US3720259A - Tubular heat exchanger supporting and spacer structure - Google Patents

Tubular heat exchanger supporting and spacer structure Download PDF

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Publication number
US3720259A
US3720259A US00074356A US3720259DA US3720259A US 3720259 A US3720259 A US 3720259A US 00074356 A US00074356 A US 00074356A US 3720259D A US3720259D A US 3720259DA US 3720259 A US3720259 A US 3720259A
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United States
Prior art keywords
tubes
convolutions
support means
bodies
spacer
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Expired - Lifetime
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US00074356A
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English (en)
Inventor
K Fritz
J Lippitsch
G Lurf
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Waagner Biro AG
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Waagner Biro AG
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Classifications

    • 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
    • F28D7/04—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 spirally coiled
    • 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
    • F28D7/08—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 otherwise bent, e.g. in a serpentine or zig-zag
    • 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
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F28F9/0135—Auxiliary supports for elements for tubes or tube-assemblies formed by grids having only one tube per closed grid opening
    • 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
    • Y10S165/424—Bar forming grid structure

Definitions

  • ABSTRACT Heat exchangers having spirally wound tubes for accommodating in their interior an inner heat-exchanging fluid while being engaged at their exterior by an outer heat-exchanging fluid.
  • the spirally wound tubes are arranged one next to the other surrounding a given axis with the convolutions of one tube axially aligned with the convolutions of the next tube.
  • the tubes form a group having an inner region directed toward the latter axis and an outer region directed away from the latter axis.
  • a supporting structure At one of these regions there is a supporting structure while a spacer structure is fixed to the supporting structure and extends between the convolutions of the tubes to form with the latter a unitary assembly of tubes acting as a unitary structure in which the convolutions are maintained at given locations with respect to each other.
  • the spacer structure serves to transmit to the supporting structure the weight of the tubes and the spacer structure as well as any thermal or mechanical stresses or reaction forces resulting from flow of the fluids during operation of the heat exchanger.
  • the present invention relates to heat exchangers.
  • the present invention relates to heat exchangers composed of spirally wound tubes with spacers situated therebetween to provide between the tubes flow paths for an outer heat exchanging fluid which engages the exterior of the tubes the interior of which accommodates an inner heat-exchanging fluid.
  • the heat exchanger includes a plurality of spirally wound tubes for accommodating in their interior an inner heat-exchanging fluid while an outer heat-exchanging fluid is adapted to engage the exterior of tubes.
  • the spirally wound tubes are arranged one next to the other with the convolutions of one tube axially aligned with the convolutions of the next tube, and the several tubes form at least one group of tubes having an inner region surrounding a given axis, and directed toward this axis, while the group of tubes has an outer region directed away from this axis.
  • a support means is situated adjacent at least one of these regions of the tubes, and a spacer means extends between the convolutions of the tubes for maintaining the convolutions at a given spacing with respect to each other.
  • This spacer means forms a unitary structural assembly with the tubes and is operatively connected with the support means to transmit to the latter forces resulting from the weight of the tubes and the spacer means as well as any mechanical or thermal stresses or forces resulting from reactions to the flow of the fluids, so that in this way substantially all stresses encountered during operation are transmitted to the support means.
  • FIG. 1 is a schematic representation of a heat exchanger provided with the structure of the invention
  • FIG. 2 is a schematic plan view of the heat exchanger taken along line II of FIG. 1 in the direction of the arrows;
