • the left single, partially shown plate 23 has a circumferential first edge portion 23a with a height h1 and a flank angle ⁇ . Adjoining this first section 23a is a second section 23b of height h2 with a flank angle ⁇ , where ⁇ > ⁇ . This second section 23b forms a so-called insertion edge due to the larger angle ⁇ .
  • the plate 24 of the second type is shown individually; it has a plate bottom 24e and four adjoining sections, namely a first section 24a of height H1 with a flank angle ⁇ , a second section 24b of height H2 with a flank angle of 0 degrees, a third section 24c of height H3 with a flank angle ⁇ and a fourth portion 24d of the height H4 with a flank insertion angle ⁇ .
  • the second section 24b is therefore not inclined, but runs perpendicular to the plate bottom 24e.
  • the image shown in the middle of FIG. 4 results in different channel heights h and H for the stacking of these plates Coolant channel 25 and the charge air channel 26.
  • the plates 23, 24 are with their conical edge regions, ie the inclined at the angle ⁇ flanks in the areas 27, 28 parallel to each other and to each other and are soldered in these areas.
  • the respectively subsequent insertion flank region 23b or 24d serves to facilitate assembly and at the same time leads to improved soldering - owing to the widened solder gap.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Control Of Motors That Do Not Use Commutators (AREA)
  • Curing Cements, Concrete, And Artificial Stone (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)

Abstract

The invention relates to a stacked panel-shaped heat transmitter comprising a plurality of interstacked trough-shaped panels ( 23,24 ) of a first and second type forming therebetween flow channels ( 25,26 ) for a first medium at a first height h and for a second medium at a second height H. The panels ( 23,24 ) have erect peripheral edges which are soldered to each other, the height thereof being different for the first and second type of panel. According to the invention, the first type of panel ( 23 ) has an edge ( 23 a) corresponding to height h 1 and a flank angle A. The second type of panel ( 24 ) has a higher edge which consists of at least three sections ( 24 a , 24 b , 24 c), the height thereof being H 1 , H 2 and H 3 . The first edge section ( 24 a) corresponding to a height H 1 and the third edge section ( 24 c) corresponding to a height H 3 respectively have a flank angle alpha. The second edge section ( 24 b) corresponding to height H 2 extends vertically in relation to the base of the panel ( 24 e).

Description

Die Erfindung betrifft einen Plattenwärmeübertrager in Stapelbauweise nach dem Oberbegriff des Patentanspruches 1 und bekannt durch die DE-A 195 11 991 der Anmelderin.The invention relates to a plate heat exchanger in stack construction according to the preamble of claim 1 and known from DE-A 195 11 991 of the Applicant.

Plattenwärmeübertrager in Stapelbauweise sind bekannt, z. B. durch die DE-A 43 14 808 und die DE-A 197 50 748, jeweils von der Anmelderin. Bei diesem bekannten Wärmetauschertyp werden grundsätzlich gleiche Platten eines einzigen Typs verwendet, um eine hohe Zahl von Gleichteilen zu erreichen. Daraus ergibt sich für die am Wärmetausch beteiligten Medien, z. B. Öl und Kühlmittel dieselbe Kanalhöhe, d. h. derselbe Strömungsquerschnitt. Den unterschiedlichen Wärmeübergangsbedingungen der unterschiedlichen Medien kann durch verschiedene, d. h. angepasste Turbulenzeinlagen zwischen den Platten begegnet werden.Plate heat exchangers in stack construction are known, for. Example by DE-A 43 14 808 and DE-A 197 50 748, in each case by the Applicant. In this known type of heat exchanger basically the same plates of a single type are used to achieve a high number of identical parts. This results in the media involved in the heat exchange, z. As oil and coolant same channel height, d. H. the same flow cross-section. The different heat transfer conditions of the different media can by different, d. H. adapted turbulence inserts are encountered between the plates.

