WO2010086004A1 - Vorrichtung zur einflussnahme auf die strömung im bereich einer rohrträgerplatte eines rohrbündel-wärmeaustauschers - Google Patents
Vorrichtung zur einflussnahme auf die strömung im bereich einer rohrträgerplatte eines rohrbündel-wärmeaustauschers Download PDFInfo
- Publication number
- WO2010086004A1 WO2010086004A1 PCT/EP2009/009082 EP2009009082W WO2010086004A1 WO 2010086004 A1 WO2010086004 A1 WO 2010086004A1 EP 2009009082 W EP2009009082 W EP 2009009082W WO 2010086004 A1 WO2010086004 A1 WO 2010086004A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- section
- flow
- cross
- guide ring
- annular gap
- Prior art date
Links
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/16—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
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/02—Header boxes; End plates
- F28F9/026—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits
- F28F9/0265—Header boxes; End plates with static flow control means, e.g. with means for uniformly distributing heat exchange media into conduits by using guiding means or impingement means inside the header box
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
- F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
-
- 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
Definitions
- the invention relates to a device for influencing the flow in the region of a tube carrier plate of a tube bundle heat exchanger, in particular for the food and beverage industry, with an outer channel surrounded by an outer shell for a heat transfer medium, with a number of axially parallel to the outer shell extending through the outer channel , together forming an inner channel, each end supported in the pipe support plate inner tubes, with a common for all inner tubes, formed in a Ausauscherflansch inlet or outlet and a common, formed in a connection piece outlet or entry for a product, with at least one Flow in the flow area of the pipe support plate influencing displacement, which is immovably attached to one / on the Ausauscherflansch or the connecting piece connecting bow / connection fitting, axially symmetrical and ko nzentrisch arranged to the pipe support plate and which is formed from at least two sections which form a common, largest inner outer diameter at their connecting cross-section, and with the displacer, which divides the flow to the inner channel axially
- a device of the generic type is known from DE 10 2005 059 463 A1 B3 or WO 2007/068343 A1.
- the eligible shell-and-tube heat exchanger is described in DE 94 03 913 U1.
- Such shell and tube heat exchangers are generally better than other types of heat exchangers because of their cross-sectional geometry, such as plate heat exchangers suitable for thermal treatment of high and low viscosity products, whole piece solids products, pulp or fibers. Nevertheless, it can also be observed here that in the case of fibrous media, for example juices with pulp, deposits form on the inlet openings of the inner tubes of the tube carrier plates. The treatment at relatively high temperatures favors the agglomeration of fibers and the formation of pulp. These are preferably deposited on the webs between the multi-arranged inner tubes and on the transverse to the flow direction oriented surfaces of the tube support plate and can lead to blockages there. Temporary deposits dissolve from time to time and the lumps then possibly get into the packaging of the particular product intended for the end user, where they are undesirable.
- the inventive idea is then to solve the problem of the uniform distribution of power in this area in Rohrtragerplatten with large radial extent that the known, desired current-mechanical effects of the Verdrangerkorpers compared to its surroundings also from another component, a Leit ⁇ ng
- This arrangement and configuration causes the guide ring axial flow divides the flow to the inner channel of the shell and tube heat exchanger, deflects outwards by a radial flow component is generated, and in a nozzle-like outer between the guide ring and an outer inner contour of Ausauscherflansches or connecting piece Ring gap cross section accelerated. Subsequent to the nozzle-like narrowed outer annular gap cross-section, the guide ring, viewed in the flow direction, forms, together with the outer inner contour, a widening outer annular gap cross-section.
- the device according to the invention is primarily used on the inflow side of the tube support plate, so that here the deposits in question are effectively prevented.
- the displacer and the guide ring are arranged either in a connecting bow designed as a 180-degree elbow or in a connection fitting effecting a 180-degree flow deflection, these ends ending either in an exchanger flange or a connecting piece.
- the connecting bend or connecting fitting in each case connects two adjacent tube bundles of the tube bundle heat exchanger connected in series, essentially in parallel, connected in series.
- a related tube bundle heat exchanger is known, for example, from DE 94 03 913 U1, a connecting sheet used in this is disclosed, for example, in WO 2004/051 174 A1 or WO 2004/083 761 A1 and a related connection fitting is described in DE 10 2005 059 463 A1.
