EP0160662B1 - Wärmetauscher mit mantel und rohrbündel und verfahren dafür - Google Patents

Wärmetauscher mit mantel und rohrbündel und verfahren dafür Download PDF

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Publication number
EP0160662B1
EP0160662B1 EP84903691A EP84903691A EP0160662B1 EP 0160662 B1 EP0160662 B1 EP 0160662B1 EP 84903691 A EP84903691 A EP 84903691A EP 84903691 A EP84903691 A EP 84903691A EP 0160662 B1 EP0160662 B1 EP 0160662B1
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EP
European Patent Office
Prior art keywords
tube
shell
layer
boundary
space
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP84903691A
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English (en)
French (fr)
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EP0160662A4 (de
EP0160662A1 (de
Inventor
Richard A. Holl
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Vapor Corp
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Vapor Corp
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Filing date
Publication date
Application filed by Vapor Corp filed Critical Vapor Corp
Priority to AT84903691T priority Critical patent/ATE34220T1/de
Publication of EP0160662A1 publication Critical patent/EP0160662A1/de
Publication of EP0160662A4 publication Critical patent/EP0160662A4/de
Application granted granted Critical
Publication of EP0160662B1 publication Critical patent/EP0160662B1/de
Expired legal-status Critical Current

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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
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/02—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by influencing fluid boundary
    • 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
    • F28F13/003—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by using permeable mass, perforated or porous materials