Bei sehr unterschiedlichen Medien, z. B. flüssigen und gasförmigen benötigt man für eine effiziente Wärmeübertragung Strömungskanäle unterschiedlichen Querschnitts. In der DE-A 195 11 991 der Anmelderin wurden daher zwei Lösungen für einen Plattenwärmeübertrager in Stapelbauweise vorgeschlagen, bei denen für ein erstes Medium, z. B. ein Kühlmittel eines Kühlmittelkreislaufes eines Verbrennungsmotors ein geringerer Kanalquerschnitt vorgesehen ist als für ein zweites Medium, z. B. die von einem Kompressor verdichtete und erwärmte Ladeluft für den Verbrennungsmotor. Bei der ersten Lösung werden nur gleiche Platten mit gleicher Kanalhöhe verwendet, allerdings werden auf der Ladeluftseite zwei oder mehr Kanäle parallel geschaltet, so dass sich der doppelte oder mehrfache Strömungsquerschnitt für die Ladeluft gegenüber dem Strömungsquerschnitt für das Kühlmittel ergibt. Nach der zweiten Lösung werden unterschiedliche Plattentypen, d. h. von zweierlei Bauart verwendet, so dass sich für die von Ladeluft durchströmten Strömungskanäle etwa die doppelte Kanalhöhe wie für die Kühlmittelkanäle ergibt. Die zwei verschiedenen Plattentypen weisen senkrecht gegenüber dem Plattenboden aufgestellte, mit einem Absatz versehene Ränder auf, wobei beim Stapeln dieser Platten die umlaufenden Absätze als Auflage und Anschlagfläche für benachbarte Platten dienen. Die Plattenränder werden in den sich überlappenden, senkrecht aufgestellten Bereichen miteinander verlötet - hierfür ist ein definierter, relativ eng tolerierter Spalt erforderlich, anderenfalls ist die Lötung nicht dicht. Insofern ist diese Bauweise durch eine erhöhten Fertigungs- und Kostenaufwand gekennzeichnet.For very different media, eg. As liquid and gaseous flow channels of different cross-section are needed for efficient heat transfer. In DE-A 195 11 991 of the Applicant therefore two solutions have been proposed for a plate heat exchanger in a stacked construction, in which for a first medium, for. B. a coolant of a coolant circuit of an internal combustion engine, a smaller channel cross-section is provided as for a second medium, for. B. compressed and heated by a compressor charge air for the internal combustion engine. In the first Solution only equal plates are used with the same channel height, but two or more channels are connected in parallel on the charge air side, so that the double or multiple flow cross section for the charge air over the flow cross section for the coolant results. According to the second solution, different plate types, ie of two types are used, so that results in about twice the channel height as for the coolant channels for the flow channels through which charge air flows. The two different types of plates have perpendicular to the plate bottom established, provided with a shoulder edges, which stacking these plates serve the circumferential paragraphs as a support and stop surface for adjacent plates. The plate edges are soldered together in the overlapping, vertically positioned areas - this requires a defined, relatively narrow tolerance gap, otherwise the soldering is not tight. In this respect, this design is characterized by an increased production and cost.

Es ist Aufgabe der vorliegenden Erfindung, einen Plattenwärmeübertrager der eingangs genannten Art dahingehend zu verbessern, dass er mit einem geringeren Fertigungs- und Kostenaufwand herstellbar ist.It is an object of the present invention to improve a plate heat exchanger of the type mentioned in that it can be produced with a lower production and cost.

