US3850235A - Heat exchanger - Google Patents

Heat exchanger Download PDF

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Publication number
US3850235A
US3850235A US00277285A US27728572A US3850235A US 3850235 A US3850235 A US 3850235A US 00277285 A US00277285 A US 00277285A US 27728572 A US27728572 A US 27728572A US 3850235 A US3850235 A US 3850235A
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United States
Prior art keywords
walls
tubular
tubular walls
combination
wall
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 - Lifetime
Application number
US00277285A
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English (en)
Inventor
G Beckmann
K Fritz
J Lippitsch
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.)
Waagner Biro AG
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Waagner Biro AG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Waagner Biro AG filed Critical Waagner Biro AG
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Publication of US3850235A publication Critical patent/US3850235A/en
Anticipated expiration legal-status Critical
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/10—Water tubes; Accessories therefor
    • F22B37/14—Supply mains, e.g. rising mains, down-comers, in connection with water tubes
    • F22B37/143—Panel shaped heating surfaces built up from tubes
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/355—Heat exchange having separate flow passage for two distinct fluids
    • Y10S165/40—Shell enclosed conduit assembly
    • Y10S165/401—Shell enclosed conduit assembly including tube support or shell-side flow director
    • Y10S165/416—Extending transverse of shell, e.g. fin, baffle
    • Y10S165/423—Bar

