EP1876390A1 - Méthode pour la production de vapeur dans une chaudière à tube de gaz et chaudière à tube de gaz pour la utilisation de cette méthode - Google Patents

Méthode pour la production de vapeur dans une chaudière à tube de gaz et chaudière à tube de gaz pour la utilisation de cette méthode Download PDF

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Publication number
EP1876390A1
EP1876390A1 EP06388049A EP06388049A EP1876390A1 EP 1876390 A1 EP1876390 A1 EP 1876390A1 EP 06388049 A EP06388049 A EP 06388049A EP 06388049 A EP06388049 A EP 06388049A EP 1876390 A1 EP1876390 A1 EP 1876390A1
Authority
EP
European Patent Office
Prior art keywords
steam
flow
gas
distance
wall
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Withdrawn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
EP06388049A
Other languages
German (de)
English (en)
Inventor
Bodil Irene Mosekaer Nielsen
Thomas Paarup Pedersen
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.)
Alfa Laval Aalborg AS
Original Assignee
Aalborg Industries AS
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 Aalborg Industries AS filed Critical Aalborg Industries AS
Priority to EP06388049A priority Critical patent/EP1876390A1/fr
Priority to CN2007800326447A priority patent/CN101512223B/zh
Priority to EP07764471.4A priority patent/EP2044365B1/fr
Priority to PCT/DK2007/000342 priority patent/WO2008003322A1/fr
Priority to KR1020097002269A priority patent/KR101009212B1/ko
Priority to JP2009516904A priority patent/JP2009541705A/ja
Priority to DK07764471.4T priority patent/DK2044365T3/da
Publication of EP1876390A1 publication Critical patent/EP1876390A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/0206—Heat exchangers immersed in a large body of liquid
    • F28D1/0213—Heat exchangers immersed in a large body of liquid for heating or cooling a liquid in a tank
    • 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
    • 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
    • F22B1/1884—Hot gas heating tube boilers with one or more heating tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B9/00—Steam boilers of fire-tube type, i.e. the flue gas from a combustion chamber outside the boiler body flowing through tubes built-in in the boiler body
    • F22B9/02—Steam boilers of fire-tube type, i.e. the flue gas from a combustion chamber outside the boiler body flowing through tubes built-in in the boiler body the boiler body being disposed upright, e.g. above the combustion chamber
    • F22B9/04—Steam boilers of fire-tube type, i.e. the flue gas from a combustion chamber outside the boiler body flowing through tubes built-in in the boiler body the boiler body being disposed upright, e.g. above the combustion chamber the fire tubes being in upright arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G3/00—Steam superheaters characterised by constructional features; Details of component parts thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G3/00—Steam superheaters characterised by constructional features; Details of component parts thereof
    • F22G3/006—Steam superheaters with heating tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates

