EP3794295A1 - Appareil à tubes rotatifs - Google Patents

Appareil à tubes rotatifs

Info

Publication number
EP3794295A1
EP3794295A1 EP19727590.2A EP19727590A EP3794295A1 EP 3794295 A1 EP3794295 A1 EP 3794295A1 EP 19727590 A EP19727590 A EP 19727590A EP 3794295 A1 EP3794295 A1 EP 3794295A1
Authority
EP
European Patent Office
Prior art keywords
hollow tubes
welding
drehrohparparat
sections
ribs
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP19727590.2A
Other languages
German (de)
English (en)
Other versions
EP3794295B1 (fr
EP3794295C0 (fr
Inventor
Niclas SCHULTHEIS
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Grenzebach BSH GmbH
Original Assignee
Grenzebach BSH GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Grenzebach BSH GmbH filed Critical Grenzebach BSH GmbH
Publication of EP3794295A1 publication Critical patent/EP3794295A1/fr
Application granted granted Critical
Publication of EP3794295B1 publication Critical patent/EP3794295B1/fr
Publication of EP3794295C0 publication Critical patent/EP3794295C0/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27D—DETAILS OR ACCESSORIES OF FURNACES, KILNS, OVENS, OR RETORTS, IN SO FAR AS THEY ARE OF KINDS OCCURRING IN MORE THAN ONE KIND OF FURNACE
    • F27D15/00—Handling or treating discharged material; Supports or receiving chambers therefor
    • F27D15/02—Cooling
    • F27D15/0206—Cooling with means to convey the charge
    • F27D15/0273—Cooling with means to convey the charge on a rotary hearth
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27D—DETAILS OR ACCESSORIES OF FURNACES, KILNS, OVENS, OR RETORTS, IN SO FAR AS THEY ARE OF KINDS OCCURRING IN MORE THAN ONE KIND OF FURNACE
    • F27D15/00—Handling or treating discharged material; Supports or receiving chambers therefor
    • F27D15/02—Cooling
    • F27D15/0206—Cooling with means to convey the charge
    • F27D15/028—Cooling with means to convey the charge comprising a rotary drum
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27B—FURNACES, KILNS, OVENS, OR RETORTS IN GENERAL; OPEN SINTERING OR LIKE APPARATUS
    • F27B7/00—Rotary-drum furnaces, i.e. horizontal or slightly inclined
    • F27B7/20—Details, accessories, or equipment peculiar to rotary-drum furnaces
    • F27B7/38—Arrangements of cooling devices
    • F27B7/40—Planetary coolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27D—DETAILS OR ACCESSORIES OF FURNACES, KILNS, OVENS, OR RETORTS, IN SO FAR AS THEY ARE OF KINDS OCCURRING IN MORE THAN ONE KIND OF FURNACE
    • F27D9/00—Cooling of furnaces or of charges therein
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D11/00—Heat-exchange apparatus employing moving conduits
    • F28D11/02—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller
    • F28D11/04—Heat-exchange apparatus employing moving conduits the movement being rotary, e.g. performed by a drum or roller performed by a tube or a bundle of tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27D—DETAILS OR ACCESSORIES OF FURNACES, KILNS, OVENS, OR RETORTS, IN SO FAR AS THEY ARE OF KINDS OCCURRING IN MORE THAN ONE KIND OF FURNACE
    • F27D9/00—Cooling of furnaces or of charges therein
    • F27D2009/0002—Cooling of furnaces
    • F27D2009/0051—Cooling of furnaces comprising use of studs to transfer heat or retain the liner
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F27—FURNACES; KILNS; OVENS; RETORTS
    • F27D—DETAILS OR ACCESSORIES OF FURNACES, KILNS, OVENS, OR RETORTS, IN SO FAR AS THEY ARE OF KINDS OCCURRING IN MORE THAN ONE KIND OF FURNACE
    • F27D9/00—Cooling of furnaces or of charges therein
    • F27D2009/007—Cooling of charges therein
    • F27D2009/0072—Cooling of charges therein the cooling medium being a gas
    • F27D2009/0078—Cooling of charges therein the cooling medium being a gas in indirect contact with the charge
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element

Definitions

  • the invention relates to a rotary kiln, in particular a sectional cooler for cooling a free-flowing solid, with attached to its walls structures for increasing the heat conduction according to the preamble of claim 1.
