US20130112156A1 - Heat exchanger for generating steam for solar power plants - Google Patents

Heat exchanger for generating steam for solar power plants Download PDF

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Publication number
US20130112156A1
US20130112156A1 US13/510,374 US201013510374A US2013112156A1 US 20130112156 A1 US20130112156 A1 US 20130112156A1 US 201013510374 A US201013510374 A US 201013510374A US 2013112156 A1 US2013112156 A1 US 2013112156A1
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US
United States
Prior art keywords
heat
heat exchanger
inlet
tube
tubes
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
US13/510,374
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English (en)
Inventor
Dirk Band
Wolfgang Hegner
Jorg Stahlhut
Vitali Tregubow
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.)
Balcke Duerr GmbH
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Balcke Duerr 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
Application filed by Balcke Duerr GmbH filed Critical Balcke Duerr GmbH
Assigned to BALCKE-DURR GMBH reassignment BALCKE-DURR GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: Tregubow, Vitali, Band, Dirk, HEGNER, WOLFGANG, STAHLHUT, JORG
Publication of US20130112156A1 publication Critical patent/US20130112156A1/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
    • F28D7/08—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
    • F28D7/082—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 with serpentine or zig-zag configuration
    • F28D7/085—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 with serpentine or zig-zag configuration in the form of parallel conduits coupled by bent portions
    • F28D7/087—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 with serpentine or zig-zag configuration in the form of parallel conduits coupled by bent portions assembled in arrays, each array being arranged in the same plane
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B29/00—Steam boilers of forced-flow type
    • F22B29/06—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B29/00—Steam boilers of forced-flow type
    • F22B29/06—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes
    • F22B29/061—Construction of tube walls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B29/00—Steam boilers of forced-flow type
    • F22B29/06—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes
    • F22B29/061—Construction of tube walls
    • F22B29/062—Construction of tube walls involving vertically-disposed water tubes
    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/04—Arrangements for sealing elements into header boxes or end plates
    • F28F9/16—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling
    • F28F9/18—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding
    • F28F9/185—Arrangements for sealing elements into header boxes or end plates by permanent joints, e.g. by rolling by welding with additional preformed parts

