EP3026339B1 - Brûleur par allumage de matière solide - Google Patents

Brûleur par allumage de matière solide Download PDF

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Publication number
EP3026339B1
EP3026339B1 EP14195218.4A EP14195218A EP3026339B1 EP 3026339 B1 EP3026339 B1 EP 3026339B1 EP 14195218 A EP14195218 A EP 14195218A EP 3026339 B1 EP3026339 B1 EP 3026339B1
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EP
European Patent Office
Prior art keywords
combustion air
muffle
load
burner
air feed
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Application number
EP14195218.4A
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German (de)
English (en)
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EP3026339A1 (fr
Inventor
Andre Bätz
Steven Maclean
Joel Maia
Tais Mazza
Holger Dr. Wulfert
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Loesche GmbH
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Loesche GmbH
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Application filed by Loesche GmbH filed Critical Loesche GmbH
Priority to EP14195218.4A priority Critical patent/EP3026339B1/fr
Priority to PCT/EP2015/077060 priority patent/WO2016083225A1/fr
Priority to RU2017108689A priority patent/RU2665375C1/ru
Publication of EP3026339A1 publication Critical patent/EP3026339A1/fr
Application granted granted Critical
Publication of EP3026339B1 publication Critical patent/EP3026339B1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D1/00—Burners for combustion of pulverulent fuel
    • F23D1/04—Burners producing cylindrical flames without centrifugal action
    • 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

Definitions

  • the invention relates to a solid fuel-fired burner with a fuel supply by means of conveying air, with a burner muffle and with at least one combustion air supply.
  • Such solids-fired burners are used, for example, in a hot gas generator in process plants.
  • a hot gas generator in process plants.
  • Examples include grinding plants for grinding coal, cement clinker, granulated blastfurnace, raw meal or other moist, especially mineral, to be shredded materials.
  • lignite or hard coal fired hot gas generators are used.
  • Generic burners can also be used in other firing systems such as for waste heat boiler for steam generation.
  • solid fuels can be, for example, rock or lignite dust, biomass dust or mixtures thereof.
  • a generic burner is for example from the DE 197 06 077 A1 known.
  • solid which is crushed and called fuel dust is pneumatically conveyed into a combustion chamber and burned by supplying combustion air.
  • the burner On the output side, the burner is a burner muffle, a supply for the gas to be heated and a mixing part is provided, which is then arranged on the burner muffle.
  • Another burner is out of the DE 102 32 373 A1 known, which is a further development of the burner DE 197 25 613 A1 for firing with solids represents. This type of burner is also referred to by the manufacturer as a pulse burner.
  • pulverized coal is transported with a gaseous carrier medium, which may preferably be air, and blown into a reaction space by means of an injection lance.
  • the injection lance leads from the burner head to the point of the largest diameter of the conical reaction space and has a deflection hood at the outlet end.
  • the combustion air is supplied via a radial blade grid at the head end of the reaction space.
  • the blade grid and part of the reaction space are surrounded by an air collecting housing in which the combustion air is to be calmed and from which the combustion air is to reach the reaction space via the blade grid. Due to its flow pattern, the burner generates a large range of turbulent fluctuation movements. As a result, the burner dust after its exit from the deflection hood to the air guide vane, which is provided in the region of the burner head, transported back and from a swirling, helical flame heated to about 1,000 ° C and ignited. The flame jet itself has a very strong impulse and produces a very fast recirculation of the gas. In the further development, the main focus was on increasing the flame stability and the flame jet speed.
  • Hot gas generators are used, for example, in grinding mills in the grinding of coal to produce hot process gas.
  • the ground coal can be used for example in coal gasification or pig iron or steel production in the PCI process (Pulverized Coal Injection).
  • the necessary control ranges of the burner or of the hot gas generator are determined by the parameters of the following heat-consuming systems. This consumption depends in particular on the sometimes highly fluctuating moisture of the material to be ground and dried, the necessary throughput of the heat-consuming apparatus, in this case the grinding unit, and the ambient temperature.
  • the possible minimum and maximum throughput of such a roller mill is between 40% and 100%. This means that the mill has a control ratio of 1: 2.5.
  • the solid fuel burners To replace the known oil or gas fired burners with solid fuel burners, the solid fuel burners must achieve a control ratio of 1: 8 to 1:10.
