TWI681049B - Coke oven device having centric recirculation for the production of coke, and method for operating the coke oven device, and control installation, and use thereof - Google Patents

Abstract

The invention relates to a coke oven device (10) for the production of coke by coking coal at a minimized emission of nitrous oxide by measures internal to the coke oven device, having a multiplicity of twin heating flues (13) each having a fired heating duct (11) and an exhaust-gas-conducting heating duct (12), said heating ducts in each case being partitioned from one another in pairs by a bulkhead (14) and from a respective oven chamber (10.2) by two stretcher-bond walls (15), wherein the heating ducts in pairs for internal exhaust-gas recirculation on an outer circular flow path (19, 19.1) are fluidically coupled to one another by means of an upper coupling passage (14.2), wherein in the lower region on the base (5.4) of the respective twin heating flue at least one inlet from the group of in each case coke oven gas inlet (18), combustion air inlet (16), mixed-gas inlet (17) is provided; wherein at least one exhaust-gas recirculation passage (14.2) is disposed so as to be more centric than at least one of the inlets and defines a more centric flow path (GP4). This enables reduced emissions of nitrous oxide. The invention furthermore relates to a method for operating the coke oven device.

Description

Coke oven device including central recycling for coke production, operation method of coke oven device, and control device and use thereof

The invention relates to a device and method for producing coke, as well as a control device and corresponding uses. More particularly, the present invention relates to an apparatus and method according to the preamble of the corresponding independent request item.

The demand for coke ovens in the world is still high, and it is estimated that it will continue to remain high in the future, for example, as described in the following publication: "K. Wessiepe et al.: Optimization of Combustion and Reduction of NOx-Formation at Coke Chambers ....COKE MAKING INTERNATIONAL; 9,2; 42-53; VERLAG STAHLEISEN MBH; 1997". Since the individual operating time or service life of the coke oven may be quite long, the planning and construction of the coke oven must also be carried out with a long-term perspective, so it is important to know which environment can be implemented in the coke oven in the next few years Technical improvements. Despite stricter environmental standards, it is still There are hundreds of coke ovens newly built and put into production. However, at the same time, most politicians clearly realize that energy production from coke ovens is not particularly environmentally friendly. Therefore, for the construction of new coke ovens, or for the operation of existing coke ovens, especially in relation to nitrogen oxides (NOx), increasingly strict emission requirements are set. In this context, many parties are working to improve the coking efficiency or its environmental friendliness, for example, you can browse the following publications and professional articles cited therein: "AJNowak et al.: CFD model of coupled thermal processes within coke oven battery.. .. Computer Assisted Mechanics and Engineering Sciences, 17: 161-172, 2010". The subject of this publication is the simulation of conventional optimization measures.

The following refers to the emission limits allowed today or those allowed by existing plants: 500 mg/Nm ³ , which is equivalent to about 250 ppm at 5% oxygen O ₂ . The following references can be used as future limits: about 350 mg/Nm ³ in Europe (about 170 ppm at 5% oxygen O ₂ ), or soon even about 200 mg/Nm ³ in Asia, especially in Japan, South Korea, Taiwan and China. In other words, NOx emissions should be reduced by half or more as soon as possible. However, some environmental protection departments, especially those in Asia, now require the upper limit to be only in the range of about 100 mg/Nm ³ , which is equivalent to 1/5. In view of the stricter requirements, especially for diesel vehicles, it is expected that the limit values allowed in Europe in a short time will also be lower than 350 mg/Nm ³ .

Specifically, nitrogen oxides are respectively released through flue gas generated by the combustion of coke oven gas, or formed during combustion, especially at a nozzle brick temperature of about 1250°C (exhaust gas guide tube groove on the substrate) Above) (so-called thermal formation of NOx). As the temperature increases, the thermal formation of NOx is further promoted or initiated in an exponential manner, respectively, so that the emission of nitrogen oxides largely depends on the thermal conditions in the coke oven. As we all know, by setting a specific temperature state, in particular, it can affect the emission of NOx in the vertical flue gas guide flue of the coke oven. The rule of thumb for this is temperature The higher the NOx emission, the stronger. Therefore, furnace operators are limited by environmental technical parameters and are dedicated to or forced to keep the temperature as low as possible, especially not allowing the temperature rise to exceed the limit of 1250°C. However, furnace operators are also concerned about the efficient coking process, and expect the operating mode when the nozzle brick temperature is up to 1325°C; the coking efficiency increases with increasing temperature, the higher the operating temperature, the more the furnace set can be designed at the same output compact. For example: in the case of increased operating temperature, only about 95 to 98 furnaces need to be built instead of 100 furnaces, which is equivalent to equipment savings of 2% to 5% (lower investment and factory cost reduction of 5%, involving for example 100 million to 800 million euros).

Therefore, attempts to reduce the NOx emissions by implementing reduced temperature levels during coking or by avoiding temperature peaks in the heating flue, especially by adjusting the operating mode, are very undesirable, as this will result in loss of output and make the coke Production is even more uneconomical. Therefore, it is quite undesirable or unrealizable for the operator of the coke oven to operate in a non-optimal operating state. It is therefore acceptable that NOx emissions are kept at an unfavorably high level. However, furnace operators do know that if the input of thermal energy can be kept constant with a relatively moderate temperature drop, this will have a positive effect on NOx emissions while providing a considerable output.

In the case of various types of coke ovens, the furnace operator must observe these parameters. In particular, the distinction is made according to the direction of coke injection between the vertical chamber furnace and the horizontal chamber furnace. In the case of a horizontal chamber furnace, coking is carried out in batches. After coking, the coke is injected horizontally (batch operation). In contrast, the coal in the vertical chamber furnace is continuously fed and discharged in the vertical direction (continuous operation). The invention particularly relates to a horizontal chamber furnace.

The furnace chamber usually has a height of 4 to 8.5 m, wherein the height of the furnace chamber or the heating tube groove is also predetermined by the operation mode, respectively. The height affects the pressure difference in the heating tube groove. If a larger pressure difference is required, a larger height must be selected. It can be assumed that the temperature must be as constant as possible throughout the height This is because only in this way can an effective operating state be set without excessively increasing NOx emissions. As far as possible, the temperature gradient should be significantly less than 40K or 40°C respectively, especially in the temperature range of 1000 to 1100°C in the furnace chamber. A temperature maximum that is significantly higher than the average temperature will promote the thermal formation of NOx. Therefore, when the temperature remains uniform, just below the temperature at which heat formation of NOx occurs, the coke oven can be operated with the best compromise between high output and low NOx emissions.

The simulation of the operating state is a practical tool that can better judge the effects of various optimization measures. However, coke ovens are relatively complex equipment and have corresponding complexity in terms of simulation. For example, a new structure with a new gas path may mean that each calculation requires several weeks of calculation workload, so that in the case of simulation, it may also produce several years of workload (for example, if more than 100 changes are required) . Therefore, for cost reasons, not only must the new measures of technical scale be tested with limited possibilities, but even simple structural measures must be checked in many ways before they can be studied in more detail through simulations Described measures. This leads to structural changes in existing furnace designs that can only be carried out in a very gentle and conservative manner.

The measures to date have been tested directly on the coke oven or its structural design, respectively, and also work in the case of an operating mode that optimizes the output, usually from the inside of the heated flue from down to up Flue gas recirculation, which is driven by the pressure difference or the difference in temperature and density (internal circuit path of partial volume flow of flue gas, so-called circulating flow), and/or stepping of combustion air , So that the combustion gases are introduced into the heating flue from the partitions or adhesive walls at different heights respectively. The grading here is carried out especially considering the following standards: the highest gas collection chamber temperature in the adjacent furnace chamber above the coal block must be lower than 820°C; the surface temperature of the top plate must be as low as or equal to 60°C; the temperature difference inside the furnace chamber wall< =40K, especially between 500mm above the bottom of the furnace/combustion furnace and 500mm below the upper edge of the furnace chamber.

The circulating flow path here (partially at the end of the heating tube groove, or in a completely circular manner) is usually implemented in a so-called dual heating flue. Heating flues or heating tube slots arranged in pairs adjacent to each other, in particular, vertically aligned heating flues or heating tube slots are coupled to each other, wherein the gas from the burning heating tube slots returns to the non-combusting heating tube slots In the middle, the gas returns only at the up/down reversal point, or returns at both the top and bottom. In the case of a horizontal chamber furnace, about 24 to 40 heating tube slots can be provided in the spray direction, so there are about 12 to 20 double pairs. Alternatively, the circulating flow implemented here can be configured in an autonomous manner by means of the pressure difference, so that no additional active fluid adjustment or support is required.

In the 1920s, optimization of circulating flow routes has begun, especially for industrial-scale uniform heat distribution. Since the 1970s, the effects of circulating flow paths on NOx emissions have also been studied in more detail.

The configuration of a coke oven having a circulating flow path used in most cases in the past can be described as follows. The heating gas is directed upwards to rise in the pair of heating tube grooves (dual heating flues) in the direction of flow, and therefore in the burning heating tube groove, and here in particular in multiple stages of combustion, said The heating gas is followed by the flue gas being guided back to the base through the parallel exhaust gas guide tube groove and sucked at the latter, where part of the volumetric flow of inert (consumed) exhaust gas is led back to the upwardly directed combustion Heating tube groove. In this case, the heating tube grooves at the upper and lower ends can in each case be coupled to one another through exhaust gas recirculation openings or channels, in particular in the region of the furnace chamber base, the position of which is at least approximately the same as the height level of the inlet. Therefore, the average nozzle brick temperature in the heating flue can be controlled and maintained at a medium level (for example, at a nozzle brick temperature of 1240 to 1300°C), especially by reducing the local flame temperature (higher than in the case of rich gas heating) 2000 ℃, lower than 2000 ℃ in the case of mixed gas heating), can reduce NOx emissions. The following cloth of the lower channel can be mentioned Set (height position), for example: between 0mm (so directly at the level of the burner plane) to 300mm above the burner plane. The cross-sectional area here is usually predetermined by a layer approximately 120 mm high. The lower channel on the base can be closed by rollers as needed, and the roller can roll in front of the channel on the plane of the furnace. The channel is advantageously realized through the gap in the wall layer (gap or missing brick).

The heating tube grooves are arranged in pairs and aligned in the vertical direction, or are dual heating flues, therefore, the temperature curve can be affected with a relatively low force, especially in the case of specific adaptation of the flue gas circulation path under. Here, there are always two types of heating flue-heating tube slots: upwardly pouring and burning heating tube slots; downwardly pouring exhaust gas leads to the heating tube slots. In the upper region, the pair of heating tube grooves are connected to each other through a cross section of the free opening, thereby forming a channel through which the heating tube grooves are fluidly connected to each other. For example, in the case of rich gas heating, the partial volume flow of flue gas directed back to the burning heating tube slot is typically 30% to 45% of the entire flue gas volume generated in the upwardly infused heating tube slot. An example of such an arrangement with circulating heating dual-heat flues is the so-called Combiflame heating system, which has been established since the late 1980s. A combination of air grading and circulating flow paths is performed therein. Prior to this, until the mid-1980s, air staging (Otto system) or circulation flow path (Koppers system) was performed.

As far as the single channel mentioned in this specification is concerned, this can also refer to a pair of channels, which are arranged in pairs at the same height position.

As mentioned previously, combustion can also be carried out in stages, where gas or air is guided into the corresponding heating flue through at least one stepped air tube slot at least at a height above the combustion furnace plane (base), or In this way, the corresponding exhaust gas is discharged. Staged combustion can be combined with circulating flow paths.

If special attention is paid to the measures directed at the coke oven, the heat optimization measures are especially through the optimization of the type of media path, the optimization of the structural design of the coke oven, and in particular the optimization of the respective walls of the furnace chamber and the corresponding The structure design of the heating flue (stretcher-bond wall, partition board) is realized, and the stability of the coke oven has a considerable correlation with the structural design. Small measures of structural design can have a great influence on the temperature balance and coking process. However, in specific examples, each measure has very unfavorable side effects that should be avoided, for example, in terms of the statics of the heating wall, the flow resistance or the final flow velocity and temperature distribution. It can therefore be expected that the structural modifications described in more detail below can only be carried out within strict tolerances. The task particularly faced by those with ordinary knowledge in the technical field to which the present invention pertains is to eliminate any risk of weakening the heating wall composite material through new measures. In fact, depending on the operating state, high lateral forces can act on each wall. For example, after approximately 75% of the carbonization time, in particular, a high lateral internal pressure (propulsion pressure of coal batch) is generated on the staggered brick-brick wall approximately 1 m high above the burner plane. The pressure may even cause the joints to expand, and thereby produce undesirable bypass flows between the various heating flues and the (adjacent) furnace chamber (with the migration of coke oven gas and the formation of CO associated therewith). As a result, the balance of the gas mixture is destroyed. In particular, only an insufficient amount of air is available for the additional amount of gas to be burned in the heating tube groove. Furthermore, in the case of adjacent furnace chambers, different filling times, for example a deviation of 12 hours in each case, also lead to different lateral forces in the corresponding walls. Therefore, in the case of measures to reduce emissions, the stability of the furnace also has a high priority. High stability is usually achieved through the tongue-and-groove arrangement of bricks. Considering the tightness, this structural mode is also preferable in order to avoid detours and premature combustion.