Definitions

  • the invention relates to a heat exchanger for generating steam for solar power plants.
  • Heat exchangers which are arranged in a modular manner and which operate according to the so-called circulation principle (natural or forced circulation) are known from the state of the art.
  • the heat exchanger comprises a number of heat exchanger modules such as a preheater module, one or several evaporator modules and a superheater module, which are switched together into a functional unit by means of respective inlet and outlet headers, circulation pipes and an external steam collecting drum.
  • the invention is based on the object of providing a heat exchanger which allows a compact configuration, cost-effective production and secure operation.
  • the heat exchanger in accordance with the invention for generating steam for solar power plants comprises an outer casing with an inlet and outlet nozzle for a heat-emitting medium.
  • the exchanger further comprises an inlet and an outlet header for a heat-absorbing medium, preferably water, said inlet and outlet header being arranged substantially within the outer casing.
  • a tube bundle is further disposed within the outer casing, comprising a number of tube layers with continuous tubes which are arranged in such a way that the heat-emitting medium can be flow entirely around the same and which are designed as flow paths for the heat-absorbing medium from the inlet header to the outlet header.
  • the tube bundle is arranged in a meandering fashion.
  • the heat exchanger in accordance with the invention is arranged for generating steam according to the forced-flow principle, so that the heat-absorbing medium which is fed into the inlet header is successively preheated, evaporated and superheated in the course of the flow paths, so that a superheated steam exits from the outlet header.
  • the energy required for the preheating, evaporation and superheating is essentially provided entirely by the heat transfer from the heat-emitting medium to the heat-absorbing medium within the outer casing.
  • the heat exchanger therefore combines at least three different apparatuses, which are preheater, evaporator and superheater.
  • heat exchange occurs according to the counter-flow or cross-flow principle.
  • a heat-absorbing medium preferably water, flows through the meandering tubes.
  • the overall size of the heat exchanger is reduced in its entirety, the heat transmission from heat-emitting to heat-absorbing medium is improved and further the thermal elasticity of the configuration is increased.
  • the supplied heat-absorbing medium preferably water
  • the supplied heat-absorbing medium preferably water
  • the water which enters via the inlet header into the heat exchanger in the fluid state is preheated in the course of its flow within the heat exchanger tubes in the direction towards the outlet header, and is evaporated and superheated, so that superheated steam will leave the heat exchanger via the outlet header, which superheated steam can be supplied to the steam turbine for power generation.
  • Continuous tubes shall mean in this connection that every tube which respectively defines a flow path for the heat-absorbing medium does not have any branching or mixing points between the inlet header and the outlet header.
  • the tubes further extend completely “within the outer casing”, which means that no parts of the tube bundle are disposed outside of the outer casing and that the heat-emitting medium flows entirely around the tubes. No external energy sources are therefore required which promote preheating, evaporation or superheating.
  • the heating areas of the continuous tubes therefore successively form in the direction of flow the preheater, evaporator and superheater zone.
  • the heat exchanger can be erected either horizontally or vertically. Vertical installation is preferable because it allows an even better utilization of the surface area.
  • Several of the heat exchangers in accordance with the invention can be operated next to one another in parallel on a relatively small surface area. The available space is very limited in solar-thermal power plants because the parabolic trough collectors require a large amount of space.
  • the space-saving configuration of the heat exchanger in accordance with the invention allows a nearly remote installation, so that the flow paths of the heated media to the heat exchanger can appropriately be reduced. The temperatures of the heat-emitting medium are higher when entering the heat exchanger, so that the heat yield will be improved.
  • a further preferred embodiment of the invention provides that the tube bundle comprises a number of vertical tube layers in the case of vertical installation, with each tube layer being formed by the same number of tubes, and that the tube layers are arranged in such a way that the tubes of the individual tube layers are aligned in the horizontal direction to lie precisely next to one another, with the directions of flows of the heat-absorbing medium being in opposite directions in the horizontally adjacent tube sections which are arranged transversely to the central axis of the outer casing.
  • the arrangement of the tube bundles in individual tube layers allows an extremely compact configuration. Since the tubes can be disposed precisely next to one another horizontally, conventional spacers can be used between the tubes.
  • the inlet and the outlet headers have a circular cross-section.