Definitions

  • the present invention relates to a method of producing steam in a gas tube steam boiler and a gas tube steam boiler for implementing said method.
  • the primary design parameters are involving the input gas temperature, the exhaust gas temperature and the desired maximum energy output, i.e. feed water temperature, steam pressure, temperature and mass flow.
  • the steam should be dry or even more preferred superheated.
  • the heat transfer from the gas tubes to the steam in the steam head space is significantly improved, whereby the efficiency of the boiler is increased and at the same time the produced steam has a higher quality by being dried and possibly superheated.
  • said horizontal projection of said flow path is at least two times said distance.
  • the steam outlet is located at a distance from the axis of the wall, preferably proximate to the wall of the head space, thus restricting the steam flow to flow sideways along all of the gas tubes before leaving through the steam outlet.
  • the horizontal projection of the flow path extends from proximate or at a first point on said wall past said axis to proximate or at a second point on said wall opposite said first point and preferably extends back from the second point and at least partways back to said first point.
  • the steam flow is caused to move past all of the gas tubes, preferably at least two times before leaving through the steam outlet steam outlet.
  • the steam flow velocity is lower when flowing from the second point towards the first point than when flowing from proximate said first point towards said second point, providing a relative high velocity, preferably approximately 15-30 m/s, more preferably 15-25 m/s over a part of the distance between the water surface and the steam outlet and to pass the gas tubes at a reduced velocity, preferably approximately 10-15 m/s over a subsequent part of the path from the water surface to the steam outlet, whereby the high velocity provides a turbulent flow around the gas tubes securing a high heat transfer and securing that possible droplets of water in the steam will hit the tubes and evaporate.
  • the hot gasses for the gas tubes are provided from a combustion chamber, combusting a fuel such as oil, carbon dust, natural gas, etc., however, also hot exhaust gasses from a gas turbine or an internal combustion motor and the like may be used.
  • a combustion chamber may be provided in contact with the water in the heat exchange compartment, in order to deliver further heating to the water directly from the combustion chamber.
  • the present invention relates to a gas tube steam boiler comprising
  • This gas tube steam boiler is particularly suited for carrying out the above method.
  • the present invention relates to a gas tube steam boiler comprising
  • the gas tube steam boiler shown in Fig. 1 comprises a heat exchange compartment 2 filled with water, said water forming a water surface 2a, and a steam head space 8 above said water surface and delimited by a cylindrical wall 1 with a substantially vertical axis 10, a top plate 4 and a diameter D.
  • a steam outlet 6 is connected to the steam head space 8 and several gas tubes 3 extend through the heat exchange compartment 2 and the steam head space 8. Heated gas flows through the gas tubes 3 in order to generate a flow of steam from the water surface by heat exchange between the gas tubes 3 and the water in the heat exchange compartment 2.
  • the steam flow from the water surface is caused to flow along a conduit delimited by the baffle plates 7', 7", whereby said steam is made to flow in a direction transverse to the gas tubes 3 and all of the steam in the flow is constrained to flow between the two baffle plates 7', 7" in a horizontal direction and back between the upper baffle plate 7" and the top plate 4 in an opposite horizontal direction and out through the steam outlet 6.
  • the two baffle plates 7', 7" each covers a smaller area than the cross sectional area of the steam head space 5 and the edges of the two baffle plates 7', 7" are connected to vertical plates 9 extending from the top plate 4 down to the lower baffle plate 7' in the vertical direction and in the horizontal direction all the way across between individual positions on the cylindrical wall of the steam head space 5.
  • the gas tubes 3 extend from the bottom of the boiler, possibly from a combustion chamber 14 as shown in Fig. 2 up through the water filled heat exchange compartment 2 and the steam head space 5, where the gas tubes 3 extend through the plates 7', 7" and through holes in the top plate 4, from where the gas leaves through a gas exhaust 11.
  • the water level inside the boiler corresponds to the level measured with different traditional equipment, such as pressure difference between two known levels, water level glasses, etc.
  • the actual water level seen inside the boiler will rise because of the presence of a large amount of steam bubbles inside the water area, and the water level will be fluctuating more or less, dependent on the heat load and the steam pressure.
  • the highest water level will be around the gas tubes 3 and accordingly the gas tubes are wetted by water up to this water level, which typically is about 250 mm above the measured water level, in the following named water surface in cold condition.
  • the total height h of the steam head space 5 is subdivided into the distance h1 between the top plate 4 and the first plate 7", the distance h2 between the first plate 7" and the second plate 7', and finally the distance h3 between the second plate 7' and the water surface in cold condition.
  • the distances h1 and h2 are dimensioned in such a way that the steam velocity between the top plate 4 and the first plate 7" is approximately 10-15 m/s and the steam velocity between the two plates 7' and 7" is approximately 20-30 m/s., i.e. the distance h1 is approximately two times the distance h2. Under all circumstances the distance h3 should be sufficient to secure that during boiling at full load, the actual water level should be approximately 200 mm below the second plate 7'.
  • the flow of the steam perpendicular to the gas tubes 3 is relatively high between the two plates 7', 7", a bit lower between the top plate 4 and the plate 7" and even between the water surface and the plate 7' a certain cross flow relative to the gas tubes 3 will be present.
  • the steam velocity provides a higher heat transfer coefficient from the gas tubes 3 to the steam compared to a traditional situation in which the steam head space 5 transmits steam at a low velocity, substantially parallel to the tubes.
  • the heat transfer is close to the same heat transfer that exists in the water filled heat exchange compartment 2 in which water is in direct contact with the gas tubes 3.
  • the produced steam is not only free of water droplets when it leaves the boiler through the steam outlet 6, but it is actually superheated. This superheating ensures that no salts leave the boiler, resulting in that there will be no deposits in the steam pipe from the boiler to the user.
  • a possible steam outlet valve after the steam outlets can be dimensioned to a higher steam velocity, which means that the size of the valve can be reduced, thus saving both space, weight and costs for said steam outlet valve.
  • the total heating surface can be reduced due to increased heat transfer, which means reduced tube length, number of tubes, boiler height and thus both weight and cost price for the boiler.
  • the direct result of using the present invention is that approximately 40% of the tubes (approximately 240 kg) in the standard boiler design can be saved. Furthermore, the tube length and accordingly the boiler height is shortened by 520 mm, which with a boiler diameter of 1300 and a plate thickness of 12 mm provides a difference in plate weight of approximately 200 kg.
  • the steam flow is restricted to a helically flow path by means of a helically shaped plate positioned between a central tube and the outer wall of the boiler 1, said steam flow path again having a length corresponding to at least the distance between two opposite point of the wall of the boiler 1.