  • a rotary kiln is used for cooling or heating a free-flowing Guts, in particular a bulk material.
  • a rotary tube apparatus is used, in particular in its embodiment as a sectional cooler, for continuous processes in process engineering.
  • coolers are used to cool very hot products such as calcined pigments, slags, metal oxides and hydroxides, cement clinker, sponge iron, scale, activated carbon, catalysts, Coke, metallurgical residues, etc. required. Without cooling the very hot products, further process control is often not possible. In many cases, the heat energy contained in the solid is to be at least partially recovered in the context of the technologically necessary cooling.
  • Apparatus and methods for cooling such bulk materials which are of an initial temperature of e.g. 700 ° C to 1400 ° C to final temperatures of e.g. 80 ° C to 200 ° C must be cooled.
  • coolers that use a direct contact of ambient air with the material to be cooled, are used for this task with air or water indirectly operated rotary kiln cooler.
  • “Indirectly” means that the cooling medium, for example water or air, does not come into direct contact with the hot product to be cooled, but a heat exchange takes place from the hot product to the cooling medium via an apparatus wall separating the media.
  • BESTATIGUNGSKOPIE US 1 218 873 A, US 2 283 129 A and US 2 348 446 A disclose indirect air-cooled solids coolers which operate with both a single closed drum housing and those which guide the solids in multiple tubes within a drum ,
  • a rotary tube is sprayed from the outside with water; or the drum passes through a water bath as described in US 4 557 804 A, wetting the surface of the rotating drum with water and cooling the wall of the apparatus, while cooling the hot product in the drum by heat dissipation to the cooled wall of the apparatus ,
  • EP 0 567 467 B1 discloses a rotary tube cooler with a rotary tube, which rotates within a fixed, bricked envelope and in which the cooling medium, for example air or water, flows in the cavity formed between the rotary tube and the lining.
  • the cooling medium for example air or water
  • sectional coolers As they have become known by the Grenzebach BSH GmbH, to increase the heat exchanger surface, a plurality of chambers, for example six or eight chambers, the so-called sections, created, which are located in a rotary drum housing, creating a cavity arises between the chambers. Based on the cross section of a cylindrical housing so that each chamber fills a circular sector or circular cross-section.
  • hot product cooling water is passed through the cavities formed in the drum housing between the sections.
  • the supply and removal of the cooling water via a sealed rotary joint on the side of the product discharge of the drum and pipe connections to or from the individual double tubes.
  • Such sectional coolers have a special construction, leading to a high material and labor costs in the production, especially by the required extensive welding.
  • the drum housing itself also necessarily has a high weight, because the drum and the walls of the chambers must be made thick walls for strength reasons. Although both lead to a high total weight of the apparatus, but allows a particularly effective heat dissipation.
  • Sectional coolers consist essentially of a rotating rotor, which is usually driven by a chain. At the ends of the rotor are rigid housings for the product supply and removal. Depending on the size of the radiator, the rotor is either mounted on the ends of its own axle (axle radiator) or has a rotary-tube-typical raceway bearing. Inside the rotor consists of a plurality of section-shaped chambers, which are arranged pie-shaped around a central hollow shaft. This arrangement is completely surrounded by the outer jacket. In the section-shaped chambers are conveying elements. Depending on the requirements, these can be shovels, chains or the like. Depending on requirements, sectional coolers with diameters between 0.8 and 4 m and lengths of 3 to 30 m are built.
  • Sectional coolers work with indirect water cooling.
  • the cooling water passes through an inner central hollow shaft between the individual sections, flows around them and exits through an outer central hollow shaft again.
  • the product to be cooled usually falls directly into the product housing and is transported by the rotational movement and the conveying elements to the other end of the radiator.
  • the rotation ensures a permanent mixing of the product in the sections and thus a good heat transfer.
  • the product can be conveyed in cocurrent or countercurrent to the cooling medium.
  • Sectional coolers can be used to cool almost all free-flowing bulk solids. They are often found behind rotary kilns in calcination processes or the like. Their main goal is usually to cool down the products so that they can be handled with other apparatus (conveyors, grinders, etc.). Often, cooling itself is an important part of the manufacturing process.
  • Typical products include: As petroleum coke, Zinkblenderöstgut, soda, pigments and many more.
  • the inlet temperatures of the products can be up to 1400 ° C.
  • the invention relates to any Drehrohparparate that are used for cooling or heating a free-flowing Guts.