  • the invention is therefore based on the object of specifying a solid-fueled burner and a method for its operation, which achieves a high control ratio of 1: 8 or higher.
  • the generic solid-fueled burner is further developed in that the burner muffle is subdivided into a main-load muffle and a partial-load muffle, wherein the partial-load muffle covers 5% to 10% of the volume of the main muffle having.
  • the part-load muffle itself is essentially conical with a rotationally symmetrical basic shape, which has an axis of rotation.
  • the main load muff in turn, likewise has a rotationally symmetrical basic shape with an axis of rotation.
  • the axis of rotation of the main muffle and the axis of rotation of the part load muffle are in extension to each other. In other words, this can also be a single axis of rotation.
  • the main muffle is provided immediately after the part load muffle.
  • the invention is based on the finding that generic burners are usually designed only for one operating point, usually at 100% burner power. If now such a dimensioned burner driven with a lower load, so both the amount of combustion air supplied and the amount of fuel supplied is reduced. It has been found that from about 30% to 40% of the maximum load on a burner optimized for maximum load, the speeds at the burner head are so low that proper self-sustaining combustion can no longer be maintained and the burner fails, because the flame collapses. This is due to the fact that the flow rates of the combustion air and the fuel are very low, so that there is no sufficient mixing of the combustion air with the pulverized fuel and on the other hand that the supporting effect of the burner muffle is eliminated, since the flame far away from this. In addition, this plays an inadequate coordination of the combustion air-fuel ratio into it.
  • the burner muffle is subdivided into a main-load muffle and a partial-load muffle.
  • the part load muffle has a much smaller volume than the main load muffle. This results in the advantage that, if the burner is operated with, for example, only 20% of its maximum power, the flame can withdraw into the part load muffle and since it has a smaller volume, yet can be supported by the muffle wall. Due to the smaller volume and the outflow velocities of the combustion air and the fuel are sufficient so that the flame does not go out.
  • the burner is in full load operation or driven close to it, the flame of the burner can extend from the partial load muffle to the main muffle and occupy the entire space in the burner muffle, which is also referred to as the reaction space.
  • the part of the flame which is outside the part load muffle is supported by the main load muffle.
  • the burner head ie the area in which at least the fuel is supplied to the burner muffle or the combustion chamber, is located near or at the beginning of the partial load muffle.
  • the burner muffle consists of a small-volume part-load muffle, which widens in the direction of the burner mouth and converts to the bulky main muffle. This can be achieved, for example, in the form of two cylinders or cone-like structures arranged concentrically on the same axis of rotation, wherein a transition from the partial load muffle to the main load muffle is provided substantially in the radial direction.
  • combustion air supply is carried out at least three parts.
  • a first combustion air supply and a second combustion air supply for supplying combustion air are formed in the partial load muffle.
  • a third combustion air supply is provided for supplying combustion air into the main load muffle.
  • the combustion air supply By dividing the combustion air supply into different partial flows, a good and targeted combustion of the fuel can be achieved, as targeted a certain ratio of the combustion air to the fuel can be maintained.
  • the burner is operated only with 30% of its maximum load, and the burner flame is located substantially in the part load muffle, are also supplied via the different combustion air supply the combustion air mainly in the part load muffle.
  • This serves on the one hand for a good mixing of the fuel with the combustion air, which in turn enables efficient combustion and, on the other hand, prevents a collapse of the flame.
  • Another advantage of the division is that the individual feeds of the combustion air supply are each smaller. As a result, the combustion air supplies are operated at higher flow rates, which positively influences the stability of the flame.
  • solid fuel burners are generally operated at a lambda value between 1.4 and 2.0.
  • the quantities of combustion air both locally and temporally, must be adapted differently to the pulverulent fuel as a function of the thermal heat output.
  • This local and temporal supply of combustion air can be achieved by the use of the division of the combustion air supply according to the invention
  • the burner according to the invention is operated in part-load operation, for example at 30% of the maximum load, it must be ensured that the required lambda value is present in the region of the flame.
  • This can in turn be achieved by keeping the volume flow of the combustion air for the third combustion air supply relatively low and directing the majority of the combustion air via the first and / or second combustion air supply directly into the partial load muffle, since in this operating state the flame is substantially in the part load muffle is located. In other words, a large part of the combustion air is conducted into the part-load muffle.
