EP1567818B2 - Vorrichtung zur verlängerung der standzeit eines rohrbündel-wärmeaustauschers in indirekt beheizten uht-anlagen für nahrungsmittel - Google Patents

Vorrichtung zur verlängerung der standzeit eines rohrbündel-wärmeaustauschers in indirekt beheizten uht-anlagen für nahrungsmittel Download PDF

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Publication number
EP1567818B2
EP1567818B2 EP03780029.9A EP03780029A EP1567818B2 EP 1567818 B2 EP1567818 B2 EP 1567818B2 EP 03780029 A EP03780029 A EP 03780029A EP 1567818 B2 EP1567818 B2 EP 1567818B2
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EP
European Patent Office
Prior art keywords
tube
uht
macro
swirl
twist
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EP03780029.9A
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German (de)
English (en)
French (fr)
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EP1567818A1 (de
EP1567818B1 (de
Inventor
Uwe Schwenzow
Ludger Tacke
Helmut Buss
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GEA TDS GmbH
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GEA TDS GmbH
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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
    • F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
    • C—CHEMISTRY; METALLURGY
    • C25—ELECTROLYTIC OR ELECTROPHORETIC PROCESSES; APPARATUS THEREFOR
    • C25F—PROCESSES FOR THE ELECTROLYTIC REMOVAL OF MATERIALS FROM OBJECTS; APPARATUS THEREFOR
    • C25F3/00—Electrolytic etching or polishing
    • C25F3/16—Polishing
    • C25F3/22—Polishing of heavy metals
    • C25F3/24—Polishing of heavy metals of iron or steel
    • 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
    • F28D7/16—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 in parallel spaced relation
    • 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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/18—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by applying coatings, e.g. radiation-absorbing, radiation-reflecting; by surface treatment, e.g. polishing
    • F28F13/185—Heat-exchange surfaces provided with microstructures or with porous coatings
    • 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

