EP0314028A1 - Procédé pour augmenter le rendement d'un processus de vapeur - Google Patents

Procédé pour augmenter le rendement d'un processus de vapeur Download PDF

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Publication number
EP0314028A1
EP0314028A1 EP88117638A EP88117638A EP0314028A1 EP 0314028 A1 EP0314028 A1 EP 0314028A1 EP 88117638 A EP88117638 A EP 88117638A EP 88117638 A EP88117638 A EP 88117638A EP 0314028 A1 EP0314028 A1 EP 0314028A1
Authority
EP
European Patent Office
Prior art keywords
steam
feed water
water
cooled
excess
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.)
Withdrawn
Application number
EP88117638A
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German (de)
English (en)
Inventor
Timo Dr. Korpela
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.)
Alstom Power Turbinen GmbH
Original Assignee
AEG Kanis Turbinenfabrik GmbH
AEG Kanis 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 AEG Kanis Turbinenfabrik GmbH, AEG Kanis GmbH filed Critical AEG Kanis Turbinenfabrik GmbH
Publication of EP0314028A1 publication Critical patent/EP0314028A1/fr
Withdrawn legal-status Critical Current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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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
    • F01K7/18—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 turbine being of multiple-inlet-pressure type
    • 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
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/18—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters
    • F01K3/185—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters using waste heat from outside the plant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B3/00—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass
    • F22B3/04—Other methods of steam generation; Steam boilers not provided for in other groups of this subclass by drop in pressure of high-pressure hot water within pressure- reducing chambers, e.g. in accumulators