Definitions

  • a plurality of curved tubular walls are equidistantly arranged with respect to each other around a central axis with each of these walls having an inner concave side directed toward the axis and an outer convex side directed away from the axis and with each of the walls including an elongated tube having a hollow interior through which a heatexchanging medium is adapted to flow.
  • Each of the walls further includes a fin structure fixed to the tube thereof at least partially along the tube for forming a vibration-resistant, unitary tubular wall structure.
  • the heat exchanger is manufactured by curving a plurality of finned tubes and welding the tubes to each other to form a tubular wall.
  • the present invention relates to heat exchangers which are adapted to be used as steam generators for nuclear power plants.
  • the present invention relates particularly to that type of heat exchanger where a heat-exchanging medium flows through a plurality of tubes along similar flow paths.
  • Yet another object of the present invention is to provide a heat exchanger which enable the spacing between the tubes to be maintained in a predetermined manner which will assure proper flow for the heat exchanging medium which is at the exterior of the tubes, even though the latter are located extremely close to each other.
  • a heat exchanger which is particularly adapted to be used as a steam generator for a nuclear power plant, is provided with a plurality of curved tubular walls which are equidistantly arranged with respect to each other around a central axis with each of these walls having an inner concave side directed toward this axis and an outer convex side directed away from this axis.
  • Each of the walls include an elongated tube having a hollow interior through which a heat-exchanging medium is adapted to flow, and each of these walls further includes a fin means fixed to the tube thereof at least partially along the tube for forming a vibration-resistant, unitary wall structure.
  • the tubes which can have fins adjoined thereto or which may be initially manufactured with fins are curved to a predetermined curvature and then are welded together so as to fonn according to this method of the invention the tubular walls of the invention.
  • FIG. 1 is a schematic plan view of one embodiment of a heat exchanger according to the invention.
  • FIG. 2 is a schematic plan view of another embodiment of a heat exchanger according to the invention.
  • FIG. 3 is a schematic fragmentary partly sectional elevation taken along line II of FIG. 1 or II-II of FIG. 2 and illustrating one possible embodiment of a structure for supporting the tubular walls;
  • FIG. 4 is a fragmentary partly sectional schematic elevation taken along line II of FIG. 1 and IIII of FIG. 2 and illustrating another possible embodiment of a structure for supporting the tubular walls of the invention.
  • FIGS. 5-8 respectively illustrate in schematic fragmentary sectional views different embodiments of spacer means according to the invention.
  • FIG. 1 there is illustrated therein, in a schematic plan view, a heat exchanger in which a plurality of cylindrical tubular walls are concentrically arranged with respect to each other around a common axis which is normal to the plane of FIG. 1, with the several cylindrical tubular walls 4 being arranged as illustrated in dot-dash lines in FIG. 1.
  • These tubular cylindrical concentric walls 4 are surrounded by an outer tubular cylindrical wall 3, while they extend around an inner cylindrical tubular wall 5.
  • the heat-exchanging medium which flows around the tubular walls at the exterior thereof flows in a direction perpendicular to the plane of FIG. 1 so as to flow in a direction which is parallel to the central axis of the heat exchanger.
  • the plurality of concentric cylindrical tubular walls 3-5 are situated within a pressure vessel 12.
  • a supporting frame means is formed by a plurality of bars 8 which are fixed, as by welding, to the inner surface of the pressure vessel 12 and which extend radially with respect to the central axis, being uniformly distributed about the central axis in a manner shown in FIG. 1.
  • the several bars 8 of the supporting frame means are fixed, as by welding, at their inner ends to a cylindrical fluiddisplacement pipe 13 situated at the center of the pressure vessel 12 and thus being carried by the bars 8.
  • the inner fluid-displacing body 13 and the outer pressure vessel 12, which are coaxial and have a common axis coinciding with the central axis of the heat exchanger define between themselves the space within which the tubular walls 3-5 are concentrically arranged.
  • the heat exchanger has tubular walls 1 and 2 which in a plane perpendicular to the central axis of the heat exchanger have the configuration of an involute curve.
  • the tubular walls 1 and 2 which have the involute curvature have tubes all situated in planes normal to the central axis of the heat exchanger while the connecting tubes 14, which are approximately of a semicircular configuration, extend from the end of one tube of involute wall 1 or 2 down to the opposed involute wall tube which is located in the next lower horizontal plane.
  • the tubes of FIG. 2 have a constant pitch so that they progress in a helical manner vertically in an axial direction.
  • the tubular walls are curved so as to have inner concave sides directed toward the central axis of the heat exchanger and outer convex sides directed away from the central axis of the heat exchanger.
  • the several tubular walls are all equidistantly arranged with respect to each other, in a radial direction with respect to the central axis.
  • the several concentric cylindrical tubular walls 3-5 are all situated equidistantly from each other, and the same is true of the involute tubular walls 1 and 2 of FIG. 2.
  • FIGS. 3 and 4 schematically illustrate in fragmentary sectional elevations different embodiments, respectively, of arrangements according to which the supporting frame means 8 supports the several tubular walls. It is to be understood that both the construction of FIG. 3 and that of FIG. 4 is applicable both to FIG. 1 and to FIG. 2.
  • the several tubular walls are suspended in such a way that they hang from the supporting frame means.
  • the several tubular walls 1-5 are welded at their top ends to the several bars 8 of the supporting frame means so as to hang downwardly from the latter.
  • a spacer means 11 is provided for further determining the distance between the several tubular walls.
