EP0706007A2 - Procédé et brûleur pour la combustion d'un combustible pulvérisé - Google Patents

Procédé et brûleur pour la combustion d'un combustible pulvérisé Download PDF

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Publication number
EP0706007A2
EP0706007A2 EP95115733A EP95115733A EP0706007A2 EP 0706007 A2 EP0706007 A2 EP 0706007A2 EP 95115733 A EP95115733 A EP 95115733A EP 95115733 A EP95115733 A EP 95115733A EP 0706007 A2 EP0706007 A2 EP 0706007A2
Authority
EP
European Patent Office
Prior art keywords
air
primary
burner
primary air
air pipe
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
EP95115733A
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German (de)
English (en)
Other versions
EP0706007B1 (fr
EP0706007A3 (fr
Inventor
Hans-Ulrich Dr.-Ing. Thierbach
Matthias Dr.-Ing. Jochem
Wolfgang Dipl.-Ing. Schreier
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.)
BBP Energy GmbH
Original Assignee
L&C Steinmueller 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 L&C Steinmueller GmbH filed Critical L&C Steinmueller GmbH
Publication of EP0706007A2 publication Critical patent/EP0706007A2/fr
Publication of EP0706007A3 publication Critical patent/EP0706007A3/fr
Application granted granted Critical
Publication of EP0706007B1 publication Critical patent/EP0706007B1/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
    • F23D1/00—Burners for combustion of pulverulent fuel
    • F23D1/02—Vortex burners, e.g. for cyclone-type combustion apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2214/00—Cooling

