US3771589A - Method and apparatus for improved transfer of heat - Google Patents

Method and apparatus for improved transfer of heat Download PDF

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Publication number
US3771589A
US3771589A US00194282A US3771589DA US3771589A US 3771589 A US3771589 A US 3771589A US 00194282 A US00194282 A US 00194282A US 3771589D A US3771589D A US 3771589DA US 3771589 A US3771589 A US 3771589A
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Prior art keywords
medium
heat exchange
flow
set forth
zone
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US00194282A
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English (en)
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J Lage
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/12—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by creating turbulence, e.g. by stirring, by increasing the force of circulation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • 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

Definitions

  • ABSTRACT Disclosed are a method for improving the heat transfer characteristics of a heat exchanger and a heat exchanger structure capable of operating in accordance with the method.
  • the disclosed method comprises causing a heat exchange medium to flow alternately through two different types of zones. In the first zone the flow patterns developed in the fluid are generally translatory while in the second zone the patterns are generally rotational.
  • the heat exchange fluid is caused to flow at least partly across the heat exchange surface while in the second zone.
  • the zones are presented as compartments divided by a wall, one of the compartments being at least partially bounded by the heat exchange surface.
  • the medium flows in a translatory manner through one compartment and through a conducting device which interconnects the compartments. A rotational movement is imparted on the fluid flowing into the'other compartment.
  • the present invention relates to a method for improving the heat transfer characteristics of an indirect heat exchanger and an exhanger constructed to carry out the process.
  • the heat transfer medium is usually directed to flow in a generally unconstrained manner across the heat transfer surface, whereby the medium follows a substantially uncontrolled, nearly random flow path across the surface. In such instances the path of least resistance is taken by the fluid and in most instances this is also the shortest path. Accordingly, most of the individual particles of the medium traverse the heat transfer surface only once. Moreover, it is extremely rare under such circumstances for any individual particle of heat transfer medium to contact the entirety of a heat exchange surface. As a result, low heat transfer coefficients are developed.
  • the primary object of the present invention is to provide a heat transfer method and apparatus which facilitate the longest possible contact between the particles of the heat transfer medium and the heat transfer surface whereby a high heat transfer coefficient results. This result is obtained by causing the particles of the medium to flow across the heat transfer surface in an aligned, forced flow path.
  • the desired results are achieved, according to the invention, by developing alternating flow patterns in the medium which is guided essentially translatorily in a first zone and rotatingly in a second zone.
  • the medium is conducted at least partially along the heat exchange surface in the second zone.
  • the medium in the second zone is caused to traverse a spiral path.
  • a further advantageous feature of the invention consists in causing only a part of the medium to traverse the entire helical path while remaining parts of the medium are fed in at downstream locations to traverse only the remainder of the path.
  • a heat exchanger adapted to carry out the process has a housing defining a chamber which is subdivided into first and second flow compartments.
  • the second compartment is bounded at least partially by the heat exchange surface.
  • the exchanger is provided with an inlet communicating with the first chamber and an outlet communicating with the second chamber.
  • Medium under pressure is supplied to the first flow chamber, and a conducting device which intercommunieates the compartments and directs fluid flowing therethrough into the second flow compartment in at least one essentially translatory jet.
  • the conducting device is also disposed and arranged to cause the medium to flow rotatingly through said second compartment.
  • translatory flow designates a flow in which the medium traverses substantially the shortest path and flows generally in a single direction, for example, as through a space, pipe or nozzle.
  • the medium does not flow over the direct and shortest path, but rather, it is subjected to a rotating flow.
  • rotating flow designates a flow which circulates around an axis, such as for example, a pulsating flow, a rotating or a twisting flow, a rolling movement of the medium, as well as combinations of these. If at the same time an additional secondary forward movement, preferably in the axial direction is imparted to the medium, then the particles of the medium will follow a generally helical path. In this manner the medium may form a roller progressing through the flow chamber in an axial direction.
  • the cross section of the roller does not need to be circular, for example in the case where the flow chamber is rectangular, and its diameter can change along the axis.
  • a considerably greater heat transfer coefficient can be achieved in the case of a purely rotating flow than in the case of translatory flow, resulting from improved intermixture of the medium.
  • a still further increase in the magnitude of heat transfer coefficient can be achieved through the establishment of a helical flow path. With helical flow paths, multiple sweeps of the medium across the heat exchange surface provide a better utilization of the available heat transfer surface.
  • the method and apparatus of the present invention may be utilized with all fluid mediums, whether gases or liquids, or condensing or evaporating fluids.
  • FIG. 1 is a schematic view diagrammatically illustrating the basic concepts and principles of the invention
  • FIG. 2 is an elevational, cross sectional view of an exchanger which embodies the principles and concepts of the invention and has several chambers arranged in series;
  • FIG. 3 is an enlarged, cross sectional view taken substantially along line IIIIII of FIG. 2;
  • FIG. 4 is a cross sectional view taken substantially along line IVIV of FIG. 3;
  • FIG. 5 is a cross sectional view similar to FIG. 3 illustrating another embodiment of this invention.