  • the use of the several spacer elements 11 in the manner illustrated in FIG. 3 further serves to damp vibrations in the tubular walls. As is particularly apparent from the left end of the bar 8 shown in FIG.
  • the several bars 8 are fixed in cantilever fashion at their outer ends-to the inner surface of the outer vessel 12 by way of suitable supporting brackets 15 which are fixed on the one hand to the vessel 12 at the inner surface thereof and which on the other hand are fixed with the several bars 8, respectively, at their outer ends.
  • the several bars 8 of the supporting frame means in turn carry at their inner ends the displacement pipe 13 which is coaxial with the several tubular walls l-S. Through the pipe 13 are guided the several connecting tubes which respectively communicate with the different heating units of the heat exchanger. Furthermore, in order to avoid a short circuit in the flow paths, the pipe 13 is tightly closed at a given location so that the fluid medium in which the pipe 13 is located stagnates in the pipe 13.
  • the several tubular walls 1-5 rest on the supporting frame means formed by the bars 8, with these tubular walls being fixed at their bottom ends, as by welding, to the several bars 8 so that in this case the several tubular walls extend upwardly from the supporting frame means.
  • the several bars 8 in this embodiment are carried by the pressure vessel 12 and are connected with the pipe 13 in the manner described above in connection with FIG. 3.
  • the supporting frame means takes the form of a carrier grid having its several bars extending radially from the pipe 13 out to the vessel 12.
  • the several tubular walls l-S are spaced from each other by way of a spacer means composed of spacer components 16 which have a mushroom-shaped configuration.
  • These spacer elements 16 are arranged in such a way that there are fixed at their smaller ends to the fin means 7 which is in turn fixed to the several tubes of the several walls, extending between these tubes, and the enlarged head ends of the several mushroom-shaped spacer elements 16 are directed toward each other in pairs, as illustrated in FIG. 4, so that these enlarged head ends of each pair of opposed spacer elements 16 will be able to engage each other, if necessary, while their smaller foot ends are respectively welded to the several fin means 7 which extend between the several tubes of the several tubular walls.
  • FIG. 5 illustrates one embodiment of a spacer means used with the tubular walls of the heat exchanger of the invention.
  • each of the tubular walls is composed of an elongated tube 6 which has a fin means 7 fixed thereto as by being welded to the tube 6 along the length thereof.
  • Each pair of fins located between a pair of successive tube convolutions 6 of each wall are also welded to each other so as to form in this way the vibration-resistant unitary tubular wall structure of each of the tubular walls of the heat exchanger of the invention.
  • every other tubular wall has the fin means 7 which extends between every other pair of convolutions formed with a bore passing therethrough.
  • the left and right tubular walls have fins formed with openings passing therethrough in order to accommodate the elongated spacer components 9, while the intermediate tubular wall of FIG. 5 does not have any bores or openings passing through the fins thereof.
  • the alternating tubular walls or in other words every second tubular wall, will have at the fin means thereof openings for accommodating the spacer means 9.
  • the fin means situated between alternating pairs of successive convolutions of the tube 6 are formed with openings to accommodate the spacer means 9.
  • the spacer means 9 takes the form of a plurality of radially extending elongated pins or rods 9 which respectively extend through the openings which are formed in the fin means 7 and which are welded to the fin means 7 in such a way that successive coaxial spacer pins 9 which extend along a common radius of the heat exchanger have ends directed toward each other and situated close to a fin means between a pair of tubular convolutions of a tubular wall means between the alternating pair which carry the spacer means 9, and in the same way this same pair of pins 9 project at their outer ends into the space between a pair of tubular convolutions of the next inner and next outer tubular walls which are not illustrated in FIG. 5.
  • each of the elongated spacer components 9 of this embodiment has a length corresponding to twice the distance between successive tubular walls.
  • the alternating tubular walls of the arrangement shown in FIG. 5 are to be considered as having a maximum thickness equal to double the distance between the successive tubular walls so that it is necessary to introduce into or remove from the assembly, as required, a tubular wall structure having this maximum thickness.
  • FIG. 5 shows the details of the structure of the individual tubular walls.
  • each individual tubular wall is made up of a number of tubular portions 6. Initially the tubular portions 6 are straight and a pair of elongated fins 7 are welded axially toeach of the tubular portions 6 at diametrically opposed sides thereof.
  • each wall has a continuous tube extending spirally around the axis of the tubular wall.
  • involute tubular walls of FIG. 2 it is possible to simplify the construction by first forming a flat tubular wall with all of the fins joined to each other and then curving this flat wall into the shape of an involute.
  • tubes to which the fins are welded it is possible to utilize finned tubes which are integrally formed with fins when they are initially manufactured, and then such finned tubes are correspondingly curved and welded as described above.
  • the advantage of joining the fins to the tubes by welding the fins thereto is that with such construction it is not essential to provide fins which extend completely along the entire length of the tubes.
  • the fins may be distributed along the tubes with spaces being situated between successive fins, so that in the completed tubular wall there are passages or openings extending through the tubular wall enabling the heat-exchanging medium at the exterior of the tubular walls to flow through these openings in order to mix portions of this outer heat-exchanging me dium located at different passages defined between successive tubular walls.
