US20070181292A1 - Tube bundle heat exchanger - Google Patents

Tube bundle heat exchanger Download PDF

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Publication number
US20070181292A1
US20070181292A1 US10/565,305 US56530504A US2007181292A1 US 20070181292 A1 US20070181292 A1 US 20070181292A1 US 56530504 A US56530504 A US 56530504A US 2007181292 A1 US2007181292 A1 US 2007181292A1
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US
United States
Prior art keywords
tubes
tube bundle
channel
heat exchanger
bundle heat
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.)
Abandoned
Application number
US10/565,305
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English (en)
Inventor
Jiri Jekerle
Klaus-Dieter Rothenpieler
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.)
Arvos GmbH
Original Assignee
Alstom Power Energy Recovery GmbH
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=34071845&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=US20070181292(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Alstom Power Energy Recovery GmbH filed Critical Alstom Power Energy Recovery GmbH
Assigned to ALSTOM POWER ENERGY RECOVERY GMBH reassignment ALSTOM POWER ENERGY RECOVERY GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JEKERLE, JIRI, ROTHENPIELER, KLAUS-DIETER
Assigned to ALSTOM POWER ENERGY RECOVERY GMBH reassignment ALSTOM POWER ENERGY RECOVERY GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: JEKERLE, JIRI, ROTHENPIELER, KLAUS-DIETER
Publication of US20070181292A1 publication Critical patent/US20070181292A1/en
Abandoned legal-status Critical Current

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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
    • F28D7/06—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 having a single U-bend
    • 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
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
    • 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
    • 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
    • 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
    • F28F9/0131—Auxiliary supports for elements for tubes or tube-assemblies formed by plates

