EP2486356B1 - Inner heat exchanger, particularly for motor vehicle air conditioners - Google Patents

Inner heat exchanger, particularly for motor vehicle air conditioners Download PDF

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Publication number
EP2486356B1
EP2486356B1 EP10752757.4A EP10752757A EP2486356B1 EP 2486356 B1 EP2486356 B1 EP 2486356B1 EP 10752757 A EP10752757 A EP 10752757A EP 2486356 B1 EP2486356 B1 EP 2486356B1
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EP
European Patent Office
Prior art keywords
heat exchanger
inner heat
exchanger according
pipe
individual pipes
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EP10752757.4A
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German (de)
French (fr)
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EP2486356A2 (en
Inventor
Claus Röck
Andreas Gorzel
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ContiTech Kuehner GmbH and Cie KG
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ContiTech Kuehner GmbH and Cie 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • 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
    • 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
    • F28F9/0246—Arrangements for connecting header boxes with flow lines
    • F28F9/0251—Massive connectors, e.g. blocks; Plate-like connectors
    • F28F9/0253—Massive connectors, e.g. blocks; Plate-like connectors with multiple channels, e.g. with combined inflow and outflow channels

Definitions

  • the invention relates to an inner heat exchanger according to the preamble of claim 1.
  • a heat exchanger is from document US Pat. No. 6,625,235 known.
  • Internal heat exchangers are used as fuel coolers, as cooling elements for oil pressure pipes and as heat exchangers for stationary cooling systems. They are generally used for cooling fluid or gas transporting media. A major application of the internal heat exchangers is in automotive air conditioning systems.
  • a one-piece heat exchanger tube with a multi-chamber profile which has a central channel, around which a plurality of outer channels are arranged.
  • the outer channels are divided by intermediate walls which extend in the radial direction.
  • projections are provided which extend into the central channel. These projections serve to reduce the cross-sectional area and thus increase the Flow rate.
  • the projections may be helical.
  • the inner channel is used as a high-pressure side
  • the outer channels are used as a low-pressure side.
  • the heat exchange is not optimal in this device, since the outer channels are arranged on a concentric circle around the central channel and lie only with their inclined toes in the vicinity of the high pressure side refrigerant fluid leading to the central channel.
  • the heat transfer between the refrigerant fluid in the central channel and the cooler refrigerant fluid in the outer channels is thus not very efficient.
  • an internal heat exchanger which is constructed from a two-part coaxial tube system.
  • an inner tube is inserted or coextruded together with the outer tube.
  • the annular space between inner tube and outer tube represents an outer tube longitudinal channel, which is divided by webs or corrugated ribs into a plurality of parallel outer longitudinal channels.
  • These outer longitudinal channels can take a helical course to extend the flow path for the refrigerant passed therethrough.
  • From the DE 10 2005 056 651 A1 is designed as a coaxial tube inner heat exchanger known, which is designed for the separate management of the two, different pressure level having refrigerant flows.
  • a turbulence generator is provided in the form of a helix.
  • the helix deflects the refrigerant flowing in the inner tube, so that no laminar flow can form in the wall region. This is intended to produce improved mixing and improved heat exchange.
  • the countercurrent leading outer channels are located in an annular wall of the coaxial tube around the inner tube. An efficient heat transfer is not possible.
  • the invention has the object of providing an inner heat exchanger of the type described above in such a way that the efficiency of heat transfer between the two separated by the inner heat exchanger conducted fluid flows is increased.
  • connection components are provided at both ends of the cylindrical flow body, via which the fluids which flow through the inner heat exchanger mainly in countercurrent, separately from each other or are derived ,
  • the Koaxialrohr principle of an inner heat exchanger with an outer tube and a coaxially disposed therein inner tube to form an outer longitudinal channels having annular space is abandoned.
  • a circular bundle of individual tubes is arranged in a cylinder-shaped flow body representing the housing, which each lead a subset of the fluid flow to be cooled.
  • These individual tubes are each arranged in a separate tube longitudinal channel and are lapped therein over the housing length of the cooling fluid flow in direct contact. This allows a particularly efficient heat transfer, which can not be realized in the indirect contact principle of the known from the prior art designs.
  • annular wall set at a distance from the end of the flow body defines a cavity in which the individual flows of the cooling fluid come together again coming from the longitudinal bores.
  • the outer tube forms at its ends a projection over the flow body, in which the respective connecting parts can be inserted sealingly.
  • outer tube and flow body are integrally formed. This has essentially manufacturing advantages.
  • the individual tubes have a star-shaped cross-section.
  • the cooling surface is increased again due to the larger surface area.
  • connection components advantageous embodiments of the structure of the connection components are disclosed.
  • the design and arrangement of a distributor ring on the outer connecting flange serves for uniform distribution of the fluid flow to be cooled.
  • a mushroom-shaped, axially extending spacer is arranged at the opposite end face of the baffle surface, in the collar-shaped periphery semicircular recesses for receiving the ends of the individual tubes are arranged.
  • the mushroom-like shape prevents the cooling fluid flow from tearing off. The individual tubes are safely washed over their entire length and the entire peripheral surface.
  • Extending axially outwardly spaced cams on the spacer form a clearance space in which the partial flows of the cooling fluid flow can flow together again.
  • continuous webs dividing the pipe interior into subchannels are arranged continuously in the individual pipes and the webs have a subdivision of the pipe inside cross section cross-shaped arrangement on.
  • the flow rate of the cooling fluid flow and the heat transfer coefficient are increased by this design.
  • the invention provides a powerful internal heat exchanger in a compact design, which is particularly suitable for applications in motor vehicle air conditioning systems, in particular in CO 2 air conditioning systems of motor vehicles.
  • This inner heat exchanger is also suitable for use as a high-performance fuel cooler in the automotive sector. It is applicable everywhere, where by means of internal heat exchanger two fluid streams with different temperature level heat transfer are passed to each other.
  • the in Fig. 1 shown inner heat exchanger has an outer tube 11 and a suitably inserted into the outer tube 11, cylinder-shaped flow body 20.
  • this flow body 20 lying on a circumference nine individual tubes 12 are arranged axially parallel.
  • a fluid flow to be cooled (hereinafter referred to as "hot” fluid flow) runs in the direction of the arrow A.
  • the cooling countercurrent (hereinafter referred to as "cold” fluid flow) is guided by the flow body 20 and flows through the heat exchanger in the direction of the arrow B.
  • the flow body 20 will be explained in more detail elsewhere.
  • connection components 13, 14 and 15, 16 are respectively provided at both ends of the flow body 20, via which the fluid flows are separated from one another predominantly in countercurrent operation be added or derived.
  • connection component 13, 14 or 15, 16 is essentially constructed in two parts from an outer connection flange 14 or 16 and a respective collector flange 13 or 15.
  • Each collector flange 13 and 15 respectively has nine through-connection openings 17, which receive the ends of the nine individual tubes 12 tightly after assembly of the heat exchanger.
  • the connection openings 17 terminate in an annular collection channel 18 formed by plugging together the connection flange 14 or 16 with the respective header flange 13 or 15, which via a connection bore 19 located outside the central axis in the connection flange 14 or 16 with the corresponding, not shown here Fluid circuit is connected.
  • connection components 13, 14 and 15, 16 are of identical design and each have a continuous, central central opening 21 which is sealed with the flow body 20 and connects the flow body 20 flowing through cold fluid with the corresponding, not shown here fluid circuit.
  • the respective connection component 13, 14 or 15, 16 is mounted as follows with the heat exchanger housing ( Fig. 1 and Fig. 6 to Fig. 8 ).
  • the collector flange 13 and 15 has a central connecting piece 22 with two circumferential grooves 23 and 24, in each of which a sealing ring 25 and 26 is introduced.
  • the collector flange 13 and 15 is inserted with its connecting piece 22 fitting sealingly in a protruding edge region of the outer tube 11 and the front side sealingly connected to the individual tubes 12 of the flow body 20.
  • the outer connecting flanges 14 and 16 each have two mutually coaxially arranged sockets 28 and 29.
  • the connecting piece 28 with the larger diameter has a circumferential groove 31 for receiving a sealing ring 32.
  • the sealing nozzle 29 with a smaller diameter also has a circumferential groove 34 for receiving a further sealing ring 33.
  • the connecting piece 28 is formed as an annular wall which surrounds a circumferential distribution ring 35, which has a central Opening 50 which has a larger inner diameter than the outer diameter of the protruding smaller sealing nozzle 29th
  • the distributor ring 35 is clamped with an outer bent-back collar 51 on the free end of the connecting piece 28. At the other end of the distributor ring 35, this has a radially inwardly projecting bottom 52, whose end 53 extends axially bent back.
  • the bottom 52 of the distributor ring 35 divides the annular space within the connecting piece 28 into two distributor spaces 18 and 54.
  • the connecting flange 14 or 16 is inserted with its connecting piece 28 in the collector flange 13 and 15 respectively.
  • the small sealing nozzle 29 seals the inlet and outlet of the cold fluid flow to the flow body 20 in the connecting piece 22 of the collector flange 13 and 15 from.
  • the bearing lugs 27 in the collector flanges 13, 15 and the connecting flanges 14 and 16 serve to fasten the flanges together and the tight clamping of the flow body 20th
  • Connection component 15, 16 and connection component 13, 14 are constructed identically in this embodiment. But it may also be sufficient to provide the distributor ring 35 only in the connection component 15, 16, which is provided in the inflow direction of the hot fluid flow.
  • the distributor ring 35 serves to distribute the hot fluid flow supplied via the connection bore 19 located outside the center axis, which is distributed via the two distributor spaces 18 and 54 over the entire annular cross section in the connection flange 14 or 16 and thus uniformly all the connection openings 19 in the respective collector flange 13 or 15 reached.
  • the flow body 20 which is suitably inserted into the outer tube 11 over almost its entire length, has turbulence in the incoming cold fluid flow produce a pointed outward baffle 42 (FIG. Fig. 2 ).
  • the flow body 20 is in each case perforated over its entire length ( Fig. 5 ), wherein for each individual tube 12 a single opening in the form of a longitudinal bore 43 with a larger inner diameter than the outer diameter of the respective individual tube 12 is provided.
  • the introduced cold fluid stream strikes the baffle 42, which has a central, tip-shaped protrusion 44. As a result, the cold fluid flow is deflected radially to the longitudinal bores 43. The cold fluid flow flows through the annular gaps 45, which are located between the outer circumference of the individual tubes 12 and the respective longitudinal bore 43 of the flow body 20 ( Fig. 2 ).
  • Each individual tube 12 is surrounded by a partial flow of the cold fluid flow in the associated longitudinal bore 43, which represents a tube longitudinal channel. This results in a defined cooling with improved heat exchange.
  • annularly covering wall 46 (FIG. Figure 3 and Fig. 5 ) is arranged at an axial distance from the main body of the flow body 20, which has a central opening 47 for the outflow of the cold fluid flow. Due to the axial distance of the wall 46, a cylindrical cavity 48 is formed at the end of the flow body 20.
  • the annular surface of the wall 46 is pierced by lying on a circumference receiving holes 49 through which the ends of the individual tubes 12 of the tube bundle suitably to be connected via the aligned connection openings 17 of the collecting flange 15 with the annular distribution space 18 in the connection member 15, 16 ,
  • the flow body 20 forms with its longitudinal bores 43 inner, axially parallel pipe longitudinal channels, in which the parallel individual tubes 12 are arranged.
  • the cold fluid conducted through the flow body 20 can directly contact and flush around the individual tubes 12 carrying the hot fluid flow, so that efficient cooling of the hot fluid flow flowing in the individual tubes 12 takes place.
  • the guidance of the cold and hot fluids may alternatively be provided in cocurrent or countercurrent.
  • FIG. 9 to 13 an alternative embodiment of the flow body 20 'is shown.
  • connection openings 18 Collecting duct, distribution room 19 connecting holes 20 cylindrical flow body 21 Central openings, inlet and outlet bores 22 spigot 23 circumferential groove 24 circumferential groove 25 seal 26 seal 27 bearing eyes 28 spigot 29 tight fitting 31 groove 32 seal 33 seal 34 circumferential groove 35 distribution ring 42 baffle 43 longitudinal bores 44 Central bulge 45 Annular column 46 Circular wall 47 Central opening 48 cavity 49 mounting holes 50 Opening distribution ring 51 collar 52 ground 53 End distribution ring 54 distribution space 20 ' Flow body 60 spacer 61 recesses 62 spacer lugs