  • a rotary tube apparatus reference will always be made to a rotary tube refrigerator and its cooling function;
  • the invention is intended for use with any introduced into such a rotary tube cooler pourable Good.
  • the hollow tubes are arranged in rows which extend in the longitudinal direction of the rotary tube apparatus.
  • two adjacent rows of hollow tubes each have an offset arrangement of the hollow tubes.
  • the hollow tubes can be applied for example by screws, gluing or riveting on the walls of sections.
  • welding methods are also suitable, in particular submerged arc welding, gas metal arc welding, friction welding or stud welding.
  • a particularly adapted to the hollow tubes and therefore particularly suitable method is the sleeve welding.
  • the hollow tubes have a length of less than 10 cm, in particular less than 5 cm. They particularly preferably have a length of 3.6 cm.
  • the hollow tubes have a diameter of less than 5 cm, in particular of 3.0 cm.
  • the hollow tubes have a wall thickness of 1 cm or less, in particular of 0.5 cm.
  • the rotary tube cooler has a plurality of sections, on the radial walls and on the circular arc wall a higher density of hollow tubes have as in the corner regions between the radial walls and between the radial walls on the one hand and the circular arc wall on the other.
  • the sections each have about 500 ribs or 500 hollow tubes per meter of length of the rotary tube cooler.
  • the invention also relates to a method for operating a rotary tubular apparatus, in particular a rotary tube cooler, as described above.
  • the method is characterized in that the solid moves around the hollow tubes in a turbulent flow.
  • FIG. 1 is a representation of the wear of a component (vertical axis), for example, the rotary tube apparatus, as a function of the ratio of the hardness of the material of the component to the hardness of a wear body (horizontal axis), for example of zinc oxide,
  • Fig. 2 is an illustration of the wear of a component (vertical axis), for example, of the rotary tube apparatus, as a function of the ratio of the hardness of the material of the component to the hardness of zinc oxide (horizontal axis) for various materials usable in a rotary tube apparatus;
  • FIG. 3 shows a representation of the Brinell hardness [HBW] (vertical axis) as a function of the elongation at break, measured in [%], for various materials (horizontal axis) that can be used in a rotary tube apparatus, in particular for its cooling function-carrying components such as the cooling fins,
  • HCW Brinell hardness
  • FIG. 7 is a sectional view of a section of a section of a sectional cooler with a rectangular rib, which is connected via a screw and a nut with a wall of the section,
  • FIG. 8 is a sectional view of a section of a section of a sectional cooler with a corrugated rib in cross-section
  • FIG. 10 shows a cross section through a schematically illustrated sectional cooler with eight sections, which are each partially filled with a free-flowing material (shown in black),
  • 11 is an isometric cross-sectional view of a sector of a
  • Sectional cooler according to FIG. 10 which is equipped with rows of hollow ribs according to FIG. 9,
  • Fig. 12 is a plan view in rows in on an inner wall of a
  • 13 shows a representation of a particle of a product to be cooled flowing around the rib.
  • a large number of criteria are taken into account when optimizing a rotary tube cooler.
  • the best possible combination of material, joining method and geometry is determined.
  • the optimization of the heat transfer of the rotary tube cooler, in particular of the sectional cooler is improved by the introduction and optimization of the cooling fins.
  • the substrate to be cooled is introduced at a high temperature, for example up to 950 ° C., into a rotary tube cooler, for example a sectional cooler. Due to the constant cooling of the sections by a cooling fluid, such as water, the temperatures of the sections are lowered. Depending on the geometry, however, cooling fins in the sections can reach a temperature of, for example, 550 ° C., proportionately at the inlet of the product.
  • the mechanical stresses of the ribs are low. They are limited to loads due to contact with the product.
  • the ribs have no supporting or strength-increasing role within the sectional cooler. It is therefore also possible to consider materials whose limit of use is below the said 550 ° C.
  • the main stress lies in the region of the wear resistance through the substrate to be cooled or heated, for example powdered zinc oxide. Depending on the composition of the atmosphere within the sectional cooler, processes of high temperature corrosion may also take place.
  • the choice of materials is limited to metals and their alloys as well as ceramic materials.
  • the ceramic materials despite their good properties in terms of corrosion resistance, have poor thermal conductivity. In addition, their brittle behavior is to be judged critically.
