JET BURNER APPARATUS

RELATED APPLICATION

[0001]This application is a national phase of international application No. PCT/DE2023/100229 filed on Mar. 23, 2023, and claims the benefit of German application No. 10 2022 106 814.5 filed on Mar. 23, 2022, which are incorporated herein by reference in their entirety and for all purposes.

FIELD OF DISCLOSURE

[0002]The present disclosure concerns a jet burner apparatus for combustion of at least one fuel with at least one oxidizer. Furthermore, the present disclosure concerns a combustion chamber device with a jet burner apparatus, and furthermore a thermal exhaust gas cleaning system and a gas turbine with a jet burner apparatus.

BACKGROUND

[0003]Ever more stringent legal requirements impose, for example in thermal exhaust air cleaning systems, a trend towards ever lower NOx values which are difficult to achieve with the former combustion devices or burners, since sometimes very high combustion chamber temperatures prevail with a low mass stream. Also, in conventional low NOx jet burners, the burner jet enters the flow region very deeply after the burner head, whereby larger recirculation zones occur at the side of this jet. Accordingly, attempts are made to achieve rapid homogenization of fuel and oxidizer with complex injection geometry, but in larger burners this rapidly leads to high investment levels. Finally, the present burners are not designed for the use of hydrogen.

SUMMARY

[0004]The present disclosure is based on the object of creating a jet burner apparatus of the type cited initially which can be produced easily and cheaply, achieves an even and rapid mixing of fuel and oxidizer, causes lower NOx emissions and/or is at least prepared for the use of hydrogen/methane mixtures.

[0010]wherein the at least one injection device is arranged in the at least one flow channel such that the oxidizer flows around the at least one injection device, and

[0011]wherein the at least one swirl device is arranged upstream or downstream of the at least one injection device relative to the main flow direction.

[0012]With the jet burner apparatus according to examples disclosed herein, it may be advantageous that, in comparison with a conventional jet burner apparatus, significantly lower NOx values can be achieved with a more even combustion. The swirling increases the local speed amount and hence the shear layer and turbulence. This increases the mixing of fuel and oxidizer, reinforcing a premixing effect for combustion or thermal oxidation, which achieves a reduction in NOx emissions with a simultaneous increase in burn-out. The swirling also increases the recirculation in the combustion chamber, whereby flue gas with reduced oxygen content flows back into the combustion zone, which also leads to a reduction in NOx emissions. Thus as a whole, the combustion chamber temperature can be achieved with simultaneously reduced NOx emissions.

[0013]The swirling of the oxidizer and fuel creates a recirculation zone in the interior of the jet burner apparatus, which pushes the jet stream towards the outside. In the case of possible installation in a combustion chamber of larger diameter or larger width, the swirling causes an additional recirculation radially to the side of the jet burner apparatus. This widens the flow downstream of the jet burner apparatus, resulting firstly in a better mixing—also with secondary air- and a more homogenous temperature profile etc., and secondly cold flows, amongst others along the combustion chamber wall, are reduced. The structure of the jet burner apparatus according to examples disclosed herein and its operation therefore allow an increased temperature for the complete fluid, i.e. the mixture of oxidizer and fuel, also essentially directly downstream of the jet burner apparatus.

[0014]For applications with thermal exhaust air cleaning, i.e. oxidation of any reactive substances dissolved in the oxidizer, furthermore an increase in the complete fluid stream downstream of the jet burner apparatus can be achieved and the entire system operated at a low reactor temperature, since any cold air paths with reduced exhaust air cleaning reactions are greatly decreased. As a result, therefore, cleaning of the dissolved substances can be achieved with reduced reactor temperature, which means a fuel saving with simultaneously reduced NOx emissions.

[0015]In principle, a jet burner apparatus is a burner device or burner stage with high speed and high turbulence. It may be operated premixed, unmixed or even post-mixed with respect to the fuel and oxidizer. Different types and also effects for stabilizing the flame and reducing emissions are known.

[0016]The low emission values are achieved in a jet burner apparatus with fuel injection in a so-called jet, i.e. the flow in the at least one flow channel, by the higher flow speed which, at the same time, increases the corresponding turbulence and hence causes a better mixing of fuel and oxidizer.

[0017]The speed distribution in the jet stream in the at least one flow channel is ideally such that oxidation is stabilized, in that the turbulent flame speed is greater than or equal to the flow speed, and the mixture of fuel and oxidizer thereby delivers sufficient energy for oxidation.

[0018]Conventionally, a jet burner apparatus with a direct injection of fuel into the jet stream in the at least one flow channel has a central flame which, in particular, has speed components in the direction of the central longitudinal axis. Such a jet burner apparatus admittedly has very low emission values at the correct load point, i.e. at the optimally set load point, but also a tendency to instability. Stabilization therefore preferably takes place via recirculation zones, usually around the flame.

