EP0175875B1 - Öl- oder Gasbrenner zur Heissgaserzeugung - Google Patents

Öl- oder Gasbrenner zur Heissgaserzeugung Download PDF

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Publication number
EP0175875B1
EP0175875B1 EP85109292A EP85109292A EP0175875B1 EP 0175875 B1 EP0175875 B1 EP 0175875B1 EP 85109292 A EP85109292 A EP 85109292A EP 85109292 A EP85109292 A EP 85109292A EP 0175875 B1 EP0175875 B1 EP 0175875B1
Authority
EP
European Patent Office
Prior art keywords
burner
mixing tube
openings
nozzle
diameter
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.)
Expired
Application number
EP85109292A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0175875A1 (de
Inventor
Winfried Prof. Dr.-Ing. Buschulte
Erich Adis
Manfred Bader
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.)
Deutsches Zentrum fuer Luft und Raumfahrt eV
Original Assignee
Deutsche Forschungs und Versuchsanstalt fuer Luft und Raumfahrt eV DFVLR
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 Deutsche Forschungs und Versuchsanstalt fuer Luft und Raumfahrt eV DFVLR filed Critical Deutsche Forschungs und Versuchsanstalt fuer Luft und Raumfahrt eV DFVLR
Priority to AT85109292T priority Critical patent/ATE34447T1/de
Publication of EP0175875A1 publication Critical patent/EP0175875A1/de
Application granted granted Critical
Publication of EP0175875B1 publication Critical patent/EP0175875B1/de
Expired 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

