US3842605A - Method and apparatus for regenerative heating in thermal power plants - Google Patents

Method and apparatus for regenerative heating in thermal power plants Download PDF

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Publication number
US3842605A
US3842605A US00118621A US11862171A US3842605A US 3842605 A US3842605 A US 3842605A US 00118621 A US00118621 A US 00118621A US 11862171 A US11862171 A US 11862171A US 3842605 A US3842605 A US 3842605A
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United States
Prior art keywords
vapor
high pressure
turbine
generator
pressure
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Expired - Lifetime
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US00118621A
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English (en)
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E Tegtmeyer
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Individual
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Priority to US00118621A priority Critical patent/US3842605A/en
Priority to BE773876A priority patent/BE773876A/fr
Priority to IT30966/71A priority patent/IT940531B/it
Priority to CA132,338A priority patent/CA972974A/en
Priority to DE19722201397 priority patent/DE2201397A1/de
Priority to CH121272A priority patent/CH547944A/xx
Priority to NL7202367A priority patent/NL7202367A/xx
Priority to GB837672A priority patent/GB1377548A/en
Priority to FR7206276A priority patent/FR2127769A5/fr
Priority to SE02399/72A priority patent/SE368982B/xx
Application granted granted Critical
Publication of US3842605A publication Critical patent/US3842605A/en
Priority to JP1979167631U priority patent/JPS5585507U/ja
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/22—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type the turbines having inter-stage steam heating
    • 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
    • F01K19/00—Regenerating or otherwise treating steam exhausted from steam engine plant
    • F01K19/02—Regenerating by compression
    • 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
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • F01K7/40—Use of two or more feed-water heaters in series
    • 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
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • F01K7/44—Use of steam for feed-water heating and another purpose