Die Lösung dieser Aufgabe wird durch die Merkmale des Patentanspruches 1 erreicht. Zunächst sind die Ränder sowohl des ersten als auch des zweiten Plattentyps gegenüber dem Plattenboden geneigt angeordnet, d. h. mit einem Flankenwinkel α, der ein einfaches Stapeln der Platten ermöglicht. Aufgrund der Konizität der Ränder bzw. Flanken ist ein Ausgleich von Fertigungsungenauigkeiten durch elastische Verformung möglich. Durch die erfindungsgemäße Randausbildung des zweiten Plattentyps wird ein Strömungskanal mit größerer Kanalhöhe erreicht. Dies geschieht dadurch, dass der Randbereich des zweiten Plattentyps einen ersten und einen dritten Flankenabschnitt sowie einen mittleren bzw. zweiten, senkrecht zum Plattenboden verlaufenden Abschnitt aufweist, der für die Kanalhöhe maßgebend ist. Die Platten werden durch Tiefziehen, in mehreren Schritten, hergestellt - insofern ist der Fertigungsaufwand relativ gering.The solution of this problem is achieved by the features of claim 1. First, the edges of both the first and the second plate type are inclined relative to the plate bottom, ie with a flank angle α, which allows easy stacking of the plates. Due to the taper of the edges or flanks compensation of manufacturing inaccuracies by elastic deformation is possible. The edge formation according to the invention of the second plate type achieves a flow channel with a larger channel height. This happens because the edge region of the second plate type has a first and a third flank section as well as a middle or second section extending perpendicularly to the plate plate, which is decisive for the channel height. The plates are made by deep drawing, in several steps - so far, the production cost is relatively low.

Gemäß einer vorteilhaften Weiterbildung der Erfindung werden die Platten des ersten und zweiten Typs in abwechselnder Reihenfolge gestapelt, so dass jeweils ein Kanal geringer mit einem Kanal größerer Höhe abwechselt. Möglich sind jedoch auch andere Reihenfolgen, so dass z. B. zwei oder mehrere Kanäle parallel von einem Strömungsmedium beaufschlagt werden.According to an advantageous embodiment of the invention, the plates of the first and second types are stacked in an alternating order, so that in each case one channel alternates less with a channel of greater height. However, other sequences are possible, so that z. B. two or more channels are acted upon in parallel by a flow medium.

Nach einer vorteilhaften Weiterbildung der Erfindung weist der Rand des ersten Plattentyps eine Einführflanke mit einem größeren Flankenwinkel als der an den Plattenboden angrenzende Flankenabschnitt auf. Dadurch wird ein leichteres Einführen der nächsten Platten beim Stapeln erreicht, also eine vereinfachte Montage ermöglicht. Darüber hinaus ergibt sich durch diese Einführflanke eine verbesserte Verlötung der Randbereiche.According to an advantageous development of the invention, the edge of the first plate type has an insertion flank with a larger flank angle than the flank section adjoining the plate bottom. As a result, an easier insertion of the next plates is achieved when stacking, thus allowing a simplified installation. In addition, results from this Einführflanke improved soldering of the edge areas.

Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung ist auch der zweite Plattentyp mit einer Einführflanke versehen, die ebenfalls die zuvor erwähnten Vorteile einer verbesserten Montage und Verlötung mit sich bringt.According to a further advantageous embodiment of the invention, the second plate type is also provided with a Einführflanke, which also brings the aforementioned advantages of improved assembly and soldering with it.

Nach einer vorteilhaften Ausgestaltung der Erfindung sind in den Strömungskanälen Mittel zum Erzeugen von Verwirbelungen, beispielsweise Turbulenzeinlagen bzw. Turbulenzbleche, Noppen, Sicken, usw., zwischen den Platten angeordnet und mit diesen verlötet. Dadurch wird ein verbesserter Wärmeübergang durch Verwirbelung der Medien und eine erhöhte Druckfestigkeit des Plattenstapels erreicht. Es ist möglich, die Turbulenzeinlagen hinsichtlich ihres Druckabfalls und ihrer geometrischen Gestaltung an die unterschiedlichen Medien wie Kühlmittel und Ladeluft anzupassen. Die Turbulenzeinlagen definieren durch ihre Höhe den Abstand der Platten und damit die Kanalhöhe.According to an advantageous embodiment of the invention means for generating turbulence, for example, turbulence inserts or turbulence sheets, nubs, beads, etc., are arranged between the plates and soldered to these in the flow channels. As a result, an improved heat transfer is achieved by swirling of the media and increased pressure resistance of the plate stack. It is possible to adapt the turbulence inserts to the different media such as coolant and charge air with regard to their pressure drop and their geometric design. The turbulence inserts define by their height the distance of the plates and thus the channel height.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird im Folgenden näher beschrieben. Es zeigen