  • the tubes of one tube layer on one circumferential line of the inlet and outlet header are connected with the inlet and outlet header offset from one another by the same angle. The production process will be facilitated in this way because sufficient space is provided for welding work, production by metal cutting or other work on the headers.
  • the tubes of the adjacent tube layers are further preferably connected with the inlet and outlet headers in such a way that the tubes of the one tube layer are arranged with respect to the tubes of the adjacent tube layer offset by an angle on an adjacent circumferential line of the respective inlet and outlet header.
  • the circumferential areas of the inlet and outlet headers can be utilized optimally, so that the arrangement of the tube layers can be provided with a compact configuration. There is still sufficient space for welding work, production by metal cutting or other work on the headers.
  • the tube bundle comprises a separate section in which the preheating of the heat-absorbing medium mainly occurs.
  • the separate preheater section can be realized by a local separation within the outer casing for example. It is also possible to control the flow of the heat-emitting medium and therefore the distribution of the temperature in the heat exchanger in such a way that the preheating of the heat-absorbing medium mainly occurs in this preheater section. Alternatively, the preheating could also occur completely outside of the outer casing, i.e. in a separate preheater. In this case, the heat exchanger in accordance with the invention would be arranged mainly for the evaporation and the superheating of the heat-absorbing medium.
  • the tube bundle comprises a separate section in which the evaporation of the heat-absorbing medium mainly occurs.
  • the separate evaporator section can be realized for example by a local separation within the outside jacket. It is also possible to control the flow of the heat-emitting medium and consequently the distribution of the temperature in the heat exchanger in such a way that the evaporation of the heat-absorbing medium mainly occurs in this evaporator section. Alternatively, the evaporation could also occur completely outside of the outer casing, i.e. in a separate evaporator. In this case, the heat exchanger in accordance with the invention would be arranged mainly for the preheating and the superheating of the heat-absorbing medium.
  • the tube bundle comprises a separate section in which the superheating of the heat-absorbing medium mainly occurs.
  • the separate superheater section can be realized for example by a local separation within the outside jacket. It is also possible to control the flow of the heat-emitting medium and consequently the distribution of the temperature in the heat exchanger in such a way that the superheating of the heat-absorbing medium mainly occurs in this superheater section. Alternatively, the superheating could also occur completely outside of the outer casing, i.e. in a separate superheater. In this case, the heat exchanger in accordance with the invention would be arranged mainly for the preheating and the evaporation of the heat-absorbing medium.
  • the tubes are connected via nipples with the inlet and outlet header.
  • the connection between the nipples and the individual tubes preferably occurs by material connection, e.g. by welding.
  • the welding process can occur in an automated manner.
  • the weld seams are checked individually, e.g. by means of x-rays.
  • the tubes are directly connected with the inlet and outlet header without nipples.
  • the connection between the headers and the individual tubes preferably occurs by material connection, e.g. by welding.
  • the welding process can also occur in an automated manner.
  • the weld seams are checked individually, e.g. by means of x-rays.
  • the nipples are materially connected with the inlet and outlet header by means of welding for example.
  • the welding process can also be performed automatically in this case too.
  • the nipples are made directly by means of metal cutting from the material of the inlet and outlet header.
  • the nipples can be milled out of the initially tubular material of the inlet and outlet header. Potential damage caused by welding work is reduced thereby.
  • the tubes of the tube bundle are arranged in an internal housing which is arranged concentrically within the outer casing and comprises an inlet and outlet opening for the heat-emitting medium.
  • the cross-sectional profile of the internal housing is preferably rectangular, so that the tube bundle is enclosed as tightly as possible by said internal housing.
  • the inlet and the outlet opening of the internal housing can be connected with the corresponding inlet and outlet nozzles in such a way that a separate space is created between the outer casing and the internal housing.
  • a flow of the heat-emitting medium can be permitted along the inside wall of the outer casing.
  • the inlet and the outlet nozzles for the heat-emitting medium are arranged in the bottom part of the outer casing in the case of a vertical installation of the heat exchanger.
  • the compactness of the heat exchanger is increased even further thereby.
  • maintenance work is facilitated thereby because the connections on the casing side are arranged close to the bottom part.
  • the space between the outer casing and the internal housing is used as a flow channel for the heat-emitting medium.