Definitions

  • the invention relates to a tube bundle heat exchanger having at least one channel that carries a heating or cooling medium, in particular, a heating gas, whereby the tubes of the tube bundle extend essentially axis-parallel to the channel longitudinal axis through the channel, and the heating or cooling medium is directed through rings and discs, which are arranged on and fastened to the respective jacket walls of the channel in an alternating fashion, in a zigzag pattern as seen in the axial direction of the channel, through the channel which exhibits an essentially annular cross section.
  • a heating or cooling medium in particular, a heating gas
  • Tube bundle heat exchangers through which various gaseous and/or liquid media flow on the tube and jacket side (channel side) are required for many chemical and petrochemical processes.
  • baffles rings and discs
  • This flow component can act upon the heating surface tubes with pulsating forces such that they are induced to oscillate and, in the worst case, are mechanically loaded by constant oscillation, particularly in the resonant range of the tubes.
  • the natural frequency of the tubes is primarily determined by the tube diameter, the wall thickness of the tubes and the interval of the support points (tube plates, baffles that support a tube).
  • the oscillation generation frequency of the medium is dependent on the transverse component of the velocity of the medium and the tube spacing. If the natural frequency of the tubes matches the oscillation generation frequency, it leads to an oscillation resonance with uncontrolled high oscillation amplitudes, and as a result of that, to high mechanical loading of the tubes and a danger of cracks or other mechanical damage.
  • the edge tubes i.e., the tubes lying in the area of the outer or inner jacket region
  • the outer tubes of a tube bundle are held by the ring plates or rings and the inner tubes of the tube bundle are held by the discs, the baffle intervals become or would become very close to each other, which leads or would lead to a large pressure loss on the jacket side.
  • the task of the present invention is to create a tube bundle heat exchanger that avoids the disadvantages mentioned above, and to securely support the particular tubes of the tube bundle inside the channel or channels and to prevent oscillation resonances on the tube bundle tubes that can lead to mechanical damage.
  • the solution provides that in at least one channel, the rings and discs accommodate and position all of the tubes of a channel by means of cylindrical recesses or bores, and the perimeter contour of each of the rings and discs on the medium flow-through side follow the Midpoints of the outermost or innermost tube bundle tubes, whereby the perimeter contour includes a web that surrounds all of the outermost or innermost tubes.
  • the width of the web as the distance between the outer wall of the tube and the perimeter contour is at least partially constant. This means that in the case of the aforesaid regions between the mid-point or the outer wall of the outermost and innermost tubes, the same distance prevails to the perimeter contour, which represents a simplification from the design and manufacturing perspectives.
  • the width of the web is between 3 and 10 millimeters. This further development makes it possible for not only the inner and central tubes of the tube bundle to be securely accommodated and positioned, but also the outermost and innermost tubes of the particular channel. In a particularly advantageous further development, the width of the web is made less than 3 millimeters. With this design, a maximum of free passageway cross section of the heating or cooling medium is achieved on the flow-through side of the rings and discs.
  • a design of the rings and discs can be achieved that is advantageous in terms of manufacture, a constant flow-through cross section, etc. It can be advantageous, or additionally advantageous, that the perimeter contour runs at least partially parallel to an imaginary line connecting two or more outer or inner tube mid-points. This is advantageous when sufficient flow-through cross section is available at the rings and discs, and the perimeter contour thus does not have to follow each individual tube cross section.
  • the rings and discs designed with the perimeter contour are arranged in the outer channel or channels.
  • the tubes of the particular tube bundles can be configured as U-tubes or straight tubes.
  • Heat exchangers according to the invention can thus be equipped with tube bundles of varying designs, and can thus be used for the widest variety of applications.
  • the tubes are arranged inside the channel in a spacing or structure with a triangular or square or other geometrical shape.
  • the triangular spacing or structure is particularly advantageous at high pressures in heat exchangers, since a significantly more highly stiffened tube plate can be achieved.
  • Square or other geometrical structures or tube spacings are advantageous for moderate and low pressures.
  • FIG. 1 a longitudinal section through a tube bundle heat exchanger according to a state of the art
  • FIG. 2 a longitudinal section through a tube bundle heat exchanger according to the invention