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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)

Description

Die Erfindung betrifft einen inneren Wärmetauscher nach dem Oberbegriff des Anspruchs 1. So ein Wärmetauscher ist aus Dokument US 6 625 235 bekannt.The invention relates to an inner heat exchanger according to the preamble of claim 1. Such a heat exchanger is from document US Pat. No. 6,625,235 known.

Innere Wärmetauscher werden als Kraftstoffkühler, als Kühlorgan für Öldruckleitungen und als Wärmetauscher für stationäre Kühlanlagen benutzt. Sie werden generell zur Kühlung von fluid- oder gastransportierenden Medien angewandt. Eine Hauptanwendung der inneren Wärmetauscher ist in Kraftfahrzeugklimaanlagen.Internal heat exchangers are used as fuel coolers, as cooling elements for oil pressure pipes and as heat exchangers for stationary cooling systems. They are generally used for cooling fluid or gas transporting media. A major application of the internal heat exchangers is in automotive air conditioning systems.

Eine Möglichkeit zur Effizienzsteigerung von Klimaanlagen, die in Kraftfahrzeugen zum Einsatz kommen, ist der Einsatz eines inneren Wärmetauschers, in dem niederdruckseitiger Rücklauf und hochdruckseitiger Vorlauf des Kältemittels in voneinander getrennten, aber benachbarten Kanälen realisiert sind. Durch dieses benachbarte, im Gegen- oder Gleichstrom betriebene getrennte Führen der beiden Kältemittelströme wird das Kältemittel im hochdruckseitigen Kanal zusätzlich heruntergekühlt, ohne dass dafür zusätzliche Energie verbraucht wird.One way to increase the efficiency of air conditioning systems, which are used in motor vehicles, is the use of an internal heat exchanger, are implemented in the low-pressure side return and high-pressure side flow of the refrigerant in separate, but adjacent channels. By this adjacent, operated in counter or DC separate guiding the two refrigerant streams, the refrigerant is additionally cooled down in the high-pressure side channel, without that additional energy is consumed.

