EP2299227B1 - Tubular heat exchanger - Google Patents

Tubular heat exchanger Download PDF

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Publication number
EP2299227B1
EP2299227B1 EP10171888.0A EP10171888A EP2299227B1 EP 2299227 B1 EP2299227 B1 EP 2299227B1 EP 10171888 A EP10171888 A EP 10171888A EP 2299227 B1 EP2299227 B1 EP 2299227B1
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EP
European Patent Office
Prior art keywords
tube
heat exchanger
tubular heat
product
juice
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EP10171888.0A
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German (de)
French (fr)
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EP2299227A2 (en
EP2299227A3 (en
Inventor
Roland Feilner
Jörg Zacharias
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Krones AG
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Krones AG
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Priority to PL10171888T priority Critical patent/PL2299227T3/en
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Publication of EP2299227A3 publication Critical patent/EP2299227A3/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
    • F28F1/34—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely
    • F28F1/36—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending obliquely the means being helically wound fins or wire spirals
    • 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
    • F28D7/106—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 consisting of two coaxial conduits or modules of two coaxial conduits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
    • F28F1/424—Means comprising outside portions integral with inside portions
    • F28F1/426—Means comprising outside portions integral with inside portions the outside portions and the inside portions forming parts of complementary shape, e.g. concave and convex
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0042—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for foodstuffs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0098—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for viscous or semi-liquid materials, e.g. for processing sludge
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers

Definitions

  • the invention relates to a tubular heat exchanger specified in the preamble of claim 1 species and an inner and / or jacket tube of such a tubular heat exchanger.
  • Out DE 102 56 232 B4 is a tubular heat exchanger, according to the preamble of claim 1, for the UHT treatment of milk and dairy products for sterilization known.
  • the jacket tube is a smooth tube.
  • the inner tubes are tantdrallrohre, in which the multi-course mutually opposing swirls intersect at angles between 25 ° and 35 ° along the tube axis, ie with helix angles between 65 ° and 55 °. This angle range is specially adapted to milk and milk products, which are very prone to build up on the contacted surface. Therefore, the swirls are additionally electrochemically polished. The combination of the two measures results in an optimal inhibition of the buildup of milk and milk products and thus in long life of the tube heat exchanger up to a required cleaning cycle.
  • helix angles of 45 ° which are to be regarded as optimal in terms of heat transfer, but which lead to milk and milk products to an inadmissibly strong formation of deposits. Inclination between 25 ° and 35 ° and the additional surface treatment are therefore an optimum for milk and milk products in terms of inhibiting the product-specific formation of deposits, however, as well as the usual helix angle of 45 ° to the tube axis, an unfavorable relationship between the achieved increase in heat transfer and excessive Increase of the pressure loss in the flow.
  • Out DE 600 19 635 T2 is a tube heat exchanger for the treatment of juices with fibers and / or particles known in which simply twisted inner and / or outer tubes are used.
  • the helix angle is shown at about 45 °, while the helix angle in the jacket tube at about 75 °, in each case based on the tube axis, is shown.
  • this tubular heat exchanger it is disadvantageous that, in order to increase the heat transfer, it is necessary to accept very high pressure loss with a constant flow area and the boundary layer of the flow is excited to strong rotation at the swirlings extending at the same helix angle to the pipe axis. This requires very high, possibly for the product disadvantageous, delivery pressure for the treatment of the product in the tubular heat exchanger.
  • the invention has for its object to provide a tubular heat exchanger of the type mentioned above and a use of such a tubular heat exchanger, which allow optimally short residence times and small heat exchanger surfaces in the processing of juices or juicy food products with medium to high viscosity despite only moderate delivery pressure.
  • the propensity for product batch formation is of secondary importance to juices and juice-like food products, since when using cross-twist tubes with the indicated shallow helix angles it is primarily important that pulp, fibers or particles as constituents of the juices or juice-like food products are not used because of the shallow helix angles Suspending and collecting tend, but quickly washed away. Furthermore, such a cleaning up to a hygienic condition is possible.
  • the tube heat exchanger is particularly well suited for the thermal treatment of juices or juice-like food products with viscosities> about 5 mPas, wherein the product may contain pulp, fibers or particles.
  • each swirl in the axial section of the tube has a trough-like depression with mutual, approximately wedge-shaped ribs in cross section, between which a swirl depth between approximately 0.8 mm to 1.2 mm exists in the depression.
  • the interaction between the relatively shallow helix angles and the moderate swirl depth results even at moderate delivery pressure in an optimal ratio for juices and juicy food products of medium to high viscosities between the increase in heat transfer and the resulting increase in pressure loss.
  • the recesses and the ribs are located on the product-contactable surface.
  • the width seen in the direction of the tube axis in the depression is a multiple of the twist depth. It should be between about 5.0 and 20.0 mm.
  • the depressions are relatively wide depressions, at the limiting ribs components of the product are rapidly flushed, and also a hygienic cleaning, e.g. for a product change.
  • both multistage swirls cover the entire surface of the pipe surface.
  • the jacket tube with several cross-spiral inner tubes forms a module of the tubular heat exchanger.
  • This module can extend over 3.0, 6.0 m or more and, suitably, is combined in series to treat the product in the multi-module tubular heat exchanger.
  • a heat transfer medium is used in the flow channel between the jacket tube and the inner tubes.
  • the respective cross-spiral inner tube has the depressions of the swirls on the outside or the inside, for example, depending on which pipe surface the product flows along.
  • the used swirls on the inner and outer tube surfaces in the flows are effective.
  • module M of a tubular heat exchanger W for the thermal treatment of juices or juicy food products with medium to high viscosities, for example, a viscosity of more than about 5 mPas consists of a jacket tube 1 and at least one inside the jacket tube 1 at a distance from the inner wall of the jacket tube
  • the module M is combined in the tube heat exchanger W, for example, with other, similar or similar modules not shown, to form a treatment section of a certain conveying length.
  • the product is treated either by a recuperative process, ie product by product separated by, for example, the inner tube 2, or by a method in which a heat transfer medium (steam or water) is used, the heat transfer medium is separated from the product by, for example, the respective Inner tube 2.
  • a recuperative process ie product by product separated by, for example, the inner tube 2
  • a method in which a heat transfer medium steam or water
  • the respective method is, preferably, operated in countercurrent or in direct current.
  • the jacket tube 1 in Fig. 1 is designed as a cross-twist tube with substantially mutually symmetrical to the tube axis X crossing,
  • D1, D2 wherein the twist angle ⁇ to the tube axis X between 18 ° to 23 ° and the angle of attack ⁇ 67 ° and 72 ° to the tube axis.
  • the funneldrallrohr for example similar to that in Fig. 4 shown formed with pointing to the tube interior recesses 3.
  • the respective inner tube 2 is also a Buchdrallrohr with substantially mutually symmetrical to the tube axis X crossing multi-speed swirls and helix angles ⁇ between 18 ° and 23 °.
  • the jacket tube 1 is a smooth tube.
  • each inner tube 2 contained in the jacket tube 1 is a Buchdrallrohr with each other substantially symmetrical to the tube axis X crossing, Distance to twist D1, D2 and helix angles a1 between 18 ° and 23 ° to the tube axis X.
  • the twists D1, D2 are more common, so that despite the relatively steep angle of attack (helix angle a1 between 18 ° and 23 °) the entire Pipe surface offers the product above all the heat transfer intensifying macrostructures, and is achieved between the increase in heat transfer and the pressure loss caused by the swirls an optimum.
  • Fig. 4 illustrates the macrostructures formed by the intersecting swirls D1, D2 of the respective funneldrallrohres as the inner tube 2, which are present on the inside and the outside of the tube.
  • Fig. 4 lie the tube axis X facing in the axial direction successively trough-like depressions 3, which are each bounded by substantially wedge-shaped ribs 5 and have a twist depth T between 0.8 mm and 1.2 mm.
  • the width B of each recess 3 is a multiple of the twist depth T, preferably between 5.0 mm and 20.0 mm.
  • a rounded tip 4 is provided corresponding to the recess 3, which is bounded in the axial direction by approximately V-shaped grooves 6.
  • the ribs 5 and the grooves 6 could be rounded, for example, with regard to a good cleanability of the tube.
  • the ribs 5 and the grooves 6 extend as well as the wells 3 and the crests 4 at the helix angle ⁇ , ⁇ 1 helical and periodically crossing each other over the entire inner or outer pipe surface.
  • FIG Fig. 5 is a funneldrallrohr as a jacket or inner tube 1, 2 indicated, in which the recesses 3 on the outside of the tube (ie the tube axis X facing away) are present.
  • the twist depth T is between 0.8 mm and 1.2 mm.
  • the helix angles ⁇ , ⁇ 1 are between 18 ° and 23 ° to the tube axis X.
  • the in Fig. 5 shown cross-twist tube is suitably used as the inner tube 2, for example, if the product flows between the jacket tube 1 and the outside of the inner tube 2. If a heat transfer medium is used, which flows in the flow channel between the jacket tube 1 and each inner tube 2, the cross-twist tube is expediently analogous to the inner tube 2 Fig. 4 educated.

