EP1567818B1 - Dispositif pour prolonger la duree d'utilisation d'un echangeur thermique a faisceau tubulaire dans des installations a ultra-haute temperature (uht) pour produits alimentaires, a chauffage indirect - Google Patents

Dispositif pour prolonger la duree d'utilisation d'un echangeur thermique a faisceau tubulaire dans des installations a ultra-haute temperature (uht) pour produits alimentaires, a chauffage indirect Download PDF

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Publication number
EP1567818B1
EP1567818B1 EP03780029A EP03780029A EP1567818B1 EP 1567818 B1 EP1567818 B1 EP 1567818B1 EP 03780029 A EP03780029 A EP 03780029A EP 03780029 A EP03780029 A EP 03780029A EP 1567818 B1 EP1567818 B1 EP 1567818B1
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Prior art keywords
tube
uht
swirl
macro
product
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EP03780029A
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German (de)
English (en)
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EP1567818A1 (fr
EP1567818B2 (fr
Inventor
Uwe Schwenzow
Ludger Tacke
Helmut Buss
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GEA TDS GmbH
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Tuchenhagen Dairy Systems 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.
  • 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 (DE-U-94 03 913, Tuchenhagen Dairy Systems GmbH, Ahaus), wherein a plurality of 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 surrounds the parallel-connected inner tubes flows in countercurrent.
  • tube bundle heat exchangers DE-U-94 03 913, Tuchenhagen Dairy Systems GmbH, Ahaus
  • 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 of the deposits and the re-provision of aseptic conditions constitutes an interruption in operation, which represents a considerable cost factor on the one hand with regard to an interruption of the production and on the other hand with regard to the cleaning process itself.
  • the extension of service life is a priority concern in order to reduce production costs.
  • An essential starting point for extending the service life is the reduction of the formation rate.
  • priority should be given to complete denaturing of potentially formation-forming protein by appropriate constructive measures. If the possibilities of reducing the prerelease of the milk are exhausted, attention must be paid to the area of shell and tube heat exchangers in the relevant high temperature ranges of the UHT heater for further reduction.
  • 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 in 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 evaporation and condensation tube in devices such as heat exchangers and heat pipes and which has on the surface of its inner pipe 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 is provided, which extend at an angle to the longitudinal direction of the heat transfer tube, these narrow grooves only partially grip the tube and each of the narrow grooves has a base and two side surfaces and is formed parallel to the main grooves and to these.
  • 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.
  • DE 197 51 405 A1 describes a heat transfer tube in which the heat exchange surface has zones of different surface roughness on the side facing the flowing medium, these zones being strip-shaped and running in a small angle of inclination with respect to the main flow direction of the medium.
  • the operation of this known heat transfer tube stands and falls obviously with the alternately arranged strip-shaped zones of different surface roughness, because this arrangement is intended to produce in the region of the transition between the flowing medium and the heat exchange surface of the thermal boundary layer tearing distribution of the flow velocity.
  • the said zones can hardly be described as relatively large macro-roughness structures of the pipe and with regard to the different surface roughnesses there is no indication as to whether these Surface roughness would favor or inhibit product batch formation in UHT heaters and / or downstream UHT heaters.
  • 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 subordinate UHT hot holder has macro-roughness structures M R at least on the surface of its tube inner wall, which at an angle of attack 35 ⁇ ⁇ ⁇ 25 degrees oriented 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 present invention with a view is based on the extension of the service life or the reduction of the cleaning and sterilization time to the primary goal, are determined essentially by the physical conditions on the surface.
  • 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 gap-free 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 gap-free 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 shows 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, secondly, by the micro-surface texture m R substantially within the laminar sub-layer of the flow boundary layer in the inner ear.
  • 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.
  • 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 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; in the adjacent bundle of tubes, these inlet and outlet conditions each turn 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 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.
  • a so-called swirl 3a * which is defined by a swirl depth t and a swirl width b (FIG. 3), forms the desired macro-roughness structure M R which extends over the laminar lower layer of the boundary layer within the pipe flow in the inner pipe 3, 3 * rises and provides for the increased turbulence and the desired pulse exchange. It can be seen from FIG.
  • 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.
  • the stainless steel tube supplied to the electrochemical polishing is usually longitudinally welded and, because of this longitudinal seam, calibrated and subsequently pickled tubes.
  • the starting sheet for tube production was usually cold rolled, annealed and chemically pickled.
  • 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 produced by the electrochemical polishing are, compared to the untreated starting surface, essentially the reduction of the true surface from the projected, the reduction of the energy level of the surface (surface tension) and the gapless, chromium oxide-rich passive layer (passivation).

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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)

Claims (9)