  • the first and the second combustion air supply can be arranged arbitrarily in the region of the partial load muffle. It is advantageous if the first combustion air supply and the second combustion air supply are designed as an annular gap around the axis of rotation, wherein the first combustion air supply is provided closer to the axis of rotation than the second combustion air supply.
  • the combustion air can be injected well and evenly into the partial load muffle. Assuming that the fuel is injected relatively close to the axis of rotation, it turns out that way also a good mixing of the combustion air with the fuel. On the other hand, this provides the fuel with a sufficient amount of combustion air for combustion.
  • a further advantage of this arrangement - the first combustion air feed closer to the axis of rotation than the second combustion air feed - is that the principle which has already been described with respect to the main load muffle and the partial load muffle is also continued here. If the burner is operated at the lower end of its power range, for example at 10% of the maximum power, the required combustion air tends to be supplied by the first combustion air supply, which is closer to the axis of rotation, since in this operating state the flame is also smaller , However, if the burner is operated at 30% or 80% of its maximum load, combustion air can also be introduced into the part-load muffle through the second combustion air feed, resulting in sufficient combustion air supply for the corresponding load conditions.
  • the ratio of the exit cross-sectional areas of the combustion air of the first combustion air supply to the exit cross-sectional areas of the combustion air of the second combustion air supply is 1: 8 to 1:10. This means that the outlet cross-sectional areas of the first combustion air supply are made smaller than those of the second combustion air supply. This in turn makes it possible that the volume flow at assumed equal exit velocity of the combustion air of the first combustion air supply is less than the second combustion air supply. This in turn ensures that the flame is optimally supported and sufficient combustion air can be made available depending on the load condition of the burner.
  • the outlet cross-sectional areas of the combustion air of the third combustion air supply can be made arbitrarily large.
  • the ratio of the sum of the outlet cross-sectional areas of the combustion air of the first combustion air supply and the second combustion air supply to the outlet cross-sectional areas of the combustion air of the third combustion air supply is 1: 7 to 1:11.
  • the dimensioning of the outlet cross-sectional areas is such that, assuming an same flow rate through the outlet cross-sectional areas of the third combustion air supply, which conduct combustion air into the main muffle, significantly more combustion air can be supplied as by the two combustion air supply lines, which conduct combustion air into the part load muffle.
  • the second and / or the third combustion air supply in each case two or more independent combustion air feeds are executed with independent cross-sections.
  • This is particularly advantageous for burners with a maximum power of more than 10 MW.
  • This division is based on the finding that, as previously described in general, even with burners, which are designed for example for a maximum load of more than 100 MW, it is advantageous to further divide the combustion air supply, so that in each case an optimal supply to the one Combustion air quantity as well as in relation to the position of the supply line in the Brennermuffel the combustion air is possible. This allows for a sufficiently high lambda values and on the other hand a sufficiently high mixing within the burner muffle, so that a good combustion is achieved.
  • the second and / or third combustion air supply are each divided in the ratio of about 30:70 of the outlet cross-sectional areas of the combustion air, wherein the outlet for the smaller combustion air flow is provided closer to the axes of rotation.
  • the second combustion air supply is split into two separate combustion air supply lines, wherein the part of the second combustion air embodiment located further in the vicinity of the rotation axis has 30% of the cross-sectional area and the more external part of the second combustion air supply has 70% of the exit cross-sectional area.
  • the third combustion air supply can be divided into two, with one part having 30% and the other 70% of the total outlet cross-sectional areas.
  • swirl devices are provided for influencing the combustion air flows in a circular orbit about the axes of rotation within the part-load and main-load burner muffle. This ensures that a so-called swirl or whirl combustion chamber is generated.
  • a gas flow sets in, which rotates or runs around the axes of rotation in a spiral or helical manner.
  • the vortex profile of the gas flow thus generated in the combustion chamber forces the fuel particles due to the centrifugal force acting on a circular path on the outer walls of the combustion chamber.
  • the residence time of the fuel particles in the burner muffle or in the combustion zone of the combustion chamber, which is formed by the burner muffle increases, whereby a better more complete combustion can be achieved.
  • the invention relates to a method for operating a solid-fueled burner.
  • a burner has at least a first combustion air supply, a second combustion air supply and a third combustion air supply.
  • a burner muffle which consists of a partial load muffle and a main load muffle, wherein the first and the second combustion air supply for the supply of combustion air are designed in the part load muffle.