  • the materials available for selection are shown in Table 1 with some of their properties. As shown in the selection, materials of different categories are included in the process of selection. For example, the sectional cooler with all its Built-in components mainly of structural steel S235JR with material number 1.0038. Also suitable, however, are other alloys, for example of aluminum or magnesium, as well as various steel grades.
  • the selection of the material to be used is made according to a plurality of criteria. Since the main stress on the cooling fins, which is caused by the zinc oxide wear, it is necessary to minimize this.
  • the types of wear occurring are sliding wear and impact wear.
  • a high resistance to the two types, which are composed of the mechanisms of abrasion and surface dislocation, can be achieved by a combination of high hardness and ductility.
  • the mechanism of abrasion can be counteracted by a high hardness of the material.
  • the wear is divided by abrasion in three zones.
  • the zone with a ratio of less than 0.6 the greatest wear is caused by the low hardness of the component.
  • a range with a ratio of the hardness of the two components between 0.6 to 1.2 there is a transition from the wear high position to the wear low position. From a value of 1, 2, the wear is minimized by abrasion, since the wear body can not penetrate into the component due to its lower hardness.
  • the tempering steel 25CrMo4 is the only material that is in the wear low-lying position.
  • the magnesium alloy, the pure nickel and the carbon steel, are in the range of maximum wear by abrasion. All other materials are in the area of the transition (Fig. 2).
  • the surface smoothness is also important, and the materials are also judged against their wear resistance.
  • the elongation at break can be used. This reflects the ductility of the materials, which counteracts with increasing levels of surface disruption.
  • FIG. 3 compares the material properties of the hardness with respect to the elongation at break, since the wear is dependent on the combination of both properties.
  • the proportion of abrasion outweighs that of the surface disruption. This is due to the small particle diameters of the zinc oxide between 0 mm and 6 mm. Accordingly, a weighting factor is included, which is not considered in Figure 3.
  • the ratio of the abrasion to the surface disruption is, for example, too.
  • the thermal conductivity of the individual materials is taken into account. Regardless of the geometry can be achieved by the use of particularly suitable materials with higher thermal conductivity increased heat fluxes.
  • the number of usable materials can be limited depending on the joining method.
  • the thermal expansion coefficient must be taken into account. If the sections are made of structural steel, the coefficient is about 12 x If the cooling fins are made of other materials, tensions may arise. The sections and cooling fins have room temperature during the joining process. When the cooler is put into operation, the temperature rises and the components expand. With materials of different coefficients of thermal expansion, these therefore expand differently. Due to this difference in the expansions, stresses arise in the region of the joining zone.
  • the aluminum alloy has the highest thermal conductivity, but also a high difference to the thermal expansion coefficient of structural steel. Together with the magnesium alloy, which has a significantly lower thermal conductivity than the aluminum alloy, the greatest stresses are to be expected in the region of the joining zone. All other materials have a similar range of thermal expansion coefficient and thermal conductivity, with X6CrMoS17 ferritic stainless steel having the lowest thermal conductivity.
  • the heat flow shown in Figure 5 results in dependence on the thermal conductivity. It shows a course that is similar to a root function. At low values of thermal conductivity increases the heat flow steep. With increasing thermal conductivities, the heat flow continues to increase, but the slope of the gradient decreases sharply. For this reason, the heat flux of X6CrMoS17 is about 20% lower than that of S235JR, although the thermal conductivity is over 50% below that.
  • the thermal conductivity of the aluminum alloy exceeds the value of the structural steel by more than 200%. The gain in heat flow, however, is only 20%. The course thus approaches a maximum heat flow.
  • Fig. 5 shows the transferred heat flow as a function of the thermal conductivity.
  • Another evaluation criterion is the thermal diffusivity with respect to the explained thermal fatigue. Although the number of operating cycles of a sectional cooler is small, since they are taken out of operation almost exclusively for maintenance and repair, thermal fatigue of the cooling fins may still occur if the thermal conductivity is too low. Therefore, higher temperature conductivities of the materials, as well as the geometries are preferable to cracks in the components and
  • FIG. 6 graphically illustrates the thermal conductivity of the materials versus the thermal diffusivity.
  • the aluminum alloy again provides the best result due to its high thermal and thermal conductivity. Since the thermal conductivity is composed of the thermal conductivity, the density and the specific heat capacity, it becomes clear why the aluminum alloy having the low density and the high heat conductivity has a high thermal conductivity.