  1. Dispositif pour prolonger la durée d'utilisation d'un échangeur thermique à faisceau tubulaire dans des installations à ultra haute température (UHT) à chauffage indirect, destinées à des produits alimentaires, en particulier du lait et des produits laitiers, constitué d'un échangeur thermique à faisceau tubulaire qui comporte
    - un canal extérieur (2') entouré d'une paroi extérieure (2),
    - des tubes intérieurs (3 ; 3*) d'axe parallèle à la paroi extérieure (2), s'étendant à travers le canal extérieur (2'), formant un faisceau tubulaire (1) constitutif d'un canal intérieur (3'), s'appuyant par leurs extrémités sur une plaque de support (7, 8),
    - une entrée (E) et une sortie (A) d'un produit (P) à chauffer, ladite entrée et ladite sortie étant communes à tous les tubes intérieurs (3 ; 3*), et
    - des raccords (4a, 4b) prévus à proximité des extrémités de la paroi extérieure (2) et des plaques de support (7, 8) des tubes, débouchant radialement dans, respectivement sortant radialement du canal extérieur (2'), et, pourvus chacun d'un canal perpendiculaire (4a*, 4b*) pour un fluide caloporteur (W),
    étant observé qu'au moins la paroi intérieure (3a) du tube intérieur considéré (3, 3*) présente une structure de surface à rainures torsadées (3*) avec des macrostructures de rugosité (mR) ayant un angle d'incidence (α) par rapport à l'axe longitudinal du tube intérieur (3 ; 3*)
    caractérisé en ce que
    - la paroi intérieure (3a) du tube structurée par des macrostructures de rugosité (MR) est traitée entièrement par un procédé de polissage électrochimique produisant une mirco-configuration de surface (Mr) qui se distingue structurellement et énergétiquement par une tendance réduite à l'adhérence de substances étrangères en raison d'une passivation et d'une réduction du niveau énergétique de la surface traitée de la paroi intérieure (3a) du tube, et
    - l'angle d'incidence (a) se trouve dans la zone 35 ≥ α ≥ 25 degrés.
  2. Dispositif selon la revendication 1 caractérisé en ce que le tube intérieur (3, 3*) qui présente une structure de surface à rainures torsadées (3*) avec des macrostructures de rugosité (MR) comporte un profilage hélicoïdal intérieur et extérieur, dont la torsion (3a*) présente un angle d'inclinaison (δ = 90 degrés - α) se trouvant dans la zone 55 ≤ δ ≤ 65 degrés.
  3. Dispositif selon la revendication 2 caractérisé en ce que la torsion (3a*) qui peut être choisie préalablement en fonction du type de produit, présente une profondeur de rainure (t) et une largeur de rainure (b).
  4. Dispositif selon les revendications 2 ou 3 caractérisé en ce que le tube ayant une structure de surface à rainures torsadées (3*) présente un pas unique de hauteur (HG).
  5. Dispositif selon les revendications 2 ou 3 caractérisé en ce que le tube ayant une structure de surface à rainures torsadées (3*) présente un nombre de pas (g) de hauteur de pas (HG).
  6. Dispositif selon la revendication 5 caractérisé en ce que la largeur des rainures torsadées (b) se déduit de la hauteur (HG) divisée par le nombre de pas (g), à savoir (b = HG/g).
  7. Procédé d'utilisation du dispositif selon l'une des revendications 1 à 6 caractérisé en ce que le nombre Reynolds (Re) de l'écoulement dans le tube intérieur (3, 3*) se trouve dans la zone 35.000 ≤ Re ≤ 65.000.
  8. Procédé selon la revendication 7 caractérisé en ce que les tubes intérieurs considérés (3 ; 3*) sont agencés dans un échauffeur à ultra haute température (UHT) et dans un accumulateur de chaleur à ultra haute température (UHT) disposé en aval dudit réchauffeur.
  9. Dispositif selon les revendications 7 ou 8 caractérisé en ce que les tubes intérieurs (3 ; 3*) des échangeurs thermiques de l'installation à ultra haute température (UHT), qui sont disposés en amont et en aval de l'échauffeur à ultra haute température (UHT) et de l'accumulateur de chaleur à ultra haute température (UHT), sont également pourvus de macrostructures de rugosité (MR) et d'une micro-configuration de surface (mR), dans la mesure où ils sont utilisés dans une zone de température au-dessus de 100°C.
EP03780029.9A 2002-12-02 2003-11-22 Dispositif pour prolonger la duree d'utilisation d'un echangeur thermique a faisceau tubulaire dans des installations a ultra-haute temperature (uht) pour produits alimentaires, a chauffage indirect Expired - Lifetime EP1567818B2 (fr)

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 (fr) 2002-12-02 2003-11-22 Dispositif pour prolonger la duree d'utilisation d'un echangeur thermique a faisceau tubulaire dans des installations a ultra-haute temperature (uht) pour produits alimentaires, a chauffage indirect

Publications (3)

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

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ID=32403682

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Application Number Title Priority Date Filing Date
EP03780029.9A Expired - Lifetime EP1567818B2 (fr) 2002-12-02 2003-11-22 Dispositif pour prolonger la duree d'utilisation d'un echangeur thermique a faisceau tubulaire dans des installations a ultra-haute temperature (uht) pour produits alimentaires, a chauffage indirect

Country Status (6)

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

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WO2023098966A1 (fr) 2021-11-30 2023-06-08 Gea Tds Gmbh Procédé et système pour le traitement uht d'un produit alimentaire à boire à base de plantes dans des conditions stériles

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DE102005007557A1 (de) * 2005-02-18 2006-08-24 Tuchenhagen Dairy Systems Gmbh Verfahren und Vorrichtung zur Herstellung einer verlängert haltbaren Trinkmilch
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
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
JP2009521660A (ja) 2005-12-21 2009-06-04 エクソンモービル リサーチ アンド エンジニアリング カンパニー ファウリングを抑制させるための耐食材料、改良された耐食性およびファウリング抵抗性を有する伝熱装置、およびファウリングを抑制させるための方法
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
WO2014060425A1 (fr) * 2012-10-17 2014-04-24 Tetra Laval Holdings & Finance S.A. Elément de retenue de tube
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DE50304393D1 (de) 2006-09-07
EP1567818A1 (fr) 2005-08-31
ATE334371T1 (de) 2006-08-15
EP1567818B2 (fr) 2013-07-17
WO2004051174A1 (fr) 2004-06-17
DK1567818T4 (da) 2013-08-19
DE10256232B4 (de) 2004-10-21
DE10256232A1 (de) 2004-07-15
DK1567818T3 (da) 2006-11-20
ES2268454T3 (es) 2007-03-16
ES2268454T5 (es) 2013-11-25

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