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

Description

Die Erfindung betrifft einen Röhrenwärmetauscher der im Oberbegriff des Patentanspruchs 1 angegebenen Art sowie ein Innen- und/oder Mantelrohr eines solchen Röhrenwärmetauschers.The invention relates to a tubular heat exchanger specified in the preamble of claim 1 species and an inner and / or jacket tube of such a tubular heat exchanger.

Aus DE 102 56 232 B4 ist ein Röhrenwärmetauscher, gemäß dem Oberbegriff von Anspruch 1, zum UHT-Behandeln von Milch und Milchprodukten zur Entkeimung bekannt. Das Mantelrohr ist ein glattes Rohr. Die Innenrohre sind Kreuzdrallrohre, in denen sich die mehrgängigen zueinander gegensinnigen Drallungen unter Anstellwinkeln zwischen 25° und 35° längs zur Rohrachse kreuzen, das heißt mit Drallwinkeln zwischen 65° und 55°. Dieser Winkelbereich ist speziell auf Milch und Milchprodukte abgestimmt, die sehr stark zur Ansatzbildung an der kontaktierten Oberfläche neigen. Deshalb sind die Drallungen zusätzlich elektrochemisch poliert. Die Kombination der beiden Maßnahmen resultiert in einer optimalen Hemmung der Ansatzbildung von Milch und Milchprodukten und somit in langer Standzeit des Röhrenwärmetauschers bis zu einem erforderlichen Reinigungszyklus. Es werden Drallwinkel auch von 45° erwähnt, die hinsichtlich der Wärmeübertragung als optimal anzusehen sind, die jedoch bei Milch und Milchprodukten zu einer unzulässig starken Ansatzbildung führen. Anstellwinkel zwischen 25° und 35° und die zusätzliche Oberflächenbehandlung sind demzufolge für Milch und Milchprodukte hinsichtlich der Hemmung der produktspezifischen Ansatzbildung ein Optimum, bedingen jedoch wie auch die gängigen Drallwinkel von 45° zur Rohrachse ein ungünstiges Verhältnis zwischen der erzielten Steigerung des Wärmeübergangs und einer exzessiven Steigerung des Druckverlustes in der Strömung.Out DE 102 56 232 B4 is a tubular heat exchanger, according to the preamble of claim 1, for the UHT treatment of milk and dairy products for sterilization known. The jacket tube is a smooth tube. The inner tubes are Kreuzdrallrohre, in which the multi-course mutually opposing swirls intersect at angles between 25 ° and 35 ° along the tube axis, ie with helix angles between 65 ° and 55 °. This angle range is specially adapted to milk and milk products, which are very prone to build up on the contacted surface. Therefore, the swirls are additionally electrochemically polished. The combination of the two measures results in an optimal inhibition of the buildup of milk and milk products and thus in long life of the tube heat exchanger up to a required cleaning cycle. There are also mentioned helix angles of 45 °, which are to be regarded as optimal in terms of heat transfer, but which lead to milk and milk products to an inadmissibly strong formation of deposits. Inclination between 25 ° and 35 ° and the additional surface treatment are therefore an optimum for milk and milk products in terms of inhibiting the product-specific formation of deposits, however, as well as the usual helix angle of 45 ° to the tube axis, an unfavorable relationship between the achieved increase in heat transfer and excessive Increase of the pressure loss in the flow.