Definitions

  • the invention relates to a method of the type mentioned in the preamble of claim 1.
  • the tertiary air is supplied for this purpose in an annular jet surrounding the swirled jacket air, which emerges from the annular space of a tertiary air tube surrounding the jacket air pipe.
  • the jacket air pipe and the tertiary air pipe are each connected to a spiral inlet housing and separate air inlet lines.
  • a swirl insert which is fastened to the core air tube and which produces a rotational flow resulting in a uniform flow through the primary air tube is provided within the primary air tube.
  • the coal dust is enriched within the mixture flow on the outer circumference of the primary air pipe; when it emerges from the primary air pipe, the coal dust concentration in the edge region is torn open by a ring arranged there, whereby recirculation vortices are generated. These recirculation vortices ensure accelerated heating of the coal dust and sufficient mixing of the coal dust with part of the jacket air.
  • the coal dust concentration at a defined point in the burner muffle causes the occurrence of a very severe lack of air, which is associated with the initial phase of the coal dust in terms of location and time.
  • a rectangular intake manifold is connected upstream of the primary air pipe.
  • This object is achieved in that the flow velocity of the primary air is changed before the coal dust concentration in the edge region is torn open.
  • the flow rate can be changed by drawing in the cross section, as a result of which the coal dust is concentrated, accelerated and deflected in the direction of the inner recirculation area which forms in the primary combustion zone. By tearing open the coal dust concentration in the edge area, fine dust is transported out of the concentrated dust flow and mixed into the jacket air flow.
  • the flow cross section can be expanded, whereby the gas flow is slowed down.
  • the separation of fine dust occurs because it follows the expansion most quickly.
  • the tearing up of the coal dust concentration in the edge area which is primarily fine coal dust, causes turbulence, transport of the fine dust to the outside and rapid mixing of the fine dust into the jacket air.
  • the process control with an enlarged flow cross section is preferred.
  • the step air can be supplied in a ring jet or in single jets.
  • the separation of the step air into individual jets enables a greater depth of penetration to be achieved and flue gas from the combustion chamber can enter the flame between the individual jets.
  • the outlet area of the jacket air pipe is preferably cooled in order to avoid caking of slag.
  • the invention is also directed to a burner of the type mentioned in claim 6 and dependent claims 7 to 13 dependent thereon.
  • the present invention is directed to a burner according to the preamble of claim 14, the main objective of which is to simply apply the fuel / air mixture to the primary air pipe in order to reduce the formation of nitrogen oxides by evenly introducing the coal dust into the flame.
  • Fig. 1 shows a longitudinal section through an embodiment of the burner according to the invention.
  • An oil ignition lance 1 is provided in the longitudinal axis of the burner and is arranged within a core air tube 2.
  • the flame cone 3 of the oil pilot flame is indicated schematically in the figure.
  • the core air tube is closed at its rear end by a plate 2a, which is penetrated by the oil lance, and has a side opening 2b near its rear end.
  • the core air tube is axially displaceable — as indicated by the arrow P — in a guide tube 4.
  • a core air supply tube 5 is connected to it.
  • the outlet opening of the core air supply pipe 5 is assigned to the lateral opening 2b of the core air pipe 2 and provided with a corresponding axial opening width such that when the core air pipe is displaced, the air brought in via the core air supply pipe can enter the core air pipe unhindered.
  • the front section of the core air tube is surrounded by a primary air tube 6 to form a cylindrical ring channel, the outlet opening of which is set back relative to the outlet opening of the core air tube.
  • the core air tube is charged with a coal dust-gas mixture in the following way.
  • the coal dust-gas mixture brought up from a coal grinding plant or coal dust source, not shown, is fed to a deflection manifold 7 upstream of the burner, in which a concentration of the coal dust K is forced on the side of the manifold facing the combustion chamber.
  • the deflection manifold 7 is preferably a continuously curved manifold. As FIGS. 2 and 3 show, this forced concentration takes place independently whether the flow is from below (Fig. 2) or from above (Fig. 3).
  • the manifold 7 is followed by a channel extension 8 serving as a delay channel, which in the embodiment shown is a channel with a rectangular cross section, ie there is an expanding transition from a line with a round cross section to a line with a rectangular cross section.
  • the flow rate of the gas from z. B. reduced 23 m / s to 12 m / s, which also reduces the coal dust speed.
  • at least partial segregation of the coal dust-gas mixture is achieved in the delay channel 8, as is shown schematically in FIGS. 2 and 3 by the coal dust K and the gas flow G.