  • the magnesium alloy also has a high thermal conductivity. In terms of thermal diffusivity, the alloy X6CrMoS17 has the worst characteristics. The other materials have approximately the same temperature conductivities, with the known differences inticianleitmaschineen.
  • the factors or evaluation criteria described above such as hardness, elongation at break, thermal conductivity, expansion coefficient, thermal conductivity, heat flow and the costs evaluated. Depending on the importance of the individual evaluation criteria, these are provided with weighting factors, for example (see Table 2).
  • the transferred heat flow with the same weighting factor is also included in the evaluation, since it has been shown that the thermal conductivity is decisive for the heat flow, but has no linear course. Accordingly, the determined heat flow serves as an additional factor to compensate for this nonlinearity. Another major influence is the criteria associated with wear and fatigue of the materials.
  • the evaluation is carried out by providing the highest value of a rating criterion with the value one.
  • the value zero forms the lower limit.
  • a linear course is formed so that the remaining values lie between the two limits.
  • the determined values are multiplied by the respective weighting factor. This is done for the different evaluation criteria and finally the individual results are added up.
  • the best possible valuation of the sum is thus at the value one.
  • Example: The alloy 25CrMo4 has the highest hardness with 216 HBW. Accordingly, this corresponds to the value 1. It follows that for each 2.16 HBW, the remaining materials each receive 0.01 evaluation points. This results in a value of 0.57 for the structural steel S235JR with a hardness of 123 HBW. Multiplied by the weighting factor, the values are 0.3 and 0.171.
  • the tempering steel has the considerable disadvantage that in the case of a weld, it must be annealed for several hours with low stress at temperatures between 680 ° C and 720 ° C and then cooled slowly to reduce stresses within the heat affected zone by welding. In the case of the large components of a sectional cooler, this also means, in addition to the time, a great technical outlay.
  • the easily weldable structural steel S355JR does not only need such a time-consuming, but also cost-intensive after-treatment.
  • the tempered steel 25CrMo4 is preferable in all joining methods, except in welding, where the advantages of structural steel outweigh the ease of handling.
  • a big advantage of bonding is that with all metals a good pretreatment can achieve an equivalent result. Accordingly, different material combinations are possible. However, depending on the type of adhesive used, other factors must be considered.
  • Structural adhesives can absorb stresses up to 30 MPa. This is much lower than the other joining methods. However, in order to be able to bear these stresses, very complex pretreatments of the workpieces are necessary, since only in this way can a good wetting of the surfaces take place, which is decisive for the quality of the bond. Since a uniform and thin layer thickness of the adhesive is also crucial, both sections and cooling fins must meet high tolerances. Despite the low thermal conductivity of the adhesive, the heat flow is only imperceptibly changed due to the small layer thickness.
  • screw connections can endure significantly higher stresses by adapting the components used, such as screws and nuts.
  • a large number of holes must be introduced into the sections through which the screws are passed. This reduces the stiffness of the sections.
  • this area must be sealed. This requires the use of other components.
  • the clamping force between the screw head and the nut additionally creates, in addition to the weakening of the sections through the bores, stresses in the sections which overlap with the stresses occurring during operation.
  • a rib 2 In a section 1 (FIG. 7) of a sectional cooler, a rib 2 has a rectangular shape (rectangular rib) and is connected by a screw 3 and a nut 4 to a wall 5 of the section 1. In this way, the rib 2 forms a bearing surface for the screw head of the screw 3. By using screws 3, the ribs 2 can be replaced non-destructively.
  • rivet connections can also be used
  • the method of press connection requires the use of ribs, which are at least partially inserted through the wall of the section.
  • the wall of the section and the respective rib can additionally be glued or welded.
  • Another method for making a connection between the ribs and the wall is joining by welding divided into two categories. Both submerged arc welding and gas metal arc welding are used, as well as friction welding and stud welding.
  • Submerged arc welding is not suitable for all welding positions, as the powder lies loosely on the welding zone. Thus, only welding positions can be realized with low inclination.
  • Each section of a sectional cooler consists of two joined parts. These are welded together after the introduction of the turning strips and conveying blades.
  • the welding torches of the MSG welding which can be automated as well as manually, have significantly smaller dimensions.
  • the preparations to weld the ribs to the sections are less than the preparations required for gluing, screwing or riveting. Inaccuracies can be compensated by introducing additional welding filler.
  • the ribs need only be chamfered to ensure full contact.
