US20110315094A1 - Continuous Evaporator - Google Patents

Continuous Evaporator Download PDF

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Publication number
US20110315094A1
US20110315094A1 US13/254,188 US201013254188A US2011315094A1 US 20110315094 A1 US20110315094 A1 US 20110315094A1 US 201013254188 A US201013254188 A US 201013254188A US 2011315094 A1 US2011315094 A1 US 2011315094A1
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US
United States
Prior art keywords
steam generation
generation tubes
tubes
evaporator
mass flow
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
US13/254,188
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English (en)
Inventor
Jan Brückner
Joachim Franke
Gerhard Schlund
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.)
Siemens AG
Original Assignee
Siemens 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 Siemens AG filed Critical Siemens AG
Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: FRANKE, JOACHIM, BUECKNER, JAN, SCHLUND, GERHARD
Publication of US20110315094A1 publication Critical patent/US20110315094A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
    • F22B1/1815—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines using the exhaust gases of gas-turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B21/00—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically
    • F22B21/02—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from substantially straight water 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
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/62—Component parts or details of steam boilers specially adapted for steam boilers of forced-flow type
    • 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
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/4935—Heat exchanger or boiler making

Definitions

  • the invention relates to a method for designing a once-through evaporator and to a once-through evaporator for a horizontally constructed waste heat steam generator with a first evaporator heating surface which incorporates a number of first steam generation tubes, the arrangement of which is essentially vertical and through which the flow is from the bottom to the top, and another second evaporator heating surface, which on the flow substance side is connected downstream from the first evaporator heating surface, which incorporates a further number of second steam generation tubes the arrangement of which is essentially vertical and through which the flow is from the bottom to the top.
  • the heat contained in the expanded working substance or heating gas from the gas turbine is utilized for the generation of steam for the steam turbine.
  • the heat transfer is effected in a waste heat steam generator connected downstream from the gas turbine, in which it is usual to arrange a number of heating surfaces for the purpose of preheating water, for steam generation and for superheating steam.
  • the heating surfaces are connected into the water-steam circuit of the steam turbine.
  • the water-steam circuit usually incorporates several, e.g. three, pressure stages, where each of the pressure stages can have an evaporator heating surface.
  • a design as a once-through steam generator For the steam generator connected downstream on the heating gas side from the gas turbine as a waste heat steam generator, several alternative design concepts can be considered, namely a design as a once-through steam generator, or a design as a recirculatory steam generator.
  • a once-through steam generator the heating up of steam generation tubes, which are provided as evaporation tubes, results in the flow substance being evaporated in a single pass through the steam generation tubes.
  • the water which is fed around the circulation is only partially evaporated during its passage through the evaporator tubes. After the steam which has been generated has been separated off, the water which has not yet been evaporated is then fed once more to the same evaporator tubes for further evaporation.
  • a once-through steam generator is not subject to any pressure limitations.
  • a high live steam pressure favors a high thermal efficiency, and hence low CO 2 emissions from a fossil-fuel fired power station.
  • a once-through steam generator has, by comparison with a recirculatory steam generator, a simple construction and can thus be manufactured at particularly low cost.
  • the use of a steam generator, designed in accordance with the once-through principle, as the waste heat steam generator for a combined cycle gas turbine plant is therefore particularly favorable for the achievement of a high overall efficiency for the combined cycle gas turbine plant together with simple construction.
  • a once-through steam generator which is designed as a waste heat steam generator can basically be engineered in one of two alternative forms of construction, namely as a vertical construction or as a horizontal construction.
  • a once-through steam generator with a horizontal construction is then designed so that the heating substance or heating gas, for example the exhaust gas from the gas turbine, flows through it in an approximately horizontal direction, whereas a once-through steam generator with a vertical construction is designed so that the heating substance flows through it in an approximately vertical direction.
  • a once-through steam generator with a horizontal construction can be manufactured with particularly simple facilities, and with particularly low manufacturing and assembly costs.
  • an uneven distribution of the flow substance can arise across the steam generation tubes, in particular within each individual row of tubes in the steam generation tubes of the second evaporator heating surface, said tubes being connected downstream on the flow substance side, leading to temperature imbalances and, because of different thermal expansions, to mechanical stresses.