  • the formation of the dust streak K can be determined by a corresponding geometric design of the entry of the coal dust line into the delay channel.
  • the already slowed down coal dust strand K meets a strand breaker 9 at the end of the delay channel 8.
  • the strand breaker 9 consists of a multiplicity of rod-shaped crushing elements 10 which are connected upstream of a predetermined circular sector of the inlet opening 11a of a venturi-like inlet assembly 11 and extend essentially parallel to the burner axis .
  • the crusher elements consist of cuboids arranged at a distance. The crushing elements can be easily replaced when worn.
  • the inlet assembly 11 surrounds the end of the guide tube 4 facing the combustion chamber, forming an annular channel.
  • the gas flow applied to the rear wall of the delay channel is introduced into the through a closing plate 12, preferably extending at an angle of 45 ° and penetrated by the guide tube 4 deflected annular entry opening of the inlet assembly 11 and strikes the delayed dust flow which is broken up by the strand breaker at an angle of almost 90 °. This ensures that the coal dust is evenly distributed over the ring cross-section.
  • the venturi-like design of the inlet assembly 11 accelerates the gas flow parallel to the burner axis.
  • any local strands of coal dust that may be present on the circumference are dissolved, whereby coal dust and gas are mixed.
  • the constriction of the free cross-section in the entry assembly can be between 10 - 70%.
  • the gas flow is blocked, which results in a further equalization.
  • the closing plate 12 together with the associated side walls 13 and 14, and the end wall 15 carrying the crushing elements 10 together with the inlet assembly 11 constitute a structural unit which is one with the side wall 16a facing away from the combustion chamber Air box 16 is connected by a screw 17.
  • Components 12, 13, 14 and 15 form an intake manifold. After the connection has been established, the inlet assembly 11 projects into the primary air pipe 6, which is welded to the side wall 16a.
  • a hot, strongly substoichiometric, compact primary combustion zone with the most complete pyrolysis of the fuel and internal fuel grading is sought.
  • An air ratio of 0.4 - 0.6 should be realized in the primary flame.
  • such a design is sought at the dust outlet end of the primary air pipe 6 that, on the one hand, a gradation of the fuel input into the primary flame is achieved and, on the other hand, a stable and fast ignition of the coal dust is supported.
  • the aim is Concentrate and slow down fine dust on the outer circumference of the dust outlet in order to ensure rapid mixing with the jacket air, which is supplied via a jacket air pipe which concentrically surrounds the primary air pipe 6 to form a cylindrical ring channel.
  • a flame holder 19 is assigned to the outlet end of the primary air pipe 6 in the embodiment according to FIG. 1, the end of the flame facing the combustion chamber is shown on an enlarged scale in FIG. 5.
  • This flame holder consists of a tubular channel 20 with a straight cylindrical section 20a, a conically tapering section 20b and a conically widening section 20c.
  • the channel overlaps with its straight cylindrical end 20a the free edge of the primary air pipe and is supported on the end of the core air pipe 2 by means of radially extending webs 21, so that when the core air pipe 2 is displaced, the flame holder 19 moves in a corresponding manner (see FIG. 1 and 6).
  • blocking teeth 22 are provided which protrude into the primary flow and are arranged in a uniform circumferential distribution. Instead of individual locking teeth, one can toothed locking ring may be provided.
  • the blocking teeth in the area of the narrowest cross-section cause a swirling of the flow in the outer area, as a result of which fine dust in particular is discharged from the concentrated flow and transported away to the outside.
  • the turbulence of the flow also favors the mixing of the fine dust into the jacket air flow.
  • the accelerated and inwardly deflected coarse dust reaches the inner recirculation zone, where the coal dust is cross-viewed by the recirculation flow.
  • the fuel input into the primary flame is thus classified several times.
  • FIG. 7 Another possibility for the design of the channel of a flame holder is shown in FIG. 7.
  • the channel 23 there has a straight cylindrical section 23a and an adjoining conically widening section 23b.
  • Blocking teeth 24, comparable to blocking teeth 22, are formed near the outlet end of the widening section 23b. It should be pointed out that separate locking teeth may not be required, but that a continuous locking ring may be sufficient.
  • the expansion of the dust cross section in the channel section 23b slows down the gas flow and results in a Speed profile with an outside slower and an inside faster flow.
  • a separation of fine dust occurs, since this follows the expansion most quickly, ie the coal concentration will be higher in the area adjacent to the core air pipe than in the outer, slower flow, since the coarser coal particles will keep their direction of flow.
  • the blocking teeth 24 cause a further slowdown of the dust in the outer region of the coal dust cross section and a swirling of the flow, which favors the transport of the fine dust to the outside and thus its rapid mixing into the jacket air.
