EP1570223B1 - Heat exchanger - Google Patents
Heat exchanger Download PDFInfo
- Publication number
- EP1570223B1 EP1570223B1 EP03788989A EP03788989A EP1570223B1 EP 1570223 B1 EP1570223 B1 EP 1570223B1 EP 03788989 A EP03788989 A EP 03788989A EP 03788989 A EP03788989 A EP 03788989A EP 1570223 B1 EP1570223 B1 EP 1570223B1
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- European Patent Office
- Prior art keywords
- tube
- heat exchanger
- lateral area
- area
- accordance
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- 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.)
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- 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
- F28F9/0224—Header boxes formed by sealing end plates into covers
Definitions
- the present invention relates to a heat exchanger, in particular a charge air cooler for a motor vehicle.
- the air to be supplied to the combustion can be compressed, for example with a turbocharger, before it is supplied to the combustion chambers of the internal combustion engine.
- a turbocharger a heat exchanger designed as a charge air cooler is connected downstream, with which the compressed air can be cooled to an allowable temperature before its combustion.
- An intercooler is for example in the DE 197 57 034 A1 described.
- the hot air is introduced into a first collecting channel of the heat exchanger, where it is distributed and flows into flat tubes, which open into the collecting channel.
- the flat tubes are side by side, and arranged with the long sides of their cross-section containing side surfaces parallel to each other and form a flow path, is passed through the cooling air.
- cooling fins are arranged between the flat tubes, which effect an effective heat exchange between the flat tubes and the cooling air flow.
- the flat tubes open into a second collecting channel, which supplies the incoming therein, cooled, compressed charge air combustion in the engine.
- the tubes are usually inserted into openings of a tube plate and soldered fluid-tight. At any charge of compressed air, this solder joint is subject to high mechanical loads due to rapid pressure changes. Especially the narrow sides of flat tubes do not meet the increasing strength requirements, which may result in leaks especially in the sides of the tubesheet facing areas such pipe-ground connections.
- the WO 02/04881 A1 describes a head piece for a condenser, which is formed from a tube plate and a box part.
- the tube plate has tube insertion openings and is stiffened by longitudinal shoulders with the tube insertion openings intersecting the shoulders.
- the object of the invention is to provide a heat exchanger, in particular a charge air cooler, are reduced in the mechanical loads of pipe-floor connections without additional expenditure of material.
- a heat exchanger tubes which are adapted to be flowed through by a first medium and to be flowed around by a second medium, so that heat from the first to the second medium or vice versa transferable.
- At least one collecting box communicating with the tubes comprises at least one tubesheet which has a substantially flat central region and at least one side region angled or rounded off from the central region.
- the tube bottom preferably has two, in particular opposite, side regions, which are angled or rounded off from the central region.
- In the central area are tube openings into which the tubes can be inserted to form the communicating connection with the collecting box.
- a middle region of a tube plate is to be regarded as essentially flat if the tubesheet is largely flat in this region.
- a tube bottom middle region with outlines of tube openings formed as so-called passages and / or with other minor deviations from a flatness is essentially planar in the context of the invention.
- the tubesheet has passages which delimit the tube openings which according to the invention point out of the collection box. These passages serve to increase the contact area between the inserted tubes and the tubesheet, thereby enhancing the tube-to-floor connection.
- the passage of the at least one pipe opening on or in the at least one side region is particularly advantageously lower than in the middle region of the pipe bottom. As a result, an attack surface for mechanical stresses originating from the side region is reduced at the tube-bottom connection, while a high stability of the tube-bottom connection in the middle region of the tube bottom is maintained.
- the at least one side region of the tube bottom comprises one or more flat partial regions, so that the collecting container has a faceted shape. This allows a secure production with low manufacturing tolerances.
- the at least one side region has a rounding with an approximately constant radius of curvature or a plurality of curves with different Curvature radii on.
- a particularly good approximation to a semicircular cross section of the tube bottom is achieved.
- an improved approach to a semicircular shape of the tube bottom cross-section is a continuous convex design of the at least one side region. Concave areas of strong deformation in the case of pressure loads are thereby avoided.
- the heat exchanger is designed as a charge air cooler, which is particularly preferably used in motor vehicles.
- the intercooler on two headers, of which a first for distribution and a second is provided for the collection of charge air.
- each of the headers has exactly one tubesheet, which is provided with a series of tube openings. It is also advantageous to use a series of flat tubes with intermediate, in particular soldered, corrugated fins, as this achieves an increased heat transfer area.
- the cooling medium is preferably air, although other cooling media such as water or coolant are conceivable.
- FIG. 1a shows a section of a heat exchanger 10 in a perspective view.