Aus DE 600 19 635 T2 ist ein Röhrenwärmetauscher zur Behandlung von Säften mit Fasern und/oder Teilchen bekannt, bei dem einfach gedrallte Innen- und/oder Außenrohre verwendet werden. Im Innenrohr ist der Drallwinkel mit etwa 45° dargestellt, während der Drallwinkel im Mantelrohr mit etwa 75°, jeweils bezogen auf die Rohrachse, gezeigt ist. Bei diesem Röhrenwärmetauscher ist es nachteilig, dass zugunsten gesteigerter Wärmeübertragung sehr starker Druckverlust bei gleichbleibender Anströmfläche in Kauf zu nehmen ist und die Grenzschicht der Strömung an den mit dem gleichen Drallwinkel zur Rohrachse verlaufenden Drallungen zu starker Rotation angeregt wird. Dies bedingt sehr hohen, gegebenenfalls für das Produkt nachteiligen, Förderdruck für die Behandlung des Produkts im Röhrenwärmetauscher.Out DE 600 19 635 T2 is a tube heat exchanger for the treatment of juices with fibers and / or particles known in which simply twisted inner and / or outer tubes are used. In the inner tube, the helix angle is shown at about 45 °, while the helix angle in the jacket tube at about 75 °, in each case based on the tube axis, is shown. In the case of this tubular heat exchanger, it is disadvantageous that, in order to increase the heat transfer, it is necessary to accept very high pressure loss with a constant flow area and the boundary layer of the flow is excited to strong rotation at the swirlings extending at the same helix angle to the pipe axis. This requires very high, possibly for the product disadvantageous, delivery pressure for the treatment of the product in the tubular heat exchanger.

Weiterer Stand der Technik ist enthalten in: CN 101 101 185 A , US 2004/244958 A1 , CN 26 30 783 Y , US 5 992 51 A .Further prior art is contained in: CN 101 101 185 A . US 2004/244958 A1 . CN 26 30 783 Y . US 5 992 51 A ,

Der Erfindung liegt die Aufgabe zugrunde, einen Röhrenwärmetauscher der eingangs genannten Art sowie eine Verwendung eines solchen Röhrenwärmetauschers anzugeben, die bei der Bearbeitung von Säften oder saftartigen Lebensmittelprodukten mit mittlerer bis hoher Viskosität trotz nur moderaten Förderdrucks optimal kurze Verweilzeiten und kleine Wärmetauscherflächen ermöglichen.The invention has for its object to provide a tubular heat exchanger of the type mentioned above and a use of such a tubular heat exchanger, which allow optimally short residence times and small heat exchanger surfaces in the processing of juices or juicy food products with medium to high viscosity despite only moderate delivery pressure.

Die gestellte Aufgabe wird mit den Merkmalen des Patentanspruchs 1 und des Patentanspruchs 9 gelöst.The stated object is achieved with the features of patent claim 1 and claim 9.