Definitions

  • the invention relates to the method for increasing the efficiency in the steam process, in which the steam generated in the steam generating system with a hot material stream is fed into a steam turbine, the cooled steam stream condenses from the steam turbine and the feed water of the steam generating system is preheated.
  • the problem is that compared to the gas stream low feed water flow and accordingly low steam flow.
  • the gases can therefore not be cooled down very much without reducing the pressure in the steam process, which in turn reduces the efficiency.
  • the optimal pressure level of the waste heat boiler of a gas turbine is 30-40 bar and the gases can be cooled to a little below 200 ° C with an 1-pressure boiler.
  • the Swedish publication SE-416 835 also shows a preheating system that is a 2-printing process.
  • the steam turbine is fed by the HP part and the LP part gives steam for other general needs, such as preheating the fuel oil and other heating.
  • the system also has a feed water preheater that takes its heat from the LP part of the steam generator.
  • This system also consists of a multi-stage preheating system, with the steam being fed into the steam turbine only at a pressure / temperature level.
  • the power output of the steam turbine can be increased with this system, since the tapping quantity to be discharged by the steam turbines is reduced in a situation in which evaporation would otherwise take place in the preheater.
  • Figure 3a shows a 1-pressure solution in which the evaporation temperature (I) and the so-called "pinch point" temperature difference A 1 limit the cooling available for evaporation and overheating and the amount of heat to be transferred to a value Q0.
  • the amount of heat required to preheat the corresponding amount of feed water is Q 1, which is sufficient for a very low gas cooling in the usual applications in which the inlet temperature of the gas is low. A considerable amount of heat Q h is lost.
  • the gas stream to be cooled can at most be cooled to a temperature T a .
  • a second evaporator at a lower pressure level, ie a 2-pressure solution, which is shown in Figure 3b.
  • the steam (II) generated in this way is fed as an intermediate feed into the steam turbine, as in publication SCH-621 186, or in factory processes or the like, as in publication SE-416 835.
  • the amount of heat recovered from the gas stream to be cooled is increased in comparison to the 2-pressure process by the amount Q2 and the gas stream to be cooled is cooled to a temperature T b at the most .
  • the most important advantage of the invention can be considered that it enables in a simple way: - A process that almost corresponds thermodynamically to a multi-pressure process, in which there are separate steam generator circuits for each pressure level of the expansion device of the process described here, which results in high efficiency - Cooling of the gases reasonably close to the feed water temperature - Solves the operational problems of partial load in the boilers and other objects in which the amount of gas is independent of the heat output - Achieving the advantages described above economically cheaper than with the usual processes, both through increased electricity generation and through lower investment costs.
  • Figure 1 shows an embodiment of the process according to the invention as a process diagram.
  • Figure 2 shows an alternative arrangement of the evaporation according to the invention as a process diagram.
  • Figures 3a to 3d show the temperature-heat quantity diagrams that explain the invention and its technical level.
  • the process gains its thermal energy through a boiler arrangement, which is generally marked with a cipher 1.
  • the components of the boiler arrangement 1 are arranged in the energy-generating medium flow 14, which typically arises from the waste gas flow from the gas turbine, the flue gas flow from the other combustion process, other corresponding hot gas flow or liquid flow.
  • the process shown in the picture would work as a common counterflow system as follows.
  • the steam flow HT is taken from the drum 2, which is passed over the superheater 6 and is then led into the HP part of the steam turbine.
  • This condensation water is normally controlled in various ways via the feed water tank 4 into the system as feed water VS.
  • VH water heater which in this case is the same as VS, is so small that it does not allow a particularly large reduction in the flue gas temperature, as previously stated, regardless of how cold the feed water is.
  • load regulation i.e. with constant or sliding pressure, have no significant effect on efficiency in this regard.
  • the secondary flow V1 of the water comes into the first expansion steam generator 11, in which it can be expanded, whereby it is divided into steam flow H2 and residual water flow V2. Thereafter, the steam stream H2 is overheated with the help of the gas stream 14 in the low-temperature superheater 8 and conducted into the steam turbine 3 at a point corresponding to this pressure.
  • the pressure of the superheated steam is typically 15 bar and the temperature is 250 ° C.
  • the residual water stream V2 is again fed into the next expansion evaporator 12, in which it can be expanded further, dividing it into steam stream H3 and into residual water stream V3.
  • the pressure of the steam stream H3 is typically 5 bar and the temperature is 153 ° C. This stream is mainly led into the stage of the steam turbine 3 corresponding to this pressure as partial steam H31.
  • Part of this steam flow can be fed as part flow H32 into the feed water tank 4 for heating the feed water.
  • the corresponding residual water stream V3 is fed further into the next expansion evaporator 13, in which it is allowed to expand further, in order to form the steam stream H4 and the water stream V4.
  • the pressure of the steam flow H4 can be 1 bar and the temperature 100 ° C.
  • This residual water flow V4 is via the condenser 10 into the condensation water VL led, the temperature is typically about 40 ° C.
  • the arrangement implemented with the surface heat exchanger 5 with regard to the condensation water VL and VLK and the feed water VK and VS relates to the degassing of the feed water and as such is not associated with this invention.
  • the heat recovery according to Figure 3c is increased in this invention by increasing the water flow through the feed water preheater and increasing the heat area of the feed water preheater, which is as much as necessary and profitable.
  • the flue gas can in principle be cooled down to the temperature of the feed water coming from the condenser. B. to the temperature T c , the amount of heat recovered also increases compared to the 2-pressure solution by the amount Q3.
  • saturated HD water is obtained more than the amount of heat Q available to the evaporation and overheating part of the boiler can evaporate and overheat. Therefore, the excess feed water is removed from the boiler and used to generate vapors of lower pressures, in the alternative ways described in this application and thus cooled again in the feed water preheater (the cooling phase of the water is not shown in Figure 3c).
  • the resulting LP vapors are fed into the steam turbine as an intermediate feed, whereby the electrical power of the turbine increases.
  • the primary steam flow HT into the steam turbine 3 remained constant at 37.4 kg / s.
  • Figure 1 shows only one example process according to the invention.
  • the principle of the invention can be applied in many different ways, by adhering to its principle of feeding in excess feed water and z.
  • B. evaporated with the expansion methods 11, 12 and 13 mentioned and this steam leads into the steam turbine 3.
  • expansion vaporizers at three pressure / temperature levels, but expansion vaporizers can only have one or more than three.
  • the steam obtained from these expansion evaporators can be superheated with gas flow in one or more superheaters 8, or the vapors can be fed into the turbine without overheating.
  • a particularly favorable way of realizing the overheating is to overheat the steam HS available in each case from the expansion evaporator in the heat exchanger 23 with the water V1 coming into this evaporator.
  • the steam flow H3 is accordingly overheated with the water flow V2, the steam flow H4 with the water flow V3 etc.
  • partial steam streams H32 can be taken at various points in the evaporation process and led to the feed water heating or this phase can be omitted and the entire steam into the Guide turbine 3.
  • the arrangements connected to the feed water tank 4 and the heat exchanger 5 itself can also be different.
  • the excess feed water to be circulated can either be returned to the suction side of the feed water pump 16 or, using a separate circulating pump, to the pressure side thereof.
  • low-temperature circulating water V1 can also be used to evaporate using a surface heat exchanger combination 21 ( Figure 2), this excess water flow V1 being the stream to be cooled or, if desired, the superheating stream as well Is medium.
  • a lower water flow for evaporation can also be taken from this at the same time, from which the corresponding steam flow HS is created in the steam turbine. This water can of course also be taken elsewhere.
  • the system described above is shown in Figure 2. Otherwise, the variations of the system described above are applicable in connection with this or similar evaporators (if these evaporators are available at several pressure levels).
  • the excess feed water V1 taken for circulation can be fed into a steam separator of the same pressure (not shown in the pictures).
  • the steam obtained from this separator is fed into the boiler or into the boiler drum 2 and the remaining water is fed into devices 11, 12, 13; 21 cooled, which generate LP steam.
  • ND vapors H2, H3, H4; HS are treated as described above. If the getting of salts of the cooling water in the LP circulation is to be avoided, the feed water V1 in the boiler drum 2 is taken from a special feed water channel before the preheated feed water VH has mixed into the boiler water VP.
  • waste heat from the process e.g. B. flue gas flow
  • the waste heat energy of the flue gas can thus be used extremely effectively.
  • the heat flow 14 can also be another flue gas flow or an exhaust gas flow from any engine, e.g. B. a ship machine, or a hot medium flow from any process, the medium can be gaseous, liquid or a combination of the two.
  • Stream 14 may also include solid particles.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP88117638A 1987-10-27 1988-10-22 Procédé pour augmenter le rendement d'un processus de vapeur Withdrawn EP0314028A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI874718A FI77511C (fi) 1987-10-27 1987-10-27 Foerfarande foer hoejning av aongprocessens verkningsgrad.
FI874718 1987-10-27