- the desired fluidic effect of the guide ring arises, inter alia, from the annular gap cross section between the latter and the outer inner contour of the exchanger flange or the connecting piece.
- the guide ring influences the surrounding flow particularly effectively if, as provided for in two proposals, a first extended passage cross section within the exchanger flange or a second extended passage cross section within the connection piece is part of the outer inner contour.
- the desirable separation of the flow is brought about, according to an advantageous embodiment, by a circumferential inner flow separation edge embodied on the displacement body.
- This internal flow-off edge is particularly effective if, as also provided, it is positioned in a widening inner annular gap cross-section of the guide ring.
- the fluid-mechanical function of the proposed displacement body is particularly advantageous for carrying, if, as is provided by a further advantageous embodiment, the inner flow separation edge at the narrowest point (minimum inner Rinspaltquerites) of the inner annular gap cross-section is positioned.
- a further embodiment in this respect provides for the inner flow separation edge, as seen in the flow direction, to be positioned behind the narrowest point (minimum inner gap cross-section) of the inner annular gap cross-section.
- the requirements placed on the displacer not only consist in exerting a particularly effective influence on the flow that can be influenced by it in the region of the tube support plate, but it is also to be designed in such a way that it causes the lowest possible pressure losses and not itself becomes a problem for deposits.
- An advantageous embodiment provides in this regard that the at least two sections of the drängerMechs are designed axially symmetrical and at the connecting cross-section with each other, the common, largest inner outer diameter, forming the inner flow breaking edge.
- the two sections, the flowed-in and the flow-out section are each bounded by a concave outer contour.
- the attachment of the displacer to the connecting bow or the connection fitting is favored mechanically and fluidically if, as provided, the flowed portion of the displacer is provided with a shaft part extending in the direction of its axis of symmetry, which is engaged by the fastening cross-piece (s) (attack).
- the flow resistance of the displacer is kept small if the first concave outer contour assigned to the inflowed section is rounded off on the inflow side by a first convex outer contour.
- concave outer contours are rounded off by a second convex outer contour. This continuous transition between see the two concave outer contours counteracts a product approach formation in this area, without being forfeited by this rounding the desirable formation of the to be provided in this area inner flow separation edge.
- the second concave outer contour assigned to the streamed sections is rounded off at the downstream side by a third convex outer contour.
- the desirable detachment of the flow at the guide ring is brought about in accordance with an advantageous embodiment by a peripheral outer flow tear-off edge embodied thereon.
- the latter is particularly effective when it, as is also provided, is positioned in the widening outer annular gap cross-section of the exchanger flange or the connecting piece.
- the fluid-mechanical function of the proposed guide ring is particularly advantageous if, as is provided by a further advantageous embodiment, the outer flow-off edge is positioned at the narrowest point (minimum outer annular gap cross-section of the outer annular gap cross-section.
- a further related embodiment provides to position the outer flow-off edge, as seen in the flow direction, behind the narrowest point (minimum outer Rinspaltquerexcellent) of the outer annular gap cross-section.
- the flow resistance of the guide ring is kept small when the free end of its inflow section is convexly rounded.
- a related rounding also counteracts a product approach formation in the inflow of the guide ring.
- a product approach formation in the outflow region of the guide ring is counteracted when the free end of the outflow section of the guide ring is convexly rounded.
- the immovable attachment of the displacer and the guide ring is very simple, if this at least one of both attacking at the same time rod-shaped attachment with the connecting beam or the connection du ⁇ gsarmatur are connected. Sufficient stability of the attachment and a symmetrical influence of the flow through the attachment are ensured when three evenly distributed over the circumference of the displacer and thus also of the guide ring arranged mounting brackets are provided.
- the least possible influence on the flow through the fastening system (s) results in the inflow region of the guide ring when it engages (engages) at the free end of the inflow section of the guide ring.
- the least possible influence on the flow through the fastening traverse (s) results in the inflow region of the displacement body when it engages (touches) the flowed-on section of the displacement body.
- a low flow resistance of the attachment is achieved and a product attachment formation by the attachment is counteracted if, as is furthermore provided, the flowed-off section of the displacement body is provided with a shaft part extending in the direction of its axis of symmetry, on which the fastening beam (s) attacks (attack).
- the connecting bow or the connecting fitting is formed in the fastening region of the fastening traverse (s) with a reinforced wall thickness in the form of a circumferential reinforcing ring.
