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EP0004081A2 - Refroidisseur à cuve - Google Patents

Refroidisseur à cuve Download PDF

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Publication number
EP0004081A2
EP0004081A2 EP79100708A EP79100708A EP0004081A2 EP 0004081 A2 EP0004081 A2 EP 0004081A2 EP 79100708 A EP79100708 A EP 79100708A EP 79100708 A EP79100708 A EP 79100708A EP 0004081 A2 EP0004081 A2 EP 0004081A2
Authority
EP
European Patent Office
Prior art keywords
cooling
shaft
cooler according
cooling channels
shaft cooler
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
EP79100708A
Other languages
German (de)
English (en)
Other versions
EP0004081A3 (en
EP0004081B1 (fr
Inventor
Otto Heinemann
Rainer Philipp
Heinz-Herbert Schmits
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.)
ThyssenKrupp Industrial Solutions AG
Original Assignee
Krupp Polysius AG
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 Krupp Polysius AG filed Critical Krupp Polysius AG
Publication of EP0004081A2 publication Critical patent/EP0004081A2/fr
Publication of EP0004081A3 publication Critical patent/EP0004081A3/xx
Application granted granted Critical
Publication of EP0004081B1 publication Critical patent/EP0004081B1/fr
Expired legal-status Critical Current

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Classifications

    • 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
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/04—Tubular elements of cross-section which is non-circular polygonal, e.g. rectangular
    • 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
    • F27D15/0286—Cooling in a vertical, e.g. annular, shaft
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0058—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for only one medium being tubes having different orientations to each other or crossing the conduit for the other heat exchange medium
    • 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
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0045—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for granular materials