Definitions

  • the invention relates to a burner for generating hot gas with a nozzle from which a fuel jet enters a mixing tube, with a diaphragm surrounding the outlet of the nozzle, which burner housing into an upstream prechamber accommodating the nozzle and a downstream combustion chamber accommodating the mixing tube divided, with a central passage in the orifice for the passage of the fuel jet emerging from the nozzle and with a number of openings in the orifice surrounding the passage through which combustion air enters the mixing tube from the prechamber, the openings being located within a surface , which results from the projection of the clear mixing tube cross-sectional area onto the diaphragm, and the distance between the edges of adjacent openings is at least 50% of the opening diameter.
  • the fuel supplied centrally via a nozzle is supplied with combustion air via openings which are arranged in an orifice surrounding the nozzle.
  • the combustion air and the fuel are mixed downstream of the nozzle in a mixing room which is arranged in a mixing tube.
  • a flame front forms during operation, from which hot gases outside the mixing tube flow back to a recirculation opening at the upstream end of the mixing tube.
  • This object is achieved in a burner of the type described at the outset according to a first embodiment in that the orifice is arranged upstream of at least one air guide channel which merges smoothly into the openings at least in the region of the radially outer edges of the openings.
  • An air duct upstream of the orifice directs the combustion air approximately parallel before it passes through the openings and before it enters the mixing chamber, so that a less disturbed flow can be achieved. This prevents turbulence from being carried into the mixing chamber which would otherwise continue in the flame and in the recirculation flow and would lead to increased combustion noises.
  • the channel is formed by a tube piece surrounding the nozzle at a concentric distance.
  • a common air supply channel is thus assigned to all openings, which is formed by the annular gap between the inner wall of the pipe socket and the nozzle.
  • the annular gap can be arranged along a cone narrowing in the direction of flow. This additionally achieves an effect which reduces the turbulence in the air flow, which is particularly advantageous in particular in combination with an opening with an inclined longitudinal axis.
  • the noise-reducing effect of the pipe section is particularly favorable if its length is between 10 and 120% of its inside diameter in the transition area to the openings; this length is preferably between 20 and 70% of the inside diameter, and it is very particularly favorable if this length is between 30 and 50% of the inside diameter of the pipe section.
  • each opening is assigned its own air duct, which merges smoothly into the opening. It can also be provided here that the air guide channels narrow conically in the flow direction.
  • the air ducts can be arranged on a cylindrical surface concentrically surrounding the nozzle, in a modified embodiment they are arranged on a conical outer surface concentrically surrounding the nozzle. It is advantageous if the longitudinal axis of the channels is inclined between 3 ° and 6 ° with respect to the longitudinal axis of the mixing tube, since then optimal mixing takes place in the interior of the mixing tube without the undesirable turbulence occurring.
  • the air duct can be worked into a common guide body concentrically surrounding the nozzle.
  • the length of these air supply ducts corresponds to 0.5 to 4 times the radial distance of the openings from the longitudinal axis of the nozzle, preferably to 2 to 3 times the radial distance of these openings from the longitudinal axis of the nozzle.
  • the object is also achieved in a burner of the type described at the outset in accordance with a further embodiment in that the openings are chamfered on the side of the orifice facing the antechamber.
  • the chamfering of the openings in a multi-hole screen already leads to a considerable reduction in noise generation, since in this case too the combustion air gets into the mixing chamber more trouble-free.
  • the openings in the diaphragm can have a circular cross section, but it is also possible to use other cross sections, for example the openings can have the shape of ring sections.
  • the adjacent openings can lie on a common circle around the longitudinal axis of the nozzle, but they can also be offset from one another in the radial direction, so that, for example, openings are arranged on two concentrically arranged partial circles which are offset from one another.
  • the distance between the edges of adjacent openings is more than 50% of the opening diameter, in particular more than 100%.
  • An arrangement has proven to be particularly advantageous in which the longitudinal axes of the openings are inclined to converge in the flow direction with respect to the longitudinal axis of the mixing tube, preferably with an angle of inclination between 3 ° and 6 °.
  • This can be achieved by arranging the openings in the diaphragm itself or by deforming the diaphragm in such a way that the longitudinal axes of the openings are inclined with respect to the longitudinal axis of the mixing tube.
  • the mixing tube has a larger diameter at its upstream end than at its downstream end.
  • the mixing tube can narrow in steps or conically.
  • the upstream end of the mixing tube has an inner diameter which is larger than the diameter of a circumferential circle lying on the outer sides of the openings; in a modified embodiment, the inner diameter can also be chosen so that it is equal to the diameter of this circumferential circle.
  • the mixing tube has a length that extends up to three times the inside diameter of the mixing tube inlet. This length of the mixing tube is slightly longer than the length of the mixing tube normally used. It has been found that this extension of the mixing tube leads to an additional reduction in noise.
  • This extended mixing tube can have openings in its jacket through which an ignition device projects into the mixing tube.
