Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
  • F23D—BURNERS
  • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
  • F23D14/46—Details, e.g. noise reduction means
  • F23D14/84—Flame spreading or otherwise shaping
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
  • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
  • F23M9/00—Baffles or deflectors for air or combustion products; Flame shields
  • F23M9/08—Helical or twisted baffles or deflectors

Definitions

• the invention relates to a combustion chamber of an industrial heating boiler that can be heated with a combustion device, with a static flow mixing device, comprising at least one static mixer element and at least one base plate, with which the at least one static mixer element can be connected, the static mixer element comprising a base body with a material thickness made of a heat-resistant material is formed and having a through channel, wherein
• the through-channel runs in its longitudinal axis direction from a front side of the base body, the so-called inflow side, through the base body to a rear side of the base body opposite the inflow side, the so-called outflow side, the through-channel with its inlet opening being essentially centrally located on the inflow side of the static mixer element is positioned and where
• spaced-apart flow guide elements are arranged on the inflow side, which are each in the form of flat guide vanes that protrude from the inflow side, and which each run from an edge section of the inlet opening of the through channel in the distal direction to the outer edge of the inflow side, whereby
• a swirl surface is arranged which is recessed compared to the flow control elements and slopes downwards towards the outer edge of the inflow side, with the flow control elements being increased by one guide vane height in comparison to an adjacent swirl surface, with the at least one base plate having a or has a plurality of recesses for receiving a base section of a static mixer element in a form-fitting manner.
• heating boilers or steam boilers with a combustion chamber known as a flame tube are known from the prior art, which are also known as flame tube smoke tube boilers or shell boilers.
• a boiler type is used as an industrial boiler wherever the supply of heating water and/or process steam for industrial applications is required.
• such boilers or steam boilers can provide thermal output of up to around 40 MW (megawatts).
• heating boiler for the supply of heating water at temperatures of up to around 80°C and of a steam boiler for the provision of process steam, for example at temperatures of 180°C and Steam pressures of 10 bar, for example.
• steam boiler for the provision of process steam, for example at temperatures of 180°C and Steam pressures of 10 bar, for example.
• industrial heating boiler below includes both the heating boilers mentioned above and corresponding steam boilers for the supply of process steam.
• Such industrial heating boilers usually comprise a horizontally arranged, tubular or cylinder-shaped combustion chamber, on the first end of which or
• Cover surface protrudes a burner device in the flame tube. Firing is usually done with natural gas or fuel oil.
• a so-called turning chamber On the front side or top surface of the flame tube opposite the burner device there is a so-called turning chamber, in which the fuel gas or flue gas from the flame tube is deflected in the longitudinal direction of the industrial boiler and enters a so-called second flue gas flue, which is usually designed as a tube bundle heat exchanger.
• the flue gas can also be deflected several times in the longitudinal direction of the industrial boiler.
• a so-called 3-pass flame tube boiler comprises a second and a further, third flue gas pass downstream in the flow direction of the flue gas, which is also usually designed as a tube bundle heat exchanger.
• Such heat storage elements are intended to delay the cooling of the combustion chamber by dissipating heat, but have the disadvantage that such heat storage elements only act as displacement bodies within the combustion chamber and impede the flow of the flue gas within the combustion chamber or can lead to a high pressure loss in the combustion chamber, as well as a reduction in the combustion chamber volume relevant for combustion. This is problematic insofar as the discharge of the flue gas in the downstream chimney can be impaired due to an excessive pressure loss due to installations in the combustion chamber and subsequently the operation of the boiler is disrupted by such installations.
• the complete combustion process can be negatively influenced due to the reduced free combustion chamber volume.
• the hot fuel gas stream from the burner device is turbulently swirled when it hits such a heat storage element standing transversely in the direction of flow inside the combustion chamber, but the flow around and swirling of the gas stream is undirected and random.
• Another disadvantage is that when using heat storage elements made of a refractory fireclay material, such as an oven insulation of a boiler, such a heat storage element absorbs the exhaust heat of the flue gas flow only very slowly.
• An estimate of the transient heat conduction in a heat storage element can be determined using the combination of Biot number (Bi), Fourier number (Fo) and the dimensionless mean temperature (0) in the heat storage element.
• the Biot number reflects the ratio of the thermal resistance within a solid body to the convective heat transfer resistance in the surrounding fluid. With large Biot numbers (Bi »1), the convective heat transfer becomes so large that the surface temperature of the body corresponds to the temperature of the surrounding fluid and, due to the low heat conduction in the solid body, shows a clear gradient to the temperature inside the body.
• Another disadvantage is that if several such heat storage elements are arranged one behind the other in the flow direction of the flue gas within the combustion chamber, the downstream heat storage elements are positioned in the flow shadow of the first heat storage element that is subjected to the frontal flow, which is why the downstream heat storage elements, in particular made of refractory material, are heated even more slowly than the frontal or first heat accumulator element in the direction of flow.
• the combustion chamber or the flame tube must in any case be operated without internal installations in the form of such heat storage elements.