  • expansion bends for example, have hitherto been incorporated to compensate for these stresses, in order to avoid damage to the waste heat steam generator.
  • this measure can be technically comparatively expensive in the case of a waste heat steam generator with a horizontal construction.
  • the object underlying the invention is thus to specify a method for designing a once-through evaporator together with a once-through evaporator, for a waste heat steam generator of the type identified above, which has a particularly long service life while permitting a particularly simple construction.
  • this object is achieved in accordance with the invention in that a minimum mass flow density is prescribed and the second steam generation tubes are designed in such a way that the mean mass flow density which is established through the second steam generation tubes when operating at full load does not fall below the prescribed minimum mass flow density.
  • the invention then starts from the consideration that it would be possible to achieve a particularly simple construction for the waste heat steam generator or once-through evaporator, as applicable, by the elimination of the previously-usual expansion bends. In doing so however, the mechanical stresses caused by the temperature imbalances in the steam generation tubes which are connected in parallel with one another in each individual row must be reduced in some other way. These occur, in particular, in the second evaporator surface, to which is admitted a water-steam mixture.
  • the temperature imbalances are here caused by the different proportions of water and steam at the flow side entry to the individual tubes in a row of tubes, and the resulting different through-flow through these tubes.
  • a static stabilization of the flow and at the same time a particularly simple construction for the waste heat steam generator, can be achieved by direct modification of the parameters of the steam generation tubes in the second evaporator heating surface.
  • a reduction in the temperature imbalances can be achieved by designing the second steam generation tubes in such a way that the mean mass flow density which is established through the second steam generation tubes when operating at full load does not fall below a prescribed minimum mass flow density.
  • the value of the prescribed minimum mass flow density is 180 kg/m 2 s. That is, a design of the steam generation tubes to achieve such a choice of mass flow density leads to a particularly good static stabilization of the flow in each individual row of tubes in the second evaporator heating surface, and hence to a particularly good equalization of the temperature in steam generation tubes which are connected in parallel in each individual row of tubes in the second evaporator heating surface.
  • this different mass flow density in the tubes is caused by a frictional pressure loss in the steam generation tubes which is small by comparison with the geodetic pressure loss. That is, a flow which has a high proportion of steam in the flow substance flows through individual steam generation tubes comparatively fast with a low frictional pressure loss, whereas a flow with a high proportion of water is disadvantaged by its greater geodetic pressure loss, caused by its mass, and can tend towards stagnation. In order to even out the through-flows, the frictional pressure loss should therefore be increased. This can be achieved in that the internal diameter of the second steam generation tubes is advantageously chosen in such a way that the mean mass flow density which is established when operating at full load does not fall below the prescribed minimum mass flow density.
  • the objective is further achieved by a once-through evaporator designed in accordance with the method cited above.
  • a reduction in the internal diameter for ensuring a minimum mass flow should not, however, be taken arbitrarily far.
  • the surface of the steam generation tubes must permit adequate heat input.
  • the steam generation tubes often also have external ribbing, which in turn requires a certain minimum diameter.
  • a minimum thickness is also required on grounds of rigidity and stability.
  • the internal diameter of the second steam generation tubes should advantageously not be less than a minimum diameter, determined by reference to prescribed operating parameters.
  • the internal diameter of the second steam generation tubes is then between 20 mm and 40 mm. That is, a choice of internal diameter in this range determines the mass flow density in the second steam generation tubes to be such that the frictional pressure loss in the steam generation tubes lies within a range for which a through-flow with a high proportion of water and a through-flow with a high proportion of steam lead to exit temperatures with comparatively small temperature differences. Consequently, the temperature differences within each row of tubes in the second evaporator heating surface are minimized, whereby the other operating prerequisites are satisfied at the same time.
  • a number of second steam generation tubes are connected one after another on the heating gas side as rows of tubes.
  • the steam generation tubes which are arranged one after another in the direction of flow of the heating gas are then differently heated. Particularly in the steam generation tubes on the heating gas entry side, the flow substance is comparatively strongly heated.
  • a through-flow which is matched to the heating can also be achieved in these steam generation tubes, by the design described for the steam generation tubes such that the mass flow density at full load does not drop below a minimum value. By this means, a particularly long service life is achieved for the waste heat steam generator by a simple construction.
  • the first evaporator heating surface is connected downstream from the second evaporator heating surface on the heating gas side.