  • FIG. 3 is a fragmentary axial sectional elevation showing the details of one embodiment of a structure of the invention.
  • FIG. 4 shows the structure of FIG. 3 as viewed in the direction of arrow II of FIG. 3, illustrating the manner in which a spacer means and support means are interconnected;
  • FIG. 5 is a fragmentary sectional illustration taken along line III of FIG. 3 in the direction of the arrow and showing further details of the embodiment of FIG. 3;
  • FIG. 6 us a fragmentary axial section illustrating another embodiment of the structure of the invention.
  • FIG. 7 is a fragmentary axial section illustrating a further embodiment of a heat exchanger of the inven tion.
  • FIG. 8 is a fragmentary axial section illustrating a still further embodiment of a heat exchanger according to the invention.
  • FIG. 1 there is schematically represented therein, in an axial section which contains the central axis of the illustrated heat exchanger, a plurality of groups 1 of heat-exchanging tubes where each group has the tapered configuration illustrated. Groups of tubes are situated one above the other surrounding the central axis of the heat exchanger with these groups of tubes having an inner region directed toward the central axis and an outer region directed away from the central axis.
  • the exterior heat-exchanging fluid flows through the heat exchanger in the manner indicated by the arrows in FIG. 1 so that the outer heat exchanging fluid has at the groups of tubes 1 the main direction indicated by the arrows which extend upwardly toward the right and left of FIG.
  • baffles 9 which separate the several groups 1 from each other.
  • These baffles are simply in the form of tapered annular walls each forming part of a cone whose center is in the central axis of the heat exchanger.
  • a conical baffle 2 which has its apex directed downwardly and situated substantially at the receiving end of the heat exchanger where the exterior heat-exchanging fluid is received. This conical baffle 2 will direct the outer fluid between the baffles 9 and along the exteriors of the tubes which form the several groups 1.
  • a support means is provided for supporting the tubes which form the groups 1, and this support means includes outer elongated bodies extending parallel to the axis of the heat exchanger and situated at the outer region of the groups 1.
  • the support means also includes inner elongated bodies 4 which extend parallel to the axis of the heat exchanger and which are situated at the inner region of the groups of tubes 1.
  • these inner bodies 4 and outer bodies 5 are in the form of elongated bars extending parallel to the axis of the heat exchanger and fixed in any suitable way to the outer wall of the heat exchanger, such as to the bottom tapered wall thereof illustrated in FIG. 1.
  • the several tapered baffles 9 are also fixed to and extend between the bars 4 and 5 which form the elongated bodies of the support means.
  • the annular baffles 9 may be welded at their outer edges to the inner surfaces of the axial bars 5 of the support means and at their inner edges to the outer surfaces of the axial inner bars 4 of the support means.
  • the several bars 5 as well as the several bars 4 are circumferentially distributed about the central axis of the heat exchanger with these bars being arranged in radially aligned pairs.
  • the welding of these bars 4 and 5 to the tapered baffles 9 forms a supporting framework for the several groups of tubes.
  • FIG. 3 illustrates five spirally wound tubes of a group, these tubes 10, 20, 30, 40 and 50 being arranged with the convolutions of one tube axially aligned with the convolutions of the next tube.
  • the lowermost tube 10 has convolutions ll, 12, 13, 14 from the outer to the inner region of the spirally wound tube
  • the next tube has the convolutions 2l-24 respectively axially aligned with the convolutions 11-14, and so on.
  • FIGS. 3-5 there is a spacer means 3 in the form of metal wires which are curved so as to have a wave-shaped configuration. These wires are welded at their ends to the radially aligned bars 4 and 5 of the support means.
  • the several wires 3 which form the spacer means extend over and under the convolutions of the tubes in the manner illustrated in FIG. 3 so as to interconnect the tubes with each other while maintaining them at a given spacing with respect to each other. Following any one of the wires 3 of FIG.
  • each wire 3 extends first over and under adjoining convolutions of one tube, then over and under adjoining convolutions of the next tube and so on, so that each of the wires 3 serves not only to maintain a given spacing between adjoining convolutions of the same tube but also to maintain the spacing between adjoining convolutions of adjoining tubes.