  • the third combustion air supply is designed to supply combustion air into the main muffle.
  • the solids-fired hot gas generator is operable in a continuous operating state between about 10% to 100% of its maximum power. It is further provided that the combustion air supply is controlled such that a flame is up to about 30% of the maximum power of the solids-fired hot gas generator substantially within the part load muffle.
  • the method is also based on the explained finding that in generic solid-fuel burners it is not possible to achieve operating states which are below about 40% of the maximum designed output.
  • the reason for this is that at a load range of 20% to 30% of the maximum load, the flow rates of both the combustion air and the fuel supply are so low that the flame is broken off or collapsed. This is also caused by the fact that the flame of the burner muffle is so far away that no supporting effect through the burner muffle is more present.
  • the combustion air supply is controlled such that the flame retreats from an amount of about 30% of the maximum power of the entire burner muffle, which is formed by the Kleinlastmuffel and the partial load muffle, substantially in the part load muffle.
  • This is smaller volume than the bulky Hauptlastmuffel.
  • the flame is better supported in the part load muffle.
  • With a smaller flow volume of the combustion air as well as delivery volume of the fuel supply a sufficiently good mixing and thus a combustion achieved so that the flame does not collapse. This makes it possible to operate the solid-fueled burner continuously between 10% or less up to 100% of its maximum power.
  • the second and third combustion air supply are operated at about 10% of their maximum design speed and that the first combustion air supply is operated at about 70% of its maximum design speed.
  • the speed with which the combustion air is blown out defines the volume of combustion air per unit time. This is decisive for influencing the burning behavior.
  • the flow rate is a common factor to influence this volume of combustion air per unit time, since the exit cross-sectional areas are determined by design.
  • the maximum design speed can be understood as meaning, in particular, the flow rate that is present when the burner is operated at 100% of its power.
  • the second and third combustion air supply By operating the second and third combustion air supply at about 10% of their maximum design speed and the first combustion air supply at about 70% of their maximum design speed, it is achieved that, when operated at 10% of the burner's maximum output, the relatively small flame is mainly due to the first combustion air supply is supplied with combustion air. If this combustion air supply is relatively close to the axes of rotation and the outlet of the delivery air of the fuel supply, then the flame is sufficiently supplied with combustion air and additionally supported. If the first combustion air supply is designed such that it directs its combustion air into the part-load muffle, it is also achieved by the process control according to the invention that, above all, combustion air reaches the part-load muffle. As a result, a supply of the flame, which has retreated into the partial load muffle, additionally supported.
  • the first combustion air supply from 70% to 100% of its maximum design speed.
  • the second combustion air supply can be continuously increased from 10% to 20% of its maximum design speed.
  • the second combustion air supply is located at the edge of the partial load muffle, so that by increasing the volume flow through the second combustion air supply, the flame is well supplied with additional air in the part of the partial mast, on the other hand also extending the flame is extended into the main muffle.
  • the flow velocity of the combustion air can be increased by the third combustion air supply in operation from 30% of the maximum power. It is preferred in this case if the flow rate is continuously increased from 10% to 100% of its maximum design speed when operating between 40% and 100% of the maximum power of the solid-fueled burner.
  • a section is shown by a schematic diagram of a burner 10 according to the invention.
  • the burner shown is a solids-fired burner 10.
  • the solids are supplied via the fuel supply 12 at the burner head, in which, for example, pulverized coal is blown into a burner muffle 20 by means of conveying air.
  • the burner muffle 20 is formed in two parts in the burner 10 according to the invention. It consists of a partial load muffle 21 and a main load muffle 22, which adjoins the part load muffle 21.
  • the partial load muffle 21 as well as the main load muffle 22 are rotationally symmetrical and arranged so that the respective rotational symmetry axis 25 coincides.
  • the partial load muffle 21 has approximately 5% to 10% of the volume of the main load muffle 22.
  • the solid-fuel fired burner 10 shown in sketched form has a high control ratio of 1:10. This is achieved by defining a partial load range I and a main load range II in the reaction space through the two-part burner muffle 20.
  • the reaction space is the internal volume of the burner muffle 20. If the burner 10 is operated at a low load or power, for example 10% of its maximum load, the operating parameters are adjusted such that the burner flame is substantially in the partial load range I. If the burner 10 is started up and operated, for example, with 70% of its maximum load or maximum power, then the now existing burner flame extends from the partial load range I to far into the partial load range II.