Dank der Verwendung zumindest eines Kreuzdrallrohres in dem Röhrenwärmetauscher für das Innenrohr wird wegen der sich kreuzenden Drallungen eine erhebliche Steigerung der Wärmeübertragung erzielt. Jedoch wird die erzielbare Steigerung der Wärmeübertragung mit der mit der Kreuzdrallung einhergehenden Steigerung des Druckverlustes bei der Durchströmung durch Beschränken des Anstellwinkels auf 72° bis 67° zur Rohrachse und dem sich daraus ergebenden Drallwinkel von 18° bis 23°, also auf einen relativ spitzen Drallwinkel, in ein optimales Verhältnis gebracht, das trotz nur moderaten Förderdrucks in einer verkleinerten Wärmetauscherfläche resultiert. In anderen Worten benötigt der Röhrenwärmetauscher aufgrund der Verwendung von solchen Kreuzdrallrohren eine relativ kleine Wärmetauscherfläche und damit eine kurze Förderstrecke. Die Neigung zur Produktansatzbildung ist bei Säften und saftähnlichen Lebensmittelprodukten von sekundärer Bedeutung, da es bei der Verwendung von Kreuzdrallrohren mit den angegebenen flachen Drallwinkeln primär darauf ankommt, dass Pulpe, Fasern oder Teilchen als Bestandteile der Säfte oder saftartigen Lebensmittelprodukte eben wegen der flachen Drallwinkel nicht zum Verhängen und Sammeln tendieren, sondern zügig weitergespült werden. Ferner wird so eine Reinigung bis zu einem hygienisch einwandfreien Zustand möglich.Thanks to the use of at least one Kreuzdrallrohres in the tube heat exchanger for the inner tube, a significant increase in heat transfer is achieved because of the intersecting swirls. However, the achievable increase in heat transfer with the associated with the cross-twist increase in pressure loss in the flow by limiting the angle of attack at 72 ° to 67 ° to the tube axis and the resulting helix angle of 18 ° to 23 °, ie a relatively acute angle of twist , brought into an optimal ratio, which results despite only moderate discharge pressure in a reduced heat exchanger surface. In other words, the tube heat exchanger requires a relatively small heat exchanger surface and thus a short conveyor line due to the use of such Kreuzdrallrohren. The propensity for product batch formation is of secondary importance to juices and juice-like food products, since when using cross-twist tubes with the indicated shallow helix angles it is primarily important that pulp, fibers or particles as constituents of the juices or juice-like food products are not used because of the shallow helix angles Suspending and collecting tend, but quickly washed away. Furthermore, such a cleaning up to a hygienic condition is possible.

Der Röhrenwärmetauscher ist besonders gut geeignet zur thermischen Behandlung von Säften oder saftartigen Lebensmittelprodukten mit Viskositäten > etwa 5 mPas, wobei im Produkt Pulpe, Fasern oder Teilchen enthalten sein können.The tube heat exchanger is particularly well suited for the thermal treatment of juices or juice-like food products with viscosities> about 5 mPas, wherein the product may contain pulp, fibers or particles.

Bei einer zweckmäßigen Ausführungsform weist jede Drallung im Achsschnitt des Rohres eine muldenartige Vertiefung mit beiderseitigen, im Querschnitt annähernd keilförmigen Rippen auf, zwischen denen in der Vertiefung eine Dralltiefe zwischen etwa 0,8 mm bis 1,2 mm vorliegt. Das Zusammenspiel zwischen den relativ flachen Drallwinkeln und der moderaten Dralltiefe resultiert selbst bei moderatem Förderdruck in einem für Säfte und saftartige Lebensmittelprodukte mittlerer bis hoher Viskositäten optimalen Verhältnis zwischen der Steigerung des Wärmeübergangs und der entstehenden Steigerung des Druckverlustes. Die Vertiefungen und die Rippen sind an der vom Produkt kontaktierbaren Oberfläche angeordnet.In an expedient embodiment, each swirl in the axial section of the tube has a trough-like depression with mutual, approximately wedge-shaped ribs in cross section, between which a swirl depth between approximately 0.8 mm to 1.2 mm exists in the depression. The interaction between the relatively shallow helix angles and the moderate swirl depth results even at moderate delivery pressure in an optimal ratio for juices and juicy food products of medium to high viscosities between the increase in heat transfer and the resulting increase in pressure loss. The recesses and the ribs are located on the product-contactable surface.

Bei einer zweckmäßigen Ausführungsform ist die in Richtung der Rohrachse gesehene Breite in der Vertiefung ein Vielfaches der Dralltiefe. Sie sollte zwischen etwa 5,0 und 20,0 mm liegen. Die Vertiefungen sind relativ weite Mulden, an deren begrenzenden Rippen Bestandteile des Produkts zügig weitergespült werden, und die auch eine hygienisch einwandfreie Reinigung, z.B. für einen Produktwechsel, ermöglichen. Um den Effekt der Kreuzdrallung optimal nutzen zu können, bedecken beide mehrgängigen Drallungen die Rohroberfläche vollflächig.In an expedient embodiment, the width seen in the direction of the tube axis in the depression is a multiple of the twist depth. It should be between about 5.0 and 20.0 mm. The depressions are relatively wide depressions, at the limiting ribs components of the product are rapidly flushed, and also a hygienic cleaning, e.g. for a product change. In order to be able to optimally use the effect of cross-twisting, both multistage swirls cover the entire surface of the pipe surface.

Bei einer zweckmäßigen Ausführungsform bildet das Mantelrohr mit mehreren Kreuzdrall-Innenrohren einen Modul des Röhrenwärmetauschers. Dieser Modul kann sich über 3,0, 6,0 m oder mehr erstrecken und wird, zweckmäßig, zur Behandlung des Produktes im Röhrenwärmetauscher mit mehreren Modulen in Reihe kombiniert. Im Strömungskanal zwischen dem Mantelrohr und den Innenrohren wird beispielsweise ein Wärmeträgermedium verwendet.In an expedient embodiment, the jacket tube with several cross-spiral inner tubes forms a module of the tubular heat exchanger. This module can extend over 3.0, 6.0 m or more and, suitably, is combined in series to treat the product in the multi-module tubular heat exchanger. In the flow channel between the jacket tube and the inner tubes, for example, a heat transfer medium is used.

Bei einer weiteren Ausführungsform weist das jeweilige Kreuzdrall-Innenrohr die Vertiefungen der Drallungen auf der Außenseite oder der Innenseite auf, beispielsweise abhängig davon, entlang welcher Rohroberfläche das Produkt strömt.In another embodiment, the respective cross-spiral inner tube has the depressions of the swirls on the outside or the inside, for example, depending on which pipe surface the product flows along.