• the object of the present invention is to overcome the disadvantages of such heat storage elements which have become known from the prior art and to provide a static mixer element which is suitable for use in a combustion chamber of a generic industrial heating boiler and which can be used during operation of an industrial heating boiler which is equipped with a equipped with the static mixer element according to the invention within its combustion chamber, the following advantages can be achieved in comparison to a combustion chamber without internals:
• the static mixer element in a static mixer element for use in a combustion chamber of an industrial heating boiler that can be heated with a burner device, the static mixer element comprises a base body with a material thickness which is formed from a heat-resistant material and which has a through-channel, the through-channel running in its longitudinal axis direction from a front side of the base body , the so-called inflow side, through the base body to a rear side of the base body opposite the inflow side, the so-called outflow side, the through-channel with its inlet opening being positioned essentially centrally on the inflow side of the static mixer element and several spaced-apart flow guide elements being arranged on the inflow side , which are each in the form of flat vanes, which protrude from the inflow side, are formed, and which each starting from an edge portion of the unit opening of the through-channel run in the distal direction up to the outer edge of the inflow side, with a swirl surface being arranged between two flow guide elements, which is recessed compared to the flow guide elements and inclined
• a static mixer element Due to its structured inflow side with a plurality of flow elements and intermediate swirl surfaces, a static mixer element according to the invention offers the additional advantage that the inflow side has a high specific surface area for a gaseous medium or a fuel gas to flow around.
• specific surface area means the sum of all interfaces between the structured base body, in particular on its inflow side, and a gaseous phase, i.e. the fuel gas flowing around a static mixer element, in relation to the volume of the static mixer element (m 2 surface / m 3 volume).
• the term "structured" inflow side is used synonymously with a high specific surface area.
• flow guide element is generally understood below to mean elevations in the form of flat guide vanes, which protrude from the inflow side and which impart a directed twisting movement to an inflowing gaseous medium or here to the fuel gas within a combustion chamber of an industrial boiler imprint.
• the static mixer element is expediently positioned within a gas flow in such a way that the inflow direction of the combustion gas essentially corresponds to the direction of the longitudinal axis of the through-channel.
• the structured inflow side of the static mixer element is aligned essentially transversely to the inflow direction of the fuel gas.
• Such flow guide elements can be designed, for example, as straight or curved ribs or webs, or as straight or curved blade sections. According to the invention, the flow guide elements each run in the distal direction or in the radial direction, starting from the through-channel towards the outer edge of the inflow side.
• the swirl surfaces arranged between the flow guide elements are set back somewhat in the inflow direction of the combustion gas compared to the elevations of the flow guide elements and inclined by an angle of inclination a relative to a frontal plane of the inflow side, falling obliquely to the edge of the inflow side.
• This means that hot combustion gas flowing in the direction of the longitudinal axis of the passage channel is deflected outwards by the static mixer element in the distal or radial direction when it hits one of the sloping swirl surfaces and hits the combustion chamber wall of the industrial heating boiler distributed as evenly as possible over a wide area.
• the swirl surfaces are inclined at an angle of inclination ⁇ of 20° to 70°, preferably 30° to 60°, particularly preferably 45°, towards the outer edge of the inflow side.
• the through-channel has a through-channel length which essentially corresponds to the material thickness of the base body, and the several flow guide elements each have the material thickness of the base body at least in sections, with the recessed swirl surfaces in sections of the base body having a reduced material thickness are arranged.
• the through-channel with a through-channel length that essentially corresponds to the material thickness of the base body is implicitly essentially perpendicular to the inflow side of the base body.
• the onflow side of the base body is thus essentially transverse to the onflowing side Combustion gas and flows evenly around it.
• a swirl flow can thus be imparted particularly effectively to the inflowing combustion gas by the flow guide elements.
• the swirl surfaces which slope downwards in the outflow direction and are located in indentations in the base body or in indentations on the inflow side, are also subjected to a uniform flow of fuel gas in this design and ensure a uniformly directed deflection of the combustible gas along the edge of the inflow side in a lateral direction.
• the entire inner surface of the combustion chamber is advantageously evenly charged with hot combustion gas deflected by the swirl surfaces.
• the plurality of flow guide elements on the inflow side of the static mixer element can each be designed in the form of curved guide vanes with a radius of curvature.
• the desired twisting movement which is imposed on the fuel gas flow when it flows around at least one static mixer element, which is positioned inside a combustion chamber of an industrial boiler, can be precisely set or calculated.
• the pressure loss which can increase as a result of the flow around the static mixer element with a rotating swirl movement, must be taken into account.
• a static mixer element according to the invention can be particularly effective if the flow guide elements each have a variable guide element height in relation to the respective adjoining swirl surfaces, the guide element height increasing along a guide element length from the passage channel to the outer edge of the inflow side. With increasing guide element height, an increased swirl flow can be applied to the deflected portion of the fuel gas.
• the guide element height on the inside of the guide elements adjacent to the passage channel can be 20% to 50% of the material thickness of the static mixer element and/or the guide element height on the outside of the guide vanes adjacent to the edge of the inflow side can be 50% up to 100% of the material thickness of the static mixer element.