  • combustion air supplies 30 This behavior of the flame is achieved by the control of combustion air supplies 30.
  • Fig. 1 For this purpose, three combustion air supply lines 31, 32, 33 are provided. The first and the second combustion air supply 31, 32 lead their combustion air in the partial load muffle 21. The third combustion air supply 33 is arranged such that its combustion air is supplied directly into the main load muffle 22.
  • FIG. 2 is a further sketch of a section through a burner 10 according to the invention shown, in which now the various feeds into the burner interior or the burner muffle 20 are shown.
  • the burner muffle of the burner 10 is again designed in two parts and has a partial load muffle 21 and a main load muff 22.
  • the partial load muffle 21 has a substantially conical shape. It widens from the burner head in the direction of the main load muffle 22.
  • the angle of the cone is here preferably between 15 ° and 25 °.
  • the main load muffle 22 connects. This has at the beginning of a cone-like basic shape, which later merges into a cylinder-like shape. Both parts of the muffle 20 are rotationally symmetrical about a rotation axis 25 executed.
  • a starting burner 13 In the center of the axis of rotation 25 is located at the beginning of the burner head to the partial load muffle 21, a starting burner 13. To the starting burner 13, an annular gap is provided, which is provided as a fuel supply 12. By means of this annular gap, for example, pulverized coal can be blown into the burner interior or reaction space by means of a carrier medium, such as air. In principle, of course, other solid, crushed fuels can be blown thereby.
  • annular gap of the fuel supply 12 a further annular gap is provided concentrically. This is connected to the first combustion air supply 31.
  • swirling means 41 are provided in order to be able to impart a directional impulse to the exiting combustion air.
  • a second annular gap is provided, which is connected to the second combustion air feed 32.
  • This annular gap also ends in the partial load muffle 21.
  • swirl devices 42 are likewise provided at the transition of the annular gap for the second combustion air 32 into the partial load region I in order to be able to impart a swirl impulse to the incoming combustion air.
  • openings are still provided for supplying the third combustion air 33 in the region of the main load muffle 22. It is essential here at their position that the openings lead directly into the main load muffle, ie in the main load area II and not in the partial load range I. Thus, the proportion of combustion air, which is supplied via the third combustion air supply 33, are passed directly into the main load muffle ,
  • the respective volume flow of combustion air can be calculated.
  • the maximum design speeds for the combustion air supply 31, 32, 33 can be determined depending on the fuel used, for example lignite or hard coal, as well as the intended use of the burner.
  • the diagram shows three different curves, labeled a, b and c.
  • the curve a relates to the first combustion air supply 31, the curve b, the second combustion air supply 32 and the curve c, the third combustion air supply 33.
  • the addition of the combustion air supplied via the various combustion air feeds 31, 32, 33 gives the total amount of combustion air. This can be derived from the desired lambda value and the desired burner load.
  • the total combustion air supply is then split among the various combustion air supplies 31, 32, 33.
  • the first combustion air supply 31 is operated at 70% of its design speed.
  • the second combustion air supply 32 and the third combustion air supply 33 are each operated at 10% of their maximum design speed.
  • This operating state with 10% of the maximum design speed is also referred to as the cooling air position. This means that a large part of the combustion air is blown into the partial load range I. This in turn has the consequence that, since relatively little fuel is blown into the combined burner muffle 20, the flame is mainly in the partial load range I.
  • the first combustion air supply 31 is continuously increased to its maximum value.
  • the second combustion air supply 23 is continuously increased to about 20% of its maximum delivery speed, whereas the third combustion air supply 33 continues to operate at 10% of its maximum design speed.
  • This continuous startup of the air supply via the first and second combustion air feeds 31, 32 has the effect that a higher combustion air volume is available in the partial load range I.
  • This combustion air volume is stressed by the flame, which is operated with the solid fuel.
  • the amount of fuel per time is also increased. Due to the design according to the invention, the flame of the burner 10 continues to remain substantially in the partial load range I and can thus continue to be supported by the partial load muffle 21.
  • the first combustion air supply 31 is still operated at full load, that is, at its maximum Auslege für.
