EP0428174A2 - Dispositif de mélange avec flamme tourbillonnante pour brûleur à huile - Google Patents

Dispositif de mélange avec flamme tourbillonnante pour brûleur à huile Download PDF

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Publication number
EP0428174A2
EP0428174A2 EP90121914A EP90121914A EP0428174A2 EP 0428174 A2 EP0428174 A2 EP 0428174A2 EP 90121914 A EP90121914 A EP 90121914A EP 90121914 A EP90121914 A EP 90121914A EP 0428174 A2 EP0428174 A2 EP 0428174A2
Authority
EP
European Patent Office
Prior art keywords
burner tube
baffle plate
slots
constriction
nozzle
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
EP90121914A
Other languages
German (de)
English (en)
Other versions
EP0428174B1 (fr
EP0428174A3 (en
Inventor
Harro Kaminski
Engelbert Wittek
Armin Borth
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.)
ELECTRO-OIL GmbH
Original Assignee
ELECTRO-OIL 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 ELECTRO-OIL GmbH filed Critical ELECTRO-OIL GmbH
Publication of EP0428174A2 publication Critical patent/EP0428174A2/fr
Publication of EP0428174A3 publication Critical patent/EP0428174A3/de
Application granted granted Critical
Publication of EP0428174B1 publication Critical patent/EP0428174B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/36—Details, e.g. burner cooling means, noise reduction means
    • F23D11/40—Mixing tubes or chambers; Burner heads
    • F23D11/406—Flame stabilising means, e.g. flame holders