Zur Behandlung des jeweiligen Produktes bieten sich zwei unterschiedliche Verfahren an, entweder ein rekuperatives Verfahren, bei welchem Produkt gegen Produkt getrennt durch das jeweilige Kreuzdrallrohr, z.B. im Gegenstrom, verarbeitet wird, oder ein Verfahren mit einem Wärmeträgermedium gegen das Produkt getrennt durch das jeweilige Kreuzdrallrohr, wobei dann, vorzugsweise, die Vertiefungen der beiden Drallungen des Kreuzdrallrohres dem Produkt zugewandt sind.For the treatment of the respective product, there are two different methods, either a recuperative process in which product versus product separated by the respective cross spin tube, e.g. in countercurrent, is processed, or a method with a heat transfer medium against the product separated by the respective Kreuzdrallrohr, in which case, preferably, the recesses of the two convolutions of the Kreuzdrallrohres are facing the product.

Die verwendeten Kreuzdrallrohre sind zweckmäßig Edelstahlrohre, bei denen die beiden Drallungen an den inneren und äußeren Rohroberflächen in den Strömungen wirksam sind.The used Kreuzdrallrohre are expediently stainless steel tubes, in which the two swirls on the inner and outer tube surfaces in the flows are effective.

Ausführungsformen des Erfindungsgegenstandes werden anhand der Zeichnungen erläutert. Es zeigen:

Fig. 1
einen Röhrenwärmetauscher zur thermischen Behandlung von Säften oder saftartigen Lebensmittelprodukten am Beispiel eines Moduls mit einem Kreuzdrallrohr als Mantelrohr,
Fig. 2
eine andere Ausführungsform eines Moduls mit zumindest einem Innenrohr als Kreuzdrallrohr in einem beispielsweise glatten Mantelrohr,
Fig. 3
eine weitere Ausführungsform eines Moduls, in welchem das Mantelrohr und jedes Innenrohr als Kreuzdrallrohr ausgebildet sind,
Fig. 4
einen Detailschnitt der Rohrwandung eines Kreuzdrallrohres mit zum Rohrinneren weisenden Vertiefungen der beiden Drallungen, und
Fig. 5
einen Querschnitt der Rohrwandung eines Kreuzdrallrohres mit an der Rohraußenseite liegenden Vertiefungen der beiden Drallungen.
Embodiments of the subject invention will be explained with reference to the drawings. Show it:
Fig. 1
a tubular heat exchanger for the thermal treatment of juices or juice-like food products using the example of a module with a cross-twist tube as a jacket tube,
Fig. 2
another embodiment of a module having at least one inner tube as a cross-twist tube in an example smooth tubular casing,
Fig. 3
a further embodiment of a module in which the jacket tube and each inner tube are formed as a cross-twist tube,
Fig. 4
a detail section of the pipe wall of a Kreuzdrallrohres pointing to the tube interior recesses of the two swirls, and
Fig. 5
a cross section of the pipe wall of a Kreuzdrallrohres lying on the outside of the tube depressions of the two swirls.

Ein in Fig. 1 gezeigter Modul M eines Röhrenwärmetauschers W zur thermischen Behandlung von Säften oder saftartigen Lebensmittelprodukten mit mittleren bis hohen Viskositäten, beispielsweise einer Viskosität von mehr als etwa 5 mPas, besteht aus einem Mantelrohr 1 und zumindest einem im Inneren des Mantelrohres 1 im Abstand von der Innenwand des Mantelrohres 1 untergebrachten, in etwa koaxialen Innenrohr 2. Der Modul M ist in dem Röhrenwärmetauscher W beispielsweise mit nicht gezeigten weiteren, gleichartigen oder ähnlichen Modulen kombiniert, um eine Behandlungsstrecke einer bestimmten Förderlänge zu bilden. Das Produkt wird entweder nach einem rekuperativen Verfahren behandelt, d.h. Produkt gegen Produkt getrennt durch z.B. das Innenrohr 2, oder nach einem Verfahren, bei dem ein Wärmeträgermedium (Dampf oder Wasser) verwendet wird, wobei das Wärmeträgermedium gegen das Produkt getrennt ist durch beispielsweise das jeweilige Innenrohr 2. Das jeweilige Verfahren wird, vorzugsweise, im Gegenstrom oder im Gleichstrom betrieben.An in Fig. 1 shown module M of a tubular heat exchanger W for the thermal treatment of juices or juicy food products with medium to high viscosities, for example, a viscosity of more than about 5 mPas, consists of a jacket tube 1 and at least one inside the jacket tube 1 at a distance from the inner wall of the jacket tube The module M is combined in the tube heat exchanger W, for example, with other, similar or similar modules not shown, to form a treatment section of a certain conveying length. The product is treated either by a recuperative process, ie product by product separated by, for example, the inner tube 2, or by a method in which a heat transfer medium (steam or water) is used, the heat transfer medium is separated from the product by, for example, the respective Inner tube 2. The respective method is, preferably, operated in countercurrent or in direct current.