[0019]Furthermore, it is understood that the central longitudinal axis is preferably an axis of symmetry along the jet burner apparatus, and the main flow direction, in particular parallel thereto, is an axial direction, i.e. any twist with respect to the main flow direction remains disregarded unless explicitly specified otherwise.

[0020]The at least one flow channel, which preferably runs parallel to the main flow direction, is preferably delimited radially outwardly relative to the central longitudinal axis by the flame tube. On the radial inside, the at least one flow channel is preferably delimited by a guide tube whereby, as a whole, a circular ring-shaped cross-section is formed. It is however also conceivable that the flow channel does not completely surround the flame tube, whereby for example in cross-section an at least substantially C-shaped form is created, or in cross-section the flow channel is formed from a plurality of circle ring sectors which may be regarded as sub-units of the flow channel. The wall thickness of the flame tube and guide tube may be the same or different.

[0021]Preferably, the flame tube and guide tube, inside which the flame tube is arranged, are oriented parallel to one another. It is however also conceivable that both tubes are formed such that they run towards one another downstream relative to the main flow direction, i.e. either both tubes enclose an angle greater than zero with the central longitudinal axis, or just one of the two. Thus the cross-section of the flow channel reduces downstream. Such a tapering may however also only concern a portion of the flow channel.

[0022]It is favorable if the flow tube forms at least one diffuser at its downstream end relative to the main flow direction, wherein the diffuser may comprise multiple segments. The widening of the diffuser slows down the flow and builds up static pressure. Accordingly, the diffuser promotes recirculation of the inner flow. Also, because of the diffuser, the geometry of the flame tube is stabilized, e.g. the corresponding end of the flame tube has a stiffness which is greater than that of a cylindrical design. The diffuser preferably causes a spreading of a part of the oxidizer flowing along the outside of the flame tube. Spreading or widening of this part of the oxidizer may be particularly important for rapid mixing of fuel and oxidizer, which preferably leads to improved cleaning of exhaust air.

[0023]In an embodiment of examples disclosed herein, it is provided that the at least one flow channel is configured as a ring. In this respect, it should be understood that, as described above, the ring shape of the flow channel may also be formed by a plurality of ring sectors or segments, i.e. relative to a cross-section, the channel may also be interrupted in at least one portion.

[0024]In an embodiment of examples disclosed herein, it is provided that a through-flow cross-sectional area of the at least one flow channel is constant or diminishes along the main flow direction.

[0025]In an embodiment of examples disclosed herein, it is provided that the through-flowable cross-sectional area of the at least one flow channel is constant upstream of the at least one injection device relative to the main flow direction, and reduces downstream of the at least one injection device. It is however also possible that the through-flowable cross-sectional area widens upstream of the at least one injection device in order to improve the inflow into the flow channel.

[0026]This has the advantage of accelerating the fluid stream, whereby the flow is stabilized, leading to an improved mixing because of a reduction in detachment zones, and because of higher speeds and turbulence. Accordingly, combustion is achieved with a higher burn-out and lower emissions.

[0027]The acceleration of the flow at the injection device may also serve as a dynamic flame block.

[0028]It is favorable if the through-flowable cross-sectional area of the at least one flow channel reduces multiple times, preferably in two stages, upstream of the at least one injection device relative to the main flow direction, has a constant through-flowable cross-sectional area in the region of the at least one injection device, and reduces again at least once downstream of the at least one injection device.

[0029]It is preferred if the ratio of the length of the flow channel upstream of the at least one injection device to the width of the through-flowable cross-sectional area is at least 0.5.

[0030]In an embodiment of examples disclosed herein, it is provided that the at least one injection device is formed as a ring tube.

[0031]Preferably, the injection device has a round or angular cross-section, wherein round or rounded cross-sections include circular, oval and elliptical cross-sections.

[0032]In an embodiment of examples disclosed herein, it is provided that the swirl device is attached to the at least one injection device or spaced from the at least one injection device.

[0033]It is favorable if the swirl bodies of the swirl device have the form of straight or curved plates; however, wing profiles or similar, amongst others, are also conceivable.

[0034]In an embodiment of examples disclosed herein, it is provided that the at least one injection device has first injection openings, the central axes of which point at least approximately in the main flow direction.

[0035]Thus the fuel and/or oxidizer is injected into the combustion chamber at least approximately parallel to the main flow direction, wherein the central axis of an injection opening means its main outflow direction.

[0036]It is however also conceivable that the central axes of the injection openings and the main flow direction enclose an angle of more than zero, since it may be advantageous not to orient the injection openings in the direction of the main flow direction but, depending on further adjustable elements of the jet burner apparatus, to predefine an angle relative to the main flow direction, for example in order to optimize the mixing of the injected fuel and through-flowing oxidizer.

[0037]In an embodiment of examples disclosed herein, it is provided that at least one of the first injection openings has an injection nozzle protruding in the main flow direction.