- FIG. 1 shows a central section through a so-called tube bundle as a modular part of a possibly consisting of a plurality of such tube bundle shell and tube heat exchanger, wherein on each side a circular connecting bow or a connection fitting with 180 degree deflection according to DE 10 2005 059 463 A1 is arranged on the / the features of the invention find application.
- Figure 2 is a perspective view of a central section through a
- FIG. 3 is a perspective view of the central section through the connecting arch according to FIG. 2, the view now being directed to the
- Figure 4 shows the central section through the connecting sheet according to the
- Figures 2 and 3 and Figure 4a shows a central section through the isolated, detached from Figure 4 displacer.
- a prior art tube bundle heat exchanger 100 generally composed of a plurality of tube bundles 100.1 to 100.n, wherein 100.i denotes an arbitrary tube bundle (FIG. 1, see also DE 94 03 913 U1), consists of an outer channel in its middle part 200 * limiting outer sheath 200 with a, based on the display position, left side disposed fixed bearing side Jardinmantelflansch 200a and a right side arranged loslager constitutionalenareamantelflansch 200b.
- a first transverse channel 400a * bounded by a first housing 400.1 with a first connecting piece 400a closes and the outer jacket flange 200a adjoins a second transverse channel 400b * bounded by a second housing 400.2 with a second connecting branch 400b.
- the two housings 400.1, 400.2 are likewise sealed off from the respectively adjacent outer jacket flange 200b, 200a by a flat gasket 900, the first housing 400.1 arranged on the right side being connected to the outer jacket 200 via a replacement bearing 600 with the interposition of an O-ring 910 against the left arranged fixed bearing 500, 700, 400.2 is pressed.
- the loose bearing side tube support plate 800 engages through an unspecified hole in the loose bearing side Ausauscherflansch 600 through and is compared to the latter by means of the dynamically stressed O-ring 910, which also seals the first housing 400.1 statically against the loose bearing side 600 Ausauscherflansch.
- the latter and the loose-side pipe support plate 800 form a so-called movable bearing 600, 800, which permits the changes in length of the inner pipes 300 welded in the loose bearing side pipe support plate 800 as a result of temperature change in both axial directions.
- the inner tubes 300 based on the display position, either from left to right or vice versa of a product P are flowed through, wherein the average flow velocity in the Inner tube 300 and thus in the inner channel 200 * is marked with v.
- the design in the form of a cross-section takes place in such a way that this average flow velocity v is also present in a connection bend 1000 or a connection fitting 1100, which, with reference to the relevant tube bundle 100.i, on the one hand with the fixed-side Exchanger flange 500 and on the other hand indirectly connected to one with the loslager chandelieren pipe support plate 800 firmly connected loslager stoolen connection piece 80Od.
- the fixed-bearing-side exchanger flange 500 has a first connection opening 500a, which corresponds to a nominal diameter DN and thus a nominal passage cross-section A 0 of the connection bend 1000 connected there or the connection fitting 1100, wherein the connection opening 500a is generally dimensioned such that there is the middle one Flow velocity v in the inner tube 300 and mecanickanal 300 * corresponding flow rate is present.
- a second connection opening 800a is dimensioned in the loose-side-side connecting piece 80Od, with the respective connection opening 500a or 800a being directed to a respectively enlarged through-flow cross-section 500c or 800c in the region to the adjacent pipe support plate 700 or 800, respectively. NEN conical transition 500b and 800b extended.
- the extended passage cross section 500c or 800c is substantially cylindrical with a diameter Di (largest diameter of the first extended passage cross section 500c) executed, the latter usually one to two nominal widths larger than the nominal diameter DN of the connecting bow 1000 or the connection fitting 1100 (nominal passage cross section A 0 of the connecting bend or the connection fitting) and accordingly correspondingly larger than the total passage cross section nA, all of the inner tubes 300 of the number n entering the fixed bearing side exchanger flange 500 are dimensioned with a respective inner tube diameter D and a passage cross section A 1 .
- the extended passage section 500c and 800c forms an inner contour K 1 in the fixed bearing side exchanger flange 500 and the movable bearing 80Od connecting piece together with the first conical transition 500b or 800b.