  • the wires which extend over a convolution of one tube into engagement with the next axially aligned convolution of the next tube will become situated between the wires which extend over this latter tube.
  • FIG. 5 which is taken in a plane normal to the main direction of flow of the outer fluid, the several wires 3 will become situated one next to the other between the tubes, thus forming wire bands which provide the spacers determining the spacing between the several tubes.
  • the inner and outer bars 4 and 5 form the elongated bodies of the support means which together with the tapered baffles 9 of the support means form the supporting structure for the bundles of tubes.
  • the several wires 3 extend through suitable bores in the bars 4 and 5 and are welded to the exterior surfaces thereof which are directed away from the tubes, as is apparent from FIGS. 3 and 4.
  • FIG. 5 shows the next tube at its inner convolution 64 which is axially aligned with the convolution 54 of the tube 50 and which directly engages the next higher baffle 9 as illustrated in FIG. 5.
  • the group of six tubes in the illustrated example is situated between the baffles 9 which are fragmentarily illustrated in FIG. 5.
  • the spacer means takes the form of annular bodies 6 in the forms of rings or sleeves which surround and engage the tubes and which are welded to each other at those locations where they engage each other so that in this way also the spacer means of this embodiment will form a network of the tubes providing the equivalent ofa unitary structure.
  • the spacer means 7 takes the form of angled strips of sheet metal, which while being substantially wave-shaped and following substantially the paths occupied by the wires 3 of FIG. 3, are in fact relatively sharply angled narrow strips of sheet metal which are welded to each other where they engage each other so as to form a honeycomb type of spacer means as illustrated in FIG. 7.
  • the parts of the spacer means which engage the bars 4 and 5 of the support means are welded thereto.
  • those rings 6 which engage the bars 4 and 5 are directly welded thereto.
  • the ends of the strips 7 are welded to the bars 4 and 5.
  • the spacer means also takes the form of elongated relatively narrow strips of sheet metal, but these strips are curved so as to form to the configurations of the wires 3 while at the same time having a width corresponding to the spacers 7 of FIG. 7.
  • the curvature of the wave-shaped spacer strips 8 is such that in this embodiment each strip extends around the axis of a convolution through approximately 120, and of course the same is true of the wires of FIG. 3.
  • the several strips 8 are welded at their ends to the bars 4 and 5 in the manner illustrated for the bar Sin FIG. 8.
  • the tubes are spirally curved in such a way that they will have with respect to each other the relationship shown, for example, in FIG. 3, although this relationship is also illustrated in FIGS. 6-8.
  • the several tubes will have at their convolutions cross sections the centers of which are situated as illustrated in FIG. 3.
  • This arrangement is such that the centers of any group of three adjoining convolutions of a pair of tubes will form either an isosocles triangle or an equilateral triangle.
  • the center of convolution 22 of FIG. 3 forms with the centers of convolutions 32 and 43 of the next pair of successive tubes, inan upward direction as viewed in FIG.
  • any similar group of three convolutions of three successive tubes will have the same relationship.
  • the center of the convolution 32 forms with the centers 21 and 22 of the next adjoining tube an isosocles triangle.
  • the center of convolution 11 forms with the centers of convolutions 21 and 22 also an isosocles triangle.
  • the centers of three adjoining convolutions of three successive tubes will form an equilateral triangle in an axial plane while a pair of adjoining convolutions of one tube with the intermediate convolution of the next tube will form an isosocles triangle in an axial plane.
  • any one convolution has a diameter only slightly greater than the outer diameter of the next inner convolution, so that between the convolutions of the several tubes there are formed narrow, spiral paths through which the exterior heatexchanging fluid is adapted to flow, achieving in this way an extremely favorable heat exchange.
  • the distribution of the tubes in an axial direction is such that in this axial direction the spacing between the tubes is equal to the diameters of a pair of successive axially aligned convolutions plus a single thickness of a spacer component.
