EP2442061B1 - Verfahren zum Kühlen des Rauchgases einer Feuerungsanlage in einem Wärmetauschers einer Dampfzeugungsanlage - Google Patents

Verfahren zum Kühlen des Rauchgases einer Feuerungsanlage in einem Wärmetauschers einer Dampfzeugungsanlage Download PDF

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Publication number
EP2442061B1
EP2442061B1 EP11006156.1A EP11006156A EP2442061B1 EP 2442061 B1 EP2442061 B1 EP 2442061B1 EP 11006156 A EP11006156 A EP 11006156A EP 2442061 B1 EP2442061 B1 EP 2442061B1
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EP
European Patent Office
Prior art keywords
heat exchanger
medium
bypass
steam generation
plant
Prior art date
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Application number
EP11006156.1A
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German (de)
English (en)
French (fr)
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EP2442061A2 (de
EP2442061A3 (de
Inventor
Robert von Raven
Alexander Seitz
Johannes Martin
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.)
Martin GmbH fuer Umwelt und Energietechnik
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Martin GmbH fuer Umwelt und Energietechnik
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Application filed by Martin GmbH fuer Umwelt und Energietechnik filed Critical Martin GmbH fuer Umwelt und Energietechnik
Priority to PL11006156T priority Critical patent/PL2442061T3/pl
Publication of EP2442061A2 publication Critical patent/EP2442061A2/de
Publication of EP2442061A3 publication Critical patent/EP2442061A3/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
    • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
    • 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
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B15/00—Water-tube boilers of horizontal type, i.e. the water-tube sets being arranged horizontally
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B31/00—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B31/00—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus
    • F22B31/08—Installation of heat-exchange apparatus or of means in boilers for heating air supplied for combustion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
    • F22D1/00—Feed-water heaters, i.e. economisers or like preheaters
    • F22D1/02—Feed-water heaters, i.e. economisers or like preheaters with water tubes arranged in the boiler furnace, fire tubes, or flue ways
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G1/00—Steam superheating characterised by heating method
    • F22G1/02—Steam superheating characterised by heating method with heat supply by hot flue gases from the furnace of the steam boiler