Fig. 1
einen Schnitt in der Ebene I-I gemäß Fig. 2 durch einen Plattenwärmeübertrager in Stapelbauweise nach dem Stand der Technik (linke Hälfte) und gemäß der Erfindung (rechte Hälfte),
Fig. 2
eine Ansicht von oben in schematischer (nicht vollständiger) Darstellung auf den Plattenwärmeübertrager,
Fig. 3
eine Skizze zur Berechnung des Flankenwinkels α der Plattenränder und
Fig. 4
eine schematische Darstellung der erfindungsgemäßen Randbereiche eines ersten und eines zweiten Plattentyps.
An embodiment of the invention is illustrated in the drawing and will be described in more detail below. Show it
Fig. 1
a section in the plane II of Figure 2 by a plate heat exchanger in stack construction according to the prior art (left half) and according to the invention (right half),
Fig. 2
a view from above in a schematic (not complete) representation of the plate heat exchanger,
Fig. 3
a sketch for calculating the edge angle α of the plate edges and
Fig. 4
a schematic representation of the edge regions according to the invention of a first and a second plate type.

Fig. 1 zeigt einen Schnitt längs der Ebene I-I (Fig. 2) durch einen Plattenwärmeübertrager 1, dessen linke Seite L eine Ausbildung nach dem Stand der Technik gemäß DE-A 195 11 991 der Anmelderin zeigt und dessen rechte Hälfte R die erfindungsgemäße Ausbildung des Plattenwärmeübertragers 1 wiedergibt. Dieser besteht aus zwei unterschiedlichen Plattentypen, nämlich einer Platte 2 geringerer Höhe und einer Platte 3 größerer Höhe. Beide Plattentypen 2, 3 weisen jeweils einen ebenen Boden 2a, 3a und einen hochgestellten Rand 2b, 3b auf, der hinsichtlich seiner geometrischen Ausbildung unten noch näher erläutert wird. Die Platten 2, 3 sind in bekannter Weise aufeinander gestapelt und bilden Strömungskanäle 4 der Höhe h und Strömungskanäle 5 der Höhe H, also mit unterschiedlicher Kanalhöhe (H > h). Innerhalb der Strömungskanäle 4, 5 sind im dargestellten Ausführungsbeispiel Turbulenzeinlagen 6, 7 angeordnet, die den Kanalquerschnitt ausfüllen und mit den benachbarten Plattenböden 2a, 3a verlötet sind. Die Strömungskanäle 4 stehen mit einem Verteilerkanal 8 in Verbindung, der fluchtend zu einem Eintrittsstutzen 9 für ein erstes Medium angeordnet ist. Die Strömungskanäle 5 mit der größeren Kanalhöhe H stehen mit einem Verteilerkanal 10 in Verbindung, der fluchtend zu einem Eintrittsstutzen 11 eines zweiten Mediums angeordnet ist. Das erste Medium, welches durch den Eintrittsstutzen 9 in den Plattenwärmeübertrager 1 eintritt, ist ein Kühlmittel eines nicht dargestellten Kühlmittelkreislaufes eines Verbrennungsmotors eines Kraftfahrzeuges, während das zweite Medium, welches durch den Eintrittsstutzen 11 in den Plattenwärmeübertrager 1 eintritt, die von einem nicht dargestellten Kompressor verdichtete und damit erwärmte Ladeluft ist, die in diesem Plattenwärmeübertrager durch das Kühlmittel gekühlt und dann dem nicht dargestellten Verbrennungsmotor zugeleitet wird. Die weiteren Bauteile dieses Plattenwärmeübertragers wie ringförmige Abstandhalter 12 und 13 unterschiedlicher Höhe für die niedrigen Strömungskanäle 4 und die höheren Strömungskanäle 5, ebenso wie eine untere Abschlussplatte 14 und eine obere Abschlussplatte 15 entsprechen dem bekannten Stand der Technik. Fig. 1 shows a section along the plane II (Fig. 2) by a plate heat exchanger 1, the left side L shows a training in the prior art according to DE-A 195 11 991 of the Applicant and its right half R, the inventive design of Plate heat exchanger 1 reproduces. This consists of two different types of plates, namely a plate 2 lesser height and a plate 3 of greater height. Both plate types 2, 3 each have a flat bottom 2a, 3a and a raised edge 2b, 3b, which will be explained in more detail below with regard to its geometrical design. The plates 2, 3 are stacked in a known manner and form flow channels 4 of height h and flow channels 5 of height H, ie with different channel height (H> h). Within the flow channels 4, 5 turbulence inserts 6, 7 are arranged in the illustrated embodiment, which fill the channel cross-section and are soldered to the adjacent plate bottoms 2a, 3a. The flow channels 4 are connected to a distribution channel 8 in connection, which is arranged in alignment with an inlet connection 9 for a first medium. The flow channels 5 with the larger channel height H are connected to a distribution channel 10 in connection, which is arranged in alignment with an inlet connection 11 of a second medium. The first medium, which enters through the inlet nozzle 9 in the plate heat exchanger 1, is a coolant of a coolant circuit, not shown, of an internal combustion engine of a motor vehicle, while the second medium, which enters through the inlet nozzle 11 in the plate heat exchanger 1, which is compressed by a compressor, not shown and thus heated charge air, which is cooled in this plate heat exchanger by the coolant and then fed to the internal combustion engine, not shown. The other components of this plate heat exchanger such as annular spacers 12 and 13 different height for the low flow channels. 4 and the higher flow channels 5, as well as a lower end plate 14 and an upper end plate 15 correspond to the known prior art.