  • the hot heat-emitting medium enters via the inlet nozzle of the outer casing and the inlet opening of the internal housing into the interior of the internal housing and flows upwardly.
  • the heat-emitting medium flows through the annular flow channel which is produced by the concentric arrangement of the outer casing and the internal housing, then back downwardly where it then exits the outer casing via the outlet nozzle.
  • the dwell time of the heat-emitting medium in the heat exchanger is increased thereby, so that the heat transmission to the heat-absorbing medium is generally improved.
  • FIG. 1 shows a side view of an embodiment of the heat exchanger in accordance with the invention
  • FIG. 2 shows a sectional view along the line A-A of FIG. 1 ;
  • FIG. 3 shows a detailed view “X” of FIG. 2 ;
  • FIG. 4 shows a sectional view along the line B-B of FIG. 3 ;
  • FIG. 5 shows a detailed view of the inlet header of FIG. 1 and FIG. 2 ;
  • FIG. 6 shows a top view of the inlet header of FIG. 5 .
  • FIGS. 1 and 2 show an embodiment of the heat exchanger 1 in accordance with the invention.
  • the heat exchanger 1 is vertically erected in a space-saving manner.
  • An inner housing 3 is disposed within the outer casing 2 , which inner housing has a rectangular cross-sectional profile.
  • the meandering tubes of the tube bundle 11 are arranged in the inner housing 3 .
  • the heat-absorbing medium such as water enters the heat exchanger 1 via the inlet header 6 . After flowing through the tubes of the tube bundle 11 , it exits from the heat exchanger 1 via the outlet header 7 .
  • the water is preheated and thereafter evaporated and subsequently superheated on the path from the inlet header 6 to the outlet header 7 .
  • the superheated steam which exits from the heat exchanger 1 is guided for power generation to the downstream steam turbine (not shown).
  • the individual “zones”, which are preheater, evaporator and superheater, are not visible from the outside.
  • the heat exchanger 1 for the generation of steam which works according to the forced-flow principle such as the Benson principle, generates a superheated steam in the course of the flow within the heat exchanger 1 from the feed water which enters in fluid form into the inlet header, which superheated steam can be taken from the outlet header 7 .
  • the conventionally used steam drums, circulation pipes, inlet and outlet headers and numerous weld seams can be omitted, so that the compactness is increased and production costs can be saved.
  • the claws 8 are used for mounting the heat exchanger 1 . Maintenance work can be performed in a simple manner via manholes 9 which comprise transparent glass windows and/or locking means.
  • the heat-emitting medium preferably concerns thermal oil which is heated in the absorber tubes of the parabolic fluted reflectors to approximately 400° C. Fluid salts or other suitable heat carrier media could be used as an alternative.
  • the thermal oil enters the heat exchanger 1 via the inlet nozzle 4 of the outer casing 2 . It flows from there in the direction of the outlet nozzle 5 and flows about the tube bundle 11 which is shaped in a meandering manner. Once the thermal oil has transferred a portion of its thermal energy to the water, it exits from the heat exchanger 1 via the outlet nozzle 5 .
  • the flow of the thermal oil on the casing side can be guided in such a way that the thermal oil will enter and exit in the bottom part of the heat exchanger 1 .
  • the space between the inner housing 3 and the outer casing 2 is used as a flow path for the downwardly flowing thermal oil.
  • both the inlet nozzle and also the outlet nozzle are arranged in the bottom region of the vertically erected heat exchanger 1 .
  • FIG. 2 Two tubes of a tube layer are indicated in FIG. 2 . It is understood that the number of the tubes and the tube layers of a tube bundle 11 are adjusted according to the different conditions.
  • FIG. 3 shows a tube layer 20 with the four tubes 21 , 22 , 23 , 24 for example. It clearly shows the meandering structure of the tube bundle 11 .
  • FIG. 4 illustrates the arrangement of the individual tube layers 20 , 30 with respect to each other.
  • each tube has an opposite direction of the tube flow with respect to its horizontally adjacent tube in the case of vertical installation. This means for example that the flow in the tube 21 is opposite to the flow in the horizontally adjacent tube 34 .
  • This opposite flow in the respectively adjacent tube layers 20 , 30 additionally ensures a constant temperature distribution within the heat exchanger 1 .
  • simple spacers 12 can be used.
  • FIG. 5 shows a header in accordance with the invention on an enlarged scale. It concerns the inlet header 6 .
  • the inlet and outlet headers 6 , 7 differ only slightly from one another.
  • the nipples 22 a, 33 a are clearly recognizable, which are used for fastening the tubes 22 , 33 to the inlet header 6 .
  • the nipples 21 a, 22 a, 23 a, 24 a and therefore also the tubes 21 , 22 , 23 , 24 of the first tube layer 20 are disposed on a first circumferential line 13 and respectively open into the header 6 offset by the same angle a.
  • the tubes 31 , 32 , 33 , 34 with the same nipples 31 a, 32 a, 33 a, 34 a enter the header 6 on an adjacent circumference line 14 offset by the same angle ⁇ .
  • FIG. 6 shows a top view of the header 6 .
  • the angle ⁇ by which a tube of one layer is offset from the next tube of the next layer, is in this case 45° each.