Definitions

  • ABSTRACT A method and apparatus is herein provided for power plants which improves the useful life thereof by increasing their operating efficiency above that heretofore obtained, and at the same time achieving a sub- 1" spas; s rew 39 cot/113 a o 22 -4- I COOLING WATER L P /5 attests t HE HEATER HTR 30 HTR COBlI ISZNPSATE 26 BOILER FEED DRAIN PUMP 3/1971 Harris 60/65 METHOD AND APPARATUS FOR REGENERATIVE HEATING llN THERMAL POWER PLANTS BACKGROUND OF THE INVENTION
  • Conventional power plants consist of a steam generator, using either fossil-fuel or nuclear fuel, that supplies steam to a multi-stage turbine-generator exhausting to a condenser at high vacuum.
  • the condensate therefrom is pumped through a number of feedwater heaters that utilize steam extracted from progressively higher pressure stages of the turbine, until the final feedwater temperature is increased as high as possible consistent with design of the steam generator, or economic considerations of the cycle.
  • feedwater heaters that utilize steam extracted from progressively higher pressure stages of the turbine, until the final feedwater temperature is increased as high as possible consistent with design of the steam generator, or economic considerations of the cycle.
  • regenerative feedwater heating results in a high cycle efficiency being primarily dependent upon the number of extraction points and feedwater heaters that it is economically feasible to utilize.
  • thermodynamic gain progressively diminishes with each additional feedwater heater that is added to the cycle. This is because of the fact that as the turbine extraction point moves closer to turbine throttle pressure, the steam passes through a smaller portion of the turbine resulting in less work, before it is extracted and condensed in the feedwater heater. It is therefore obvious that if turbine throttle pressure were used for this purpose there would be no thermodynamic gain whatsoever and there exists an economic point, dependent on fuel costs, at which the capital costs of additional feedwater heaters in the cycle would become greater than the thermodynamic gain achieved over the expected useful life of the power plant.
  • Another object of the present invention is the provision of a power plant wherein a plurality of the higher pressure conventional extraction feedwater heaters are eliminated from the turbine cycle as well as all associated high pressure turbine extraction sources.
  • Another object of the present invention is the provision of a high efficiency power plant wherein a high pressure feedwater heater is provided which is supplied with vapor at suitable pressure-temperature conditions from a vapor compressor to achieve the desired final feedwater temperature.
  • Another object of the present invention is the provision of a high efficiency power plant wherein a compressor is utilized to supply suitable high pressure and high temperature vapor to a feedwater heater and wherein the low pressure vapor supplied to said compressor is extracted from the power-plant turbines after the greatest part of the available work energy of such vapor has been utilized to produce work within the turbines.
  • FIGURE is a diagrammatic illustration of a power plant in accordance with the present invention, wherein a compressor is employed to compress relatively low pressure extraction vapor from the turbine after its greatest work energy has been utilized in such turbine, thereby eliminating the conventional high pressure turbineextraction sources for feedwater heating that decreases the work availability of such vapor within the turbine.
  • a vapor generator 5 is diagrammatically shown in the FIGURE wherein vapor, such as steam, is produced and supplied to a turbine throttle valve 6 at a high pressure and high temperature. From the throttle valve 6 such steam expands through a high pressure turbine 7. Since this turbine 7 is devoid of the former conventional high pressure extraction sources A and B for feedwater heating, the steam that otherwise would have been extracted now performs additional work within such turbine before exhausting and passing to a reheater 8 located within the steam generator 5 wherev such steam is reheated again to a high temperature. l
  • This reheated steam then flows through an intercept valve 9, where its expanded flow passes through tandem connected intermediate pressure turbine 10, also devoid of former conventional, high pressure extraction sources C and D for feedwater heating which again produces the aforementioned increased work performance, and then flows'through a tandem connected low pressure turbine 12 from which it exhausts to a condenser 13 at a high vacuum.
  • the work energy resulting from the expanding steam passing through the tandem turbine sections 7, 10 and 12, drives an electric generator 14 coupled to these turbines, resulting in conversion of the energy into electrical power at high efficiency.
  • the vapor-liquid, or feedwater, regenerative cycle is performed by apparatus comprising a condensate pump 15 which removes the condensate feedwater from the condenser 13 and pumps it through low pressure heaters 16 and 17 into a deaerating feedwater heater 18, with such heaters receiving extraction steam pressure from points of the low pressure turbine 12 through lines 19 and 20, respectively. Since the deaerating feedwater heater 18 is also connected by a line 22 to the low pressure turbine 12, the condensatefeedwater is accordingly heated to the saturation temperature corresponding to the extraction steam pressure from another point of the low pressure turbine 12.
  • This heated condensate-feedwater is removed from the deaerating feedwater heater 18 by a boiler feed pump 23 and forced through a high pressure heater 24 to the steam generator 5, at a sufficiently high discharge pressure to overcome piping, heat exchanger and boiler internal resistances.
  • the high pressure heater 24 is sup plied with steam from a steam compressor 25 also connected to the low-pressure turbine 12 by a line 26, which thus imparts to the steam supplied to the steam generator 5 a pressure and saturation temperature equal to or greater than that normally heretofore supplied from the highest pressure extraction source of a steam turbine.
  • the steam compressor 25 receives steam from the low pressure turbine 12 at approximately 15 p.s.i.a. and compresses it to about 900 p'.s.i.a. corresponding to a saturation temperature of 532F which, neglecting superheat in the compressed steam, would result in heating the feedwater flowing through high pressure heater 24, to this saturation temperature of about 532F when supplied to the steam generator 5.
  • the steam compressor 25 may alternatively be equipped with an intercooler 31 and/or an aftercooler 32.
  • Either the intercooler 31 or the aftercooler 32 or both receive cooling steam by line 33 through valve 38 or by line 35 through valve 37 which is in turn heated by exchange with the hotter compressed steam in the intercooler 31 or aftercooler 32 and subsequently recycled by line 34 through valve 39 or by line 36 through valve 40 to a point in the turbine cycle downstream of the point from which the cooler high pressure discharged steam was received, thus imparting additional useful heat to the intermediate pressure and/or low pressure turbines.
  • Drains from the high pressure heater 24 flow through a drain line 27 to the deaerating feedwater heater 18, and similarly drains from low pressure heater l7 flow through a drain line 28 to low pressure heater 16, from which such drains are drawn by a drain pump 29 and returned to the feedwater system through a line 30.
  • the gain in additional work within the turbines is substantially greater than the work required to compress the low pressure extraction steam to the same pressure-temperature levels that otherwise would be required by direct extraction to feedwater heaters at these same relatively high levels.
  • the net gain in cycle efficiency results in a corresponding reduction in atmospheric pollution from fossil-fuel plants.
  • the vapor compression principle of the present invention can be used advantageously for vapor reheating, especially in nuclear installations where vapor is supplied to the turbine throttle at saturated conditions and the moisture resulting from expansion of the vapor through moisture regions produces a reduction of turbine efficiency.
  • Such vapor compression not only reduces losses due to moisture in the vapor but also can provide one or more stages of reheat, thus establishing a higher reheat gain factor than is economically possible with initial saturated vapor as presently utilized for conventional saturated vapor nuclear installations.
  • the method of operating a vapor-liquid cycle power plant for the production of energy output at high efficiency comprising a turbine cycle of low and high pressure and a vapor generator comprising:
  • a high pressure turbine connected to said vapor generator for passing of the high pressure and temperature vapor therethrough to cause operation of said high pressure turbine andthe passage of the exhaust vapor therefrom back to said high pressure vapor generator for reheating
  • tandem connected intermediate pressure turbine and a low pressure turbine with said intermediate pressure turbine being connected to said vapor generator and operable upon the passage of high pressure vapor progressively through said tandem connected intermediate pressure and low pressure turbines, as well as through said high pressure turbine, to cause operation of an electrical generator;
  • a high pressure heater connected to said deaerating' feedwater heater and to said vapor generator
  • a compressor operable to supply high pressure and high temperature vapor to said high pressure heater, to cause the liquid passing therethrough to be substantially raised in temperature and pressure when supplied to said vapor generator.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
US00118621A 1971-02-25 1971-02-25 Method and apparatus for regenerative heating in thermal power plants Expired - Lifetime US3842605A (en)