  • a direction which is normal to the main direction of flow of the exterior fluid which is to say in a plane containing the axes of convolutions 12, 33, and 54 in FIG.
  • the distribution of the tubes also is equal to the diameters of a pair of successive convolutions plus a single thickness of the spacer component, while in the embodiment of FIG. 8 the distribution in this direction is equal to that of a pair of successive convolutions plus twice the thickness of the spacer members.
  • the spacer members of FIGS. 3 and 8 extend through 120 around the exterior of each convolution.
  • the spacers bring about a uniform distribution of the tube convolutions under all operating conditions and they also serve to transmit the load to the support means formed by the bars 4 and 5. It is preferred to weld the spacers to each other where they engage each other, as pointed out above.
  • Each group of tubes is thermally elastic. Only very small additional stresses are encountered in the tubes as a result of the influence of temperature and thermal changes.
  • the spacer means of the invention acts as a faultless vibration node with a known damping action which remains constant during operation of the heat exchanger, since the weight of the tubes themselves and any other forces acting thereon, such as, for example, the forces of the flowing fluids, will bring about a predetermined and constant pressing force.
  • the convolutions of the tubes are narrowly wound.
  • the spacer means formed by the spacer components forms with the tubes a single unitary structural assembly acting as one unit in response to the stresses which are encountered, with substantially all of the load and stresses being transmitted to the rugged support means formed by the bars 4 and 5.
  • the spacers of the invention serve to hang or suspend the tubes of the convolutions from the bars 4 and 5.
  • the lowermost tube of any group may be considered as supported by the lower baffle 9, as illustrated in FIG. 3 for the tube 10
  • the next higher tube is supported by the lowermost spacer, and it will be seen that the several tubes 20-50 of FIG. 3 are in fact supported by the spacer means so as to be suspended thereby between bars 4 and 5, and of course the same is true for the embodiments of FIGS. 6-8.
  • the tubes are arranged so close to each other that extremely narrow gaps are defined therebetween compelling the exterior fluid to flow at a high speed so as to achieve an extremely efficient rate of heat exchange, enabling the area of heat exchanging surfaces to be reduced so as to achieve for a heat exchanger of a given size an output greater than has heretofore been possible.
  • the convolutions of the several tubes are axially aligned one above the other and the axial gap between any pair of axially aligned convolutions of a pair of adjoining tubes is substantially less than the radius of any tube.
  • the gap between any tube convolution and the next adjoining outer or inner convolution is also substantially less than the radius of any tube.
  • a heat exchanger at least one group of spirally wound tubes for accommodating in their interior an inner heat-exchanging fluid while an outer heatexchanging fluid engages the exterior of said tubes, said tubes surrounding a predetermined axis and being arranged adjacent each other with the convolutions of each tube substantially in axial alignment with the convolutions of the next tube, and said tubes having an inner region directed toward said axis and an outer region directed away from said axis, support means situated adjacent one of the latter regions of said tubes, and spacer means engaging said tubes and connected to said support means for interconnecting said tubes and forming therefrom a unitary assembly where said tubes remain in a predetermined relation with respect to each other determined by said spacer means and for transmitting to said support means forces resulting fromthe weight of said tubes and spacer means as well as any other forces which result from mechanical or thermal stresses or reaction forces resulting from the flow of the heat-exchanging fluids, said spacer means coacting with said tubes for providing narrow gaps therebetween with the axial gap between any pair of adjoining axially aligne
  • each of said tubes has convolutions each of which is only slightly greater than the next inner convolution of each tube so that between he convolutions of the tubes there are formed narrow spiral paths for the outer fluid which engages the exterior of the tubes.
  • said spacer means includes annular bodies surrounding and engaging said tubes and fixed to each other.