In the case of a group with multiple furnace chambers, such as 40 or 60 furnace chambers, the furnace chambers associated with the gas heat transfer tube slots are defined by staggered brick walls, especially in the corresponding tube slots phase On the narrower end side, in particular, it is defined by two mutually staggered brick-walls extending along the entire corresponding furnace chamber. Here, the individual heating tube slots are separated from each other by a so-called adhesive wall (separator), which is between the staggered brick walls and in particular the two staggered brick walls The walls extend vertically, especially on the relatively wide side of the furnace chamber. Three adhesive walls separate the two tube grooves from each other, or separate one double-heated flue from the other double-heated flue. Therefore, the corresponding heating pipe groove is delimited by two staggered brick-walled wall sections and two adhesive walls. In the spray direction (depth y), the corresponding heating tube groove is about 450 to 550 mm long or deep (center to center). The wall thickness of the staggered brickwork here is in the range of 80 to 120 mm, for example. The thickness of the bonding wall here is in the range of, for example, 120 to 150 mm.

The term "glued wall" has been established in commonly used languages. In this specification, the term is used synonymously with the term "separator", especially to clarify that staggered brick-walls and bonded walls/separators can be produced in the same structural mode, especially through in each case Produced from bricks placed next to each other on their narrow sides. The "staggered brick wall" of the horizontal chamber furnace can also be described as a longitudinal wall arranged longitudinally along the spray direction, and the "glued wall" can also be described as a lateral (separation) wall, which is arranged transverse to the spray direction.

The combustion air opening and the mixed gas opening are provided on the lower side of the corresponding heating tube, and the functions of the combustion air opening and the mixed gas opening can be selected or set separately according to the type of heating (mixed gas or coke oven gas heating). The gas opening of the coke oven leads to the heating tube groove on the lower side. In the case of a circulation flow path, in each case, a pair of heating tube grooves are connected to each other through an exhaust gas recirculation opening provided on the lower side of the furnace chamber, thus forming a double heating flue having a circulation flow path. The volumetric flow through the exhaust gas recirculation opening can be selectively adjusted, in particular the adjusting roller which is arranged on the base in the plane of the combustion furnace, and it can be repositioned. Provide a stepped gas tube groove in the bonding wall The stage gas tube slot introduces combustion air (staged gas) into the furnace chamber (air stage or bonded wall opening, respectively) at one or more height positions. The usual proportion of volume flow introduced into the furnace chamber through the base-side combustion air inlet can be expressed as 30%, and the usual proportion of volume flow through the substrate-side mixed gas inlet can be expressed as 30%, through at least one staged gas inlet (bonded wall opening ) The general proportion of volume flow can be expressed as 40%. The ratio can also be set in a similar manner according to the output requirements in order to exhaust gas from the furnace chamber.

A bypass flow in the form of a heating differential can be arranged above the exhaust gas reversal point (recirculation channel) in order to adjust the coking parameters. The bypass flow can be separated from the heating flue by a horizontal wall or a ceiling, respectively, and the channel can be covered by, for example, a sliding brick provided in the ceiling or arranged in cross section.

The above publication of K. Wessiepe specifically discusses measures for furnaces with dual heating flues (at least heating flues connected to each other through the upper channel), where it has also been discovered in the 1990s that the so-called circulating flow arrangement can provide as much as possible Advantages of low NOx concentration.

The patent documents DE 3443976 C2 and DE 3812558 C2 discuss the issues of optimal circulation flow rate and meaningful height position of the combustion air introduced in stages, in particular the example of using Koppers circulation flow furnace, which can be mentioned in an exemplary manner. It is also mentioned that returning the flue gas at a height position in the floor area of the heated flue enables the temperature to be reduced in the corresponding heated flue, thus having the effect of reducing NOx emissions.

In the first and uncensored publication number CN 107033926 A of August 2017, a device with dual heating flues is described, which has a step-by-step introduction of combustion air and has a circulating flow opening that is transverse Set on both sides of the staged air tube slot.

Experiments have been carried out with specific types of gas conducting parts or filling elements in order to be able to influence the heat distribution in the coke oven. For example, in patent document DE 3916728 C1, heating spaces (heating flues) are provided with devices in the form of permeable honeycomb elements or honeycomb grids or pebble beds, respectively, where certain types of flue gas paths are also considered to be partially advantageous. The target is to improve the flow conditions in the heating space, and it is also proposed to feed the combustion air at different heights.

Experiments have been conducted with specific coatings to efficiently remove or reflect thermal energy from the inner surface.

The above-mentioned measures directly on or in the coke oven or heating flue can be described here as the main measures, respectively. It must be noted that in the case of all the above measures, the furnace described here is usually operated by spontaneous combustion (especially above 800°C), so that the corresponding measures for cooling or lowering the gas temperature can only be under tight parameters Or only in a tight temperature range, especially to avoid burning out.

In addition, secondary measures have been tested that can be carried out in factory components arranged downstream of the coke oven, for example, the use of selected catalysts in the chimney (SCR or DeNOx), or flue gas that has been evacuated and returned to the coke oven from outside the chimney in. Independent of the question of the effectiveness of the downstream measures, the latter has in many cases been frustrated by extremely high costs (up to 50% of the total coke oven investment) or additional maintenance work. These measures are indeed effective, but in many cases the cost is too high.

In addition, the patent application DE 4006217 A1 can be mentioned, which describes a combination of various measures, including the measure of the generator in the central part of the furnace, and the two measures of external flue gas circulation, the goal is a uniform heating state and low NOx emissions, even This is also the case in the blast furnace chamber.

In particular, chemical and reactive measures are also considered, such as introducing CH ₄ gas or increasing the moisture by injecting water. However, it is impossible to inject water or steam at any position of the chamber, and it is particularly possible to be located at a neutral height position only in a neutral manner, and have an adverse effect on the (silicate) material used. The increase in the regenerative preheating temperature of the gas and air is a measure, which at the same time is considered exhausted and uneconomical.

However, at present it seems that it is still impossible to imagine that the above-mentioned internal main measures are used to meet the above requirements individually or progressively in each case. Therefore, it seems impossible to reduce NOx emissions by 2 to 5 times, at least not with reasonable efforts, and therefore not an economic way.

Despite the above-mentioned problems, the object of the present invention is to optimize the coke oven by measures directly on the coke oven or in its structural design, in particular by measures against the established heating system, which has at least A recirculation opening heating channel, especially with a circulating flow channel, is especially used to obtain the option of being able to operate the coke oven in the case of an output optimized operation mode, even without any downstream equipment parts at all. Here, a potentially large improvement potential can be expected, which also has great advantages for furnace operators, and therefore also a good opportunity for the technical concept to succeed in the market.

An object of the present invention is to provide a coke oven device and a method of operating the coke oven device, through which the NOx emissions can be kept low even when operating at full load, or in existing or new devices In this case, NOx emissions can also be minimized. The coke oven device can advantageously achieve low levels of NOx emissions, preferably without any downstream equipment components. A particular object is to provide a coke oven device and a method of operating the coke oven device, through which the NOx emissions can be reduced by measures that heat the interior of the flue.

According to the invention, this object is achieved by a coke oven device for the production of coke by coking coal or coal mixtures, wherein the coke oven device is designated to pass through the main measures inside the coke oven device through the coke oven inherent gas or gas flow Internal thermal equilibrium energy or temperature to minimize NOx emissions It has a plurality of dual heating flues, each heating flue has a heating tube slot burned by gas or combustion air (and therefore is poured upwards), and an exhaust gas directed downward to guide the heating tube slot, said heating The tube slots are in each case defined in pairs with each other by a partition, and are separated from the corresponding furnace chamber by two mutually staggered brick-brick walls, which are used on the external circulation flow path In each case, the pair of heating tube grooves for internal exhaust gas recirculation are fluidly connected to each other at the upper and lower ends by means of an upper coupling channel and optionally also by a lower coupling channel, wherein in the corresponding double heating flue In the lower region of the base, at least one inlet selected from the group of coke oven gas inlet, combustion air inlet, mixed gas inlet is provided in each case; wherein at least one exhaust gas is provided corresponding to the width (x) of the heating tube groove The recirculation channel, therefore between the staggered brickwork walls, is more central than at least one inlet (closer to the median longitudinal axis of the heating tube slot), and defines a central or more central flow path, The flow of at least one gas entering through the inlet circulates around the flow path. The exhaust gas recirculation flow path is set to be more central than the corresponding flow path or inflow path of the incoming gas, respectively. At least the recirculation at the top is more central than the inflow through the inlet. According to this measure of the relative position of the recirculation, the heat distribution in the heating tube trough can be optimized, in particular homogenization, and in particular mirror symmetry or synchronization in the heating tube trough which is poured upwards and downwards. Here, in particular, corresponding coke oven gas inlets in the form of fluids and thermal energy may be provided corresponding to at least one channel or inlet. Effect: Through the internal gas flow, through the internal fluid measure, affect the heat distribution and gas mixing, especially in the base area. No external measures are required. The internal measures here can be purely passive measures, especially purely structural measures. Thanks to structural measures, the flow conditions can be set independently. In addition, this also facilitates the operation of the device. The control/regulation of the furnace can be performed in a manner comparable to hitherto.

In this case, the y position of the corresponding inlet between the opposing partitions is preferably at least almost central in each case. It has been proved that the y position should be attached to the x position selection, and can be The degree is selected independently of the x position, especially according to the corresponding structural advantages, or depending on the required inflow angle.

In this case, the corresponding upper channel is arranged below where the differential heater is optionally present, in particular in the partition extending in the x-z plane. In contrast, the opening of the differential heater is provided in a partition extending in the x-y plane. It is not necessary to provide a lower channel.

Due to the ideal center configuration of the channel/plural channel, when viewed in the xy plane, an internal circulating flow with surrounding flow around the latter can be provided on the additional internal circulating flow path with the surrounding flow around the latter The internal circulation flow path has a (more eccentric) surrounding flow through the outside through at least one incoming gas or through the external circulation flow on the external circulation flow path.

Without providing recirculation through one or more lower channels, the terms "circulating flow" or "circulating flow path" may also refer to a flow that does not close around the entire circumference, but only bypasses, for example, a circular 180° Or 270°.

These measures are especially able to achieve combustion inertness and mixing delay intermediate layers, as well as cooling in the base area, and can be carried out directly on the coke oven or on its structural design, especially on the heating system, without any downstream equipment part. In particular, the maximum temperature between the burner plane and the lowermost channel can also be reduced. In particular, in the case where the average coal batch temperature is in the range of 1000°C, the maximum temperature may be in the range of 1050°C, and in any case below 1100°C, it can be achieved that the entire height of the heating tube tank remains significantly below The purpose of the 50K temperature difference. Through these measures, the potential to reduce the NOx in the range of 70% to 80% corresponding to the current level of 350 to 500 ppm NOx (under 5% O ₂ ) can be achieved. In particular, a level of NOx (under 5% O ₂ ) below 100 ppm can be implemented. In addition, at the same output, the amount of refractory can be reduced by as much as 5%. Therefore, the technical solution has also attracted considerable interest in economic terms. Furnace operators can operate the furnace at high output or high nozzle brick temperature with relatively low NOx emissions, respectively.

The measures described in this specification may relate in particular to coke ovens with chamber operating time between the filling procedure and the injection procedure between 15 and 28 hours, or coke ovens with heating flue temperature or nozzle brick temperature, which respectively In the range of about 1200 to 1350°C.

To date, it has been common to arrange each recirculation opening close to the staggered brickwork wall. It is also common to center the entrance on the base. In the study of optimizing NOx emissions in the context of the present invention, it has been demonstrated that the high combustion temperature causes the coke oven gas together with the combustion air to form a very hot gas mixture already located in the lower region of the furnace chamber. Due to the positioning of the inlet according to the invention, temperature peaks can be avoided. This arrangement can also be equipped with a differential heater (bypass flow) above the exhaust gas reversal point (channel). Alternatively, equipment components located downstream can further reduce NOx emissions to the extent that they can still be achieved in an economical manner.

The heating tube groove here can also be described as a heating shaft. The corresponding heating tube grooves downwards are defined by a base, which is also called a burner plane, even when no burner is used in it (especially spontaneous combustion at a temperature higher than 800°C).

