EP0032641A1 - System zur Wiedererwärmung für eine Dampfturbinenkraftanlage - Google Patents

System zur Wiedererwärmung für eine Dampfturbinenkraftanlage Download PDF

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Publication number
EP0032641A1
EP0032641A1 EP80400077A EP80400077A EP0032641A1 EP 0032641 A1 EP0032641 A1 EP 0032641A1 EP 80400077 A EP80400077 A EP 80400077A EP 80400077 A EP80400077 A EP 80400077A EP 0032641 A1 EP0032641 A1 EP 0032641A1
Authority
EP
European Patent Office
Prior art keywords
heater
turbine
steam
phase
condensates
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.)
Granted
Application number
EP80400077A
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English (en)
French (fr)
Other versions
EP0032641B1 (de
Inventor
André Jules Paquet
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.)
Hamon Sobelco SA
Original Assignee
Hamon Sobelco SA
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 Hamon Sobelco SA filed Critical Hamon Sobelco SA
Priority to EP80400077A priority Critical patent/EP0032641B1/de
Priority to AT80400077T priority patent/ATE22152T1/de
Priority to DE8080400077T priority patent/DE3071745D1/de
Priority to US06/199,193 priority patent/US4408460A/en
Priority to AU63856/80A priority patent/AU537612B2/en
Priority to JP18270780A priority patent/JPS56124611A/ja
Priority to ZA00810290A priority patent/ZA81290B/xx
Publication of EP0032641A1 publication Critical patent/EP0032641A1/de
Application granted granted Critical
Publication of EP0032641B1 publication Critical patent/EP0032641B1/de
Expired 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
    • F01K7/34—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