- a collecting box 20 for distributing a first medium consists of a tube sheet 30 and a box lid 40, which are welded together at a common contact surface 50.
- the box lid 40 is here inserted into the tube plate 30.
- a tube sheet and a box lid by soldering, bonding or positively connected with each other or in one piece or in one piece, that is, for example, consisting of a formed plate formed.
- the tube plate 30 has a tube opening 60 whose edge 70 is formed as a so-called passage in the collection box inside.
- a substantially rectangular flat tube 80 is inserted into the tube opening 60 and soldered or welded to the tube sheet 30.
- corrugated fins which are adjacent on both sides of the flat tube 80 and are soldered to the latter, so that a heat transfer from the first to the tube 80 and the ribs flowing around the second medium or from the second to the first medium is increased.
- the heat exchanger includes 10 a whole series of alternating flat tubes and corrugated fins, which form a so-called tube-rib block.
- the tube 80 is inserted into the tube opening 60 so far that an upper edge region 90 of the tube 80 extends beyond the passage 70.
- good utilization of the tube 80 facing, non-visible inner surface of the passage 70 is guaranteed as a contact surface for a pipe-floor connection.- This serves, for example, a dense soldering.
- the supernatant of the tube 80 is to be kept as low as possible over the tube plate 30. For this reason, the tube opening 60 is located in a substantially planar central region 100 of the tube bottom 30.
- the collecting box 20 If the collecting box 20 is charged with the first medium, the collecting box 20 under certain circumstances deforms such that its cross-sectional shape approaches a circular shape.
- side regions 110, 120 of the tube bottom 30 are angled relative to the central region 100. This results in a lower deformation of the tube plate 30 under pressure loading of the collecting tank 20 in these side regions 110, 120.
- the mechanically most stressed in such pressure-induced deformations end faces 130; 140 of the flat tube 80 are relieved by the fact that the tube opening 60 and thus also the tube 80 extend into the side regions 110, 120 of the tube bottom 30.
- FIG. 1 c shows a cross section of the heat exchanger section from FIG. 1 a or FIG. 1 b, wherein the sectional plane extends transversely through the tube 80.
- FIG. 2a, 2b and 2c an embodiment of the heat exchanger 210 according to the invention is shown analogous to Fig. 1a, 1b and 1c, which differs from the previous embodiment essentially in that the passage 270 is formed aus mar thed from the collecting box 220.
- the tube sheet 230 is welded to a box lid 240 at the common interface 250.
- a substantially rectangular flat tube 280 is inserted into the tube opening 260 with the passage 270 and soldered or welded to the tube sheet 230.
- the passage 270 out of the collection box 220 In order to reduce a pressure drop of a first medium flowing through the header 220 and among others through the tube 280 via the heat exchanger, the passage 270 out of the collection box 220, so that the tube 280 stuck in the passage 270 is not above the tube sheet 230 in whose substantially planar central region 300 protrudes.
- Side regions 310, 320 of the tube bottom 230 are angled relative to the central region 300 in order to reduce deformation of the header tank 220 under pressure, at least in the side regions 310, 320.
- the tube opening 260 and thus the tube 280 extend to the side regions 310, 320, which is illustrated particularly clearly in FIG. 2c.
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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)
- Separation By Low-Temperature Treatments (AREA)
- Power Steering Mechanism (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Supercharger (AREA)
Abstract
Description
Die vorliegende Erfindung betrifft einen Wärmeübertrager, insbesondere einen Ladeluftkühler für ein Kraftfahrzeug.The present invention relates to a heat exchanger, in particular a charge air cooler for a motor vehicle.
Um eine Leistungssteigerung eines Verbrennungsmotors zu erzielen, kann die der Verbrennung zuzuführende Luft beispielsweise mit einem Turbolader verdichtet werden, bevor sie den Brennkammern des Verbrennungsmotors zugeführt wird. Die Verdichtung der Luft bringt jedoch gleichzeitig eine Erwärmung derselben mit sich, die für einen optimalen Ablauf des Verbrennungsprozesses nachteilig ist. Beispielsweise kann dadurch eine verfrühte Zündung oder eine erhöhte Stickoxidemission ausgelöst werden. Um die nachteiligen Folgen von der Verbrennung zugeführter überhitzter Luft zu vermeiden, wird einem Turbolader ein als Ladeluftkühler ausgebildeter Wärmeübertrager nachgeschaltet, mit dem die komprimierte Luft vor ihrer Verbrennung auf eine zulässige Temperatur abgekühlt werden kann.In order to achieve an increase in the output of an internal combustion engine, the air to be supplied to the combustion can be compressed, for example with a turbocharger, before it is supplied to the combustion chambers of the internal combustion engine. However, the compression of the air at the same time brings about a heating of the same, which is disadvantageous for an optimal sequence of the combustion process. For example, this can trigger a premature ignition or increased nitrogen oxide emission. In order to avoid the adverse consequences of the superheated air supplied to the combustion, a turbocharger, a heat exchanger designed as a charge air cooler is connected downstream, with which the compressed air can be cooled to an allowable temperature before its combustion.