  • FIG. 6 is a cross sectional view taken substantially along line VIVI of FIG. 5.
  • FIG. 1 DESCRIPTION OF THE PREFERRED EMBODIMENTS
  • translatory flows are designated by the reference numeral 1 and rotating flows are designated by the numeral 2.
  • the flowing medium is first conducted translatorily in a first zone and as a result, its
  • the medium is directed, preferably with an increased speed and after the necessary deflections, into a second zone and into contact with a heat exchange surface 4, at any desired angle or even parallel to surface 4, whereby the flow 2 is deflected and put into rotation.
  • a heat exchange surface 4 Preferably, an axial flow direction will also be imparted upon the rotating flow, and as a result, the path of flow 2 becomes helical.
  • the medium may be conducted continuously or with interruptions along heat exchange surface 4.
  • medium can be fed into the second zone at various locations along the helical path and as a result, friction losses and the resultant lowering of speed are decreased.
  • the exchanger illustrated in FIG. 2 consists of four individual chambers 3 which have been combined into one unit although each would be fully operable by itself. Pressurized medium enters the righthand side of the installation and flows through in the direction of the arrow. Each chamber 3 is divided into a first flow compartment 9 and a second flow compartment by separating means in the nature of a wall 5 which has a lower edge portion 12 adjoining heat exchange surface 4. Wall 5 extends angularly upwardly relative to the general direction of the flow in the exchanger. The medium entering the first flow chamber 9 is guided upwardly and laterally along separating wall 5 to a gap 7 (FIGS. 3 and 4) defined by a side wall 8 of chamber 3 and a wall 6 which extends downwardly from separating wall 5. Wall 6, which may be integral with wall 5, extends toward surface 4 and terminates in spaced relationship thereto presenting an opening 11 through which the medium flows in a jet into the second flow compartment.
  • the medium is introduced into the second flow compartment in the direction of heat exchange surface 4 and it is deflected by said surface and put in rotation.
  • the medium is caused to flow in a helical path 2 (FIG. 4) which moves according to FIG. 2 from right to left.
  • the rotating paths 2 continuously increase in di ameter along the axial direction.
  • gap 7 extends along the entire length of chamber 3, fresh medium and thus new energy is continuously introduced in the second flow compartment at various locations along the helical path.
  • Separating wall 5 could be disposed parallel to heat exchange surface 4, which, from a constructional point of view, would be simpler; however, with regard to proper flow characteristics and to an efficient utilization of heat exchange surface, this would be less favorable than the configuration shown.
  • FIGS. 5 and 6 illustrate another embodiment of the exchanger.
  • gap 7 is disposed in the center of chamber 3, and the medium flows in from both sides along the paths 1.
  • two rotating paths 2 will develop (FIG. 6) at the sides of gap 7 in a second flow compartment 10'divided in such a way.
  • the advantage of this embodiment is of a constructional nature, consisting primarily in the fact that a more compact and symmetrical type of construction will be possible.
  • gap similar to gap 7 could be provided at each side of the chamber and for that matter, several such gaps could be distributed over the width of the chamber. In such cases, the rotating flows would touch each other but they should still be able to develop inspite of this. Furthermore, the gaps could decrease in flow area as the second compartment is approached, for example, through a convergence of surfaces 6 or 8 or by providing a nozzle at opening 11, whereby the medium would be accelerated as it passes into compartment 10. The maximum speed should occur as the medium enters the second compartment 10.
  • wall 6 can be provided with a flange portion 13 (indicated in FIGS. 4 and 6 by a dashed line) which is disposed adjacent opening 11 and extends generally parallel to surface 4. As a result, the medium flows into the second flow compartment 10 in a direction parallel to heat exchange surface 4.
  • the development of a rotating flow also can be enhanced by the provision of a heat exchange surface having a curvature.
  • the chamber could be cylindrical.
  • the heat exchange surface could be curved to present a convex surface in the second compartment if this would prove to be advantageous or if the shape of the heat exchange surface is determined by other considerations.
  • the axis of the helical path could be curved if, for example, an elongated shape of the successive chambers must be avoided.
  • identical chambers could be disposed on opposite sides of the heat exchange surface.
  • gap 7, which is defined between walls 6 and 8 presents a conducting device which intercommunicates compartments 9 and 10.
  • the conducting device could comprise, especially if chamber 3 is not very high, several openings in separating wall 5.
  • the openings could be round, oval or any other shape. Further, the openings could be disposed in a continuous row or replaced by an elongated slit.
  • a pipe could be utilized to convey fluid from each opening. Preferably such pipe should be of the same shape as its opening and should extend toward the heat exchange surface. Each pipe may be bent at its free end in order to achieve a similar effect to that achieved with flange 13 of limiting wall 6.
  • Separating wall 6 can be parallel to heat exchange surface 4 or it can approach it in the flow direction and as a result of the latter, the diameter of the helical rotating path would decrease along the axis of the compartment.
  • Walls swept by medium but which are not integral parts of the heat exchange surface, such as, for example, the lateral walls 8 of chamber 3, may advantageously be connected to the heat exchange surface in a heat conductive manner. Ribs may be provided for the same purpose. Such ribs may be disposed to extend in the direction of the helical path of the medium and should be connected to the heat exchange surface and- /or the lateral walls of the chamber in a heat conducting manner.
  • a heat exchanger comprising:
  • a housing defining a chamber
  • said housing including a heat exchange surface which at least partially bounds said second compartment, said means comprising a separating wall having a lower edge portion adjoining said heat exchange surface and slanting upwardly toward the upper portion of said housing in the direction of flow of a medium through said chamber,
  • said inlet being disposed to direct a flow of the heat exchange medium through said first chamber in a generally translatory stream;