Definitions

  • the present invention relates to condensed water heating systems used in steam turbine energy production installations such as power plants.
  • reheating systems generally comprise a certain number of reheaters arranged between the condenser and the steam generator of the installation for reheating the water condensed in the condenser and supplied with steam at different pressures by respective withdrawals on the turbine. Between some of the heaters and the immediately adjacent heater supplied by a vapor withdrawal at a lower pressure is disposed a phase separator receiving the mixture. steam-water from the heater purge associated with the higher pressure racking and supplying the heater associated with the lower pressure racking, in parallel with this racking. lower pressure, with vapor separated from said mixture in the phase separator.
  • a superheater is provided, the condensates of which are sent to the heater associated with the highest pressure withdrawal via a phase separator.
  • the invention therefore aims to provide a heating system which allows part of this to be used. energy lost in the heating systems of the prior art so as to increase the overall energy efficiency of. the energy production installation with which the heating system is associated.
  • the invention also aims to provide a heating system for a steam turbine power plant which, while having better efficiency than the heating systems of the prior art, is of simpler construction than the latter.
  • Another object of the invention is to provide a heating system for a steam turbine energy production installation which at least partially avoids the erosion phenomena which are encountered in heating systems.
  • the invention achieves these aims thanks to the fact that the two-phase turbine produces mechanical energy by recovering the kinetic energy of the condensers of the exchanger by condensation which l 'feeds. This results in an increase in the energy efficiency of the installation with which the heating system according to the invention is associated and the elimination of erosion phenomena in the main control valve and the phase separator since these are eliminated at the profit from the biphasic turbine.
  • FIG. 1 there is shown the diagram of a conventional heating system with seven heaters R 1 , R 2 , R 3 , R 4 , R 5 , R 6 and R 7 .
  • the heaters R 1 to R 7 heat the condensed water and taken up by an extraction pump PE in the condenser (not shown) of the fossil-fuel power station and steam turbine with which this heating system is associated.
  • the heater R 1 is supplied from a racking S 1 with steam at 0.3 bar and at a flow rate representing 4.5% by weight of the total flow rate (100% by weight) supplied by the heater R 7 at steam generator (not shown) of the installation.
  • the vapor condensed in the heater R 1 is returned by a drain pipe P O to the condenser.
  • the second heater R 2 arranged in series in the main circuit CP of condensed water, downstream of the heater R 1 is supplied from a withdrawal S 2 with steam at a pressure of 1 bar, with a flow rate of 4, 5% by weight.
  • the third heater R 3 arranged downstream relative to R 2 on the circuit CP, is supplied from a racking S 3 with steam at a pressure of 2 bars, with a flow rate representing 3% by weight of the total flow rate.
  • the flow of the main circuit CP at the outlet of the heater R 3 which represents 75% by weight of the flow total at the outlet of the heater R 7 , is sent to a heater by mixing or degassing tank R 4 which is supplied from a racking S 4 with steam at a pressure of 4 bars and at a flow rate representing 3.5 % by weight of the total flow.
  • the water coming from the heater R 3 and the steam coming from the racking S 4 are mixed in the heater by mixing R 4 and this mixture is taken up by a food pump PA which sends it to the heater R 5 , which is supplied, at from a racking S 5 with steam at a pressure of 9 bars and at a flow rate representing 7% of the total flow.
  • the water leaving the heater R 5 is then sent to a heater R 6 which is supplied, from a racking S 6 , with steam at a pressure of 18 bars and at. a flow representing 7% of the total flow.
  • the water leaving the heater R 6 is further heated in the last heater R 7 which is supplied, from a racking S 7 , with steam at a pressure of 36 bars and at a flow rate representing 7.5 % by weight of the total flow.
  • the condensed water leaving the heater R 7 therefore represents, as indicated above, 100% of the total flow rate which is sent under a pressure of the order of 200 to 220 bars to the steam generator GV (not shown) of the installation where this water is vaporized to be returned to the turbine (not shown).
  • a motorized emergency regulating valve V 1 is connected in bypass with respect to the main regulating valve SR 1 on the drain pipe P 1 to return, if necessary, the condensates of the pipe of purge P 1 directly at condenser.
  • the regulation valves SR 1 and V 1 are controlled by a level regulator RN 1 intended to regulate the water level in the heater R 7 .
  • the mixture at 244 ° C of the purge line P is sent via the main control valve SR 1 into the phase separator SP which separates the water from the steam resulting from the expansion, the latter being sent by a CV line 1 on the steam side in the heater R 6 and the water being sent through a CE pipe on the water side in the heater R 6 .
  • the condensates collected in the heater R 6 are sent by a drain pipe P 2 to a phase separator SP 2 via a main control valve SR 2 with which is connected in parallel a motorized emergency control valve V 2 .
  • the condensates at 207 ° C of the drain pipe P 2 are separated in the phase separator SP 2 and the steam is sent by a pipe CV 2 on the steam side of the heater R 5 , while the water is sent by a pipe CE 2 water side of heater R 5 .