[0038]It is favorable here that, depending on their profile or geometry along the central axis, injection nozzles at the injection openings can increase the speed with which the fuel emerges from the injection opening.

[0039]In an embodiment of examples disclosed herein, it is provided that the at least one injection device has second injection openings, the central axes of which each enclose an angle of between 0 degrees and 90 degrees with the main flow direction.

[0040]In particular, it may be advantageous if the second injection openings enclose an angle different from zero with the first injection openings.

[0041]Additional injection openings, which are not oriented in the main flow direction, preferably allow local premixed combustion, or at least an increase in the local mixing of fuel and oxidizer, and thereby, as well as an increase in available fuel volume, the homogenization of the mixture overall is accelerated.

[0042]In a further possible embodiment of examples disclosed herein, it may be provided that the first and second injection openings are controllable independently of one another, i.e. either the first, the second or both the first and second injection openings can be activated or deactivated, whereby the volume flow of fuel can be adjusted. Furthermore, it is possible that different fuels are injected via the first and the second injection openings. The first and the second injection openings of the at least one injection device may be arranged alternately or in groups.

[0043]In an embodiment of examples disclosed herein, it is provided that a first and a second injection device are arranged in the at least one flow channel, wherein the first and second injection devices are arranged at the same height or offset to one another relative to the main flow direction.

[0044]This allows either a larger quantity of fuel or different fuel to be mixed with the through-flowing oxidizer inside a flow channel.

[0045]In an embodiment of examples disclosed herein, it is provided that the jet burner apparatus has a first and a second flow channel, wherein the first flow channel is arranged radially on the inside of the second flow channel relative to the longitudinal axis, and wherein the second flow channel is delimited radially outwardly by the flame tube relative to the central longitudinal axis.

[0046]Thus, firstly, the first flow channel is delimited radially on the inside by a guide tube, and secondly, the two flow channels are separated from one another by a further guide tube. Preferably, the flame tube and the two guide tubes are oriented parallel to one another.

[0047]In an embodiment of examples disclosed herein, it is provided that a first injection device is arranged in the first flow channel, and a second injection device is arranged in the second flow channel.

[0048]Thus either more fuel can be injected into the totality of flow channels, or different fuels injected per injection device.

[0049]In an embodiment of examples disclosed herein, it is provided that a swirl device is arranged in the first and/or second flow channel upstream of the first and/or second injection device relative to the main flow direction.

[0050]It is advantageous here that the swirling of the respective through-flowing oxidizer part by means of the swirl device can accelerate and improve the mixing of fuel and oxidizer.

[0051]In an embodiment of examples disclosed herein, it is provided that the jet burner apparatus comprises multiple injection nozzles for injection of at least one fuel, and that an injection device and a swirl device are arranged in the first flow channel, and that the injection nozzles are arranged in the second flow channel, wherein the swirl device is arranged upstream of the injection device relative to the main flow direction.

[0052]The same fuel or also different fuels can be supplied into the second flow channel via the injection nozzles.

[0053]In an embodiment of examples disclosed herein, it is provided that the jet burner apparatus comprises multiple injection nozzles for injection of at least one fuel, which are arranged at least partly radially inside the guide tube.

[0054]Preferably, fuel or a mixture of fuel and oxidizer can be injected via the injection nozzles. The oxidizer here flushes or flows around the outer surface of the injection nozzles.

[0058]With a central burner stage, it is favorable that an additional, axially swirled oxidizer part is supplied to the combustion chamber.

[0059]In an embodiment of examples disclosed herein, it is provided that the central burner stage furthermore comprises at least one injection device, wherein the at least one injection device is arranged at least partly downstream of the swirl device relative to the main flow direction, and wherein the injection device of the central burner stage comprises multiple differently formed injection openings.

[0060]Thus additionally, either the same fuel or another fuel may be injected, which is rapidly and efficiently mixed with a swirled oxidizer part by an upstream swirl device relative to the main flow direction.

[0061]In an embodiment of examples disclosed herein, it is provided that the central burner stage furthermore comprises a baffle plate with a plurality of baffle openings for fuel and/or oxidizer, wherein the baffle plate is arranged downstream of the injection device relative to the main flow direction, and wherein the baffle plate comprises multiple differently formed baffle openings.

[0062]With such a central burner stage, it may be advantageous that, in comparison with conventional pilot stages, significantly lower NOx values can be achieved with a more even combustion. A more even and faster mixing of fuel and oxidizer accelerates the corresponding thermal reactions, whereby the combustion chamber temperature can be lowered.

[0063]In particular, the use of the baffle plate preferably promotes recirculation, accelerates the injected fuel and/or allows an improved mixing of fuel and oxidizer. As a result, as already stated, combustion can preferably take place at lower temperatures, whereby in particular the NOx emissions are lowered.

[0064]It is particularly advantageous if each two adjacent baffle openings of the baffle plate, and/or each two adjacent injection openings of the injection device, are formed and/or arranged differently in shape, dimensions and orientation relative to one another and/or relative to the main flow direction or central longitudinal axis.

