EP2486356B1 - Échangeur de chaleur interne en particulier pour climatiseurs de véhicules à moteur - Google Patents

Échangeur de chaleur interne en particulier pour climatiseurs de véhicules à moteur 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
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP10752757.4A
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German (de)
English (en)
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EP2486356A2 (fr
Inventor
Claus Röck
Andreas Gorzel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ContiTech Kuehner GmbH and Cie KG
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ContiTech Kuehner GmbH and Cie KG
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Publication of EP2486356A2 publication Critical patent/EP2486356A2/fr
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Publication of EP2486356B1 publication Critical patent/EP2486356B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • 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)

Claims (12)

  1. Echangeur de chaleur interne, en particulier pour climatiseurs de véhicules automobiles, comprenant un boîtier pour le guidage séparé d'un courant de fluide de refroidissement et d'un courant de fluide à refroidir, qui sont acheminés ou évacués par le biais de composants de raccordement disposés aux extrémités du boîtier,
    le boîtier de l'échangeur de chaleur interne présentant un corps d'écoulement (20) cylindrique, plusieurs tubes individuels (12) formant un faisceau de tubes parallèle étant disposés sur un pourtour circulaire à proximité du pourtour du corps d'écoulement (20), lesquels conduisent au courant de fluide à refroidir,
    les tubes individuels (12) pénétrant à travers des alésages longitudinaux (43) du corps d'écoulement (20) s'étendant avec leurs axes parallèles, et présentant à chaque fois, en formant un interstice annulaire (45), un plus grand diamètre que le diamètre extérieur du tube individuel respectif (12),
    caractérisé en ce que
    le corps d'écoulement (20) présente, au niveau d'une extrémité frontale, une surface d'impact (42) s'étendant sur sa section transversale, se précintrant vers l'extérieur à l'encontre de la direction d'afflux du courant de fluide de refroidissement.
  2. Echangeur de chaleur interne selon la revendication 1, caractérisé en ce que
    les tubes individuels (12) à l'autre extrémité frontale du corps d'écoulement (20) pénètrent à travers des alésages de réception (49) d'une paroi annulaire (46) présentant une ouverture centrale (47), située à l'extrémité du corps d'écoulement (20) à distance de celui-ci, les diamètres des alésages de réception (49) correspondant au diamètre extérieur respectif des tubes individuels (12).
  3. Echangeur de chaleur interne selon la revendication 1, caractérisé en ce que le boîtier de l'échangeur de chaleur interne présente un tube externe (11) dans lequel est disposé de manière adaptée le corps d'écoulement (20).
  4. Echangeur de chaleur interne selon la revendication 3, caractérisé en ce que le tube externe (11) et le corps d'écoulement (20) sont réalisés d'une seule pièce.
  5. Echangeur de chaleur interne selon la revendication 1, caractérisé en ce que les tubes individuels (12) présentent une section transversale de forme stellaire.
  6. Echangeur de chaleur interne selon la revendication 1, caractérisé en ce que les composants de raccordement (13, 14, respectivement 15, 16) sont réalisés essentiellement en deux parties, et se composent en l'occurrence à chaque fois d'une bride de raccordement externe (14, respectivement 16), et d'une bride collectrice interne (13, respectivement 15), qui sont emboîtées l'une dans l'autre et disposées de manière hermétique à chaque fois aux extrémités du corps d'écoulement (20).
  7. Echangeur de chaleur interne selon la revendication 6, caractérisé en ce que la bride de raccordement externe (14, respectivement 16) présente deux tubulures (22 et 29) disposées coaxialement l'une par rapport à l'autre, une bague de distribution (35) divisant l'espace interne de la tubulure de raccordement (22) en deux espaces de distribution (18 et 54) sur la tubulure de raccordement (22) ayant le plus grand diamètre, la bague de distribution (35) présentant une ouverture centrale (50) dont le diamètre est supérieur au diamètre extérieur de la tubulure d'étanchéité (29).
  8. Echangeur de chaleur interne selon la revendication 6, caractérisé en ce que la bride collectrice (13, respectivement 15) présente d'un côté des ouvertures de réception traversantes (17) pour les tubes individuels (12), et de l'autre côté un espace de réception (18) pour la tubulure de raccordement (22) de la bride de raccordement (16) pourvue de la bague de distribution (35).
  9. Echangeur de chaleur interne selon la revendication 1, caractérisé en ce qu'à l'extrémité frontale du corps d'écoulement (20') opposée à la surface d'impact (42) est disposé un élément d'espacement (60) en forme de champignon, s'étendant axialement, dans la périphérie en forme de collerette duquel sont disposés des évidements de forme semi-circulaire (61) pour recevoir les extrémités des tubes individuels (12).
  10. Echangeur de chaleur interne selon la revendication 9, caractérisé en ce que des cames d'espacement (62) s'étendant axialement vers l'extérieur sont disposées sur l'élément d'espacement (60).
  11. Echangeur de chaleur interne selon la revendication 1, caractérisé en ce que des nervures continues divisant l'espace interne des tubes en canaux partiels sont disposées dans les tubes individuels (12).
  12. Echangeur de chaleur interne selon la revendication 11, caractérisé en ce que les nervures présentent un agencement en forme de croix divisant la section transversale interne des tubes.
EP10752757.4A 2009-09-28 2010-09-02 Échangeur de chaleur interne en particulier pour climatiseurs de véhicules à moteur Active EP2486356B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910044119 DE102009044119A1 (de) 2009-09-28 2009-09-28 Innerer Wärmetauscher, insbesondere für Kraftfahrzeugklimaanlagen
PCT/EP2010/062845 WO2011036044A2 (fr) 2009-09-28 2010-09-02 Échangeur de chaleur interne en particulier pour climatiseurs de véhicules à moteur