The heating tube slot here should be understood as the term for the very specific vertical heating flue of the two vertical heating flues used for the dual heating flue. The heating flue here should be understood as any one of the two vertically heating flues of the dual heating flue. In the corresponding operating state of the coke oven, the heating tube groove is ignited in an upward manner or poured downward. In each context explained, the direction of gas flow is irrelevant, so the term heating flue is used here rather than the term heating tube slot. Therefore, the term heating flue may refer to a heating tube slot that is poured upward or a heating tube slot that is poured downward.

The coal mixture herein should be understood as a mixture mainly composed of different coal types, wherein the mixture may also contain, for example, at least one additive from the following group: petroleum coke, oil, asphalt varieties (for example, used tires, coal dust And coke powder), binders or coking agents (eg, molasses, oil residues, cellulose-based additives, sulfite or sulfate compounds or lye), where the mixture may also contain biomass.

In the absence of other references, the details of the spacing of the ducts, inlets, channels or nozzles in each case refer to the corresponding median longitudinal axis, and the details of the spacing of masonry or walls refer to the inner surface in each case .

It has been shown that the air or gas path according to the invention can be implemented not only in the case of dual heating flues, but also in the case of so-called four flue furnaces or alternative arrangements, where the concept of fluidly coupled heating flues It is applied and in particular increases exponentially if the heating flues are coupled in pairs.

The introduced combustion air or heating gas is used to generate the required process heat at the base area or at a specific stage height position.

It has been shown that the arrangement according to the invention can also eliminate multiple staged air inlets (especially if only a single gas stage is provided), especially if the furnace chamber height is below 8 m. Therefore, the change in the position of the lower base-side inlet according to the present invention can respectively reduce the structural force or complexity of the furnace at another position.

The width (wall thickness) of the corresponding separator is preferably 80 to 200 mm, and more preferably 120 to 150 mm. The width (wall thickness) of the corresponding staggered brick wall is preferably 80 to 120 mm. This provides sufficiently strong insulation and stability in each case.

Independent of the various optimization measures described, at least one combustion air inlet or staged air inlet for introducing combustion air from the stepped air tube slot extending in the partition into the heating tube slot may be provided at the partition At least one combustion stage height position in the plate.

Here, the lower region of the heating flue base may correspond to the plane of the combustion furnace, or to the height range of up to 2 to 3 layers of bricks in the masonry furnace (2 to 3 wall layers), corresponding in the range of about 120 mm At the height of the layer. The base area defined according to this specification can also extend, for example up to a height of 1200 mm. The base area is preferably defined as the area from the burner plane to the height above the burner plane from 100 to a maximum of 800 mm. Here, the high details in this description relate to the burner plane, and therefore to the lowest point of the corresponding heating tube groove. The lower channel is a channel that defines the circulation flow or the lower reversal point of the flow, especially below the upper channel. The corresponding lower channel does not have to be arranged in the base area.

According to an exemplary embodiment, with respect to the width (x) of the heating tube groove, all exhaust gas recirculation channels are arranged more centrally than at least one inlet, in particular more centrally than all inlets. This provides a clear separation of the way the gas flows (i.e. the centrally directed recirculated gas, and the eccentrically directed new incoming gas).

According to an exemplary embodiment, all exhaust gas recirculation channels are arranged more centrally than at least one inlet. This makes it particularly effective to separate from the staggered brickwork wall. According to an exemplary embodiment, at least one exhaust gas recirculation channel is arranged more centrally than all inlets. This allows the staggered brickwork walls to be separated from the recirculated exhaust gas by the blanket of incoming new gas. According to an exemplary embodiment, all exhaust gas recirculation channels are arranged more centrally than all inlets. This provides a particularly effective arrangement.

According to an exemplary embodiment, at least two inlets including a coke oven gas inlet are provided on both sides of the coupling channel/channel, and the circulating flow of the outflow channel/channel is provided on a more inward circulating flow path than through the corresponding The inflow path of the gas introduced at the inlet is closer to the central longitudinal axis of the heating tube groove in such a way as to be closer to the wall of the frame bond. As a result, excessive sudden mixing of coke oven gas and combustion air or mixed gas can be prevented.

According to an exemplary embodiment, at least two inlets are provided on both sides of the coupling channel, with corresponding exhaust gas recirculation channels between the inlets being arranged to include or define laterally through the inlets, and at least three or four The upward flow part of the flow runs at least across a certain height part (especially in the height range of 0 to 1000mm), closer to the staggered brick wall in such a way that it is at least almost parallel to each other or at least adjacent to each other , So that the delayed mixing in this height portion is formed on the flow path in the corresponding heating tube groove. More complete mixing is only performed above this height portion.

According to an exemplary embodiment, the corresponding coke oven gas inlet is disposed adjacent to the corresponding staggered brick-walled wall, and/or the corresponding combustion air inlet is disposed opposite the coke oven gas inlet to correspond to the corresponding Staggered brick walls are adjacent to each other. This arrangement as close as possible to the staggered brickwork walls enables central recirculation in the base area, which provides advantages for a uniform heat distribution. It has been proven in particular that the mixing of the individual airflows can be delayed accordingly, or it can be further repositioned to a higher height position.

According to an exemplary embodiment, the corresponding combustion air and/or mixed gas inlets are arranged adjacent to the corresponding staggered brick-walled walls, and the corresponding exhaust gas recirculation channels are arranged in a neutral position, in particular relative to The median longitudinal axis in the corresponding heating tube groove is mirror-symmetrical. This combination of optimization measures provides a particularly powerful effect.

According to an exemplary embodiment, the corresponding partition has at least one additional coupling lower and/or upper channel, which is disposed at a more central height position (in the z direction) closer to the center of the height of the heating tank than the outer circulation flow path More central), and is designated to form an internal inert intermediate layer on the central flow path between gas and air volume flow. The temperature distribution, in particular in the base region, can thus be homogenized. It has been particularly proven that through additional recirculation channels, temperature peaks at specific height positions can be effectively avoided, especially without any risk of weakening of the heated wall composite. In other words, the permeable gas forms an insulating intermediate layer in the partition between the heating tube slots, and the partial volume flow of exhaust gas/flue gas from the descending heating tube slots can be directed through the intermediate layer and again led back A rising heating tube slot in which a combustion inert intermediate flow with a combustion delay effect can be produced by means of an intermediate layer.

According to the present invention, a significant additional effect of NOx reduction has been achieved through a single additional channel. The exhaust gas or the larger volume flow of the exhaust gas can be introduced into the upwardly filled heating tank in this way, especially at different height positions, especially at a distance from the base area, so that the local temperature decreases and the width and/or height The temperature distribution is homogenized.

According to the present invention, the corresponding partition may have at least one additional coupling channel that is disposed more inside than the outer circulation flow path, closer to the center of the height of the heating tube groove, and is designated for use in the gas Form an internal inert intermediate layer between the volume flow of air (acting on combustion technology or mixing technology). This makes it possible to obtain a uniform temperature distribution even at relatively high altitude positions.

It has been shown that at least one additional exhaust gas recirculation channel (for the volume flow of the exhaust gas returning through the adhesive wall back to the upwardly filled heating pipe groove) is provided between the staged air inlet and the base side air inlet of the heating pipe groove The flow conditions at the height position are favorable. According to the invention, with The inert separation layer with heat insulation function can be formed by introducing the internally circulating inert exhaust gas inside, which has the effect of delaying the mixing in the subsequent stage. In particular, a separate layered layer may be formed, which prevents cross-mixing or at least repositions the cross-mixing upward again to a higher height position.

The invention is also based on the concept that the exhaust gas can additionally be directed to a more central height position of the corresponding heating tube groove at a lower pressure difference than the upper and lower ends, in the sense of detour, corresponding to the most outward The exhaust gas recirculation channel goes further inward. In particular, due to the lower pressure difference, the further inward detour or circulation flow constituted by the external circulation flow does not reduce the external circulation flow, or imperceptibly reduces the external circulation flow. However, the effect on heat transfer or local temperature can still be performed in an effective manner.

It has been specifically demonstrated that even in the case of one or more internal circulation flow paths, there is no risk of short-circuiting the external circulation flow, or excessively reducing the risk of external circulation flow in terms of volumetric flow. It is possible to effectively avoid circulating circulation with the outside or short-circuit between the individual channels, in particular because the spacing and/or diameter ratio between the channels is suitable for the pressure conditions in the corresponding furnace. It is also possible to control the risk of configuring circulating flow in the opposite direction, especially because the flow pulse of the incoming gas is utilized.

According to an exemplary embodiment, the corresponding partition has at least one additional coupling lower and/or upper exhaust gas recirculation channel, which is disposed at a more central height position closer to the height of the heating pipe groove than the external circulation flow, and Designated for additional upward or downward internal bypass circulation flow (additional recirculation) to form an internal inert intermediate layer (acting on combustion) between the gas and air volume flow on the additional internal bypass circulation flow path Technical or hybrid technical aspects), wherein the internal inert intermediate layer is preferably defined by the external circulation flow path.

According to an exemplary embodiment, the corresponding partition has a plurality of additional coupling exhaust gas recirculation channels, which are provided above and below at least one air stage in the partition and are designated for at least two further inwards An additional bypass circulation flow, closer to the center of the height of the heated flue than the outer circulation flow surrounding one or more air stages, is used to form between the volume flow of gas and air on the additional internal bypass circulation flow path One or more internal inert intermediate layers (acting on combustion technology or mixing technology), wherein the corresponding internal inert intermediate layer is preferably defined by an external circulation flow path. This enables a stepped effect on the flow and temperature distribution at different height positions, regardless of the stepped air tube slot.

According to the present invention, it is particularly effective that the laminar flow conditions prevail in at least one inert intermediate layer, which can prevent or at least delay the cross-mixing of the returned exhaust gas with the newly introduced gas. The delay of the cross-mixing can be carried out in a more or less effective manner according to the flow conditions, but especially at least in such a manner that the cross-mixing is performed at the earliest above the NOx formation region. The concept of an energy and economically advantageous circulation flow path can also be advantageously further fully utilized in the case where very high flame temperatures dominate, and therefore apply to the case of rich gas heating.

According to an exemplary embodiment, the lower and optionally upper exhaust gas recirculation channels in the height direction are configured to span at least 2 to 5 wall layers, in particular at least 3 to 4 wall layers, and/or Across up to 8 to 10 wall layers. This provides a good compromise between sufficient stability of the structure and sufficient flow resistance or flow rate of the recirculated gas. According to an exemplary embodiment, the corresponding lower/lowermost exhaust gas recirculation channels in the height direction extend through a plurality of wall layers or refractory layers, in particular across at least 2 to 5 wall layers. This can also achieve a sufficient flow distribution. Integration in existing structures can also be performed in a simple manner.

According to an exemplary embodiment, the inner inert intermediate layer in the x direction is arranged to be more internal or more central than the flow path of the inflowing gas, respectively, and to be more neutral or at a more neutral height position than the external circulation flow path, respectively . This facilitates the effect of ordering in the corresponding relative height positions.

According to an exemplary embodiment, the exhaust gas recirculation channel is arranged in the area of the median width (x) of the heating pipe groove, in particular the distance x from the median longitudinal axis is less than 30 or 20 or 10% of the width of the heating pipe groove. The advantages explained above based on the inert intermediate layer result from this.

According to an exemplary embodiment, the corresponding lower exhaust gas recirculation channel is provided between the corresponding coke oven gas inlet and the corresponding combustion air and/or mixed gas inlet. This achieves the aforementioned effects on temperature and flow distribution, especially in the base area, especially the separation of the individual gas flows.

According to an exemplary embodiment, the corresponding coke oven gas inlet is arranged closer to the staggered brick type than one third of the width of the heating flue (the interval x between the opposed staggered brick walls) The distance x of the wall of the masonry, especially from the inner surface of the staggered brick wall is 10 to 350 mm, especially less than 300 mm, wherein the corresponding lower exhaust gas recirculation channels are set to be respectively wider than the width of the heating flue 1/3 is closer to the central or median longitudinal axis of the heating flue, especially with a spacing x of 30 to 300 mm. This provides effective separation of the airflow. The flow paths can flow in parallel without cross-mixing, or appear before the latter.

According to an exemplary embodiment, the corresponding combustion air inlets and/or mixed gas inlets are arranged closer to one-third of the width of the heating flue (the interval x between the opposite staggered brick walls) Staggered along the brick wall, and the corresponding lower exhaust gas recirculation channel is set closer to the center of the heating flue than one third of the width of the heating flue, especially the interval x is 30 to 300mm. This provides effective separation of the airflow. The flow paths can flow in parallel without cross-mixing, or appear before the latter.