Ein Ladeluftkühler ist beispielsweise in der
Bei Wärmeübertragern wie insbesondere derartigen Ladeluftkühlern sind die Rohre üblicherweise in Öffnungen eines Rohrbodens gesteckt und fluiddicht verlötet. Bei jeder Beladung mit komprimierter Luft unterliegt diese Lötverbindung aufgrund schneller Druckänderungen hohen mechanischen Belastungen. Besonders die Schmalseiten von Flachrohren erfüllen nicht die steigenden Festigkeitsanforderungen, wodurch sich Undichtigkeiten insbesondere in den Seiten des Rohrbodens zugewandten Bereichen solcher Rohr-Boden-Verbindungen ergeben können.In heat exchangers such as in particular such charge air coolers, the tubes are usually inserted into openings of a tube plate and soldered fluid-tight. At any charge of compressed air, this solder joint is subject to high mechanical loads due to rapid pressure changes. Especially the narrow sides of flat tubes do not meet the increasing strength requirements, which may result in leaks especially in the sides of the tubesheet facing areas such pipe-ground connections.
Ein einfacher Weg, um die Festigkeit von Rohr-Boden-Verbindungen zu steigern, ist eine Verwendung von Rohren und/oder Rohrböden mit höherer Wandstärke oder von Außen- und/oder Innenrippen mit höherer Materialstärke. Die vergrößerte mechanische Stabilität ist in beiden Fällen einleuchtend, der dafür benötigte Mehraufwand an Materialkosten und -gewicht jedoch sehr hoch.One simple way to increase the strength of pipe-to-floor joints is to use higher wall thickness pipes and / or tubesheets, or higher and higher strength outer and / or inner ribs. The increased mechanical stability is obvious in both cases, but the extra work required for material costs and weight is very high.
Andere Lösungsvorschläge befassen sich mit einer Verminderung der mechanischen Beanspruchung der Rohr-Boden-Verbindungen durch Verwendung von Zugankern in den Ladeluftkästen. Diese Zuganker stabilisieren die Ladeluftkästen und entlasten dadurch die Rohr-Boden-Verbindungen, bringen jedoch eine Erhöhung des Materialaufwands und des durch den Ladeluftkühler verursachten Druckverlustes mit sich.Other proposed solutions address a reduction in the mechanical stress on the pipe-floor joints by using tie rods in the charge air boxes. These tie rods stabilize the charge air boxes and thereby relieve the pipe-to-floor connections, bring However, an increase in the cost of materials and caused by the intercooler pressure loss with it.
Die
Die Aufgabe der Erfindung ist es, einen Wärmeüberträger, insbesondere einen Ladeluftkühler, bereitzustellen, bei dem mechanische Belastungen von Rohr-Boden-Verbindungen ohne Mehraufwand an Material verringert werden.The object of the invention is to provide a heat exchanger, in particular a charge air cooler, are reduced in the mechanical loads of pipe-floor connections without additional expenditure of material.
Diese Aufgabe wird durch einen Wärmetauscher mit den Merkmalen des Anspruchs 1 gelöst.This object is achieved by a heat exchanger with the features of claim 1.
Gemäß Anspruch 1 weist ein Wärmeübertrager Rohre auf, die geeignet sind, von einem ersten Medium durchströmt und von einem zweiten Medium umströmt zu werden, so daß Wärme von dem ersten auf das zweite Medium oder umgekehrt übertragbar ist. Zumindest ein mit den Rohren kommunizierender Sammelkasten umfaßt zumindest einen Rohrboden, der einen im wesentlichen ebenen Mittelbereich und zumindest einen gegenüber dem Mittelbereich abgewinkelten oder abgerundeten Seitenbereich aufweist. Bevorzugt weist der Rohrboden zwei insbesondere gegenüberliegende Seitenbereiche auf, die gegenüber dem Mittelbereich abgewinkelt oder abgerundet sind. In dem Mittelbereich befinden sich Rohröffnungen, in die die Rohre zu einer Bildung der kommunizierenden Verbindung mit dem Sammelkasten einsteckbar sind.According to claim 1, a heat exchanger tubes, which are adapted to be flowed through by a first medium and to be flowed around by a second medium, so that heat from the first to the second medium or vice versa transferable. At least one collecting box communicating with the tubes comprises at least one tubesheet which has a substantially flat central region and at least one side region angled or rounded off from the central region. The tube bottom preferably has two, in particular opposite, side regions, which are angled or rounded off from the central region. In the central area are tube openings into which the tubes can be inserted to form the communicating connection with the collecting box.