[0065]It is furthermore advantageous if the baffle plate is arranged at the injection device, i.e. in the immediate physical vicinity relative to the main flow direction, without however thereby hindering the flow of oxidizer around the injection device through the baffle opening of the baffle plate.

[0066]In an embodiment of examples disclosed herein, it is provided that the flame tube is arranged in a casing tube such that, between the flame tube and the casing tube, a bypass flow channel is formed through which a part of the oxidizer can flow.

[0067]The diversion of a part of the oxidizer flow into the bypass flow channel preferably accelerates the rapid mixing of the fuel and oxidizer.

[0068]In an embodiment of examples disclosed herein, it is provided that at least one bypass injection device for injection of fuel is arranged in the bypass flow channel between the flame tube and the casing tube.

[0069]Because of the bypass injection device, fuel is already mixed with part of the oxidizer in the bypass flow channel. Thus the bypass injection increases the combustion, wherein the fuel which is injected by means of the bypass injection device may be the same fuel as the fuel injected via the further injection devices, but also a fuel different from this.

[0070]In an embodiment of examples disclosed herein, it is provided that at least one bypass swirl device for swirling the oxidizer part is arranged in the bypass flow channel between the flame tube and the casing tube, wherein the bypass injection device is arranged downstream of the at least one bypass swirl device relative to the main flow direction.

[0071]This promotes the mixing of the fuel injected by the bypass injection device and the oxidizer part flowing through the bypass flow channel. Also, the fuel from the bypass injection device is injected into the swirled oxidizer part, which leads to improved mixing.

[0072]In an embodiment of examples disclosed herein, it is provided that a narrowing element is arranged on the upstream end of the casing tube relative to the main flow direction, for setting the part of the oxidizer flowing through the bypass flow channel.

[0073]The part of the oxidizer flowing through the bypass flow channel can be set via the narrowing element. The narrowing element is preferably configured as a tube ring with rectangular cross-section. For improved distribution of the oxidizer, the upstream surface of the narrowing element may also be profiled.

[0074]It is also conceivable that, in addition, fuel can be injected into the bypass flow channel via the narrowing element.

[0075]In an embodiment of examples disclosed herein, it is provided that the oxidizer enters the jet burner apparatus with a speed of 50 m/s to 70 m/s, in particular 60 m/s.

[0076]The object is furthermore achieved according to examples disclosed herein by the use of a jet burner apparatus as described above. Here, the jet burner apparatus is used for combustion of at least one fuel with at least one oxidizer, in particular for cleaning a contaminated gas stream, preferably a gas stream contaminated with organic substances. Such a jet burner apparatus is thus used in particular for exhaust gas cleaning and/or exhaust air cleaning.

[0077]The object may furthermore be achieved according to examples disclosed herein by a combustion chamber system with at least one combustion chamber and at least one jet burner apparatus as described above, wherein the outer periphery of the jet burner apparatus is connected to a floor of the combustion chamber.

[0078]In an embodiment of examples disclosed herein, it is provided that the jet burner apparatus is inserted in the combustion chamber device and attached outside the combustion chamber device, wherein between the outer periphery of the jet burner apparatus and the combustion chamber device, a ring gap is formed through which a part of the oxidizer can flow.

[0079]Accordingly, in particular in a jet burner apparatus with casing tube, a part of the oxidizer flows firstly through the flow channel between flame tube and casing tube, and secondly through the ring gap between the casing tube and the corresponding insertion region of the combustion chamber device. This ring gap may be formed asymmetrically as a result of production tolerances or also due to thermal deformations. The provision of a casing tube nonetheless ensures that a symmetrical flow from the flame tube to the opening of the combustion chamber device prevails.

[0080]The object may furthermore be achieved according to examples disclosed herein by a thermal exhaust gas cleaning plant with a jet burner apparatus as described above.

[0081]The object may furthermore be achieved according to examples disclosed herein by a gas turbine device with a jet burner apparatus as described above.

[0086]Further advantages and/or features of the jet burner apparatus according to examples disclosed herein are the subject of the following description and the illustration of exemplary embodiments in the drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

[0087]FIG. 1 shows a schematic, perspective illustration of a first embodiment of a jet burner apparatus according to examples disclosed herein;

[0088]FIG. 2 shows a first schematic, perspective, longitudinal sectional illustration of the first embodiment from FIG. 1;

[0089]FIG. 3 shows a schematic, longitudinal sectional illustration of the first embodiment from FIG. 1;

[0090]FIG. 4 shows a schematic, perspective, longitudinal sectional illustration of a second embodiment of a jet burner apparatus according to examples disclosed herein;

[0091]FIG. 5 shows a schematic, perspective illustration of a first embodiment of a burner stage;

[0092]FIG. 6 shows a schematic, perspective, sectional illustration of the first embodiment from FIG. 5;

