US20060035183A1 - Mixer - Google Patents

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Publication number
US20060035183A1
US20060035183A1 US11/202,208 US20220805A US2006035183A1 US 20060035183 A1 US20060035183 A1 US 20060035183A1 US 20220805 A US20220805 A US 20220805A US 2006035183 A1 US2006035183 A1 US 2006035183A1
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US
United States
Prior art keywords
fluid
mixer
stream
passageway
axis
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.)
Abandoned
Application number
US11/202,208
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English (en)
Inventor
Richard Carroni
Timothy Griffin
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.)
General Electric Technology GmbH
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Individual
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 Individual filed Critical Individual
Assigned to ALSTOM TECHNOLOGY LTD reassignment ALSTOM TECHNOLOGY LTD ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: GRIFFIN, TIMOTHY, CARRONI, RICHARD
Publication of US20060035183A1 publication Critical patent/US20060035183A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/62—Mixing devices; Mixing tubes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F25/00—Flow mixers; Mixers for falling materials, e.g. solid particles
    • B01F25/10—Mixing by creating a vortex flow, e.g. by tangential introduction of flow components
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F25/00—Flow mixers; Mixers for falling materials, e.g. solid particles
    • B01F25/30—Injector mixers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2900/00—Special features of, or arrangements for burners using fluid fuels or solid fuels suspended in a carrier gas
    • F23D2900/14—Special features of gas burners
    • F23D2900/14021—Premixing burners with swirling or vortices creating means for fuel or air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2900/00—Special features of, or arrangements for burners using fluid fuels or solid fuels suspended in a carrier gas
    • F23D2900/14—Special features of gas burners
    • F23D2900/14701—Swirling means inside the mixing tube or chamber to improve premixing