  • the coarser dust is only slowed down comparatively little by the delayed flow.
  • a device for influencing the swirl in the form of rotatably mounted axial swirl flaps 25 is arranged in a section of the jacket air pipe 18 that widens toward the inflow end and can be adjusted from the outside via a linkage 26 and an actuator. These axial swirl flaps impose a swirl of adjustable size on the jacket air.
  • a muffle 27 constructed of a ceramic mass adjoins the end of the jacket air tube 18 facing the combustion chamber and extends towards the combustion chamber with an S-shaped configuration of its inner surface.
  • This muffle shape combines with the corresponding design of the Coal dust discharge and a strong swirl of the jacket air with the help of the swirl flaps 25 guarantees a fast, intensive ignition. Due to the high peripheral speed of the jacket air and an appropriate design of the dust outlet cross-section, a rapid mixing of fine dust into the jacket air is realized.
  • the S-shape of the muffle which can be seen in particular in FIG. 1, prevents the primary flame from tearing open even with a high swirl intensity of the jacket air.
  • the S-shape runs out to the combustion chamber in such a way that an outflow of the jacket air can take place with a flow component almost parallel to the burner axis.
  • the core air tube 6 and the flame holder 19, and thus the dust outlet cross section are axially displaceable to control the course of the combustion in the primary flame.
  • the exit speed of the jacket air and the location and speed of the mixing of the coal dust into the jacket air can be influenced by shifting the inner outlet cross section.
  • the location and intensity of the ignition and the grading of the fuel within the primary flame can thus be set.
  • the shift in the coal dust outlet cross-section can react very well to a wide variety of coal qualities with regard to ignition and combustion behavior.
  • an air ratio of 0.9 - 1.05 should be achieved with a combustion with burnout air and an air ratio of 1.1 - 1.3 with a combustion without burnout air.
  • a ring comprising a plurality of stepped air nozzles 28 is provided around the burner muffle 27, the stepped air nozzles being embedded in the ceramic compound KM forming the muffle 27.
  • Eight spaced stage air nozzles 28 are preferably provided.
  • the arrangement of the stepped air nozzles 28 is intended, on the one hand, to enable adequate external recirculation to the primary flame and to keep the oxygen away from the primary flame for a sufficiently long time, and on the other hand to securely enclose the primary flame in an oxygen-rich cas flow.
  • the nozzles 28 are initially arranged with an angle of incidence directed outward from the burner axis in order to avoid direct rapid mixing of the step air into the primary flame which is formed.
  • the air nozzles 28 are all shown with the same outward angle of attack. However, it is also possible to assign differentiated axial angles of attack to the nozzles and thus to achieve a multiple air gradation within the flame.
  • the stepped air nozzles 28 not only have a radially outward angle of attack, but also a tangential angle at the same time, ie they extend so that the nozzle axis Torch axis does not cut.
  • a swirl is thus imparted to the step air flow so that it concentrically forms a muffle 27 "pneumatic muffle" is coming.
  • a swirl is preferably applied to the step air flow which is in the same direction as the swirl imparted to the jacket air flow by the swirl flaps 25. This stabilizes the flow and prevents the step air flow from mixing too quickly with the flow of the primary flame.
  • the jets emerging from the stepped air nozzles 28 draw flue gas RG out of the flame environment as they flow out, as a result of which the oxygen partial pressure in the secondary combustion zone drops and the NO x formation in this area is reduced.
  • nozzles with a constant discharge angle can be used as stepped air nozzles, it is advantageous if nozzles with a variable discharge angle are used. To achieve this, two-channel nozzles are used, the design of which can be read in particular from FIGS. 10-12.
  • the two-channel nozzle 28 has a straight cylindrical section 28a, in which a partition 29 is arranged.
  • the partition does not have to be arranged in the center, but can be arranged offset from a radial plane.
  • the partition 29 ends at a distance from an outlet opening 30 which is inclined with respect to the nozzle axis A.
  • the outlet opening 30 is covered by remaining tube sections 28b and 28c and also by a cover plate 31 which is inclined at a first angle with respect to the axis A and by an opposite one another predetermined angle with respect to the axis A inclined cover plate 32 limited.
  • the angles of the cover plates 31 and 32 determine the possible exit angles with which a gas flow can exit the exit opening 30.
  • a different exit angle with respect to the axis A can be achieved by volumetrically different action of the channels 33 or 34 determined by the partition 29 with step air. It can e.g. B. be possible that when the channels 33 and 34 are loaded with 50% of the step air, the step air jet emerges parallel to the cover plate 31 or that when the channel 33 is loaded with 10% of the step air and the channel 34 with 90% of the step air of the nozzle 28 the beam emerges parallel to the cover plate 32.