  • phase separator SP 2 as well as the regulation valves SR 2 and V 2 which are controlled by a level regulator RN 2 which regulates the water level in the heater R 6 , operate in the same way and play the same role as the phase separator SP and the regulation valves SR 1 and V 1 described above.
  • the condensates at 175 ° C collected in the heater R 5 are sent by a drain pipe P 3 to the heater by mixing R 4 , via a main regulating valve SR 3 with which a bypass valve is connected. motorized emergency control V 3 .
  • the valves SR 3 and V 3 are controlled by a level regulator RN 3 which regulates the level in the heater R 5 .
  • the mixture circulating in the drain line P 3 which represents 21.5% by weight of the total flow, is mixed in the degassing tank R 4 with the water coming from the heater R 3 and the steam coming from the withdrawal S 4 so that the food pump PA has a flow representing 100% of the total flow.
  • the condensates collected in the heater R 3 are sent by means of a drain pipe P 4 to a phase separator SP 3 , by means of a main regulating valve SR 4 with which a bypass valve is connected.
  • motorized emergency regulation V 4 which, like the valves V 1 , V 2 and V 3 , returns condensates directly to the condenser in the event of an incident.
  • the regulation valves SR 4 and V 4 are controlled by a level regulator RN 4 which regulates the water level in the heater R 3 .
  • the condensates at 120 ° C of the drain pipe P 4 are divided in the phase separator SP 3 , from where the steam is sent to the steam side of the heater R 2 by a pipe CV 3 while the water is sent to the water side of the heater R 2 by a pipe CE3.
  • the drain pipe P5 which collects the condensates at 100 ° C from the heater R 2 is connected in RA to a branch pipe CD which is connected between, on the one hand, the condenser and, on the other hand, the main line CP, between the heaters R 2 and R 3 .
  • a motorized emergency control valve V 5 is arranged in the bypass line CD between the RA connection and the condenser, and a main control valve SR 5 is arranged in the line CD between the RA connection and the line connection CD with the CP main line.
  • the regulation valves SR 5 and V5 are controlled by a level regulator RN 5 which regulates the water level in the heater R 2 .
  • a condensate recovery pump PR is placed in the line CD between the connection RA and the regulating valve SR 5 to re-inject the condensates from the drain line P5 into the main line CP. If the pump stops PR, the condensates are returned to the condenser by the emergency regulating valve V 5 .
  • part of the heat energy of the mixture from the heaters R 7 , R 6 , R 5 , R 3 and R 2 is used to heat the water in the main circuit, either by direct reinjection into the latter from the heaters R S and R 2 , either by sending to the following heater after separation of the liquid phase and the vapor phase in the phase separators SP 1 , SP 2 and SP 3 .
  • part of the energy of this mixture present in the form of pressure is lost in the phase separators which, moreover, have the drawback of being subject to strong erosion due to the high speed of the mixing at the regulating valve outlet.
  • the heating system according to the invention of FIG. 2 differs essentially from that of FIG. 1 in that the main control valves SR 1 , SR 2 , SR 3 and SR 4 , as well as the phase separators SP ,, SP 2 and SP 3 have been eliminated and replaced by two-phase turbines.
  • Biphasic turbines are turbines of a particular design which are fed by means of a mixture of a liquid and a gas or vapor to drive in rotation a shaft, thus providing a mechanical work, while ensuring a separation of the liquid and gas, so that these can be collected separately at the outlet of the turbine. Since this type of turbine is known, in particular from US Patents 3,879,949, 3,972,195 and 4,087,261 to which reference may be made, no detailed description will be given in this specification.
  • the condensates of the heater R 7 are introduced into the two-phase turbine TB 1 as a function of the level in this heater by adjusting the position of the moderator V ' 1 of the two-phase turbine TB 1 controlled by the level regulator RN 1 . These condensates are sent to the condenser by the emergency control valve V 1 in the event of the unavailability of the two-phase turbine TB 1 .
  • the vapor separated therein is directed to the steam zone of the heater R 6 , while the separated water joins the condensates of the heater R 6 .
  • This mixture is introduced into the following two-phase turbine TB 2 as a function of the level in the heater R 6 ; by adjusting the position of its moderator V ' 2 controlled by the level regulator RN 2 .
  • the mixture is directed to the condenser by the emergency control valve V 2 .
  • the vapor separated in the two-phase turbine TB 2 is directed to the vapor zone of the heater R 5 , while the separated water joins the condensates of this heater.
  • this mixture is introduced into the following two-phase turbine TB 3 as a function of the level in the heater R 5 , by adjusting its moderator V ' 3 controlled by the level regulator RN 3 . If the TB 3 two-phase turbine is unavailable, the mixture is directed to the condenser by the emergency control valve V 3 .
  • the vapor separated in the two-phase turbine TB 3 is directed to the heater by mixing R 4 , while the separated water is sent directly to the next two-phase turbine TB 4 .
  • the vapor separated therein is directed to the steam zone of the heater R 3 , while the separated water joins the condensates of this heater.
  • this mixture is introduced into the last two-phase turbine TB 5 as a function of the level in the heater R 3 , by adjusting its moderator V ' 4 controlled by the level regulator RN 4 . If the TB 5 two-phase turbine is unavailable, the mixture is directed to the condenser by the emergency control valve V 4 .