Definitions

  • the invention relates to a device for extending the service life of a tube bundle heat exchanger in indirectly heated UHT systems for food, in particular for milk or milk products, according to the preamble of claim 1.
  • a UHT process with indirect product heating by heat exchange by means of a heat transfer medium on a wall is understood to mean a thermal product treatment, which is also called aseptic heating, in which virtually all microorganisms, but at least all spoil Microorganisms that could grow during the storage phase of the product at room temperature. Accordingly, all microorganisms except some, possibly the heating process surviving heat-resistant spores must be killed. However, at normal room temperature they do not grow above a critical level during the storage phase.
  • the indirect product heating by a heat exchange on a wall can be done both with so-called plate heat exchangers or, as in the present case, with so-called tube bundle heat exchangers.
  • the problem is represented continuously on milk or milk products with approximately the same kinematic viscosity ⁇ , since these applications represent an essential field of application of the UHT systems of the generic type.
  • a UHT heating system with indirect product heating initially includes a preheater for heating the product. Thereafter, the milk is usually passed through a so-called. Homogenizer in this indirect UHT heater system. This is followed by a further heat exchange, a so-called preheat attitude for protein stabilization of the milk proteins for the subsequent milk heating process, then the actual UHT heating with heat retention, then the cooling with heat exchange with the incoming milk and, if necessary, a post-cooling. Depending on the particular technology, homogenization may take place before or even after UHT heating.
  • the heat transfer medium is water, which is circulated and heated in accordance with the temperature-time curve in the milk supply at higher temperature in countercurrent to the milk and the return of the milk, this also cools in countercurrent.
  • This heat exchange is regenerative, whereby up to 90% of the energy used can be recovered.
  • the UHT heater is excluded from this regenerative heat exchange and the necessary residual heating is effected here by indirect heating with steam during diversion of the water cycle (Principle FINNAH, Ahaus, H. KESSLER, Dairy Process Engineering, 3rd edition, 1988).
  • An indirect UHT heating system which has been used successfully in practice, realizes both the regenerative heat exchange and the non-regenerative heat exchange in the UHT heater by means of so-called tube bundle heat exchangers (US Pat. DE-U-94 03 913 ; Tuchenhagen Dairy Systems GmbH, Ahaus), wherein several parallel connected inner tubes are provided, which are traversed by the milk, while the heat transfer medium, usually water or steam, in the annular gap space (outer channel) of the jacket tube (outer jacket), which in parallel Inner tubes surrounds, flows in countercurrent.
  • a single-tube system without heat exchange is used for the UHT-Hanger.
  • the flow rate of the product, of the milk or of the milk product has a decisive influence on the product batch formation, since in this case the deposition process is overlaid by shearing forces in the area of the flow boundary layer of the pipe inner wall as a result of deposit formation.
  • UHT heating systems with shell and tube heat exchangers make particular use of this last-mentioned effect with respect to plate heat exchangers, since the flow velocity in the inner tubes is chosen to be relatively high due to the design and thus a relatively high Reynolds number, corresponding to the flow boundary layer, from the one lower residence time of the milk ingredients follows, is given.
  • the UHT heater and the UHT hot holder are the critical equipment area of a UHT heating system as far as the problem of batch formation is concerned. It is obvious that on the one hand the heat exchange at the inner tubes deteriorates due to product batch formation, ie the heat transfer coefficient k is significantly reduced, and on the other hand due to the deposit formation the pressure loss ⁇ p v in the inner tubes, which is inversely proportional to the fifth power of the inner tube diameter D i , increases significantly.
  • the cleaning and sterilization time accounts for about 10 to 15% of the service life, so there is also the desire and the need to reduce these times in absolute terms and not only relative to a prolonged service life.
  • cleaning in particular such using chemical means, however, it should be noted that the germs in topographical shoals (roughness) especially on rolled, annealed, chemically pickled and then not further mechanically treated surfaces correspondingly require extended exposure times. Thereafter, in the sense of the hygienic final conditions, the subsequent problem arises that all organic and inorganic contamination substances must be washed away from the surface without residue.
  • a heat transfer tube which is used as an evaporation and condensation tube in devices such as heat exchangers and heat pipes and which has on the surface of its tube inner wall macro-roughness structures which extend at an angle to the longitudinal direction of the heat transfer tube.
  • These macro-roughness structures are, on the one hand, a multiplicity of mutually parallel main grooves, which run at said angle, have a trapezoidal cross-section and whose depth is in the range of 0.15 to 0.35 mm.