Definitions

  • This invention is concerned with new shell and tube apparatus for heat transfer and with a new process for heat transfer, as employed in such apparatus.
  • EP-A-42613 describes a new process and apparatus for heat transfer by which the heat transfer can be increased without a corresponding disproportionate increase in pumping power, and with avoidance of turbulence in the presence of laminar wake-interference flow.
  • EP-A-42613 discloses shell and tube heat exchange apparatus for heat exchange between two fluids comprising:
  • An object of the present invention is to provide an improvement on such apparatus, permitting easier manufacture, assembly and disassembly.
  • the spheroidal members (28) and the space-filling material (58) constitute a unitary body, the spheroidal members protruding from the body engaging the inner wall of the tube (20).
  • fluid flow within the shell space also takes the form of a non-turbulent boundary layer immediately adjacent to the tube outer surface, and a core-layer interfacing with the boundary-layer, and there is a shell-side fluid flow interrupter structure within the shell space comprising a plurality of spheroidal members surrounding and contacting the tube outer wall, the structure interrupting non-turbulently the full development of at least the boundary-layer at the tube outer surface at a plurality of spaced interruption spots, whereby parts of the interrupted boundary-layer will separate non-turbulently from the tube outer surface between the interruption spots and mix with the core layer to effect heat transfer between the tube outer surface, its respective boundary-layer, and the core-layer; and the space between the shell-side interrupter structure spherical members and the shell inner wall is filled with a space-filling material to prevent useless flow of fluid in a part of the shell interior space remote from the tube outer surface.
  • boundary-layers 30 immediately adjacent the passage surfaces 20, which act to insulate the wall surfaces from the main body of the fluid flowing in a core layer 32 between the interfacing with the boundary layers 30, and which therefore reduce the heat transfer between the surfaces 20 and the core layer 32. It is also known that an unobstructed boundary layer increases progressively in thickness in the direction of fluid flow, which will increase its insulating effect.
  • the boundary layers 30 are interrupted in a "spot-wise" manner at spaced spots 34 by means of fluid flow interrupter spheres 28 interposed between the heat transfer surfaces, while maintaining a non-turbulent fluid flow in the core 32.
  • the heat transfer surfaces 20 not roughened, etc., but on the contrary they are made as smooth as is economically possible, to the extent that in many embodiments the surfaces 20 will be polished to the desired degree of smoothness.
  • the disruption of the boundary layers 30 at the multitude of spaced spots 34 ensures that they stay thin, while the manner of their disruption ensures that turbulence is avoided that would cause unduly high friction drag.
  • the polishing of all surfaces including those of the spheres also assists in the desired minimizing of the friction drag.
  • the ratio of convective heat transfer to friction power per unit heat transfer surface area is improved by providing specially shaped interrupting and mixing structures of low friction drag immediately adjacent a smooth heat transfer surface using hydraulic radii that guarantee total laminar flow.
  • the mixing structures contain cellular voids, which are connected with one another. In each of which the fluid rotates spiral-like as a single laminar eddy.
  • These eddies are very efficient means of mixing laminar streams, and preferably are obtained by coinciding a wake eddy downstream of an interruption point with an advance eddy upstream of a subsequent interruption point so as to produce wake-interference flow, which provides the highest efficiency.
  • boundary layers 30 on the curved surfaces of the mixing structures are fairly thick, whereas the boundary layers of the heat transfer surfaces, situated opposite the mixing-structure surfaces, remain very thin on average because they are reduced regularly and spotwise at the large number of contact points between the surface of the mixing structure and the heat transfer surface, and are in addition exposed to the highest local velocities which occur predominantly very close to the flat heat transfer surface. This allows rapid heat flow through the heat transfer surface.
  • the general direction of flow of the fluid is indicated by arrows 31 and the flow interrupter structure causes the production of laminar flow eddies 38 of shape and rotational frequency that depend upon the geometry of the structure.
  • Wake-eddies will be produced around the spots of interruption downstream of the flow, while advance eddies will be produced upstream of the flow. If the spacing of the interruption spots 34 is made such that the advance- and wake-eddies of immediately successive spots coincide, then wake-interference flow is obtained whereby, in the absence of turbulent friction-drag, very efficient non-turbulent mixing is obtained between the interrupted boundary-layers 30 and the adjacent core layer 32.
  • a turbulent flow which is to be avoided, may be distinguished from an eddy in that the former is irregular and there is no observable pattern as with an eddy. Eddies and swirls therefore do not constitute turbulence. Again a laminar eddy or vortex is confined by solid boundaries or by laminar fluid flows, while a turbulent eddy or vortex will be surrounded by other eddies and vortices which interact with the turbulent eddy or vortex.
  • the conditions for maintenance of laminar flow with a particular structure can be observed for example by providing suitable windows in an experimental structure and adding visible fluids to the fluid flow if required.
  • the interposed structure it is not necessary for the interposed structure to touch the passage walls as long as it is sufficiently close thereto to provide the necessary extent of interruption to the boundary layers.
  • the portion of each spherical surface around the actual point of contact and submerged in the boundary layer will also be effective in this interrupting function.
  • the interrupter structure may therefore be suspended within the enclosure and not actually touch the walls, or touch the walls at fewer points than there are interruption points.
  • the profile of the interrupter structure elements of the structure of Figure 1 taken in the direction of flow of the fluid in the passage is of course a circle.
  • Other profiles can be used and should be such as to present a smoothly contoured surface to the fluid flow, so as to reduce friction losses to a minimum and also to ensure the maintenance of laminar flow, for example an ellipsoidal profile shows an egg-shaped profile and a drop-shaped profile; in the latter two profiles the face of largest radius faces upstream.
  • the fluid is very viscous, such as a viscous oil that is to be heated.
  • the spacing apart of the parallel walls 20 of the passage can be increased considerably without the establishment of turbulent flow, but such a fluid is usually of low thermal conductivity and a thermal boundary layer will be established immediately adjacent to the heat transfer surface that is much thinner that the respective boundary layer.
  • the interposed structure must be arranged to interrupt this thinner thermal boundary-layer irrespective of the thickness of the boundary layer.
  • the principal factor in the determination of the thickness of the thermal boundary layer is the Prandtl number, which is high and the thermal conductivity is low.
  • FIGS 2 and 3 show a single tube-in-shell exchanger as disclosed in EP-A-42613 in which one fluid path with inlet and outlet 14 and is respectively is formed by the annular space between an outer shell 54 and an inner circular cross-section tube 22, while the other fluid path with inlet 48 and outlet 50 is of course formed by the tube 22.
  • the annular shell space is of radial dimension just sufficient to receive flow-interrupting spheres 28 and the spaces between the spheres and the inner wall of the outer shell are completely filled with a suitable cementitious material 56 to prevent fluid flow therethrough that would be wasted.
  • the interrupter system employed within the tube 22 comprises rows of smaller spheres that used to provide the necessary flow capacity with a suffi- cienty large number of interrupting points 34 both along the length of the tube and also around its circumference. As with the shell-side interrupter system the useless space between the rows if filled with a cementitious or other suitable material 58, such as concrete or ceramic cement.
  • the separate spheres 28 and cement 58 in which they are embedded can constitute a unitary structure formed for example by casting, so that the spheroidal members 28 protruding from the central matrix will engage the inner tube wall.
  • a unitary structure can be more easily manufactured and more easily assembled into and disassembled from the apparatus.
  • successive spheroidal members along the length of the structure are displaced offset circumferentially, giving the same effect as if the rows of spheroidal members had been disposed helically, with a large number of flow interruption points adjacent the tube surface 20 and enhanced reduction of the flow cross-sectional area.
  • the cylinder of spheroidal members and the space-filling material 56 that are disposed against the shell inner wall can constitute a cylindrical unitary structure that is slid into position and removed as a unit.
  • the invention is applicable to a multiple tube in shell heat exchanger in which a plurality of parallel tubes 22 are disposed within a single outer shell 54.
  • the outer spheres 28 may be arranged in rows, circles or helixes thereof with some of the spheres contacting two adjacent tubes, so that it disrupts the boundary layers of both tubes.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Dispersion Chemistry (AREA)
  • Chemical & Material Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Central Heating Systems (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)
  • Feeding, Discharge, Calcimining, Fusing, And Gas-Generation Devices (AREA)