  • the material has approximately the same thermal conductivity as the starting material. Thus, welds with full area contact between fin and section can provide very good results in terms of the transferred heat flow between the two components.
  • Friction welding is characterized by a very good quality in the area of the weld zone. The strength is above that of the base material. Also, the thermal load and, associated therewith, distortion and residual stresses are lower than in a fusion welding process.
  • Stud welding is characterized by very short welding times. These are significantly lower than those of friction welding. Due to the short welding times, the thermal load is lower than, for example, in MIG / MAG welding. The strength of the cohesive connection is higher than that of the base material. Also, the compound is not affected by aging processes, as is the case with bonds.
  • the preparation of the weld zone is identical to that of MSG or submerged arc welding (UP welding) and therefore also significantly lower than the other methods considered.
  • UP welding submerged arc welding
  • the sections need not be provided with elaborate holes with minimal tolerances. Welding additives are not required, only a shield against the atmosphere by a protective gas is necessary.
  • the mild steel S355JR is preferable to the tempered steel 25CrMo4 because it is very easy to weld and requires no after-treatment.
  • the structural steel S355JR is a low-alloyed structural steel, an inert gas is recommended as the protective gas, as this is less expensive than an inert gas.
  • a geometry of the cooling fins is also provided which satisfies a plurality of criteria, in particular with regard to the heat flow.
  • the heat flow, based on the contact surface between the fin and the section is used to determine the heat flow, based on 1 mm 2 .
  • the efficiency of the different geometries can be estimated independently of the size of the rib or its contact surface with the section. Since some ribs, such as the paddle-shaped ribs occupy a significantly larger area of the section than their contact surface, this is taken into account by a projected area, ie the area which is covered by the contour of the rib
  • the heat flow is also related to the projected area.
  • the weight of the ribs is also included in the evaluation.
  • the heat flow serves as another criterion of the efficiency of the considered geometry. By a high quotient heat flow and weight therefore result in better use of resources, reducing material consumption and associated material costs.
  • the weighting of the different criteria is shown in Table 4.
  • the two heat flows related to the surfaces are the decisive criteria of the geometries. For this reason, the weighting factors together are 0.65.
  • the reference of the heat flow to the weight of the rib gives an indication of the efficiency of the rib, but no decisive information about the general improvement of the heat flow to the currently used cooling fin. For this reason, the criterion is not negligible, but factorized with a weighting factor of 0.2 lower than the heat flows, based on the areas. With a weighting factor of 0.15, the thermal diffusivity is below the other factors. This is justified because the ratio of the heat flows at different times, especially for the thermal fatigue is crucial.
  • Table 5 shows the evaluation of the geometry.
  • the tubular geometry of the cooling fin will be explained below using the example of a standardized tube.
  • the dimensions are taken, for example, from DIN EN 10220.
  • the evaluation is carried out identically to the above given again evaluation.
  • the same evaluation criteria with the same weighting factors are used.
  • another evaluation criterion, the heat flow is added. Since it is a pipe rib, this addition is possible without further adjustments.
  • the heat flow is weighted by a factor of 0.3.
  • the maximum achievable sum thus increases to the value 1, 3.
  • Table 6 shows the evaluation of the optimization of diameter and wall thickness.
  • Geometry determines the most preferred length of the rib.
  • the arrangement in combination with the number is also crucial for the transferred heat flow.
  • Fig. 10 The graphical determination of the area coverage of a preferably inclined mounted or alternatively horizontally mounted sectional cooler 8 is shown in Fig. 10 in cross section. It turns out that every section of the section is covered over a similar period of time. Thus, there is no area where attachment of cooling fins would not have a positive effect. Considering the distribution of the zinc oxide more closely, it is noticeable that the product has different speeds in the different areas.
  • the areas marked A, A 'and A "in Fig. 10 are the zones where the zinc oxide flows at lower speeds while traveling at higher speeds in the areas B, B' and B".
  • the positions within the cooler can be determined for the heat transfer coefficients.
  • the additional gain in transferred heat flow is clearly visible in all areas of the cooler.
  • the ratio of the heat flow between finned and non-finned surface increases by a further 15%.
  • the distribution of the ribs over the length of the radiator should be uniform.
  • the Montage selbiger can be kept simple. This advantage outweighs the small advantage of the increased ratio of heat flow in the lower temperature range.
  • the preferred number of cooling fins to be introduced is also determined.