  • the second combustion air supply 32 is continuously increased. That is, the blow-off speed is continuously increased from 20% of the maximum lay-up speed to 100% of the maximum lay-up speed, so that 100% of the maximum lay-up speed is present at 100% of the power of the burner 10.
  • the blow-off rate of the third combustion air supply 33 is maintained to about 40% of the maximum load of the burner at 10% of the design speed. From the range around 40% of the maximum burner output, this also increases continuously until it reaches its maximum design speed at 100% of maximum burner power.
  • the burner flame extends only from about 30% of the maximum power of the burner in the main load range II. From 30% or 40%, the flame has such a strength that no longer There is a risk that it breaks off or goes out due to a stall of the combustion air. In other words, the flame migrates gradually from about 30% of the maximum power from the partial load muffle 21 into the main load muffle 22.
  • Another functionality of the combustion air supplied via the third combustion air feed 33 is that the wall-like burnout zones of the muffle 20 can hereby also be cooled. As a result, lower requirements can be made of the materials of the burner muffle 20.
  • Fig. 4 is a more detailed view of a section through a burner 10 according to the invention shown and in Fig. 5 is an enlargement of the burner head to the part load muffle 21 Fig. 4 shown.
  • the burner 10 according to the invention is essentially rotationally symmetrical.
  • a starting burner 13 is arranged with its feed 52. This is operated for example with gas or oil. It serves to start the burner 10 according to the invention.
  • the starting burner 13 is first operated for a time until a sufficiently high temperature is present in the muffle 20 in order to start the actual solid fuel-fired burner 10.
  • swirl devices 41 which can also be referred to as swirl blades, are arranged in the annular gap in order to be able to impart a twist in helical form about the central axis 25 to the injected combustion air.
  • annular gap for the second combustion air supply 32 is arranged around the annular gap for the first combustion air supply 31.
  • swirl devices 42 or swirl vanes are again provided shortly before the outlet in order to twist the combustion air which is thereby blown out.
  • the main load muffle 22 connects.
  • the third combustion air supply 31 is guided.
  • This feed is not carried out again in the embodiment shown here via an annular gap, but a supply 60 for the third combustion air leads into an air distributor 61 for the third combustion air.
  • This in turn is connected to outlet openings 62 for the third combustion air.
  • These openings lead into the main load area II, ie into the interior or reaction space of the main load muff 22.
  • the air distribution 61 is connected to the interior of the main load muff 22 by means of a mask having the outlet opening 62. Through the openings 62 for the third combustion air supply of the combustion air also a swirl can be given up.
  • Into the muffle 20 projects laterally a pilot burner 51 into it. This is used to start the starting burner 13.
  • normal external air can be supplied as combustion air through the first, second and third combustion air feeds 31, 32, 33.
  • the burner 10 according to the invention is used in a hot gas generator, in particular for coal grinding plants, then it is advantageous to supply a mixture of outside air and oxygen-poor air or recirculated air via the third combustion air feed 33. This is necessary because the hot process gases used in mill grinding in coal grinding plants must have a maximum oxygen content of 10% in order to prevent dust explosions.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Muffle Furnaces And Rotary Kilns (AREA)

Claims (13)

  1. Brûleur par allumage de matières solides (10)
    avec une arrivée de combustible (12) au moyen d'air de refoulement et
    avec un moufle de brûleur (20),
    dans lequel le moufle de brûleur (20) est divisé en un moufle à charge principale (22) et en un moufle à charge partielle (21),
    dans lequel le moufle à charge partielle (21) présente 5 % à 10 % du volume du moufle à charge principale (22),
    dans lequel le moufle à charge partielle (21) présente une forme de base conique symétrique en rotation avec un axe de rotation (25),
    dans lequel le moufle à charge principale (22) présente une forme de base symétrique en rotation avec un axe de rotation (25),
    dans lequel l'axe de rotation (25) du moufle à charge principale (22) se situe dans un prolongement de l'axe de rotation (25) du moufle à charge partielle (21), et
    dans lequel le moufle à charge principale (22) est prévu directement dans le prolongement du moufle à charge partielle (21),
    caractérisé en ce
    qu'en supplément de l'arrivée de combustible au moyen d'air de refoulement, une arrivée d'air de combustion réalisée en trois parties est prévue,
    qu'une première arrivée d'air de combustion (31) et une deuxième arrivée d'air de combustion (32) sont réalisées pour amener de l'air de combustion dans le moufle à charge partielle (21),
    qu'une troisième arrivée d'air de combustion (33) est réalisée pour amener de l'air de combustion dans le moufle à charge principale (22),
    que la première arrivée d'air de combustion (31) et la deuxième arrivée d'air de combustion (32) sont disposées respectivement en tant qu'une fente annulaire autour de l'arrivée de combustible (12), et
    que la première arrivée d'air de combustion (31) et la deuxième arrivée d'air de combustion (32) sont réalisées sous la forme d'une fente annulaire autour des axes de rotation (25), et
    que la première arrivée d'air de combustion (31) est prévue davantage à proximité des axes de rotation (25) que la deuxième arrivée d'air de combustion (32).