  • two inner walls 36 and 37 are provided in the air box 16 in addition to the side wall 16a and the side wall 35 shown on the right in the air box 16.
  • the inner wall 36 separates the step air from the jacket air and the inner wall 37 separates the step air into two partial flows.
  • the space between the partition walls 36 and 37 is connected via the space between the partition walls 37 and 35 through passage sections 38 to the subchannels 34 of the stepped air nozzles 28, while the subchannels 33 are connected directly to the space between the side wall 35 and the partition wall 37.
  • FIG. 8 it should be noted that this represents a development along the line VIII-VIII in FIG. 1, while FIG. 1 shows a section along the line I-I in FIG. 8.
  • stepped air nozzles 28 each individually at least via one Sub-area are rotatably arranged.
  • the individual nozzle is rotatably supported in a guide tube 39.
  • both the tangential and the radial inflow angle would be adjustable and thus a particularly good optimization of the air gradation on the burner could be achieved.
  • the application of subchannels 33 and 34 would, however, be more complicated.
  • step air nozzles can be shut off in order to be able to implement the required exit speeds of the step air even in part-load operation.
  • control flaps 41, 42 and 43 are shown, which shows a diagram of the air flows supplied to the burner by a blower 44 and the fuel supplied by a coal mill 45.
  • the control flap 41 regulates the jacket air and the step air upstream of the control flaps 39 and 40 simultaneously.
  • the control flap 42 regulates the primary air supplied via a pressure-increasing blower 42a and the control flap 43 regulates the core air insofar as the core air pipe has to be acted on.
  • the muffle 27 is formed in a pipe basket 46 which is integrated into the steam circuit of a steam generator and which is connected to the wall bore 47 of the combustion chamber and burns into the burner. Insulation 48 is also provided in the area of the muffle.
  • FIG. 14 shows two further embodiments of the burner according to the invention. As far as possible, the reference numerals have been taken from FIG. 1.
  • the core air tube 2 is not axially displaceable. Rather, the oil ignition lance is 1 with a guide cylinder 1a and swirl ring 1b arranged at its front end, axially displaceable, as indicated by the double arrow. Furthermore, the inlet assembly 11 is not designed in a venturi-like manner, but is instead formed by a straight tube 11 ′ with a fastening flange. The diameter of the straight tube 11 'corresponds essentially to the diameter of the primary air tube 6 and thus represents an extension of the primary air tube.
  • a flame holder 19 is used, the channel 23 of which is designed according to FIG. 7.
  • the straight cylindrical section 23a overlaps the outlet end of the primary air tube 6, but is not connected to the core air tube 2 via webs as in the embodiment according to FIG. 1, but is axially displaceable in the direction of the double arrow via at least one schematically illustrated actuating rod 23c.
  • the jacket air tube 18 With regard to the design of the jacket air tube 18, different embodiments are shown in the lower and upper half of FIG. 14. An embodiment is shown in the upper half of FIG. 14, in which the jacket air tube 18 is designed as a double-walled air tube with walls 18a and 18b. The annular space delimited by the walls is acted upon with air via a duct 49 arranged in the air box 16, regulated by a regulating flap 50, which can escape into the combustion chamber from the annular gap at the front end of the double-walled jacket air pipe. In the exit area, the double jacket is formed in the longitudinal direction with an essentially S-shaped cross section.
  • the jacket air pipe is provided in its outlet area with a cooling winding 51 through which a cooling medium 52 flows.
  • the cross section of the outlet area in the longitudinal direction is in essentially S-shaped. Contamination in the outlet flow area of the jacket air pipe is largely avoided by cooling by means of air or the cooling medium flowing into the combustion chamber.
  • the step air does not emerge into the combustion chamber in individual jets but in an annular jet surrounding the jacket air.
  • the jacket air tube 18 is surrounded by a stepped air tube 53, to which the burner muffle 27 made of ceramic material is connected.
  • An adjustable swirl device 54 is provided in the inlet area of the stepped air pipe 53, which swirls the air supplied by a duct 55 arranged in the air box 16 with a control flap 56.
  • the venturi-like configuration of the inlet assembly 11 can be dispensed with.
  • the displaceability of the core air tube 2 can also be dispensed with if the flame holder 19 is arranged to be displaceable alone, as in the embodiment according to FIG. 14.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Pre-Mixing And Non-Premixing Gas Burner (AREA)
EP95115733A 1994-10-06 1995-10-06 Procédé et brûleur pour la combustion d'un combustible pulvérisé Expired - Lifetime EP0706007B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4435640A DE4435640C2 (de) 1994-10-06 1994-10-06 Brenner zur Verbrennung von staubförmigem Brennstoff
DE4435640 1994-10-06