Definitions

  • the invention relates to a swirl flame mixing device for oil burners with an atomizer nozzle arranged in a downstream conically narrowed burner tube, with an axially displaceable baffle plate assigned to the atomizer nozzle, which has a central opening, from which slots extend radially outwards, which pass through from the Plane of the baffle plate bent wing-like sections are formed, and which is provided with a cylindrical boundary in continuation of its outer circumference - seen in the direction of flow.
  • a generic mixing device is already from the DE-PS 35 42 174 known.
  • a smaller diameter guide tube is arranged in the burner tube, which is axially adjustable and receives a potty-shaped baffle plate.
  • the baffle plate is used to hold the flame, ie it establishes a balance between the outflow speed of a fuel-air mixture and the re-ignition speed of the flame when recirculation is intended in the combustion chamber.
  • the baffle plate forms an adjustable annular gap with the burner tube, the baffle plate being flowed through by a primary air stream for a substoichiometric pre-combustion and the annular gap by a secondary air stream for a complete combustion of the heating oil.
  • the heating oil passes from the atomizer nozzle into the combustion zone through a central opening in the downstream baffle plate, which forms a six-pointed passage.
  • Slits in the baffle plate give the primary air passing through a swirl, which promotes a mixture of heating oil and air and gasification of the heating oil.
  • a relatively large slot width in the area of the central opening achieves a locally limited strong swirl effect, which favors the ignition after each control activation of the burner.
  • this mixing device has the disadvantage that the Swirl movement of the combustion gas mixture is converted relatively unhindered into an axial astronomical movement, whereby the mixing of heating oil and air and gasification of the heating oil are impaired.
  • This is supported by the primary air flowing at a high speed of, for example, more than 10 meters per second through the central opening of the baffle plate in jet form, which impedes the desired swirling in the center of the mixing and combustion zone and reduces the ignitability of the combustion gas mixture with its shock pulse .
  • the secondary air flowing primarily in the axial direction of the burner tube reduces the swirl of the combustion gas mixture.
  • DE-GM 77 24 029 discloses a similar mixing device in which the guide tube is provided with four fins evenly distributed around the circumference, which are formed by means of angle profile pieces and ensure that the guide tube is inserted exactly coaxially into the burner tube.
  • this support of the guide tube and the baffle plate used is relatively complex in terms of design and does not change the swirl-reducing effect of the axially aligned secondary air flow.
  • DE-PS 24 61 078 already discloses a furnace with a burner which has an annular gap on the outside for the supply of secondary air which, before exiting into a combustion chamber, flows through openings in a plate to which vane-shaped baffles are assigned in order to deflect the air to the outside of the flame core, so that an air jacket is formed with a helical flow direction.
  • the perforated plate has high pressure losses and, due to discontinuous transitions, produces an incompletely formed swirl-jacket flow which does not yet have the desirable mixing and gasification effect.
  • the additional swirl plate holding a central guide tube is relatively complex to manufacture.
  • the object of the invention is to create an improved mixing device for oil burners which gives the flame an increased swirl which favors the ignition and practically pollutant-free combustion of the heating oil.
  • the burner tube has a constriction protruding radially downstream of the conical narrowing.
  • the constriction provided according to the invention reduces the flame escape speed in the axial direction of the burner tube and thus supports the baffle plate already provided as the flame holding device.
  • the swirl of the primary air of the flame is retained to a greater extent, so that an intensive mixing of the heating oil with the air and its greater gasification takes place in a mixing zone before the constriction.
  • the result is an intensely mixed combustion gas which promotes rapid combustion with a shorter flame with the characteristic of a so-called "blue flame", whereby less solid carbon, but more carbon monoxide is processed.
  • there is practically no soot in the exhaust gas smaller amounts of carbon monoxide are contained in the exhaust gas and a reduction in nitrogen oxide formation can also be found.
  • the ratio of a smallest constriction diameter to a smallest diameter of the adjacent conical constriction is approximately 0.85 to 0.8, a practically satisfactory reduction in the flame escape speed being achieved while increasing the flame swirl.
  • the constriction is formed by an annular body - preferably by crimping a burner tube mouth - held in the burner tube.
  • Different applications can be easily taken into account by using different ring bodies.
  • the constriction is formed by a shaping, in particular crimping, of the burner tube opening of the burner tube, thereby saving an additional component.
  • the constriction forms a conical nozzle with a cone angle of 90 ° to 180 °, the cone tip of which lies in front of or in the plane of the burner tube opening.
  • the nozzle is e.g. formed by an annular body held in the burner tube or a shape of the burner tube and in particular causes a low-loss and uniform outflow behavior of the combustion products.
  • the burner tube in addition to the burner tube mouth, has several, preferably evenly, distributed around the burner tube longitudinal axis to the burner tube center aligned rib-like projections has that the projections laterally guide the cylindrical boundary of the baffle plate, and that the projections have an angle of attack to the longitudinal axis of the burner tube.
  • the angle of attack can be 0 °, but is preferably significantly larger.
  • the projections provided according to the invention form, on the one hand, a guide which is favorable in terms of production technology and a lateral holder for the baffle plate.
  • they give the secondary air flow a swirl due to its angle of attack above 0 ° to the longitudinal axis of the burner tube, which stabilizes the enclosed flame and can support the swirl of the primary air flow.