• the degree of deflection of the medium flowing towards the combustion chamber wall can be regulated or optimized by suitably selecting the height of the guide elements and/or the angle of inclination of the swirl surfaces.
• a static mixer element can have a base section with bearing surfaces on its underside and on its upper side have an edge of the inflow side with a round, preferably semi-circular, edge contour.
• the use of a base section increases the stability of a static mixer element. This is particularly advantageous because of the dynamic pressure that occurs during operation, which is generated by the fuel gas flowing around a static mixer element.
• a round, preferably semi-circular edge contour in the area of the upper side of a static mixer element offers the advantage of the most uniform possible gap spacing between the combustion chamber wall and the edge of the inflow side of the static mixer element during operation when installed transversely to the direction of flow of the combustion gas within a substantially cylindrical flame tube or a corresponding combustion chamber to offer.
• a static mixer element is expediently set up in the operating position within the combustion chamber of a boiler transversely to the direction of flow of the hot fuel gas.
• a static mixer element can be designed in one piece and preferably include an expansion joint with a joint width that extends from the passage channel to the edge of the inflow side through the entire material thickness of the static mixer element. If necessary, an expansion joint can be used to prevent thermal stresses from building up in a static mixer element during operation, which could possibly lead to cracks in the base body.
• a static mixer element can be designed in two parts or in several parts, with the individual parts of the static mixer element being able to be connected to one another in a form-fitting manner using plug-in connections.
• Such plug-in connections can, for example, comprise pin-shaped connecting elements which are arranged on one of the parts of the static mixer element and which are provided in corresponding recesses on another part of the two-part or multi-part static mixer element.
• the configuration as a two-part or multi-part static mixer element is advantageous in particular in the case of larger static mixer elements which, for example, have a diameter or a width on the inflow side of 500 mm or 600 mm.
• the assembly of such a static mixer element in its operating position within a combustion chamber of an industrial heating boiler is considerably facilitated by the multi-part structure, since the static mixer elements can become very heavy with increasing size.
• the through-channel can have an inlet opening with a free cross-sectional area and an inner diameter on the inflow side and one on the outflow side
• a diffuser section with a diffuser angle ß in relation to the outflow side the diffuser section extending to the outlet opening of the through-channel on the outflow side and an inner diameter at the outlet opening being larger than the inner diameter at the inlet opening.
• the divergent diffuser section widening towards the outlet opening in the flow direction of the fuel gas can have a diffuser angle ⁇ of 90° to 160°, preferably 120°, and can be modeled on the diffuser of a Laval nozzle.
• the through-channel has one or more connecting devices on the inflow side for the captive attachment of corresponding coupling elements of an adjustment ring within the through-channel.
• Two longitudinal slots which are arranged on opposite wall sections and in the direction of the longitudinal axis of the through-channel and which serve as guides for a plug-in connection, can preferably be provided as parts of the connection device.
• two longitudinal slits running in the direction of the longitudinal axis and arranged on opposite wall sections of the through-channel together with transverse slits respectively downstream of the longitudinal slits can also be provided, with the transverse slits being positioned transversely thereto at the end of the longitudinal slits.
• These longitudinal slots and downstream transverse slots can serve as guides for a lockable plug-in connection, for example in the form of a bayonet lock, and can be provided as parts of the connection device for fastening an adjustment ring within the through-channel.
• a static flow mixing device which is suitable for use in a combustion chamber of a heating boiler and which comprises at least one static mixer element and at least one base plate to which the at least one static mixer element can be connected.
• the at least one standing plate has one or more recesses for receiving a base section of a static mixer element in a form-fitting manner.
• a static flow mixing device can also include a base plate, which can be positioned at the bottom, i.e. below the base plate, and which expediently has base feet to compensate for any unevenness and allows the static mixer elements to be positioned exactly horizontally in the operating position within a cylindrical combustion chamber.
• a static flow mixing device can optionally also comprise one or more base plates, which can be placed between the base plate and a base plate if necessary.
• a static flow mixing device can have multiple components comprise, which can be connected to each other in the form of a stack and which can be used to adjust the height of the at least one static mixer element in its operating position within a combustion chamber of a boiler.
• One or more components, which the set includes a static flow mixing device can expediently also be designed in such a way that they can be positively connected to one another and, in the event of a turbulent flow of hot combustion gas within the combustion chamber, are connected in a stationary manner in their relative position in the assembly of the components.
• a static flow mixing device which also includes at least one adjustment ring with a longitudinal axis direction, an outer diameter and a free inner diameter
• the at least one adjustment ring can be fastened, preferably coaxially, on the inflow side within the through-channel of a static mixer element.
• the free inner diameter of an adjustment ring defines its inner free cross-sectional area.
• the free cross-sectional area of the through-channel can be changed or reduced by inserting an adjusting ring into the through-channel.
• the flow profile or the flow cross section in the through-channel of a static mixer element can be adjusted in a particularly simple and cost-effective manner.