[0093]FIG. 7 shows a schematic top view of the first embodiment from FIG. 5;

[0094]FIG. 8 shows a schematic, perspective illustration of a third embodiment of a jet burner apparatus according to examples disclosed herein;

[0095]FIG. 9 shows a schematic, perspective, longitudinal sectional illustration of the third embodiment from FIG. 8;

[0096]FIG. 10 shows a schematic, longitudinal sectional illustration of a part of a combustion chamber device according to examples disclosed herein with an inserted jet burner apparatus;

[0097]FIG. 11 shows a schematic, perspective illustration of a second embodiment of a burner stage;

[0098]FIG. 12 shows a schematic side view of the second embodiment of a burner stage from FIG. 11;

[0099]FIG. 13 shows a schematic, perspective illustration of a third embodiment of a burner stage;

[0100]FIG. 14 shows a schematic, perspective illustration of a fourth embodiment of a burner stage;

[0101]FIG. 15 shows a schematic, perspective illustration of a fifth embodiment of a burner stage;

[0102]FIG. 16 shows a schematic top view of the fifth embodiment of a burner stage from FIG. 15;

[0103]FIG. 17 shows a schematic, perspective, partial illustration of a sixth embodiment of a burner stage; and

[0104]FIG. 18 shows a schematic, perspective, partial illustration of a seventh embodiment of a burner stage.

[0105]The same or functionally equivalent elements carry the same reference signs in all figures.

DETAILED DESCRIPTION OF THE DRAWINGS

[0106]FIG. 1 shows a schematic, perspective illustration of a first embodiment of a jet burner apparatus 100 according to examples disclosed herein which serves for combustion of at least one fuel with at least one oxidizer.

[0107]The jet burner apparatus 100 is formed substantially rotationally symmetrically about a central longitudinal axis 102, wherein a main flow direction 104 runs at least approximately parallel to the central longitudinal axis 102.

[0108]The jet burner apparatus 100 comprises, as components visible in FIG. 1, a flame tube 106, on the downstream end of which a diffuser 108 is formed, wherein it is furthermore evident from FIG. 1 that the cross-section of the flame tube 106 tapers in a portion 110, accelerating the flow.

[0109]The flame tube 106 is surrounded by a casing tube 112, whereby between the flame tube 106 and the casing tube 112, a ring-shaped bypass flow channel 114 is formed in which a bypass swirl device 116 with a plurality of swirl plates 118 is arranged for swirling the oxidizer part flowing through the bypass flow channel.

[0110]A narrowing element 120 is arranged at the upstream end of the casing tube 112, and serves to set the part of the oxidizer which should flow through the bypass flow channel 114.

[0111]FIG. 2 shows a first schematic, perspective, longitudinal sectional illustration of the first embodiment from FIG. 1, while FIG. 3 shows a purely schematic, longitudinal sectional illustration.

[0112]It is clear from FIGS. 2 and 3 that a guide tube 122 is arranged inside the flame tube 106, whereby between the flame tube 106 and the guide tube 122, a flow channel 124 is formed through which a part of the oxidizer can flow.

[0113]A swirl device 126 with a plurality of swirl plates 128, and an injection device 130 in the form of a ring tube, are arranged inside the flow channel 124, wherein the injection device 130 in the form of a ring tube is arranged downstream of the swirl device 126.

[0114]The through-flowing part of the oxidizer is thereby deflected only once for swirling, and the flow speed can hence be used preferably almost unchanged for mixing with the fuel. Injection of the fuel is preferably optimized by such a structure and optimally fewer pressure losses and/or lower emissions are achieved.

[0115]Furthermore, a central burner stage 132, comprising an injection device 134 and a swirl device 136, is arranged inside the guide tube 122. The injection device 134 with injection openings 138 is formed tubular and oriented parallel to the guide tube 122, so that a ring-shaped central flow channel 140 is formed between the guide tube 122 and the injection device 134.

[0116]The cross-section of the guide tube 122 increases once in the region of the swirl device 126 and again after the injection device 130. Correspondingly, in the portion 110 of the flame tube 106, its inner radius reduces at the level of the swirl device 126 and again after the injection device 130. As a whole, the flow inside the flow channel 124 is thereby accelerated in two stages.

[0117]It is however also conceivable that the through-flowable cross-sectional area of the flow channel 124 is already reduced in stages multiple times, preferably twice, upstream of the injection device 130.

[0118]FIG. 4 shows a schematic, perspective, longitudinal sectional illustration of a second embodiment of a jet burner apparatus 100 according to examples disclosed herein;

[0119]In contrast to the first embodiment from FIGS. 1 and 2, the guide tube 122 has a constant cross-section along the main flow direction 104.

[0120]Also, within the guide tube 122, the central burner stage 132 comprises, as well as the injection device 134 and swirl device 136, a further injection device 142 in the form of a ring tube which is arranged downstream of the swirl device 136, and a baffle plate 144 which is arranged downstream of the injection device 142 in the form of a ring tube.