Especially in the context of the flow test, it has been proved that the repositioning of the lower exhaust gas recirculation channel closer to the center of the heating flue can achieve the separation of the inflow gas and the reduction of cross-mixing. Therefore, the temperature distribution can be influenced in a targeted manner, especially at selected height positions. It has been shown that a relatively low uniform combustion temperature T2 can be set thereby, especially in the lower region of the furnace chamber, which has a positive effect on NOx emissions.

According to a variant, the corresponding coke oven gas inlet is arranged closer to the corresponding staggered brickwork wall than the corresponding lower exhaust gas recirculation channel, in particular at the median longitudinal axis distance from the staggered brickwork The pitch of the inner surface of the wall is 10 to 350 mm, especially less than 300 mm. This can also provide advantages in terms of structure.

According to an exemplary embodiment, each dual-heated flue provides at least one additional lower exhaust gas recirculation channel, or at least another pair of lower exhaust gas recirculation channels, in particular at least one above the (first) lower coupling channel At another height position, in particular below at least one stepped air inlet. This enables a targeted influence on the temperature and flow distribution at selected height positions.

According to an exemplary embodiment, up to 5 lower exhaust gas recirculation channels, or up to 5 pairs of lower exhaust gas recirculation channels, are provided on each dual-heated flue between two staged air inlets. This influence system at various height positions provides a particularly high degree of flexibility.

According to an exemplary embodiment, at least two additional height positions above the lowermost pair of channels, each dual-heated flue is provided with at least two pairs of additional lower exhaust gas recirculation channels, in particular between three and seven At other heights there are three to seven pairs of lower exhaust gas recirculation channels. Provides high variability through up to seven internal circulation flows.

According to an exemplary embodiment, at a further height position below the staged air inlet/inlet, up to ten additional lower exhaust gas recirculation channels are provided per dual-heated flue, or up to ten pairs of lower exhaust gas recirculation aisle. This makes it possible to configure the circulation flow in a uniform manner, and the gas can distribute the recirculated gas in such a way that it gradually mixes with each other at the corresponding height position. A higher number of channels can also be chosen to adapt the channel geometry to the desired flow state without creating too tight parameters.

The term graded air is used synonymously with the term graded gas. Therefore, the stepped air tube groove can also conduct non-air gas.

According to an exemplary embodiment, at least one additional height position between at least two staged air inlets, each dual-heated flue is provided with at least one additional lower exhaust gas recirculation channel or at least another pair of lower exhaust gas Circulation channel. This enables optimization by combining the circulation flow path of the recycled gas and the inflow path of the stepped gas.

According to an exemplary embodiment, at least one additional lower exhaust gas recirculation channel or at least another pair of lower exhaust gas recirculation channels is provided below each dual heating flue and above the staged air inlet or all staged air inlets. This provides particularly high variability.

According to an exemplary embodiment, at least one further lower exhaust gas recirculation channel or at least another one is provided at each two-stage heating flue at at least one additional height position above the staged air inlet or all staged air inlets To the lower exhaust gas recirculation channel. This also enables the internal circulating flow (path) to be separated from the gas introduced in a stepwise manner.

According to an exemplary embodiment, up to five additional upper exhaust gas recirculation channels or up to five pairs of additional upper exhaust gas recirculation are provided at each dual-heated flue above the staged air inlet or all staged air inlets aisle. This provides particularly high variability.

Due to the above measures, increased residence time and more complete burnout can be ensured, especially in the case of a reduced CO ratio, and a higher heat input into the furnace chamber can also be achieved, which is in the vertical height direction More evenly. It has been particularly proven that in the case of exhaust gas recirculation exceeding 50%, it is possible to ensure that combustible gas components are completely burned to form exhaust gas. This makes it possible to make better use of the heat content of the medium, especially in a continuous manner over time. Therefore, the proportion of CO in the exhaust gas, which is usually 200 to 400 ppm, can be further reduced.

If the exhaust gas recirculation channels are provided above all the staged gas inlets, part of the hot exhaust gas can be directed into the down-filled heating tube grooves already before the reversal point, which has a positive effect on temperature management, especially in batches In the gas collection space above the material. Here, it generally does not exceed 800 to 820°C (the chemical quality of soot and raw gas). Due to the exhaust gas returning further below, the temperature of the individual furnace chambers can also be lowered.

In each case, the exhaust gas recirculation channels may be provided in pairs or individually, so in the case of odd numbers (for example, three or five, or other numbers of additional exhaust gas recirculation channels).

It has proved to be advantageous, depending on the type of construction of the coke oven device, between two and ten additional exhaust gas recirculation channels.

According to an exemplary embodiment, in each case, at least two intermediate layers are provided between the various channels. This also provides good stability. The stability of this type of heated wall composite composed of staggered brick-walls and bonded walls is advantageous in terms of the stability of the coal propulsion fuel pressure under load (maximum is about 75%). Coke ovens are usually constructed in layers with a layer height, including joints between 100 and 160 mm, in particular about 120 to 130 mm. The architectural teaching of coke oven is through tongue-and-groove connection or through tongue-groove curvature (tongue-and-groove curvature) teaches all bricks ideally connected to the heated wall. If a large channel cross-sectional area across multiple layers is desired, the heated wall composite is weakened, and there is a risk of deformation and migration of raw material gas from the furnace chamber due to the expansion joint. There is an insufficient amount of combustion air in the heating tube slot, which may adversely lead to the formation of CO. Therefore, high stability in the lateral (horizontal) direction is very important.

In the vertical direction, it is also desirable to have the prestress of the heating wall to protect the heating wall composite from vertical bending. Therefore, the upper and lower sides of the bricks are also preferably connected with tongue and groove. The vertical prestressing of the heated wall is carried out in particular by a sufficiently high roof weight.

For example, at the end of the carbonization cycle, through the steel column passing through the chamber, the horizontal injection of the coke batch produces a further high loading force on the wall composite, which must take into account the transverse and vertical directions through the heated wall composite High enough prestress. Therefore, additional channels, especially those with a relatively large cross-sectional area, require complex considerations in terms of furnace stability and life.

According to a variant, the recirculation channels are arranged as follows: in each case, a wall layer has a recirculation channel, and above it there is a layer of composite stable refractory without channels, always alternating with, for example, up to ten channels ; Or in each case, a wall layer has a recirculation channel, and above it there are two layers of composite stable refractory material without channels, after which a wall layer has a recirculation channel, and there is one or Two layers of composite stable refractory without channels. This provides good stability. The channel is relatively small, but can be easily integrated into the architectural shape of the furnace.

According to an exemplary embodiment, at least one, in particular a centrally arranged, stepped air tube slot is arranged in the baffle, the air tube slot has at least one stepped air inlet, in particular at least There is at least one stepped air inlet above a recirculation channel. This opens up further possibilities to influence the flow and temperature distribution.

According to an exemplary embodiment, at least two tiered air tube slots are arranged in the (corresponding) partition, in particular air tube slots arranged in parallel, the tiered air tube slots are connected to the upper/uppermost exhaust gas recirculation Above the channel, and the uppermost staged air inlet above all exhaust gas recirculation channels leads to the combustion heating tube slot. For example, this can also optimize the temperature and flow distribution by means of gases introduced in steps in different width positions or (x) positions, respectively. The unified channel can be adjusted in a simple way from above the top plate by means of adjusting elements or sliders.

According to an exemplary embodiment, at least two stepped air tube slots are arranged in at least one baffle, in particular air tube slots arranged in parallel, the stepped air tube slots located above the upper/uppermost exhaust gas recirculation channel The two uppermost stepped air inlets lead to the burning heating tube slot. Therefore, the gas introduced in a stepwise manner can be introduced into the heating tube groove in a uniform manner across the width (x direction).

Other embodiments of stepped air tube slots, through separate inlets or through a common inlet, provide the advantage that the circulating flow, especially in the lower region of the heating tube slot, can be moved away and into the center in any way, so it can be very effective Separated from the incoming gas. Here too, structural advantages can be produced, as well as cost advantages in the device structure, or advantages in terms of operation. The stepped air tube slot can also be moved to the outside, so that the flow of inert exhaust gas by means of recirculated gas can be configured to be as central as possible (at least more central than other gases). A favorable secondary heat distribution can also be achieved. In particular, it has structural advantages.

According to an exemplary embodiment, the corresponding lower/lowermost exhaust gas recirculation channels are respectively provided at intervals of at least 50 mm above the lower region or above the base of the heating tube groove. Therefore, in particular When tuning through the arrangement of the inlet, a positive fluid effect can be achieved. In particular, the lower edge of the lowermost circulation channel is arranged in the range of 0 to 150 mm above the burner plane, with a stable separation layer with a height of about 120 to 130 mm above it, and a minimum height (eg, about 120 mm) above it Another channel, where this change from the channel to the separation layer can extend to a height of 800 mm.

According to an exemplary embodiment, the coke oven gas inlet or corresponding gas flue (nozzle or tube) is disposed at a distance from the median longitudinal axis that is at least 50% of the width of the heating tube slot. This spacing provides effective separation from the more centrally located flow path of the recirculated gas.

According to a variant, the steps are only provided in the rising heating tank.

According to a variant, at least three additional coupled exhaust gas recirculation channels are provided, in which at least two internal additional circulating flows are provided, wherein, in each case, during the gas phase (outlet of the staged air tube slot) An exhaust gas recirculation channel is provided above and below. This allows measures to be effectively combined.

According to an exemplary embodiment, the combustion air inlet and/or mixed gas inlet and/or coke oven gas inlet are relative to the median longitudinal axis of the heating tube slot (either relative to the normal of the substrate or relative to the vertical direction) to An angle of 0° or an angle of less than 30° is aligned, especially less than 20° or less than 10° with respect to the vertical direction (z), and all inlets are inclined or aligned especially in the same direction. This alignment, which is aligned in a vertically upward manner as much as possible, enables the flame to be placed in the center, which provides an advantage in terms of temperature distribution. Therefore, the volumetric flow of the exhaust gas can flow in the heating tube groove in a center and almost vertical upward direction, and therefore, in the normal direction in the vertical height direction z, new incoming gas can form an air blanket for separation. Contrary to highly inclined alignment, this volume flow will not hit the wall. Therefore, the combustion can be directed toward the center of the heating tube groove, and thus not toward the outer surface, and thus a moderate temperature can be set. can To effectively avoid local temperature peaks. It has been shown that the corresponding inflow pulses in this context can be used particularly advantageously for additionally extracting smoking gas from non-burning heating tube slots, or for more targeted mixing of gases. The corresponding inflow pulses can be released into other gases and therefore will not dissipate on the wall. In contrast, hitherto the furnace inlets have generally been aligned obliquely at large inclination angles greater than 30°. It has been shown that in this alignment situation, the inflow pulses of the corresponding gases are not particularly effectively utilized, and in particular cannot be used to smoke cigarette smoke from non-burning heating tube slots. The alignment according to the invention enables a particularly high recycling rate.

According to an exemplary embodiment, the corresponding combustion air inlet and/or the corresponding mixed gas inlet and/or the corresponding coke oven gas inlet have a maximum cross-sectional area of 0.06 m ² , especially in the case where the furnace chamber height exceeds 6 m . In the case of such an upper limit, it can be ensured that the incoming gas flows into the heating tube groove at a specific minimum pulse or a specific minimum velocity, so that the flow state in the heating tube groove can be effected through the inlet in an effective manner. Due to this type of relatively small cross-sectional area, a high ejection effect can be achieved. In particular, the gas can be entered in such a way that the circulating flow rate or the proportion of recycled gas is increased respectively. Since the cross-section is small or reduced in this way, the incoming pulse of the medium can also be increased in such a way that the rate of the returned exhaust gas can be increased, especially from about 30% to 45% when the coke oven gas is heated % To about 50% to 80%. A high flow rate can be set, which has the effect of increasing the volume flow of the exhausted or entrained exhaust gas, respectively. In particular, it is possible to achieve a high inflow velocity of the heating flue exceeding 2 m/s. It also ensures a stable flame profile, which helps to delay the burnout characteristics.

According to an exemplary embodiment, the cross-sectional area of the corresponding lower and/or upper exhaust gas recirculation channel is greater than 0.005 m ² , in particular greater than 0.01 m ² . This makes the flow pulse of the recirculated exhaust gas relatively weak, and has a stronger effect of the flow pulse of newly-entered gas. Therefore, a large effect can be achieved through a relatively small newly entered volume flow, and a high circulation flow rate can be selected.

According to an exemplary embodiment, the cross-sectional area of the corresponding lower exhaust gas recirculation channel has a rectangular geometry, which is elongate in particular in the width direction (x) transverse to the injection direction. This achieves the integration of the walls in a simple way, with the option to adjust the size with minimal structural action. The cross-sectional area of the corresponding upper exhaust gas recirculation channel can likewise have a rectangular geometry, which is elongate in particular in the width direction (x) transverse to the injection direction, or has a square geometry.