Fig. 2 zeigt eine Ansicht auf den Plattenwärmeübertrager 1 gemäß Fig. 1 von oben mit Blick auf den Ladelufteintrittsstutzen 11 - der Kühlmitteleintrittsstutzen 9 ist verdeckt und daher gestrichelt dargestellt. Auf der oberen Abschlussplatte 15 ist ferner ein Kühlmittelaustrittsstutzen 16 angeordnet, während ein Ladeluftaustrittsstutzen 17 gestrichelt (weil verdeckt) dargestellt ist. Die Ladeluft strömt also einerseits diagonal vom Eintrittsstutzen 11 durch die Strömungskanäle 5 zum Austrittsstutzen 17 und andererseits von oben nach unten durch den Plattenwärmeübertrager 1. Dagegen strömt das Kühlmittel vom Eintrittsstutzen 9 ebenfalls diagonal durch die Strömungskanäle 4 zum Austrittsstutzen 16, allerdings von unten nach oben. Andere Strömungsformen nach dem erwähnten Stand der Technik sind möglich. Fig. 2 shows a view of the plate heat exchanger 1 according to FIG. 1 from above with a view of the charge air inlet nozzle 11 - the coolant inlet nozzle 9 is hidden and therefore shown in dashed lines. On the upper end plate 15, a coolant outlet pipe 16 is further arranged, while a charge air outlet nozzle 17 by dashed lines (because hidden) is shown. The charge air thus flows on the one hand diagonally from the inlet nozzle 11 through the flow channels 5 to the outlet nozzle 17 and the other from top to bottom through the plate heat exchanger 1. In contrast, the coolant from the inlet nozzle 9 also flows diagonally through the flow channels 4 to the outlet nozzle 16, but from bottom to top. Other flow forms according to the mentioned prior art are possible.