[0121]The cooperation of the swirl device 136, the injection device 142 and the baffle plate is explained in more detail below in connection with FIGS. 5 to 8.

[0122]FIGS. 5 to 7 show a first embodiment of a central burner stage 132 in a schematic, perspective illustration and sectional illustration, and in a schematic top view.

[0123]In FIGS. 5 to 7, the central burner stage 132 is shown inside the swirl device 126 and the injection device 130 of the flow channel 124, without being separated therefrom by the guide tube 122.

[0124]It is evident that both the swirl plates 128 of the swirl device 126, and also the swirl plates 146 of the swirl device 136, at least partially receive the injection device 130 or the injection device 142 at their respective downstream edges.

[0125]The swirl plates 128 and the swirl plates 146 may differ in size, and also have a different angle of inclination relative to the main flow direction 104, whereby the through-flowing oxidizer part is swirled to a differing extent.

[0126]The baffle plate 144 is connected to the injection device 134 via webs 148 and thereby fixed in position.

[0127]The baffle plate 144 has circular baffle openings 150 and slot-like baffle openings 152 which are arranged alternately in the circumferential direction.

[0128]The different geometries of the baffle openings 150, 152 create different zones on the baffle plate 144 which preferably stabilize one another.

[0129]Fuel from two injection openings 154 of the injection device 142 is injected through each of the slot-like baffle openings 152, whereas fuel from only one injection opening is injected through each of the circular baffle openings 150.

[0130]Because of the different opening shapes of the baffle openings 150, 152 within a baffle plate 144, different types of combustion can take place at the same time. Whereas a richer combustion occurs at the circular baffle openings 150 with an assigned injection opening 154, a leaner combustion optimally prevails at the slot-like baffle openings 152, and is again stabilized via the richer combustion.

[0131]The respective two injection openings 154, which supply fuel to the combustion chamber through a slot-like baffle opening 152, are preferably radially offset to the longitudinal center axis of the slot-like baffle opening 152, relative to the central longitudinal axis 102.

[0132]This can have the advantage that the burner flame or combustion in the radially outer region of the baffle plate 144 is stabilized. This may also be partly because a larger stream of oxidizer is produced through the radially offset arrangement of slot-like baffle opening 152 and the two injection openings 154 on the radially inner long side of the slot-like baffle opening, i.e. hotter flow paths occur on the radially outer long sides of the slot-like baffle openings 152, while the colder flow paths preferably form radially on the inside.

[0133]In other words, it is particularly advantageous if, relative to the circumferential direction of the baffle plate 144, the center point of the corresponding baffle openings 150, 152 or their central axis is arranged radially further inward than the center point of the assigned injection opening or openings 154, because this leads to a stable flame at the outer edge of the baffle plate 144.

[0134]The same or different fuel may be injected or supplied through the injection devices 130, 134, 142.

[0135]FIGS. 8 and 9 show a schematic, perspective illustration and a schematic, perspective, longitudinal sectional illustration of a third embodiment of a jet burner apparatus 100 according to examples disclosed herein.

[0136]In comparison with the second embodiment in FIG. 4, the jet burner apparatus 100 in FIGS. 8 and 9 has a bypass injection device 156 in the form of a ring tube, which is arranged downstream of the bypass flow channel 114.

[0137]Furthermore, the casing tube 112 is surrounded by a further casing tube 158, forming a further bypass flow channel 160 through which a part of the oxidizer can flow.

[0138]Also, a further injection device 162 in the form of a ring tube is arranged inside the flow channel 124 and arranged between the injection device 130 and the guide tube 122.

[0139]In addition, the jet burner apparatus in FIGS. 8 and 9 has a plurality of injection nozzles 164, via which in addition fuel can be supplied at defined points of the jet burner apparatus in order to influence the combustion.

[0140]FIG. 10 shows a schematic, longitudinal sectional illustration of a part of a combustion chamber device 200 according to examples disclosed herein with an inserted jet burner apparatus 100.

[0141]The jet burner apparatus 100 is inserted in the combustion chamber device 200 and attached outside the combustion chamber device 200, wherein between the outer periphery of the jet burner apparatus 100 and the combustion chamber device 200, a ring gap 204 is formed through which a part of the oxidizer can flow. This ring gap 204 may be formed asymmetrically as a result of production tolerances or also due to thermal deformations. The provision of a casing tube 112 nonetheless ensures that a symmetrical flow from the flame tube 106 to the opening of the combustion chamber device 200 prevails.

[0142]FIGS. 11 and 12 show a second embodiment of a burner stage 132 which differs from the first embodiment in that the burner stage has a first baffle plate 166 arranged downstream of the inner injection device 142 in the form of the ring tube (designated below as the first injection device 142), and a second baffle plate 168 arranged downstream of the outer injection device 130 in the form of a ring tube (designated below as the second injection device 130).