Definitions

  • the invention relates to a method for cooling the flue gas of a furnace in a heat exchanger of a steam generating plant.
  • Heat exchangers are needed in many applications.
  • the transmitted energy is determined by the different temperatures of the guided in the heat exchanger media.
  • different control mechanisms are known to vary the flow rate of these media. Since the heat exchanger surface can not be changed as a rule, but often certain media temperatures should be achieved at the heat exchanger outlet, the flow rate in the heat exchanger is varied.
  • An alternative is to operate the heat exchanger in cocurrent or countercurrent. While in DC operation at the heat exchanger output, the media temperatures can be closely approximated, the countercurrent operation usually provides a higher heat exchange at the same heat exchanger surface.
  • the switchover from DC to countercurrent excretes as a control mechanism, since already during installation of the heat exchanger, the piping is set and this can not be changed during operation.
  • the WO 2010/034292 proposes a shell-and-tube heat exchanger in which the medium flows of process plants to be cooled flow through straight heating surface tubes and thereby release the existing heat of the hot medium flow via the tube wall to the cooling medium surrounding the tubes.
  • Such heat exchangers are not suitable for cooling the flue gas of combustion plants.
  • a special field of application of particularly large heat exchangers lies in the cooling of the gases of combustion plants, which are operated as a steam generating plant.
  • the air supplied to the grate or the combustion area air is preheated and the exhaust gases are cooled.
  • Heat exchangers are used as evaporators and superheaters to supply a turbine with steam.
  • the feedwater of the steam generator is often preheated in an Ecomizer for further cooling of the flue gases.
  • the exhaust gas temperature varies depending on the combustion process.
  • deposits are formed in the evaporator and in the superheaters, which affect the effectiveness of the heat exchanger.
  • the Ecomizer will eventually be exposed to different exhaust gas temperatures.
  • the efficiency of the Ecomizers varies according to the deposits caused by the flue gases on the heat exchanger tubes.
  • a denitrification system for the flue gases is provided, the catalytic effects of which run optimally only at certain temperatures. These are, for example, in an SCR plant between 250 ° C and 270 ° C.
  • the heat exchangers still have a high efficiency, which decreases during the service life, however, as a result of deposits.
  • the running time of the plant is determined in particular by the fact that the flue gas temperature at the denitrification plant must remain within a certain temperature window.
  • the invention is therefore based on the object of developing a generic-Bes method in such a way that the desired temperature window can be maintained longer.
  • the Ecomizer can initially be operated in DC, for example.
  • DC direct current to countercurrent
  • the flue gas temperature rises.
  • the flue gas temperature is then lowered.
  • the heat exchanger can continue to operate as the flue gas temperature remains within the specified temperature window.
  • the flue gas temperature can thus be reduced from 265 degrees Celsius to 255 degrees Celsius by switching from direct current to countercurrent. This can significantly extend the runtime of the system.
  • valves in the supply line, the discharge line and the bypasses can be meaningfully controlled so that no lines with superheated media can be closed on both sides. This is particularly necessary in Darnpfer Wegungsanlagen necessary to avoid excessive pressures in the lines.
  • a three-way valve be arranged between the medium inlet, the first bypass and the feed line.
  • a three-way valve ensures that the medium is distributed from the medium inlet to the bypass and supply line.
  • the three-way valve can be set so that it always passes through the entire inflow at the medium inlet, without that at this point the line system is reduced in cross section or even closed.
  • An advantageous use of the device is in the treatment of liquid media. This mainly affects media that are over 130 ° C hot.
  • One embodiment variant provides that the gas flows in the direction from the heat exchanger inlet to the heat exchanger outlet. Depending on the circuit of the system, however, the gas can also flow from the heat exchanger outlet to the heat exchanger inlet.
  • the gas has a temperature above 100 ° C.
  • the device described can be used in a steam generating plant at various locations.
  • the heat exchanger may be a superheater, an ecomizer or a combustion air preheater.
  • heat exchangers of a steam generating plant can be operated so that the required gases are kept in special temperature windows and it can be switched during operation between DC and countercurrent mode.
  • This method can be implemented in a particularly simple manner if the changeover takes place via two three-way valves. This simplifies valve control and, regardless of control by valve design, ensures that the steam generating system does not contain overheated media in lines that can be completely closed at the line inlet and outlet.
  • the device 1 shown essentially consists of a heat exchanger 2, which is supplied via a feed line 3 with a medium 16.
  • This feed line 3 leads from a medium inlet 4 to the heat exchanger inlet 5.
  • a discharge line 6 from the heat exchanger outlet 7 is provided at the side facing away from the medium exchanger inlet side.
  • a first bypass 8 leads from the medium inlet 4 to the outlet 6 and a second bypass 9 leads from the supply line 3 to the medium outlet 10.
  • a first bypass valve 11 is provided between the medium inlet and the first bypass 8, and a second bypass valve 12 is provided between the second bypass 9 and the medium outlet 10.
  • a supply valve 13 is arranged and in the discharge line 6, a discharge valve 14 is provided.
  • the second medium in the present case is a gas whose flow is indicated by the arrows 15.
  • the heat exchanger 2 is thus in the in FIG. 1 shown example operated in DC.
  • the supply line valve 13 and the discharge valve 14 are opened, so that the medium 16 flows through the heat exchanger 2 in direct current to the gas 15.
  • the first bypass 8 allows via the first bypass valve 11, an adjustment of the heat exchanger performance and the temperature of the medium at the medium outlet 10.
  • the second bypass valve 12 is closed, so that no medium flows through the second bypass 9.
  • the medium 16 flows through the first bypass valve 11 and the first bypass 8 through the heat exchanger 2 to the second bypass valve 12 and from there to the medium outlet 10. Since the gas continues to flow in the direction of the arrows 15, the heat exchanger 2 in this valve setting in Countercurrent operated. An adjustment of the medium temperature at the medium outlet 10 is possible via the position of the supply valve 13, via which a bypass flow from the medium inlet 4 directly to the medium outlet 10 is achieved. The path from the medium inlet via the outlet 6 to the medium outlet 10 is closed by the discharge valve 14.
  • FIGS. 3 and 4 are the ones in the Figures 1 and 2 shown circuits in a corresponding manner, however, each described with 2 two-way valves.
  • the bypass valve 11 and the supply valve 13 have been combined to form a first three-way valve 17, while the bypass valve 12 and the discharge valve 14 are combined to form a second three-way valve 18.
  • the first bypass valve 17 thus distributes the medium 16 coming from the medium inlet 4 to the supply line 3 and the first bypass 8.
  • the second three-way valve 18 carries the medium guided in the discharge 6 with the medium coming from the second bypass 9 to the medium outlet 10.
  • the heat exchanger 2 can thus from the in FIG. 3 shown DC operation in the in FIG. 4 shown countercurrent operation can be switched. While in DC operation the second bypass 9 is closed via the setting on the second three-way valve 18, the outlet 6 is closed in countercurrent operation via the second three-way valve 18, while the second bypass 9 is opened.
  • steam generating plant 20 is the furnace in which burned with preheated combustion air fuels such as waste in particular, not shown.
  • the exhaust gases produced during combustion are indicated by the arrows 21, 22 and 23.
  • the medium thus flows from the medium inlet 37 via the first three-way valve 34 and the supply line 38 to the Ecomizer 28 and the Ecomizer 28 via the discharge line 39 and the second two-way valve 35 on to the boiler drum 40.
  • a control of the medium temperature via the first bypass 41 between the first bypass valve 34 and the drain 39 is possible.
  • FIG. 6 shows that by a simple switch on the second bypass valve 35 of the Ecomizer 28 of the in FIG. 5 shown DC operation in a in FIG. 6 shown countercurrent operation can be switched.
  • the water 29 flows in this circuit from the medium inlet 37 via the first two-way valve 34 and the first bypass 41 to the Ecomizer 28. From there, the water passes through the second bypass 36 to the second three-way valve 35 and back to the boiler drum 40th
  • the supply line 38 assumes in this circuit the function of a possible bypass to controlled by the first three-way valve 34 water on Ecomizer 28 over to lead directly to the first three-way valve 35 and from there to the boiler drum 40.
  • Serving as the cooling medium water 29 is vaporized in the evaporator 24 and steam initially supplied via the first superheater 25, then via the second superheater 26 and finally via the third superheater 27 of the turbine 30, which drives the generator 31.
  • This makes it possible to provide a control of the medium temperatures on the gas and water side in this circuit without additional pipe or valve effort in a simple manner.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Chimneys And Flues (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Physical Or Chemical Processes And Apparatus (AREA)
EP11006156.1A 2010-10-12 2011-07-27 Verfahren zum Kühlen des Rauchgases einer Feuerungsanlage in einem Wärmetauschers einer Dampfzeugungsanlage Active EP2442061B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL11006156T PL2442061T3 (pl) 2010-10-12 2011-07-27 Sposób schładzania gazu spalinowego instalacji paleniskowej w wymienniku ciepła instalacji wytwarzania pary