  • recirculation openings are provided in the jacket of the upstream end of the mixing tube adjoining the orifice and are arranged at a distance from the orifice so that there is a closed piece of pipe between the orifice and the recirculation openings located.
  • the length of the pipe section preferably corresponds to approximately 1/4 of the mixing pipe diameter.
  • a further pipe section adjoins the mixing tube downstream, the diameter of which is at most as large as that of the downstream end of the mixing tube.
  • This piece of pipe is advantageously at a distance from the downstream end of the mixing tube which is between 1/10 and 1/4 of the diameter of the mixing tube. It is advantageous if the length of this pipe section is between 1/2 and 1 diameter of the mixing tube, preferably 2/3 of this diameter. This measure also reduces the overall sound level, specifically in that a core flow is again pressed through a constriction after leaving the large mixing tube part, with the aim of dampening the vortex formation occurring at the inner mixing cone of the flow.
  • the invention relates to a wide variety of oil or gas burners and is discussed below using the example of a so-called blue burner, ie a burner in which oil is completely burned with a blue flame.
  • a so-called blue burner ie a burner in which oil is completely burned with a blue flame.
  • the invention is not limited to such blue burners; for example, the desired noise reduction can be achieved with the described constructional measures also for heating burners and yellow burners.
  • the burner shown in FIGS. 1 and 2 comprises a cylindrical burner housing 1, which is subdivided into an upstream antechamber 3 and a downstream combustion chamber 4 by a wall, which is referred to below as an orifice 2.
  • the orifice 2 has a central passage 5, into which a nozzle 6 is inserted, which is connected to a fuel supply line 7.
  • the longitudinal axis of the nozzle 6 coincides with the longitudinal axis of the burner housing.
  • a cylindrical mixing tube 8 Downstream of the orifice 2 is connected to this a cylindrical mixing tube 8 which, via circumferential slots 9 immediately after the orifice 2, forms a connection between its interior 10 forming the mixing space and an annular space 11 serving as a recirculation space, which surrounds the mixing tube 8 concentrically.
  • An ignition device 12 is led from the prechamber through the diaphragm 2 and ends at the outlet end of the mixing tube 8, so that ignition can take place in this area.
  • a measuring probe 13 is inserted from the antechamber through the orifice 2 into the combustion chamber 4.
  • a number of openings 14, each with a circular cross section, are arranged, which establish a connection between the prechamber 3 and the interior space 10 surrounded by the mixing tube 8 in the combustion chamber 4.
  • the nozzle 6 is surrounded at a distance by a cylindrical pipe section 15 which extends up to the diaphragm 2.
  • the inside diameter of this pipe section 15 is selected such that the inner wall of the pipe section 15 merges smoothly into the openings 14 in the region of the outer edges of the openings 14, as is clear from FIG. 2.
  • the radius of the circle on which the openings 14 lie lies between the outer radius of the nozzle 6 and the radius of the inner wall of the tube piece 15, so that the openings 14 with the inner region of their edge are the envelope of the nozzle 6 touch, with the outside area the inner wall of the pipe section 15.
  • the number of openings 14 along the circle surrounding the nozzle is selected such that webs 16 remain between the openings, the width of which is at least 50% of the diameter of the openings 14. It is particularly advantageous if the inner diameter of the pipe section 15 is slightly smaller than the inner diameter of the mixing pipe 8. This allows a maximum distance of adjacent openings in the circumferential direction to be achieved with a predetermined cross-sectional area of the openings 14, this maximum distance leading to the best possible noise reduction. If the inside diameter of the pipe section is increased beyond the inside diameter of the mixing tube, there is again an increase in noise despite the even greater distances between adjacent bores.
  • fuel for example gas or oil
  • the nozzle can be designed as an atomizing nozzle when using oil.
  • Combustion air is introduced into the interior 10 of the mixing tube 8 through the openings 14, so that fuel and combustion air mix intimately in the interior 10.
  • this mixture is ignited and burns in a flame front which is located approximately in the area of the outlet-side end of the mixing tube in accordance with the respective flow rate.
  • the combustion air is passed through the pipe section 15 through an annular channel 17 surrounding the nozzle 6 before the combustion air can enter the interior 10 of the mixing pipe 8 through the openings 14.
  • the air flow is calmed, so that the air passes through the openings 14 largely without turbulence.
  • the turbulence in the mixing tube 8 and in the combustion area is also reduced compared to a construction in which the air enters the mixing tube 8 directly from the prechamber without a guide channel upstream of the openings 14. Due to the low turbulence, there is a significant reduction in noise during the burning process itself.
  • the tube piece 15 is cylindrical in the embodiment shown in Figure 1 (solid lines).
  • the pipe section 15 has the shape of a truncated cone, and a parallel inner wall forms with the pipe section an annular gap 17 running along a truncated cone shell.
  • FIG Lines drawn Such an arrangement is shown in FIG Lines drawn. This arrangement also contributes to a calming of the air flow.
  • FIGS. 3 and 4 A burner of similar construction is shown in FIGS. 3 and 4, parts corresponding to one another have the same reference numerals.
  • the mixing tube 8 is frustoconical, the inlet end having an outer diameter which is substantially larger than the diameter of the circle on which the openings 14 are arranged. It has been found that this conical narrowing of the mixing tube leads to an additional reduction in noise during the burning process.