  • the second evaporator heating surface which is connected downstream on the flow substance side and is thus designed to further heat up a flow substance which has already been evaporated, also lies in a comparatively more strongly heated region of the heating gas duct.
  • a once-through evaporator of this type can expediently be used in a waste heat steam generator, and the waste heat steam generator used in a combined cycle gas turbine plant.
  • the steam generator downstream on the heating gas side from a gas turbine it is advantageous to connect the steam generator downstream on the heating gas side from a gas turbine.
  • a supplementary heat source can expediently be arranged behind the gas turbine, to raise the heating gas temperature.
  • the advantages achieved by the invention consist, in particular, in the fact that designing the second steam generation tubes in such a way that the mean mass flow density established through the second steam generation tubes when operating at full load does not fall below a prescribed minimum mass flow density achieves a static stabilization of the flow, and thus a reduction in the temperature differences between steam generation tubes connected in parallel and in the mechanical stresses which result therefrom.
  • This makes the service life of the waste heat steam generator particularly long.
  • An appropriate design of steam generation tubes enables further expensive technical measures such as expansion bends to be foregone, and thus at the same time permits a particularly simple cost-saving construction for the waste heat steam generator or combined cycle gas turbine power station, as applicable.
  • FIGURE here shows a simplified representation of a longitudinal section through a steam generator with a horizontal construction.
  • the once-through steam generator 1 for the waste heat steam generator 2 shown in the FIG. is connected downstream from a gas turbine, not shown here in more detail, on its exhaust gas side.
  • the waste heat steam generator 2 has a surrounding wall 3 which forms a heating gas duct 5 through which the exhaust gas from the gas turbine can flow in an approximately horizontal direction as heating gas, as indicated by the arrows 4 .
  • Arranged in the heating gas duct 5 is a number of evaporator heating surfaces 8 , 10 , designed according to a once-through principle. In the exemplary embodiment shown in the FIG., each of two evaporator heating surfaces 8 , 10 is shown, but a larger number of evaporator heating surfaces could also be provided.
  • Each of the evaporator heating surfaces 8 , 10 shown in the FIG. incorporates a number of rows of tubes, 11 and 12 respectively, each in the nature of a nest of tubes, arranged behind each other in the direction of the heating gas.
  • Each row of tubes 11 , 12 incorporates in turn a number of steam generation tubes, 13 and 14 respectively, in each case arranged beside each other in the direction of the heating gas, of which in each case only one can be seen for each row of tubes 11 , 12 .
  • the first steam generation tubes 13 of the first evaporator heating surface 8 which are arranged approximately vertically and connected in parallel so that a flow substance W can flow through them, are here connected on their output sides to an outlet collector 15 which is common to them.
  • the second steam generation tubes 14 of the second evaporator heating surface 10 which are also arranged approximately vertically and connected in parallel so that a flow substance W can flow through them, are also connected on their output sides to an outlet collector 16 which is common to them.
  • a comparatively expensive collection system could also be provided for both the evaporator heating surfaces 8 , 10 .
  • the steam generation tubes 14 of the second evaporator heating surface 10 are connected downstream from the steam generation tubes 13 of the first evaporator heating surface 8 , via a downpipe 17 .
  • the evaporation system formed by the evaporator heating surfaces 8 , 10 can have admitted to it the flow substance W which, in a single pass through the evaporation system, is evaporated and after it emerges from the second evaporator heating surface 10 is fed away as steam D.
  • the evaporation system formed by the evaporator heating surfaces 8 , 10 is connected into a steam turbine's water-steam circuit, which is not shown in more detail.
  • the water-steam circuit of the steam turbine has connected into it a number of other heating surfaces 20 , indicated schematically in the FIG.
  • the heating surfaces 20 could be, for example, superheaters, medium-pressure evaporators, low-pressure evaporators and/or preheaters.
  • the second steam generation tubes 14 are now designed in such a way that the mass flow density does not fall below a minimum prescribed for full load as 180 kg/m 2 s.
  • their internal diameter is between 20 mm and 40 mm so that, on the one hand, the required operating parameters such as rigidity, heat input etc. are satisfied and, on the other hand, temperature imbalances within a row of tubes in the second evaporator heating surface 10 are minimized. This reduces the mechanical stress loadings on the waste heat steam generator 2 , guaranteeing a particularly long service life and at the same time a simple construction due to the elimination of the previously usual expansion bends.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Thermal Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Heat Treatment Of Water, Waste Water Or Sewage (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
US13/254,188 2009-03-09 2010-02-09 Continuous Evaporator Abandoned US20110315094A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102009012321.0 2009-03-09
DE102009012321A DE102009012321A1 (de) 2009-03-09 2009-03-09 Durchlaufverdampfer
PCT/EP2010/051534 WO2010102869A2 (de) 2009-03-09 2010-02-09 Durchlaufverdampfer