  2. Brûleur par allumage de matières solides selon la revendication 1, caractérisé en ce
    que le rapport entre les surfaces de section transversale de sortie de l'air de combustion de la première arrivée d'air de combustion (31) et les surfaces de section transversale de sortie de l'air de combustion de la deuxième arrivée d'air de combustion (32) va de 1:8 à 1:10.
  3. Brûleur par allumage de matières solides selon l'une quelconque des revendications 1 ou 2,
    caractérisé en ce
    que le rapport entre la somme des surfaces de section transversale de sortie de l'air de combustion de la première arrivée d'air de combustion (31) et de la deuxième arrivée d'air de combustion (32) et les surfaces de section transversale de sortie de l'air de combustion de la troisième arrivée d'air de combustion (33) va de 1:7 à 1:11.
  4. Brûleur par allumage de matières solides selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce
    que des souffleurs servant à refouler l'air de combustion vers les arrivées d'air de combustion (31, 32, 33) sont prévues, et
    que la vitesse nominale maximale de la première (31) et de la deuxième (32) arrivée d'air de combustion est 1,8 à 2,5 fois supérieure à la vitesse nominale maximale de la troisième arrivée d'air de combustion (33).
  5. Brûleur par allumage de matières solides selon l'une quelconque des revendications 1 à 4,
    caractérisé en ce
    que la deuxième (32) et/ou la troisième (33) arrivée d'air de combustion sont réalisées dans le cas d'un brûleur avec une puissance maximale supérieure à 10 MW dans respectivement deux arrivées d'air de combustion (32, 33) ou plus respectivement indépendantes avec des sections transversales indépendantes.
  6. Brûleur par allumage de matières solides selon la revendication 5, caractérisé en ce
    que la deuxième (32) et/ou la troisième (33) arrivée d'air de combustion sont réparties respectivement selon un rapport d'environ 30:70 des surfaces de section transversale de sortie de l'air de combustion, dans lequel la sortie pour le flux d'air de combustion respectivement plus petit est prévue davantage à proximité des axes de rotation (25).
  7. Brûleur par allumage de matières solides selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce
    que sont prévus au niveau de la sortie au moins de la première et de la deuxième arrivée d'air de combustion (31, 32), des dispositifs de tourbillonnement (41, 42) servant à influencer les écoulements d'air de combustion sur une trajectoire autour des axes de rotation (25) à l'intérieur du moufle à charge partielle (21) et du moufle à charge principale (22).
  8. Procédé servant à faire fonctionner un brûleur par allumage de matières solides (10)
    avec au moins une première arrivée d'air de combustion (31), une deuxième arrivée d'air de combustion (32) et une troisième arrivée d'air de combustion (33),
    avec un moufle à charge partielle (21) et un moufle à charge principale (22),
    dans lequel la première (31) et la deuxième arrivée d'air de combustion (32) sont configurées pour amener de l'air de combustion dans le moufle à charge partielle (21) et la troisième arrivée d'air de combustion (33) est configurée pour amener de l'air de combustion dans le moufle à charge principale (22), dans lequel le brûleur par allumage de matières solides (10) peut fonctionner dans un état de fonctionnement continu entre 10% et 100% de sa puissance (P) maximale,
    caractérisé en ce
    que les arrivées d'air de combustion (31, 32, 33) sont régulées de telle manière qu'une flamme se trouve sensiblement à l'intérieur du moufle à charge partielle (21) jusqu'à 30 % de la puissance (P) maximale du brûleur par allumage de matières solides (1).