  • FIG. 3 a partial cross section according to section A-A in FIG. 2 ,
  • FIG. 4 a partial cross section according to section B-B in FIG. 2 ,
  • FIG. 5 an enlarged detail view C according to FIG. 3 ,
  • FIG. 6 an enlarged detail view D according to FIG. 3 .
  • FIG. 7 as FIG. 5 , but tube bundle tubes inside the channel laid out with a different (square) geometric structure
  • FIG. 8 as FIG. 3 , but tube bundle tubes inside the channel laid out with a different (triangular) geometric structure
  • FIG. 9 an enlarged detail view E according to FIG. 8 .
  • a tube bundle heat exchanger 1 according to a state of the art can be seen in FIG. 1 .
  • Such tube bundle heat exchangers are required for the widest variety of chemical and petrochemical processes.
  • a heating or cooling medium 20 which is most often a heating gas, is fed through an inlet channel 18 to one or more channels or gas channels 4 , 5 in which the heat or cold is conveyed to tubes or heating surface tubes 3 of a larger number of tube bundles 2 running therein which heat or cool a liquid or gaseous medium, e.g., water or steam, that is to be heated or cooled.
  • a liquid or gaseous medium e.g., water or steam
  • the design of the tube bundle heat exchanger 1 according to FIG. 1 provides that the first gas channel or gas passage 4 , the second gas channel or gas passage 5 and finally the outlet channel 19 are connected around the centrally arranged inlet channel 18 in a radial view and concentric to one another.
  • the channels 4 , 5 , 18 , 19 exhibit a common longitudinal axis 6 , which corresponds to the longitudinal axis of the tube bundle heat exchanger 1 .
  • the cross section of the inlet channel 18 is essentially round and those of the gas channels 4 and 5 as well as the outlet channel 19 are essentially annular.
  • the heating or cooling medium flow 20 that flows in at the one end of the tube bundle heat exchanger 1 through the inlet channel 18 is turned by 180° at the other end by the tube plate or end plate 17 that accommodates the tube bundle 2 and is directed to the first gas channel or gas passage 4 . After flowing through the first gas channel 4 , there is another 180° turn and directing of the heating or cooling medium flow 20 into the second gas channel 5 . Finally, after flowing through the second gas channel 5 the heating or cooling medium flow 20 is turned 180° an additional time by the tube plate 17 and is directed out of the heat exchanger 1 through the outlet channel 19 .
  • the tubes 3 are supported and positioned at certain intervals by means of baffles.
  • the heating or cooling medium flow 20 does not flow through the gas channel 4 , 5 parallel to the tubes 3 , but instead flows into the tubes 3 transversely or essentially transversely, and significantly better heat transmission is achieved in this way.
  • the baffles are configured in such a way that at the two jacket walls 7 , 8 (inner 7 and outer 8 gas channel delimitation) of the gas channel 4 , 5 , rings 9 and discs 10 are arranged in alternating fashion so that a zigzag pattern of heating or cooling medium flow through the gas channel 4 , 5 is formed.
  • the outer tubes 3 of the tube bundle tubes running in the gas channel 4 , 5 are supported and positioned by the rings 9 fastened on the jacket wall 8
  • the inner tubes 3 of the tube bundle tubes running in the gas channel 4 , 5 are supported and positioned by the discs 10 fastened on the jacket wall 7 .
  • the tubes 3 are supported by the rings 9 and the discs 10 in the axial direction, in each case at a support distance S (distance between two rings 9 or between two discs 10 ), whereby when viewed axially, the support of the discs 10 in each case lies midway between the support of the rings 9 .
  • the tube bundle heat exchanger 1 exhibits at least one gas channel 4 , 5 , rings 9 and discs 10 , which accommodate and position all tubes 3 of the tube bundle tubes of this gas channel 4 , 5 , each by means of a cylindrical recess or bore 11 .
  • the perimeter contour 12 of the rings 9 and the discs 10 on the medium flow-through side 13 follows mid-points 14 , 15 of the outermost or innermost tube bundle tubes 3 , whereby the perimeter contour 12 includes a web 16 that surrounds all of the outermost or innermost tubes 3 .
  • the medium flow-through side 13 of the rings 9 or the discs 10 involves the side 13 of the rings 9 or the discs 10 that is passed by the medium flow 20 and thus forms the free passage or passageway of the heating or cooling medium flow 20 between ring 9 and inner jacket wall 7 or disc 10 and outer jacket wall 8 , see FIGS. 3 through 9 .
  • the perimeter contour of the rings 9 or discs 10 on the flow-through side 13 is not designed with a circular shape, but according to the invention and as described above it follows the mid-points 14 , 15 respectively of the outermost and innermost tube bundle tubes 3 , i.e., the perimeter contour 12 of the rings 9 the mid-points 15 of the innermost tube bundle tubes 3 and the perimeter contour 12 of the discs 10 the mid-points 14 of the outermost tube bundle tubes 3 , whereby the perimeter contour 12 additionally includes ring or disc material or a web 16 , so that each individual tube bundle tube 3 is bordered or surrounded by this web 16 (see FIGS. 3 through 9 ) in order thus to securely support laterally even the innermost and outermost tubes 3 .