[0143]Also, the burner stage 132 in FIGS. 11 and 12 has no central injection device 134 with injection openings 138. In contrast, an inner circular disc 169 is arranged centrally.

[0144]The first baffle plate 166 is divided into four equal segments 170, which are arranged spaced apart from one another relative to the circumferential direction of the first baffle plate 166.

[0145]The second baffle plate 168 is divided into five equal segments 172, which are arranged spaced apart from one another relative to the circumferential direction of the second baffle plate 168.

[0146]The segments 170 and 172 are separated from one other, preferably in the region of the second slot-like baffle opening 152.

[0147]It is also conceivable that the first baffle plate 166 is divided into more than four segments 170 or fewer than four segments 170, wherein the segments 170 of the first baffle plate 166 may be the same or different from one another. The same applies accordingly to the second baffle plate 168, which may also be divided into more or fewer than five segments 172, wherein these segments 172 may also be the same or different.

[0148]Because of the decoupled arrangement of the segments 170 and 172, as a whole less thermal expansion occurs. Also, in the production of the comparatively smaller segments 170, 172, less waste material occurs than in production of a cohesive first or second baffle plate 166, 168.

[0149]In addition, more connections 174 are required for attaching the segments 172, 174, whereby the fixing of the first and second baffle plates 166, 168 is improved and a defect or failure of a single connection 174 can be better compensated.

[0150]FIGS. 11 and 12 also show a particularly preferred embodiment of the connections 174.

[0151]In this particularly preferred embodiment of the connections 174, the connections 174 each comprise a screw 176, a nut 178 and a spacer 180 formed as a sleeve.

[0152]Preferably, each segment 170, 172 is attached to the first or second injection device 142, 130 respectively by two or more pairs of connections 174, wherein the connections 174 of the individual pairs are arranged on mutually opposite sides of the injection device 142, 130.

[0153]The nuts 178 are attached, preferably welded, to the side of the first and second injection devices 142, 130.

[0154]The desired distance between injection device and baffle plate can be set via the spacers 180, which are preferably interchangeable or exchangeable. Thus the oxidizer flow around the injection devices 142, 130 and through the baffle plates 166, 168 can be set.

[0155]Because of the spacing of the baffle plates 166, 168 and the lateral attachment of the nuts 178, weld seams or weld points on the downstream-side hot surface of the injection devices 142, 130 are avoided.

[0156]The screws 176 are screwed into the associated nuts 178 for attachment of the respective segments 170, 172, wherein the bore provided in the baffle plates 166, 168 for the respective connection 174 may additionally have a thread corresponding to the screw 176.

[0157]FIG. 13 shows a third embodiment of a burner stage 132 which differs from the second embodiment in FIGS. 11 and 12 by the type and manner of attachment of the segments 170, 172 to the respective injection device 142, 130.

[0158]In the third embodiment, the connections 174 are also arranged in pairs on mutually opposite sides of the first and second injection devices 142, 130.

[0159]In the third embodiment, the connections 174 also comprise a screw 176, a nut 178 and a sleeve-like spacer 180.

[0160]Each screw 176 of a connection pair extends through one of the segments 170, 172 into an assigned U-shaped bracket 182, which is guided against the first or second injection device 142, 130 on the upstream side and at least partially surrounds this. The two screws 176 are secured to the assigned U-shaped bracket 182 by means of the respective nuts 178. The two associated spacers 180 of the connection pair are arranged between the ends of the U-shaped bracket 182 and the corresponding segment, whereby the distance between this segment and the first or second injection device 142, 130 is set.

[0161]The brackets 182 may be fixed to the respective injection device 142, 130, for example by one or more weld points.

[0162]Alternatively, the brackets 182 are at least partially displaceable in the circumferential direction of the first or second injection device 142, 130, whereby a further degree of freedom for reducing thermal stress is provided. The movability of non-fixed brackets 182 in the circumferential direction may be limited by stops (not shown) which are attached to the first and second injection devices 142, 130.

[0163]The brackets 182 are preferably made of a metal.

[0164]The friction resistance between a bracket 182 and the first or second injection device 142, 130 may be adjusted via the width of non-fixed brackets 182. Thus the risk of tilting of the associated, indirectly attached segment 170, 172 about the circumferential axis of the first or second injection device 142, 130 is reduced.

[0165]The bores 152 for the connections 174 in the first and second baffle plates 166, 168, and also the sleeve-like spacers 180, may be provided with an internal thread corresponding to the screws 176.

[0166]FIG. 14 shows a fourth embodiment of a burner stage 132 which differs from the third embodiment in FIG. 13 in that connection pairs of two screws 176, two nuts 178 and two spacers 180 secure a region of one of the segments 170, 172 on the first or second injection device 142, 130, not by means of a bracket 182 but by means of a transverse web 184, which rests on the upstream surface of the injection device opposite the segment. The corresponding segment 170, 172, the two spacers 180 of a connection pair and the associated transverse web 184 thereby define a rectangle on the inside.