Aus der EP 1 202 016 A2 ist ein einstückiges Wärmetauscherrohr mit einem Mehrkammerprofil bekannt, das einen Zentralkanal aufweist, um den mehrere Außenkanäle angeordnet sind. Die Außenkanäle sind durch Zwischenwände, die in radialer Richtung verlaufen, unterteilt. An der Wandung des Zentralkanals sind Vorsprünge vorgesehen, die sich in den Zentralkanal hinein erstrecken. Diese Vorsprünge dienen der Verringerung der Querschnittsfläche und somit der Erhöhung der Strömungsgeschwindigkeit. Die Vorsprünge können wendelförmig ausgebildet sein. Der Innenkanal wird als Hochdruckseite, die Außenkanäle werden als Niederdruckseite verwendet. Der Wärmeaustausch ist bei dieser Vorrichtung nicht optimal, da die Außenkanäle auf einem konzentrischen Kreis um den Zentralkanal angeordnet und nur mit ihren geneigten Fußspitzen in der Nähe des das hochdruckseitige Kältemittelfluid führenden Zentralkanals liegen. Der Wärmeübergang zwischen dem Kältemittelfluid in dem Zentralkanal und dem kühleren Kältemittelfluid in den Außenkanälen ist somit nicht sonderlich effizient.From the EP 1 202 016 A2 is a one-piece heat exchanger tube with a multi-chamber profile is known which has a central channel, around which a plurality of outer channels are arranged. The outer channels are divided by intermediate walls which extend in the radial direction. On the wall of the central channel projections are provided which extend into the central channel. These projections serve to reduce the cross-sectional area and thus increase the Flow rate. The projections may be helical. The inner channel is used as a high-pressure side, the outer channels are used as a low-pressure side. The heat exchange is not optimal in this device, since the outer channels are arranged on a concentric circle around the central channel and lie only with their inclined toes in the vicinity of the high pressure side refrigerant fluid leading to the central channel. The heat transfer between the refrigerant fluid in the central channel and the cooler refrigerant fluid in the outer channels is thus not very efficient.

Aus der DE 199 44 950 A1 ist ein innerer Wärmetauscher bekannt, der aus einem zweiteiligen Koaxialrohrsystem aufgebaut ist. In ein Außenrohr des Koaxialrohrsystems ist ein Innenrohr eingeschoben bzw. zusammen mit dem Außenrohr koextrudiert. Der Ringraum zwischen Innenrohr und Außenrohr stellt einen äußeren Rohrlängskanal dar, der durch Stege oder Wellrippen in mehrere parallele Außenlängskanäle aufgeteilt ist. Diese Außenlängskanäle können einen wendelförmigen Verlauf nehmen, um den Strömungsweg für das dort hindurchgeleitete Kältemittel zu verlängern. Dadurch wird zwar der Wärmekontakt zwischen diesem Kältemittelstrom und dem durch das Innenrohr hindurchgeleiteten Kältemittelstrom erhöht, eine weitere signifikante Effizienzerhöhung der Klimaanlage ist aber noch nicht erreicht.From the DE 199 44 950 A1 an internal heat exchanger is known which is constructed from a two-part coaxial tube system. In an outer tube of the coaxial tube system, an inner tube is inserted or coextruded together with the outer tube. The annular space between inner tube and outer tube represents an outer tube longitudinal channel, which is divided by webs or corrugated ribs into a plurality of parallel outer longitudinal channels. These outer longitudinal channels can take a helical course to extend the flow path for the refrigerant passed therethrough. Although this increases the thermal contact between this refrigerant flow and the refrigerant flow conducted through the inner tube, a further significant increase in the efficiency of the air conditioning system has not yet been achieved.

Aus der DE 10 2005 056 651 A1 ist ein als Koaxialrohr ausgebildeter innerer Wärmetauscher bekannt, der für die getrennte Führung der beiden, unterschiedliches Druckniveau aufweisenden Kältemittelströme ausgebildet ist. Im Innenraum eines Innenrohres ist ein Turbulenzerzeuger in Form einer Wendel vorgesehen. Die Wendel lenkt das im Innenrohr strömende Kältemittel um, so dass sich keine laminare Strömung im Wandbereich ausbilden kann. Dadurch soll eine verbesserte Vermischung und ein verbesserter Wärmeaustausch hergestellt werden. Die den Gegenstrom führenden Außenkanäle liegen in einer Ringwand des Koaxialrohres um das Innenrohr. Eine effiziente Wärmeübertragung ist nicht möglich.From the DE 10 2005 056 651 A1 is designed as a coaxial tube inner heat exchanger known, which is designed for the separate management of the two, different pressure level having refrigerant flows. In the interior of an inner tube, a turbulence generator is provided in the form of a helix. The helix deflects the refrigerant flowing in the inner tube, so that no laminar flow can form in the wall region. This is intended to produce improved mixing and improved heat exchange. The countercurrent leading outer channels are located in an annular wall of the coaxial tube around the inner tube. An efficient heat transfer is not possible.

Der Erfindung liegt die Aufgabe zugrunde, einen inneren Wärmetauscher der eingangs beschriebenen Art derart auszugestalten, dass der Wirkungsgrad der Wärmeübertragung zwischen den beiden getrennt durch den inneren Wärmetauscher geleiteten Fluidströmen gesteigert wird.The invention has the object of providing an inner heat exchanger of the type described above in such a way that the efficiency of heat transfer between the two separated by the inner heat exchanger conducted fluid flows is increased.

Die Aufgabe wird erfindungsgemäß durch die im Kennzeichen des Anspruchs 1 genannten Merkmale gelöst.The object is achieved by the features mentioned in the characterizing part of claim 1.