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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)
US00074356A 1969-09-26 1970-09-22 Tubular heat exchanger supporting and spacer structure Expired - Lifetime US3720259A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
AT916069A AT304597B (de) 1969-09-26 1969-09-26 Radialstromwärmetauscher

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US3720259A true US3720259A (en) 1973-03-13

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US00074356A Expired - Lifetime US3720259A (en) 1969-09-26 1970-09-22 Tubular heat exchanger supporting and spacer structure

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US (1) US3720259A (enrdf_load_stackoverflow)
AT (1) AT304597B (enrdf_load_stackoverflow)
CH (1) CH522190A (enrdf_load_stackoverflow)
DE (1) DE2045353B2 (enrdf_load_stackoverflow)
FR (1) FR2063172B1 (enrdf_load_stackoverflow)
GB (1) GB1283282A (enrdf_load_stackoverflow)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3916990A (en) * 1974-02-25 1975-11-04 Foster Wheeler Corp Gas turbine regenerator
US3955620A (en) * 1974-04-26 1976-05-11 Artemov Lev N Heat exchanger
US4019468A (en) * 1976-04-21 1977-04-26 Combustion Engineering, Inc. Support for furnace tubes
US4095648A (en) * 1976-07-01 1978-06-20 Hudson Products Corporation Tube bundles
US4286654A (en) * 1979-03-19 1981-09-01 Foster Wheeler Limited Heat exchanger tube supports
US4286366A (en) * 1977-12-23 1981-09-01 Phillips Petroleum Company Method for the construction of a baffled heat exchanger
WO1986003278A1 (en) * 1984-11-29 1986-06-05 Vapor Corporation Boiler having improved heat absorption
US4640342A (en) * 1984-01-26 1987-02-03 Westinghouse Electric Corp. Expandable antivibration bar for heat transfer tubes of a pressurized water reactor steam generator
US4702311A (en) * 1985-05-03 1987-10-27 Technos Et Compagnie Methods and devices for fastening bundles of tubes together
US4732590A (en) * 1987-01-28 1988-03-22 Mcneil John A Flash economizer
US5016706A (en) * 1989-10-30 1991-05-21 Carrier Corporation Heat exchanger tube support
US5088550A (en) * 1991-04-16 1992-02-18 Tippman Joseph R Radial flow heat exchanger
US5501269A (en) * 1993-08-25 1996-03-26 Jenkins; Robert E. Condenser unit
EP0717252A3 (de) * 1994-12-17 1997-11-19 BDAG Balcke-Dürr Aktiengesellschaft Vorrichtung zur Halterung von Rohren eines Wärmeüberträgers
EP0874209A1 (en) * 1997-04-24 1998-10-28 Giorgio Scanferla Heat exchanger for water heating apparatuses and method for producing the same
US6178926B1 (en) * 1999-08-31 2001-01-30 Foster Wheeler Corporation Double-fired horizontal tube heater
WO2002029349A1 (en) * 2000-10-04 2002-04-11 Joseph Kaellis Heat exchanger
US6808017B1 (en) 1999-10-05 2004-10-26 Joseph Kaellis Heat exchanger
US20060108108A1 (en) * 2004-11-19 2006-05-25 Naukkarinen Olli P Spirally wound, layered tube heat exchanger and method of manufacture
US20080296004A1 (en) * 2005-07-22 2008-12-04 Linde Aktiemgesellschaft Wound Heat Exchanger with Anti-Drumming Walls
US20120043052A1 (en) * 2010-07-23 2012-02-23 Heat-Line Corporation Geothermal Energy Transfer System
WO2013040707A1 (en) * 2011-09-19 2013-03-28 Heat-Line Corporation Modular energy transfer unit with common inlet and common outlet
US20130186594A1 (en) * 2012-01-24 2013-07-25 Alstom Technology Ltd. Exchange Tube Support and Securing Assembly for Tube Exchanger
US20160265793A1 (en) * 2015-03-10 2016-09-15 Joseph Copeland Heat transfer apparatus and heat transfer system for masonry heater
US20200003108A1 (en) * 2018-06-30 2020-01-02 Deere And Company Cooling system

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Publication number Priority date Publication date Assignee Title
US3809061A (en) * 1971-11-03 1974-05-07 Steam Engine Syst Corp Heat exchanger and fluid heater
SE7505362L (sv) * 1975-05-07 1976-11-08 Atomenergi Ab Vermevexlingsanordning
US4041726A (en) * 1976-03-29 1977-08-16 Paul Mueller Company Hot water system
FR2355191A1 (fr) * 1976-06-16 1978-01-13 Creusot Loire Dispositif de maintien d'une nappe de tubes a l'interieur d'une enceinte
FR2462684A1 (fr) * 1979-08-03 1981-02-13 Saunier Duval Echangeur de chaleur a paroi developpable et a deux fluides circulant a contre-courant
EP0105938A1 (de) * 1982-10-07 1984-04-25 STAHL- UND APPARATEBAU HANS LEFFER GmbH Halterung für die Rohre eines Rohrbündels innerhalb eines Behälters
DE3329202A1 (de) * 1983-08-12 1985-02-21 MTU Motoren- und Turbinen-Union München GmbH, 8000 München Profilrohr-waermetauscher

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CA685283A (en) * 1964-04-28 Clarke, Chapman And Co. Limited Heat exchangers
GB685848A (en) * 1950-01-24 1953-01-14 Vickers Electrical Co Ltd Improvements relating to the construction of tubular heat exchangers
US3199582A (en) * 1962-04-06 1965-08-10 Foster Wheeler Corp Heat exchanger tube anti-vibration structure
GB1017455A (en) * 1962-06-08 1966-01-19 Motala Verkstad Ab Staying device for tubes, rods and the like in steam generators, heat exchangers andthe like
US3439737A (en) * 1965-11-23 1969-04-22 Atomic Energy Authority Uk Spacer grid for heat exchange elements with mixing promotion means
US3352289A (en) * 1966-06-13 1967-11-14 Vapor Corp Steam generator
GB1188564A (en) * 1967-11-14 1970-04-22 Hick Hargreaves And Company Lt Tube supports
US3554168A (en) * 1968-10-17 1971-01-12 Stone & Webster Eng Corp Furnace apparatus