  • the spacer means has a construction according to which shorter pins or studs 9 are respectively welded at one of their ends to fins in the manner shown in FIG. 6, with these spacer components 9 also extending radially with respect to the central axis of the heat exchanger.
  • spacer pins 9 are welded in the manner shown in FIG. 6.
  • the length of the several spacer pins corresponds to the clearance between I fins of successive tubular walls so that these spacer pins serve to determine the distance between the pairs of successive tubular walls.
  • the spacer pins 9 are fixed either at their outer ends to the fins and project from their outer ends inwardly toward the central axis of the heat exchanger or they are fixed at their inner ends to the several fins and project outwardly away from the central axis of the heat exchanger.
  • the successive tubular walls are threaded into the space surrounded by the previously assembled tubular wall.
  • the tubular walls of FIGS. 5 and 6 form the cylindrical walls as shown in FIG. 1, then it is clear that at each tubular wall the space between the spiral tubular convolutions thereof also forms a spiral similar to a screw thread extending around the axis of the tubular wall. Therefore, if it is assumed that the left tubular wall of FIG. 5, for example, has first been assembled into the heat exchanger, then the intermediate tubular wall of FIG. 5 can be threaded with respect to the left spacer components 9 until this intermediate wall is surrounded by the left wall of FIG.
  • each tubular wall can be threaded into its concentric relationship with respect to the immediately preceding tubular wall which has just been introduced into the heat exchanger. In this way it becomes possible to fix the spacer pins 9 to the tubular walls prior to assembly thereof into the heat exchanger with simple threading of the successive tubular walls into the heat exchanger taking place in the above-described manner.
  • the spacer means takes the form of a plurality of bolts 10 which serve to determine the distance between successive pairs of tubular walls.
  • FIG. 8 The arrangement which is illustrated in FIG. 8 is similar to FIG. 7. The difference is that in this embodiment instead of using headed screws 10 threaded studs are used. These threaded studs 10 of FIG. 8 are assembled with the remaining structure in the manner described above in connection with FIG. 7. Thus, after the threaded end portion of a stud 10 is threaded into a threaded opening formed in a fin 7 of one tubular wall, the opposite end of the stud 10 which extends through the opening of the adjoining tubular wall is welded directly to the fin structure of the latter wall so that in this way the studs 10 of FIG. 8 serve the same purpose as the bolts 10 of FIG. 7.
  • the several tubular walls are each composed of tubular portions extending either along elements of a cylinder or along elements of a wall having an involute curvature, and these several tubular portions are welded to each other to form the unitary tubular wall structure.
  • the several spacer pins of FIGS. 5 and 6 may be fixed to the tubular walls prior to curving thereof.
  • the several finned tubes are welded to each other at the free edges of their fins in order to form a flat tubular panel. While such a panel is still in its flat condition it is possible to fix the spacer pins 9 thereto in a manner described above and shown in FIGS. 5 and 6, and then after these spacer pins are fixed to the flat panels it is possible to curve the latter so as to form either part of a cylinder or so as to have the involute curvature of FIG. 2. It is also possible to fix the pins 9 to the fins of the tubes prior to curving of the individual finned tubes with the pins then being joined to the fin of an adjoining tubular portion when the several tubular portions are assembled. It will be noted that in allof the abovedescribed embodiments the tubular walls extend axially of the heat exchanger and have the distance therebetween determined by the spacers which extend transversely with respect to the tubular walls.
  • a plurality of curved tubular walls equidistantly arranged with respect to each other around a central axis with each of said walls having an inner concave side directed toward said axis and an outer convex side directed away from said axis, each of said walls including an elongated tube having a hollow interior through which a heatexchanging medium is adapted to flow and each of said walls further including a fin means fixed to said tube thereof at least partially along said tube for forming a vibration-resistant, unitary tubular wall structure, each of said tubular walls including a plurality of tubular portions which are axially spaced from each other and which are welded one to the next by way of said fin means.
  • each of said tubular walls extends along an involute curve in a plane normal to said central axis.
  • tubular walls respectively have the configuration of cylinders and are concentrically arranged with respect to said axis with the tube of each of said tubular walls extending spirally around said axis.
  • said spacer means includes a plurality of screws radially arranged with respect to said central axis and fixed to adjoining tubular walls for spacing the latter from each other as well as fixing them to each other.
  • each screwv is fixed to a pair of said walls with one of said pair of walls forming an inner wall while the other of said pair of walls forms an outer wall situated at a greater distance from said central axis than said inner wall, each screw being threaded to the fin means of said inner wall and being welded to the fin means of said outer wall.
  • said spacer means includes a plurality of elongated radially extending spacer elements welded to said fin means of said walls and determining the radial distance therebetween.
  • each of said tubular walls has a pair of opposed ends and frame means welded to said walls at one of the ends thereof for fixing the walls to each other and determining the radial spacing therebetween, and spacer means carried by said walls for determining the distance therebetween at locations beyond said frame means.
  • an inner pipe has an axis coinciding with said central axis and an outer cylinder coaxially surrounds said inner pipe and defines therewith a space in which said tubular walls are located, and a plurality of supporting bars extending radially between and being fixed to said inner pipe and outer cylinder, said bars forming a supporting frame means and said plurality of tubular walls being fixed at one of the ends thereof to said supporting frame means.