Priority Applications (11)

Application Number Priority Date Filing Date Title
US00118621A US3842605A (en) 1971-02-25 1971-02-25 Method and apparatus for regenerative heating in thermal power plants
BE773876A BE773876A (fr) 1971-02-25 1971-10-13 Procede et appareil pour le chauffage a regeneration dans les centralesthermiques
IT30966/71A IT940531B (it) 1971-02-25 1971-11-11 Metodo e impianto per riscaldamento rigenerativo in impianti termici di produzione di energia
CA132,338A CA972974A (en) 1971-02-25 1972-01-13 Method and apparatus for regenerative heating in thermal power plants
DE19722201397 DE2201397A1 (de) 1971-02-25 1972-01-13 Verfahren und Vorrichtung zur regenerativen Vorwaermung bei Waermekraftwerken
CH121272A CH547944A (de) 1971-02-25 1972-01-27 Dampfkraftanlage mit einem dampferzeuger und verfahren zum betrieb der dampfkraftanlage.
NL7202367A NL7202367A (fr) 1971-02-25 1972-02-23
GB837672A GB1377548A (en) 1971-02-25 1972-02-23 Thermal power plants
FR7206276A FR2127769A5 (fr) 1971-02-25 1972-02-24
SE02399/72A SE368982B (fr) 1971-02-25 1972-02-25
JP1979167631U JPS5585507U (fr) 1971-02-25 1979-12-05

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00118621A US3842605A (en) 1971-02-25 1971-02-25 Method and apparatus for regenerative heating in thermal power plants

Publications (1)

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US3842605A true US3842605A (en) 1974-10-22

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US00118621A Expired - Lifetime US3842605A (en) 1971-02-25 1971-02-25 Method and apparatus for regenerative heating in thermal power plants

Country Status (11)

Country Link
US (1) US3842605A (fr)
JP (1) JPS5585507U (fr)
BE (1) BE773876A (fr)
CA (1) CA972974A (fr)
CH (1) CH547944A (fr)
DE (1) DE2201397A1 (fr)
FR (1) FR2127769A5 (fr)
GB (1) GB1377548A (fr)
IT (1) IT940531B (fr)
NL (1) NL7202367A (fr)
SE (1) SE368982B (fr)

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3992884A (en) * 1975-01-03 1976-11-23 Fives-Cail Babcock Thermal power plant
US4047386A (en) * 1976-06-10 1977-09-13 Scm Corporation Process for heating condensate
US4110987A (en) * 1977-03-02 1978-09-05 Exxon Research & Engineering Co. Thermal energy storage by means of reversible heat pumping utilizing industrial waste heat
US4637350A (en) * 1984-09-28 1987-01-20 Hitachi, Ltd. System for recovering drain
US4763480A (en) * 1986-10-17 1988-08-16 Kalina Alexander Ifaevich Method and apparatus for implementing a thermodynamic cycle with recuperative preheating
US7040095B1 (en) * 2004-09-13 2006-05-09 Lang Fred D Method and apparatus for controlling the final feedwater temperature of a regenerative rankine cycle
WO2010086898A1 (fr) * 2009-01-30 2010-08-05 日立Ｇｅニュークリア・エナジー株式会社 Centrale électrique, et procédé de fonctionnement de la centrale électrique
WO2010086897A1 (fr) * 2009-01-30 2010-08-05 株式会社日立製作所 Installation utilisant de la vapeur, procédé d'exploitation de l'installation, appareil d'alimentation de vapeur et procédé d'alimentation de vapeur
US20110283704A1 (en) * 2009-01-30 2011-11-24 Hitachi, Ltd. Power Plant
US8091361B1 (en) * 2007-11-05 2012-01-10 Exergetic Systems, Llc Method and apparatus for controlling the final feedwater temperature of a regenerative Rankine cycle using an exergetic heater system
US20120167568A1 (en) * 2009-09-23 2012-07-05 Carsten Graeber Steam power plant
US8222504B1 (en) 2011-04-20 2012-07-17 Ernie Ball Inc. Musical instrument string having cobalt alloy wrap wire
US20120297771A1 (en) * 2011-05-27 2012-11-29 General Electric Company Variable feedwater heater cycle
US20140318130A1 (en) * 2011-12-19 2014-10-30 Suez Environment Cogeneration method and equipment
US20150052894A1 (en) * 2011-10-07 2015-02-26 IFP Energies Nouvelles Ocean thermal energy conversion method and system
CN115929430A (zh) * 2022-12-21 2023-04-07 东方电气集团东方汽轮机有限公司 一种工业供热汽轮机回热系统