  • a plurality of mutually parallel narrow grooves are provided, which extend at an angle to the longitudinal direction of the heat transfer tube, these narrow grooves the tube only partially detect and each of the narrow grooves has a base and two side surfaces and within the main grooves and to these is formed in parallel.
  • the side surfaces of said narrow grooves are inclined closely to the base surface, whereby each of the side surfaces and the base surface each form a sharp cut.
  • the edges of the grooves should act as nucleation sites for the bubbles.
  • Such heat transfer tubes are not suitable for use in indirectly heated UHT systems for foodstuffs, since in particular the narrow grooves would favor product batch formation and thus reduce the service life of the UHT systems.
  • the said zones can hardly be described as relatively large macro-roughness structures of the tube and with regard to the different surface roughnesses there is no indication as to whether these surface roughnesses would favor or inhibit the formation of a batch in UHT heaters and / or UHT subcarriers.
  • Tube bundle heat exchanger which usually consists of a plurality of tube bundles, each of which has a plurality of parallel connected inner tubes with a common inlet and a common outlet for a product to be heated.
  • the respective group of inner tubes is enclosed by an outer sheath, which is provided near the ends with a radially in or out connecting connecting piece for a heat transfer medium, which bounded from the outer sheath relative to the inner tubes outer channel in countercurrent to the pipe flow in one of the inner tubes Passes through the inner channel.
  • the inventive solution makes use of two mechanisms, namely on the one hand by the mechanism of increasing the turbulence in the thermal and hydraulic boundary layer of the pipe flow in the inner tube.
  • This is achieved by virtue of the fact that the respective inner tube of a UHT heater and downstream UHT hot holder has macro-roughness structures M R at least on the surface of its tube inner wall, which are oriented at an angle of attack 35 ⁇ ⁇ ⁇ 25 degrees with respect to the longitudinal axis of the inner tube.
  • This results in a turbulent momentum exchange transverse to the main flow direction in the region of the thermal and hydraulic boundary layer, whereby the formation of product approaches is inhibited.
  • Such macro-roughness structures must be such that they protrude from the laminar lower layer of the boundary layer and thus generate or favor the desired momentum exchange.
  • these macro-roughness structures must be oriented with respect to the main flow direction of the pipe flow so that the addition of product approaches is not favored.
  • the invention further makes use of a second mechanism, which is decisively influenced by the microscopic nature of the surface of the tube inner wall of the inner tube.
  • a second mechanism which is decisively influenced by the microscopic nature of the surface of the tube inner wall of the inner tube.
  • the surface of the pipe inner wall structured in this way is treated surface-wide by means of an electrochemical polishing process which produces a micro-surface texture m R which is characterized structurally and energetically by a reduced tendency for the adhesion of foreign substances.
  • this is not primarily concerned with the structural feature of the surface, which is determined by a so-called roughness depth value, such as the average roughness R z or the arithmetic mean roughness R a (definition according to DIN EN ISO 4287). It is in fact a widespread fallacy (see G.
  • HENKEL A-4830 Waidhofen / Thaya, article No. 35, 2001, "Modern surface treatment of high quality stainless steel tubes for heat exchanger use", reprint from PROCESS, 8th year, March 2001, "Appearance is deceptive") to define the quality of a metal surface by specifying a roughness depth value, because this is only a quantitative comparison size given, which can not convey a real idea of the effective surface shape and other-quality.
  • the prevention of scale formation on stainless steel surfaces, or at least their reduction or inhibition, which the present invention has set as its primary objective with a view to extending the service life or reducing the cleaning and sterilization time, essentially depends on the physical conditions the surface determined.
  • the microscopic binding mechanisms of surface contamination are of interest.
  • these are mainly bridge bonds and also mechanical anchors.
  • a micro-surface quality m R is proposed, which changes the energetic rather than the structural nature of the respective stainless steel surface. This is achieved by professional electrochemical polishing (see also the company publication HENKEL pickling and electropolishing technology, A-3830 Waidhofen / Thaya, "The surface ensures the value of the component").
  • the surface of these tubes is coated on the one hand with a gapless passive layer, which consists of a relatively thick chromium oxide layer (> 2 nm compared to ⁇ 1 nm in the mechanical pre-grinding, without electrochemical polishing).
  • a gapless passive layer which consists of a relatively thick chromium oxide layer (> 2 nm compared to ⁇ 1 nm in the mechanical pre-grinding, without electrochemical polishing).
  • the surface is virtually stress-free as a result of the stress-free electrochemical polishing removal and exhibits a material-specific, specific energy level of about 1.3 N / m (compared to about 2.2 N / m with mechanical pre-sanding). Passivation and reduction of the energy level result primarily in the reduced tendency for the adhesion of foreign substances, i. the significantly strongly reduced tendency of the coating.