Definitions

  • This invention relates to a mixer and a method for mixing first and second fluids.
  • the two fluids may be gases, e.g. air and a combustible gas, or a gas and a liquid, e.g. air and a liquid fuel, or liquids.
  • the mixer may, in particular, form part of a combustion device.
  • Venturi injectors are relatively simple devices for attaining reasonable mixing; however, the quality falls short of that achieved by the swirl-based concepts. Venturi units rely upon low local pressures to draw additive fluid into a carrier fluid; mixing is attained by virtue of the shear layer across the longitudinal jet of fluid, whose principal velocity component is axial.
  • U.S. Pat. No. 4,123,800 describes a mixer in which a certain degree of twisting motion is imparted to the flow downstream of the Venturi constriction, to further aid in mixing, by means of skewed grooves machined into the walls of the divergent section downstream of a throat section into which the additive fluid is injected. However, this twisting motion is only imparted near the walls, without significantly affecting the bulk of the flow, and does not meaningfully assist the mixing process.
  • the present invention provides a passageway along which a stream comprising the first fluid flows along an axis of the passageway, the passageway having, in sequence in the downstream direction, a convergent section, a throat, and a divergent section; an injector for introducing the second fluid into the stream in the passageway upstream of the divergent section; and a swirl generator in the passageway upstream of the convergent section.
  • the invention also provides a method of mixing fluids, comprising the sequential steps of:
  • FIG. 1 is a schematic axial section through one embodiment of a mixer
  • FIG. 2 is a graph of angular velocity, ⁇ , in the circumferential direction against radial distance, r, from the axis of a swirling stream created in a preferred embodiment of the mixer;
  • FIG. 3 shows the angular velocity field produced by the swirling stream having the radial distribution of angular velocity shown in FIG. 2 ;
  • FIG. 4 a is a cross-section through the convergent section of a mixer, showing one possible arrangement of injectors
  • FIG. 4 b in a view similar to FIG. 4 a, showing another possible arrangement of injectors
  • FIG. 5 is a schematic axial section through a mixer combined with a burner sector
  • FIG. 6 is an inlet end view of the mixer in FIG. 5 ;
  • FIG. 7 is an outlet end view of the burner sector.
  • the mixer illustrated in FIG. 1 comprises a passageway 1 having an axis 2 along which a stream of air (the carrier fluid or first fluid) flows in the direction of the arrow 3 .
  • the passageway 1 has an upstream end portion or inlet section 4 which is cylindrical, a convergent section 6 which is conical and which converges at an angle ⁇ with respect to the axis 2 , a divergent section 7 which is conical and diverges at an angle a with respect to the axis 2 , and a downstream end portion or outlet section 8 which is cylindrical.
  • the passageway has a throat 9 between the convergent and divergent sections 6 , 7 ; in the embodiment illustrated, the throat 9 is of negligible axial length.
  • the convergent section 6 , throat 9 , and divergent section 7 together constitute a Venturi section.
  • An injector comprising a plurality of injection ports 11 in the peripheral wall 12 of the passageway 1 introduces fuel (the additive fluid or second fluid) into the stream in the convergent section 6 at multiple locations along and around the axis 2 .
  • the additive fluid is a liquid, it can be injected as sprays, and droplet atomisation and penetration can be enhanced by using high-pressure injectors.
  • a swirl generator 13 is provided in the inlet section 4 of the passageway 1 . This imparts swirl to the bulk flow of the carrier fluid prior to the convergent section 6 and prior to the injection of the fuel. Conservation of angular momentum results in increased angular velocities of the swirling stream at the throat 9 . Such a configuration enhances mixing between the carrier fluid and additive fluid by virtue of the circumferential shear layers which are formed. These shear layers promote cross-stream diffusion. Mixing begins earlier than in a conventional Venturi injector and results in a longer time being available for mixing and a more uniform concentration profile.
  • FIG. 2 is a graph of the angular velocity, ⁇ , in the circumferential direction against radial distance, r, from the axis 2 , illustrating a radical form of such an angular velocity profile.
  • FIG. 3 A swirling velocity field resulting from the application of inlet angular velocities similar to those of FIG. 2 is depicted in FIG. 3 .
  • a swirl generator 13 In order to generate such an angular velocity profile, a swirl generator 13 is used in which the swirl angle varies in the radial direction, typically increasing with distance from the axis.
  • vortex breakdown Whilst strong levels of swirl are beneficial to mixing, vortex breakdown has to be avoided if flashback is to be prevented in combustion applications.
  • vortex breakdown is promoted by expansion downstream of a swirl generator, we have found that vortex breakdown does not occur so readily if a convergent section is placed between the swirl generator and the divergent section.
  • studies have shown that abrupt changes in tangential velocity profiles tend to reduce the tendency of vortex breakdown. Instead, flashback is hindered by the strongly swirling axial jet which is formed.
  • the value of ⁇ required to avoid vortex breakdown is a function of the angular velocity profile produced by the swirl generator 13 . For example, we have found that (for a given operating condition, i.e.
  • ⁇ should lie between 15° and 25°, whereas in a configuration where the swirl angle changes from 15° to 30°, ⁇ may be reduced to less than 15°.
  • the nature of the divergence downstream of the throat 9 can be selected for various needs. If recirculation zones are not desired, expansion must not be sudden, so a more gradual increase in the cross-section of the divergent section 7 is needed. Such a configuration may be applicable to cases where no negative axial velocities are desired, for example in catalytic combustion.
  • the mixer may be used for premixed combustion, in which case sudden expansion serves to aerodynamically anchor the homogeneous flame.
  • the mixer does not require the large inlet to throat diameter ratio (typically 2) normally necessary for strongly accelerating a carrier fluid, because of the high degree of mixing resulting from tangential shear in the carrier fluid, for which the axial velocities need no longer be so high.
  • the present mixer if flow separation is to be avoided, small angles of divergence are still necessary, but the relatively large throat diameter results in shorter diffusers and hence smaller pressure losses. Such a saving of space may be highly advantageous in catalytic combustion applications.
  • the peripheral wall 12 of the passageway may be coated with a catalytic material for the purpose of quenching radicals, which are precursors of homogeneous ignition and combustion. This assists in preventing flashback and flame anchoring, these two phenomena being encouraged by the lower velocities encountered in the boundary layer near the peripheral wall.
  • the injection ports 11 may simply be holes which each face the axis 2 . However, introducing the additive fluid in a direction which is skewed to the axis 2 results in increased turbulence and better mixing of the additive fluid with the carrier fluid.
  • FIGS. 4 a and 4 b show possible orientations of the injection ports 11 . In FIG. 4 a the ports 11 are symmetrically arranged with respect to planes containing the axis of the passageway. In FIG. 4 b the ports 11 are angled so as to assist the swirling motion of the carrier fluid. However, the injection ports may instead be angled in the opposite sense with respect to the swirl direction of the carrier fluid.
  • Injection ports 11 of different sizes may be provided in order to achieve different depths of penetration of the additive fluid into the stream.
  • Fuels which are particularly prone to causing flashback due to their high flames speeds and diffusivity for example hydrogen-containing gases such as synthesis gas, can be used in the mixer because of the very high velocities achievable and the possibility of avoiding recirculation zones.
  • the swirl generator 13 may surround a central member or mandrel, which may be in the form of a central injection tube for providing a central air jet hindering the formation of recirculating regions at the exit.
  • the swirl generator 13 may circumferentially surround a central fuel injection lance, which could additionally inject air, in order to further enhance mixing.
  • FIG. 5 illustrates such an embodiment.
  • the circular cross-section of the divergent section 7 gradually changes into a sector of an annulus ( FIG. 7 ) in which a number of burners 14 are located (three burners being shown by way of example).
  • the burners 14 may be very simple (e.g. utilising sudden expansion without swirl) because complete fuel/air mixing has already been achieved prior to entry into the burners.
  • a flow straightener 16 which has also has the function of flashback prevention is placed near the exit of the divergent section 7 , upstream of the burners 14 .
  • the flow straightener 16 has a similar construction to the swirl generator 13 , except that it has straight channels. Flow straightening ensures that the flow distribution into each burner is identical. Small channels (hydraulic diameter typically less than 5 mm) act as flame arrestors. The channels may be coated with a catalyst for quenching radicals, further hindering flashback. In order to minimise pressures losses, the flow straightener has a very small axial length, typically less than 15 mm.
  • the embodiment of FIG. 5 can be used for liquid fuels if the geometry ensures very high velocities such that the mixer residence time (i.e. the time taken for the fuel to move from the injection point to the burners) is very short, typically less than 3 ms at 3 bar.
  • the mixer could be used for mixing any two (or more) different fluids. It is possible to introduce the second fluid into the passageway at any convenient location upstream of the divergent section 7 .
  • the throat 9 may be of substantial length and the second fluid may be introduced into the throat.
  • the second fluid may be introduced into the inlet section 4 (upstream or, preferably, downstream of the swirl generator 13 ).
  • the second fluid may be introduced through a tube extending along the axis 2 . It is also possible to introduce at least one further fluid into the passageway upstream of the divergent section 7 .