• the base body of the static mixer element can, for example, be manufactured in large numbers in a specific geometry and size to match the combustion chamber dimensions of a defined industrial heating boiler.
• the at least one adjustment ring can expediently have external coupling elements, the at least one adjustment ring being captively fastenable on the inflow side within the through-channel of a static mixer element, preferably on connecting devices within the through-channel.
• an adjustment ring can be attached particularly easily and securely within the through-channel.
• the inserted adjusting ring can also support the individual parts of the static mixer element statically and improve the overall stability of the structure of such a static flow mixing device.
• two or more static mixer elements in a static flow mixing device, can be fastened one behind the other on one or more base plates, with the passage channels of the two or more static mixer elements preferably being arranged coaxially one behind the other, and with at least those downstream of a first static mixer element on the inflow side Static mixer elements, preferably all static mixer elements, are each equipped with an adjustment ring fastened in their respective through-channel.
• the two or more adjustment rings can be arranged such that the inner diameters of the adjustment rings decrease in the static mixer elements arranged one behind the other on the outflow side.
• the inside diameters of the adjustment rings are therefore smaller on the outflow side, viewed in the inflow direction of the combustion gas.
• the use of different inner diameters means that the fuel gas flowing along the horizontal axis of the combustion chamber is distributed over a number of static mixer elements.
• a combustion chamber of an industrial heating boiler that can be heated with a combustion device can be specified with a static flow mixing device according to the invention, the flow mixing device being positioned in the combustion chamber in such a way that the inflow side of the at least one static mixer element is essentially transverse to an inflow direction of a gaseous flow medium is set up, the longitudinal axis direction of the at least one through-channel and/or the longitudinal axis direction of the at least one adjustment ring being arranged parallel to the longitudinal axis direction of the combustion chamber, preferably coaxially with the longitudinal axis direction of the combustion chamber.
• a flow path of the fuel gas flow leads through the one or more through-channels arranged one behind the other several static mixer elements positioned one behind the other, wherein optionally several plug-in rings, the free inner cross-sectional areas of which can preferably taper in the outflow direction.
• One or more further flow paths of the hot combustion gas stream can be defined on the outside when flowing around the one or more static mixer elements, the combustion gas being deflected to the wall of the combustion chamber by hitting the inclined swirl surfaces.
• the guide elements or guide vanes ensure that a controlled turbulent swirl flow is imposed on the fuel gas flow.
• an industrial boiler having a combustion chamber in which a static flow mixing device according to the invention is positioned.
• a combustion chamber in which a static flow mixing device according to the invention is positioned.
• FIG. 1 is an isometric view obliquely from the front of a first variant embodiment of a static mixer element according to the invention
• FIG. 1A shows a detail from FIG. 1 on an enlarged scale
• FIG. 2 shows the static mixer element shown in FIG. 1 in a front view
• FIG. 3 is a sectional view from above according to the section line A-A shown in Fig. 2 of the in
• Fig. 1 shown static mixer element
• Fig. 4 is a sectional side view of the static mixer element shown in Fig. 1 along line B-B shown in Fig. 2;
• Fig. 6 is an isometric view obliquely from the side of a base plate as part of a static flow mixing device according to the invention
• Fig. 7 is an isometric view obliquely from the side of a pedestal as part of a static flow mixing device according to the invention.
• FIG. 8 in an isometric view obliquely from above, a first embodiment of a static flow mixing device according to the invention with two static mixer elements according to FIG. 1;
• - Fig. 9 is an exploded view obliquely from the side of the individual parts of the assembly shown in Fig. 8;
• FIG. 10 is an isometric view obliquely from the side of a second embodiment of a static flow mixing device according to the invention with six static mixer elements positioned one behind the other according to FIG. 1;
• FIG. 11 is an isometric view obliquely from the front of a second variant embodiment of a static mixer element according to the invention.
• Fig. 12 shows in an exploded view obliquely from the side the individual parts of the structure shown in Fig. 11;
• FIG. 14 is an isometric view obliquely from the front of a third variant embodiment of a static mixer element according to the invention.
• Fig. 15 is an exploded view obliquely from the side of the individual parts of the structure shown in Fig. 14;
• FIG. 16 in an isometric view obliquely from above a fourth embodiment of a static flow mixing device according to the invention with two static mixer elements according to FIG. 15;
• FIG. 17 is an exploded view obliquely from the side of the individual parts of the structure shown in Fig. 16;
• the other figures are each schematic representations of CFD calculations, each in diagram form based on the flow velocity (Flow velocity) in [m/s], the heat flux density (Convection_Wall_Heatflux) in [W/m2] and the temperature (Temper ature_Celsius) in [°C] illustrate differences between the flow conditions in a combustor without internals compared to the same combustor with internals in the form of static flow mixing devices according to the invention.