Claims (5)

1. Wärmeaustauschvorrichtung zum Austauschen von Wärme zwischen zwei Fluden, bei der ein äußeres Gehäuse (54) eine Innenwand, einen Einlaß (14) ins Innere davon und einen Auslaß (16) daraus zum Durchtritt des ersten Fluidums durch den Gehäuse-Innenraum aufweist,
bei der in dem äußeren Gehäuse (54) mindestens ein Rohr (22) angeordnet ist, das eine Innenfläche und eine Außenfläche sowie einen Einlaß (48) zum Inneren und einen Auslaß (50) zum Durchtritt von Fluidum durch das Rohrinnere aufweist und bei dem jede Rohrwand eine Wärmeaustauschwand zwischen den zwei Fluden im Gehäuseinneren und im Rohrinneren darstellt,
wobei der Fluidum-Strom im Rohrinneren die Form einer nicht-turbulenten Grenzschicht (30) unmittelbar an der Rohr-Innenfläche und einer an die Grenzschicht angrenzenden Kernschicht (32) einnimmt,
bei der ein in jedem Rohr vorgesehenes rohrseitiges Strömungsunterbrecher-Gebilde eine Vielzahl von langgestreckten Reihen von kugeligen Gliedern (28), welche die innere Wand des Durchtrittes berühren, aufweist und in nicht-turbulenter Weise die volle Entwicklung wenigstens der Grenzschicht an der Innenfläche·des Rohres an einer Vielzahl von Abstand voneinander aufweisenden Unterbrechungsstelle unterbricht, wobei Teile der unterbrochenen Grenzschicht sich zwischen den Unterbrechungsstellen auf nicht-turbulente Weise von der Rohr-Innenfläche trennen und sich mit der Kernschicht mischen, um eine Wärmeübertragung zwischen der Rohr-Innenfläche, der entsprechenden Grenzschicht und der Kernschicht zu bewirken, une bei der der Raum zwischen den langgestreckten Reihen mit einem raumfullenden Material gefüllt ist, um in dem von der Rohr-Innenfläche ferngelegenen Teil des Rohrinneren nutzlosen Fluidumfluß zu verhindern,
dadurch gekennzeichnet, daß die kugeligen Glieder (28) und das raumfüllende Material (58) einen einheitlichen Körper bilden, wobei die kugeligen Glieder von dem Körper unter Berührung der inneren Wand des Rohres (22) vorragen.
2. Wärmeaustauschvorrichtung nach Anspruch 1, wobei der erste Fluidum-Strom in dem Gehäuse-Raum die Form einer nicht-turbulenten Grenzschicht unmittelbar an der Rohr-Außenfläche und einer an die Grenzschicht angrenzenden Kernschicht einnimmt, dadurch gekennzeichnet, daß ein gehäuseseitiges Strömungsunterbrecher-Gebilde in dem Gehäuse-Raum eine Vielzahl von kugeligen Gliedern (28) aufweist, welche die äußere Rohrwand umgeben und berühren, und in nicht-turbulenter Weise die volle Entwicklung wenigstens der Grenzschicht an der Außenfläche des Rohres an einer Vielzahl von Abstand voneinander aufweisenden Unterbrechungsstellen unterbricht, wobei Teile der unterbrochenen Grenzschicht sich zwischen den Unterbrechungsstellen auf nicht-turbulente Weise von der Rohrau- ßenfläche trennen und sich mit der Kernschicht mischen, um eine Wärmeübertragung zwischen der Rohr-Außenfläche, der entsprechenden Grenzschicht und der Kernschicht zu bewirken,
und daß der Raum zwischen den kugeligen Gliedern des gehäuseseitigen Strömungsunterbrecher-Gebildes und der Rohr-Trennwand mit einem raumfüllenden Material (56) gefüllt ist, um in einem von der Rohr-Außenfläche ferngelegenden Teil des Rohrinnenraumes nutzlosen Fluidumfluß zu verhindern.
3. Wärmeaustauscher nach Anspruch 2, dadurch gekennzeichnet, daß im Inneren des Gehäuses eine Vielzahl von zueinander parallelen Rohren angeordnet ist und einige der Kugeln des gehäuseseitigen Unterbrecher-Gebildes die Außenfläche von mehr als einem Rohr berühren.
4. Wärmeaustauschvorrichtung nach Anspruch 1, 2 oder 3, dadurch gekennzeichnet, daß der Abstand von einander unmittelbar folgenden Unterbrechungsstellen in Strömungsrichtung derart ist, daß eine Sog-Interferenz-Strömung zwischen den einander folgenden Unterbrechungsstellen gebildet ist.
5. Wärmeaustauscher nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die kugeligen Glieder in Form einer Wendel angeordnet sind.
EP84903691A 1983-10-05 1984-09-19 Wärmetauscher mit mantel und rohrbündel und verfahren dafür Expired EP0160662B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84903691T ATE34220T1 (de) 1983-10-05 1984-09-19 Waermetauscher mit mantel und rohrbuendel und verfahren dafuer.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US53919883A 1983-10-05 1983-10-05
US539198 1990-05-11