Landscapes

  • 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)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP06388049A 2006-07-05 2006-07-05 Méthode pour la production de vapeur dans une chaudière à tube de gaz et chaudière à tube de gaz pour la utilisation de cette méthode Withdrawn EP1876390A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP06388049A EP1876390A1 (fr) 2006-07-05 2006-07-05 Méthode pour la production de vapeur dans une chaudière à tube de gaz et chaudière à tube de gaz pour la utilisation de cette méthode
CN2007800326447A CN101512223B (zh) 2006-07-05 2007-07-05 一种在气体管道蒸汽锅炉中产生蒸汽的方法以及用于实现所述方法的气体管道蒸汽锅炉
EP07764471.4A EP2044365B1 (fr) 2006-07-05 2007-07-05 Méthode pour la production de vapeur dans une chaudière à tubes de gaz et chaudière à tubes de gaz
PCT/DK2007/000342 WO2008003322A1 (fr) 2006-07-05 2007-07-05 Procédé de production de vapeur dans une chaudière à vapeur à tube de gaz et chaudière à vapeur à tube de gaz pour mettre en œuvre ledit procédé
KR1020097002269A KR101009212B1 (ko) 2006-07-05 2007-07-05 가스 튜브 스팀 보일러에 스팀을 생성하는 방법 및 상기 방법을 사용하는 가스 튜브 스팀 보일러
JP2009516904A JP2009541705A (ja) 2006-07-05 2007-07-05 ガス管蒸気ボイラーの蒸気生成方法及び上記方法を実施するためのガス管蒸気ボイラー
DK07764471.4T DK2044365T3 (da) 2006-07-05 2007-07-05 Fremgangsmåde til produktion af damp i en gasrørsdampkedel og gasrørsdampkedel

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06388049A EP1876390A1 (fr) 2006-07-05 2006-07-05 Méthode pour la production de vapeur dans une chaudière à tube de gaz et chaudière à tube de gaz pour la utilisation de cette méthode

Publications (1)

Publication Number Publication Date
EP1876390A1 true EP1876390A1 (fr) 2008-01-09

Family

ID=38016951

Family Applications (2)

Application Number Title Priority Date Filing Date
EP06388049A Withdrawn EP1876390A1 (fr) 2006-07-05 2006-07-05 Méthode pour la production de vapeur dans une chaudière à tube de gaz et chaudière à tube de gaz pour la utilisation de cette méthode
EP07764471.4A Not-in-force EP2044365B1 (fr) 2006-07-05 2007-07-05 Méthode pour la production de vapeur dans une chaudière à tubes de gaz et chaudière à tubes de gaz