• the heat flux density increased heat transport is represented by negative values, which are illustrated as "white areas" in the following figures. The smaller the local value of the heat flux density, the greater the outward heat flow. Show it:
• - Fig. 21 shows a side view of the course of the temperature in the combustion chamber of the 2 MW
• Combustion chamber of the 2 MW industrial boiler with a fifth embodiment of a static flow mixing device according to the invention which comprises six static mixer elements arranged one behind the other, each with a width of 300 mm;
• Heat flux density at the combustion chamber wall of the 2 MW industrial boiler with the fifth embodiment of the flow mixing device (width of 300 mm);
• - Fig. 24 shows a side view of the course of the temperature in the combustion chamber of the 2 MW
• Combustion chamber of the 10 MW industrial boiler with a sixth embodiment of a static flow mixing device according to the invention which comprises six static mixer elements arranged one behind the other, each with a width of 600 mm;
• Heat flux density at the combustion chamber wall of the 10 MW industrial boiler with the sixth embodiment of the flow mixing device (width of 600 mm); - Fig. 30 shows a side view of the course of the temperature in the combustion chamber of the 10 MW
• Flow velocity in [m/s] during the oncoming flow of a front inflow side of the static flow mixing device in the inflow direction of a gaseous medium according to the sixth embodiment of the invention (width of 600 mm).
• FIGS. 1 to 4 each show different views of a first embodiment variant of a static mixer element 10 according to the invention.
• the static mixer element 10 is made here in one piece from a heat-resistant ceramic material and has a base body with a front side 11, which is referred to below as the inflow side 11, and a rear side 12, which is referred to as the outflow side 12 below.
• the rear outflow side 12 is opposite the front inflow side 11 .
• the inflow side 11 here has an upper or lateral edge 13 with an essentially semicircular contour.
• the static mixer element 10 On its underside, the static mixer element 10 has a base section 14 with a width 15 and bearing surfaces 16. The bearing surfaces 16 of the base section 14 are each inclined here and serve as standing surfaces for the static mixer element 10 in conjunction with a standing plate, such as those in Fig. 7 is shown.
• the base body of the static mixer element 10 has a width 17, a maximum material thickness 18 or initial depth and a height 19.
• the base body of the static mixer element 10 also has a through-channel 20 which, with its inlet opening 21, is positioned essentially centrally on the inflow side 11 of the static mixer element 10 is.
• the through-channel 20 has its outlet opening 22 on the outflow side 12 .
• a free cross-sectional area 23 of the through-channel 20 is essentially circular here with an inner diameter D E of the through-channel 20 in the region of its inlet opening 21 .
• the inlet opening 21 is bordered here by a peripheral edge section 24 or edge web on the inflow side 11, this edge section 24 or edge web having an outer diameter DR.
• the through-channel 20 is designed as a diffuser section 25 from about halfway up to the outlet opening 22, with an inner diameter DA of the diffuser section 25 at the outlet opening 22 being larger than the inner diameter D E of the through-channel 20 in the region of its inlet opening 21.
• a diffuser angle ⁇ is selected here, for example, at 120°.
• the direction of the longitudinal axis 26 of the through-channel 20 is symbolized by a dot-dash line 26 .
• the through-channel 20 thus runs in the direction of the longitudinal axis 26 and with a channel length 27 from the front or inflow side 11 of the base body through the base body to the rear or outflow side 12 of the base body.
• the longitudinal axis direction 26 of the through-channel 20 corresponds to the X-axis direction.
• the Y axis direction indicates the lateral width direction 17 of the static mixer element 10
• the Z axis direction indicates the height direction 19 of the static mixer element 10 .
• the static mixer element 10 is structured on the inflow side 11 and has a plurality of swirl surfaces 28 which are each inclined towards the outer edge 13 of the inflow side 11 at an angle of inclination ⁇ . Furthermore, a plurality of flow guide elements 30 spaced apart from one another are arranged on the inflow side 11 and are each in the form of flat guide vanes 31 which protrude from the inflow side 11 .
• the flow guide elements 30 each run from the edge section 24 of the inlet opening 21 of the through-channel 20 approximately in the distal or radial direction to the outer edge 13 of the inflow side 11.
• the guide vanes 31 have a guide vane width 32 or width 32 of the flow guide element 30 and a guide vane length 33 or length 33 of the flow guide element 30.
• the guide vanes 31 are designed here in the form of curved guide vanes 31 with a radius of curvature 34 .
• the radius of curvature 34 of a guide vane 31 can be specified as a first, somewhat larger radius of curvature R, which is measured at a first flank 35 of the guide vane 31, which is concavely curved.
• R the radius of curvature
• the guide vane 31 protrudes beyond the lower-lying swirl surface 28 adjoining the first flank 35 by an inner guide vane height 36 or guide element height 36, which on the inside of the guide vane 31 adjoins the edge section 24 around the inlet opening 21 of the through-channel 20 is measured.
• An outer guide vane height 37 or guide element height 37 is measured on the first flank 35 on the edge 13 of the inflow side 11 .
• the ratio between the larger radius of curvature R on the first flank 35 and the smaller radius of curvature r on the second flank 38 of the guide vane 31 or the flow guide element 30 depends essentially on the selection of the guide vane width 32 and on the size of the radii of curvature R, r.