Um das kühlende und das zu kühlende Fluid in den Wärmetauscher ein- bzw. abzuleiten, sind an beiden Enden des zylinderförmigen Durchflusskörpers Anschlussbauteile vorgesehen, über welche die Fluide, welche durch den inneren Wärmetauscher vorwiegend im Gegenstrombetrieb strömen, getrennt voneinander zu- bzw. abgeleitet werden.In order to introduce the cooling and the fluid to be cooled in the heat exchanger or discharge, connection components are provided at both ends of the cylindrical flow body, via which the fluids which flow through the inner heat exchanger mainly in countercurrent, separately from each other or are derived ,

Durch die Erfindung wird das Koaxialrohr-Prinzip eines inneren Wärmetauschers mit einem Außenrohr und einem koaxial darin angeordneten Innenrohr unter Bildung eines Außenlängskanäle aufweisenden Ringzwischenraumes aufgegeben. Gemäß der Erfindung ist in einem das Gehäuse darstellenden zylinderförmigen Durchflusskörper ein kreisförmiges Bündel von Einzelrohren angeordnet, die jeweils eine Teilmenge des zu kühlenden Fluidstroms führen. Diese Einzelrohre sind jeweils in einem separaten Rohrlängskanal angeordnet und werden darin über die Gehäuselänge von dem kühlenden Fluidstrom im direkten Kontakt umspült. Hierdurch ist ein besonders effizienter Wärmeübergang ermöglicht, der bei dem indirekten Kontaktprinzip der aus dem Stand der Technik bekannten Ausführungen nicht realisiert werden kann.By the invention, the Koaxialrohr principle of an inner heat exchanger with an outer tube and a coaxially disposed therein inner tube to form an outer longitudinal channels having annular space is abandoned. According to the invention, a circular bundle of individual tubes is arranged in a cylinder-shaped flow body representing the housing, which each lead a subset of the fluid flow to be cooled. These individual tubes are each arranged in a separate tube longitudinal channel and are lapped therein over the housing length of the cooling fluid flow in direct contact. This allows a particularly efficient heat transfer, which can not be realized in the indirect contact principle of the known from the prior art designs.

Eine vorteilhafte Ausgestaltung der Erfindung ist im Kennzeichen des Patentanspruchs 2 offenbart. Die mit Abstand zu dem Ende des Durchflusskörpers angesetzte Ringwand begrenzt einen Hohlraum, in dem die Einzelströme des kühlenden Fluids aus den Längsbohrungen kommend wieder zusammenfließen.An advantageous embodiment of the invention is disclosed in the characterizing part of patent claim 2. The annular wall set at a distance from the end of the flow body defines a cavity in which the individual flows of the cooling fluid come together again coming from the longitudinal bores.

In weiterer vorteilhafter Ausgestaltung der Erfindung weist das Gehäuse des Innenwärmetauschers ein Außenrohr auf, in das der Durchflusskörper eingepasst angeordnet ist. Das Außenrohr bildet an seinen Enden einen Überstand über den Durchflusskörper, in den die jeweiligen Anschlussteile dichtend eingeschoben werden können.In a further advantageous embodiment of the invention, the housing of the inner heat exchanger on an outer tube, into which the flow body fitted is arranged. The outer tube forms at its ends a projection over the flow body, in which the respective connecting parts can be inserted sealingly.

In weiterer vorteilhafter Ausgestaltung sind Außenrohr und Durchflusskörper einteilig ausgebildet. Dieses hat im Wesentlichen fertigungstechnische Vorteile.In a further advantageous embodiment, outer tube and flow body are integrally formed. This has essentially manufacturing advantages.

In vorteilhafter Ausgestaltung der Erfindung weisen die Einzelrohre einen sternförmigen Querschnitt auf. Dadurch wird die Kühlfläche aufgrund der größeren Oberfläche nochmals erhöht.In an advantageous embodiment of the invention, the individual tubes have a star-shaped cross-section. As a result, the cooling surface is increased again due to the larger surface area.

In den Ansprüchen 6 bis 8 werden vorteilhafte Ausgestaltungen des Aufbaus der Anschlussbauteile offenbart. Die Ausbildung und Anordnung eines Verteilerringes am äußeren Anschlussflansch dient der gleichmäßigen Verteilung des zu kühlenden Fluidstroms.In the claims 6 to 8 advantageous embodiments of the structure of the connection components are disclosed. The design and arrangement of a distributor ring on the outer connecting flange serves for uniform distribution of the fluid flow to be cooled.

In weiterer vorteilhafter Ausgestaltung der Erfindung ist an dem der Prallfläche gegenüberliegenden stirnseitigen Ende des Durchflusskörpers ein pilzförmiger, sich axial erstreckender Abstandshalter angeordnet, in dessen kragenförmigen Umfang halbkreisförmige Ausnehmungen zur Aufnahme der Enden der Einzelrohre angeordnet sind. Durch die pilzartige Form wird der kühlende Fluidstrom daran gehindert, abzureißen. Die Einzelrohre werden sicher über ihre gesamte Länge und die gesamte Umfangsfläche umspült.In a further advantageous embodiment of the invention, a mushroom-shaped, axially extending spacer is arranged at the opposite end face of the baffle surface, in the collar-shaped periphery semicircular recesses for receiving the ends of the individual tubes are arranged. The mushroom-like shape prevents the cooling fluid flow from tearing off. The individual tubes are safely washed over their entire length and the entire peripheral surface.

Sich axial nach außen erstreckende Abstandsnocken am dem Abstandshalter bilden einen Abstandsraum, in dem die Teilströme des kühlenden Fluidstroms wieder zusammenfließen können.Extending axially outwardly spaced cams on the spacer form a clearance space in which the partial flows of the cooling fluid flow can flow together again.

In weiterer vorteilhafter Ausgestaltung der Erfindung sind in die Einzelrohre durchgehende, den Rohrinnenraum in Teilkanäle aufteilende Stege durchgehend angeordnet und die Stege weisen eine den Rohrinnenquerschnitt unterteilende kreuzförmige Anordnung auf. Die Strömungsgeschwindigkeit des kühlenden Fluidstromes und der Wärmeübergangskoeffizient werden durch diese Ausbildung erhöht.In a further advantageous embodiment of the invention, continuous webs dividing the pipe interior into subchannels are arranged continuously in the individual pipes and the webs have a subdivision of the pipe inside cross section cross-shaped arrangement on. The flow rate of the cooling fluid flow and the heat transfer coefficient are increased by this design.

Durch die Erfindung wird ein leistungsstarker innerer Wärmetauscher in kompakter Bauweise geschaffen, der sich besonders für Anwendungen in Kraftfahrzeugklimaanlagen, insbesondere in CO2-Klimaanlagen von Kraftfahrzeugen, eignet. Dieser innere Wärmetauscher ist aber auch zum Einsatz als leistungsstarker Kraftstoffkühler im Automobilbereich geeignet. Er ist überall dort anwendbar, wo mittels inneren Wärmetauschers zwei Fluidströme mit unterschiedlichem Temperaturniveau wärmeübergangsmäßig aneinander vorbeigeführt werden.The invention provides a powerful internal heat exchanger in a compact design, which is particularly suitable for applications in motor vehicle air conditioning systems, in particular in CO 2 air conditioning systems of motor vehicles. This inner heat exchanger is also suitable for use as a high-performance fuel cooler in the automotive sector. It is applicable everywhere, where by means of internal heat exchanger two fluid streams with different temperature level heat transfer are passed to each other.