  • the steam separated in the two-phase turbine TB S is directed to the steam zone of the heater R 2 , while the separated water joins the condensates of this heater in RA.
  • the downstream part of this system then functions as the corresponding part of the conventional heating system of FIG. 1.
  • the energy of the water and steam mixture in each of the two-phase turbines is collected on a common shaft A to drive an auxiliary alternator, a pump or the like.
  • the two-phase turbines may not be coupled on the same shaft.
  • FIG. 3 shows a conventional heating system for a nuclear power plant and on which the same reference letters as those used in FIGS. 1 and 2 have been used to designate similar elements. Since the heating system of FIG. 3 is classic and also has many similarities with that of the Fig. 1, it will be described more succinctly than this.
  • This heating system comprises, on the main circuit PC, a subcooler SOR six heaters and R 11 to R 16 fed with steam by soutira- gs S 11 to S 16, respectively.
  • the heater R 16 is also supplied with steam separated by a phase separator SP 11 from the condensates of a superheater SU (not shown).
  • Main regulation valves SR 11 and relief valves V 11 controlled as a function of the level in the superheater make it possible to direct the condensates from the latter to the phase separator SP 11 or to the condenser as required, as described above.
  • the following heater R 15 is supplied with steam separated from the condensates of the heater R 16 by a phase separator SP12 .
  • Main regulation valves SR 12 and emergency valves V 12 controlled by a level regulator RN 11 . are planned.
  • the condensates from the heater R 15 are sent to a recovery tank for the DRT purges via a main valve regulation SR 13 .
  • an emergency regulating valve V 13 allows these condensates to be sent directly to the condenser.
  • the DRT tank also receives condensate from a SE dryer (not shown) via a main regulation valve SR 15 .
  • An emergency regulating valve V 15 controlled like the SR 15 valve depending on the level in the dryer, makes it possible to direct these condensates directly to the condenser if necessary.
  • the DRT tank finally receives the condensates from the heater R 14 , an emergency regulation valve V 14 controlled by the level regulator R 14 being however provided to send them to the condenser if necessary.
  • the content of the DRT tank is reinjected by a condensate recovery valve PR into the main circuit CP, between the feed pump PA and the heater R 14 , via a main regulation valve SR 16 controlled by a level regulator RN 13 associated with the tank DRT.
  • This RN 13 regulator also controls an emergency regulating valve V 16 making it possible to return the condensates from the DRT tank to the condenser.
  • the condensate from the heater R13 is sent either to a phase separator SP 13 via a main control valve SR 17 or to the condenser via an emergency control valve V 17 , depending of the level regulator RN 15 of the heater R 13 .
  • the condensates from the heater R 12 are sent, either directly to the sub-heater SOR and, from there, to the condenser via a main control valve SR 18 , or directly to the condenser via a emergency control valve V 18 , depending on the control of the level regulator RN 16 of the heater R12.
  • two-phase turbines TB 11 , TB 12 , T B 13 ' TB 14 and TB 15 are substituted respectively for the main control valves SR 11 , SR 12 , BR 13 , SR 17 and SR 18 , and for the phase separators SP 11 , SP 12 and SP 13 deleted.
  • the steam separated by the turbines TB 11 and TB 12 feeds the heaters R 16 and R 15 respectively , while the water joins the respective condensates of these heaters to feed the following turbines TB 12 and TB 13 respectively.
  • the steam separated by the two-phase turbine TB 13 is directed to the DRT tank, while the water is sent upstream of the condensate recovery pump PR to be reinjected with the purges of the DRT tank in the main circuit CP.
  • the two-phase turbine TB 14 separates the steam from the condensates of the heater R 13 and sends it to the side steam from the heater R 12 , while the water reaches the condensates of this heater.
  • This mixture is introduced into the two-phase turbine TB 15 and the vapor separated therein is directed to the steam zone of the heater R11. The water joins the condensates of this heater and the mixture thus formed feeds the SO R sub-cooler.
  • the turbine biphasic TB 11 to TB 15 are supplied to the level in the heat exchanger by condensation from which they receive the condensate by adjusting the position of their respective moderator V '11, V' 12, V '13, V '14 and V' 15 .
  • the energy of the mixture of water and steam in each of the turbines is collected on a common shaft A to drive auxiliary members or individually on the shaft of each turbine.
  • the two-phase turbine heating system makes it possible both to supply the heaters in cascade with steam drawn from the condensates of a previous heater or of a superheater and to provide mechanical power additional. This therefore makes it possible to increase the overall yield of the energy production installation with which the heating system is associated.
  • the heating system according to the invention In addition to this advantage in terms of efficiency, which can amount to an additional power supply of 0.5 to 0.8%, the heating system according to the invention.
  • This eliminates static phase separators from the heating systems of the prior art since it is the two-phase turbines themselves which carry out the separation. This therefore results in the elimination of the aforementioned erosion phenomena in the phase separators and a simplification of the pipe diagram.