  9. Procédé selon la revendication 8,
    caractérisé en ce
    que lors d'un fonctionnement autour de 10 % de la puissance (P) maximale du brûleur par allumage de matières solides (1), la deuxième (32) et la troisième arrivée d'air de combustion (33) fonctionnent avec environ 10 % de leur vitesse nominale maximale, et
    que la première arrivée d'air de combustion (31) fonctionne avec environ 70 % de sa vitesse nominale maximale.
  10. Procédé selon l'une quelconque des revendications 8 ou 9,
    caractérisé en ce
    que lors d'un fonctionnement entre environ 10, % et environ 30 % de la puissance (P) maximale du brûleur par allumage de matières solides (1), la première arrivée d'air de combustion (31) est élevée en continu de 70 % à 100 % de sa vitesse nominale maximale.
  11. Procédé selon l'une quelconque des revendications 8 à 10,
    caractérisé en ce
    que lors d'un fonctionnement entre environ 10% et environ 30 % de la puissance (P) maximale du brûleur par allumage de matières solides (1), la deuxième arrivée d'air de combustion (32) est élevée en continu de 10 % à 20 % de sa vitesse nominale maximale.
  12. Procédé selon l'une quelconque des revendications 8 à 11,
    caractérisé en ce
    que lors d'un fonctionnement entre environ 30 % et 100 % de la puissance (P) maximale du brûleur par allumage de matières solides (10), la deuxième arrivée d'air de combustion (32) est élevée en continu de 20 % à 100 % de sa vitesse nominale maximale.
  13. Procédé selon l'une quelconque des revendications 8 à 12,
    caractérisé en ce
    que lors d'un fonctionnement entre environ 40 % et 100 % de la puissance (P) maximale du brûleur par allumage de matières solides (10), la troisième arrivée d'air de combustion (33) est élevée en continu de 10 % à 100 % de sa vitesse nominale maximale.
EP14195218.4A 2014-11-27 2014-11-27 Brûleur par allumage de matière solide Active EP3026339B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP14195218.4A EP3026339B1 (fr) 2014-11-27 2014-11-27 Brûleur par allumage de matière solide
PCT/EP2015/077060 WO2016083225A1 (fr) 2014-11-27 2015-11-19 Brûleur à combustible solide
RU2017108689A RU2665375C1 (ru) 2014-11-27 2015-11-19 Горелка на твёрдом топливе

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14195218.4A EP3026339B1 (fr) 2014-11-27 2014-11-27 Brûleur par allumage de matière solide

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EP3026339A1 EP3026339A1 (fr) 2016-06-01
EP3026339B1 true EP3026339B1 (fr) 2019-02-27

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EP (1) EP3026339B1 (fr)
RU (1) RU2665375C1 (fr)
WO (1) WO2016083225A1 (fr)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4523530A (en) * 1982-02-26 1985-06-18 Sumitomo Metal Industries, Ltd. Powdery coal burner
US4531461A (en) * 1982-05-14 1985-07-30 T.A.S., Inc. Solid fuel pulverizing and burning system and method and pulverizer and burner therefor
DE3310500C2 (de) * 1983-03-23 1985-04-04 Steag Ag, 4300 Essen Brenner zur Verbrennung von staubförmigen Brennstoffen, insbesondere Kohlenstaub
FR2581444B1 (fr) * 1985-05-03 1988-11-10 Charbonnages De France Procede pour la combustion de combustibles fluides et bruleur a turbulence adapte a sa mise en oeuvre
DE19527083A1 (de) * 1995-07-25 1997-01-30 Lentjes Kraftwerkstechnik Verfahren und Brenner zur Verminderung der Bildung von NO¶x¶ bei der Verbrennung von Kohlenstaub
DE19706077A1 (de) 1997-02-17 1998-08-20 Loesche Gmbh Heißgaserzeuger
DE19725613A1 (de) 1997-06-17 1998-12-24 Kohlenstaubtechnik Dr Schoppe Heißgaserzeuger
DE10232373B4 (de) 2002-07-17 2009-04-02 Schoppe, Fritz, Dr.-Ing. Verfahren zur Erhöhung der Flammstabilität bei Kohlenstaubfeuerungen und Vorrichtung zur Ausführung des Verfahrens

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

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Publication number Publication date
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RU2665375C1 (ru) 2018-08-29
WO2016083225A1 (fr) 2016-06-02

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