Publications (3)

Publication Number Publication Date
EP0706007A2 true EP0706007A2 (fr) 1996-04-10
EP0706007A3 EP0706007A3 (fr) 1997-05-02
EP0706007B1 EP0706007B1 (fr) 2001-04-04

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP95115733A Expired - Lifetime EP0706007B1 (fr) 1994-10-06 1995-10-06 Procédé et brûleur pour la combustion d'un combustible pulvérisé

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EP (1) EP0706007B1 (fr)
AT (1) ATE200347T1 (fr)
DE (2) DE4435640C2 (fr)
ES (1) ES2156595T3 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006011326C5 (de) * 2006-03-09 2015-03-19 Alstom Technology Ltd. Rundbrenner

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT404398B (de) * 1996-12-04 1998-11-25 Voest Alpine Ind Anlagen Brenner für die verbrennung von feinkörnigen bis staubförmigen, festen brennstoffen
DE102004059679B4 (de) * 2003-12-16 2005-12-22 Alstom Power Boiler Gmbh Rundbrenner zur Verbrennung von staubförmigem Brennstoff
DE102005046831A1 (de) * 2005-09-29 2007-04-12 Küppersbusch Großküchentechnik GmbH Staubfeuerungsvorrichtung
DE202008009650U1 (de) * 2008-07-18 2009-11-26 Ammann Schweiz Ag Mehrstoff-Brenner
AT524888A1 (de) 2021-03-23 2022-10-15 Mme Eng E U Ultra-Low-NOx-Brenner

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5984008A (ja) * 1982-11-08 1984-05-15 Babcock Hitachi Kk 微粉炭燃焼装置
JPS604706A (ja) * 1983-06-23 1985-01-11 Babcock Hitachi Kk 微粉炭バ−ナ
US4517904A (en) * 1984-02-28 1985-05-21 Riley Stoker Corporation Furnace, burner and method for burning pulverized coal
EP0445938A1 (fr) * 1990-03-07 1991-09-11 Hitachi, Ltd. Brûleur à charbon pulvérisé, chaudière au charbon pulvérisé et procédé pour la combustion de charbon pulvérisé
DE4102610A1 (de) * 1991-01-25 1992-07-30 Ver Kraftwerks Ag Peitz Nieder Kohlenstaub-drallbrenner
DE4217879A1 (de) * 1992-05-29 1993-12-02 Babcock Energie Umwelt Brenner für staubförmigen Brennstoff

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0640793B1 (fr) * 1990-06-29 1999-02-24 Babcock-Hitachi Kabushiki Kaisha Appareil de combustion

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5984008A (ja) * 1982-11-08 1984-05-15 Babcock Hitachi Kk 微粉炭燃焼装置
JPS604706A (ja) * 1983-06-23 1985-01-11 Babcock Hitachi Kk 微粉炭バ−ナ
US4517904A (en) * 1984-02-28 1985-05-21 Riley Stoker Corporation Furnace, burner and method for burning pulverized coal
EP0445938A1 (fr) * 1990-03-07 1991-09-11 Hitachi, Ltd. Brûleur à charbon pulvérisé, chaudière au charbon pulvérisé et procédé pour la combustion de charbon pulvérisé
DE4102610A1 (de) * 1991-01-25 1992-07-30 Ver Kraftwerks Ag Peitz Nieder Kohlenstaub-drallbrenner
DE4217879A1 (de) * 1992-05-29 1993-12-02 Babcock Energie Umwelt Brenner für staubförmigen Brennstoff

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 008, no. 195 (M-323), 7.September 1984 & JP 59 084008 A (BABCOCK HITACHI KK), 15.Mai 1984, *
PATENT ABSTRACTS OF JAPAN vol. 009, no. 117 (M-381), 22.Mai 1985 & JP 60 004706 A (BABCOCK HITACHI KK), 11.Januar 1985, *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006011326C5 (de) * 2006-03-09 2015-03-19 Alstom Technology Ltd. Rundbrenner

Also Published As

Publication number Publication date
ATE200347T1 (de) 2001-04-15
EP0706007B1 (fr) 2001-04-04
EP0706007A3 (fr) 1997-05-02
ES2156595T3 (es) 2001-07-01
DE4435640A1 (de) 1996-04-18
DE4435640C2 (de) 2001-01-04
DE59509155D1 (de) 2001-05-10

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