Ausgehend von der Erkenntnis, daß sich die Geometrie des Sammelkastens unter Druckbelastung durch Verformung einer Kugelgestalt annähert, da die Kugelform unter allen dreidimensionalen Körpern bei gegebener Oberfläche das größtmögliche Volumen aufweist, ist es Grundgedanke der Erfindung, die geometrische Form eines Querschnitts des Rohrbodens einem Kreisausschnitt anzunähern, so daß Verformungen, die durch eine Druckbelastung des Sammelkastens auftreten, verringert werden, wodurch Verbindungen von Rohren mit dem Rohrboden mechanisch entlastet werden. Zu diesem Zweck reicht zumindest eine der Rohröffnungen im Mittelbereich des Rohr-bodens in den zumindest einen Seitenbereich hinein. Dadurch ist gewährleistet, daß wenigstens ein dem Seitenbereich zugewandter Bereich der Rohr-Boden-Verbindung an einen gegenüber dem Mittelbereich abgewinkelten oder abgerundeten Bereich des Rohrbodens grenzt. Daraus resultierend befindet sich dieser Bereich der Rohr-Boden-Verbindung in einem Gebiet des Sammelkastens, welches im Falle von Druckbelastungen eine verringerte Verformung und damit weniger mechanische Spannungen aufweist.Starting from the knowledge that the geometry of the collecting box approaches a spherical shape under pressure due to deformation, since the spherical shape has the greatest possible volume of all three-dimensional bodies for a given surface, it is the basic idea of the invention to approximate the geometric shape of a cross section of the tube bottom to a circular cutout , so that deformations, which occur by a pressure load of the collecting tank, are reduced, whereby connections of pipes with the tube sheet are mechanically relieved. For this purpose, at least one of the tube openings extends in the central region of the tube bottom into the at least one side area. This ensures that at least one region of the pipe-floor connection facing the side region adjoins an area of the pipe bottom which is angled or rounded off from the central region. As a result, this area of the pipe-floor connection is located in a region of the collecting tank, which in the case of pressure loads has a reduced deformation and thus less mechanical stress.
Durch die erfindungsgemäße Ausgestaltung des Wärmeübertragers werden dessen mechanische Festigkeit und damit auch dessen Lebensdauer erhöht, ohne daß dafür ein Mehraufwand an Material, Teilezahl oder Fertigungszeit nötig wäre.Due to the inventive design of the heat exchanger whose mechanical strength and thus its life is increased, without the need for extra effort on material, parts number or production time would be necessary.
Ein Mittelbereich eines Rohrbodens ist im Rahmen der vorliegenden Erfindung dann als im wesentlichen eben anzusehen, wenn der Rohrboden in diesem Bereich größtenteils eben ist. Insbesondere ein Rohrbodenmittelbereich mit als sogenannte Durchzüge umgeformten Umrandungen von Rohröffnungen und/oder mit anderen geringfügingen Abweichungen von einer Ebenheit ist im Rahmen der Erfindung im wesentlichen eben.In the context of the present invention, a middle region of a tube plate is to be regarded as essentially flat if the tubesheet is largely flat in this region. In particular, a tube bottom middle region with outlines of tube openings formed as so-called passages and / or with other minor deviations from a flatness is essentially planar in the context of the invention.
Der Rohrboden weist Durchzüge auf, die die Rohröffnungen begrenzen, die erfindungsgemäß aus dem Sammelkasten herausweisen. Diese Durchzüge dienen einer vergrößerten Kontaktfläche zwischen den eingesteckten Rohren und dem Rohrboden, wodurch die Rohr-Boden-Verbindung verstärkt wird. Besonders vorteilhaft ist der Durchzug der zumindest einen Rohröffnung am beziehungsweise im zumindest einen Seitenbereich niedriger als im Mittelbereich des Rohrbodens. Dadurch wird eine Angriffsfläche für aus dem Seitenbereich herrührende mechanische Spannungen an der Rohr-Boden-Verbindung verkleinert, während eine hohe Stabilität der Rohr-Boden-Verbindung im Mittelbereich des Rohrbodens aufrechterhalten bleibt.The tubesheet has passages which delimit the tube openings which according to the invention point out of the collection box. These passages serve to increase the contact area between the inserted tubes and the tubesheet, thereby enhancing the tube-to-floor connection. The passage of the at least one pipe opening on or in the at least one side region is particularly advantageously lower than in the middle region of the pipe bottom. As a result, an attack surface for mechanical stresses originating from the side region is reduced at the tube-bottom connection, while a high stability of the tube-bottom connection in the middle region of the tube bottom is maintained.