  • the removal effected by the electrochemical polishing method is about 10 to 15 ⁇ m, which has been shown, for example, by a study (G. HENKEL), that 1 cm 2 projected surface then has about 2.5 to 4 cm 2 true surface area ( compared to 12 to 14 cm 2 with mechanical pre-sanding).
  • the tendency for scale formation is inhibited when the topographic shoals of a surface whose number is related to the aforementioned true surface are at least equal to, better smaller than the representative size of the undesirably accumulating particles.
  • the product mixtures consist of proteins with a size of 1 to 2 ⁇ m, microorganisms> 1.5 ⁇ m and sugars and salts in the range of 0.7 to 0.8 ⁇ m.
  • the objective pursued by the invention namely to prolong the service life of the UHT heating systems in question and to shorten the cleaning and sterilization time, can be achieved in a significant way by combining the two measures described above Macro-roughness structures M R outside the laminar sublayer and on the other by the micro-surface texture m R substantially inside the laminar sub-layer of the flow boundary layer in the inner ear relate.
  • the invention provides that the swirl, product-preselected, has a swirl depth t and a swirl width b. It is further proposed in this context to make the swirl tube catchy with a pitch H G.
  • a further development of the device according to the invention provides that the swirl tube is more multi-threaded Gear number g and each with a pitch H G is formed. In this way it is possible to cover the entire surface of the inner tube with the desired macro-roughness structures.
  • the critical range of a UHT heating system is to be seen in relation to product approaches in the field of UHT heaters and UHT heaters.
  • product approaches are also evident in other areas of a UHT heating system.
  • the inner tubes of the UHT plant upstream and downstream of the UHT heater and UHT heat holder should also be installed in a temperature range above of 100 degrees Celsius, are provided with the macro-roughness structures M R and the micro-surface texture m R according to the invention.
  • a tube bundle 1 ( FIG. 1 ; see also DE-U-94 03 913 ) consists in its middle part of an outer channel 2 'delimiting outer shell 2 with a, based on the presentation position, left side arranged Festlager conciseenareamantelflansch 2a and a right side arranged loslager constitutionalenareamantelflansch 2b.
  • the latter is followed by a first transverse channel 4a * bounded by a first housing 4.1 with a first connecting branch 4a, and a second transverse channel 4b * bounded by a second housing 4.2 adjoining the outer bearing flange 2a with a second connecting branch 4b.
  • a number of axially parallel to the outer shell 2 through the outer channel 2 'extending, together an inner channel 3' forming inner tubes 3, 3 *, starting with four and then rising to nineteen and possibly more in number, are each end in one fixed bearing pipe support plate 8 and a loslager remedyen pipe support plate 8 (both also referred to as pipe mirror plate) and welded at its pipe outer diameter D a in this, this overall arrangement introduced via an unspecified opening on the second housing 4.2 in the outer shell 2 and a fixed bearing side Ausauscherflansch 5 is clamped together with the second housing 4.2 with the interposition of a respective flat gasket 9 (fixed bearing 5, 7, 4.2).
  • the two housings 4.1, 4.2 are also sealed with respect to the respective adjacent Jardinmantelflansch 2b, 2a with a flat gasket 9, wherein the right side arranged first housing 4.1 in conjunction with the outer shell 2 via a loslager facultyencommunauscherflansch 6 with the interposition of an O-ring 10 against the left side arranged fixed bearing 5, 7, 4.2 is pressed.
  • the loslager discoverede tube support plate 8 engages through an unspecified hole in the pilot bearing side Ausauscherflansch 6 through and is compared to the latter by means of the dynamically stressed O-ring 10, which also seals the first housing 4.1 statically against the loslager facilityen exchanger flange 6.
  • the latter and the loslager furnishede tube support plate 8 form a so-called.
  • Floating bearing 6, 8 which allows the changes in length of welded in the loslager constitutionalen tube support plate 8 inner tubes 3, 3 * due to temperature change in both axial directions.
  • the inner tubes 3, 3 * based on the presentation position, either from left to right or vice versa to be flowed through by a product P to be heated, wherein the average flow velocity in Inner tube 3, 3 * and thus in the inner channel 2 'is marked with v.
  • the cross-sectional interpretation usually takes place in such a way that this average flow velocity v is also present in a connecting bend 11 which is connected on one side to the fixed bearing side exchanger flange 5 and on the other side indirectly to a loose bearing side connecting piece 8d connected to the loose bearing side tube carrier plate 8. With the two connecting bend 11, the tube bundle 1 in question is connected in series with the respectively adjacent tube bundle.
  • the fixed bearing side exchanger flange 5 forms an inlet E for the product P and the loose bearing side connecting piece 8d accommodates an associated outlet A; at each adjacent tube bundle return These entry and exit conditions in each case accordingly.