The individual inlets and/or corresponding channels here can have the same size, or can be specially adapted according to the height position.

According to an exemplary embodiment, the corresponding exhaust gas recirculation channel has at least one circulating flow edge and/or convex curvature, in particular a radius (or equivalent degree or millimeter) of at least one quarter of a wall layer or at least 30° , Especially a circulating flow edge or convex curvature inward relative to the corresponding circulating flow path. This facilitates circulating flow, especially when there is only a slight pressure difference. At the same time, a favorable flow distribution can be ensured in the upwardly filled heating tube groove.

According to an exemplary embodiment, the corresponding exhaust gas recirculation channel has at least one sharp flow edge and/or concave curvature, in particular with a maximum radius (or equivalent degree or millimeter) of one or two wall layers, in particular relative to the corresponding The sharp flow edge or concave curvature of the circulating flow path outward. This can ensure that the flow flows on the optimal flow path. The gas conduction profile can be provided through or in the channel.

According to an exemplary embodiment, the corresponding exhaust gas recirculation channel has at least one surrounding flow profile having at least one radius and at least one sharp flow edge (break-away edges, respectively). This combined profile provides a particularly positive fluid effect and has the advantage that additional internal circulation flow can be configured at very low pressure differentials. phase In particular, the corresponding radius can be configured at an angle of 30° to 60°. This type of flow optimization can allow the layout of the channels to be designed in a more flexible manner, especially since there is only a very small pressure difference in the range of a few Pascals (Pa) in the relatively high heating tube groove. Flow barriers can be achieved through the edges in the channel, which has the effect of only returning the flow forward into the corresponding upwardly filled heating tube groove.

According to an exemplary embodiment, the lower exhaust gas recirculation channel is arranged to be offset up and down from each other at the top end on both sides of the staged air tube slot, which extends in the partition, in particular with the stability in the partition Combining webs. Therefore, the flow distribution can also be affected in a larger width range (x). Relative to the horizontal direction, an offset between 10 and 200 mm may be advantageous, especially to improve the cooling effect.

According to an exemplary embodiment, at a position between the mixed gas inlet and the combustion air inlet, at least one conveying channel for introducing the recirculated exhaust gas into the lower side of the corresponding heating tube groove is provided below the exhaust gas recirculation channel/channel, Especially in the middle part above the regenerator of the coke oven plant. These transfer channels have a larger flow path and are constructed in the form of tube slots (circular or rectangular), and can be provided in combination with the above-mentioned bypass opening (differential heater).

According to an exemplary embodiment, at least one inlet in the lower region, in particular the coke oven gas inlet, includes an inlet nozzle and is located at a height of 0.0 to 0.45 m, in particular 0.05 to 0.25 m above the base of the heating tube slot It leads to the heating pipe groove. It has been shown that this distance from the substrate has a positive effect on the flow distribution in the substrate area. This nozzle design embodiment can be referred to as gas grading and can advantageously be combined with other measures described herein. The nozzle tube provided on the base of the heating tube slot preferably terminates at a height of about 0.25 m above the tube slot floor (combustion furnace plane), and is preferably composed of a refractory material. Therefore, coke oven gas flows in from the tube at a height position of about 0.25 m and mixes with the air flowing in the base.

In the case of a top heating furnace (=cross burner), the inlet nozzle for calibrating the volumetric flow can be arranged in the nozzle tube, preferably on the base at the height of the tube floor/combustion furnace plane. The height position of the nozzle tube is lower than 500mm or preferably lower than 350 or 300mm can also protect the nozzle provided therein from carbon or soot deposits, which reduces the flow cross section and high temperature, which can prevent any output loss. In the case of a bottom-burning furnace, the nozzle is arranged below the level of the furnace in the furnace unit, the latter operating under atmospheric conditions (no risk for high temperatures). In the case of two types of furnaces, the nozzle tube protrudes into the heating tube slot by 0.05 to 0.5 m, preferably 0.25 m, so that in the case of a bottom-burning furnace, the gas enters the same height position as the cross-burning furnace.

According to an exemplary embodiment, the inlet nozzle is aligned so as to be orthogonal to the base of the heating tube slot, in particular perpendicular. The additional inlets are also preferably aligned so as to be at least almost orthogonal or vertical, respectively.

According to the present invention, the above object is also achieved by a method for operating a coke oven device for producing coke through coking coal or a coal mixture, through the main measures inside the coke oven device through the inherent gas of the coke oven Internal heat equalization of energy to minimize NOx emissions, especially for operating the aforementioned coke oven device, where the corresponding dual-heated flue has a combustion heating tube slot and flue gas heat conduction or exhaust gas guide tube slot, around the partition The internal exhaust gas recirculation on the external circulation flow path, especially at the upper and lower ends of the heating tube slot, is set through at least one coupling channel through the partition, especially through the upper and lower coupling channels, where the corresponding In the lower region of the base of the dual-heated flue, coke oven gas and/or combustion air and/or mixed gas (that is, at least one gas selected from the group of coke oven gas, combustion air, and mixed gas) enters; The circulation on the circulation flow path or at least one central flow path can in each case be directed to be more central than the incoming gas (hence closer to the median longitudinal axis in the xy plane), in particular, through the incoming gas, Especially following In the ring, it is defined on both sides or has circumferential flow on both sides. This provides the aforementioned advantages. Through at least one of the incoming gases, the separation of the exhaust gas recirculation herein can be achieved in terms of fluid technology and thermal technology.

Because at least one partial volume flow of the returned exhaust gas is in particular introduced between the volume flow of the heating gas introduced in the base region of the upwardly infused heating tube groove and at least one partial volume air flow (into the base tube groove), the returned The partial volume flow of the gas can be directed forward and used as an inert intermediate layer in the following way: the inert intermediate layer initially separates the reactants of the gas and air in the lower region of the heating tube groove (in terms of combustion technology), and in the vertical direction The further process of the flow further induces a delayed burnout characteristic above. This can lead to the effect of reducing NOx.

According to an embodiment, in each case, in the partition between the heating tube slots, at least one adiabatic intermediate layer of partial volume flow of exhaust gas/flue gas from the downward heating tube slots is formed here as a plurality of double heating The flue, in each case, each heated flue has heating tube slots in pairs.

According to an embodiment, at least one additional internal circulation flow is set, in particular through at least a pair of additional channels at the top and bottom, to be set more central than the incoming gas and more inward than the external circulation flow path, and by Defined by the external circulation flow path. It has been shown that when there is a pressure difference in the range of a few pascals, it is already possible to configure another internal circulation flow further arranged inward. The pressure difference can be significantly lower than 1 mbar, especially in the range of less than 10 or 5 Pascals (Pa), for example 2 to 4 Pa, and additional circulation flow can still be configured.

According to an embodiment, in the case of rich gas heating or mixed gas heating, the proportion of internally recirculated exhaust gas on the circulation flow path or the plurality of circulation flow paths is set to exceed 50%, in particular to exceed 70%, Especially 80%. In contrast, to date, the proportion of recirculated exhaust gas in the case of rich gas heating is at most 25% to 45%, or in the case of mixed gas heating 10% to 20%. High recirculation rates can be achieved through optimized gas paths and energy-saving processes that minimize emissions.

According to one embodiment, the method for rich gas heating is essentially using coke oven gas; or wherein the method for mixed gas heating is essentially using a mixture of blast furnace gas, coke oven gas and optional conversion furnace gas; or The method is to use natural gas as at least a partial replacement of coke oven gas. It has been shown that the flow concept according to the invention can be implemented in any of these types of operating situations.

The mixed gas usually consists of two or three gases or gas mixtures, in particular blast furnace gas (mostly), coke oven gas (small proportion) and optional reformer gas. Coke ovens (especially compound furnaces) are usually heated with rich gas only for about 5% of the operating time per year, and the flame temperature is significantly higher than 2000°C (high heating value of rich gas or coke oven gas, respectively). However, in the case of mixed gas heating (blast furnace gas), the flame temperature is, for example, only in the range of about 1700°C. However, some furnaces are not operated as composites and must be operated with coke oven gas or rich gas to the extent of 100%, respectively. According to the present invention, it has been proved that, although the flame temperatures are very different, relatively low NOx emissions can be achieved for rich and heated gas mixtures. This provides the furnace operator with the maximum flexibility of his/her furnace operation, more or less independent of the emission regulations that may be predefined in time or calendar date. In particular, in the case of rich gas heating, the furnace operator can select the operation mode without hesitation.

Especially in downstream equipment components, purified coke oven gas with a lower heating value between 17000 and 19000 kJ/Nm ³ is used as rich gas. Rich gas is usually composed of CO, H ₂ , CH ₄ , O ₂ , N ₂ , CO ₂ and higher quality hydrocarbons.

According to the present invention, in the case of rich gas heating, the circulating flow of the returned exhaust gas can be increased from about 30% to 45% to more than 50% before, and in the case of mixed gas heating, from about 15% to 25% before Increased to more than 50%. This makes it very permeable to pass relatively cold exhaust gases Effectively cool the flame temperature in the upwardly filled heating tube groove. In particular, a cooling effect in the range of at least 5 to 60°C can be achieved, thereby minimizing thermally formed nitrogen oxides. In addition to this, uniform coke quality can be achieved, especially due to the very uniform heat flow, and thanks to the lower temperature gradient, the thermal stress on the chamber wall can be minimized. The furnace can be operated at at least almost the same coking rate at lower heating temperatures, as is the case with furnaces operating at higher temperatures hitherto with stronger NOx emissions.

Here, natural gas can also be fed through the inlet of the coke oven gas, which is provided in particular as LNG (liquefied natural gas). Depending on the pumping location/source, natural gas up to 90% to 100% is composed of methane (CH ₄ ) and slightly more higher quality hydrocarbons. Due to the low flame temperature of methane, methane is the preferred substitute for coke oven gas (less thermal NOx is formed). However, methane/natural gas is more expensive. In addition, the purified coke oven gas produced indoors will not find any buyers. Depending on the mode of operation, the coke oven gas may be replaced at least partially by natural gas. When natural gas is used, the effects of the present invention can also be achieved.

According to an embodiment, the sub-stoichiometric combustion ratio is set to <0.9, in particular the combustion ratio in the range of 0.5 to 0.8, in particular the combustion ratio of 0.7, especially in the plane of the furnace on the base of the corresponding heating tube groove In the base area. The lower the air excess (Lambda) set below the first combustion stage, the weaker the combustion, or the heat conduction can be set in the lower region of the heating flue, respectively. It has been shown that the number of air in the base area of the heating tube groove is less than 0.9, in particular in the range of 0.5 to 0.8, with a good safety factor to comply with the limit values required for NOx emissions. Independently, the air value in the head region can be set in the range of 1.2 to 1.3.

The combustion ratio can be adjusted by supplying the total air volume of the heating wall composed of, for example, 10 to 25 double-heated flues to the air valve before the entire furnace group. For this purpose, for example, a metal plate The resistance is placed in the inlet cross section of the corresponding valve, for example to reduce the amount of air sucked in, ie the so-called air volume of the entire heating wall. In addition, adjustment flaps can be provided in the air valve to further influence the total amount or direction of the partial amount, which in each case flows into the respective regeneration section. For example, the first regeneration preheats a part of the respective amounts of gas and air that flow into the substrate, and the second regeneration preheats a part of the amount used to stage air.

According to an embodiment, with the aid of recirculated exhaust gas, a preferably layered intermediate layer is arranged between the incoming gas and the staged air tube slot or the gas from the staged air tube slot, especially at the height of the heating tube slot 5% to 75%, preferably 15% to 50% of the height range, especially in the height of 0.25 to 4m. This can promote the separation of the airflow.

According to an embodiment, with the aid of the incoming gas, an insulating and mixed delayed air blanket is arranged between the corresponding staggered brick wall and the circulating flow path. Laminar flow or intermediate layers can be identified especially by Reynolds number less than 2320.

According to an embodiment, the amount of gas introduced between the first stage and the second stage (one or more bonded wall stages), in particular the amount of gas introduced through the combustion air and mixed gas inlet (base stage) on the substrate The ratio is set to 50:50, or the ratio in the first stage is lower. The reduction of the proportion of gas introduced into the substrate in the first stage can optionally be carried out through a higher proportion of recycled gas. This influences the flow profile, in particular in the area of the substrate, to achieve further changes.

According to an embodiment, the volume flow ratio introduced into the heating tube groove is set as follows: through the combustion air inlet <30%, through the mixed gas inlet <30%, through the recirculation channel >40%, and optionally at least one staged gas Entrance. According to an embodiment, the volume flow introduced into the furnace chamber at the combustion air inlet and the mixed gas inlet is set or adjusted to 45% and 55% of the volume flow introduced through the recirculation channel and optionally at least one stepped gas inlet between. This can also have a more effective effect on different height positions in each case. The method here is carried out in particular with rich gas heating. The method of heating through the rich gas preferably uses lean rich gas having a reduced low heating value in the rich gas heating mode, in which a gas having a lower heating value is provided as a rich gas in a range of 14000 to a maximum of 17000 kJ/Nm ³ . Therefore, the flame temperature and the above measures can be significantly reduced, especially the difference of 50 to 300K.