  • the swirl of the secondary air thus also hinders a conversion of the rotary movement of the primary air into a longitudinal movement.
  • the projections are drop-shaped in a section parallel to the longitudinal axis of the burner tube.
  • the correspondingly known wing profiles with drop-shaped projections in cross-section ensure a well-formed swirl flow of the secondary air and uniform and controlled flow conditions in the mixing and combustion zone.
  • the projections to the burner tube longitudinal axis preferably have an angle of attack of 15 to 45 °, as a result of which the desired short flame can be achieved with a sufficient flame escape speed.
  • the projections impart a secondary air flow passing between the burner tube and the cylindrical boundary of the dust disk in the same direction as the baffle plate of a primary air flow flowing through the slots, so that the swirl effect of the two partial air flows support one another.
  • the atomizer nozzle with a nozzle mouth protrudes into the central opening of the baffle plate and is arranged in the plane of the baffle plate .
  • the inventive arrangement of the nozzle mouth in The opening and plane of the baffle plate reduce the relatively large cross section of the opening. This ensures that a twisted air supply is also established in the center, ie that the jet passing through the opening is damped and rotated at least on the outer circumference by the swirl of the primary air from the adjacent slots. This also favors a better mixing of the heating oil into the combustion air and a stronger gasification of the heating oil and improves the ignitability of the combustion gas mixture in front of the atomizer nozzle.
  • the atomizer nozzle carries a pair of ignition electrodes, each of which is bent approximately S-shaped downstream in the longitudinal direction of the burner tube to the longitudinal axis of the burner tube, each ignition electrode at the electrode base and electrode tip being aligned approximately parallel to the longitudinal axis of the burner tube, and are the ignition electrodes through the central opening of the baffle plate passed and protrude with the electrode tips downstream over the level of the baffle plate.
  • the electrode tips arranged in this way lie in a region of the combustion gas mixture which is favorable for the ignition.
  • the ignition electrodes with the electrode tips preferably protrude about 3 mm above the level of the baffle plate.
  • the ignition electrodes are bent towards one another, starting from the electrode base, and are aligned approximately parallel to one another next to the electrode tip.
  • the electrode tips are preferably at a distance of about 3 mm from one another.
  • the width of the slots following the central opening is greater than in the central region and that the width of the slots in the middle area is dimensioned so that an air film formation is still achieved.
  • the width of the slots in the radially outer end region is larger than in the central region.
  • a strong air flow impinges more or less directly on the cylindrical boundary, in order then to be diverted to the tear-off edge while rotating in the cup. This is advantageous for keeping the outer slot areas free of coke deposits.
  • the course of the radially outer end regions of the slots is preferably such that the air flow passing through them meets the boundary at an angle of approximately 45 °. As a result, a relatively strong air flow is deflected through the cylindrical boundary and given a corresponding rotation.
  • the radially outer end region of the slots can be curved in an arc.
  • the slots are generally arc-shaped curved, for example with a single radius.
  • the arcuate course of the slots has the further advantage that the air flow passing through the slots is fanned out and the associated surface area of the baffle plate is fully acted upon.
  • the ratio of the radius of the boundary to the radius of the slots is preferably approximately 1.82.
  • An advantageous width of the slots in the radially inner and / or outer area can be approximately 2 mm.
  • the width of the slots in the middle area must be such that an air film is still formed. This is the case with a width of approximately 0.7 mm.
  • the central opening is six-pointed, the slots starting from the tips. This improves the manufacturing and flow conditions in particular.
  • the burner tube carries a coaxial tube sleeve which is in the direction of flow protrudes beyond the conical constriction, has a radially projecting constriction at the front and has injection openings opening into a gap between it and the burner tube.
  • the tube sleeve causes a tertiary gas flow through the injection openings in the area of the burner tube mouth due to the negative pressure prevailing there.
  • the tertiary flow results in a reduction in the pollutant content of the combustion gases.
  • the radially inward-directed tertiary flow reduces the flame escape speed in the axial direction, which is accompanied by the advantages already mentioned for constricting the burner tube.
  • the mixing device can have a constriction only on the tube sleeve, but can also be constricted on the tube sleeve and burner tube.
  • the internal dimensions of the constriction of the tube sleeve correspond to those of the constriction of the burner tube.
  • the constrictions of the tube sleeve and the burner tube are preferably at an axial distance of about 5 mm from one another.
  • the injection openings are arranged on the tube sleeve in the flow direction in front of the burner tube mouth, as a result of which the suction is promoted through the injection openings and a blow-out of the primary and secondary air flow through the injection openings is counteracted.
  • a single injection port is sufficient, e.g. in the form of an elongated hole.
  • the injection openings are preferably (elongated) holes distributed over the circumference of the tube sleeve.
  • Fig. 1 shows a device with a burner tube 1, which has a somewhat tapered, but cylindrical Mit telab4.000 2 and adjacent to it has a conical narrowing 3, which is formed along a mixing space of length A.
  • a conical narrowing 3 which is formed along a mixing space of length A.
  • six beads 4 are formed in the burner tube and delimit a partial cylinder surface area on the inside.
  • an annular body 6 is flanged into the burner tube 1, which limits the mixing space downstream in relation to a flow direction arrow ST.