  • an air supply duct comparable to the pipe section 15 is missing. Instead, the openings 14 are chamfered on their side facing the prechamber 3. These chamfers, which are incorporated directly into the panel 2, also contribute to a substantial calming of the combustion air flowing into the mixing tube and thus lead to a reduction in noise
  • the nozzle 6 is surrounded by a guide body 18 into which axially parallel channels 19 are incorporated, in such a way that each opening 14 has its own channel 19 assigned.
  • the channels 19 enter the respective opening 14 smoothly.
  • the channels 19 have the same cross section over their entire length, but it can be provided that the channels 19 narrow in the direction of flow.
  • the channels 19 can run axially parallel in the guide body, as shown in solid lines in FIG. 5, but they can also be arranged on a conical jacket, as is indicated by dash-dotted lines in FIG. It is advantageous if the inclination of the channels 19 with respect to the longitudinal axis of the nozzle is between 3 ° and 6 °. It has been found that optimal noise reduction can be achieved with such an arrangement. In this case, too, the channels themselves can still narrow in the direction of flow. It is important in this context that in all cases the channels 19 pass into the openings 14 smoothly, so that no turbulence can occur in this transition area.
  • the mixing tube 8 is extended compared to the exemplary embodiments in FIGS. 1 to 4, so that the length is approximately up to three times as large as the inside diameter of the mixing tube inlet. This extension of the mixing tube also contributes to an additional reduction in noise.
  • the mixing tube in this exemplary embodiment has jacket openings 20 through which the ignition device 12 projects into the interior 10 of the mixing tube 8. These jacket openings 20 are located between the upstream and the downstream end of the mixing tube.
  • FIG. 7 A further preferred exemplary embodiment of a burner is shown in FIG. 7, in which corresponding parts are again identified by the same reference numerals.
  • annular space 21 which surrounds the nozzle 6 in the region of the opening 5 and which opens into an annular gap 22 surrounding the opening 5 is incorporated into the guide body 18.
  • the rinse gap 22 can be formed by the opening itself, which then has a diameter that is somewhat larger than the diameter of the nozzle 6 in this area.
  • the annular space 21 communicates with the prechamber 3 via channels 23, which run essentially radially in the guide body 18, so that combustion air can enter the interior not only via the channels 19 and the openings 14, but also for the channels 23, the annular space 21 and the annular gap 22. Since this combustion air occurs in the immediate vicinity of the fuel entering the interior, a particularly effective mixing can take place here, the introduction of turbulence into the interior by the combustion air being largely avoided. This measure also serves to reduce noise.
  • the mixing tube 8 is extended and has jacket openings 20.
  • the part 24 of the mixing tube located upstream of the jacket opening 20 has a larger diameter than the part 25 located downstream of the jacket opening 20.
  • the diameter of the part 24 is considerably larger than the diameter of the circle on which the openings 14 lie.
  • the axes of the openings 14 run parallel to the longitudinal axis of the mixing tube 8.
  • these openings in the diaphragm in such a way that their longitudinal axes are inclined convergingly in the flow direction with respect to the longitudinal axis of the mixing tube, for example with an inclination angle between 3 ° and 6 °. This inclination can be generated by appropriate incorporation of the openings in the panel or by a deformation of the panel in the region of the openings 14.
  • the combustion air can be introduced into the mixing chamber largely without turbulence, so that a considerable reduction in noise can be achieved.
  • the overall sound level can be reduced, for example, by 8 to 10 dB (A) of the absolute value if you compare the noise level with that of a burner in which the combustion air enters the mixing room directly through the openings in the panel without suitable protective measures.
  • the exemplary embodiment in FIG. 8 is constructed in the region of the prechamber and the air inlet ducts like the exemplary embodiment in FIG. 3, in particular reference is made to this exemplary embodiment.
  • the burner differs from the exemplary embodiment in FIG. 5, to the explanatory description of which reference is made only in that the circumferential slots 9 are at a distance from the orifice 2, so that a between the orifice 2 and the circumferential slots 9 Pipe piece 30 is formed with a closed outer surface.
  • This blank 30 has a length which corresponds to approximately 1/4 of the mixing tube diameter. It has been found that this has an effect on the formation of vortices in the mixing tube which reduces the overall sound level.
  • the burner in the region of the prechamber is designed in the same way as in the exemplary embodiment in FIG. 8.
  • the structure differs from that
  • Embodiment of Figure 7 only in that the inner diameter of the upstream part 24 of the mixing tube 8 corresponds to the diameter of the circumferential circle which surrounds the openings 14 adjacent to the outside.
  • the inside diameter of the downstream part 25 is correspondingly smaller. This version also helps to reduce the overall sound level.
  • FIG. 10 largely corresponds to that of FIG. 8. It differs from this only in that the mixing tube 8 is followed by a further, coaxially arranged pipe section 40 which is at a distance from the end of the mixing tube which is between 1/10 and 1 / 4 of the mixing tube diameter.
  • the length of the pipe section 40 is between 1/2 and 1 mixing pipe diameter, preferably 2/3 of this diameter.
  • the inside diameter of the pipe section 40 can be equal to the inside diameter of the mixing pipe 8 at its outlet, but the inside diameter of the pipe section 40 is preferably smaller, as is shown in the exemplary embodiment in FIG. 10.
  • mixing tube can also be combined with one another in another way, for example a mixing tube can have circumferential slots 9 offset downstream and a pipe section 40 attached downstream, the mixing tube can also narrow in the flow direction.