Das Mantelrohr 1 in Fig. 1 ist als Kreuzdrallrohr mit einander im Wesentlichen symmetrisch zur Rohrachse X kreuzenden, mehrgängigen Drallungen D1, D2 ausgebildet, wobei der Drallwinkel α zur Rohrachse X zwischen 18° bis 23°und der Anstellwinkel β 67° und 72° zur Rohrachse betragen. Das Kreuzdrallrohr ist beispielsweise ähnlich dem in Fig. 4 gezeigten mit zum Rohrinneren weisenden Vertiefungen 3 ausgebildet. In Fig. 1 ist das jeweilige Innenrohr 2 ebenfalls ein Kreuzdrallrohr mit im Wesentlichen einander symmetrisch zur Rohrachse X kreuzenden mehrgängigen Drallungen und Drallwinkeln α zwischen 18° und 23°.The jacket tube 1 in Fig. 1 is designed as a cross-twist tube with substantially mutually symmetrical to the tube axis X crossing, mehrgängigen swirls D1, D2, wherein the twist angle α to the tube axis X between 18 ° to 23 ° and the angle of attack β 67 ° and 72 ° to the tube axis. The Kreuzdrallrohr for example similar to that in Fig. 4 shown formed with pointing to the tube interior recesses 3. In Fig. 1 is the respective inner tube 2 is also a Kreuzdrallrohr with substantially mutually symmetrical to the tube axis X crossing multi-speed swirls and helix angles α between 18 ° and 23 °.

In der Ausführungsform in Fig. 2 des Moduls M ist das Mantelrohr 1 ein glattes Rohr. Hingegen ist jedes im Mantelrohr 1 enthaltene Innenrohr 2 ein Kreuzdrallrohr mit einander im Wesentlichen symmetrisch zur Rohrachse X kreuzenden, mehrgängigen Drallungen D1, D2 und Drallwinkeln a1 zwischen 18° und 23° zur Rohrachse X. Die Drallungen D1, D2 sind mehrgängig, damit trotz des relativ steilen Anstellwinkels (Drallwinkel a1 zwischen 18° und 23°) die gesamte Rohroberfläche dem Produkt vor allem den Wärmeübergang intensivierende Makrostrukturen anbietet, und zwischen der Steigerung des Wärmeübergangs und dem durch die Drallungen bedingten Druckverlust ein Optimum erzielt wird.In the embodiment in FIG Fig. 2 of the module M, the jacket tube 1 is a smooth tube. On the other hand, each inner tube 2 contained in the jacket tube 1 is a Kreuzdrallrohr with each other substantially symmetrical to the tube axis X crossing, mehrgängigen twist D1, D2 and helix angles a1 between 18 ° and 23 ° to the tube axis X. The twists D1, D2 are more common, so that despite the relatively steep angle of attack (helix angle a1 between 18 ° and 23 °) the entire Pipe surface offers the product above all the heat transfer intensifying macrostructures, and is achieved between the increase in heat transfer and the pressure loss caused by the swirls an optimum.

In der Ausführungsform in Fig. 3 des Moduls M werden für das Mantelrohr 1 und jedes Innenrohr 2 Kreuzdrallrohre mit einander im Wesentlichen symmetrisch zur Rohrachse X kreuzenden, mehrgängigen Drallungen D1, D2 verwendet, wobei auch hier die Drallwinkel α, α1 zwischen 18° und 23° zur Rohrachse X betragen.In the embodiment in FIG Fig. 3 of the module M are used for the casing tube 1 and each inner tube 2 Kreuzdrallrohre with each other substantially symmetrical to the tube axis X crossing, mehrgängigen Drallungen D1, D2, wherein also the twist angle α, α1 be between 18 ° and 23 ° to the tube axis X.

Fig. 4 verdeutlicht die durch die sich kreuzenden Drallungen D1, D2 des jeweiligen Kreuzdrallrohres als das Innenrohr 2 gebildeten Makrostrukturen, die an der Innenseite und der Außenseite des Rohres vorliegen. In Fig. 4 liegen der Rohrachse X zugewandt in Achsrichtung aufeinanderfolgend muldenartige Vertiefungen 3 vor, die jeweils von im Wesentlichen keilförmigen Rippen 5 begrenzt sind und eine Dralltiefe T zwischen 0,8 mm und 1,2 mm haben. Die Breite B jeder Vertiefung 3 beträgt ein Vielfaches der Dralltiefe T, vorzugsweise zwischen 5,0 mm und 20,0 mm. An der Rohraußenseite ist entsprechend der Vertiefung 3 eine gerundete Kuppe 4 vorgesehen, die in axialer Richtung durch annähernd V-förmige Nuten 6 begrenzt wird. Bei einer nicht gezeigten Alternative könnten die Rippen 5 und die Nuten 6 gerundet sein, beispielsweise im Hinblick auf eine gute Reinigbarkeit des Rohres. Die Rippen 5 bzw. die Nuten 6 verlaufen wie auch die Vertiefungen 3 und die Kuppen 4 unter dem Drallwinkel α, α1 schraubengangartig und periodisch einander kreuzend über die gesamte innere bzw. äußere Rohroberfläche. Fig. 4 illustrates the macrostructures formed by the intersecting swirls D1, D2 of the respective Kreuzdrallrohres as the inner tube 2, which are present on the inside and the outside of the tube. In Fig. 4 lie the tube axis X facing in the axial direction successively trough-like depressions 3, which are each bounded by substantially wedge-shaped ribs 5 and have a twist depth T between 0.8 mm and 1.2 mm. The width B of each recess 3 is a multiple of the twist depth T, preferably between 5.0 mm and 20.0 mm. On the outside of the tube, a rounded tip 4 is provided corresponding to the recess 3, which is bounded in the axial direction by approximately V-shaped grooves 6. In an alternative not shown, the ribs 5 and the grooves 6 could be rounded, for example, with regard to a good cleanability of the tube. The ribs 5 and the grooves 6 extend as well as the wells 3 and the crests 4 at the helix angle α, α1 helical and periodically crossing each other over the entire inner or outer pipe surface.