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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)
  • Engine Equipment That Uses Special Cycles (AREA)
US13/510,374 2009-11-17 2010-10-25 Heat exchanger for generating steam for solar power plants Abandoned US20130112156A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP09014365.2 2009-11-17
EP09014365.2A EP2322854B1 (de) 2009-11-17 2009-11-17 Wärmetauscher zur Dampferzeugung für Solarkraftwerke
PCT/EP2010/006512 WO2011060870A1 (de) 2009-11-17 2010-10-25 Wärmetauscher zur dampferzeugung für solarkraftwerke

Publications (1)

Publication Number Publication Date
US20130112156A1 true US20130112156A1 (en) 2013-05-09

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US13/510,374 Abandoned US20130112156A1 (en) 2009-11-17 2010-10-25 Heat exchanger for generating steam for solar power plants

Country Status (10)

Country Link
US (1) US20130112156A1 (ko)
EP (1) EP2322854B1 (ko)
KR (1) KR20120117748A (ko)
CN (1) CN102667338B (ko)
AU (1) AU2010321334B2 (ko)
ES (1) ES2435550T3 (ko)
MA (1) MA33812B1 (ko)
PT (1) PT2322854E (ko)
WO (1) WO2011060870A1 (ko)
ZA (1) ZA201203459B (ko)

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* Cited by examiner, † Cited by third party
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CN104949150A (zh) * 2015-07-03 2015-09-30 哈尔滨哈锅锅炉工程技术有限公司 一种锅炉管式空气预热器管箱与连通箱的连接结构
CN111912260A (zh) * 2020-06-24 2020-11-10 哈尔滨汽轮机厂辅机工程有限公司 一种集预热、蒸发、过热为一体的换热设备
US11283400B2 (en) 2018-08-11 2022-03-22 Tyll Solar, Llc Solar energy system
US11739931B2 (en) 2018-10-01 2023-08-29 Header-coil Company A/S Heat exchanger, such as for a solar power plant

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102721031A (zh) * 2012-06-11 2012-10-10 东方电气集团东方汽轮机有限公司 一种直流式蒸汽发生器
EP3155319B1 (en) 2014-06-10 2020-02-12 Siemens Aktiengesellschaft Modular heat recovery steam generator construction
CA2954881C (en) * 2014-07-03 2023-01-17 Tyll Solar, Llc Solar energy system
US11150037B2 (en) * 2014-10-10 2021-10-19 Baltimore Aircoil Company, Inc. Heat exchange apparatus
CN107606641A (zh) * 2017-10-27 2018-01-19 四川省洪雅青衣江元明粉有限公司 一种基于mvr技术中的预热器
CA3139844A1 (en) 2019-06-17 2020-12-24 Aalborg Csp A/S Heat exchanger with pipe bundle

Citations (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2221382A (en) * 1937-12-14 1940-11-12 Riley Stoker Corp Steam generator
US2547589A (en) * 1947-07-02 1951-04-03 Comb Eng Superheater Inc Apparatus for extracting heat from gases under pressure
US2980083A (en) * 1958-09-22 1961-04-18 Combustion Eng Heat exchange organization
US3110288A (en) * 1958-06-26 1963-11-12 Babcock & Wilcox Ltd Heat exchanger construction
US4296804A (en) * 1979-06-28 1981-10-27 Resistoflex Corporation Corrosion resistant heat exchanger element and method of manufacture
US4325171A (en) * 1979-10-15 1982-04-20 Econo-Therm Energy Systems Corporation Means and method for sealing heat exchanger walls
US4612976A (en) * 1983-02-10 1986-09-23 Novatome Steam generator for a nuclear reactor cooled with liquid metal
US4753773A (en) * 1985-05-09 1988-06-28 Stone & Webster Engineering Corporation Double tube steam generator
US5044427A (en) * 1990-08-31 1991-09-03 Phillips Petroleum Company Heat exchanger
US5771963A (en) * 1995-12-05 1998-06-30 Asea Brown Boveri Ag Convective countercurrent heat exchanger
US5871045A (en) * 1995-07-01 1999-02-16 Bdag Balcke-Durr Aktiengesellschaft Heat exchanger
US6019070A (en) * 1998-12-03 2000-02-01 Duffy; Thomas E. Circuit assembly for once-through steam generators
US20030051501A1 (en) * 2001-09-18 2003-03-20 Hitoshi Matsushima Laminated heat exchanger and refrigeation cycle
US20030178185A1 (en) * 2002-03-22 2003-09-25 Wanni Amar S. Heat exchanger with reduced fouling
US6820685B1 (en) * 2004-02-26 2004-11-23 Baltimore Aircoil Company, Inc. Densified heat transfer tube bundle
US7533633B2 (en) * 2004-07-05 2009-05-19 Hitachi Power Europe Gmbh Establishing a connection between steam generator heating surfaces and a collector and/or distributor
US20130192586A1 (en) * 2011-07-29 2013-08-01 David T. Wasyluk Shop assembled vertical serpentine flow molten salt solar receiver
US8708035B2 (en) * 2008-09-08 2014-04-29 Balcke-Dürr GmbH Heat exchanger in a modular construction