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  • Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Gas Burners (AREA)
  • Pre-Mixing And Non-Premixing Gas Burner (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
  • Heterocyclic Carbon Compounds Containing A Hetero Ring Having Nitrogen And Oxygen As The Only Ring Hetero Atoms (AREA)
  • Nitrogen Condensed Heterocyclic Rings (AREA)
  • Feeding, Discharge, Calcimining, Fusing, And Gas-Generation Devices (AREA)
  • Treating Waste Gases (AREA)
  • Spray-Type Burners (AREA)
  • Feeding And Controlling Fuel (AREA)
EP85109292A 1984-08-16 1985-07-24 Öl- oder Gasbrenner zur Heissgaserzeugung Expired EP0175875B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85109292T ATE34447T1 (de) 1984-08-16 1985-07-24 Oel- oder gasbrenner zur heissgaserzeugung.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19843430010 DE3430010A1 (de) 1984-08-16 1984-08-16 Brenner zur heissgaserzeugung
DE3430010 1984-08-16

Publications (2)

Publication Number Publication Date
EP0175875A1 EP0175875A1 (de) 1986-04-02
EP0175875B1 true EP0175875B1 (de) 1988-05-18

Family

ID=6243088

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85109292A Expired EP0175875B1 (de) 1984-08-16 1985-07-24 Öl- oder Gasbrenner zur Heissgaserzeugung

Country Status (9)

Country Link
US (1) US4629414A (da)
EP (1) EP0175875B1 (da)
JP (1) JPS61125511A (da)
AT (1) ATE34447T1 (da)
CA (1) CA1259557A (da)
DE (2) DE3430010A1 (da)
DK (1) DK160642C (da)
FI (1) FI86106C (da)
NO (1) NO160314C (da)