- the product P to be treated either flows via the first connection opening 500a or the second connection opening 800a to the tube bundle 100.1 to 100.n, so that either the fixed-bearing-side tube support plate 700 or the loose-side pipe support plate 800 is flown. Since in any case a heat exchange between product P in the inner tubes 300 or the inner channels 300 * and a heat transfer medium M in the outer jacket 200 or in the outer channels 200 * has to take place in countercurrent, this heat transfer medium M flows either the first connection piece 400a or to the second connecting piece 400b with a flow velocity in the outer casing c.
- a per se known displacement body 10 ( Figure 4a; for example, prior art according to DE 10 2005 059 463 A1) is formed a total of rotationally symmetrical to its longitudinal axis, an axis of symmetry S and is composed of a pre preferably cylindrical shank portion 10i having a shaft diameter d 3 and an adjoining flowed-on portion 10a immediately thereafter, wherein the transition between the two is continuous.
- the inflow portion 10a is connected to a remote, flow-away portion 10b, and both Sections 10a, 10b form at their connection cross-section with each other a common, largest inner outer diameter d max , which may at the same time also be a circumferential inner flow-off edge 10c
- the Verdrangerkorper 10 is so arranged in the Ausauscherflansch 500 or the connecting piece 80Od of the connecting bow 1000 and the connection fitting 1100 ( Figures 2 to 4) that its Symmetneachse S concentric with the longitudinal axis of the Rohrbundeis 100 ⁇ and thus concentric with the pipe support plate 700, 800 ((s The shaft part 10 ⁇ is fixedly connected to the connecting bow 1000 or the connection fitting 1100.
- the above-described arrangement known per se realizes, as far as the displacement body 10 alone is concerned, one on the upstream side of the pipe support plate 700 , 800 positioned Verdrangerkorper 10
- the solution according to the invention then consists (FIGS. 2 to 4, 4 a) that the displacement body 10, which is known per se and has its basic features, is arranged in a rotationally symmetrical, hulsenformigen guide ring 11 such that the axis of symmetry S of the displacement body 10 and that of the guide ring 11 are congruent latter is at least of a Anstrom- 11 a and a Abstromabêt formed 11 b, which are designed axialsymmet ⁇ sch and a common greatest external diameter D max to each other at their connecting cross-sectional form (Figure 3), which at the same time a circumferential outer Stromungsab ⁇ sskante 11c
- the respective free end of the inflow 11a and the outflow section 11b are preferably rounded in a convex manner
- the guide ring 11 is connected directly or indirectly to the connecting bow 1000 or the connection fitting 1100 in the illustrated embodiment, the Verdrangerkorper 10 and this concentrically enclosing guide ring 11 over three evenly over the circumference of the Verdrangerkorpers 10 and thus also the guide ring 11 arranged distributed , stabformige fastening beams 12 with the connecting bow 1000 fixedly connected ( Figure 3), wherein the fastening bars 12 at the free end of the Anstromabitess 11 a and at the same time directly or indirectly on the flowed portion 10a, and here preferably on the extending in the direction of the axis of symmetry S shaft portion 1Oi, attack (Figure 4a).
- the connection arc 1000 or the connection fitting 1100 is formed in the fastening region of the fastening crossbars 12 with a reinforced wall thickness in the form of a circumferential reinforcing ring 13 (FIGS. 2 to 4).
- the at least two sections 10a, 10b of the displacement body 10 are each bounded by a concave outer contour 10g, 10h (FIG. 4a), wherein the first concave outer contour 10g assigned to the flowed-in section 10a is rounded off on the upstream side by a first convex outer contour 10d.
- the concave outer contours 10g, 10h are rounded off from one another by a second convex outer contour 10e, and the second concave outer contour 10h associated with the outflowed portion 10b is rounded off on the downstream side by a third convex outer contour 10f.
- the displacer 10 forms between its shaft portion 10i and the adjoining inflow portion 10a, which is formed with the first concave outer contour 10g, and the Anströmabites 11 a of the guide ring 11, which forms a first portion of an inner inner contour K M , a nozzle-like narrowing inner annular gap cross-section A S1 (FIG. 4).
- the latter is limited at its narrowest point, a minimum inner annular gap cross section As mi ⁇ i, radially inwardly of the inner flow separation edge 10c.