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  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Confectionery (AREA)
  • Input Circuits Of Receivers And Coupling Of Receivers And Audio Equipment (AREA)
  • Separation By Low-Temperature Treatments (AREA)
  • Vehicle Body Suspensions (AREA)
US11/202,208 2003-02-14 2005-08-12 Mixer Abandoned US20060035183A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB0303495.6 2003-02-14
GB0303495A GB2398375A (en) 2003-02-14 2003-02-14 A mixer for two fluids having a venturi shape
PCT/EP2004/050074 WO2004071637A1 (en) 2003-02-14 2004-02-03 Mixer

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2004/050074 Continuation WO2004071637A1 (en) 2003-02-14 2004-02-03 Mixer

Publications (1)

Publication Number Publication Date
US20060035183A1 true US20060035183A1 (en) 2006-02-16

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US11/202,208 Abandoned US20060035183A1 (en) 2003-02-14 2005-08-12 Mixer

Country Status (6)

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US (1) US20060035183A1 (de)
EP (1) EP1592495B1 (de)
AT (1) ATE357965T1 (de)
DE (1) DE602004005572T2 (de)
GB (1) GB2398375A (de)
WO (1) WO2004071637A1 (de)

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090000287A1 (en) * 2007-05-15 2009-01-01 Jared Dean Blaisdell Exhaust Gas Flow Device
US20090019842A1 (en) * 2007-07-20 2009-01-22 Mitsubishi Fuso Truck And Bus Corporation Exhaust purification device for engine
US20100269516A1 (en) * 2007-11-27 2010-10-28 Alstom Technology Ltd Method for operating a gas turbine installation and equipment for carrying out the method
US20110033806A1 (en) * 2008-04-01 2011-02-10 Vladimir Milosavljevic Fuel Staging in a Burner
US20110088375A1 (en) * 2008-03-27 2011-04-21 Mitsubishi Fuso Truck And Bus Corporation Exhaust purification apparatus for internal combustion engine
CN104492619A (zh) * 2014-12-04 2015-04-08 苏州国环环境检测有限公司 溶液定向浓度调节系统
US9046265B2 (en) 2010-08-16 2015-06-02 Alstom Technology Ltd Reheat burner
CN105605579A (zh) * 2016-02-26 2016-05-25 上海诺特飞博燃烧设备有限公司 一种金属纤维低氮燃烧装置的风燃全预混器
US20160334100A1 (en) * 2014-01-09 2016-11-17 A. O. Smith (China) Water Heater Co., Ltd. Multi-cavity gas and air mixing device
US20160362785A1 (en) * 2015-06-15 2016-12-15 Samsung Electronics Co., Ltd. Apparatus for manufacturing semiconductor device having a gas mixer
CN106440798A (zh) * 2016-11-29 2017-02-22 德米特（苏州）电子环保材料有限公司 煅烧设备
US9810126B2 (en) 2010-01-12 2017-11-07 Donaldson Company, Inc. Flow device for exhaust treatment system

