EP0125432A2 - Dispositif de refroidissement ou séchage pour matériau à gros grains s'écoulant bien - Google Patents

Dispositif de refroidissement ou séchage pour matériau à gros grains s'écoulant bien Download PDF

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Publication number
EP0125432A2
EP0125432A2 EP84103053A EP84103053A EP0125432A2 EP 0125432 A2 EP0125432 A2 EP 0125432A2 EP 84103053 A EP84103053 A EP 84103053A EP 84103053 A EP84103053 A EP 84103053A EP 0125432 A2 EP0125432 A2 EP 0125432A2
Authority
EP
European Patent Office
Prior art keywords
rotation
rocker arm
pivot axis
cam
segment
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
EP84103053A
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German (de)
English (en)
Other versions
EP0125432B1 (fr
EP0125432A3 (en
Inventor
Alfred Klöckner
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.)
Individual
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Individual
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 Individual filed Critical Individual
Priority to AT84103053T priority Critical patent/ATE25765T1/de
Publication of EP0125432A2 publication Critical patent/EP0125432A2/fr
Publication of EP0125432A3 publication Critical patent/EP0125432A3/de
Application granted granted Critical
Publication of EP0125432B1 publication Critical patent/EP0125432B1/fr
Expired legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F26—DRYING
    • F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
    • F26B17/00—Machines or apparatus for drying materials in loose, plastic, or fluidised form, e.g. granules, staple fibres, with progressive movement
    • F26B17/001—Machines or apparatus for drying materials in loose, plastic, or fluidised form, e.g. granules, staple fibres, with progressive movement the material moving down superimposed floors
    • F26B17/002—Machines or apparatus for drying materials in loose, plastic, or fluidised form, e.g. granules, staple fibres, with progressive movement the material moving down superimposed floors with floors which may rotate and turn over as a whole or in part, e.g. around a horizontal axis