  • the fixed bearing side exchanger flange 5 has a first connection opening 5a, which corresponds on the one hand to a nominal diameter DN and thus to a nominal passage cross section A 0 of the connecting bend 11 connected thereto and which, on the other hand, is dimensioned such that there the mean flow velocity v in the inner tube 3, 3 * or Inner channel 3 'corresponding flow velocity is present.
  • the product P to be treated either flows via the first connection opening 5a or the second connection opening 8a to the tube bundle 1, so that either the fixed-bearing-side tube carrier plate 7 or the tube-side tube carrier plate 8 is flown against. Since a heat exchange between product P in the inner tubes 3, 3 * and a heat transfer medium W in the outer jacket 2 has to take place in countercurrent in each case, this heat transfer medium W flows either to the first connecting piece 4a or to the second connecting piece 4b at a flow rate c. In the event that the product P flows to the tube bundle 1 via the first connection opening 5a, an inlet temperature of the product ⁇ E would be present here.
  • the heat transfer medium W would leave the outer jacket 2 in countercurrent via the second connecting piece 4b with an outlet temperature of the heat transfer medium ⁇ A.
  • the temperature difference at the product inlet ⁇ - ⁇ a - ⁇ E present in the region of the second connecting piece 4 b in practice, in addition to the abovementioned pressure drop ⁇ p v in the inner tubes 3, 3 *, provides a reliable indicator of the degree of product batch formation in the inner tubes 3, 3 * dar.
  • the proposed device according to the invention is reflected in the design of the surface of the tube inner wall 3a of the respective inner tubes 3, 3 *, wherein the respective eligible inner tube 3, 3 *, which has the tube outer diameter D a , in the form of a so-called.
  • Swirl tube 3 * is formed (see also FIGS. 2 to 5 ).
  • a so-called spin 3a * which is defined by a twist depth t and a twist width b ( FIG. 3 ), forms the desired macro-roughness structure M R , which rises above the laminar underlayer of the boundary layer within the tube flow in the inner tube 3, 3 * and provides for the increased turbulence and the desired pulse exchange.
  • the surface of the tube inner wall 3a of the swirl tube 3 * which is structured by the macro-roughness structure M R, is furthermore treated over the entire surface by means of an electrochemical polishing process which produces a micro-surface texture m R which is structurally and energetically characterized by a reduced inclination for characterizes the attachment of foreign substances.
  • the expert electrochemical polishing method is usually applied to simply standardized inner surface designs of the inner tube 3, 3 * designed as a stainless steel tube, wherein the stainless steel is preferably austenitic chromium nickel steel alloys. In the electrochemical polishing supplied stainless steel tube is usually longitudinally welded and, because of this longitudinal seam, calibrated and then bleached bare tubes.
  • the starting sheet for tube production was usually cold rolled, annealed and chemically pickled.
  • the processing of Rehre in the tube bundle 1 is expediently carried out after the electrochemical polishing; a mechanical rework of the circular welds does not take place.
  • the average surface roughness for the surface is R a ⁇ (0.7 to 0.8) ⁇ m and in the region of the longitudinal weld R a ⁇ 1.2 ⁇ m.
  • the surface roughness is reduced by the electrochemical removal from the surface, this aspect has only a relative one to the micro surface texture m R sought here, namely the reduction in the tendency for foreign substances to adhere to the surface subordinate influence.
  • the influencing factors generated by the electrochemical polishing are, in comparison to the untreated starting surface, essentially the reduction of the true surface area over the projected ones Reduction of the energy level of the surface (surface tension) and the gapless, chromium oxide-rich passive layer (passivation).
  • a catchy trained swirl tube 3 * ( FIG. 4 ), which has the same pitch H G and spin width b as that according to FIG. 2
  • the macro-roughness structure M R covers the entire surface due to the treatment by means of the electrochemical polishing process extends.
  • the degree of surface coverage desired or required by macro-roughness structures M R depends on the product-specific requirements. As long as an increase in the proportion of the surface occupied by macro-roughness structures M R results in an extension of the service life, the inner tubes designed as a swirl tube 3 * will be equipped with the multistage swirl 3a * required for this purpose.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Geometry (AREA)
  • Electrochemistry (AREA)
  • Materials Engineering (AREA)
  • Metallurgy (AREA)
  • Organic Chemistry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Food Preservation Except Freezing, Refrigeration, And Drying (AREA)
  • Greenhouses (AREA)
  • Confectionery (AREA)
EP03780029.9A 2002-12-02 2003-11-22 Vorrichtung zur verlängerung der standzeit eines rohrbündel-wärmeaustauschers in indirekt beheizten uht-anlagen für nahrungsmittel Expired - Lifetime EP1567818B2 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10256232A DE10256232B4 (de) 2002-12-02 2002-12-02 Vorrichtung zur Verlängerung der Standzeit von Rohrbündel-Wärmeaustauschern in indirekt beheizten UHT-Anlagen für Nahrungsmittel
DE10256232 2002-12-02
PCT/EP2003/013131 WO2004051174A1 (de) 2002-12-02 2003-11-22 Vorrichtung zur verlängerung der standzeit eines rohrbündel-wärmeaustauschers in indirekt beheizten uht-anlagen für nahrungsmittel