Alle Teile des dargestellten Plattenwärmeübertragers 1 bestehen vorzugsweise aus einer Aluminiumlegierung, sind lotplattiert und werden miteinander verlötet, so auch die konisch ausgebildeten Randbereiche 2b mit den Randbereichen 3b. Die Konizität dieser Randbereiche 2b, 3b wird im Folgenden näher beschrieben.All parts of the illustrated plate heat exchanger 1 are preferably made of an aluminum alloy, are solder-plated and are soldered together, as well as the conically shaped edge regions 2b with the edge regions 3b. The conicity of these edge regions 2b, 3b will be described in more detail below.

Fig. 3 zeigt eine Skizze mit einer ersten Platte 20 und einer zweiten Platte 21, die ineinander gestapelt sind. Die Platten 20, 21 weisen jeweils einen ebenen Boden 20a, 21a sowie schräg aufgestellte, umlaufende Randbereiche 20b, 21b auf, die unter einem stumpfen Winkel γ gegenüber den Böden 20a, 21a geneigt sind. Der stumpfe Winkel γ setzt sich dabei aus einer Summe von 90 ° plus einem Winkel α zusammen. Die Platten 20, 21 weisen jeweils eine Wandstärke s im Boden- und Randbereich auf, die Kanalhöhe zwischen den Platten 20, 21 ist mit h angegeben. Die Schnittpunkte der eingezeichneten Linien A, B, C sowie die Schnittpunkte A, C, D bilden jeweils rechtwinklige Dreiecke. Die Strecke A-C ergibt sich als Summe aus s plus h, während die Strecke A-D der Wandstärke s entspricht. Daraus ergibt sich folgende Winkelbeziehung: sin α = s/(s+h); somit ergibt sich aus der Wahl der Wandstärke s und der Kanalhöhe h der so genannte Flankenwinkel α. Fig. 3 shows a sketch with a first plate 20 and a second plate 21, which are stacked in one another. The plates 20, 21 each have a flat bottom 20a, 21a and obliquely erected peripheral edge portions 20b, 21b, which are inclined at an obtuse angle γ relative to the bottoms 20a, 21a. The obtuse angle γ is composed of a sum of 90 ° plus an angle α. The plates 20, 21 each have a wall thickness s in the bottom and edge region, the channel height between the plates 20, 21 is indicated by h. The intersections of the drawn lines A, B, C as well as the intersections A, C, D each form right triangles. The distance AC results as the sum of s plus h, while the distance AD corresponds to the wall thickness s. This results in the following angular relationship: sin α = s / (s + h); thus results from the choice of the wall thickness s and the channel height h of the so-called flank angle α.

Die Bedingung ist dabei, dass der Punkt A senkrecht über dem Punkt C liegt. Beim Stapeln der Scheiben 20, 21 ergibt sich eine Kontaktfläche 22 zwischen der Außenfläche des Randbereiches 21b und der Innenfläche des Randbereiches 20b. In diesem Kontaktbereich 22 werden die Scheiben miteinander verlötet.The condition is that the point A is located vertically above the point C. When stacking the discs 20, 21 results in a contact surface 22 between the outer surface of the edge region 21b and the inner surface of the edge region 20b. In this contact region 22, the discs are soldered together.