Anhand der Zeichnung werden nachstehend zwei Ausführungsbeispiele der Erfindung näher erläutert. Es zeigt

Fig. 1
einen inneren Wärmetauscher mit einem ein Gehäuse bildenden zylinderförmigen Durchflusskörper, der in ein Außenrohr eingesetzt ist, in explosionsartiger, perspektivischer, schematischer Darstellung;
Fig. 2
den im Außenrohr eingesetzten Durchflusskörper des Innenwärmetauschers in Stirnansicht;
Fig. 3
den im Außenrohr eingesetzten Durchflusskörper des Innenwärmetauschers im Längsschnitt gemäß Linie II - II in Fig. 2;
Fig. 4
den in das Außenrohr einzusetzenden, ein Rohrbündel führenden zylinderförmigen Durchflusskörper in Detaildarstellung in Stirnansicht;
Fig. 5
den in Fig. 4 dargestellten Durchflusskörper im Halbschnitt;
Fig. 6
einen Sammelflansch eines der beiden Anschlussbauteile im Längsschnitt;
Fig. 7
einen äußeren Anschlussflansch eines der beiden Anschlussbauteile mit auf seinen Anschlussstutzen aufgesetztem Verteilerring;
Fig. 8
das aus Sammlerflansch und Anschlussflansch sowie aufgesteckten Verteilerring bestehende Anschlussbauteil im zusammengesteckten Zustand;
Fig. 9
eine modifizierte Ausführung des zylinderförmigen Durchflusskörpers;
Fig. 10 + 11
die stirnseitigen Ansichten des in Fig. 9 gezeigten Durchflusskörpers;
Fig. 12
eine perspektivische Darstellung des in Fig. 9 bis 11 gezeigten DurchFlusskörpers;
Fig. 13
den in den Fig. 9 bis 12 gezeigten Durchflusskörper, eingesetzt in einem Außenrohr im Längsschnitt.
Reference to the drawings, two embodiments of the invention will be explained in more detail below. It shows
Fig. 1
an inner heat exchanger with a housing forming a cylindrical flow body, which is inserted into an outer tube, in an exploded, perspective, schematic representation;
Fig. 2
the flow body used in the outer tube of the inner heat exchanger in front view;
Fig. 3
the flow body used in the outer tube of the inner heat exchanger in longitudinal section along line II - II in Fig. 2 ;
Fig. 4
in the outer tube to be inserted, a tube bundle leading cylindrical flow body in detail in front view;
Fig. 5
the in Fig. 4 illustrated flow body in half section;
Fig. 6
a collection flange of one of the two connection components in longitudinal section;
Fig. 7
an outer connecting flange of one of the two connecting components with a distributor ring mounted on its connecting piece;
Fig. 8
the connection component consisting of collector flange and connection flange and plugged-on distribution ring in the assembled state;
Fig. 9
a modified embodiment of the cylindrical flow body;
Fig. 10 + 11
the frontal views of the in Fig. 9 shown flow body;
Fig. 12
a perspective view of the in Fig. 9 to 11 shown by flow body;
Fig. 13
in the Fig. 9 to 12 shown flow body used in an outer tube in longitudinal section.

Der in Fig. 1 gezeigte innere Wärmetauscher weist ein Außenrohr 11 und einen in das Außenrohr 11 passend eingesetzten, zylinderförmig ausgebildeten Durchflusskörper 20 auf. In diesem Durchflusskörper 20 sind auf einem Kreisumfang liegend neun Einzelrohre 12 achsparallel angeordnet. In den Einzelrohren 12 läuft ein zu kühlender Fluidstrom (nachfolgend "heißer" Fluidstrom genannt) in Richtung des Pfeils A. Der kühlende Gegenstrom (nachfolgend "kalter" Fluidstrom genannt) wird von dem Durchflusskörper 20 geführt und durchströmt den Wärmetauscher in Richtung des Pfeils B. Der Durchflusskörper 20 wird nachfolgend an anderer Stelle noch näher erläutert.The in Fig. 1 shown inner heat exchanger has an outer tube 11 and a suitably inserted into the outer tube 11, cylinder-shaped flow body 20. In this flow body 20 lying on a circumference nine individual tubes 12 are arranged axially parallel. In the individual tubes 12, a fluid flow to be cooled (hereinafter referred to as "hot" fluid flow) runs in the direction of the arrow A. The cooling countercurrent (hereinafter referred to as "cold" fluid flow) is guided by the flow body 20 and flows through the heat exchanger in the direction of the arrow B. The flow body 20 will be explained in more detail elsewhere.

Um den kalten und den heißen Fluidstrom in den das Wärmetauschergehäuse bildenden zylinderförmigen Durchflusskörper 20 ein- bzw. abzuleiten, sind an beiden Enden des Durchflusskörpers 20 jeweils zweiteilige Anschlussbauteile 13,14 bzw. 15,16 vorgesehen, über welche die Fluidströme vorwiegend im Gegenstrombetrieb getrennt voneinander zu- bzw. abgeleitet werden.In order to feed the cold and the hot fluid flow into the cylindrical flow body 20 forming the heat exchanger housing, two-part connection components 13, 14 and 15, 16 are respectively provided at both ends of the flow body 20, via which the fluid flows are separated from one another predominantly in countercurrent operation be added or derived.

Jedes Anschlussbauteil 13, 14 bzw. 15,16 ist im Wesentlichen zweiteilig aus je einem äußeren Anschlussflansch 14 bzw. 16 und je einem Sammlerflansch 13 bzw. 15 aufgebaut. Jeder Sammlerflansch 13 bzw. 15 weist jeweils neun durchgehende Anschlussöffnungen 17 auf, die nach der Montage des Wärmetauschers die Enden der neun Einzelrohre 12 dicht aufnehmen. Die Anschlussöffnungen 17 enden in einem durch das Zusammenstecken des Anschlussflansches 14 bzw. 16 mit dem jeweiligen Sammlerflansch 13 bzw. 15 gebildeten ringförmigen Sammelkanal 18, der über eine außerhalb der Mittelachse liegende Anschlussbohrung 19 im Anschlussflansch 14 bzw. 16 mit dem entsprechenden, hier nicht dargestellten Fluidkreislauf verbunden ist.Each connection component 13, 14 or 15, 16 is essentially constructed in two parts from an outer connection flange 14 or 16 and a respective collector flange 13 or 15. Each collector flange 13 and 15 respectively has nine through-connection openings 17, which receive the ends of the nine individual tubes 12 tightly after assembly of the heat exchanger. The connection openings 17 terminate in an annular collection channel 18 formed by plugging together the connection flange 14 or 16 with the respective header flange 13 or 15, which via a connection bore 19 located outside the central axis in the connection flange 14 or 16 with the corresponding, not shown here Fluid circuit is connected.

Beide Anschlussbauteile 13, 14 bzw. 15, 16 sind baugleich ausgeführt und weisen jeweils eine durchgehende, mittige Zentralöffnung 21 auf, die abgedichtet mit dem Durchflusskörper 20 fluchtet und das den Durchflusskörper 20 durchströmende kalte Fluid mit dem entsprechenden, hier nicht dargestellten Fluidkreislauf verbindet.Both connection components 13, 14 and 15, 16 are of identical design and each have a continuous, central central opening 21 which is sealed with the flow body 20 and connects the flow body 20 flowing through cold fluid with the corresponding, not shown here fluid circuit.