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP07764471.4A Not-in-force EP2044365B1 (fr) 2006-07-05 2007-07-05 Méthode pour la production de vapeur dans une chaudière à tubes de gaz et chaudière à tubes de gaz

Country Status (6)

Country Link
EP (2) EP1876390A1 (fr)
JP (1) JP2009541705A (fr)
KR (1) KR101009212B1 (fr)
CN (1) CN101512223B (fr)
DK (1) DK2044365T3 (fr)
WO (1) WO2008003322A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2789909A1 (fr) * 2013-04-12 2014-10-15 RETECH Spólka z o.o. Générateur de vapeur
CN109000214A (zh) * 2018-08-28 2018-12-14 郭召海 油田专用过热蒸汽发生器及其应用工艺

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1546665A (en) * 1921-06-18 1925-07-21 Frank F Landis Steam boiler
FR809123A (fr) * 1935-11-19 1937-02-24 Chaudière à vapeur
GB1140222A (en) * 1965-02-12 1969-01-15 Schmidt Sche Heissdampf Improvements relating to gas coolers
US3437077A (en) * 1966-01-21 1969-04-08 Babcock & Wilcox Co Once-through vapor generator
US4991408A (en) * 1989-09-29 1991-02-12 John Liszka Adiabatic separator
DE10237681A1 (de) * 2002-08-16 2004-03-04 Ritter Energie- Und Umwelttechnik Gmbh & Co. Kg Plattenwärmetauscher für Schwerkraftumwälzung in Wärmespeichern

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2044684U (zh) * 1989-02-17 1989-09-20 孙继忠 蒸汽净化罐
JP3126487B2 (ja) 1992-04-28 2001-01-22 東京エレクトロン株式会社 酸化処理装置
US5653282A (en) * 1995-07-19 1997-08-05 The M. W. Kellogg Company Shell and tube heat exchanger with impingement distributor
JP2000088478A (ja) * 1998-09-14 2000-03-31 Osaka Gas Co Ltd 熱交換器
CN2385220Y (zh) * 1999-06-25 2000-06-28 刘强 常压立式蒸汽锅炉
JP4313605B2 (ja) * 2003-05-06 2009-08-12 株式会社神戸製鋼所 流体冷却器
KR100530265B1 (ko) * 2005-05-17 2005-11-22 김도연 스팀 발생 장치

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1546665A (en) * 1921-06-18 1925-07-21 Frank F Landis Steam boiler
FR809123A (fr) * 1935-11-19 1937-02-24 Chaudière à vapeur
GB1140222A (en) * 1965-02-12 1969-01-15 Schmidt Sche Heissdampf Improvements relating to gas coolers
US3437077A (en) * 1966-01-21 1969-04-08 Babcock & Wilcox Co Once-through vapor generator
US4991408A (en) * 1989-09-29 1991-02-12 John Liszka Adiabatic separator
DE10237681A1 (de) * 2002-08-16 2004-03-04 Ritter Energie- Und Umwelttechnik Gmbh & Co. Kg Plattenwärmetauscher für Schwerkraftumwälzung in Wärmespeichern

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2789909A1 (fr) * 2013-04-12 2014-10-15 RETECH Spólka z o.o. Générateur de vapeur
CN109000214A (zh) * 2018-08-28 2018-12-14 郭召海 油田专用过热蒸汽发生器及其应用工艺
CN109000214B (zh) * 2018-08-28 2024-04-02 新疆桑顿能源科技有限公司 油田专用过热蒸汽发生器及其应用工艺

Also Published As

Publication number Publication date
KR20090031606A (ko) 2009-03-26
JP2009541705A (ja) 2009-11-26
EP2044365B1 (fr) 2013-05-15
EP2044365A1 (fr) 2009-04-08
KR101009212B1 (ko) 2011-01-19
CN101512223A (zh) 2009-08-19
DK2044365T3 (da) 2013-08-12
CN101512223B (zh) 2011-12-07
WO2008003322A1 (fr) 2008-01-10

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