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US20110315094A1 true US20110315094A1 (en) 2011-12-29

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US13/254,188 Abandoned US20110315094A1 (en) 2009-03-09 2010-02-09 Continuous Evaporator

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US (1) US20110315094A1 (zh)
EP (1) EP2409078B1 (zh)
JP (1) JP2012519831A (zh)
KR (1) KR101662348B1 (zh)
CN (1) CN102753891B (zh)
AR (1) AR080536A1 (zh)
AU (1) AU2010223502A1 (zh)
BR (1) BRPI1009427A2 (zh)
CA (1) CA2754669A1 (zh)
DE (1) DE102009012321A1 (zh)
ES (1) ES2582029T3 (zh)
PL (1) PL2409078T3 (zh)
RU (1) RU2011140815A (zh)
TW (1) TWI529349B (zh)
WO (1) WO2010102869A2 (zh)
ZA (1) ZA201105820B (zh)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110197830A1 (en) * 2008-09-09 2011-08-18 Brueckner Jan Continuous steam generator
CN105258094A (zh) * 2015-11-13 2016-01-20 江苏绿叶锅炉有限公司 燃气自然循环余热锅炉
CN110094709A (zh) * 2019-05-28 2019-08-06 上海锅炉厂有限公司 一种直流式蒸发器及其设计方法

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CN102753891A (zh) 2012-10-24
RU2011140815A (ru) 2013-04-20
CN102753891B (zh) 2015-02-11
KR20110128850A (ko) 2011-11-30
AR080536A1 (es) 2012-04-18
EP2409078B1 (de) 2016-04-13
WO2010102869A2 (de) 2010-09-16
KR101662348B1 (ko) 2016-10-04
BRPI1009427A2 (pt) 2016-03-01
CA2754669A1 (en) 2010-09-16
DE102009012321A1 (de) 2010-09-16
TWI529349B (zh) 2016-04-11
JP2012519831A (ja) 2012-08-30
ES2582029T3 (es) 2016-09-08
EP2409078A2 (de) 2012-01-25
PL2409078T3 (pl) 2016-10-31
TW201043872A (en) 2010-12-16
ZA201105820B (en) 2012-04-25
AU2010223502A1 (en) 2011-09-29

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