Fig. 4 zeigt in einer schematischren Skizze die beiden Plattentypen, d. h. eine Platte 23 des ersten Typs, einzeln dargestellt auf der linken Seite, und eine Platte 24 des zweiten Typs, rechts einzeln dargestellt; der Zusammenbau beider Platten 23, 24 ist in der Mitte von Fig. 4 dargestellt, wobei sich ein Strömungskanal 25 der Höhe h (für das Kühlmittel) und ein Strömungskanal 26 der Höhe H (für die Ladeluft) ergibt. Die Darstellung zeigt, dass H > h ist; wobei die Platten so gewählt werden, dass das Verhältnis der Kanalhöhe H zur Kanalhöhe h in einem Bereich von 1,5 bis 10 liegt, vorzugsweise in einem Bereich zwischen 2 und 6 liegt. Die Platten 23, 24 entsprechen den Platten 2, 3 in Fig. 1.. Fig. 4 shows in a schematic sketch the two plate types, ie a plate 23 of the first type, shown individually on the left side, and a plate 24 of the second type, shown individually on the right; the assembly of both plates 23, 24 is shown in the middle of Fig. 4, wherein a flow channel 25 of the height h (for the coolant) and a flow channel 26 of the height H (for the charge air) results. The representation shows that H>h; the plates being chosen so that the ratio of the channel height H to the channel height h is in a range of 1.5 to 10, preferably in a range between 2 and 6. The plates 23, 24 correspond to the plates 2, 3 in FIG. 1.

Die links einzeln, teilweise dargestellte Platte 23 weist einen umlaufenden ersten Randabschnitt 23a mit einer Höhe h1 und einem Flankenwinkel α auf. An diesen ersten Abschnitt 23a schließt sich ein zweiter Abschnitt 23b der Höhe h2 mit einem Flankenwinkel β an, wobei β > α. Dieser zweite Abschnitt 23b bildet eine so genannte Einführflanke aufgrund des größeren Winkels β.The left single, partially shown plate 23 has a circumferential first edge portion 23a with a height h1 and a flank angle α. Adjoining this first section 23a is a second section 23b of height h2 with a flank angle β, where β> α. This second section 23b forms a so-called insertion edge due to the larger angle β.

Auf der rechten Seite von Fig. 4 ist die Platte 24 des zweiten Typs einzeln dargestellt; sie weist einen Plattenboden 24e und vier aneinander anschließende Abschnitte auf, und zwar einen ersten Abschnitt 24a der Höhe H1 mit einem Flankenwinkel α, einen zweiten Abschnitt 24b der Höhe H2 mit einem Flankenwinkel von 0 Grad, einen dritten Abschnitt 24c der Höhe H3 mit einem Flankenwinkel α und einen vierten Abschnitt 24d der Höhe H4 mit einem Flankeneinführwinkel β. Der zweite Abschnitt 24b ist also nicht geneigt, sondern verläuft senkrecht zum Plattenboden 24e.On the right side of Fig. 4, the plate 24 of the second type is shown individually; it has a plate bottom 24e and four adjoining sections, namely a first section 24a of height H1 with a flank angle α, a second section 24b of height H2 with a flank angle of 0 degrees, a third section 24c of height H3 with a flank angle α and a fourth portion 24d of the height H4 with a flank insertion angle β. The second section 24b is therefore not inclined, but runs perpendicular to the plate bottom 24e.

Durch diese Geometrie der Platten 23, 24, d. h. ihrer Randbereiche 23a, 23b und 24a bis 24d ergibt sich beim Stapeln dieser Platten das in der Mitte von Fig. 4 dargestellte Bild mit unterschiedlichen Kanalhöhen h und H für den Kühlmittelkanal 25 und den Ladeluftkanal 26. Die Platten 23, 24 liegen mit ihren konischen Randbereichen, d. h. den unter dem Winkel α geneigten Flanken in den Bereichen 27, 28 parallel zueinander und aneinander und werden in diesen Bereichen verlötet. Der jeweils anschließende Einführflankenbereich 23b bzw. 24d dient einer erleichterten Montage und führt gleichzeitig zu einer verbesserten Verlötung - wegen des erweiterten Lotspaltes. Durch Variation der Höhe H2 des zweiten Abschnittes 24b kann die Kanalhöhe H verändert werden.As a result of this geometry of the plates 23, 24, ie their edge regions 23a, 23b and 24a to 24d, the image shown in the middle of FIG. 4 results in different channel heights h and H for the stacking of these plates Coolant channel 25 and the charge air channel 26. The plates 23, 24 are with their conical edge regions, ie the inclined at the angle α flanks in the areas 27, 28 parallel to each other and to each other and are soldered in these areas. The respectively subsequent insertion flank region 23b or 24d serves to facilitate assembly and at the same time leads to improved soldering - owing to the widened solder gap. By varying the height H2 of the second section 24b, the channel height H can be changed.