[0167]It is conceivable that the spacers 180 and/or the transverse webs 184 are attached to the respective first or second injection device 142, 130.

[0168]Furthermore, the friction resistance between transverse web and the first or second injection device 142, 130 can be set via the size of the contact area of the transverse web.

[0169]Alternatively or additionally, the segments 170, 172 may be secured to the first or second injection device 142, 130 by multiple U-shaped plates (not shown). These U-shaped plates, like the brackets 182 from FIG. 13, are guided against the first or second injection device 142, 130 on the upstream side and attached thereto, for example by a weld connection. The two legs of the U-shaped plates, which grip around the respective injection device 142, 130 on mutually opposite sides, are divided into a downstream-side portion and an upstream-side portion. The respective downstream-side portion of a leg is rotated about the leg axis, e.g. by 90°, in order to set the distance of the respective segment 170, 172 from the first or second injection device 142, 130. The rotated downstream-side portions of the legs are guided through corresponding openings in the respective segment 170, 172 and bent over on the downstream side of the segment 170, 172 so as to secure the set distance.

[0170]FIGS. 15 and 16 show a fifth embodiment of a burner stage 132 which has measures for noise reduction.

[0171]Firstly, the slot-like baffle openings 152 of the segments 170, 172 of the first and second baffle plate 166, 168 are attached to the first or second injection device 142, 130 on both sides, i.e. at a slot inner web 185 and at the slot outer web 186, by one or two pairs of connections 174, which prevents flow-induced oscillations at the slot inner web 185 and the slot outer web 186 or at least reduces such oscillations.

[0172]Secondly, the slot-like baffle openings 152 of the first or second baffle plate 166, 168 have one or more constrictions.

[0173]The constrictions are produced by pairs of opposite bulges 187 of the respective baffle plate 166, 168 which may be formed with constant or non-constant inner or outer contour, such as e.g. tooth-like or similar, wherein preferably the number of constrictions and hence also the number of bulges 187 of adjacent slot-like baffle openings 152 differs along the circumferential direction of the first and second baffle plates 166, 168.

[0174]The term “bulge” in this description and in the appended claims means a region of the respective baffle plate, disc or similar which protrudes or projects. Such a protruding or projecting region partially constricts the baffle opening concerned, or partially reduces the distance between opposite elements of the burner apparatus.

[0175]In FIGS. 15 and 16, accordingly the slot-like baffle openings 152, which are formed by two adjacent segments 170, 172, have two pairs of bulges 187, while the remaining slot-like baffle openings 152 each have only one pair of bulges 187.

[0176]The bulges 187 may lie directly opposite one another or may also be arranged offset to one another.

[0177]Furthermore, further bulge elements (not shown) may protrude into the annular gap 188 between the first and second baffle plates 166, 168.

[0178]Thirdly, preferably also the inner circular disc 169 is provided with bulges 187 along its outer circumference, so that constricted portions are formed in the annular gap 190 between the inner circular disc 169 of the first baffle plate 166.

[0179]Further measures for noise reduction are conceivable which cause the formation of symmetrical and/or asymmetrical constrictions in the region of the annular gaps 188, 190 and along the slot-like baffle openings 152.

[0180]FIG. 17 shows a sixth embodiment of a burner stage 132 with a measure for reducing vibration-induced noise at the gaps between two adjacent segments 170 of the first baffle plate 166 or two adjacent segments 172 of the second baffle plate 168.

[0181]At a slot-like baffle opening 152 formed by two adjacent segments 170 or two adjacent segments 172, the slot inner web 185 and the slot outer web 186 are each divided by a gap. The resulting free ends or sub-pieces of the webs 185, 186 vibrate due to the oxidizer flow and thereby generate noise.

[0182]To reduce this noise, an upstream bent extension 192, which at least partly overlaps or protrudes beyond the other sub-piece 196 of the slot outer web 186, is provided on a sub-piece 194 of the slot outer web 186. The extension 192 is preferably a portion of the sub-piece 194.

[0183]As an alternative, FIG. 18 shows—in a seventh embodiment of a burner stage 132-a plate-like element 198 which is attached to the upstream-side surface of the two sub-pieces 194, 196 of the split slot outer web 186. Preferably, the plate-like element 198 is welded to the two sub-pieces 194, 196. Such a closure of the gap also suppresses a vibration of the two sub-pieces 194, 196 and consequently also the local generation of noise.

[0184]Additionally or alternatively, it is conceivable that the gaps between the sub-pieces of the slot inner web 185 and slot outer web 186 of a slot-like baffle opening 152 are covered on the downstream-side surface by a common plate-like transverse element (not shown). The plate-like transverse element is accordingly oriented at least approximately perpendicularly to the circumferential direction of the respective baffle plate 166, 168.

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