Publications (3)

Publication Number Publication Date
EP0160662A1 EP0160662A1 (de) 1985-11-13
EP0160662A4 EP0160662A4 (de) 1986-02-20
EP0160662B1 true EP0160662B1 (de) 1988-05-11

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ID=24150219

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84903691A Expired EP0160662B1 (de) 1983-10-05 1984-09-19 Wärmetauscher mit mantel und rohrbündel und verfahren dafür

Country Status (12)

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EP (1) EP0160662B1 (de)
JP (1) JPS61500132A (de)
KR (1) KR910003073B1 (de)
AU (1) AU585839B2 (de)
BR (1) BR8407108A (de)
DE (1) DE3471157D1 (de)
DK (1) DK247585A (de)
IT (1) IT1176887B (de)
MX (1) MX161055A (de)
NO (1) NO852255L (de)
WO (1) WO1985001571A1 (de)
ZA (1) ZA847652B (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110300050A1 (en) * 2010-06-08 2011-12-08 Memc Electronic Materials, Inc. Trichlorosilane Vaporization System

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1015261A (en) * 1910-12-03 1912-01-16 William Arthur Bone Steam generation-feed-water heating, and heating of liquids generally.
FR535531A (fr) * 1920-07-07 1922-04-15 Bristol Aeroplane Co Ltd Perfectionnements aux chaudières à tubes d'eau, réchauffeurs d'eau et générateurs de vapeur
GB531112A (en) * 1939-07-12 1940-12-30 Walter Engel Improvement in or relating to the manufacture of heat exchange units
FR1189249A (fr) * 1957-11-14 1959-10-01 Réacteur nucléaire à liquide bouillant
US3170512A (en) * 1963-03-29 1965-02-23 Carrier Corp Heat exchanger
US3704748A (en) * 1970-02-11 1972-12-05 Ratheon Co Heat transfer structure
US3921712A (en) * 1970-03-02 1975-11-25 American Standard Inc Heat exchanger structure for a compact boiler and the like
US3921711A (en) * 1972-05-30 1975-11-25 American Standard Inc Turbulator
US4051891A (en) * 1975-10-01 1977-10-04 Halm Instrument Co., Inc. Heat transfer block means
EP0042613A3 (de) * 1980-06-24 1982-08-11 Richard Adolf Holl Vorrichtung und Verfahren zur Wärmeübertragung

Also Published As

Publication number Publication date
EP0160662A4 (de) 1986-02-20
DK247585D0 (da) 1985-06-03
DE3471157D1 (en) 1988-06-16
BR8407108A (pt) 1985-08-27
KR850700066A (ko) 1985-10-21
EP0160662A1 (de) 1985-11-13
JPS61500132A (ja) 1986-01-23
MX161055A (es) 1990-07-18
IT8423041A0 (it) 1984-10-05
DK247585A (da) 1985-06-03
IT1176887B (it) 1987-08-18
IT8423041A1 (it) 1986-04-05
AU585839B2 (en) 1989-06-29
AU3436384A (en) 1985-04-23
KR910003073B1 (ko) 1991-05-17
ZA847652B (en) 1985-05-29
NO852255L (no) 1985-06-04
WO1985001571A1 (en) 1985-04-11

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