Definitions

  • the invention relates to a device for cooling or drying coarse-grained, free-flowing material with a plurality of floors lying one above the other and rotatable about a common axis of rotation, wherein each floor is divided into several segments, each of which can be tilted about a radial axis of rotation that is common to the common axis of rotation, and with which Holding segments in the plane of their base and allowing the segments to tilt only in a rotation range, each with one rocker arm assigned to each base and pivotable about a fixed pivot axis, each tilting a segment in the rotation range, with a first lever arm that moves into the The path of movement of the holders for the segments protrudes, and a second lever arm which, when the first lever arm pivots, engages a segment to forcibly tilt it about its tilt axis.
  • a device of the type described above has already become known from DE PS 3 028 263.
  • these devices which are also referred to as so-called circular coolers, depending on the space and in particular the desired throughput, two or more trays up to about eight trays are provided one above the other.
  • circular coolers with a larger number of bases are preferably used.
  • a certain throughput time of the good through the round cooler is desired for the good to be dried or cooled. This entails that in such a case, for example, a circular cooler with several trays must circulate faster than a circular cooler with only two trays,
  • the present invention is therefore based on the object of improving a device of the type mentioned at the outset in such a way that reliable operation is ensured even at higher speeds of the respective floors.
  • This task is based on a device of a gangs mentioned type solved according to the invention in that the first lever arm of the rocker arm is adjustable in the direction of rotation of the floors relative to the second lever arm.
  • the arrangement is preferably such that the first lever arm is formed from a cam disk which is connected to the second lever arm via a plate.
  • the cam disc is adjustably held on the plate. It has proven to be expedient here to design the plate and cam disc in such a way that they can be screwed together in different discrete positions.
  • the cam disc with such a cam curve which, in the untilted state of the rocker arm, begins at a point below the pivot axis of the rocker arm in the direction of rotation of the floors in front of the pivot axis and up to a point in a short distance below a floor.
  • the brackets for the segments in the lower point of the cam curve begin to attack, so it is achieved due to the location of the point of application and the formation of the cam curves that practically all of the applied force is converted into a torque on the rocker arm and not into a load on the rocker arm.
  • the cam curve is expediently designed in such a way that it runs in an inclined straight line or a disproportionately increasing curve, it can likewise be achieved that the rocker arm is slowly accelerated to its end position.
  • second cam disks are preferably attached to the mountings for the segments, which can be designed approximately in the form of a semi-ellipse with their apex pointing downwards. In this way it is achieved that the point of engagement between the first cam disk of the rocker arm and the second cam disks on the brackets for the segments continuously shifts against each other during the tilting of the rocker arm.
  • the rocker arm is usually arranged in the rocker area such that a segment passing through the rocker area is tilted immediately after entry into the rocker area. If, starting from the position of the pivot axis of the rocker arm, the point of application of the rocker arm on the segment to be tilted is shifted against the direction of rotation relative to the pivot axis of the rocker arm at higher speeds of the floor, this would mean that the rocker arm already has the segment in one position tried to tilt in which this is not yet released for tilting. For this reason, the arrangement is expediently made such that the essentially radially oriented pivot axis of the rocker arm is held adjustable in the direction of rotation of the bottoms.
  • the pivot axis of the rocker arm can be the same Angle amount are offset in the direction of rotation, in which the point of application of the rocker arm is advanced on a segment against the direction of rotation. It has proven useful to make the arrangement so that the pivot axis is adjustable in different discrete positions. According to a simple embodiment, this is achieved in that several bores aligned in the direction of rotation are provided in the housing wall of the round cooler, in each of which the pivot axis of the rocker arm can be held.
  • the cam disk is preferably extended in the direction of the pivot axis by a nose running in the direction of the bottoms and directed against the pivot axis of the rocker arm in such a way that the end of the nose facing the pivot axis is also the one furthest from the pivot axis of the rocker arm Position of the first lever arm has only a maximum predetermined distance in the direction of rotation of the floors from the pivot axis of the rocker arm. As a result, the base to be pivoted is pivoted until the second cam disc attached to the holders for the segments come out of engagement with the end of the nose. In this way, a predetermined pivot angle can be achieved in any position of the cam disk of the first lever arm with respect to the pivot axis of the rocker arm.
  • the top of the nose expediently forms an extension of the cam curve of the cam disk. It has proven to be an expedient embodiment here for the extension of the cam curve on the nose to run essentially parallel to the underside of the bottoms in the untilted state of the rocker arm.
  • a first floor, generally designated 10, is indicated in FIG. 1, of which only a first segment 11 and a subsequent segment 12 are partially indicated.
  • the segment 11 is fastened to a holder 13 which runs essentially perpendicular to the plane of the drawing and runs radially to the axis of rotation (not shown) for the base 10.
  • the segment 11 can be tilted about the radial axis 14 of the holder 13 in such a way that the sector-shaped segment, which is shown in the horizontal position in FIG. 1, is essentially tilted into an oblique position.
  • the rocker arm consists of a disc 23 which extends substantially in a plane perpendicular to the pivot axis A, a plate 24 which is fixed to the lower end of the disc 23, and a first cam disc 25 which inwards against the axis of rotation of the rotary cooler is offset from the disk 23 and is also substantially in an approximately vertical plane.
  • the cam disk 25, however, is slightly offset from the disk 23 in relation to the direction of rotation B (see the arrow in FIG. 1) with respect to the disk 23 and is slightly at an angle of about 6 ° in a horizontal plane, which is opposite to the direction of rotation B. opens, pivoted relative to the disk 23.
  • the cam disk 25, like the disk 23, preferably runs on a circular arc around the axis of rotation of the round cooler.
  • Bores 3 - 9 are formed in the plate 24 at a distance of approximately 20 mm, which lie approximately on a straight line or can also be arranged in a circle around the axis of rotation of the round cooler.
  • the first cam disk 25 there are: a distance of about 40 mm from 1, two threaded bores 26 and 27 are formed, into which two threaded bolts 28 and 29 can be screwed from the underside of the plate 24, around the first cam disk 25 in a substantially vertical position with respect to the substantially horizontal plate 24 to attach.
  • the first cam which is fixed in the position shown in Figures 1 and 2 by means of the threaded bolt 29 in the bore 7, can be shifted four positions to the right in Figure 2 such that the Threaded bolt is passed through holes 6 to 3. A total of five different positions are therefore possible for the first cam disk 25.
  • bores 3 'to 7' which are formed lying on a horizontal circle in the housing wall 17 of the round cooler.
  • the holes 3 'to 7' are used to adjust the bolt 21 for holding the entire rocker arm 20 in the housing wall.
  • the holes 3 'to 7' are also arranged approximately at a distance of 20 mm.