Das jeweilige Anschlussbauteil 13, 14 bzw. 15, 16 wird wie folgt mit dem Wärmetauschergehäuse montiert (Fig. 1 und Fig. 6 bis Fig. 8). Der Sammlerflansch 13 bzw. 15 weist einen zentrischen Anschlussstutzen 22 mit zwei Umfangsnuten 23 und 24 auf, in die jeweils ein Dichtring 25 bzw. 26 eingebracht wird. Der Sammlerflansch 13 bzw. 15 wird mit seinem Anschlussstutzen 22 passend in einen überstehenden Randbereich des Außenrohres 11 dichtend eingeschoben und stirnseitig mit den Einzelrohren 12 des Durchflusskörpers 20 dicht verbunden.The respective connection component 13, 14 or 15, 16 is mounted as follows with the heat exchanger housing ( Fig. 1 and Fig. 6 to Fig. 8 ). The collector flange 13 and 15 has a central connecting piece 22 with two circumferential grooves 23 and 24, in each of which a sealing ring 25 and 26 is introduced. The collector flange 13 and 15 is inserted with its connecting piece 22 fitting sealingly in a protruding edge region of the outer tube 11 and the front side sealingly connected to the individual tubes 12 of the flow body 20.

Die äußeren Anschlussflansche 14 und 16 weisen jeweils zwei zueinander koaxial angeordnete Stutzen 28 und 29 auf. Der Anschlussstutzen 28 mit dem größeren Durchmesser weist eine umfangsmäßige Nut 31 zur Aufnahme eines Dichtringes 32 auf. Der Dichtstutzen 29 mit kleinerem Durchmesser weist ebenfalls eine Umfangsnut 34 zur Aufnahme eines weiteren Dichtringes 33 auf. Der Anschlussstutzen 28 ist als Ringwand ausgebildet, die umfangsmäßig einen Verteilerring 35 umschließt, der eine zentrale Öffnung 50 aufweist, die einen größeren Innendurchmesser aufweist, als der Außendurchmesser des hindurchragenden kleineren Dichtstutzens 29.The outer connecting flanges 14 and 16 each have two mutually coaxially arranged sockets 28 and 29. The connecting piece 28 with the larger diameter has a circumferential groove 31 for receiving a sealing ring 32. The sealing nozzle 29 with a smaller diameter also has a circumferential groove 34 for receiving a further sealing ring 33. The connecting piece 28 is formed as an annular wall which surrounds a circumferential distribution ring 35, which has a central Opening 50 which has a larger inner diameter than the outer diameter of the protruding smaller sealing nozzle 29th

Der Verteilerring 35 ist mit einem äußeren zurückgebogenen Kragen 51 auf das freie Ende des Anschlussstutzens 28 aufgeklemmt. Am anderen Ende des Verteilerringes 35 weist dieser einen radial nach innen ragenden Boden 52 auf, dessen Ende 53 axial zurückgebogen verläuft. Der Boden 52 des Verteilerringes 35 teilt den ringförmigen Raum innerhalb des Anschlussstutzens 28 in zwei Verteilerräume 18 und 54 auf.The distributor ring 35 is clamped with an outer bent-back collar 51 on the free end of the connecting piece 28. At the other end of the distributor ring 35, this has a radially inwardly projecting bottom 52, whose end 53 extends axially bent back. The bottom 52 of the distributor ring 35 divides the annular space within the connecting piece 28 into two distributor spaces 18 and 54.

Der Anschlussflansch 14 bzw. 16 wird mit seinem Anschlussstutzen 28 in den Sammlerflansch 13 bzw. 15 eingeschoben. Der kleine Dichtstutzen 29 dichtet den Zu- und Ablauf des kalten Fluidstroms zum Durchflusskörper 20 im Anschlussstutzen 22 des Sammlerflansches 13 bzw. 15 ab.The connecting flange 14 or 16 is inserted with its connecting piece 28 in the collector flange 13 and 15 respectively. The small sealing nozzle 29 seals the inlet and outlet of the cold fluid flow to the flow body 20 in the connecting piece 22 of the collector flange 13 and 15 from.

Die Lageraugen 27 in den Sammlerflanschen 13, 15 und den Anschlussflanschen 14 und 16 dienen zum Befestigen der Flansche miteinander und dem dichten Einspannen des Durchflusskörpers 20.The bearing lugs 27 in the collector flanges 13, 15 and the connecting flanges 14 and 16 serve to fasten the flanges together and the tight clamping of the flow body 20th

Anschlussbauteil 15, 16 und Anschlussbauteil 13, 14 sind in diesem Ausführungsbeispiel identisch aufgebaut. Es kann aber auch ausreichend sein, den Verteilerring 35 nur im Anschlussbauteil 15, 16 vorzusehen, das in Zuflussrichtung des heißen Fluidstroms vorgesehen ist.Connection component 15, 16 and connection component 13, 14 are constructed identically in this embodiment. But it may also be sufficient to provide the distributor ring 35 only in the connection component 15, 16, which is provided in the inflow direction of the hot fluid flow.

Der Verteilerring 35 dient zur Verteilung des über die außerhalb der Mittelachse liegende Anschlussbohrung 19 zugeführten heißen Fluidstroms, der über die beiden Verteilerräume 18 und 54 über den gesamten kreisringförmigen Querschnitt im Anschlussflansch 14 bzw. 16 verteilt wird und somit gleichmäßig alle Anschlussöffnungen 19 im jeweiligen Sammlerflansch 13 bzw. 15 erreicht.The distributor ring 35 serves to distribute the hot fluid flow supplied via the connection bore 19 located outside the center axis, which is distributed via the two distributor spaces 18 and 54 over the entire annular cross section in the connection flange 14 or 16 and thus uniformly all the connection openings 19 in the respective collector flange 13 or 15 reached.

Der in das Außenrohr 11 nahezu über seine gesamte Länge passend eingesetzte Durchflusskörper 20 weist, um eine Turbulenz im zulaufenden kalten Fluidstrom zu erzeugen, eine spitz nach außen zulaufende Prallfläche 42 auf (Fig. 2). Im Bereich der Einzelrohre 12 ist der Durchflusskörper 20 über seine gesamte Länge jeweils durchbrochen (Fig. 5), wobei für jedes Einzelrohr 12 eine einzelne Durchbrechung in Form einer Längsbohrung 43 mit größerem Innendurchmesser als der Außendurchmesser des jeweiligen Einzelrohres 12 vorgesehen ist.The flow body 20, which is suitably inserted into the outer tube 11 over almost its entire length, has turbulence in the incoming cold fluid flow produce a pointed outward baffle 42 (FIG. Fig. 2 ). In the region of the individual tubes 12, the flow body 20 is in each case perforated over its entire length ( Fig. 5 ), wherein for each individual tube 12 a single opening in the form of a longitudinal bore 43 with a larger inner diameter than the outer diameter of the respective individual tube 12 is provided.