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010048065A DE102010048065A1 (de) 2010-10-12 2010-10-12 Vorrichtung mit einem Wärmetauscher und Verfahren zum Betreiben eines Wärmetauschers einer Dampferzeugungsanlage

Publications (3)

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EP2442061A2 EP2442061A2 (de) 2012-04-18
EP2442061A3 EP2442061A3 (de) 2015-03-04
EP2442061B1 true EP2442061B1 (de) 2017-09-27

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EP11006156.1A Active EP2442061B1 (de) 2010-10-12 2011-07-27 Verfahren zum Kühlen des Rauchgases einer Feuerungsanlage in einem Wärmetauschers einer Dampfzeugungsanlage

Country Status (11)

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US (1) US9677831B2 (ja)
EP (1) EP2442061B1 (ja)
JP (1) JP5971508B2 (ja)
BR (1) BRPI1106277B1 (ja)
CA (1) CA2754465C (ja)
DE (1) DE102010048065A1 (ja)
DK (1) DK2442061T3 (ja)
ES (1) ES2653670T3 (ja)
NO (1) NO2442061T3 (ja)
PL (1) PL2442061T3 (ja)
PT (1) PT2442061T (ja)

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DE102011015717B4 (de) 2011-03-31 2022-09-08 Thyssenkrupp Industrial Solutions Ag Wärmerückgewinnungseinrichtung
CN102937295B (zh) * 2012-11-20 2015-02-18 上海锅炉厂有限公司 一种适用脱硝设备负全程负荷投运的锅炉省煤器布置方式
US10234216B2 (en) 2013-02-01 2019-03-19 Tetra Laval Holdings & Finance S.A. Valve arrangement for a heat treatment apparatus
FR3013823B1 (fr) * 2013-11-28 2018-09-21 F2A - Fabrication Aeraulique Et Acoustique Echangeur air/air a double flux, installation de traitement d'air et methode de nettoyage d'un tel echangeur
CN108488777A (zh) * 2018-03-08 2018-09-04 苏州天沃环境能源工程有限公司 燃煤熔盐炉高温废气的热能回用设备
JP7392687B2 (ja) * 2021-06-10 2023-12-06 Ｊｆｅスチール株式会社 ボイラ燃料の予熱装置及び予熱方法
EP4328520A1 (de) * 2022-08-25 2024-02-28 ERK Eckrohrkessel GmbH Verfahren und einrichtung zur nutzung von erdwärme
EP4328519A1 (de) * 2022-08-25 2024-02-28 ERK Eckrohrkessel GmbH Verfahren und vorrichtung zur gewinnung von erdwärme sowie verfahren zur erzeugung elektrischer energie

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Also Published As

Publication number Publication date
US9677831B2 (en) 2017-06-13
PT2442061T (pt) 2017-11-27
DK2442061T3 (en) 2017-12-04
NO2442061T3 (ja) 2018-02-24
PL2442061T3 (pl) 2018-03-30
BRPI1106277B1 (pt) 2020-04-22
DE102010048065A1 (de) 2012-04-12
CA2754465A1 (en) 2012-04-12
CA2754465C (en) 2018-07-24
ES2653670T3 (es) 2018-02-08
JP2012083095A (ja) 2012-04-26
BRPI1106277A2 (pt) 2016-01-19
EP2442061A2 (de) 2012-04-18
EP2442061A3 (de) 2015-03-04
US20120085517A1 (en) 2012-04-12
JP5971508B2 (ja) 2016-08-17

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