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1828684A1 (de) * 2004-12-23 2007-09-05 Alstom Technology Ltd Vormischbrenner mit mischstrecke
WO2006075452A1 (ja) * 2005-01-13 2006-07-20 National University Corporation University Of Tsukuba マイクロバブル発生装置、マイクロバブル発生装置用渦崩壊用ノズル、マイクロバブル発生装置用旋回流発生用翼体、マイクロバブル発生方法およびマイクロバブル応用装置
ITMO20060007A1 (it) * 2006-01-13 2007-07-14 Maurizio Iacobucci Bruciatore per forni per prodotti ceramici
EP2211109A1 (de) * 2009-01-23 2010-07-28 Alstom Technology Ltd Brenner einer Gasturbine und Verfahren zum Mischen eines Kraftstoffs mit einem gasförmigen Strom
DE102017208570A1 (de) * 2017-05-19 2018-11-22 Thyssenkrupp Ag Fluidmischvorrichtung
DE102019126786A1 (de) * 2019-10-04 2021-04-08 SQW Sauerländer Quality Water GmbH & Co. KG Vorrichtung, System und Verfahren zur Reduzierung einer Oberflächenspannung und/oder einer Viskosität eines Fluids

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US1722253A (en) * 1926-12-14 1929-07-23 Coen Co Combination burner mounting and air control
US1971328A (en) * 1929-08-06 1934-08-28 William H Byrne Fuel burner
US2146250A (en) * 1937-03-18 1939-02-07 Elia Joseph A D Oil burner
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US2446059A (en) * 1944-10-05 1948-07-27 Peabody Engineering Corp Gas heater
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US3179152A (en) * 1961-02-09 1965-04-20 Babcock & Wilcox Co Combination oil and gas burner
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US3391981A (en) * 1966-06-13 1968-07-09 Coen Company Forced air draft burner construction for combustible gases
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Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8915064B2 (en) * 2007-05-15 2014-12-23 Donaldson Company, Inc. Exhaust gas flow device
US20090000287A1 (en) * 2007-05-15 2009-01-01 Jared Dean Blaisdell Exhaust Gas Flow Device
US9422844B2 (en) * 2007-07-20 2016-08-23 Mitsubishi Fuso Truck And Bus Corporation Exhaust purification device for engine
US20090019842A1 (en) * 2007-07-20 2009-01-22 Mitsubishi Fuso Truck And Bus Corporation Exhaust purification device for engine
US20100269516A1 (en) * 2007-11-27 2010-10-28 Alstom Technology Ltd Method for operating a gas turbine installation and equipment for carrying out the method
US10208960B2 (en) * 2007-11-27 2019-02-19 Ansaldo Energia Switzerland AG Method for operating a gas turbine installation and equipment for carrying out the method
US20110088375A1 (en) * 2008-03-27 2011-04-21 Mitsubishi Fuso Truck And Bus Corporation Exhaust purification apparatus for internal combustion engine
US8683783B2 (en) * 2008-03-27 2014-04-01 Mitsubishi Fuso Truck And Bus Corporation Exhaust purification apparatus for internal combustion engine
US20110033806A1 (en) * 2008-04-01 2011-02-10 Vladimir Milosavljevic Fuel Staging in a Burner
US9810126B2 (en) 2010-01-12 2017-11-07 Donaldson Company, Inc. Flow device for exhaust treatment system
US9046265B2 (en) 2010-08-16 2015-06-02 Alstom Technology Ltd Reheat burner
US20160334100A1 (en) * 2014-01-09 2016-11-17 A. O. Smith (China) Water Heater Co., Ltd. Multi-cavity gas and air mixing device
US10823400B2 (en) * 2014-01-09 2020-11-03 A.O. Smith Corporation Multi-cavity gas and air mixing device
CN104492619A (zh) * 2014-12-04 2015-04-08 苏州国环环境检测有限公司 溶液定向浓度调节系统
US20160362785A1 (en) * 2015-06-15 2016-12-15 Samsung Electronics Co., Ltd. Apparatus for manufacturing semiconductor device having a gas mixer
CN105605579A (zh) * 2016-02-26 2016-05-25 上海诺特飞博燃烧设备有限公司 一种金属纤维低氮燃烧装置的风燃全预混器
CN106440798A (zh) * 2016-11-29 2017-02-22 德米特（苏州）电子环保材料有限公司 煅烧设备

Also Published As

Publication number Publication date
GB2398375A (en) 2004-08-18
DE602004005572T2 (de) 2007-12-06
WO2004071637A1 (en) 2004-08-26
DE602004005572D1 (en) 2007-05-10
GB0303495D0 (en) 2003-03-19
EP1592495B1 (de) 2007-03-28
ATE357965T1 (de) 2007-04-15
EP1592495A1 (de) 2005-11-09

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