• a radius of curvature 34 which is, so to speak, a mean value of the two radii of curvature R and r.
• the guide vane 31 protrudes beyond the lower-lying swirl surface 28 adjoining the second flank 38 by an inner guide vane height 39 or guide element height 39, which on the inside of the guide vane 31 adjoins the edge section 24 around the inlet opening 21 of the through-channel 20 is measured.
• An outer guide vane height 40 or guide element height 40 is measured on the second flank 38 on the edge 13 of the inflow side 11 .
• the flow guide elements 30 are therefore increased by a vane height 36, 37, 39, 40 in comparison to the respective adjoining swirl surfaces 28.
• the material thickness 18 of the base body of the static mixer element 10 is reduced in the region of the recessed swirl surfaces 28 and has only a reduced material thickness 18.1 or 18.2 in the region of the swirl surfaces 28. Due to the recesses in the base body in the area of the inclined swirl surfaces 28, the total weight of the static mixer element 10 according to the invention is reduced in comparison to a base body with a constant material thickness 18 and with a smooth, unstructured front side.
• a static mixer element 10 according to the invention can be produced inexpensively in comparison to an imstructured base body due to the material saved and is easier to handle.
• the static mixer element 10 shown here has an expansion joint 45 with a joint width 46, which extends along the top side of the static mixer element 10 along its entire material thickness 18 from the through-channel 20 to the Edge 13 extends.
• FIG. 18 is intended to illustrate the direction of flow of a gaseous medium, the flue gas, within the combustion chamber of an industrial boiler, not shown here.
• the inflow direction 1 essentially corresponds to the X-axis direction or the initial axis direction 26 of the passage 20.
• such a static mixer element 10 according to the invention is arranged during operation within a combustion chamber of an industrial boiler in such a way that the initial axis direction 26 of the passage 20 is essentially in the inflow direction 1 of the flue gas is oriented.
• the inflow side 11 of the base body is thus essentially transverse to the inflow direction 1 of the flue gas.
• a first flow path 2 of the gaseous medium leads in the direction of the axis of capture 26 through the through-channel 20 of the static mixer element 10 .
• Another second flow path 3 of the gaseous medium shows schematically the course of the flow of the flue gas as it flows around the static mixer element 10 on the outside along the flow guide elements 30.
• the flow path 3 becomes when the gaseous medium hits the blade-shaped Flow guide elements 30 are set in a swirling movement and deflected in the lateral or axial direction from the static mixer element 10 in the direction of an inner wall of the combustion chamber, not shown here, when they hit the swirl surface 28 .
• an inflow plane e is also indicated with a dot-dash contour line.
• the inflow plane e conceptually forms a frontal plane on the structured inflow side 11, in which those contour sections are located which, seen in the inflow direction 1 of the flowing medium in the X-axis direction, are flown against first.
• the inflow plane e comprises those contour sections on the inflow side 11 which protrude farthest from the inflow side 11 as elevations against the inflow direction 1 .
• FIG. 31 and FIG. The swirl surfaces 28 between the guide vanes 31 are located somewhat downstream of the inflow plane e or the frontal plane in the inflow direction 1 or in the direction of the X axis, which is why they are not shown in Figures 31 and 32 either.
• Each adjustment ring 60 is essentially cylindrical and has an outer diameter d A , an inner diameter di and a wall thickness of the cylinder jacket, which from the difference between the outer diameter d A and the inner diameter di.
• Each adjusting ring 60 has an edge 61 on one of the edges of the cylinder jacket, which has an enlarged edge diameter compared to the outer diameter d A and which projects beyond the cylinder jacket of the adjusting ring 60 to the outside.
• a longitudinal axis direction 62 of the setting ring 60 is symbolized by a dash-dotted line 62 .
• a length 63 or depth of the setting ring 60 is measured on the outside away from the edge 61 and indicates the length or height of the cylinder jacket of the setting ring 60 .
• 5A shows a first adjustment ring 60.1 with an outer diameter d A and with a first inner diameter di.l.
• FIG. 5B shows a second adjustment ring 60.2 with an outer diameter d A which is the same as the outer diameter d A of the first adjustment ring 60.1, and with a second inner diameter di.2 which is smaller than the first inner diameter di.1. Consequently, the second adjustment ring 60.2 has a reduced free cross-sectional area in comparison to the first adjustment ring 60.1.
• the wall thickness of the cylinder jacket is greater in the case of the second adjustment ring 60.2 than in the case of the first adjustment ring 60.1.
• FIG. 5C shows a third adjustment ring 60.2 with an outer diameter d A that is the same as the outer diameter d A of the first and second adjustment rings 60.1, 60.2, and with a third inner diameter di.3 that is smaller than the first inner diameter di. l and smaller than the second inside diameter di.2. Consequently, the third adjustment ring 60.3 has a further reduced free cross-sectional area in comparison to the second adjustment ring 60.2.
• the wall thickness of the cylinder jacket is even greater for the third setting ring 60.3 than for the second setting ring 60.3.