Vorteilhafte Ausführungsformen der Erfindung sind Gegenstand der Unteransprüche.Advantageous embodiments of the invention are the subject of the dependent claims.
Gemäß einer Ausführungsform umfaßt der zumindest eine Seitenbereich des Rohrbodens einen oder mehrere ebene Teilbereiche, so daß der Sammelkasten eine facettierte Form aufweist. Dies ermöglicht eine sichere Herstellung mit niedrigen Fertigungstoleranzen.According to one embodiment, the at least one side region of the tube bottom comprises one or more flat partial regions, so that the collecting container has a faceted shape. This allows a secure production with low manufacturing tolerances.
Bevorzugt weist der zumindest eine Seitenbereich eine Rundung mit etwa konstantem Krümmungsradius oder mehrere Rundungen mit verschiedenen Krümmungsradien auf. Dadurch wird eine besonders gute Annäherung an einen halbkreisförmigen Querschnitt des Rohrbodens erreicht.Preferably, the at least one side region has a rounding with an approximately constant radius of curvature or a plurality of curves with different Curvature radii on. As a result, a particularly good approximation to a semicircular cross section of the tube bottom is achieved.
Ebenfalls einer verbesserten Annäherung an eine Halbkreisform des Rohrbodenquerschnitts dient eine durchgehend konvexe Ausbildung des zumindest einen Seitenbereichs. Konkave Teilbereiche starken Verformungen im Falle von Druckbelastungen werden dadurch vermieden.Also, an improved approach to a semicircular shape of the tube bottom cross-section is a continuous convex design of the at least one side region. Concave areas of strong deformation in the case of pressure loads are thereby avoided.
Gemäß einer bevorzugten Weiterbildung ist der erfindungsgemäße Wärmeübertrager als Ladeluftkühler ausgebildet, der besonders bevorzugt in Kraftfahrzeugen einsetzbar ist. Insbesondere weist der Ladeluftkühler zwei Sammelkästen auf, von denen ein erster zur Verteilung und ein zweiter zur Sammlung von Ladeluft vorgesehen ist. Vorteilhafterweise weist jeder der Sammelkästen genau einen Rohrboden auf, der mit einer Reihe von Rohröffnungen versehen ist. Auch ist es vorteilhaft, eine Reihe von Flachrohren mit dazwischenliegenden, insbesondere verlöteten Wellrippen zu verwenden, da hierdurch eine vergrößerte Wärmeübertragungsfläche erreicht wird. Als Kühlmedium dient vorzugsweise Luft, wobei auch andere Kühlmedien wie Wasser oder Kühlmittel denkbar sind.According to a preferred embodiment of the heat exchanger according to the invention is designed as a charge air cooler, which is particularly preferably used in motor vehicles. In particular, the intercooler on two headers, of which a first for distribution and a second is provided for the collection of charge air. Advantageously, each of the headers has exactly one tubesheet, which is provided with a series of tube openings. It is also advantageous to use a series of flat tubes with intermediate, in particular soldered, corrugated fins, as this achieves an increased heat transfer area. As the cooling medium is preferably air, although other cooling media such as water or coolant are conceivable.
Die Erfindung wird nachfolgend anhand von Ausführungsbeispielen unter Bezugnahme auf die Zeichnungen erläutert. Es zeigen:
- Fig. 1a:
- einen Ausschnitt eines Wärmeübertragers,
- Fig. 1b:
- einen Ausschnitt eines Wärmeübertragers,
- Fig. 1c:
- einen Querschnitt eines Wärmeübertragers,
- Fig. 2a:
- einen Ausschnitt eines Wärmeübertragers gemäß der vorliegenden Erfindung,
- Fig. 2b:
- einen Ausschnitt eines Wärmeübertragers und
- Fig. 2c:
- einen Querschnitt eines Wärmeübertragers.
- Fig. 1a:
- a section of a heat exchanger,
- Fig. 1b:
- a section of a heat exchanger,
- Fig. 1c:
- a cross section of a heat exchanger,
- Fig. 2a:
- a detail of a heat exchanger according to the present invention,
- Fig. 2b:
- a section of a heat exchanger and
- Fig. 2c:
- a cross section of a heat exchanger.