According to the invention, the above objects are also achieved by a logic unit or a control device, respectively, which is designated to perform the method as described above, wherein the volume flow introduced into the heating tube groove is set according to the above ratio, and/or The flow direction in the heating flue is switched in a cyclic manner, especially every 15 to 25 minutes. Therefore, even in the case of frequent switching, a very uniform temperature distribution can be achieved. The switching time here is, for example, in the range of 1 to 2 minutes.

According to the invention, the above object is achieved by using at least one baffle with at least one exhaust gas recirculation channel, which is further positioned inward in the width direction (x) so that the dual heating flue gas in the coke oven device In the tunnel, especially in the coke oven device as described above, it is more central than at least one gas inlet, especially more central than all gas inlets. This results in the aforementioned advantages.

According to the invention, the above object is achieved by using at least one baffle with at least one exhaust gas recirculation channel, which is further positioned inward in the width direction (x), so that only the dual heating of the coke oven device Half of the flue is directed to the coke side of the coke oven device, especially in the coke oven device as described above, more centrally than the gas inlet. This results in the aforementioned advantages.

According to the present invention, the above object is also achieved by using at least one baffle plate having at least two (particularly arranged in parallel) staged air tube slots connected to the upper/uppermost exhaust gas recirculation channel Upper and upper staged air inlets, uppermost staged air inlets Above all exhaust gas recirculation channels leading to the heated heating tube slots, and/or through the use of at least one baffle plate with at least two (particularly parallel) staged air tube slots, in all exhaust gas recirculation channels The upper/uppermost exhaust gas recirculation channels in the upper two uppermost stepped air inlets lead to the heated heating tube slots, especially in each case in the coke oven device as described above. This provides a high degree of variability in individual optimization measures.

It has been shown that due to this structure, the structural forces can be minimized. In many operating conditions, the coke-side half is hotter than the coal-side half, so the measures described here are sufficient to be implemented in the coke-side half, so in the case of, for example, 6 to 25 double pairs, especially a maximum of 20 double pairs, It is further arranged towards the rear in the spray direction, so there are about 6 to 25 per furnace chamber, especially up to 20 baffles.

According to the present invention, the above object is also achieved by using a coke oven device for coking coal or coal mixture as described above. The coal mixture contains at least one additive from the following group: petroleum coke, oil, bitumen species (eg , In the form of used tires, coal dust and coke powder), binders or coking agents (for example, molasses, oil residues, cellulose additives, sulfite or sulfate compounds or lye), where the mixture may also contain raw substance.

According to the present invention, the above object is achieved by using lean gas having a reduced low heating value in the operation of the coke oven device as described above. The rich and poor gas here is provided especially by mixing blast furnace gas and rich gas.

In particular, for blast furnace gas (BFG) and rich gas (coke oven gas is purified as a by-product), the following values can be mentioned as the volume% (wet state) and low heating value (kJ/ m ³ , dry state, anhydrous):

Blast furnace gas: 1.92% H ₂ , 59.5% N ₂ , 24.24% CO, 11.96% CO ₂ , 2.37% H ₂ O, with a low heating value of about 3349;

Rich gas: 54.98% H ₂ , 0.66% O ₂ , 5.33% N ₂ , 5.75% CO, 1.52% CO ₂ , 26.66% CH ₄ , 2.74% C ₂ H ₆ , 2.37% H ₂ O, with a low heating value of about 18422.

In each case, according to the selection of a person with ordinary knowledge in the technical field to which the present invention belongs, the percentage figure after the sum of the individual gas mixtures is 100%. The total components of each gas mixture are 100%. In this case, other components can be included in the corresponding gas mixture, in particular trace amounts of high-quality hydrocarbons and NH ₃ and H ₂ S, in particular in each case below 1.5%. For the variation range of each component, a tolerance of ±15% can be specified.

In particular, mixed gas or lean gas can be mixed from blast furnace gas and purified rich gas, especially according to the following components, which are rounded to the first decimal place, in each case, each component The tolerance variation range is ±15%:

Mixed gas: 5.6% H ₂ , 0.1% O ₂ , 55.7% N ₂ , 23.0% CO, 11.2% CO ₂ , 1.9% CH ₄ , 0.2% C ₂ H ₆ , 2.4% H ₂ O, with a low heating value of about 4396;

Rich and poor gas: 45.1% H ₂ , 0.6% O ₂ , 14.4% N ₂ , 8.9% CO, 3.3% CO ₂ , 22.2 CH ₄ , 2.3% C ₂ H ₆ , 2.4% H ₂ O, with a low heating value of about 15910 .

It has been shown that the use of lean gas can reduce NOx by 30 to 50 ppm (corresponding to 7% O ₂ in the exhaust gas), especially where the local flame temperature is reduced to a range below 2000°C. Combined with the above measures, the beneficial effect of reducing NOx is further amplified.

1‧‧‧ coke oven, especially horizontal chamber furnace

2‧‧‧ Furnace room with coal batch

3‧‧‧ Staggered brick wall

3.1‧‧‧ Wall

4‧‧‧coupled to the partition or bonded wall

4a‧‧‧Partition without partition

4.1‧‧‧Tube groove on the partition or stepped ventilation tube groove

4.2‧‧‧Combustion stage or inlet or outlet on the stepped air tube slot from/to the heating tube slot

4.3‧‧‧Wall

4.4‧‧‧Coupling the channels of two heating pipes (or the reversal point of exhaust gas or the reversal point for heating gas)

5‧‧‧Double heating flue (two vertical heating flues are arranged in pairs)

5.1‧‧‧Burning heating tube slot (vertical heating flue)

5.2‧‧‧Exhaust gas guide tube slot (vertical heating flue)

5.3‧‧‧Inner Wall

5.4‧‧‧Burner surface or bottom of heating tube

5.6‧‧‧Differential Heater

5.61 ‧‧‧ Individual opening of the differential heater

5.7‧‧‧(middle) the top plate of the heating tube slot

6‧‧‧(1) Combustion air inlet, especially for coke oven gas heating

7‧‧‧Additional combustion air inlet or mixed gas heating inlet

8‧‧‧Coke oven gas inlet or coke oven gas nozzle

9‧‧‧Circulation flow

10‧‧‧Coke oven device, especially furnace with horizontal chamber

10.2‧‧‧furnace room

11‧‧‧Burning heating tube slot (vertical heating flue)

11.1‧‧‧Inner Wall

12‧‧‧ Waste gas guide pipe groove (vertical heating flue)

13‧‧‧Double heating flue (two vertical heating flues are arranged in pairs)

14‧‧‧Baffle or adhesive wall

14a‧‧‧Partition without partition

14.1‧‧‧Tube groove or stepped air tube groove on the partition

14.11‧‧‧ Combustion stage or staged air inlet or outlet on/from the heated tube slot

14.2‧‧‧Channels coupling two heating tube slots

14.21‧‧‧Circular flow edge

14.22‧‧‧Sharp flow edge

14.3 The inner surface of the separator

15‧‧‧ Staggered brick wall

15.1‧‧‧The inner surface of the staggered brick wall

16‧‧‧(1) Combustion air inlet, especially for coke oven gas heating

17‧‧‧Additional combustion air inlet or mixed gas heating inlet

18‧‧‧Coke oven gas inlet or coke oven gas nozzle

19‧‧‧Circulation

19.1‧‧‧External circulation flow path

19.2‧‧‧(First) Internal circulation flow path

19.3‧‧‧ (separate) internal circulation flow path

20‧‧‧Logic unit or control device

d2 ‧‧‧ The mutual spacing in the x direction between the inner side wall/edge of the corresponding channel 14.2 and the outer side wall/edge of the stepped air tube slot 14.1, which is particularly centrally arranged in the heating flue

d4‧‧‧Dual heating flue known channel 4.4 mutual spacing in the x direction

d5‧‧‧ The distance from the other inlet in the x direction of the coke oven gas inlet 8, especially the interval between the coke oven gas inlet 8, G1a and the additionally entering gas stream G1

d14‧‧‧ The space between the dual heating flues according to the invention in the x direction of the channel 14.2

d15‧‧‧ According to the present invention, the distance between the coke oven gas inlet 16 and the other inlet in the x direction, especially between G1 and G1a

G1‧‧‧Heating gas or combustion air

G1a‧‧‧Coke oven gas

G1b‧‧‧gas mixture

G4‧‧‧ recirculated exhaust gas

G5‧‧‧ Staged gas or staged air from the combustion stage

G6‧‧‧ waste gas

GP1‧‧‧Inflow path or flow path, respectively used for at least one gas introduced through the inlet

GP4‧‧‧Recirculation exhaust gas/flue gas flow path

GP5‧‧‧Introduction of gas flow path in a stepwise manner

M‧‧‧The median longitudinal axis of the corresponding heating tube slot

Q14‧‧‧Cross-sectional area of the coupling channel on the inner surface of the heating tube groove

T1‧‧‧Nozzle brick temperature

T2‧‧‧Temperature of heating flue/heating tube groove (gas)

T3‧‧‧The temperature in the furnace

V(t)‧‧‧The volume flow rate of the corresponding gas flow, for example in m ³ /h

x‧‧‧horizontal direction (width or length)

x2‧‧‧x offset

x4‧‧‧The distance between the conventional passage 4.4 and the inner wall of the staggered brick wall 3

x6‧‧‧The distance between the conventional entrance 6 and the inner wall of the staggered brick wall 3

x8‧‧‧The distance between the conventional entrance 8 and the inner wall of the staggered brick wall 3

x14‧‧‧The distance between the channel 14.2 according to the present invention and the staggered brick wall

x16‧‧‧ The distance between the entrance 16 and the staggered brick wall according to the invention

x18‧‧‧The distance between the entrance 18 and the staggered brick wall according to the invention

y‧‧‧Depth or horizontal spray direction

z‧‧‧Vertical direction (vertical axis)

z2‧‧‧Height of furnace room

z4‧‧‧The height position of the corresponding stepped air inlet/outlet

α‧‧‧Inflow angle of coke oven gas relative to z axis (vertical)

Other features and advantages of the present invention result from the following drawings and description of at least one exemplary embodiment, in which:

1A, 1B, 1C, 1D, 1E, 1F, 1G, and 1H show schematic cross-sectional side and plan views of a dual heating flue or coke oven according to the prior art, respectively.

2, 3, 4, 5, 6, and 7 show schematic cross-sectional side views in the width and depth directions of a dual-heated flue according to an exemplary embodiment.

8A, 8B, 8C, 8D, 8E respectively show a cross-sectional side view and a schematic plan view of a dual heating flue or coke oven device according to an exemplary embodiment.

9 respectively shows a schematic cross-sectional side view of a cross-section or cross-sectional profile of a channel in a dual-heated flue according to an exemplary embodiment.

FIG. 10 shows a method diagram related to the operation of a coke oven device according to an exemplary embodiment.

11 and 12 show schematic cross-sectional side views of a dual-heated flue according to an exemplary embodiment.

In the case of element symbols not explicitly described in the context of individual drawings, reference may be made to other drawings. In the drawings depicting the prior art, the position and angular alignment of the various inlets and channels or flow paths are not fully shown, but are only shown in an exemplary manner (especially only in the individual heating tube grooves) and not Precise angle setting. In the drawings describing the present invention, the position and angle alignment of each inlet and channel or flow path are shown schematically (especially only in each heating tube groove), where the value or angle alignment of each pitch is more detailed in the description Define in detail.

FIGS. 1A, 1B, 1C, 1D, 1E, 1F, 1G, 1H show a coke oven 1 as a horizontal chamber furnace, which has a plurality of furnace chambers 2 and in each case a coal batch. For example, the height z2 of the furnace chamber 2 6 to 8m. The furnace cavity 2 is separated by a staggered brick-walled wall 3 which in each case extends in the y-z plane. The pair of heating tube grooves 5.1, 5.2 in each case respectively form a double heating flue 5 between two staggered brick-brick walls 3, the inner wall 5.3 of which is defined Heating space filled with gas (and no coal) from each furnace. The heating tube slots 5.1, 5.2 operate in an alternating manner as a combustion or exhaust gas-guiding heating tube slot, which requires switching the flow direction and is carried out in a cycle of, for example, 20 minutes.

The pair of heating tube grooves are separated from each other by a coupling partition (adhesive wall) 4 in each case, wherein coupling channels 4.4 are provided at the top and bottom, and the circulation flow 9 of recirculated exhaust gas can be implemented through the channels 4.4 .