• adjusting rings 60.1, 60.2, 60.3 illustrated in Figures 5A to 5C each with a different inside diameter di.1, di.2, di.3 with otherwise the same Dimensions, a set of adjustment rings 60 is provided, which can be inserted and fastened in the inlet opening 21 of the through-channel 20 if necessary. With the help of the insertable adjusting rings 60.1, 60.2, 60.3, the free cross-sectional area 23 of the through-channel 20 can thus be further reduced very easily.
• One or more connecting devices 50 are provided within the through-channel 20 on the inflow side, i.e. starting from the inlet opening 21, which preferably comprise two longitudinal slots 51, which are arranged on opposite wall sections and in the direction of the longitudinal axis 26 of the through-channel 20 and which serve as guides for a plug-in connection.
• the illustrations Fig. 1 to Fig. 4 show a particularly preferred variant in the form of guides of a lockable plug connection or a bayonet catch with two longitudinal slots 51 running in the direction of the longitudinal axis 26 and arranged on opposite wall sections of the through-channel 20 together with transverse slots 52, which correspond to the longitudinal slots 51 are respectively subordinate.
• the transverse slots 52 are each positioned at the end of the longitudinal slots 51 transversely thereto.
• each adjustment ring 60 has external coupling elements 53 which protrude laterally beyond the outer cylindrical surface of the adjustment ring 60.
• the coupling elements 53 are designed in the form of protruding pins or buttons and correspond to the longitudinal slots 51 or the transverse slots 52.
• Each adjusting ring 60 is designed in such a way that it can be inserted into the inlet opening 21 of a through-channel 20, with the coupling elements 53 on the Adjusting ring 60 engage in the corresponding longitudinal slots 51 on the walls of the through-channel 20.
• the adjusting ring 60 is inserted coaxially with its longitudinal axis direction 62 in the direction of the longitudinal axis 26 of the through-channel 20 in the X-axis direction until the peripheral edge 61 of the adjusting ring 60 rests against the edge section 24 of the through-channel 20 .
• the connection device 50 is designed as a lockable plug-in connection
• the inserted adjustment ring 60 can be captively secured by rotating it about its longitudinal axis direction 62 .
• the coupling elements 53 engage in the transverse slots 52 of this bayonet lock.
• the adjusting ring 60 can be separated from the static mixer element 10 again by turning it in the opposite direction of rotation and by pulling it out in the direction of the longitudinal axis 26 of the through-channel 20 .
• the base plate 70 is essentially cuboid here and has two base feet 71 on its underside, which extend in the longitudinal direction of the base plate 70 in the form of strips.
• the base feet 71 have the advantage of leveling out unevenness in the To be able to compensate underground at the site of a static flow mixing device, especially inside a combustion chamber of an industrial boiler.
• lateral guide profiles 72 are arranged in the longitudinal direction, which can serve to guide other components.
• FIG. 7 shows a pedestal 80 as part of a static flow mixing device according to the invention.
• the standing plate 80 shown here has two recesses 81 on its upper side, into each of which a base section 14 of a static mixer element 10 can be inserted in a form-fitting manner.
• the two recesses 81 each have sloping bearing surfaces here, which correspond to the sloping bearing surfaces 16 of the base section 14 of a static mixer element 10 .
• Lateral guide grooves 82 on the underside of the base plate 80 serve to accommodate the guide profiles 72 of the base plate 70, as shown in FIG.
• Fig. 8 illustrates a first embodiment of a static flow mixing device 100 according to the invention with two static mixer elements 10 according to Fig. 1, with a base plate 70 according to Fig. 6 and with a base plate 80 according to Fig. 7. To adjust the overall height of the static flow mixing device 100 here additionally between the base plate 70 and the standing plate 80 several base plates 75 interposed.
• FIG. 9 shows the individual parts of the structure shown in FIG. 8 in an exploded view. Here the three inserted base plates 75.1, 75.2, 75.3 can be clearly seen.
• the two static mixer elements 10 are arranged one behind the other as viewed in the X-axis direction or in the direction of flow 1 of the inflowing medium or flue gas, in such a way that the longitudinal axis directions 26 of the passage channels 20 are positioned coaxially.
• the front static mixer element 10 which is shown in Fig. 8 in the foreground of the image, there is a first adjustment ring 60.1 with a first inner diameter di.
• the second, rear static mixer element 10 there is a second adjustment ring 60.2 in the through-channel 20 with a second inner diameter di.2, which is smaller than the first inner diameter di.1.
• the central opening of a static mixer element prevents excessive back pressure and excessive pressure loss in the combustion chamber. Due to the tapering inner diameter, the centrally arranged combustion gas of the combustion jet can be divided into several static mixer elements and then deflected. The flow through the first static mixer element 10 and, associated therewith, the flow against the second flow element 10, which is located in the slipstream of the first static mixer element 10, are thus improved.
• Fig. 10 shows a second embodiment of a static flow mixing device 100 according to the invention with six static mixer elements 10 positioned one behind the other according to the embodiment of Fig. 1.