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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)
  • Control Of Turbines (AREA)
  • Water Treatment By Sorption (AREA)
  • External Artificial Organs (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP80400077A 1980-01-18 1980-01-18 System zur Wiedererwärmung für eine Dampfturbinenkraftanlage Expired EP0032641B1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP80400077A EP0032641B1 (de) 1980-01-18 1980-01-18 System zur Wiedererwärmung für eine Dampfturbinenkraftanlage
AT80400077T ATE22152T1 (de) 1980-01-18 1980-01-18 System zur wiedererwaermung fuer eine dampfturbinenkraftanlage.
DE8080400077T DE3071745D1 (en) 1980-01-18 1980-01-18 Reheating system for a steam-turbine power plant
US06/199,193 US4408460A (en) 1980-01-18 1980-10-21 Heating system for a steam turbine energy producing plant
AU63856/80A AU537612B2 (en) 1980-01-18 1980-10-30 Feed-water preheating system
JP18270780A JPS56124611A (en) 1980-01-18 1980-12-23 Condensing heating apparatus for steam turbine of energy manufacturing plant
ZA00810290A ZA81290B (en) 1980-01-18 1981-01-16 Heating system for a steam turbine energy producing plant

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP80400077A EP0032641B1 (de) 1980-01-18 1980-01-18 System zur Wiedererwärmung für eine Dampfturbinenkraftanlage

Publications (2)

Publication Number Publication Date
EP0032641A1 true EP0032641A1 (de) 1981-07-29
EP0032641B1 EP0032641B1 (de) 1986-09-10

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ID=8187354

Family Applications (1)

Application Number Title Priority Date Filing Date
EP80400077A Expired EP0032641B1 (de) 1980-01-18 1980-01-18 System zur Wiedererwärmung für eine Dampfturbinenkraftanlage

Country Status (7)

Country Link
US (1) US4408460A (de)
EP (1) EP0032641B1 (de)
JP (1) JPS56124611A (de)
AT (1) ATE22152T1 (de)
AU (1) AU537612B2 (de)
DE (1) DE3071745D1 (de)
ZA (1) ZA81290B (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4635588A (en) * 1985-02-25 1987-01-13 Hamon-Sobelco S.A. Heaters for thermal energy transformation installations

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE41202T1 (de) * 1985-01-16 1989-03-15 Hamon Sobelco Sa Verfahren und vorrichtung fuer die energierueckgewinnung aus dem abgas eines thermischen kraftwerks.
EP1806533A1 (de) * 2006-01-05 2007-07-11 Siemens Aktiengesellschaft Wasserdampfkreislauf einer Kraftwerksanlage

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR377826A (fr) * 1906-06-27 1907-09-16 Sebastian Ziani De Ferranti Perfectionnements aux installations de production de force motrice au moyen de turbines à fluide élastique
US2921441A (en) * 1953-12-17 1960-01-19 Sulzer Ag Feed water preheating system for steam power plants
FR1290451A (fr) * 1961-04-20 1962-04-13 Siemens Ag Installation d'énergie thermique, en particulier installation groupée, avec chaudière à circulation forcée

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH320887A (de) * 1954-04-06 1957-04-15 Sulzer Ag Verfahren zum Betrieb einer Dampfkraftanlage mit Zwischendampfentnahme zur Speisewasservorwärmung
US2900793A (en) * 1954-04-06 1959-08-25 Sulzer Ag Condensing steam heated boiler feed water heating system including a condensate operated turbine
CH521514A (de) * 1970-07-15 1972-04-15 Linde Ag Entspannungsturbine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR377826A (fr) * 1906-06-27 1907-09-16 Sebastian Ziani De Ferranti Perfectionnements aux installations de production de force motrice au moyen de turbines à fluide élastique
US2921441A (en) * 1953-12-17 1960-01-19 Sulzer Ag Feed water preheating system for steam power plants
FR1290451A (fr) * 1961-04-20 1962-04-13 Siemens Ag Installation d'énergie thermique, en particulier installation groupée, avec chaudière à circulation forcée

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4635588A (en) * 1985-02-25 1987-01-13 Hamon-Sobelco S.A. Heaters for thermal energy transformation installations

Also Published As

Publication number Publication date
ZA81290B (en) 1982-02-24
ATE22152T1 (de) 1986-09-15
AU537612B2 (en) 1984-07-05
EP0032641B1 (de) 1986-09-10
JPS56124611A (en) 1981-09-30
DE3071745D1 (en) 1986-10-16
US4408460A (en) 1983-10-11
AU6385680A (en) 1981-07-23

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