Adjacent dual-heated flues are completely separated from each other by a partition baffle 4a with no channels at all.

In each case, a stepped air tube slot 4.1 is provided in the partitions 4, 4a, the former being coupled to the heating tube slot through at least one combustion stage 4.2 or corresponding inlet or outlet, respectively. The corresponding combustion stage 4.2 is set at the characteristic height position z4. For example, two or three height positions z4 where stepped air enters are defined.

The corresponding wall is made of brick, which in each case defines a wall layer 3.1.

The x direction indicates the width of the furnace 1, the y direction indicates the depth (or the horizontal injection direction in the case of a horizontal chamber furnace, respectively), and the z direction indicates the vertical (vertical axis). The median longitudinal axis M of the corresponding heating tube slot runs through the center of the corresponding heating tube slot, which is arranged with respect to the inner surface/inner wall to be centered in the x direction and the y direction. The center of the corresponding dual-heated flue is not marked. The center is located approximately in the center of the corresponding baffle, the baffle has a circulating layer flow, especially the sub The center of the air duct groove. The term "center" or "center" here refers to the center of the x-y plane, and the term "center" or "center" refers to the height direction (z) in this article.

Multiple inlets, in particular (first) combustion air inlet 6 (especially for coke oven gas heating) and another combustion air inlet 7 (especially for mixed gas heating), and coke oven gas inlet 8 are provided respectively In the so-called burner plane 5.4 or on the base of the corresponding heating tube groove. The gas introduced through the inlet flows upward on the wall surface 4.3 of the partition and on the inner wall of the staggered brick wall.

The temperature of the coke oven 1 includes: the nozzle brick temperature T1, the (gas) temperature T2 in each heating tube groove, and the temperature T3 in the furnace chamber. The invention is particularly concerned with the distribution of the temperature T2 as uniform as possible.

Each air flow will be described below with reference to FIGS. 1F to 8E. The gas flow G1 identifies newly entered or supplied heating gas or combustion air, respectively. The gas stream G1 may include a gas stream G1a (coke oven gas) and/or a gas stream G1b (mixed gas). The gas flow G4 identifies the recirculated exhaust gas, which are respectively returned or wired in a circle. The gas flow G5 identifies the gas or air from the corresponding combustion stage 4.2, 14.11, respectively, and the gas flow G6 identifies the exhaust gas discharged from the corresponding heating tube groove or heating flue.

The pitches and relative positions of the various inlets and channels that have been common so far will be described below with reference to FIGS. 1D and 1E.

The distance d4 of the conventional channels 4.4 in the x direction is relatively large. The distance d5 between the coke oven gas inlet 8 and the other inlets 6, 7 in the x direction, in particular, the interval between the coke oven gas inlet 8, G1a and the additionally entering gas stream G1 is relatively small. The distance d5 is smaller than the distance d4. The distance x4 between the corresponding channel 4.4 and the inner wall of the staggered brick-walled wall 3 is relatively small (especially, between 120 and 140mm interval). From staggered brickwork The spacing x6, x8 of the inlets 6, 8 of the combined wall 3 is relatively large. The pitch x8 is smaller than the pitch x6. The spacing x4 is significantly smaller than the spacing x6, x8.

The recirculation arrows shown in FIG. 1D are shown only in a schematic manner and do not fully reflect the direction of the corresponding air flow.

FIG. 1G schematically shows a differential heat exchanger 5.6 with a separate opening 5.61 through which the gas can be diverted in the head region of the heating tube groove. The differential heat exchanger 5.6 is separated from the corresponding dual heating flue through the (middle) top plate 5.7. The differential heat exchanger 5.6 is independent of the circulating flow 9.

In order to improve the clarity, the illustration of the central part of the furnace arranged below the burner plane 5.4 was intentionally omitted. The gas supply and volume flow adjustment can be performed in the middle part.

Figures 2, 3, 4, 5, 6, 7 show various measures according to the invention for optimizing the temperature distribution in the corresponding heating tube groove. Each measure is explained in more detail in FIGS. 8A, 8B, 8C, 8D, 8E.

The coke oven device 10 having a furnace chamber 10.2 (especially having a horizontal cavity) has a plurality of dual heating flues 13, each flue having a burning heating tube slot 11 and an exhaust gas guide tube slot 12. The heating tube groove through its inner wall 11.1 defines a heating flue for conducting gas. Each heating tube groove is mutually defined by a partition (bonded wall) 14 having a coupling channel 14.2 and a partition partition 14a having no channel. In each case, at least one staged air tube slot 14.1 is provided in the partitions 14, 14a, respectively, with one or more combustion stages 14.11, or from/to the inlet or outlet of the heating tube slot, respectively. The staggered brick-walled wall 15 delimits the furnace chamber and the heating tube groove in the y direction.

The gas can flow into the corresponding heating tube slots through the multiple inlets 16, 17, 18, especially for the coke oven gas heating through the first combustion air inlet 16, through the additional combustion air inlet especially for the mixed gas heating 17 and respectively through the coke oven gas inlet 18 or coke oven gas injection mouth. The incoming and recirculating gases rise or fall in a central manner, respectively, and flow through the corresponding heating pipes and grooves on the inner surfaces 14.3, 15.1 of the corresponding partitions or staggered brick-walled walls, respectively.

One of the measures according to the invention is mainly shown in FIG. 2. The circulation flow 19 is formed by a plurality of circulation flows that flow around each other on a plurality of paths. 2 shows an external circulation flow path 19.1, which defines and flows in a layered manner around two more inward circulation flow paths 19.2, 19.3, wherein the internal circulation flow paths 19.2, 19.3 pass through the corresponding additional exhaust gas The circulation channel is defined by 14.2.

Figure 2 shows an arrangement with three circulation flow paths 19.1, 19.2, 19.3, which surrounds a staged air outlet 14.11, which is arranged at least about half of the height position in the heating tube groove. The staged gas G5 flows out of the staged gas outlet 14.11. Multiple stepped air outlets can also be optionally provided, especially also above the innermost circulation flow path 19.3. The optimization of the flow and heat distribution here can be carried out mainly through the recirculated gas G4 in the base area and in multiple height positions above it.

Figure 3 shows an arrangement with more than three circulation flow paths, where the number of lower channels is greater than the number of upper channels. The optimization here can in particular be carried out mainly in the base region via the recirculated gas G4 without entering the stepped gas in a stepped manner. In the head region of the heating tube groove, a differential heat exchanger 5.6 is provided, which can be switched independently of the corresponding circulating flow, for example by means of sliding bricks.

Figure 4 shows an arrangement with more than three circulating flow paths, where the number of lower channels is significantly greater than the number of upper channels. In particular, six lower channels (or pairs of channels) are provided at six different height positions. The lower channels are all set below the staged air outlet 14.11 of the center staged air tube slot. The six lower channels are arranged in pairs to be adjacent to the stepped air tube slots, and the upper channels are arranged individually and centrally. A single central lower channel is arranged above the stepped air outlet. In this kind of In the case of an arrangement, a particularly wide central dual-flow flow path is generated from the bottom to the top, the latter further supplementing the stepped gas and the recycled gas introduced in a central manner.

The cross-sectional area Q14 of the corresponding coupling channel 14.2 on the inner surface facing the heating tube groove will be described with reference to FIGS. 5, 6, and 7. The cross-sectional areas Q14 of the channels 14.2 disposed above the stepped air tube groove 14.1 are wider or slimmer than the cross-sectional areas Q14 of the channels 14.2 disposed laterally next to the stepped air tube groove 14.1, respectively.

Fig. 5 shows a device with multiple central stepped air outlets 14.11 and channels with different cross-sections compared to Fig. 4, the lower channel is at least partially elongated in the z direction, and the upper channel is elongated in the x direction. In the case of this change, the stepped air tube groove is composed of a plurality of lower channels on both sides, but it is not a pair. The number of lower channels on one side is not equal to the number of channels on the other side. The channels elongated in the z direction achieve an advantageous relative arrangement, the latter being especially central to a large extent (relatively small spacing d2), and especially in the case of optimized flow profiles. The relatively large cross-section Q14 of the channel shown on the right enables a strong flow effect of the incoming gas G1, especially through a large height portion.

FIG. 5 shows the mutual distance d2 in the x direction between the inner side wall/edge of the corresponding channel 14.2 and the outer side wall/edge of the stepped air tube groove 14.1, which is specifically arranged to be centered in the heating flue. The distance d2 according to the invention is very small, in particular 30 to 100 mm, preferably 50 to 70 mm. According to the invention, the channels 14.2 (especially in the case where the center of the stepped air tube groove 14.1 is arranged) can be positioned as close to each other as possible in the x direction.

FIG. 6 shows an arrangement with two stepped air tube slots, which lead to the heating tube slots at multiple height positions, respectively. All lower channels 14.2 below the uppermost stepped air outlet are centrally arranged, especially symmetrical with respect to the median longitudinal axis. The other two pairs of lower pass The channels (four channels) are provided at the width position (x) above the staged air inlet 14.11, and the width position (x) at least approximately corresponds to the width position of the staged gas outlet 14.11. The paired channels may also be arranged at multiple height positions, or may be directly adjacent to each other laterally.

Alternatively, the lower channel may be constructed narrower than the upper channel and/or narrower than the uppermost lower channel. The uppermost lower channel may also be arranged as a single channel (unpaired), and arranged in the width position in such a way that the stepped gas can flow/follow the corresponding channel and mix with the recirculated gas.

FIG. 7 shows an arrangement with two stepped air tube slots, which at the height position between the respective lower channels 14.2 together centrally lead to the heating tube slot, with the corresponding step The air tube slot is optionally provided with additional separate stepped air outlets. The central stepped air inlet 14.11 extends in particular in width, which completely overlaps the lower channel above it. The lower channels are arranged to be offset from each other with an offset of x2 in the x direction. The offset x2 also provides the advantage of a particularly wide uniform flow (no more intense flow core), especially if the channel 14.2 is relatively wide in the x direction. Therefore, the circulation flow can be designed to make it more uniform. Multiple upper channels can optionally be provided. This offset can also be provided in the case of the arrangement shown in FIG. 6.

The offset x2 in the x direction is shown in FIG. 7. This offset between adjacent channels 14.2 is in particular 50 to 100 mm and provides the advantage of positive heat distribution.

Figures 2, 3, 4, 5, 6, 7 all show the recirculation of a circulating flow path with a complete circumference. The lower channel or multiple lower channels can be optionally omitted, especially when the measures described herein, in a single dual-heated flue or in the entire furnace installation, are or must be a circulation flow path independent of the complete circumference Time.

The pitches and relative positions of the various inlets and channels according to the present invention will be described below through another exemplary embodiment with reference to FIGS. 8A, 8B, 8C, 8D, and 8E.

The inlets 16, 17, 18 are arranged opposite to each other, and are spaced from the median longitudinal axis in the x direction to be as close as possible to the staggered gaps shown schematically in (some of the heating tube grooves) in FIG. 8A顺砖式组合的墙15。 Brick wall 15 along the brick type. This arrangement can be selected or changed in each heating tube slot.

As shown in FIG. 8B, the inlets 16, 17, 18 in the x direction are arranged farther than the channel 14.2. The channels are arranged at a mutual distance d14, which is smaller than the inlet distance d15.

As shown in FIG. 8C, the staged gas G5 flows furthest in the center to the center, further outwards with laminar flow on both sides of the recirculated gas G4, which in each case further outwards has the incoming gas G1 Laminar flow of G1a and G1b. In order to improve the clarity, the angle α shown in FIG. 8C, especially related to the coke oven gas inlet 18, is set to be exaggeratedly enlarged. According to the invention, the angle α can be particularly small, in particular converging towards zero, or 0°. Depending on the design embodiment of the central part, angles in the range of 5 to 10° can also be a reasonable compromise between the additional effort in construction and plant technology and the fluid effect achieved.

In terms of arrangement, number and geometry, the channels 14.2 or the stepped gas inlet 14.11 shown in FIG. 8C can be varied according to the variants discussed in FIGS. 2 to 7. As can be seen from the respective gas flows G1, G1a, G4, and G5 shown in FIG. 8C, according to the present invention, gas flow separation or parallel flow can be achieved at least at specific height portions, respectively.