• the six static mixer elements 10 are fastened here in pairs on three standing plates 80 arranged one behind the other, viewed in the X-axis direction or in the direction of flow 1, with the through-channels 20 of the six static mixer elements 10 being arranged coaxially 26 one behind the other.
• Corresponding base plates 70 and base plates 75.1 to 75.3 serve as a stand for the static mixer elements 10.
• the first or foremost static mixer element 10 on the inflow side has a through-channel 20 without an adjusting ring.
• the other static mixer elements 10 arranged downstream in the X-axis direction, ie the second to sixth static mixer elements 10, are each equipped with an adjusting ring 60.1, 60.2, 60.3, 60.4, 60.5 fastened in their respective through-channel 20.
• the several adjustment rings 60.1, 60.2, 60.3, 60.4, 60.5 are arranged in such a way that the inside diameters di.1, di.2, di.3, di.4, di.5 of the adjustment rings 60.1, 60.2, 60.3, 60.4, 60.5 decrease or become smaller in the X axis direction of the downstream static mixer elements 10 .
• several static mixer elements 10 can also be arranged.
• FIG. 11 shows a second embodiment variant of a static mixer element 10 according to the invention, with FIG. 12 illustrating the individual parts of the structure shown in FIG. 11 in an exploded view.
• the static mixer element 10 shown here is constructed in two parts and comprises a lower first part 10.1 and an upper second part 10.2, which can be positively connected by means of a plug connection 55.
• two connecting elements 56 in the form of connecting pins are arranged here on the lower first part 10.1, which can be brought into engagement with corresponding recesses 57 on the upper second part 10.2 of the divided static mixer element 10.
• FIG. 13 shows the individual parts of a third embodiment of a static flow mixing device 100 according to the invention with two static mixer elements 10 according to FIG. 11 in an exploded view.
• Figures 14 and 15 relate to a third variant embodiment of a static mixer element 10 according to the invention, assembled from three individual parts 10.1, 10.2 and 10.3.
• the individual parts 10.1 to 10.3 can in turn be positively connected to one another by means of plug connections 55. Additional expansion joints on the base body are not required in this version either.
• Figures 16 and 17 show a fourth embodiment of a static flow mixer 100 according to the invention with two static mixer elements 10 according to Fig. 15.
• the combustion chamber 200 is essentially cylindrical in shape with a longitudinal axis direction 201 and an inner diameter 202.
• the burner flame 211 is aligned essentially coaxially with the longitudinal axis 201 of the combustion chamber 200 .
• the so-called turning chamber On the front side of the combustion chamber 200 opposite the burner device 210 is the so-called turning chamber, in which the flue gas is deflected by about 180° and in a second flue gas flue, which is indicated only schematically in the background of Fig.
• the mechanisms relevant for the heat transport in a combustion chamber of a generic industrial heating boiler are on the one hand the convective or turbulent heat transport and on the other hand the thermal radiation due to the high flame temperature of the fuel gas at approx. 1800°C.
• the turbulence or turbulent flow through the coaxial burner flame is relatively low, as is the case, for example, in 19 and FIG. 25, respectively.
• the flow speed of the combustion gas decreases, especially close to the combustion chamber wall, as a result of which the heat transfer coefficient at the combustion chamber wall is disadvantageously reduced. This is illustrated, for example, in Figures 20 and 26, respectively.
• the turbulence of the combustion gas is advantageously already intensified in the combustion chamber, as is shown in Fig. 22 - in comparison to the corresponding Fig. 19 without internals - or in Fig. 28 - is illustrated in comparison to the corresponding figure 25 without internals.
• the internals according to the invention significantly increase the convective heat transport at the combustion chamber wall (see Figures 23 and 29).
• the design according to the invention of a static flow mixing device each with six static mixer elements arranged one behind the other, each structured with swirl surfaces and flow guide elements, and the suitable use of adjustment rings distributes the interaction or deflection of the inflowing combustion gas over several static mixer elements, as is the case in the Figures Fig.
• static mixer elements according to the invention or a static flow mixing device according to the invention within a combustion chamber of an industrial boiler advantageously lowers the temperature and speed of the combustion gas already in the combustion chamber, which also reduces the subsequent flue gas path in the area of the turning chamber and when it enters the second flue gas flue downstream thermally less exposed.
• the heat transport in the combustion chamber can be analyzed in a differentiated manner.
• the heat flow at the combustion chamber wall increases significantly as a result of the installation of static mixer elements according to the invention or a static flow mixing device according to the invention in a combustion chamber.
• radius of curvature of the guide vane (of the flow guide element) (or radii R, r) first flank of the guide vane (of the flow guide element) (concavely curved) inner guide vane height (guide element height) on the first flank outer guide vane height (guide element height) on the first flank second flank of the guide vane ( of the flow control element) (convexly curved) Inner guide vane height (guide element height) on the second flank Outer guide vane height (guide element height) on the second flank Expansion joint ./. 46 joint width
• connection device (lockable plug connection)

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