  • the cam disk 25 has on its upper edge a cam curve 30, which begins at a lower point 31 lying forward in the direction of rotation and runs over a slightly curved rising part 32 to a height 33 just below the lower edge 34 of the segment 11.
  • a second cam disk 35 interacts with this cam curve 30, one of which is attached to each holder 13 of a segment.
  • This second cam disk 35 can have any shape and should only be dimensioned such that its lower end 36 is approximately at the level of the lower point 31 of the cam curve 30 when both the rocker arm 20 and the segment 11 to be tilted are in the untilted position Condition.
  • the second cam disk 35 is preferably designed in the form of a semi-ellipse, the axes of which are aligned horizontally and vertically, and the apex of which forms the lower end 36 of the second cam disk 35.
  • Such a shape of the second cam disc has proven to be particularly advantageous in cooperation with the shape of the first cam curve 30 shown in FIG.
  • the cam curve is expediently designed such that its lower point 31 lies in the non-tilted position of the rocker arm 20 at a height below the height of the pivot axis A of the rocker arm. In this way, it is ensured that when the second cam disk 35 engages the first cam disk 25, the acting force is completely converted into a torque on the rocker arm.
  • the second cam disk 35 is limited in the radial direction of the segments 11 and 12 in such a way that when the base 10 rotates, it can only engage with the cam disk 25, but not with the disk 23.
  • the disk 23 is designed in the form of a first extension 37 which extends in the direction of rotation and a second extension 38 which extends counter to the direction of rotation with respect to the pivot axis A.
  • the first attachment 37 has a second cam curve 39 and the second attachment has a third cam curve 40. Both cam curves come into engagement with the underside 34 of the segment 11 or with all other segments if this segment is to be tilted first or if this segment is to be tilted back into its horizontal position, which will be explained in more detail below.
  • the second and third cam curve each have the highest flat elevations 41 and 42, while the upper side 43 lying between these elevations is further lowered compared to these elevations.
  • the material lying on the segment 11, which is not shown flows onto a lower floor (not shown) of the round cooler or from a last lower floor of a round cooler into an outlet (not shown).
  • the rocker arm 20 is preferably not during the tilting through 90 ° but suffering resembled a smaller angle about pivot 50 0, since it comes in this position against a stopper, not shown to the plant.
  • the segment 11 is thereby increasingly pivoted counterclockwise about the axis 14 until its underside 34 comes to bear on both surfaces 42 and 41 on the upper side of the disk 23. (The segments are preferably only tilted into a position which the In this case, the segment runs directly into contact with surfaces 41 and 42 on the rocker arm). From this point in time, when the base 10 is rotated further, segment 11 is in contact with the rocker arm together with the latter the horizontal position swung back. This horizontal position is reached at the latest when the pivot axis 14 of the segment 11 has passed the vertical line shown in FIG. 1 through the pivot axis A of the rocker arm 20.
  • the time during which the segment 11 is in the pivoted state is therefore given by the time during which the pivot axis 14 of the segment 11 is from the position in FIG. 1 in which the second cam disk 35 has a first contact with the first cam disk 25 ; has run to the point where it runs through the vertical plane 44 which passes perpendicularly through the pivot axis A of the rocker arm in FIG. 1.
  • this time depends on the speed of the bases of the circular cooler or taking into account different diameters of circular coolers, ultimately on the peripheral speed of the segments 11 on their outer edge.
  • the cooling or drying time for a good that passes through such a round cooler depends on the type and the respective state of the good introduced into the round cooler itself. This lead time is therefore determined by the goods themselves.
  • the speed of the trays will be lower and the dwell time of the goods on each tray will be longer than if a circular cooler with about six trays is used Accordingly, the speed of the floors must be higher and thus the residence time of the goods must be lower on each floor if the same residence time of the goods in the circular cooler is to be achieved overall.
  • the residence time of the goods and the outer peripheral speeds of the floors for various circular coolers with three, four, five and six floors are given.
  • the circumferential speed doubles in the transition from a round cooler with three trays to a round cooler with six trays.
  • the first cam disk 25 is adjustable in or against the direction of rotation B. .
  • cam disk 25 is initially installed in a position in which the bolt 29 passes through the bore 3 on the plate 24, this results in a position in which there is a small distance in the direction of rotation between the first point of engagement 31 on the cam curve 30 and the pivot axis A in Direction of rotation results.
  • This position is therefore suitable for slow-running circular coolers or for circular coolers with a small number of trays.
  • FIG. 2 shows the greatest possible adjustment with the greatest distance between the cam disk 25 and the pivot axis A of the rocker arm.
  • a faster rotation of the soils is not only a function of the larger number of soils, but is also due to the goods to be treated and the necessary throughput time of the goods in the round cooler.
  • Such lead times are usually between about 6 to 20 minutes.
  • FIG. 4 differs from that shown in Figure 1 arrangement, only as - by that said first cam is extended 25 by a shoulder 45 which extends in the direction of rotation B of the soil 10 in the direction of the pivot axis A of the rocker arm 20 .
  • the approach 45 essentially serves to extend the cam curve 30 beyond the point 33 through the cam curve part 46.
  • This cam curve portion 46 extends in the non-tilted state of the tilting - lever 20 substantially toward the bottom of the trays 10.
  • the cam plate is parallel shown in a position 25 in which they are furthest against the direction of rotation B of the soil against the pivot axis A of the rocker arm is adjusted. If the extension or nose 45 according to the configuration of FIG.
  • FIG. 6 shows a state of the floor to be tilted and of the rocker arm in which the floor 10 has already been moved a distance in comparison to FIG. 5 is that the lower end 36 of the second cam 35 just comes out of engagement with the end of the cam portion 46 of the boss 45. In this position, the floor 10 is now forcibly tilted through a larger angle! 32. In this way it can be achieved that even a good to be dried or cooled, which is somewhat sticky or which, like for example Schilfer, has a plate-like shape such as biscuits, is surely completely tipped over from the floor.
  • the projection 45 of the cam disk 25 does not prevent the cam disk 25 from being in a position which is further adjusted against the pivot axis A of the rocker arm. In such a case, the floor to be tilted is only forcibly pivoted through a larger angle up to a vertical position if possible. Only in very extreme cases, in which a very large adjustment range of the first cam disk 25 is required due to a very large speed change range, may it be necessary to provide cam disks with different lengths 45 for certain adjustment ranges.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Drying Of Solid Materials (AREA)
EP84103053A 1983-03-30 1984-03-20 Dispositif de refroidissement ou séchage pour matériau à gros grains s'écoulant bien Expired EP0125432B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT84103053T ATE25765T1 (de) 1983-03-30 1984-03-20 Vorrichtung zur kuehlung oder trocknung von grobkoernigem rieselfaehigem gut.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3311693A DE3311693C1 (de) 1983-03-30 1983-03-30 Vorrichtung zur Kuehlung oder Trocknung von grobkoernigem,rieselfaehigem Gut
DE3311693 1983-03-30