Publications (1)

Publication Number Publication Date
EP0314028A1 true EP0314028A1 (fr) 1989-05-03

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ID=8525298

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88117638A Withdrawn EP0314028A1 (fr) 1987-10-27 1988-10-22 Procédé pour augmenter le rendement d'un processus de vapeur

Country Status (3)

Country Link
EP (1) EP0314028A1 (fr)
JP (1) JPH01280604A (fr)
FI (1) FI77511C (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010007131A1 (fr) * 2008-07-16 2010-01-21 Siemens Aktiengesellschaft Installation de turbine à vapeur et procédé de conduite d'une turbine à vapeur
EP2772618A4 (fr) * 2011-10-28 2015-07-08 Kawasaki Heavy Ind Ltd Installation de génération d'énergie
EP2561188A4 (fr) * 2010-04-22 2016-03-23 Ormat Technologies Inc Système de récupération de la chaleur perdue sur la base d'un fluide moteur organique
US10352246B2 (en) 2015-07-24 2019-07-16 Mitsubishi Hitachi Power Systems, Ltd. Water feeding method, water feeding system implementing said method, and steam generating facility provided with water feeding system

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1035728A (en) * 1963-12-03 1966-07-13 Simmering Graz Pauker Ag Condensing steam turbine plant comprising a controlled secondary circuit
FR2476240A1 (fr) * 1980-02-19 1981-08-21 Kawasaki Heavy Ind Ltd Appareil de recuperation d'energie pour installation de compresseur de gaz
US4394813A (en) * 1980-12-25 1983-07-26 Mitsui Engineering And Shipbuilding Company Limited Exhaust gas heat recovery system in internal combustion engine

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1035728A (en) * 1963-12-03 1966-07-13 Simmering Graz Pauker Ag Condensing steam turbine plant comprising a controlled secondary circuit
FR2476240A1 (fr) * 1980-02-19 1981-08-21 Kawasaki Heavy Ind Ltd Appareil de recuperation d'energie pour installation de compresseur de gaz
US4394813A (en) * 1980-12-25 1983-07-26 Mitsui Engineering And Shipbuilding Company Limited Exhaust gas heat recovery system in internal combustion engine

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010007131A1 (fr) * 2008-07-16 2010-01-21 Siemens Aktiengesellschaft Installation de turbine à vapeur et procédé de conduite d'une turbine à vapeur
US8770914B2 (en) 2008-07-16 2014-07-08 Siemens Aktiengesellschaft Steam turbine system and method for operating a steam turbine
EP2561188A4 (fr) * 2010-04-22 2016-03-23 Ormat Technologies Inc Système de récupération de la chaleur perdue sur la base d'un fluide moteur organique
EP2772618A4 (fr) * 2011-10-28 2015-07-08 Kawasaki Heavy Ind Ltd Installation de génération d'énergie
US9453432B2 (en) 2011-10-28 2016-09-27 Kawasaki Jukogyo Kabushiki Kaisha Power generation system
US10352246B2 (en) 2015-07-24 2019-07-16 Mitsubishi Hitachi Power Systems, Ltd. Water feeding method, water feeding system implementing said method, and steam generating facility provided with water feeding system
DE112016003348B4 (de) 2015-07-24 2020-06-18 Mitsubishi Hitachi Power Systems, Ltd. Wasserversorgungssystem, wasserversorgungsverfahren, und dampf erzeugende anlage, die mit wasserversorgungssystem bereitgestellt wird

Also Published As

Publication number Publication date
FI77511C (fi) 1989-03-10
JPH01280604A (ja) 1989-11-10
FI77511B (fi) 1988-11-30
FI874718A0 (fi) 1987-10-27

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