  • the width B of the material projection or web 16 between the outer wall of the outermost or innermost tube 3 and the perimeter contour 12 is preferably kept at least partially constant.
  • Another advantageous development provides a width B of the web 16 of three to ten millimeters, and an especially preferred development provides a width B of the web 16 of less than three millimeters.
  • FIGS. 7 through 9 show a further advantageous development of the invention, which consists in the perimeter contour 12 running at least in part parallel to an imaginary line connecting two or more outer or inner tube mid-points 14 , 15 .
  • the width B of the web 16 is defined as the perpendicular distance between the perimeter contour 12 and the outer wall of the tube 3 .
  • the rings 9 and discs 10 according to the invention can be simplified in terms of manufacturing and produced inexpensively, and second, the free passage cross section of the heating or cooling medium 20 on the flow-through side 13 of the rings 9 and discs 10 can be maximized.
  • the bores or cylindrical recesses 11 by means of which the rings 9 and the discs 10 are formed for accommodating all of the tubes 3 of a gas channel 4 , 5 are arranged in such a way that each individual tube bundle tube 3 is accommodated and guided in the particular bores 11 of the rings 9 and discs 10 , which are aligned axis-parallel to the channel or tube bundle heat exchanger longitudinal axis 6 .
  • the tubes 3 are not connected in fixed fashion with the rings 9 and discs 10 , and can freely elongate axially in the bores 11 during heating in the operational state.
  • the rings 9 and the discs 10 accommodate all of the tube bundle tubes 3 of a channel or gas channel 4 , 5 , the former support distance S of a given tube 3 between two rings 9 or between two discs 10 is halved to the half support distance S/ 2 .
  • this is advantageous for the lateral support of the tube bundle tubes 3 , since each individual tube 3 is in practice supported twice as often as with the known versions.
  • the development according to the invention is advantageous in terms of the prevention of resonance oscillations of the tubes 3 , and, as a result of that, also the prevention of the high mechanical loads on these tubes 3 that are brought about by the resonance oscillations.
  • An oscillation resonance on the tubes 3 forms in a known way if the natural frequency of the tubes matches the oscillation generation frequency of the medium or the heating or cooling medium 20 , whereby the oscillation generation frequency of the medium is dependent on the transverse component of the velocity of the medium and the tube spacing, while the natural frequency of the tubes 3 is primarily determined by the tube diameter, the wall thickness of the tubes 3 and the interval of the support points (tube plate 17 , rings 9 and discs 10 ).
  • the oscillation resonance inside the tube bundle heat exchanger 1 can be easily prevented and the tubes 3 can be securely supported, without decreasing the intervals of the baffles, i.e., the rings 9 and discs 10 , from each other, and thus creating higher pressure losses on the channel side or the heating or cooling medium side 20 .
  • the halved support intervals if necessary it is possible to increase the dimension of the support interval or decrease the wall thickness of the tubes 3 without losing the advantageous effect.
  • FIGS. 2 through 4 reveal a tube bundle heat exchanger 1 according to the invention that is designed with, in the preferred configuration, two channels or gas channels 4 , 5 that are arranged concentric to one another.
  • the rings 9 and discs 10 that are configured with outer perimeter 12 and that accommodate all of the tubes 3 are advantageously arranged in the outer channel 5 or the outer gas channels. This measure prevents a large medium pressure loss inside the heat exchanger 1 , since the medium flow 20 in the inner channel 4 , in which the gas still exhibits a very high temperature and therefore possesses a large volume and a high passage velocity, finds a freer passage, i.e., a larger flow-through cross section.
  • FIGS. 2 through 6 show a tube bundle heat exchanger 1 according to the invention, with tube bundles 2 formed from U-tubes 3 and with its inner tube field arranged in gas channel 4 and its outer tube field in gas channel 5
  • FIGS. 7 through 9 show a tube bundle heat exchanger 1 according to the invention with tube bundles 2 formed from straight pipes 3 .
  • the structural arrangement of these straight tubes 3 inside the channel 4 , 5 when viewed over the cross section can be freely configured, unlike the arrangement of the U-tubes 3 .
  • the straight tubes 3 can advantageously be arranged within the channel 4 , 5 in a spacing or tube structure with a triangular or square or other geometrical shape.
  • a triangular tube spacing, as shown in FIGS. 8 and 9 lends itself for tube bundle heat exchangers 1 with high to very high pressures, while square tube spacings according to FIG. 7 or another geometrical tube spacing lends itself for moderate and low pressures.
  • the tube bundle heat exchanger 1 according to the invention is not limited to the embodiments shown in the above-mentioned Figures.