  • both the heat flows of the contact surface to the cooling fin, but also the heat flows of the bottom plate, which surround the rib, are included.
  • the geometry of rectangular strips for example with the dimensions 9.9 m x 0.01 m x 0.03 m and those of the pipe ribs used, will be considered.
  • the maximum number of ribs per section is limited to 917 per meter of cooler. With this number of ribs, a heat flow is achieved, which is twice as high as that of the prior art.
  • the heat flow of the rectangular ribs is already achieved from a number of 205 ribs.
  • a geometry of the ribs results in a section 9 of a sectional cooler 8 according to the invention, as shown in FIG.
  • FIG. 12 shows the top view of the tube ribs 10 in one of the zones of higher particle velocity.
  • the ribs 10 between the rib rows 11, 12 they are always flowed through by the fine-grained zinc oxide. This reduces the rate of zinc oxide on the one hand, but on the other hand, turbulence is achieved by the deflection of the grains, which improves the convective heat transfer.
  • the arrow shown in Fig. 12 indicates the flow direction.
  • An example of what the flow around one of the fins 10 might look like is shown in FIG.
  • the particles are deflected outwards. Behind the rib create several turbulences, which are characteristic of turbulent currents. It also shows that lower velocity particles are directly behind the rib.
  • conveyor blades are also provided within the sections.
  • the selected joining process is characterized by very short welding times, so that the welding of the many ribs can be done in as short a time as possible. These short welding times are accompanied by lower thermal loads than in other fusion welding processes. This is also reflected in slight warpage of the sections and low residual stresses in the region of the heat affected zone.
  • Another advantage is the ease of use of the welding gun, so that less trained personnel can perform the welds; However, the welding can also be done automatically by a welding robot. By the small size of the welding gun, the accessibility to the sections is also granted.
  • the diameter of the ribs 10 d 30 mm.
  • the mechanical properties of the material exceed those of the base material in the area of the joining zone. In combination with the selected material for the ribs 10, thus results in the area in which the product on the ribs 10, a high resistance to the predominantly proportionate abrasion.
  • the hardness of the structural steel S355JR exceeds that of the section by almost 40%. Due to the low weight of the selected geometry, the additional costs due to the higher-grade structural steel are negligible.
  • the walls of the section 8 and the ribs have at least substantially equal values. Due to the same coefficients of thermal expansion caused by temperature differences no stresses due to different degrees of expansion of the components. The problem of thermal fatigue is also eliminated due to the same thermal diffusivity of the two materials, as previous coolers with S235JR turntables have also not exhibited any signs of fatigue of this type.
  • both materials are mild steel or low-alloy steels, they can be welded very well. In addition, no post-treatments of the joining zone are necessary.
  • the ribs 10 can be easily produced by cutting through pipes. Another advantage is that the selected steel is a very widespread steel.
  • the geometry of the rib already convinces without optimization by a very good result.
  • the values exceed those of the optimized rectangular rib.
  • the optimization achieves even better results.
  • the geometry is characterized by a large heat exchange surface with a low weight.
  • ribs 10 are preferably arranged offset. This achieves that the original task of the turning strips to reduce the wear of the sections, despite the new geometry is met.
  • the circular geometry coupled with the staggered arrangement of the ribs, creates a more turbulent flow which enhances heat transfer.
  • the outside of the rib is constantly in contact with the product to be cooled, which also ensures a high heat transfer.
  • cooling fins 10 per section 8 The considered value of 500 cooling fins 10 per section 8, relative to one meter in length, is only an example.
  • the torque required to set the radiator in rotation less.
  • the degree of reduction of the required power of the engine decreases its load, or it can be installed in a cheaper motor with less power. Connected with this, the energy requirement of the system drops.
  • the mechanical loads in the area of the pinion and the ring gear for the transmission of the motor drive on the outer wall of the rotary tube cooler decrease.
  • the loads that act on the bearings decrease.
  • the load or dimensioning of the foundations can also be smaller or smaller depending on the number of ribs.
  • the locations of the sectional coolers are distributed around the world. However, the production of the coolers always takes place at the same location.
  • each of the eight sections of this cooler is equipped with 16 turning strips. Their task is to reduce the speed of the particles to minimize the wear of the sections. Since it has been shown that more heat energy is also transmitted by the turning strips, they consequently also serve as cooling fins. With regard to the optimization of this property, the turning bars are examined.