Der eingeleitete kalte Fluidstrom trifft auf die Prallfläche 42, die eine zentrale, spitzenförmige Vorwölbung 44 aufweist. Dadurch wird der kalte Fluidstrom radial zu den Längsbohrungen 43 umgelenkt. Der kalte Fluidstrom fließt durch die kreisringförmigen Spalte 45, die sich zwischen dem Außenumfang der Einzelrohre 12 und der jeweiligen Längsbohrung 43 des Durchflusskörpers 20 darstellen (Fig. 2).The introduced cold fluid stream strikes the baffle 42, which has a central, tip-shaped protrusion 44. As a result, the cold fluid flow is deflected radially to the longitudinal bores 43. The cold fluid flow flows through the annular gaps 45, which are located between the outer circumference of the individual tubes 12 and the respective longitudinal bore 43 of the flow body 20 ( Fig. 2 ).

Jedes Einzelrohr 12 wird in der zugeordneten, einen Rohrlängskanal darstellenden Längsbohrung 43 von einem Teilstrom des kalten Fluidstroms umspült. Es ergibt sich eine definierte Kühlung bei verbessertem Wärmeaustausch.Each individual tube 12 is surrounded by a partial flow of the cold fluid flow in the associated longitudinal bore 43, which represents a tube longitudinal channel. This results in a defined cooling with improved heat exchange.

Am anderen Ende des Durchflusskörpers 20 ist eine den Querschnitt des Durchflusskörpers 20 ringförmig abdeckende Wand 46 (Fig.3 und Fig. 5) mit axialem Abstand zum Hauptkörper des Durchflusskörpers 20 angeordnet, die eine zentrale Öffnung 47 zum Abfluss des kalten Fluidstroms aufweist. Durch den axialen Abstand der Wand 46 wird ein zylinderförmiger Hohlraum 48 am Ende des Durchflusskörpers 20 gebildet. Die Ringfläche der Wand 46 ist durch auf einem Kreisumfang liegende Aufnahmebohrungen 49 durchbrochen, durch die die Enden der Einzelrohre 12 des Rohrbündels passend ragen, um über die fluchtenden Anschlussöffnungen 17 des Sammelflansches 15 mit dem ringförmigen Verteilerraum 18 in dem Anschlussbauteil 15, 16 verbunden zu werden.At the other end of the flow body 20 is a cross-section of the flow body 20 annularly covering wall 46 (FIG. Figure 3 and Fig. 5 ) is arranged at an axial distance from the main body of the flow body 20, which has a central opening 47 for the outflow of the cold fluid flow. Due to the axial distance of the wall 46, a cylindrical cavity 48 is formed at the end of the flow body 20. The annular surface of the wall 46 is pierced by lying on a circumference receiving holes 49 through which the ends of the individual tubes 12 of the tube bundle suitably to be connected via the aligned connection openings 17 of the collecting flange 15 with the annular distribution space 18 in the connection member 15, 16 ,

Der Durchflusskörper 20 bildet mit seinen Längsbohrungen 43 innere, achsparallel verlaufende Rohrlängskanäle, in denen die parallelen Einzelrohre 12 angeordnet sind. Das durch den Durchflusskörper 20 hindurch geleitete kalte Fluid kann direkt die den heißen Fluidstrom führenden Einzelrohre 12 kontaktieren und umspülen, so dass eine effiziente Kühlung des in den Einzelrohren 12 fließenden heißen Fluidstroms erfolgt.The flow body 20 forms with its longitudinal bores 43 inner, axially parallel pipe longitudinal channels, in which the parallel individual tubes 12 are arranged. The cold fluid conducted through the flow body 20 can directly contact and flush around the individual tubes 12 carrying the hot fluid flow, so that efficient cooling of the hot fluid flow flowing in the individual tubes 12 takes place.

Die Führung des kalten und des heißen Fluids kann alternativ im Gleichstrom oder im Gegenstrom vorgesehen werden.The guidance of the cold and hot fluids may alternatively be provided in cocurrent or countercurrent.

In den Fig. 9 bis 13 wird eine alternative Ausführungsform des Durchflusskörpers 20' dargestellt. Der Aufbau dieses Durchflusskörpers 20' unterscheidet sich dadurch, dass er auf der Zuflussseite für den heißen Fluidstrom einen über das Ende des Durchflusskörpers 20' hinausragenden, zentralen, pilzartigen Abstandshalter 60 aufweist, auf dessen kreisförmigen Kragenumfang halbkreisförmige Ausnehmungen 61 enthalten sind, in die die Enden der Einzelrohre 12 einklippsbar sind (Fig. 13).In the Fig. 9 to 13 an alternative embodiment of the flow body 20 'is shown. The structure of this flow body 20 'differs in that it has on the inlet side for the hot fluid flow over the end of the flow body 20' protruding, central, mushroom-like spacers 60, on whose circular collar circumference semicircular recesses 61 are included, into which the ends the individual tubes 12 are einklippsbar ( Fig. 13 ).

Stirnseitig sind an diesen Abstandshalter 60 vier in axialer Richtung verlaufende Abstandsnocken 62 angeordnet, durch die im zusammengebauten Zustand des Wärmetauschers ein axialer Hohlraum zum Sammlerflansch 15 gebildet wird, in dem der aus den Längsbohrungen 43 fließende kalte Fluidstrom zusammengeführt und in die zentrale Abflussbohrung 21 des Anschlussbauteils 15, 16 geführt werden kann. Bezugszeichenliste (Teil der Beschreibung) 11 Außenrohr 12 Einzelrohre 13 Sammlerflansch 14 Anschlussflansch 15 Sammlerflansch 16 Anschlussflansch 13,14 Anschlussbauteil 15,16 Anschlussbauteil 17 Anschlussöffnungen 18 Sammelkanal, Verteilerraum 19 Anschlussbohrungen 20 zylinderförmiger Durchflusskörper 21 Zentralöffungen, Zu-, Abflussbohrungen 22 Anschlussstutzen 23 Umfangsnut 24 Umfangsnut 25 Dichtring 26 Dichtring 27 Lageraugen 28 Anschlussstutzen 29 Dichtstutzen 31 Nut 32 Dichtring 33 Dichtring 34 Umfangsnut 35 Verteilerring 42 Prallfläche 43 Längsbohrungen 44 Zentrale Vorwölbung 45 Kreisringförmige Spalte 46 Kreisringförmige Wand 47 Zentrale Öffnung 48 Hohlraum 49 Aufnahmebohrungen 50 Öffnung Verteilerring 51 Kragen 52 Boden 53 Ende Verteilerring 54 Verteilerraum 20' Durchflusskörper 60 Abstandshalter 61 Ausnehmungen 62 Abstandsnocken Arranged on the front side 60, four spacer cams 62 extending in the axial direction, by means of which an axial cavity is formed in the assembled state of the heat exchanger to the collector flange 15, in which merges the cold fluid flow flowing from the longitudinal bores 43 and into the central outflow bore 21 of the connection component 15, 16 can be performed. <b> List of Reference Numerals </ b> (part of the description) 11 outer tube 12 individual tubes 13 Sammlerflansch 14 flange 15 Sammlerflansch 16 flange 13.14 connection component 15.16 connection component 17 connection openings 18 Collecting duct, distribution room 19 connecting holes 20 cylindrical flow body 21 Central openings, inlet and outlet bores 22 spigot 23 circumferential groove 24 circumferential groove 25 seal 26 seal 27 bearing eyes 28 spigot 29 tight fitting 31 groove 32 seal 33 seal 34 circumferential groove 35 distribution ring 42 baffle 43 longitudinal bores 44 Central bulge 45 Annular column 46 Circular wall 47 Central opening 48 cavity 49 mounting holes 50 Opening distribution ring 51 collar 52 ground 53 End distribution ring 54 distribution space 20 ' Flow body 60 spacer 61 recesses 62 spacer lugs