Publications (3)

Publication Number Publication Date
EP1567818A1 EP1567818A1 (de) 2005-08-31
EP1567818B1 EP1567818B1 (de) 2006-07-26
EP1567818B2 true EP1567818B2 (de) 2013-07-17

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EP03780029.9A Expired - Lifetime EP1567818B2 (de) 2002-12-02 2003-11-22 Vorrichtung zur verlängerung der standzeit eines rohrbündel-wärmeaustauschers in indirekt beheizten uht-anlagen für nahrungsmittel

Country Status (6)

Country Link
EP (1) EP1567818B2 (da)
AT (1) ATE334371T1 (da)
DE (2) DE10256232B4 (da)
DK (1) DK1567818T4 (da)
ES (1) ES2268454T5 (da)
WO (1) WO2004051174A1 (da)

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DE102005007556B4 (de) * 2005-02-18 2007-05-03 Tuchenhagen Dairy Systems Gmbh Verfahren und Verbindungsarmatur zur Reduzierung der Bildung von Ablagerungen an Rohrträgerplatten von Rohrbündel-Wärmeaustauschern
DE102005007557A1 (de) * 2005-02-18 2006-08-24 Tuchenhagen Dairy Systems Gmbh Verfahren und Vorrichtung zur Herstellung einer verlängert haltbaren Trinkmilch
DE102005030999B4 (de) * 2005-07-02 2007-10-25 Tuchenhagen Dairy Systems Gmbh Anordnung zur Strömungsführung in Rohrbündel-Wärmeaustauschern zur thermischen Behandlung von Suspensionen
DE102005059463B4 (de) 2005-12-13 2009-12-24 Gea Tds Gmbh Vorrichtung zur Einflussnahme auf die Strömung im Bereich einer Rohrträgerplatte eines Rohrbündel-Wärmeaustauschers
AU2006331887B2 (en) 2005-12-21 2011-06-09 Exxonmobil Research And Engineering Company Corrosion resistant material for reduced fouling, heat transfer component with improved corrosion and fouling resistance, and method for reducing fouling
US8201619B2 (en) 2005-12-21 2012-06-19 Exxonmobil Research & Engineering Company Corrosion resistant material for reduced fouling, a heat transfer component having reduced fouling and a method for reducing fouling in a refinery
DE102008050153B4 (de) 2008-10-01 2022-02-03 Rational Ag Gargerät mit Wärmetauscherleitung
DE102009006246B3 (de) * 2009-01-27 2010-05-20 Gea Tds Gmbh Vorrichtung zur Einflussnahme auf die Strömung im Bereich einer Rohrträgerplatte eines Rohrbündel-Wärmeaustauschers
DE102009040560A1 (de) 2009-09-08 2011-03-10 Krones Ag Röhrenwärmetauscher
DE102009040558A1 (de) 2009-09-08 2011-03-10 Krones Ag Röhrenwärmetauscher
DE202011051486U1 (de) * 2011-09-29 2013-01-08 Schröder Maschinenbau KG Rohrwärmetauscher
MX2015004497A (es) * 2012-10-17 2015-07-06 Tetra Laval Holdings & Finance Elementos de sujecion de tubo.
DE102016007637B4 (de) * 2016-06-23 2020-02-20 Gea Tds Gmbh Verfahren zum Betrieb eines Rohrbündel-Wärmeaustauschers zur Erhitzung eines temperatursensiblen Konzentrats eines Lebensmittelprodukts unter hohem Druck und Rohrbündel-Wärmeaustauscher zur Durchführung des Verfahrens
EP3499172B1 (de) * 2017-12-12 2021-07-14 Steinmüller Engineering GmbH Überhitzer enthaltend eine verbrennungsgasen ausgesetzte rohranordnung enthaltend längstnahtgeschweisste rohre für dampferzeuger mit korrosiven rauchgasen
WO2023098966A1 (de) 2021-11-30 2023-06-08 Gea Tds Gmbh Verfahren und anlage zur uht-erhitzung eines trinkfähigen lebensmittelprodukts auf pflanzlicher basis unter sterilen bedingungen

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EP0722075A1 (de) † 1995-01-10 1996-07-17 HDE METALLWERK GmbH Hochleistungskapillar-Wärmeaustauscher

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EP0722075A1 (de) † 1995-01-10 1996-07-17 HDE METALLWERK GmbH Hochleistungskapillar-Wärmeaustauscher

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ES2268454T5 (es) 2013-11-25
EP1567818A1 (de) 2005-08-31
DK1567818T4 (da) 2013-08-19
DE10256232A1 (de) 2004-07-15
DE50304393D1 (de) 2006-09-07
ES2268454T3 (es) 2007-03-16
DE10256232B4 (de) 2004-10-21
DK1567818T3 (da) 2006-11-20
WO2004051174A1 (de) 2004-06-17
EP1567818B1 (de) 2006-07-26
ATE334371T1 (de) 2006-08-15

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