Publications (2)

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

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP10752757.4A Active EP2486356B1 (fr) 2009-09-28 2010-09-02 Échangeur de chaleur interne en particulier pour climatiseurs de véhicules à moteur

Country Status (4)

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

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1134397B (de) * 1961-03-25 1962-08-09 Balcke Ag Maschbau Stehender Doppelrohrwaermeaustauscher mit innenliegenden Verbindungsrohren zwischen Mantelraum und Deckelraeumen
FR2507759A1 (fr) * 1981-06-15 1982-12-17 Walter Jean Jacques Echangeur de chaleur constitue d'un bloc de matiere conductrice fore de canaux pour le passage des fluides
DE19719256B4 (de) * 1997-05-07 2005-08-18 Valeo Klimatechnik Gmbh & Co. Kg Mehr als zweiflutiger Flachrohrwärmetauscher für Kraftfahrzeuge mit Umlenkboden sowie Herstelungsverfahren
DE19944950B4 (de) 1999-09-20 2008-01-31 Behr Gmbh & Co. Kg Klimaanlage mit innerem Wärmeübertrager
DE10053000A1 (de) 2000-10-25 2002-05-08 Eaton Fluid Power Gmbh Klimaanlage mit innerem Wärmetauscher und Wärmetauscherrohr für einen solchen
US6626235B1 (en) * 2001-09-28 2003-09-30 Ignas S. Christie Multi-tube heat exchanger with annular spaces
DE10260107A1 (de) * 2001-12-21 2003-10-02 Behr Gmbh & Co Wärmeübertrager, insbesondere für ein Kraftfahrzeug
DE102005056651A1 (de) 2005-11-25 2007-05-31 Behr Gmbh & Co. Kg Koaxialrohr oder Rohr-in-Rohr-Anordnung, insbesondere für einen Wärmetauscher
DE102008038140A1 (de) * 2008-08-18 2010-02-25 Krones Ag Röhrenwärmeüberträger, Doppelumlenkbogen für Röhrenwärmeüberträger, Adapter für Röhrenwärmeüberträger sowie System und Verfahren zur Wärmeübertragung zwischen wenigstens zwei Lebensmittelströmen

Also Published As

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

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