Claims (12)

  1. Inner heat exchanger, in particular for motor vehicle air conditioning systems, having a housing for the separate guidance of a cooling fluid stream and of a fluid stream to be cooled, said fluid streams being supplied and discharged via connector components arranged on the ends of the housing,
    the housing of the inner heat exchanger has a cylindrical throughflow body (20),
    close to the circumference of the throughflow body (20), a plurality of individual pipes (12) which form a parallel pipe bundle and which conduct the fluid stream to be cooled are arranged on a circular circumference,
    the individual pipes (12) project through longitudinal bores (43), which extend axially parallel, of the throughflow body (20), said longitudinal bores having a greater diameter than the outer diameter of the respective individual pipe (12) such that an annular gap (45) is formed in each case, characterized in that the throughflow body (20) has, on a face-side end, an impingement surface (42) which extends over its cross section and which bulges outward counter to the inflow direction of the fluid stream to be cooled.
  2. Inner heat exchanger according to Claim 1, characterized
    in that, at the other face-side end of the throughflow body (20), the individual pipes (12) project through receiving bores (49) of an annular wall (46) which has a central opening (47) and which is mounted onto the end of the throughflow body (20) with a spacing thereto, wherein the diameters of the receiving bores (49) correspond to the respective outer diameter of the individual pipes (12).
  3. Inner heat exchanger according to Claim 1, characterized
    in that the housing of the inner heat exchanger has an outer pipe (11) in which the throughflow body (20) is arranged in a fitting manner.
  4. Inner heat exchanger according to Claim 3, characterized
    in that the outer pipe (11) and the throughflow body (20) are formed in one piece.
  5. Inner heat exchanger according to Claim 1, characterized
    in that the individual pipes (12) have a stellate cross section.
  6. Inner heat exchanger according to Claim 1, characterized
    in that the connector components (13, 14 and 15, 16 respectively) are formed substantially in two parts, and here, are composed in each case of an outer connector flange (14 and 16 respectively) and of an inner collector flange (13 and 15 respectively) which, inserted one inside the other, are arranged sealingly in each case on the ends of the throughflow body (20).
  7. Inner heat exchanger according to Claim 6, characterized
    in that the outer connector flange (14 and 16 respectively) has two pipe stubs (22 and 29) arranged coaxially with respect to one another, wherein on the connector pipe stub (22) with the larger diameter there is arranged a distributor ring (35) which divides the interior space of the connector pipe stub (22) into two distributor chambers (18 and 54), wherein the distributor ring (35) has a central opening (50) whose diameter is larger than the outer diameter of the sealing pipe stub (29).
  8. Inner heat exchanger according to Claim 6, characterized
    in that the collector flange (13 and 15 respectively) has, on one side, continuous receiving openings (17) for the individual pipes (12) and, on the other side, a receiving chamber (18) for the connector pipe stub (22), which is provided with the distributor ring (35), of the connector flange (16).
  9. Inner heat exchanger according to Claim 1, characterized
    in that on that face-side end of the throughflow body (20') which is situated opposite the impingement surface (42) there is arranged a mushroom-shaped, axially extending spacer (60), in the collar-shaped circumference of which there are arranged semicircular recesses (61) for receiving the ends of the individual pipes (12).
  10. Inner heat exchanger according to Claim 9, characterized
    in that axially outwardly extending spacer cams (62) are arranged on the spacer (60).
  11. Inner heat exchanger according to Claim 1, characterized
    in that in the individual pipes (12) there are arranged continuous webs which divide the pipe interior into partial ducts.
  12. Inner heat exchanger according to Claim 11, characterized
    in that the webs have a cross-shaped arrangement which divides the pipe inner cross section.
EP10752757.4A 2009-09-28 2010-09-02 Inner heat exchanger, particularly for motor vehicle air conditioners Active EP2486356B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910044119 DE102009044119A1 (en) 2009-09-28 2009-09-28 Inner heat exchanger, in particular for motor vehicle air conditioners
PCT/EP2010/062845 WO2011036044A2 (en) 2009-09-28 2010-09-02 Inner heat exchanger, particularly for motor vehicle air conditioners

Publications (2)

Publication Number Publication Date
EP2486356A2 EP2486356A2 (en) 2012-08-15
EP2486356B1 true EP2486356B1 (en) 2013-07-03

Family

ID=43662552

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10752757.4A Active EP2486356B1 (en) 2009-09-28 2010-09-02 Inner heat exchanger, particularly for motor vehicle air conditioners

Country Status (4)

Country Link
EP (1) EP2486356B1 (en)
CN (1) CN102667389B (en)
DE (1) DE102009044119A1 (en)
WO (1) WO2011036044A2 (en)

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1134397B (en) * 1961-03-25 1962-08-09 Balcke Ag Maschbau Vertical double pipe heat exchanger with internal connecting pipes between the shell and cover spaces
FR2507759A1 (en) * 1981-06-15 1982-12-17 Walter Jean Jacques Fluid flow heat exchanger - has block of heat conducting material pierced with parallel channels for two liquid flow
DE19719256B4 (en) * 1997-05-07 2005-08-18 Valeo Klimatechnik Gmbh & Co. Kg More than twin-tube flat tube heat exchanger for motor vehicles with deflection floor and manufacturing process
DE19944950B4 (en) 1999-09-20 2008-01-31 Behr Gmbh & Co. Kg Air conditioning with internal heat exchanger
DE10053000A1 (en) 2000-10-25 2002-05-08 Eaton Fluid Power Gmbh Air conditioning system with internal heat exchanger and heat exchanger tube for one
US6626235B1 (en) * 2001-09-28 2003-09-30 Ignas S. Christie Multi-tube heat exchanger with annular spaces
DE10260030A1 (en) * 2001-12-21 2003-07-03 Behr Gmbh & Co Heat exchanger, especially for vehicle, has housing and cover plate for through channel(s) with coaxial openings via which collection chamber(s) communicates with through channel(s)
DE102005056651A1 (en) * 2005-11-25 2007-05-31 Behr Gmbh & Co. Kg Coaxial tube or tube-in-tube arrangement, in particular for a heat exchanger
DE102008038140A1 (en) * 2008-08-18 2010-02-25 Krones Ag Tube heat exchangers, double deflector bend for tube heat exchangers, adapter for tube heat exchangers and system and method for heat transfer between at least two food streams

Also Published As

Publication number Publication date
WO2011036044A2 (en) 2011-03-31
EP2486356A2 (en) 2012-08-15
CN102667389B (en) 2014-04-30
DE102009044119A1 (en) 2011-03-31
WO2011036044A3 (en) 2011-07-21
CN102667389A (en) 2012-09-12

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