- the second concave outer contour 10h formed on the flow-out section 10b of the displacer 10 forms, viewed in the direction of flow, a widening inner annular gap cross-section ASEI together with a second section of the inner inner contour Kn.
- the product flow P (E) entering into the tube bundle 100 results from an exiting product flow P (A) which flows out of the upstream tube bundle 100.i-1 via the connection bend 1000 or the connection fitting 1100.
- the flow is accelerated in the between the displacement body 10 and the inner inner contour K M of the guide ring 11 narrowed inner annular gap cross section Asi and reaches at its narrowest point, the minimum inner annular gap cross section Asmmi, a maximum flow velocity.
- the inner flow-off edge 10c is positioned in the embodiment at the location of the minimum inner annular gap cross-section Asmim.
- the flow is deflected behind the displacer 10 to the center of the tube support plate 700, 800, whereby a uniform flow through all inner tubes 300 or Intne ⁇ kanäle 300 * takes place in this central region (see also Figure 1).
- the passage cross section for the flow expands behind the minimum inner annular gap cross section Asmim.
- the thus curved and retarded flow must inevitably come off in this area.
- Due to the inner flow separation edge 10c the detachment takes place according to plan at this clearly defined point.
- the described flow movement behind the displacer 10 leads there according to the fluid mechanical laws to a secondary flow on which the desired effect, namely the prevention of deposits in the central region of the streamlined pipe support plate 700, 800, based in part.
- the guide ring 11 forms between its inflow section 11a and a first section of an outer inner contour K, 2 , which is essentially offset from the first niche transition 500b in Ausauscherflansch 500 and the upstream, the first connection opening 500a enclosing pipe part or from the second conical transition 800b in the connection piece 80Od and the upstream, the second connection opening 800a enclosing tube part is formed, a nozzle-like narrowing outer annular gap cross section As 2 (FIG 4).
- the outer annular gap cross-section A S2 is limited at its narrowest point, a minimum outer annular gap cross-section Asmm 2 , radially inward of the outer flow-off edge 11 c.
- the outflow portion 11 b of the guide ring 11 forms, as seen in the flow direction, together with a second portion of the outer inner contour K l2 , which substantially from the first conical transition 500 b in the exchanger flange 500 and the downstream first extended passage cross section 500 c or from the second conical transition 800 b formed in the connecting piece 80Od and the second extended second passage cross-section 800c, an expanding outer annular gap cross-section ASE2 (FIG. 4).
- the guide ring 11 in the enclosing outer inner contour K, 2 divides the via the connection arc 1000 or the connection fitting 1100 with an unevenly distributed flow velocity w to the inner channel 300 * (see FIG. 1) of the tube bundle 100.i through the annular gap cross sections A 32 , A Sm , n2 and A S E2 flowing incoming product flow P (E) axially symmetrical over the entire circumference of the annular gap cross sections and deflects him in the main to the outside ( Figures 2, 4).
- the flow is accelerated in the between the guide ring 11 and the outer inner contour Ki 2 nozzle-like narrowed outer annular gap cross section As 2 and reaches at its narrowest point, the minimum outer annular gap cross section A Sm ⁇ n2 , a maximum flow velocity.