Definitions

  • the invention relates to a shaft cooler with material supply at the upper end and material discharge at the lower end, containing in the interior of the shaft a number of cooling ducts arranged at a mutual distance and carrying a cooling medium.
  • Such a shaft cooler is an indirectly acting cooler, i.e.
  • the material to be cooled, in particular fine-grained to coarse material coming from a kiln e.g. cement clinker
  • a gaseous cooling medium in particular cooling air
  • this cooling medium does not have to be freed of carried particles after leaving the cooler by separate separating devices.
  • the invention is therefore based on the object of improving a shaft cooler of the type mentioned in such a way that, with a particularly favorable thermal efficiency, largely uniform cooling of the material to be cooled can be achieved with cooling ducts which are relatively simple to produce.
  • This object is achieved according to the invention by profiling the generally approximately vertically oriented cooling ducts in such a way that the product flow zones present between adjacent cooling ducts have an axis which deviates several times from the straight, vertical profile.
  • the cooling goods sliding down between the cooling channels in the material flow zones are intensively circulated several times over their entire vertical path, so that all the cooling goods particles repeatedly have intensive contact with the cooling channels through which the cooling medium flows in the course of their downward movement;
  • this intensive circulation of material there is also an intensive, repeated mixing of the refrigerated goods with one another, which results in a mutual exchange of heat and thus a particularly good temperature adjustment of all refrigerated goods.
  • the cooling channels required to achieve such a cooling effect can be produced relatively easily and cheaply.
  • the cooling channels of the shaft cooler according to the invention are aligned parallel to one another and approximately horizontally in the transverse direction of the shaft and extend from one shaft wall to the opposite shaft wall, so that the cooling medium is introduced into the cooling channels in an extremely simple manner and at the other end (on the opposite shaft wall) can be removed again.
  • each cooling channel has an approximately zigzag-like cross-sectional shape in its general vertical direction, the angles of the individual zigzag parts enclosing an angle of approximately 60 to 160 °, preferably approximately 100 to 120 ° .
  • these cooling channels have a particularly large cooling surface that comes into contact with the goods to be cooled, and at the same time they ensure particularly intensive and multiple circulation of the goods carried between them (in the goods pass zones).
  • all cooling channels have an angular cross-sectional shape that is particularly easy to manufacture.
  • the cooling channels have an approximately isosceles angular shape and the angle formed is between 60 ' and 160 °, preferably between 100 and 120 °, with them in the associated cooling shaft in several vertical rows each with approximately are equally spaced from each other. In this way, a sufficient cooling effect and circulation of the material to be cooled is achieved even with the more simply designed cooling channels (with an angular cross section).
  • each of these explained embodiments of the cooling channels is characterized by great stability against deformation (due to the pressure of the goods moving down).
  • These cooling channels can be produced in a simple manner by folding.
  • a cooling shaft has a plurality of shaft compartments lying one above the other with correspondingly arranged cooling channels and good passage zones formed between them, the good passage zones of all the shaft compartments lying one above the other being openly connected to one another.
  • the height of such a cooling shaft can be adapted in a modular manner to the particular intended use of the shaft cooler.
  • a plurality of cooling shafts are arranged in a row next to one another and are connected to one another by a common upper goods supply space, in which a material distributor conveyor is provided which extends over the entire length of the goods supply space. All adjacent cooling shafts can be largely even with refrigerated goods be sent.
  • the shaft cooler according to the invention can generally be used as a single unit. However, it is particularly advantageous if it is used as an indirectly acting cooling stage of a multi-stage cooling device which is connected downstream of a kiln. In such a case, it is then generally preferred that this indirectly acting shaft cooler, as a second cooling stage, is arranged downstream of a direct-acting cooler which emits all of its heated cooling air as combustion air to the furnace and forms the first cooling stage after the furnace, with which it then passes through is connected to a mechanical conveyor.
  • FIG. 1 shows an indirectly acting shaft cooler 1 according to the invention, which is used as the second cooling stage of a two-stage cooling device, which is connected downstream of a kiln 2 designed, for example, as a rotary kiln and as a first cooling stage after the rotary kiln 2, a direct-acting cooler 3 of any design ( therefore only indicated schematically), from which preferably all of the heated cooling air is introduced as combustion air into the rotary kiln 2.
  • the direct-acting cooler 3 is connected to the crop inlet chute 5 of the shaft cooler 1 according to the invention by a mechanical lifting conveyor 4 (e.g. deep cell conveyor or cup conveyor);
  • a pre-comminution device (not shown in more detail) is provided at the outlet of the first cooler 3, which comminutes the pre-cooled material to be fed to the conveyor 4 to a minimum piece size.
  • the shaft cooler according to the invention can be designed with only one cooling shaft.
  • a relatively large throughput capacity is expected, so that the shaft cooler 1 contains a plurality of cooling shafts 6 lying directly next to one another (in the illustrated illustration) example, four shafts), which are arranged in a row and can have a common outer housing.
  • coolant channels 7 in the interior of the individual cooling shafts 6 is particularly important for the present invention.
  • These cooling channels 7 are arranged at a mutual distance in the interior of the shaft and are intended for guiding a cooling medium, as will be explained later.
  • these generally approximately vertically oriented cooling channels 7 (cf. FIG. 1) are characterized by such a profile that the product flow zones 8 present between adjacent cooling channels have an axis 9 (cf. FIG. 2) that deviates several times from the straight, vertical profile.
  • the cooling channels 7 are aligned parallel to one another and approximately horizontally in the transverse direction of the shaft, and they extend from a longitudinal shaft wall 6a to the opposite longitudinal shaft wall 6b, as indicated in FIG. So the cooling channels extend in their longitudinal direction over the entire clear shaft interior, which is approximately rectangular in horizontal cross section.