  • An atomizing nozzle 7 is held in the burner tube 1 so as to be longitudinally displaceable.
  • the atomizer nozzle 7 carries on the outside a nozzle bushing 8 which is fixed with a locking screw 9.
  • a center disk 10 is attached upstream of the nozzle bushing 8 and serves air distribution purposes.
  • a holder 11 for a baffle plate 12 is fixed downstream on an end face of the nozzle bushing 8.
  • the baffle plate 12 has a central opening 13 and, starting therefrom, slots 14 which extend essentially radially outward.
  • the baffle plate 12 is connected on the outside via a peripheral edge bead 15 to a cylindrical boundary 16 which is guided on the inner surfaces of the beads 4 of the burner tube 1 .
  • Upstream is the Mixing space of length A limited by the baffle plate 12. Details of the nozzle bushing and the parts attached to it will be discussed below.
  • the combustion air flowing in the direction of flow ST is partially deflected radially outward from the center disk 10, so that a secondary air flow S flows through the channels between the burner tube 1, beads 4 and the cylindrical boundary 16 and reaches the mixing chamber of length A from the outside. Another portion of the combustion air passes as primary air flow P through the slots 14 and the opening 13 of the baffle plate 12 into the mixing chamber. Due to the orientation of the beads 4 and the slots 14, which will be explained further below, secondary and primary air flows each enter the mixing chamber with a rectified swirl, the conversion of which into an axial movement is impeded by the annular body 6.
  • heating oil is also added to the mixing chamber of length A, for which purpose the atomizing nozzle 7 projects with a nozzle mouth 17 into the central opening of the baffle plate 12 and is arranged exactly in the plane of the baffle plate. Due to the swirl of the combustion air, the heating oil emitted by the atomizing nozzle 7 is mixed finely in the mixing room and gasified at the same time.
  • the ignition electrodes 19 are bent approximately S-shaped in the longitudinal direction of the burner tube downstream of the longitudinal axis of the burner tube, wherein they are held in the carrier 18 with an electrode foot 20 oriented approximately parallel to the longitudinal axis of the burner tube. With an electrode tip 21 they reach through the opening 13 of the baffle plate 12, with an ignition distance Z of approximately 3 mm from the plane of the baffle plate 12, an electrode distance E of approximately 3 mm and an orifice distance M from the center of the nozzle mouth for optimum ignition 17 of approx. 6 mm.
  • the atomizing nozzle 7 together with the nozzle bushing 8 and the baffle plate 12 attached to it and the ignition electrodes 19 can be moved axially. If the baffle plate 12 is moved further downstream, the free cross section for the secondary air flow S is reduced due to the conical narrowing 3, so that this decreases at the expense of the primary air flow P.
  • the nozzle bushing 8 has a receptacle 22 on the inside corresponding to the outer contour of the atomizing nozzle 7 with threaded bores for the locking screw 9 and for the fastening screw of the carrier 18.
  • the center disk 10 and the holder 11 are each held on the face of the nozzle bushing 8 by crimping. 3 to 5 show, the holder 11 has a central retaining ring 22 for this purpose, from which three holding arms 23 extend and are guided to fastening tabs 24 for the baffle plate 12.
  • support arms 25 for the carrier 18 of the ignition electrodes are formed laterally on the retaining ring 22.
  • the central opening 13 of the baffle plate 12 has the shape of a six-pointed passage, the clear width of which is more than 15 mm.
  • the slots 14 extend from the tips of the opening 13 and are formed by wings 26 which are bent outwards from the plane of the baffle plate 12 (cf. FIG. 3).
  • the slots are curved in a circular arc, with variable slot widths in the radial direction. This and the arc shape of the slots causes a strong vortex formation near the opening 13 and a fanning out of the air flow over the entire surface area between the slots, so that a good ignitability is achieved and coking on the surface area is avoided.
  • the burner tube 1 has a cone angle ⁇ of approximately 12 ° in the area of the constriction 3.
  • the beads 4 have a teardrop-shaped profile parallel to the longitudinal axis of the burner tube and are inclined at an angle of attack ⁇ of approximately 15 ° to the longitudinal axis of the burner tube.
  • the angle of attack ⁇ is a maximum of approximately 45 °
  • the burner tube mouth 5 - as shown in FIGS. 7 and 8 - can also have a flange 27 or 28 adjacent to the conical constriction 3.
  • the crimp 27 aligned perpendicular to the longitudinal axis of the burner tube keeps the flame better in the mixing chamber, but causes greater flow losses.
  • the crimp 27 is equivalent to a nozzle with a cone angle of 180 °.
  • the flange 28 is inclined by approximately 45 ° to the longitudinal axis of the burner tube, which is equivalent to a nozzle angle ⁇ of 90 °. This keeps the swirl in the flame when the flow losses are not too high.
  • the burner tube 1 has an essentially cylindrical tube sleeve 29 which is pushed onto the cylindrical central section 2 and welded there, which projects somewhat beyond the burner tube mouth 5 in the direction of flow ST and has a radially projecting constriction 30 at the front.
  • the distance between the constrictions 6 and 30 is approximately 5 mm.
  • annular gap 31 diverging towards the front is formed between the burner tube and the tubular sleeve 29.
  • Elongated holes 32 open into these, which are arranged in the flow direction in front of the burner tube mouth 5 on a circular circumferential line of the tubular sleeve 29 evenly distributed.
  • the tubular sleeve 29 can also be fastened in the region of the conical narrowing 3 of the burner tube.
  • the burner tube 1 or the tube sleeve 29 is preferably made of steel with the material number 1.4878.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Nozzles For Spraying Of Liquid Fuel (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
EP90121914A 1989-11-15 1990-11-15 Dispositif de mélange avec flamme tourbillonnante pour brûleur à huile Expired - Lifetime EP0428174B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3937925A DE3937925C2 (de) 1989-11-15 1989-11-15 Brennerkopf für einen Ölbrenner
DE3937925 1989-11-15