- the outer flow-off edge 11c (FIG. 4) is positioned in the exemplary embodiment at the location of the minimum outer annular gap cross-section A Sm 2.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Details Of Heat-Exchange And Heat-Transfer (AREA)
- Devices For Dispensing Beverages (AREA)
Abstract
Description
Claims
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
BRPI0924161A BRPI0924161A2 (pt) | 2009-01-27 | 2009-12-17 | dispositivo para influenciar o fluxo na área de uma placa de tubo de distribuição de um trocador de calor de feixe tubular |
US13/146,552 US9513062B2 (en) | 2009-01-27 | 2009-12-17 | Device for influencing the flow in the area of a pipe manifold plate of a tube bundle heat exchanger |
EP09801407.9A EP2382435B1 (de) | 2009-01-27 | 2009-12-17 | Rohrbündel-wärmeaustauschers mit einer vorrichtung zur einflussnahme auf die strömung im bereich einer rohrträgerplatte |
DK09801407.9T DK2382435T3 (en) | 2009-01-27 | 2009-12-17 | Tube bundle heat exchanger with a device for influencing the flow in an area with a rørbæreplade |
ES09801407.9T ES2540748T3 (es) | 2009-01-27 | 2009-12-17 | Intercambiador de calor de haz tubular con un dispositivo para influir sobre el flujo en la zona de una placa portatubos |
PL09801407T PL2382435T3 (pl) | 2009-01-27 | 2009-12-17 | Płaszczowo-rurowy wymiennik ciepła z urządzeniem do oddziaływania na przepływ w obszarze płyty sitowej |
ZA2011/05511A ZA201105511B (en) | 2009-01-27 | 2011-07-26 | Device for influencing the flow in the area of a pipe manifold plate of a tube bundle heat exchanger |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009006246.7 | 2009-01-27 | ||
DE102009006246A DE102009006246B3 (de) | 2009-01-27 | 2009-01-27 | Vorrichtung zur Einflussnahme auf die Strömung im Bereich einer Rohrträgerplatte eines Rohrbündel-Wärmeaustauschers |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010086004A1 true WO2010086004A1 (de) | 2010-08-05 |
Family
ID=42102589
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2009/009082 WO2010086004A1 (de) | 2009-01-27 | 2009-12-17 | Vorrichtung zur einflussnahme auf die strömung im bereich einer rohrträgerplatte eines rohrbündel-wärmeaustauschers |
Country Status (10)
Country | Link |
---|---|
US (1) | US9513062B2 (de) |
EP (1) | EP2382435B1 (de) |
BR (1) | BRPI0924161A2 (de) |
DE (1) | DE102009006246B3 (de) |
DK (1) | DK2382435T3 (de) |
ES (1) | ES2540748T3 (de) |
PL (1) | PL2382435T3 (de) |
UA (1) | UA99564C2 (de) |
WO (1) | WO2010086004A1 (de) |
ZA (1) | ZA201105511B (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102997720A (zh) * | 2012-12-12 | 2013-03-27 | 中冶南方(武汉)威仕工业炉有限公司 | 管程可自由膨胀的管壳式换热器 |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10239479A1 (de) | 2002-08-28 | 2004-03-04 | Bayer Cropscience Ag | Substituierte spirocyclische Ketoenole |
EP2607833A1 (de) * | 2011-12-22 | 2013-06-26 | Tetra Laval Holdings & Finance S.A. | Modul für verbesserte Laufzeit in röhrenförmigen Wärmetauschern |
DE102014012279B3 (de) * | 2014-08-22 | 2015-08-20 | Gea Tds Gmbh | Krümmer für einen Rohrbündel-Wärmeaustauscher für große Produktdrücke, Herstellverfahren für einen und Rohrbündel-Wärmeaustauscher mit einem solchen Krümmer und Verwendung eines Rohrbündel-Wärmeaustauschers für große Produktdrücke mit einem solchen Krümmer in einer Zerstäubungstrocknungsanlage |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1263969B (de) | 1965-03-19 | 1968-03-21 | Hoesch Ag | Prallverteiler fuer eine Kugelregenanlage |
US5261485A (en) | 1991-08-21 | 1993-11-16 | Hpd, Incorporated | Slurry distributor |
DE9403913U1 (de) | 1994-03-09 | 1994-05-05 | Gea Finnah Gmbh | Rohrbündel-Wärmetauscher |
WO2004051174A1 (de) | 2002-12-02 | 2004-06-17 | Tuchenhagen Dairy Systems Gmbh | Vorrichtung zur verlängerung der standzeit eines rohrbündel-wärmeaustauschers in indirekt beheizten uht-anlagen für nahrungsmittel |