  • each cooling air duct 7 has an approximately zigzag-like cross-sectional shape in its general vertical orientation, which is formed by any number of adjoining bends 7a, ie the closed hollow Space of each cooling channel 7 is formed by parallel and spaced, appropriately folded walls.
  • Each of the bends 7a can flow in at an angle of approximately 60 to 160 ° (depending on the material and the desired throughput time); In the exemplary embodiment shown in FIG. 2, the angle ⁇ enclosed by the bends 7a is approximately 110 °.
  • cooling channels 7 are designed and arranged with respect to one another in such a way that adequate contact cooling and sufficient circulation of the material sliding down are ensured in each case.
  • the cooling channels 7 designed according to the invention can be produced by simply bending metal sheets and can be welded together with relatively few seams; The fold of the cooling duct walls also results in excellent cooling duct stability. In the embodiment illustrated in FIG.
  • the cooling ducts 7 'to be arranged on a shaft wall can also be designed in a simplified manner in such a way that the corresponding straight shaft wall (zB6c) is used simultaneously as a wall of the cooling channel 7 ', so that - as also shown in Figure 2 - such K only a zig-zag-shaped beveled wall need not have ühlkanal 7'b; nothing changes in the zigzag shape with respect to the adjacent other cooling channels 7 and the intermediate material flow zones 8.
  • each cooling shaft 6 has a plurality of shaft compartments 10a, 10b, 10c, 10d (that is to say four shaft compartments) one above the other, in which the cooling channels 7 are formed in between in the manner explained Pass-through zones 8 are provided, the pass-through zones 8 of all superimposed shaft compartments 10a to 10d being openly connected to one another.
  • the pass-through zones 8 of all superimposed shaft compartments 10a to 10d being openly connected to one another.
  • any other number of shaft compartments per shaft in extreme cases only one shaft compartment can also be provided.
  • the approximately cuboidal individual shaft compartments 10a to 10d facilitate the design and assembly of such a shaft cooler and, on the other hand, this advantageously enables multiple transverse guidance and deflection of the through Achieve cooling passages 7 of cooling medium passed through, as is illustrated by the arrows 11 in FIG.
  • the cooling channels 7 are two superimposed shaft compartments, for example 10a and 10b, 10b and 10c etc., by an external Ver Binding line 12, 12a, 12b for the cooling medium connected to each other on the corresponding shaft sides 6a, 6b.
  • the cooling air used as the cooling medium is preferably fed only to the cooling channels 7 of each lower shaft compartment 10a directly from a cooling air fan 13 via a connecting line 14, so that the cooling air then flows through the shaft compartments 10a, 10b, 10c, 10d one after the other in the transverse direction and then from the uppermost shaft compartments 10d is discharged (see arrows 15).
  • This material distributor conveyor is preferably designed as a drag chain conveyor 17 and along its length interacts with a classification grate 18 also arranged in the upper material supply space 16 in such a way that the lower drag chain center 17a slides along the grate bars of the classification grate 18 running in the longitudinal direction of the material supply space 16.
  • the material brought in with the conveyor 4 and through the chute 5 is at least partially towed over the classification grate 18, the majority of the material to be cooled then falling down and being distributed over the individual shafts 6, while this is not due to the Classifying grate 18 coarse material falling through at the coarse material outlet 18a of the classifying grate falls into a coarse material chute 19 adjoining it and arranged at the end of the shaft cooler 1.
  • a coarse material chute 19 At the lower end of this coarse material chute 19 there is a comminution device 20, with the aid of which this coarse material is first comminuted before it is added to the cooled material.
  • all cooling shafts 6 have known multiple material outlets 21 at their lower end. These product outlets 21 can also be controlled in a known manner as a function of the product outlet temperature measured there and / or the shaft fill level (determined via known fill level measuring elements (not illustrated)), so that overall the shaft cooler 1 is operated essentially continuously.
  • the material outlets 21 of all cooling shafts 6 are arranged above a common material removal device 22 (e.g. a belt conveyor), above which the outlet of the coarse material shaft 19 also ends.
  • the cooling channels have an essentially zigzag-shaped profile, they can of course also have any other suitable profile or cross-sectional shape that has the desired guiding and cooling effect for the goods can bring about by appropriate multiple deflection and circulation.
  • FIG. 4 shows a second exemplary embodiment for the profiling of the cooling channels in an enlarged section (similar to FIG. 2) of a cooling shaft.
  • all cooling channels 30 are designed in an angular cross-sectional shape.
  • these cooling channels 30 (as illustrated) have an approximately isosceles angular shape, with that of the legs of the Ab Angles of these cooling channels 30 included angle d 'can in turn be between 60 and 160 °, preferably between 100 and 120 °; in the illustrated embodiment, the angle ⁇ is approximately 110 °.
  • the size of the angle ⁇ and the arrangement (one above the other and side by side) of these cooling channels 30 generally depends mainly on the particle size of the goods to be cooled and on the desired intensity of cooling and the throughput time of the goods through a shaft, these factors being chosen by one larger or smaller angle and by the mutual spacing of the cooling channels 30 lying next to and above one another.
  • the cooling channels 30 are arranged one above the other in a plurality of vertical rows 31, 32 in the associated cooling shaft 6 '.
  • the arrangement of the cooling channels 30 'in each vertical row 31, 32 is selected such that the adjacent cooling channels lying one above the other are slightly offset in the horizontal direction and are arranged in a gap with respect to one another;
  • the cooling channels 30 of each cooling channel row 31, 32 face each other with their angular outer sides (e.g.
  • the adjacent vertical cooling channel rows 31 and 32 have approximately equal distances from one another overall and the cooling channels 30 of these adjacent rows 31, 32, which are located opposite one another, are directed towards one another with their inner angular sides 30c, again arise between the adjacent cooling channel rows 31, 32 and between the individual cooling channels 30 of each vertical cooling channel row Good passage zones 33 with an axis deviating several times from the straight, vertical course, for example 34.
  • cooling air is preferred as the cooling medium in the exemplary embodiments explained above and illustrated in the drawing, but that in some embodiments and applications, another cooling gas or a suitable cooling liquid (for example water) can also be used as the cooling medium .
  • a suitable cooling liquid for example water