Fig. 1a zeigt einen Ausschnitt aus einem Wärmeübertrager 10 in einer perspektivischen Darstellung. Ein Sammelkasten 20 zur Verteilung eines ersten Mediums besteht aus einem Rohrboden 30 und einem Kastendeckel 40, die an einer gemeinsamen Berührungsfläche 50 miteinander verschweißt sind. Der Kastendeckel 40 ist hierbei in den Rohrboden 30 hineingesteckt. Es ist aber ebenso denkbar, den Kastendeckel 40 auf den Rohrboden 30 aufzustecken oder anderweitig an dem Rohrboden 30 anzubringen. Bei anderen, nicht gezeigten Ausführungsbeispielen sind ein Rohrboden und ein Kastendeckel durch Lötung, Verklebung oder formschlüssig miteinander verbunden beziehungsweise einteilig oder einstückig, das heißt beispielsweise aus einer umgeformten Platte bestehend, ausgebildet.Fig. 1a shows a section of a
Der Rohrboden 30 weist eine Rohröffnung 60 auf, deren Rand 70 als sogenannter Durchzug in das Sammelkasteninnere hinein umgeformt ist. Ein im wesentlichen rechteckiges Flachrohr 80 ist in die Rohröffnung 60 gesteckt und mit dem Rohrboden 30 verlötet oder verschweißt. Nicht dargestellt sind Wellrippen, die beidseits an das Flachrohr 80 angrenzen und mit letzterem verlötet sind, so daß ein Wärmeübertrag von dem ersten auf ein das Rohr 80 und die Rippen umströmendes zweites Medium oder von dem zweiten auf das erste Medium gesteigert wird. Insgesamt umfaßt der Wärmeübertrager 10 eine ganze Reihe von sich abwechselnden Flachrohren und Wellrippen, die einen sogenannten Rohr-Rippen-Block bilden.The
Wie in der Seitenansicht in Fig.. 1b zu erkennen ist, ist das Rohr 80 so weit in die Rohröffnung 60 hineingesteckt, daß ein oberer Randbereich 90 des Rohres 80 über den Durchzug 70 hinausragt. Dadurch wird eine gute Ausnutzung einer dem Rohr 80 zugewandten, nicht sichtbaren Innenfläche des Durchzugs 70 als Anlagefläche für eine Rohr-Boden-Verbindung gewährleistet.- Dies dient beispielsweise einer dichten Verlötung. Um einen unnötig hohen Druckabfall des ersten Mediums über den Wärmeübertrager zu vermeiden, ist der Überstand des Rohres 80 über den Rohrboden 30 so gering wie möglich zu halten. Aus diesem Grund befindet sich die Rohröffnung 60 in einem im wesentlichen ebenen Mittelbereich 100 des Rohrbodens 30.As can be seen in the side view in Fig. 1b, the
Wird der Sammelkasten 20 mit dem ersten Medium beaufschlagt, verformt sich der Sammelkasten 20 unter Umständen derart, daß sich seine Querschnittsform einer Kreisform annähert. Um eine solche Verformung quasi vorwegzunehmen, sind Seitenbereiche 110, 120 des Rohrbodens 30 gegenüber dem Mittelbereich 100 abgewinkelt. Daraus resultiert eine geringere Verformung des Rohrbodens 30 unter Druckbelastung des Sammelkastens 20 in diesen Seitenbereichen 110, 120. Die bei solchen druckbedingten Verformungen mechanisch am stärksten beanspruchten Stirnseiten 130; 140 des Flachrohres 80 werden dadurch entlastet, daß die Rohröffnung 60 und damit auch das Rohr 80 in die Seitenbereiche 110, 120 des Rohrbodens 30 hineinreichen. Die dort vorliegende reduzierte Verformung des Rohrbodens 30 bringt eine Verringerung der mechanischen Belastung des Rohres 80 beziehungsweise der Rohr-Boden-Verbindung mit sich.If the
Fig. 1c zeigt einen Querschnitt des Wärmeübertragerausschnitts aus Fig. 1a beziehungsweise Fig. 1b, wobei die Schnittebene quer durch das Rohr 80 verläuft. Bei einem Vergleich dieser Ansicht mit Fig. 1b wird deutlich, daß durch das Hineinreichen der Rohröffnung 60 in die gegenüber dem Mittelbereich 100 abgewinkelten Seitenbereiche 110, 120 des Rohrbodens 30 der Durchzug 70 an den Stirnseiten 130, 140 des Flachrohres 80 eine reduzierte Höhe aufweist. Dadurch ergibt sich der zusätzliche Vorteil, daß für druckbedingte Verformungen eine verringerte Angriffsfläche am Rohr 80 besteht. Die gleichzeitig in Kauf genommene Verkleinerung der Anlagefläche für die Rohr-Boden-Verbindung ist tolerierbar, da ein wesentlich größerer Teil des Durchzugs 70 in dem ebenen Mittelbereich 100 des Rohrbodens 30 eine für die Stabilität der Rohr-Boden-Verbindung ausreichende Höhe behält.FIG. 1 c shows a cross section of the heat exchanger section from FIG. 1 a or FIG. 1 b, wherein the sectional plane extends transversely through the