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US4673350A (en) * 1986-08-26 1987-06-16 Eclipse, Inc. Burner assembly for radiant tube heating system
US4705022A (en) * 1986-09-25 1987-11-10 Eclipse, Inc. Recuperative radiant tube heating system
AU1688488A (en) * 1987-04-30 1988-12-02 Michael G. May Process and device for combustion of fuel
DE3801679C1 (en) * 1988-01-21 1989-05-11 Deutsche Forschungs- Und Versuchsanstalt Fuer Luft- Und Raumfahrt Ev, 5300 Bonn, De Burner for gaseous or liquid fuel
DE3801681C1 (en) * 1988-01-21 1989-05-18 Deutsche Forschungs- Und Versuchsanstalt Fuer Luft- Und Raumfahrt Ev, 5300 Bonn, De Method for burning gaseous or liquid fuel and burner for carrying out this method
DE4201061C2 (de) * 1992-01-17 1994-06-23 Man B & W Diesel Ag Brenner für vergasten flüssigen Brennstoff
DE4201060C2 (de) * 1992-01-17 1994-07-14 Man B & W Diesel Ag Brenner für vergasten flüssigen Brennstoff
DE4201059C2 (de) * 1992-01-17 1994-06-09 Man B & W Diesel Ag Flammrohr für einen Brenner für vergasten flüssigen Brennstoff
EP0558455B1 (de) * 1992-02-28 1996-09-04 Füllemann Patent Ag Brenner, insbesondere Oelbrenner oder kombinierter Oel/Gas-Brenner
DE4209220A1 (de) * 1992-03-21 1993-09-23 Deutsche Forsch Luft Raumfahrt Ablagerungsfreier brenner
US5393224A (en) * 1993-12-02 1995-02-28 American Standard Inc. Ignitor assembly for power burner furnace
US5927963A (en) * 1997-07-15 1999-07-27 Gas Electronics, Inc. Pilot assembly and control system
DE10004475C2 (de) * 2000-02-02 2002-08-22 Bosch Gmbh Robert Drallbrenner mit einem Drallkörper als Brennerelement in einer Brennkammer
EP1279895A1 (fr) * 2001-07-25 2003-01-29 Compagnie Europeenne de Bruleurs Tête de combustion d'un brûleur comprenant une zone de pré-vaporisation du combustible liquide
US6743010B2 (en) 2002-02-19 2004-06-01 Gas Electronics, Inc. Relighter control system
JP2005533235A (ja) * 2002-07-19 2005-11-04 シエル・インターナシヨネイル・リサーチ・マーチヤツピイ・ベー・ウイ 黄炎式バーナーの使用
JP2005533234A (ja) * 2002-07-19 2005-11-04 シエル・インターナシヨネイル・リサーチ・マーチヤツピイ・ベー・ウイ 青炎式バーナーの使用
ATE446478T1 (de) * 2006-02-22 2009-11-15 Tempratec Ltd Vorrichtung und verfahren zum verbrennen eines brennstoffes
JP4739275B2 (ja) * 2006-08-11 2011-08-03 Ｊｘ日鉱日石エネルギー株式会社 バーナ
DE102016113222A1 (de) * 2016-07-18 2018-01-18 Webasto SE Brenner und Fahrzeugheizgerät

Citations (2)

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DE2700671A1 (de) * 1977-01-08 1978-07-20 Deutsche Forsch Luft Raumfahrt Blaubrennender oelbrenner
DE2918416A1 (de) * 1979-05-08 1980-11-13 Deutsche Forsch Luft Raumfahrt Vergasungsoelbrenner

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DE2712564C2 (de) * 1977-03-22 1983-10-27 Max Weishaupt Gmbh, 7959 Schwendi Brenner für flüssige Brennstoffe
DE2821932A1 (de) * 1978-05-19 1979-11-22 Karl Bodemer Mischeinrichtung zur verbrennung von fluessigen kohlenwasserstoffen, insbesondere heizoel und dieseloel
DE3035707A1 (de) * 1980-09-22 1982-04-08 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5000 Köln Oel- und gasbrenner zum einbau in heizungs- und dampferzeugungskessel
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Publication number Priority date Publication date Assignee Title
DE2700671A1 (de) * 1977-01-08 1978-07-20 Deutsche Forsch Luft Raumfahrt Blaubrennender oelbrenner
DE2918416A1 (de) * 1979-05-08 1980-11-13 Deutsche Forsch Luft Raumfahrt Vergasungsoelbrenner

Also Published As

Publication number Publication date
ATE34447T1 (de) 1988-06-15
NO160314B (no) 1988-12-27
FI853128L (fi) 1986-02-17
NO160314C (no) 1989-04-05
NO853217L (no) 1986-02-17
FI86106C (fi) 1992-07-10
DE3430010C2 (da) 1987-11-12
JPH0240924B2 (da) 1990-09-13
DK160642C (da) 1991-09-02
US4629414A (en) 1986-12-16
DK160642B (da) 1991-04-02
EP0175875A1 (de) 1986-04-02
JPS61125511A (ja) 1986-06-13
DK370785D0 (da) 1985-08-15
FI86106B (fi) 1992-03-31
DE3562819D1 (en) 1988-06-23
DE3430010A1 (de) 1986-02-27
CA1259557A (en) 1989-09-19
FI853128A0 (fi) 1985-08-15
DK370785A (da) 1986-02-17

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