  • the material is determined by considering seven different relevant properties.
  • the wear mechanisms by which the ribs are loaded are on the one hand abrasion, which can be reduced by a high hardness of the material, and surface disruption, which is lowered by the ductility.
  • the differences in the thermal expansion coefficients are included in the evaluation.
  • the evaluation of the ten materials yields the result that the structural steel S355JR is best suited for use as a material of the cooling fins, taking into account the joining method selected subsequently.
  • Higher hardness compared to the alloy S235JR reduces abrasion wear. Due to identical values of the heat conduction and the heat flow of the structural steel S355JR to the structural steel S235JR no losses are to be noted in the area of the heat transfer. Since both materials also have the same coefficient of thermal expansion, there are no stresses in the contact area between rib and section due to temperature differences between the state during operation and at times when the cooler is not in operation.
  • MAG welding is used with elongated cooling fins.
  • the cooling fins are to be provided with two bevels and connected by a double HV seam over the entire surface with the sections cohesively.
  • stud welding is suitable for very good mechanical properties of the joining zone due to its very short welding times.
  • no additives are necessary. The preparation is limited to the separation of the ribs to the required length and the required skill of operating a stud welder is low.
  • a list of the weight difference depending on the number of introduced cooling fins shows the potential potential of the optimized pipe ribs.
  • the economic optimum is to be determined from the costs of increasing assembly costs in relation to the saved material, the weight and the resulting further possible savings, with increasing number of cooling fins.
  • the corresponding economic and technical design of the cooler is to be carried out. Since the results of this work and the associated geometry of the cooling fins are visually and technically very different from those of the competitors, it will be examined to what extent they can be patented or are to be protected.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Arc Welding Control (AREA)
  • Pressure Welding/Diffusion-Bonding (AREA)
  • Furnace Details (AREA)
  • Arc Welding In General (AREA)

Abstract

L'invention concerne un appareil à tubes rotatifs, destiné au refroidissement ou au chauffage de produits en vrac coulants, en particulier un refroidisseur sectionnel (8) destiné au refroidissement d'une matière solide coulante, doté de structures agencées sur ses parois, destinées à augmenter la conduction thermique, lequel appareil est caractérisé en ce que les structures comprennent des tubes creux (10).
EP19727590.2A 2018-05-14 2019-05-10 Appareil à tubes rotatifs Active EP3794295B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018003840 2018-05-14
PCT/EP2019/000140 WO2019219233A1 (fr) 2018-05-14 2019-05-10 Appareil à tubes rotatifs

Publications (3)

Publication Number Publication Date
EP3794295A1 true EP3794295A1 (fr) 2021-03-24
EP3794295B1 EP3794295B1 (fr) 2023-07-26
EP3794295C0 EP3794295C0 (fr) 2023-07-26

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US (1) US12000655B2 (fr)
EP (1) EP3794295B1 (fr)
JP (1) JP7286901B2 (fr)
KR (1) KR20210008082A (fr)
AU (1) AU2019268508A1 (fr)
CA (1) CA3099902A1 (fr)
CL (1) CL2020002937A1 (fr)
ES (1) ES2957358T3 (fr)
MX (1) MX2020012246A (fr)
PE (1) PE20210532A1 (fr)
RU (1) RU2771058C1 (fr)
WO (1) WO2019219233A1 (fr)
ZA (1) ZA202007283B (fr)

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Publication number Priority date Publication date Assignee Title
RU2771058C1 (ru) * 2018-05-14 2022-04-25 Гренцебах Бсх Гмбх Устройство с вращающейся трубкой

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Publication number Publication date
CA3099902A1 (fr) 2019-11-21
US20210215428A1 (en) 2021-07-15
MX2020012246A (es) 2021-04-13
CL2020002937A1 (es) 2021-04-09
JP7286901B2 (ja) 2023-06-06
KR20210008082A (ko) 2021-01-20
EP3794295B1 (fr) 2023-07-26
EP3794295C0 (fr) 2023-07-26
ES2957358T3 (es) 2024-01-17
PE20210532A1 (es) 2021-03-17
US12000655B2 (en) 2024-06-04
RU2771058C1 (ru) 2022-04-25
ZA202007283B (en) 2021-08-25
JP2021523339A (ja) 2021-09-02
WO2019219233A1 (fr) 2019-11-21
AU2019268508A1 (en) 2020-12-24

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