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1359081A (fr) 1961-09-07 1964-04-24 Foster Wheeler Ltd Perfectionnements aux échangeurs de chaleurs, particulièrement pour centrales nucléaires
FR1351602A (fr) * 1962-12-29 1964-02-07 Babcock & Wilcox France Perfectionnements aux échangeurs de chaleur de récupération
DE4321250A1 (de) * 1993-06-25 1995-01-05 Fritz Egger Gmbh Rohrbündel-Wärmetauscher
CN101245972A (zh) * 2008-03-14 2008-08-20 泰州市新恒盛机械制造有限公司 穿片式换热器

Patent Citations (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2221382A (en) * 1937-12-14 1940-11-12 Riley Stoker Corp Steam generator
US2547589A (en) * 1947-07-02 1951-04-03 Comb Eng Superheater Inc Apparatus for extracting heat from gases under pressure
US3110288A (en) * 1958-06-26 1963-11-12 Babcock & Wilcox Ltd Heat exchanger construction
US2980083A (en) * 1958-09-22 1961-04-18 Combustion Eng Heat exchange organization
US4296804A (en) * 1979-06-28 1981-10-27 Resistoflex Corporation Corrosion resistant heat exchanger element and method of manufacture
US4325171A (en) * 1979-10-15 1982-04-20 Econo-Therm Energy Systems Corporation Means and method for sealing heat exchanger walls
US4612976A (en) * 1983-02-10 1986-09-23 Novatome Steam generator for a nuclear reactor cooled with liquid metal
US4753773A (en) * 1985-05-09 1988-06-28 Stone & Webster Engineering Corporation Double tube steam generator
US5044427A (en) * 1990-08-31 1991-09-03 Phillips Petroleum Company Heat exchanger
US5871045A (en) * 1995-07-01 1999-02-16 Bdag Balcke-Durr Aktiengesellschaft Heat exchanger
US5771963A (en) * 1995-12-05 1998-06-30 Asea Brown Boveri Ag Convective countercurrent heat exchanger
US6019070A (en) * 1998-12-03 2000-02-01 Duffy; Thomas E. Circuit assembly for once-through steam generators
US20030051501A1 (en) * 2001-09-18 2003-03-20 Hitoshi Matsushima Laminated heat exchanger and refrigeation cycle
US20030178185A1 (en) * 2002-03-22 2003-09-25 Wanni Amar S. Heat exchanger with reduced fouling
US6820685B1 (en) * 2004-02-26 2004-11-23 Baltimore Aircoil Company, Inc. Densified heat transfer tube bundle
US7533633B2 (en) * 2004-07-05 2009-05-19 Hitachi Power Europe Gmbh Establishing a connection between steam generator heating surfaces and a collector and/or distributor
US8708035B2 (en) * 2008-09-08 2014-04-29 Balcke-Dürr GmbH Heat exchanger in a modular construction
US20130192586A1 (en) * 2011-07-29 2013-08-01 David T. Wasyluk Shop assembled vertical serpentine flow molten salt solar receiver

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104949150A (zh) * 2015-07-03 2015-09-30 哈尔滨哈锅锅炉工程技术有限公司 一种锅炉管式空气预热器管箱与连通箱的连接结构
US11283400B2 (en) 2018-08-11 2022-03-22 Tyll Solar, Llc Solar energy system
US11870392B2 (en) 2018-08-11 2024-01-09 Tyll Solar, Llc Solar energy system
US11739931B2 (en) 2018-10-01 2023-08-29 Header-coil Company A/S Heat exchanger, such as for a solar power plant
CN111912260A (zh) * 2020-06-24 2020-11-10 哈尔滨汽轮机厂辅机工程有限公司 一种集预热、蒸发、过热为一体的换热设备

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EP2322854A1 (de) 2011-05-18
CN102667338B (zh) 2015-02-11
MA33812B1 (fr) 2012-12-03
EP2322854B1 (de) 2013-09-04
WO2011060870A1 (de) 2011-05-26
AU2010321334B2 (en) 2015-12-03
CN102667338A (zh) 2012-09-12
PT2322854E (pt) 2013-09-12
ES2435550T3 (es) 2013-12-20
KR20120117748A (ko) 2012-10-24
ZA201203459B (en) 2013-01-31
AU2010321334A1 (en) 2012-06-14

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