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5178575B2 (ja) * 2009-02-23 2013-04-10 株式会社日立製作所 発電プラント給水装置及び制御方法
CN112780373B (zh) * 2020-12-30 2022-11-11 华北电力大学（保定） 一种基于超、亚临界回热的水蒸汽循环

Cited By (24)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3992884A (en) * 1975-01-03 1976-11-23 Fives-Cail Babcock Thermal power plant
US4047386A (en) * 1976-06-10 1977-09-13 Scm Corporation Process for heating condensate
US4110987A (en) * 1977-03-02 1978-09-05 Exxon Research & Engineering Co. Thermal energy storage by means of reversible heat pumping utilizing industrial waste heat
US4637350A (en) * 1984-09-28 1987-01-20 Hitachi, Ltd. System for recovering drain
US4763480A (en) * 1986-10-17 1988-08-16 Kalina Alexander Ifaevich Method and apparatus for implementing a thermodynamic cycle with recuperative preheating
US7040095B1 (en) * 2004-09-13 2006-05-09 Lang Fred D Method and apparatus for controlling the final feedwater temperature of a regenerative rankine cycle
US8091361B1 (en) * 2007-11-05 2012-01-10 Exergetic Systems, Llc Method and apparatus for controlling the final feedwater temperature of a regenerative Rankine cycle using an exergetic heater system
WO2010086898A1 (fr) * 2009-01-30 2010-08-05 日立Ｇｅニュークリア・エナジー株式会社 Centrale électrique, et procédé de fonctionnement de la centrale électrique
US20110005225A1 (en) * 2009-01-30 2011-01-13 Hitachi-Ge Nuclear Energy, Ltd. Electric Power Plant, and Method for Running Electric Power Plant
US20110283704A1 (en) * 2009-01-30 2011-11-24 Hitachi, Ltd. Power Plant
WO2010086897A1 (fr) * 2009-01-30 2010-08-05 株式会社日立製作所 Installation utilisant de la vapeur, procédé d'exploitation de l'installation, appareil d'alimentation de vapeur et procédé d'alimentation de vapeur
US8448439B2 (en) * 2009-01-30 2013-05-28 Hitachi-Ge Nuclear Energy, Ltd. Electric power plant, and method for running electric power plant
US8695347B2 (en) * 2009-01-30 2014-04-15 Hitachi, Ltd. Power plant
JP5134090B2 (ja) * 2009-01-30 2013-01-30 日立Ｇｅニュークリア・エナジー株式会社 発電プラント及び発電プラントの運転方法
US20120167568A1 (en) * 2009-09-23 2012-07-05 Carsten Graeber Steam power plant
US8222504B1 (en) 2011-04-20 2012-07-17 Ernie Ball Inc. Musical instrument string having cobalt alloy wrap wire
US20120297771A1 (en) * 2011-05-27 2012-11-29 General Electric Company Variable feedwater heater cycle
US9297278B2 (en) * 2011-05-27 2016-03-29 General Electric Company Variable feedwater heater cycle
US20150052894A1 (en) * 2011-10-07 2015-02-26 IFP Energies Nouvelles Ocean thermal energy conversion method and system
US9835143B2 (en) * 2011-10-07 2017-12-05 IFP Energies Nouvelles Ocean thermal energy conversion method and system
US20140318130A1 (en) * 2011-12-19 2014-10-30 Suez Environment Cogeneration method and equipment
US9399931B2 (en) * 2011-12-19 2016-07-26 Suez Environment Cogeneration method and equipment
CN115929430A (zh) * 2022-12-21 2023-04-07 东方电气集团东方汽轮机有限公司 一种工业供热汽轮机回热系统
CN115929430B (zh) * 2022-12-21 2024-06-07 东方电气集团东方汽轮机有限公司 一种工业供热汽轮机回热系统

Also Published As

Publication number Publication date
JPS5585507U (fr) 1980-06-12
GB1377548A (en) 1974-12-18
NL7202367A (fr) 1972-08-29
IT940531B (it) 1973-02-20
CH547944A (de) 1974-04-11
DE2201397A1 (de) 1972-09-07
FR2127769A5 (fr) 1972-10-13
SE368982B (fr) 1974-07-29
BE773876A (fr) 1972-01-31
CA972974A (en) 1975-08-19

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