In der Ausführungsform in Fig. 5 ist ein Kreuzdrallrohr als Mantel- oder Innenrohr 1, 2 angedeutet, bei dem die Vertiefungen 3 an der Rohraußenseite (d.h. der Rohrachse X abgewandt) vorliegen. Hierbei weisen die gerundeten Kuppen 4 und die Nuten 6 zur Rohrachse X. Die Dralltiefe T beträgt zwischen 0,8 mm und 1,2 mm. Die Drallwinkel α, α1 liegen zwischen 18° und 23° zur Rohrachse X. Das in Fig. 5 gezeigte Kreuzdrallrohr wird zweckmäßig als Innenrohr 2 verwendet, falls beispielsweise das Produkt zwischen dem Mantelrohr 1 und der Außenseite des Innenrohres 2 strömt. Wird mit einem Wärmeträgermedium gearbeitet, das im Strömungskanal zwischen dem Mantelrohr 1 und jedem Innenrohr 2 strömt, ist zweckmäßig das Kreuzdrallrohr als Innenrohr 2 analog zu Fig. 4 ausgebildet.In the embodiment in FIG Fig. 5 is a Kreuzdrallrohr as a jacket or inner tube 1, 2 indicated, in which the recesses 3 on the outside of the tube (ie the tube axis X facing away) are present. Here, the rounded peaks 4 and the grooves 6 to the tube axis X. The twist depth T is between 0.8 mm and 1.2 mm. The helix angles α, α1 are between 18 ° and 23 ° to the tube axis X. The in Fig. 5 shown cross-twist tube is suitably used as the inner tube 2, for example, if the product flows between the jacket tube 1 and the outside of the inner tube 2. If a heat transfer medium is used, which flows in the flow channel between the jacket tube 1 and each inner tube 2, the cross-twist tube is expediently analogous to the inner tube 2 Fig. 4 educated.

Aus der Verwendung der Kreuzdrallrohre mit einem Anstellwinkel β, β1 von 67° bis 72° und einer Dralltiefe T zwischen 0,8 mm und 1,2 mm bei einer Drallbreite B zwischen etwa 5,0 mm und 20,0 mm resultiert für mittel- oder höherviskose Säfte oder saftartige Lebensmittelprodukte, die Pulpe, Fasern oder Teilchen enthalten können, ein optimales Verhältnis zwischen der durch die Kreuzdralltechnik erzielbaren Steigerung der Wärmeübertragung oder dem Wärmeübertragungskoeffizienten und der in Kauf zu nehmenden Steigerung des Druckverlustes bei der Durchströmung, derart, dass das jeweils angewandte Verfahren (rekuperativ oder mit Wärmeträgermedium) bei nur moderatem Förderdruck eine relativ kleine Wärmetauscherfläche bei dann kurzen Verweilzeiten im Röhrenwärmetauscher erfordert bzw. der Röhrenwärmetauscher W mit einer relativ kurzen Förderstrecke auskommt.From the use of the cross-twist tubes with an angle of attack β, β1 of 67 ° to 72 ° and a twist depth T between 0.8 mm and 1.2 mm with a twist width B between about 5.0 mm and 20.0 mm results for medium or higher viscosity juices or juicy food products which may contain pulp, fibers or particles, an optimum ratio between the increase in heat transfer achievable by the cross-twist technique or the heat transfer coefficient and to be taken into account increase in the pressure loss in the flow, so that the respective method used (recuperatively or with heat transfer medium) at only moderate discharge pressure a relatively small heat exchanger surface then short residence times in the tubular heat exchanger requires or the tubular heat exchanger W with a relatively short Conveyor line gets by.

Claims (10)

  1. Tubular heat exchanger (W) for the treatment of juices and juice-type foodstuff products with medium to high viscosity, with at least one jacket tube (1) containing at least one inner tube (2), wherein at least the inner tube (2) is formed as a crosswise twisted tube with thread-like multi-start spirals (D1, D2) running at an angle of twist (α, α1) to the tube axis (X), and mutually at least essentially symmetrically to the tube axis (X) crossing multi start spirals (D1, D2) characterised in that as the inner tube (2) a crosswise twisted tube is provided with an angle of twist from 18° to 23°.
  2. Tubular heat exchanger according to Claim 1, characterised in that each spiral (D1, D2) has in cross-section a cavity-type indentation (3) with in cross-section approximately wedge-shaped ribs (5) on both sides between which, in the indentation (3), a spiral depth (T) between about 0.8 mm to 1.2 mm is present, and that the indentations and the ribs are arranged on the surface of the inner tube (2) coming in contact with the product.
  3. Tubular heat exchanger according to at least one of the previous claims, characterised in that the width (B) of the indentation (3) viewed in the direction of the tube axis (X) amounts to between about 5.0 and 20.0 mm.
  4. Tubular heat exchanger according to at least one of the previous claims, characterised in that the jacket tube (1) contains a plurality of crosswise twisted inner tubes (2) forming in the jacket tube (1) a module (M) of the tubular heat exchanger (W).
  5. Tubular heat exchanger according to at least one of the previous claims, characterised in that the respective crosswise twisted inner tube (2) has the indentations of the spirals (D1, D2) on the outer side or the inner side.
  6. Tubular heat exchanger according to at least one of the previous claims, characterised in that juices and juice-type products with viscosities of more than about 5 mPas can be processed in the tubular heat exchanger (W).
  7. Use of a tubular heat exchanger according to at least one of the previous claims, characterised in that the juice or juice-type product is processed according to a recuperative method with product separated against product by the respective crosswise twisted tube.
  8. Use of a tubular heat exchanger according to at least one of the previous claims, characterised in that the juice or juice-type product is processed according to a method with a heat transfer medium separated against the product by the respective crosswise twisted tube, preferably with the indentations (3) facing the product.
  9. Use of a tubular heat exchanger (W) according to claim 1 for the thermal treatment of juices or juice-type foodstuff products with medium to high viscosities of more than about 5 mPas.
  10. Use of a tubular heat exchange according to claim 9, wherein the juices or juice-type foodstuff products contain pulp, fibres or particles.
EP10171888.0A 2009-09-08 2010-08-04 Tubular heat exchanger Active EP2299227B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL10171888T PL2299227T3 (en) 2009-09-08 2010-08-04 Tubular heat exchanger