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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)
  • Lubricants (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)
US10/565,305 2003-07-22 2004-07-06 Tube bundle heat exchanger Abandoned US20070181292A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10333463.7 2003-07-22
DE10333463.7A DE10333463C5 (de) 2003-07-22 2003-07-22 Rohrbündelwärmetauscher
PCT/DE2004/001439 WO2005010450A1 (de) 2003-07-22 2004-07-06 Rohrbündelwärmetauscher

Publications (1)

Publication Number Publication Date
US20070181292A1 true US20070181292A1 (en) 2007-08-09

Family

ID=34071845

Family Applications (1)

Application Number Title Priority Date Filing Date
US10/565,305 Abandoned US20070181292A1 (en) 2003-07-22 2004-07-06 Tube bundle heat exchanger

Country Status (9)

Country Link
US (1) US20070181292A1 (de)
EP (1) EP1646836B1 (de)
JP (1) JP4573183B2 (de)
KR (1) KR100751961B1 (de)
AT (1) ATE344911T1 (de)
CA (1) CA2532466C (de)
DE (2) DE10333463C5 (de)
DK (1) DK1646836T3 (de)
WO (1) WO2005010450A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140014294A1 (en) * 2012-07-13 2014-01-16 Areva Np Inc. U-Bend Tube Compression/Distortion Stabilization System (CDSS)
US20180224219A1 (en) * 2015-07-06 2018-08-09 Casale Shell-and-tube equipment with antivibration baffles and related assembling method
US11486660B2 (en) * 2017-08-28 2022-11-01 Watlow Electric Manufacturing Company Continuous helical baffle heat exchanger
US11913736B2 (en) * 2017-08-28 2024-02-27 Watlow Electric Manufacturing Company Continuous helical baffle heat exchanger
US11920878B2 (en) * 2017-08-28 2024-03-05 Watlow Electric Manufacturing Company Continuous helical baffle heat exchanger

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2007083927A1 (en) * 2006-01-18 2007-07-26 Lg Chem, Ltd. Reactor with improved heat transfer performance
US20130292089A1 (en) * 2012-05-01 2013-11-07 Norcross Corporation Dual passage concentric tube heat exchanger for cooling/heating of fluid in a low pressure system
ES2842423T3 (es) * 2017-05-26 2021-07-14 Alfa Laval Olmi S P A Intercambiador de calor de carcasa y tubos

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US2774575A (en) * 1952-03-07 1956-12-18 Worthington Corp Regenerator
US2873098A (en) * 1955-10-03 1959-02-10 Yates American Machine Co Heat exchange apparatus
US3240267A (en) * 1963-07-16 1966-03-15 Borg Warner Heat exchanger
US3475137A (en) * 1967-03-09 1969-10-28 Chemical Construction Corp Apparatus for exothermic catalytic reactions with integral heat exchanger
US3490521A (en) * 1968-03-12 1970-01-20 Westinghouse Electric Corp Tube and shell heat exchanger
US3656548A (en) * 1970-04-23 1972-04-18 Borg Warner Self-positioning baffle for shell and tube heat exchangers
US3741164A (en) * 1971-03-03 1973-06-26 Foster Wheeler Corp Sodium heated steam generator
US3802498A (en) * 1970-02-02 1974-04-09 N Romanos Shell and tube heat exchanger with central conduit
US3827484A (en) * 1970-02-04 1974-08-06 W Wolowodiuk Liquid metal heat exchanger
US4357991A (en) * 1979-11-23 1982-11-09 C-I-L Inc. Heat exchanger having improved tube layout
US4834173A (en) * 1987-11-20 1989-05-30 American Standard Inc. Pressure actuated baffle seal
US4991648A (en) * 1989-02-10 1991-02-12 Mitsubishi Jukogyo Kabushiki Kaisha Multi-tube type heat transfer apparatus
US5253701A (en) * 1991-09-14 1993-10-19 Erno Raumfahrttechnik Gmbh Evaporation heat exchanger apparatus for removing heat
US5615738A (en) * 1994-06-29 1997-04-01 Cecebe Technologies Inc. Internal bypass valve for a heat exchanger
US5653282A (en) * 1995-07-19 1997-08-05 The M. W. Kellogg Company Shell and tube heat exchanger with impingement distributor
US5660230A (en) * 1995-09-27 1997-08-26 Inter-City Products Corporation (Usa) Heat exchanger fin with efficient material utilization
US5915465A (en) * 1997-03-14 1999-06-29 Deutsche Babcock-Borsig Aktiengesellschaft Heat exchanger
US6142215A (en) * 1998-08-14 2000-11-07 Edg, Incorporated Passive, thermocycling column heat-exchanger system

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FR2233587A1 (en) * 1973-06-14 1975-01-10 Chausson Usines Sa Tube bundle heat exchanger - has tube ends shaped as complementary polygons
JPS5424353A (en) * 1977-07-27 1979-02-23 Mitsubishi Heavy Ind Ltd Multiple heat exchanger
CH630721A5 (de) * 1978-01-23 1982-06-30 Agresto Ag International Sa Rohrbuendelwaermeaustauscher mit stroemungsleitvorrichtung.
JPS56162400A (en) * 1980-05-19 1981-12-14 Toshiba Corp U-tube type heat exchanger
DE3169039D1 (en) * 1980-07-23 1985-03-28 Armstrong Eng Ltd Heat exchanger
JPS6284299A (ja) * 1985-10-04 1987-04-17 Yanmar Diesel Engine Co Ltd 多管式熱交換器
JPH10227591A (ja) * 1997-02-14 1998-08-25 Usui Internatl Ind Co Ltd Ｅｇｒガス冷却装置