Claims (6)

  1. A panel-type heat exchanger (1) of stacked design consisting of a plurality of trough-shaped panels (23, 24) stacked one inside another of a first and of a second type which together form flow channels (25, 26) with a first height h for a first medium and a second height H for a second medium, the panels (23, 24) having rims which are raised at the circumference and soldered together,
    characterised in that
    the first panel type (23) has a rim (23a) of height h1 with a flank angle α and the second panel type (24) has a raised rim comprising at least three sections (24a, 24b, 24c) of heights H1, H2 and H3, the first rim section (24a) of height H1 and the third rim section (24c) of height H3 each having a flank angle α, flanks (23a, 24a, 24c) inclined at angle α lying parallel adjacent to one another in areas (27, 28) and being soldered, while the second rim section (24b) of height H2 runs perpendicular to the panel base (24e).
  2. A panel-type heat exchanger in accordance with claim 1,
    characterised in that
    panels of the first and second types (23, 24) are stacked alternately such that adjacent flow channels (25, 26) have different channel heights h, H.
  3. A panel-type heat exchanger in accordance with claim 1 or 2,
    characterised in that
    the ratio of channel height H to channel height h lies within a range of 1.5 to 10.
  4. A panel-type heat exchanger in accordance with one of claims 1 to 3,
    characterised in that
    adjacent to the first rim section (23a) of the first panel type (23) is a second section (23b) with an insertion flank, a flank angle β and a height h2, where (β) > (α).
  5. A panel-type heat exchanger in accordance with one of claims 1 to 4,
    characterised in that
    adjacent to the third rim section (24c) of the second panel type (24) is a fourth section (24d) with an insertion flank, a flank angle (β) and a height (H4).
  6. A panel-type heat exchanger in accordance with one of claims 1 to 5,
    characterised in that
    positioned between the panels (2, 2a; 3, 3a) and in the area of the flow channels (4, 5) are means for generating turbulence.
EP03760681A 2002-06-25 2003-06-23 Stacked panel-shaped heat transmitter Expired - Lifetime EP1518084B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10228263 2002-06-25
DE10228263A DE10228263A1 (en) 2002-06-25 2002-06-25 Plate heat exchanger in stack construction
PCT/EP2003/006579 WO2004001315A1 (en) 2002-06-25 2003-06-23 Stacked panel-shaped heat transmitter

Publications (2)

Publication Number Publication Date
EP1518084A1 EP1518084A1 (en) 2005-03-30
EP1518084B1 true EP1518084B1 (en) 2006-11-29

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EP03760681A Expired - Lifetime EP1518084B1 (en) 2002-06-25 2003-06-23 Stacked panel-shaped heat transmitter

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US (1) US7426957B2 (en)
EP (1) EP1518084B1 (en)
JP (1) JP4445384B2 (en)
CN (1) CN1329705C (en)
AT (1) ATE347082T1 (en)
AU (1) AU2003250843A1 (en)
DE (2) DE10228263A1 (en)
ES (1) ES2276108T3 (en)
WO (1) WO2004001315A1 (en)

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US7426957B2 (en) 2008-09-23
JP2005530979A (en) 2005-10-13
US20050241814A1 (en) 2005-11-03
WO2004001315A1 (en) 2003-12-31
JP4445384B2 (en) 2010-04-07
AU2003250843A1 (en) 2004-01-06
DE10228263A1 (en) 2004-01-22
CN1329705C (en) 2007-08-01
ATE347082T1 (en) 2006-12-15
EP1518084A1 (en) 2005-03-30
ES2276108T3 (en) 2007-06-16
DE50305856D1 (en) 2007-01-11
CN1653309A (en) 2005-08-10

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