Publications (3)

Publication Number Publication Date
EP0428174A2 true EP0428174A2 (fr) 1991-05-22
EP0428174A3 EP0428174A3 (en) 1992-01-08
EP0428174B1 EP0428174B1 (fr) 1996-06-12

Family

ID=6393542

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90121914A Expired - Lifetime EP0428174B1 (fr) 1989-11-15 1990-11-15 Dispositif de mélange avec flamme tourbillonnante pour brûleur à huile

Country Status (3)

Country Link
EP (1) EP0428174B1 (fr)
AT (1) ATE139324T1 (fr)
DE (2) DE3937925C2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8561602B2 (en) 2008-12-24 2013-10-22 Agio International Company, Ltd. Gas feature and method

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4134651C3 (de) * 1991-10-19 1999-03-18 Buderus Heiztechnik Gmbh Mischvorrichtung für einen Ölbrenner in einem zur Ausmündung hin sich konisch verjüngenden, Verbrennungsluft führenden Brennerrohr
DE9202147U1 (fr) * 1992-02-19 1992-04-30 Koerting Hannover Ag, 3000 Hannover, De
AU4984893A (en) * 1993-04-30 1994-11-21 Jin Min Choi Device for whirling diffusion of combustion air for turbo burner
DE4327987C2 (de) * 1993-08-20 1997-08-28 Electro Oil Gmbh Brennerkopf für einen Ölbrenner
DE10158295B4 (de) * 2001-11-23 2005-11-24 Bramble-Trading Internacional Lda, Funchal Strömungskörper

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3143159A (en) * 1962-10-01 1964-08-04 Nat Union Electric Corp Oil burner air control
EP0030217A1 (fr) * 1979-11-29 1981-06-10 Ab Allterm Dispositif de guidage d'air dans des brûleurs
DE8604089U1 (de) * 1986-02-15 1986-04-03 Klöckner & Co KGaA Zweigniederlassung Hechingen, 7450 Hechingen Mischeinrichtung für einen Gas- und Ölbrenner
DE3519509A1 (de) * 1985-05-31 1986-12-04 Günter Horch Stauscheibenhalterung mit stauscheibe fuer oel- oder gasbrenner
DE3542174C1 (en) * 1985-11-29 1987-07-02 Electro Oil Gmbh Mixing device for oil burners
DE8909202U1 (fr) * 1989-07-29 1989-09-14 Koerting Hannover Ag, 3000 Hannover, De

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3309027A (en) * 1964-12-18 1967-03-14 American Radiator & Standard Oil burner
US3868211A (en) * 1974-01-11 1975-02-25 Aqua Chem Inc Pollutant reduction with selective gas stack recirculation
DE7724029U1 (de) * 1977-08-02 1978-01-19 Electro-Oil Oelbrenner Gmbh, 2057 Reinbek Mischeinrichtung an kleinstoelbrennern

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3143159A (en) * 1962-10-01 1964-08-04 Nat Union Electric Corp Oil burner air control
EP0030217A1 (fr) * 1979-11-29 1981-06-10 Ab Allterm Dispositif de guidage d'air dans des brûleurs
DE3519509A1 (de) * 1985-05-31 1986-12-04 Günter Horch Stauscheibenhalterung mit stauscheibe fuer oel- oder gasbrenner
DE3542174C1 (en) * 1985-11-29 1987-07-02 Electro Oil Gmbh Mixing device for oil burners
DE8604089U1 (de) * 1986-02-15 1986-04-03 Klöckner & Co KGaA Zweigniederlassung Hechingen, 7450 Hechingen Mischeinrichtung für einen Gas- und Ölbrenner
DE8909202U1 (fr) * 1989-07-29 1989-09-14 Koerting Hannover Ag, 3000 Hannover, De

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8561602B2 (en) 2008-12-24 2013-10-22 Agio International Company, Ltd. Gas feature and method

Also Published As

Publication number Publication date
DE59010372D1 (de) 1996-07-18
ATE139324T1 (de) 1996-06-15
DE3937925C2 (de) 1994-06-09
DE3937925A1 (de) 1991-05-16
EP0428174B1 (fr) 1996-06-12
EP0428174A3 (en) 1992-01-08

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