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102009040558A DE102009040558A1 (en) 2009-09-08 2009-09-08 Tubular Heat Exchangers

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EP2299227A2 EP2299227A2 (en) 2011-03-23
EP2299227A3 EP2299227A3 (en) 2016-12-07
EP2299227B1 true EP2299227B1 (en) 2018-09-19

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US (1) US20110056663A1 (en)
EP (1) EP2299227B1 (en)
CN (1) CN102012177A (en)
BR (1) BRPI1003318A2 (en)
DE (1) DE102009040558A1 (en)
ES (1) ES2691257T3 (en)
HU (1) HUE041374T2 (en)
PL (1) PL2299227T3 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011006653A1 (en) 2011-04-01 2012-10-04 Krones Aktiengesellschaft Beverage heating system with integrated incinerator and method for heating beverages
RU2548332C1 (en) * 2013-10-08 2015-04-20 Николай Григорьевич Гладков Heat exchanger
CN104713405B (en) * 2015-03-04 2016-08-17 东南大学 A kind of equilateral triangle arrangement to whirlpool row array row heat-exchanger rig
RU2622340C1 (en) * 2016-07-15 2017-06-14 Федеральное государственное бюджетное образовательное учреждение высшего образования "Юго-Западный государственный университет" (ЮЗГУ) Vortex heat exchange element
RU2672229C1 (en) * 2017-10-17 2018-11-12 Федеральное государственное бюджетное образовательное учреждение высшего образования " Юго-Западный государственный университет" (ЮЗГУ) Vortex heat exchange element

Family Cites Families (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1426515A (en) * 1919-06-14 1922-08-22 Harry M Sprecher Milk-cooling apparatus
US1797014A (en) * 1923-11-12 1931-03-17 Edgar B Nichols Milk-treatment tank
US1918966A (en) * 1930-06-20 1933-07-18 Gen Chemical Corp Apparatus for treating gas
US2080537A (en) * 1935-12-06 1937-05-18 Cherry Burrell Corp Processing vat
US2353912A (en) * 1940-04-23 1944-07-18 Elmer H Berryman Means for homogenizing and heat-treating fluids
US2413360A (en) * 1940-10-02 1946-12-31 Walter Maguire Company Inc Heat exchanger
US2589262A (en) * 1946-06-12 1952-03-18 Hydrocarbon Research Inc Heat exchanger
DE1539323A1 (en) * 1966-06-08 1969-10-02 Siemens Ag Thermogenerator
US3850231A (en) * 1973-05-24 1974-11-26 Combustion Eng Lmfbr intermediate heat exchanger
DE9403913U1 (en) * 1994-03-09 1994-05-05 Gea Finnah Gmbh Tube bundle heat exchanger
JPH0842982A (en) * 1994-05-17 1996-02-16 Hde Metallwerk Gmbh High efficiency type capillary type heat exchanger
US5992512A (en) * 1996-03-21 1999-11-30 The Furukawa Electric Co., Ltd. Heat exchanger tube and method for manufacturing the same
US6273180B1 (en) * 1998-12-23 2001-08-14 L'air Liquide, Societe Anonyme Pour L'etude Et L'eploitation Des Procedes Georges Claude Heat exchanger for preheating an oxidizing gas
SE518089C2 (en) 1999-10-26 2002-08-27 Tetra Laval Holdings & Finance Device at a tube heat exchanger
DE10156374C1 (en) * 2001-11-16 2003-02-27 Wieland Werke Ag Heat exchange tube structured on both sides has inner fins crossed by secondary grooves at specified rise angle
DE10210016B9 (en) * 2002-03-07 2004-09-09 Wieland-Werke Ag Heat exchange tube with a ribbed inner surface
DE10256232B4 (en) * 2002-12-02 2004-10-21 Tuchenhagen Dairy Systems Gmbh Device for extending the service life of tube bundle heat exchangers in indirectly heated UHT systems for food
CN2630783Y (en) * 2003-02-17 2004-08-04 董斌 Multiway spoiling forced heat exchange tube
US20040244958A1 (en) * 2003-06-04 2004-12-09 Roland Dilley Multi-spiral upset heat exchanger tube
CN100451531C (en) * 2005-03-25 2009-01-14 清华大学 Water heater heat exchange tube
CN100489436C (en) * 2006-07-07 2009-05-20 北京美联桥科技发展有限公司 Heat exchanger employing crossed spiral tube
DE102008001659B4 (en) * 2007-07-11 2014-01-30 Halla Visteon Climate Control Corp. Exhaust gas heat exchanger with integrated mounting interface

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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Publication number Publication date
EP2299227A2 (en) 2011-03-23
US20110056663A1 (en) 2011-03-10
EP2299227A3 (en) 2016-12-07
PL2299227T3 (en) 2019-06-28
DE102009040558A1 (en) 2011-03-10
CN102012177A (en) 2011-04-13
BRPI1003318A2 (en) 2012-05-29
ES2691257T3 (en) 2018-11-26
HUE041374T2 (en) 2019-05-28

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