In Fig. 2a, 2b und 2c ist analog zu Fig. 1a, 1b und 1c ein Ausführungsbeispiel des erfindungsgemäßen Wärmeübertragers 210 dargestellt, das sich von dem vorherigen Ausführungsbeispiel im wesentlichen dadurch unterscheidet, daß der Durchzug 270 aus dem Sammelkasten 220 herausweisend umgeformt ist. Der Rohrboden 230 ist mit einem Kastendeckel 240 an der gemeinsamen Berührungsfläche 250 Verschweißt. Ein im wesentlichen rechteckiges Flachrohr 280 ist in die Rohröffnung 260 mit dem Durchzug 270 gesteckt und mit dem Rohrboden 230 verlötet oder verschweißt.In Fig. 2a, 2b and 2c, an embodiment of the
Um einen Druckabfall eines durch den Sammelkasten 220 und unter anderen durch das Rohr 280 strömenden ersten Mediums über den Wärmeübertrager zu reduzieren, weist der Durchzug 270 aus dem Sammelkasten 220 heraus, so daß das in dem Durchzug 270 steckende Rohr 280 nicht über den Rohrboden 230 in dessen im wesentlichen ebenen Mittelbereich 300 hinausragt. Seitenbereiche 310, 320 des Rohrbodens 230 sind gegenüber dem Mittelbereich 300 abgewinkelt, um eine Verformung des Sammelkastens 220 unter Druckbelastung zumindest in den Seitenbereichen 310, 320 zu reduzieren. Zu einer Entlastung der Stirnseiten 330, 340 des Flachrohrs 280 reichen die Rohröffnung 260 und damit das Rohr 280 an die Seitenbereiche 310, 320 heran, was in Fig. 2c besonders gut verdeutlicht wird.In order to reduce a pressure drop of a first medium flowing through the
Der Vorteil der verringerten Durchzugshöhe fällt bei diesem Ausführungsbeispiel zwar weg, durch den s-förmigen Querschnitt des Rohrbodens 230 im Bereich Deckelanschluß 250 - Seitenbereich 310/320 - Durchzug 270 wird dem Rohr 280 beziehungsweise der Rohr-Boden-Verbindung jedoch ebenfalls eine Belastungsreduktion zuteil.Although the advantage of the reduced draft height is omitted in this embodiment, by the s-shaped cross section of the
Claims (7)
- A heat exchanger having tubes and at least one collecting box in which the collecting box has at least a tube base (230) and a box lid (240), the tube base (230) having an essentially flat central area (300) with tube openings (260) into which the tubes can be inserted and at least one lateral area (310) angled or curved in relation to the central area, at least one tube opening (260) extending into the at least one lateral area (310) and the at least one tube opening (260) being delimited by a rim hole (270),
characterised in that
the rim hole (270) points out of the at least one collecting box and the tube base (230) has an S-shaped cross-section in the area of common contact surfaces (250) between the tube base (230) and the box cover (24) - lateral area (310). - A heat exchanger in accordance with claim 1,
characterised in that
the at least one lateral area (310) has at least one flat part. - A heat exchanger in accordance with claim 1 or 2,
characterised in that
the at least one lateral area (310) has a curve with an approximately constant radius of curvature. - A heat exchanger in accordance with claim 3,
characterised in that
the at least one lateral area (310) has a plurality of curves with different radii of curvature. - A heat exchanger in accordance with one of claims 1 to 4,
characterised in that
the at least one lateral area (310) is convex in shape. - A heat exchanger in accordance with one of claims 1 to 5,
characterised in that
the rim hole (270) is lower at or in at least one lateral area (310) of the tube floor than in the central area of the tube floor. - An intercooler, in particular for a motor vehicle,
characterised by
the features of one of the preceding claims.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10256869 | 2002-12-04 | ||
| DE10256869A DE10256869A1 (en) | 2002-12-04 | 2002-12-04 | Heat exchanger |
| PCT/EP2003/012138 WO2004051175A1 (en) | 2002-12-04 | 2003-10-31 | Heat exchanger |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1570223A1 EP1570223A1 (en) | 2005-09-07 |