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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)
US00277285A 1971-08-03 1972-08-02 Heat exchanger Expired - Lifetime US3850235A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT674871A AT313934B (de) 1971-08-03 1971-08-03 Wärmetauscher und Verfahren zu seiner Herstellung

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US3850235A true US3850235A (en) 1974-11-26

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US00277285A Expired - Lifetime US3850235A (en) 1971-08-03 1972-08-02 Heat exchanger

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US (1) US3850235A (de)
AT (1) AT313934B (de)
CH (1) CH550984A (de)
DE (1) DE2237430A1 (de)
GB (1) GB1390057A (de)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4553588A (en) * 1983-01-11 1985-11-19 Phillips Petroleum Company Tube support
US4727933A (en) * 1985-10-30 1988-03-01 Deutsche Babcock Werke Aktiengesellschaft Device for cooling hot, dust-laden gases
US6736191B1 (en) * 2001-10-09 2004-05-18 Power Engineering Contractors, Inc. Heat exchanger having longitudinal structure and mounting for placement in seawater under piers for heating and cooling of buildings
CN105697774A (zh) * 2016-03-09 2016-06-22 无锡锡洲封头制造有限公司 引水降温型封头

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH632583A5 (de) * 1978-07-12 1982-10-15 Sulzer Ag Rohrbuendel zur waermeuebertragung durch beruehrung.
US4270599A (en) * 1978-09-29 1981-06-02 Foster Wheeler Energy Corporation Tube support structure for a fluidized bed heat exchanger
DE102009031969A1 (de) * 2009-07-06 2011-01-13 Babcock Borsig Service Gmbh Rohrregister für den indirekten Wärmeaustausch
DE102012008183B4 (de) * 2011-09-06 2013-07-18 Joachim Benz Wärmetauscherbausatz
DE102014015508B4 (de) 2014-10-21 2018-09-27 Joachim Benz Wärmetauscherbausatz
CN117537330B (zh) * 2023-10-21 2024-05-28 山东北辰机电设备股份有限公司 一种全浸没式电极蒸汽锅炉

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2069515A (en) * 1935-07-05 1937-02-02 Superheater Co Ltd Economizer
GB581742A (en) * 1943-04-27 1946-10-23 Bristol Aeroplane Co Ltd Improvements in or relating to heat-exchangers
US3126949A (en) * 1964-03-31 Heat exchanger construction
US3286767A (en) * 1964-10-01 1966-11-22 Babcock & Wilcox Co Tube support arrangement
US3393665A (en) * 1966-12-14 1968-07-23 Combustion Eng Support tie for tubular walls of a furnace and adjacent tube bank
US3503440A (en) * 1968-12-23 1970-03-31 Combustion Eng Formed plate tube support

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3126949A (en) * 1964-03-31 Heat exchanger construction
US2069515A (en) * 1935-07-05 1937-02-02 Superheater Co Ltd Economizer
GB581742A (en) * 1943-04-27 1946-10-23 Bristol Aeroplane Co Ltd Improvements in or relating to heat-exchangers
US3286767A (en) * 1964-10-01 1966-11-22 Babcock & Wilcox Co Tube support arrangement
US3393665A (en) * 1966-12-14 1968-07-23 Combustion Eng Support tie for tubular walls of a furnace and adjacent tube bank
US3503440A (en) * 1968-12-23 1970-03-31 Combustion Eng Formed plate tube support

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4553588A (en) * 1983-01-11 1985-11-19 Phillips Petroleum Company Tube support
US4727933A (en) * 1985-10-30 1988-03-01 Deutsche Babcock Werke Aktiengesellschaft Device for cooling hot, dust-laden gases
US6736191B1 (en) * 2001-10-09 2004-05-18 Power Engineering Contractors, Inc. Heat exchanger having longitudinal structure and mounting for placement in seawater under piers for heating and cooling of buildings
CN105697774A (zh) * 2016-03-09 2016-06-22 无锡锡洲封头制造有限公司 引水降温型封头

Also Published As

Publication number Publication date
DE2237430A1 (de) 1973-02-15
AT313934B (de) 1974-03-11
CH550984A (de) 1974-06-28
GB1390057A (en) 1975-04-09

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