Cited By (32)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3916990A (en) * 1974-02-25 1975-11-04 Foster Wheeler Corp Gas turbine regenerator
US3955620A (en) * 1974-04-26 1976-05-11 Artemov Lev N Heat exchanger
US4019468A (en) * 1976-04-21 1977-04-26 Combustion Engineering, Inc. Support for furnace tubes
US4095648A (en) * 1976-07-01 1978-06-20 Hudson Products Corporation Tube bundles
US4286366A (en) * 1977-12-23 1981-09-01 Phillips Petroleum Company Method for the construction of a baffled heat exchanger
US4286654A (en) * 1979-03-19 1981-09-01 Foster Wheeler Limited Heat exchanger tube supports
US4640342A (en) * 1984-01-26 1987-02-03 Westinghouse Electric Corp. Expandable antivibration bar for heat transfer tubes of a pressurized water reactor steam generator
US4621592A (en) * 1984-11-29 1986-11-11 Vapor Corporation Boiler having improved heat absorption
WO1986003278A1 (en) * 1984-11-29 1986-06-05 Vapor Corporation Boiler having improved heat absorption
US4702311A (en) * 1985-05-03 1987-10-27 Technos Et Compagnie Methods and devices for fastening bundles of tubes together
US4732590A (en) * 1987-01-28 1988-03-22 Mcneil John A Flash economizer
US5016706A (en) * 1989-10-30 1991-05-21 Carrier Corporation Heat exchanger tube support
US5088550A (en) * 1991-04-16 1992-02-18 Tippman Joseph R Radial flow heat exchanger
US5501269A (en) * 1993-08-25 1996-03-26 Jenkins; Robert E. Condenser unit
EP0717252A3 (de) * 1994-12-17 1997-11-19 BDAG Balcke-Dürr Aktiengesellschaft Vorrichtung zur Halterung von Rohren eines Wärmeüberträgers
EP0874209A1 (en) * 1997-04-24 1998-10-28 Giorgio Scanferla Heat exchanger for water heating apparatuses and method for producing the same
US6178926B1 (en) * 1999-08-31 2001-01-30 Foster Wheeler Corporation Double-fired horizontal tube heater
US6808017B1 (en) 1999-10-05 2004-10-26 Joseph Kaellis Heat exchanger
US20050082047A1 (en) * 1999-10-05 2005-04-21 Joseph Kaellis Heat exchanger
WO2002029349A1 (en) * 2000-10-04 2002-04-11 Joseph Kaellis Heat exchanger
US20060108108A1 (en) * 2004-11-19 2006-05-25 Naukkarinen Olli P Spirally wound, layered tube heat exchanger and method of manufacture
US7546867B2 (en) * 2004-11-19 2009-06-16 Luvata Grenada Llc Spirally wound, layered tube heat exchanger
US8327923B2 (en) * 2005-07-22 2012-12-11 Linde Aktiengesellschaft Wound heat exchanger with anti-drumming walls
US20080296004A1 (en) * 2005-07-22 2008-12-04 Linde Aktiemgesellschaft Wound Heat Exchanger with Anti-Drumming Walls
US20120043052A1 (en) * 2010-07-23 2012-02-23 Heat-Line Corporation Geothermal Energy Transfer System
US9816732B2 (en) 2010-07-23 2017-11-14 Heat-Line Corporation Geothermal energy transfer system
WO2013040707A1 (en) * 2011-09-19 2013-03-28 Heat-Line Corporation Modular energy transfer unit with common inlet and common outlet
US20130186594A1 (en) * 2012-01-24 2013-07-25 Alstom Technology Ltd. Exchange Tube Support and Securing Assembly for Tube Exchanger
US20160265793A1 (en) * 2015-03-10 2016-09-15 Joseph Copeland Heat transfer apparatus and heat transfer system for masonry heater
US10161639B2 (en) * 2015-03-10 2018-12-25 Joseph Copeland Heat transfer apparatus and heat transfer system for masonry heater
US20200003108A1 (en) * 2018-06-30 2020-01-02 Deere And Company Cooling system
US10823039B2 (en) * 2018-06-30 2020-11-03 Deere & Company Cooling system

Also Published As

Publication number Publication date
DE2045353B2 (de) 1973-06-28
CH522190A (de) 1972-04-30
AT304597B (de) 1973-01-10
FR2063172A1 (enrdf_load_stackoverflow) 1971-07-09
FR2063172B1 (enrdf_load_stackoverflow) 1974-02-01
GB1283282A (en) 1972-07-26
DE2045353A1 (de) 1971-04-15

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