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Thermal Sciences (AREA)
  • Geometry (AREA)
  • Furnace Details (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
EP79100708A 1978-03-08 1979-03-08 Refroidisseur à cuve Expired EP0004081B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19782809927 DE2809927A1 (de) 1978-03-08 1978-03-08 Schachtkuehler
DE2809927 1978-03-08

Publications (3)

Publication Number Publication Date
EP0004081A2 true EP0004081A2 (fr) 1979-09-19
EP0004081A3 EP0004081A3 (en) 1979-10-17
EP0004081B1 EP0004081B1 (fr) 1980-10-29

Family

ID=6033836

Family Applications (1)

Application Number Title Priority Date Filing Date
EP79100708A Expired EP0004081B1 (fr) 1978-03-08 1979-03-08 Refroidisseur à cuve

Country Status (5)

Country Link
EP (1) EP0004081B1 (fr)
BR (1) BR7901378A (fr)
DE (1) DE2809927A1 (fr)
ES (1) ES478365A1 (fr)
ZA (1) ZA79867B (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998017959A1 (fr) * 1996-10-23 1998-04-30 Babcock-Bsh Gmbh Refroidisseur de puits
WO2017178212A1 (fr) * 2016-04-12 2017-10-19 Cebcon Technologies Gmbh Procédé d'hygiénisation de biomasse
EP3822569A1 (fr) 2019-11-14 2021-05-19 Promix Solutions AG Echangeur de chaleur
EP4089357A1 (fr) 2021-05-10 2022-11-16 Promix Solutions AG Echangeur de chaleur

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19643699C1 (de) * 1996-10-23 1998-03-26 Babcock Bsh Gmbh Schachtkühler
DE102009036119A1 (de) * 2009-08-05 2011-02-10 Uhde Gmbh Verfahren und Vorrichtung zur Kühlung eines feinkörnigen Feststoffes bei gleichzeitigem Austausch des darin enthaltenen Lückenraumgases

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB150056A (en) * 1919-05-26 1920-08-26 Albert Dyche An improved copper tube for refrigerators
US1737061A (en) * 1926-05-01 1929-11-26 Santa Cruz Portland Cement Com Clinker cooler
US2377943A (en) * 1939-01-07 1945-06-12 Kennedy Van Saun Mfg & Eng Means for cooling material
FR1046374A (fr) * 1950-12-13 1953-12-07 Smidth & Co As F L Transmission de chaleur

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB150056A (en) * 1919-05-26 1920-08-26 Albert Dyche An improved copper tube for refrigerators
US1737061A (en) * 1926-05-01 1929-11-26 Santa Cruz Portland Cement Com Clinker cooler
US2377943A (en) * 1939-01-07 1945-06-12 Kennedy Van Saun Mfg & Eng Means for cooling material
FR1046374A (fr) * 1950-12-13 1953-12-07 Smidth & Co As F L Transmission de chaleur

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1998017959A1 (fr) * 1996-10-23 1998-04-30 Babcock-Bsh Gmbh Refroidisseur de puits
WO2017178212A1 (fr) * 2016-04-12 2017-10-19 Cebcon Technologies Gmbh Procédé d'hygiénisation de biomasse
EP3822569A1 (fr) 2019-11-14 2021-05-19 Promix Solutions AG Echangeur de chaleur
US12104865B2 (en) 2019-11-14 2024-10-01 Promix Solutions Ag Heat exchanger
EP4089357A1 (fr) 2021-05-10 2022-11-16 Promix Solutions AG Echangeur de chaleur

Also Published As

Publication number Publication date
BR7901378A (pt) 1979-10-02
EP0004081A3 (en) 1979-10-17
ES478365A1 (es) 1979-05-16
EP0004081B1 (fr) 1980-10-29
DE2809927A1 (de) 1979-09-13
ZA79867B (en) 1980-03-26

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