| EP1570223B1 true EP1570223B1 (en) | 2007-06-13 |
Family
ID=32336007
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP03788989A Expired - Lifetime EP1570223B1 (en) | 2002-12-04 | 2003-10-31 | Heat exchanger |
Country Status (9)
| Country | Link |
|---|---|
| US (1) | US7156164B2 (en) |
| EP (1) | EP1570223B1 (en) |
| JP (1) | JP2006509177A (en) |
| CN (1) | CN100390492C (en) |
| AT (1) | ATE364827T1 (en) |
| AU (1) | AU2003293643A1 (en) |
| BR (1) | BR0307932A (en) |
| DE (2) | DE10256869A1 (en) |
| WO (1) | WO2004051175A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7413006B2 (en) * | 2006-04-06 | 2008-08-19 | Modine Manufacturing Company | Header plate for use in a heat exchanger |
| DE202008011555U1 (en) * | 2008-08-28 | 2010-01-07 | Autokühler GmbH & Co. KG | Collecting box for a charge air cooler |
| CN101832720B (en) * | 2010-04-24 | 2011-10-05 | 李宁辉 | Flue for heat exchange |
| US8851157B2 (en) | 2010-05-13 | 2014-10-07 | Adams Thermal Systems, Inc. | Partial reverse ferrule header for a heat exchanger |
| US20120018135A1 (en) * | 2010-07-20 | 2012-01-26 | Denso Marston Ltd. | Header plate, a heat exchanger, a method of making a header plate and a method of making a heat exchanger |
| FR2973492B1 (en) * | 2011-03-31 | 2017-12-15 | Valeo Systemes Thermiques | COLLECTOR BOX FOR A HEAT EXCHANGER, IN PARTICULAR FOR A MOTOR VEHICLE, AND THERMAL EXCHANGER THEREFOR |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2196730B (en) * | 1986-10-21 | 1991-06-26 | Austin Rover Group | A heat exchanger |
| JPH02109184U (en) * | 1989-02-17 | 1990-08-30 | ||
| DE4130517B4 (en) * | 1991-09-13 | 2005-12-01 | Behr Gmbh & Co. Kg | Connection box for a heat exchanger, in particular for a refrigerant condenser |
| US5307870A (en) * | 1991-12-09 | 1994-05-03 | Nippondenso Co., Ltd. | Heat exchanger |
| DE4327213C2 (en) * | 1993-08-13 | 1997-12-11 | Ruecker Gmbh | Recuperative heat exchangers, in particular coolers for motor vehicles |
| JPH0829089A (en) | 1994-07-19 | 1996-02-02 | Nippondenso Co Ltd | Heat exchanger and air conditioner using the same heat exchanger |
| JPH10132487A (en) | 1996-10-30 | 1998-05-22 | Toyo Radiator Co Ltd | Manufacture of heat exchanger tank and heat exchanger |
| DE19757034A1 (en) * | 1997-12-20 | 1999-06-24 | Behr Gmbh & Co | Heat exchanger |
| GB0016604D0 (en) | 2000-07-07 | 2000-08-23 | Llanelli Radiators Ltd | Condenser headers |
| DE10114078A1 (en) * | 2001-03-22 | 2002-09-26 | Modine Mfg Co | Heat exchangers and manufacturing processes |
-
2002
- 2002-12-04 DE DE10256869A patent/DE10256869A1/en not_active Withdrawn
-
2003
- 2003-10-31 BR BR0307932-5A patent/BR0307932A/en not_active IP Right Cessation
- 2003-10-31 CN CNB2003801051299A patent/CN100390492C/en not_active Expired - Lifetime
- 2003-10-31 EP EP03788989A patent/EP1570223B1/en not_active Expired - Lifetime
- 2003-10-31 AT AT03788989T patent/ATE364827T1/en not_active IP Right Cessation
- 2003-10-31 WO PCT/EP2003/012138 patent/WO2004051175A1/en active IP Right Grant
- 2003-10-31 JP JP2004556098A patent/JP2006509177A/en active Pending
- 2003-10-31 DE DE50307492T patent/DE50307492D1/en not_active Expired - Lifetime
- 2003-10-31 AU AU2003293643A patent/AU2003293643A1/en not_active Abandoned
- 2003-10-31 US US10/520,703 patent/US7156164B2/en not_active Expired - Lifetime
Non-Patent Citations (1)
| Title |
|---|
| None * |
Also Published As
| Publication number | Publication date |
|---|---|
| BR0307932A (en) | 2004-12-21 |
| ATE364827T1 (en) | 2007-07-15 |
| US20050252648A1 (en) | 2005-11-17 |
| DE10256869A1 (en) | 2004-06-24 |
| US7156164B2 (en) | 2007-01-02 |
| EP1570223A1 (en) | 2005-09-07 |
| WO2004051175A1 (en) | 2004-06-17 |
| AU2003293643A1 (en) | 2004-06-23 |
| CN100390492C (en) | 2008-05-28 |
| DE50307492D1 (en) | 2007-07-26 |
| WO2004051175A8 (en) | 2004-08-19 |
| JP2006509177A (en) | 2006-03-16 |
| CN1720423A (en) | 2006-01-11 |
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