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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)
US00194282A 1970-11-10 1971-11-01 Method and apparatus for improved transfer of heat Expired - Lifetime US3771589A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH1670870A CH533289A (de) 1970-11-10 1970-11-10 Verfahren zur Verbesserung der Wärmeübertragung und Einrichtung zur Durchführung des Verfahrens

Publications (1)

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US3771589A true US3771589A (en) 1973-11-13

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US00194282A Expired - Lifetime US3771589A (en) 1970-11-10 1971-11-01 Method and apparatus for improved transfer of heat

Country Status (9)

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US (1) US3771589A (de)
AT (1) AT316606B (de)
AU (1) AU3557571A (de)
BE (1) BE775087A (de)
CH (1) CH533289A (de)
DE (1) DE2153719B2 (de)
FR (1) FR2113897A1 (de)
GB (1) GB1352204A (de)
NL (1) NL7114429A (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4474226A (en) * 1981-09-25 1984-10-02 Iowa State University Research Foundation, Inc. Method and means of exchanging heat between fluid bodies
US20040240984A1 (en) * 2001-07-05 2004-12-02 Kiknadze Gennady Iraklievich Method of conversion of continuous medium flow energy and device for conversion of continuous medium flow energy
US20100096111A1 (en) * 2008-10-20 2010-04-22 Kucherov Yan R Heat dissipation system with boundary layer disruption

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2526930A1 (fr) * 1982-05-14 1983-11-18 Bertin & Cie Echangeur recuperateur de chaleur a effet convecto-radiatif en materiau ceramique
EP0839309B1 (de) * 1995-07-19 2002-03-27 Vida, Nikolaus Verfahren und vorrichtung zur beeinflussung der grenzschicht in einem kontinuierlichen medium
DE19751405C2 (de) * 1996-11-15 2001-01-18 Martin Schade Vorrichtung zum Wärmeaustausch

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1184936A (en) * 1914-09-05 1916-05-30 George C Huber Flue-protector for steam-boilers.
DE1108372B (de) * 1956-11-01 1961-06-08 Josef Cermak Dr Ing Kuehlungseinrichtung fuer thermisch hochbeanspruchte Waende
US3034769A (en) * 1956-10-26 1962-05-15 Bertin & Cie Heat exchangers
US3109485A (en) * 1958-02-25 1963-11-05 Fortier Andre Heat exchanger
US3450199A (en) * 1967-07-10 1969-06-17 Continental Aviat & Eng Corp Heat exchanger

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1184936A (en) * 1914-09-05 1916-05-30 George C Huber Flue-protector for steam-boilers.
US3034769A (en) * 1956-10-26 1962-05-15 Bertin & Cie Heat exchangers
DE1108372B (de) * 1956-11-01 1961-06-08 Josef Cermak Dr Ing Kuehlungseinrichtung fuer thermisch hochbeanspruchte Waende
US3109485A (en) * 1958-02-25 1963-11-05 Fortier Andre Heat exchanger
US3450199A (en) * 1967-07-10 1969-06-17 Continental Aviat & Eng Corp Heat exchanger

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4474226A (en) * 1981-09-25 1984-10-02 Iowa State University Research Foundation, Inc. Method and means of exchanging heat between fluid bodies
US20040240984A1 (en) * 2001-07-05 2004-12-02 Kiknadze Gennady Iraklievich Method of conversion of continuous medium flow energy and device for conversion of continuous medium flow energy
US7331752B2 (en) * 2001-07-05 2008-02-19 Inventors Network Gmbh Method of conversion of continuous medium flow energy and device for conversion of continuous medium flow energy
US20100096111A1 (en) * 2008-10-20 2010-04-22 Kucherov Yan R Heat dissipation system with boundary layer disruption
US8997846B2 (en) * 2008-10-20 2015-04-07 The Government Of The United States Of America, As Represented By The Secretary Of The Navy Heat dissipation system with boundary layer disruption
US9080821B1 (en) 2008-10-20 2015-07-14 The United States Of America, As Represented By The Secretary Of The Navy Heat dissipation system with surface located cavities for boundary layer disruption

Also Published As

Publication number Publication date
FR2113897A1 (de) 1972-06-30
AT316606B (de) 1974-07-25
AU3557571A (en) 1973-05-17
GB1352204A (en) 1974-05-08
CH533289A (de) 1973-01-31
DE2153719A1 (de) 1972-05-18
DE2153719B2 (de) 1976-12-16
NL7114429A (de) 1972-05-15
BE775087A (fr) 1972-03-01

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