Patent Citations (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2774575A (en) * 1952-03-07 1956-12-18 Worthington Corp Regenerator
US2873098A (en) * 1955-10-03 1959-02-10 Yates American Machine Co Heat exchange apparatus
US3240267A (en) * 1963-07-16 1966-03-15 Borg Warner Heat exchanger
US3475137A (en) * 1967-03-09 1969-10-28 Chemical Construction Corp Apparatus for exothermic catalytic reactions with integral heat exchanger
US3490521A (en) * 1968-03-12 1970-01-20 Westinghouse Electric Corp Tube and shell heat exchanger
US3802498A (en) * 1970-02-02 1974-04-09 N Romanos Shell and tube heat exchanger with central conduit
US3827484A (en) * 1970-02-04 1974-08-06 W Wolowodiuk Liquid metal heat exchanger
US3656548A (en) * 1970-04-23 1972-04-18 Borg Warner Self-positioning baffle for shell and tube heat exchangers
US3741164A (en) * 1971-03-03 1973-06-26 Foster Wheeler Corp Sodium heated steam generator
US4357991A (en) * 1979-11-23 1982-11-09 C-I-L Inc. Heat exchanger having improved tube layout
US4834173A (en) * 1987-11-20 1989-05-30 American Standard Inc. Pressure actuated baffle seal
US4991648A (en) * 1989-02-10 1991-02-12 Mitsubishi Jukogyo Kabushiki Kaisha Multi-tube type heat transfer apparatus
US5253701A (en) * 1991-09-14 1993-10-19 Erno Raumfahrttechnik Gmbh Evaporation heat exchanger apparatus for removing heat
US5615738A (en) * 1994-06-29 1997-04-01 Cecebe Technologies Inc. Internal bypass valve for a heat exchanger
US5653282A (en) * 1995-07-19 1997-08-05 The M. W. Kellogg Company Shell and tube heat exchanger with impingement distributor
US5660230A (en) * 1995-09-27 1997-08-26 Inter-City Products Corporation (Usa) Heat exchanger fin with efficient material utilization
US5915465A (en) * 1997-03-14 1999-06-29 Deutsche Babcock-Borsig Aktiengesellschaft Heat exchanger
US6142215A (en) * 1998-08-14 2000-11-07 Edg, Incorporated Passive, thermocycling column heat-exchanger system

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20140014294A1 (en) * 2012-07-13 2014-01-16 Areva Np Inc. U-Bend Tube Compression/Distortion Stabilization System (CDSS)
US20180224219A1 (en) * 2015-07-06 2018-08-09 Casale Shell-and-tube equipment with antivibration baffles and related assembling method
US10788273B2 (en) * 2015-07-06 2020-09-29 Casale Sa Shell-and-tube equipment with antivibration baffles and related assembling method
US11486660B2 (en) * 2017-08-28 2022-11-01 Watlow Electric Manufacturing Company Continuous helical baffle heat exchanger
US11808534B2 (en) * 2017-08-28 2023-11-07 Watlow Electric Manufacturing Company Continuous helical baffle heat exchanger
US11913736B2 (en) * 2017-08-28 2024-02-27 Watlow Electric Manufacturing Company Continuous helical baffle heat exchanger
US11920878B2 (en) * 2017-08-28 2024-03-05 Watlow Electric Manufacturing Company Continuous helical baffle heat exchanger

Also Published As

Publication number Publication date
KR100751961B1 (ko) 2007-08-27
DE502004001966D1 (de) 2006-12-21
WO2005010450A1 (de) 2005-02-03
CA2532466C (en) 2008-10-21
DK1646836T3 (da) 2007-03-19
ATE344911T1 (de) 2006-11-15
DE10333463A1 (de) 2005-02-17
DE10333463C5 (de) 2014-04-24
JP4573183B2 (ja) 2010-11-04
DE10333463B4 (de) 2006-05-04
EP1646836B1 (de) 2006-11-08
KR20060038456A (ko) 2006-05-03
EP1646836A1 (de) 2006-04-19
CA2532466A1 (en) 2005-02-03
JP2006528762A (ja) 2006-12-21

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