Publications (3)

Publication Number Publication Date
EP0125432A2 true EP0125432A2 (fr) 1984-11-21
EP0125432A3 EP0125432A3 (en) 1985-04-10
EP0125432B1 EP0125432B1 (fr) 1987-03-04

Family

ID=6195156

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84103053A Expired EP0125432B1 (fr) 1983-03-30 1984-03-20 Dispositif de refroidissement ou séchage pour matériau à gros grains s'écoulant bien

Country Status (5)

Country Link
US (1) US4604814A (fr)
EP (1) EP0125432B1 (fr)
AT (1) ATE25765T1 (fr)
CA (1) CA1246862A (fr)
DE (2) DE3311693C1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU2498177C1 (ru) * 2012-06-09 2013-11-10 Государственное научное учреждение Всероссийский научно-исследовательский институт механизации сельского хозяйства (ГНУ ВИМ Россельхозакадемии) Способ безопасной сушки семян
CN113262170B (zh) * 2021-05-18 2022-09-27 常州市龙城晨光药化机械有限公司 一种片状药品智能加工设备及其加工方法

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US766234A (en) * 1903-03-04 1904-08-02 Edwin Fidell Conveying and delivering means for packaging-machines.
DE448575C (de) * 1924-10-14 1927-08-22 J M Lehmann Fa Trockenanlage fuer Seifenmasse mit einem endlosen Foerderband aus einzelnen Platten
US2000817A (en) * 1933-06-27 1935-05-07 Midland Electric Coal Corp Apparatus for drying loose material
US3009689A (en) * 1958-11-28 1961-11-21 Walter E Hinz Heat treating furnace
US3681855A (en) * 1970-02-05 1972-08-08 Wyssmont Co Inc Nondusting,high temperature dryer
FR2112913A5 (en) * 1970-11-03 1972-06-23 Italiana Essiccatoi Rotating -tray vertical dryer - with oscillating sectors for passage of material and drying gas
DE3028263C2 (de) * 1980-07-25 1982-04-01 Paul Klöckner GmbH, 5239 Nistertal Vorrichtung zur Kühlung oder Trocknung von grobkörnigem, rieselfähigem Gut
US4392310A (en) * 1981-06-18 1983-07-12 Owens-Corning Fiberglas Corporation Drying apparatus

Also Published As

Publication number Publication date
CA1246862A (fr) 1988-12-20
DE3311693C1 (de) 1984-05-24
EP0125432B1 (fr) 1987-03-04
EP0125432A3 (en) 1985-04-10
US4604814A (en) 1986-08-12
ATE25765T1 (de) 1987-03-15
DE3462552D1 (en) 1987-04-09

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