DE10311529B3 (de) | 2003-03-17 | 2004-09-16 | Tuchenhagen Dairy Systems Gmbh | Vorrichtung zur Einflussnahme auf den Anströmbereich einer Rohrträgerplatte eines Rohrbündel-Wärmeaustauschers |
DE102005059463A1 (de) | 2005-12-13 | 2007-06-14 | Tuchenhagen Dairy Systems Gmbh | Vorrichtung zur Einflussnahme auf die Strömung im Bereich einer Rohrträgerplatte eines Rohrbündel-Wärmeaustauschers |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2343560A (en) * | 1940-06-15 | 1944-03-07 | Klein Hans | Distributor for fluids |
US2925830A (en) * | 1956-04-17 | 1960-02-23 | Kautrowitz Arthur | Fluid flow rectifier |
SE9203842L (sv) * | 1992-12-21 | 1994-06-22 | Alfa Laval Food Eng Ab | Statisk blandare |
FR2766914B1 (fr) * | 1997-07-29 | 1999-10-29 | D Applic Thermiques Comp Ind | Distributeur destine a equiper les echangeurs thermiques intratubulaires des installations de refroidissement a fluide frigorigene de type diphasique |
US7762715B2 (en) * | 2008-10-27 | 2010-07-27 | Cavitation Technologies, Inc. | Cavitation generator |
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2009
- 2009-01-27 DE DE102009006246A patent/DE102009006246B3/de not_active Expired - Fee Related
- 2009-12-17 US US13/146,552 patent/US9513062B2/en active Active
- 2009-12-17 DK DK09801407.9T patent/DK2382435T3/en active
- 2009-12-17 EP EP09801407.9A patent/EP2382435B1/de active Active
- 2009-12-17 ES ES09801407.9T patent/ES2540748T3/es active Active
- 2009-12-17 PL PL09801407T patent/PL2382435T3/pl unknown
- 2009-12-17 UA UAA201110412A patent/UA99564C2/ru unknown
- 2009-12-17 WO PCT/EP2009/009082 patent/WO2010086004A1/de active Application Filing
- 2009-12-17 BR BRPI0924161A patent/BRPI0924161A2/pt not_active IP Right Cessation
-
2011
- 2011-07-26 ZA ZA2011/05511A patent/ZA201105511B/en unknown
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1263969B (de) | 1965-03-19 | 1968-03-21 | Hoesch Ag | Prallverteiler fuer eine Kugelregenanlage |
US5261485A (en) | 1991-08-21 | 1993-11-16 | Hpd, Incorporated | Slurry distributor |
DE9403913U1 (de) | 1994-03-09 | 1994-05-05 | Gea Finnah Gmbh | Rohrbündel-Wärmetauscher |
WO2004051174A1 (de) | 2002-12-02 | 2004-06-17 | Tuchenhagen Dairy Systems Gmbh | Vorrichtung zur verlängerung der standzeit eines rohrbündel-wärmeaustauschers in indirekt beheizten uht-anlagen für nahrungsmittel |
DE10311529B3 (de) | 2003-03-17 | 2004-09-16 | Tuchenhagen Dairy Systems Gmbh | Vorrichtung zur Einflussnahme auf den Anströmbereich einer Rohrträgerplatte eines Rohrbündel-Wärmeaustauschers |
WO2004083761A1 (de) | 2003-03-17 | 2004-09-30 | Tuchenhagen Dairy Systems Gmbh | Vorrichtung zur einflussnahme auf den anströmbereich einer rohrträgerplatte eines rohrbündel-wärmeaustauschers |
DE102005059463A1 (de) | 2005-12-13 | 2007-06-14 | Tuchenhagen Dairy Systems Gmbh | Vorrichtung zur Einflussnahme auf die Strömung im Bereich einer Rohrträgerplatte eines Rohrbündel-Wärmeaustauschers |
WO2007068343A1 (de) | 2005-12-13 | 2007-06-21 | Tuchenhagen Dairy Systems Gmbh | Vorrichtung zur einflussnahme auf die strömung im bereich einer rohrträgerplatte eines rohrbündel-wärmeaustauschers |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN102997720A (zh) * | 2012-12-12 | 2013-03-27 | 中冶南方(武汉)威仕工业炉有限公司 | 管程可自由膨胀的管壳式换热器 |
CN102997720B (zh) * | 2012-12-12 | 2014-08-13 | 中冶南方(武汉)威仕工业炉有限公司 | 管程可自由膨胀的管壳式换热器 |
Also Published As
Publication number | Publication date |
---|---|
EP2382435B1 (de) | 2015-04-08 |
BRPI0924161A2 (pt) | 2016-02-10 |
ES2540748T3 (es) | 2015-07-13 |
EP2382435A1 (de) | 2011-11-02 |
US20120138265A1 (en) | 2012-06-07 |
UA99564C2 (ru) | 2012-08-27 |
DK2382435T3 (en) | 2015-07-13 |
DE102009006246B3 (de) | 2010-05-20 |
PL2382435T3 (pl) | 2015-08-31 |
ZA201105511B (en) | 2012-04-25 |
US9513062B2 (en) | 2016-12-06 |
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