The mutual distance d14 of the channels 14.2 in the x direction is relatively small, especially less than 50%, 45%, 40%, 35% or 30% of the width (x) of the heating tube groove. The distance d15 between the coke oven gas inlet 18 and the other inlets 16 and 17 in the x direction is relatively large, especially larger than 70%, 75%, 80% or 85% of the heating tube groove width (x). The spacing d15 is significantly larger than the spacing d14, especially at least 35%, 40%, 45 %, 50%, or 55%. The distance x14 between the corresponding channel 14.2 and the inner wall of the staggered brick-walled wall 3 is relatively large, especially greater than (35%, 40%) of the width (x) of the heating tube groove (in the case of a channel) Or 45%. The distance x14 is particularly preferably at least greater than 40% of the heating tube groove width (x), especially in the base area. The spacing x16, x18 of the inlets 6, 8 from the staggered brick-walled wall 15 is relatively small, especially less than 20%, 15%, or 10% of the width (x) of the heating tube groove. The spacing x16, x18 is smaller than the spacing x14 in each case. In particular, the pitch x14 is at least twice or at least three times the size of the pitch x16, x18.

Each gas flow will be described below with reference to FIGS. 8B to 8E. According to the invention, the corresponding gas flow path GP1 respectively identifies the inflow path or flow path of at least one gas G1 introduced through the inlet. According to the invention, the corresponding gas flow path GP4 identifies the flow path of the recirculated exhaust gas/flue gas G4, and according to the invention, the corresponding gas flow path GP5 identifies the flow path of the gas G5 introduced in a stepwise manner.

The inflow angle α shown in FIGS. 8C, 8E, especially for coke oven gas, is preferably less than 30°, in particular less than 10° relative to the z axis in each case. The inflow angle α can also be implemented in a similar manner for the additional inlets 17,18.

In particular, the corresponding y-position of each inlet can be central.

The distances and relative positions mentioned in the context of the respective inlets and channels can also be reciprocated with the distances and relative positions of the corresponding gas flow path/circulation flow path at least in the upstream part which is subsequently mixed with the adjacent gas flow Related.

The cross section of the channel in the y-z plane is shown in FIG. 9. The recirculated gas G4 emitted from above flows through the corresponding lower channel 14.2 and also flows out towards the top again. The gas G4 here flows in a layered manner around the two circular flow edges 14.21 and flows over the two sharp flow edges 14.22. The partition 14 defines a channel at the top through the downward convex curvature. This facilitates low flow resistance. The partition 14 also defines the bottom Channel. The current circulating flow with a very tight radius can therefore flow through the channel and be transferred to the top without any strong turbulence. One or more sharp edges 14.22 may define the flow to the bottom. By entering new gas, this type of flow optimization can also achieve good results. In particular, the recirculated gas G4 does not generate any turbulence, or only a slight turbulence, so that the flow distribution can be effectively optimized through the inlet.

FIG. 10 schematically shows that the coke oven device 10 may have a control unit 20 designated for controlling/regulating one of the volume flows V(t) as described above, in particular at least the volume flow G1 G1a, G1b, G4, G5, G6. Controlling and setting the volumetric flow can affect the flow and temperature distribution in the corresponding heating tube slots 11,12. Therefore, NOx emissions can also be set indirectly through volume flow.

11 and 12 show a modification of the exemplary embodiment shown in FIG. 5. Some lower channels arranged above the uppermost stepped air outlet in FIG. 11 are configured in pairs, wherein a single relatively large, relatively wide lower channel is provided.

Only two recirculation channels are provided between the lowermost stepped gas opening in FIG. 12 and the burner plane, especially at a relatively high height position greater than 500 mm. This makes it possible to omit channels arranged further down in the base area.

The positions of the channels shown in FIGS. 2 to 12 are shown in an exemplary manner. Each entrance can be set and aligned independently of the other entrances. The exemplary embodiments shown can also be varied in particular by changing the arrangement of the lower channels or by assigning individual or all lower channels.

Changes in the arrangement and size of the channels can be performed, in particular channels arranged above the uppermost staged air outlets and/or channels arranged at height positions between the individual staged air outlets, especially with reference to FIGS. 5, 6 , 11, 12 exemplary embodiments, in each case through Change to a channel. In particular, in the case where the channels are further repositioned upwards to a height range higher than 500 mm, some or all of the channels provided in the base area can also be omitted. The number of stepped air outlets or the number of height positions with stages is not limited to the variants shown.

10.2‧‧‧furnace room

11‧‧‧Burning heating tube slot (vertical heating flue)

12‧‧‧ Waste gas guide pipe groove (vertical heating flue)

13‧‧‧Double heating flue (two vertical heating flues are arranged in pairs)

14.1‧‧‧Tube groove or stepped air tube groove on the partition

14.2‧‧‧Channels coupling two heating tube slots

14.3 The inner surface of the separator

15‧‧‧ Staggered brick wall

15.1‧‧‧The inner surface of the staggered brick wall

16‧‧‧(1) Combustion air inlet, especially for coke oven gas heating

17‧‧‧Additional combustion air inlet or mixed gas heating inlet

18‧‧‧Coke oven gas inlet or coke oven gas nozzle

d14‧‧‧ The space between the dual heating flues according to the invention in the x direction of the channel 14.2

x‧‧‧horizontal direction (width or length)

y‧‧‧Depth or horizontal spray direction

z‧‧‧Vertical direction (vertical axis)

Claims (14)

A coke oven device (10) for producing coke through coking coal or coal mixture, wherein the coke oven device is specifically used to minimize the emission of nitrous oxide, which is a measure through the inside of the coke oven device by Coke oven inherent gas (G1, G4, G5), through the internal heat balance of energy to minimize the emission of nitrous oxide, the coke oven device has a plurality of dual heating flue (13), each heating flue has A heating tube groove (11) for gas combustion, and a downwardly injected exhaust gas guide the heating tube groove (12), which in each case are defined in pairs with each other through a partition (14), and It is separated from the corresponding furnace chamber (10.2) by two staggered brick walls facing each other, which are used in pairs for internal exhaust gas recirculation (19) on the external circulation flow path (19.1) The heating tube slots are in each case fluidly connected to each other at the upper and lower ends by means of an upper coupling channel (14.2) and optionally also by a lower coupling channel, wherein the base of the corresponding dual heating flue (5.4) In the lower region, at least one inlet selected from the group of coke oven gas inlet (18), combustion air inlet (16), mixed gas inlet (17) is provided in each case, characterized in that it corresponds to the heating tube slot The width (x) of at least one exhaust gas recirculation channel (14.2) is more central than at least one inlet (16, 17, 18), and defines a more central flow path (GP4) through at least one incoming gas ( G1, G5) flows around the flow path (GP4); wherein the corresponding exhaust gas recirculation channel (14.2) has at least one circulating flow edge (14.21) and/or convex curvature; and/or wherein the corresponding exhaust gas recirculation channel Have at least one sharp flow edge (14.22) and/or concave curvature; and/or corresponding exhaust gas The circulation channel (14.2) has at least one surrounding flow contour with at least one radius and at least one sharp flow edge. The coke oven device according to claim 1, wherein all exhaust gas recirculation channels (14.2) are arranged more centrally than at least one inlet (16, 17, 18) with respect to the width (x) of the heating tube groove. The coke oven device according to claim 1 or 2, wherein the corresponding combustion air inlet (16) and/or the corresponding mixed gas inlet (17) and/or the corresponding coke oven gas inlet (18) have a maximum of 0.06 m ² And/or where the corresponding lower and/or upper exhaust gas recirculation channels (14.2) have a cross-sectional area greater than 0.005m ² , and/or where the combustion air inlet (16) and/or mixed gas inlet ( 17) and/or the coke oven gas inlet (18) are aligned at an angle (α) of 0° or less than 30° with respect to the central longitudinal axis of the heating tube slot. The coke oven device according to claim 1, wherein the corresponding partition (14) has at least one additional coupling lower and/or upper channel (14.2), which is disposed closer to the external circulation flow path (19.1) A more central height position of the height of the heating tube trough and is specifically used to form the internal inert intermediate layer (GP4) on the central flow path; and/or wherein the corresponding partition (14) has at least one additional The lower and/or upper coupling channel (14.2), which is arranged at a more central height position closer to the height center of the heating tube groove than the external circulation flow path (19.1), and is specifically used for an additional internal circulation flow To form an internal inert intermediate layer on an internal circulation flow path (19.2, 19.3). The coke oven device according to claim 1, wherein at least one stepped air tube slot (14.1) is arranged in the partition plate (14), and the air tube slot (14.1) has at least one stepped air The inlet (14.11); or wherein at least two staged air tube slots (14.1) are arranged in the partition (14), the staged air tube slots (14.1) are connected to the upper/uppermost exhaust gas recirculation channel (14.2) ) Above, and an uppermost stepped air inlet (14.11) above all exhaust gas recirculation channels (14.2) leads to the combustion heating tube slot (11); and/or at least one of the partitions (14) At least two tiered air tube slots (14.1) are arranged in the tier, the tiered air tube slots (14.1) are above the upper/uppermost exhaust gas recirculation channel (14.2), and two The uppermost stepping air inlet (14.11) leads to the burning heating tube slot (11). The coke oven apparatus according to claim 1, wherein at least one inlet includes an inlet nozzle, and leads to the heating pipe groove (11, 12) at a height position of 0.0 to 0.45 m above the base of the heating pipe groove. An operation method of a coke oven device (10) for producing coke through coking coal or coal mixture, and through the measures inside the coke oven device by coke oven inherent gas (G1, G4, G5) Minimizing nitrous oxide emissions through internal heat balance energy is used to operate the coke oven device according to any one of claims 1 to 6, wherein one of the coke oven devices has a corresponding dual heating flue ( 13) With a burning heating tube groove (11) and an exhaust gas guide tube groove (12), an internal exhaust gas recirculation (19) on an external circulation flow path (19.1) around a partition plate (14) penetrates At least one coupling channel (14.2) passing through the partition (14) is set, wherein in the lower region of the base (5.4) of the corresponding dual heating flue, at least one selected from coke oven gas (G1a), combustion The gas of the group of air (G1) and mixed gas (G1b) enters, It is characterized in that the exhaust gas recirculation (19) on one/the circulation flow path (19.1, 19.2, 19.3) or at least one central flow path (GP4) is guided in each case to compare with the incoming gas (G1a, G1, G1b) are more central; wherein the corresponding exhaust gas recirculation channel (14.2) has at least one circulating flow edge (14.21) and/or convex curvature; and/or wherein the corresponding exhaust gas recirculation channel (14.2) has at least one sharp flow edge (14.22) ) And/or concave curvature; and/or wherein the corresponding exhaust gas recirculation channel (14.2) has at least one surrounding flow profile having at least one radius and at least one sharp flow edge. The method of claim 7, wherein at least one additional internal circulation flow (19.2, 19.3) is set and is set more centrally than the incoming gas (G1) and more than the external circulation flow path (19.1) Inwards, and therefore defined by this external circulation flow path. The method according to claim 7 or 8, wherein, in the case of rich gas heating or mixed gas heating, internally recirculated on the circulating flow path or a plurality of circulating flow paths (19.1, 19.2, 19.3) The proportion of exhaust gas is set to more than 50%; and/or where the method for rich gas heating is essentially the use of coke oven gas, or the use of lean rich gas with a reduced low heating value below 17000 kJ/Nm ³ ; or where it is used for mixed gas The method of heating is essentially the use of a mixture of blast furnace gas, coke oven gas and optional reformer gas; or wherein the method is performed with natural gas as at least a partial replacement of coke oven gas. The method according to claim 7, wherein a sub-stoichiometric combustion ratio <0.9 is set in the burner plane (5.4) of the base of the corresponding heating tube groove (11, 12). The method according to claim 7, wherein by means of the recirculated exhaust gas (G4), the incoming gas (G1) and a stepped air tube slot (14.1) or gas from the stepped air tube slot ( G5) An intermediate layer is arranged between 5% to 75% or 15% to 50% of the height of the heating tube groove, or within the height range of 0.25 to 4m height; and/or by means of For the incoming gas (G1), an air blanket is arranged between the corresponding staggered brick-like masonry wall (15) and the circulating flow path or the circulating flow paths (19.1, 19.2, 19.3). The method according to claim 7, wherein the amount of gas introduced between a first stage and a second stage (z4) is introduced through the combustion air and mixed gas inlets (16, 17) on the base (5.4) The ratio of the amount of gas is set to 50:50, or the ratio of the first stage is lower; and/or the volume flow ratio in which the heating tube groove (11,12) is introduced is set as follows: through the combustion air inlet (16)<30 %, through the mixed gas inlet (17)<30%, through the recirculation channel>40%, and optionally at least one stepped gas inlet (14.11); and/or where it is introduced at the combustion air inlet and the mixed gas inlet The volume flow of the furnace chamber is set to be between 45% and 55% of the volume flow introduced through the recirculation channel and optionally at least one stepped gas inlet. A control device (20) designated for performing the method according to any one of claims 7 to 12, wherein the volume flow (G1, G4, G5) introduced into the heating tube grooves (11, 12) is Set according to the ratio of claim 12. A use of rich and poor gas having a reduced low heating value is to operate a coke oven device according to the method described in claim 7, or a coke oven device according to claim 1.

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