EP0542932A1 - Corps rotatifs. - Google Patents

Corps rotatifs.

Info

Publication number
EP0542932A1
EP0542932A1 EP92904221A EP92904221A EP0542932A1 EP 0542932 A1 EP0542932 A1 EP 0542932A1 EP 92904221 A EP92904221 A EP 92904221A EP 92904221 A EP92904221 A EP 92904221A EP 0542932 A1 EP0542932 A1 EP 0542932A1
Authority
EP
European Patent Office
Prior art keywords
ring
elements
rotating body
spring
holding
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
EP92904221A
Other languages
German (de)
English (en)
Other versions
EP0542932B1 (fr
Inventor
Reinhard Vits
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.)
Pleq Plant & Equipment Engineering GmbH
Pleq Plant & Equipment Enginee
Original Assignee
Pleq Plant & Equipment Engineering GmbH
Pleq Plant & Equipment Enginee
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 Pleq Plant & Equipment Engineering GmbH, Pleq Plant & Equipment Enginee filed Critical Pleq Plant & Equipment Engineering GmbH
Priority to EP92904221A priority Critical patent/EP0542932B1/fr
Publication of EP0542932A1 publication Critical patent/EP0542932A1/fr
Application granted granted Critical
Publication of EP0542932B1 publication Critical patent/EP0542932B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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
    • F27D1/00—Casings; Linings; Walls; Roofs
    • F27D1/0003—Linings or walls
    • F27D1/0023—Linings or walls comprising expansion joints or means to restrain expansion due to thermic flows
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F26—DRYING
    • F26B—DRYING SOLID MATERIALS OR OBJECTS BY REMOVING LIQUID THEREFROM
    • F26B11/00—Machines or apparatus for drying solid materials or objects with movement which is non-progressive
    • F26B11/02—Machines or apparatus for drying solid materials or objects with movement which is non-progressive in moving drums or other mainly-closed receptacles
    • F26B11/022—Arrangements of drives, bearings, supports
    • 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
    • F27B7/22—Rotary drums; Supports therefor
    • F27B7/2206—Bearing rings
    • 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
    • F27B7/22—Rotary drums; Supports therefor
    • F27B7/2206—Bearing rings
    • F27B2007/2213—Bearing rings mounted floatingly on the drum
    • F27B2007/2226—Bearing rings mounted floatingly on the drum the mounting comprising elements to maintain the ring between series of abutments
    • 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
    • F27B7/22—Rotary drums; Supports therefor
    • F27B2007/2246—Support rollers

Definitions

  • the invention relates to a rotating body, in particular a rotating tube, with at least two rings for storage and / or drive, which encompass the outer sides of the rotating body, in each case a plurality of holding shoes which are evenly distributed over the circumference and which rest against the rotating body and which are connected to the Ring are connected to move radially inwards, and with a tensioning device, which is arranged coaxially on the ring and is designed to be movable relative to it in the circumferential direction and which is connected to transmission means for all holding shoes of the ring, and with at least one prestressable spring element between the ring and tensioning device, that acts in the circumferential direction on the tensioning device.
  • rotating bodies for example rotating tubes, such as those used for the thermal treatment of bulk materials, sludges or the like by direct or indirect heating
  • storage is carried out via at least two bearing rings which are fastened at a distance from one another on the outer circumference of the rotating tube and can be adjusted via corresponding Support
  • REPLACEMENT LEAF support roll on a foundation The drive then takes place via a toothed ring which, depending on the size of the rotary tube, is connected to a drive device via one or two drive pinions and which is either arranged as a separate ring on the outer circumference of the rotary tube or is integrated in a race.
  • An essential problem with such races is given by the different temperatures and thus different thermal expansions of the rotary tube and the race.
  • the problems that arise here are even more difficult to solve if such rotary tubes are to be used for high-temperature treatments and / or the body on the one hand and the rings on the other hand are made of materials with different coefficients of thermal expansion. The same problems occur with cooling or mixing tubes.
  • the disadvantage of the known arrangement is that, due to the absolutely necessary elongated holes in the articulation between the frame element and the angle lever, there is also play in the radial direction, so that the required centering of the rotating body on the axis of rotation predetermined by the ring is accordingly not possible .
  • This has a disadvantageous effect, in particular in the case of larger rotary tube diameters, since here, together with the rotary tube filling, large weights and thus large forces have to be mastered.
  • the constructively predetermined play then leads to the articulations between the angle lever and the frame element deflecting after a relatively short period of operation.
  • Another disadvantage to be considered is that with correspondingly large rotary tube diameters
  • the invention is based on the object of providing a bearing for a rotating body of the type mentioned at the outset, which ensures a practically unlimited service life, in particular in the case of large differences with regard to the coefficient of thermal expansion of the materials used for the body on the one hand and the materials used for the ring on the other .
  • the tensioning device is formed in each case from a plurality of tensioning elements running in the circumferential direction, that in each case one tensioning element is articulated to the transmission means of two adjacent holding shoes, that the transmission means are each connected to the ring in the Rotary plane pivotally mounted pressure element is formed, on the outward-facing side of the clamping elements of the adjacent pressure elements are articulated and the inward-facing side is connected to a holding shoe and that the connecting lines of the articulation points of two adjacent pressure elements on the ring and the articulation points of the these connecting clamping elements essentially form a parallelogram.
  • Such an arrangement has the advantage that the rotating body and ring are connected to one another with respect to their geometric axes, i.e. both axes always coincide regardless of different thermal expansions. Since the articulation points of two adjacent pressure elements and the articulation points of the tensioning elements connecting them form a parallelogram, so that the tensioning device as a whole is a closed system strung together
  • REPLACEMENT LEAF Radial displacement of the articulation points of the tensioning elements with the pressure elements with respect to the "ring" of the tensioning elements does not change the dimension in the circumferential direction, so that a perfect mobility of the tensioning device and thus a perfect radial mobility are also achieved by the holding shoes large diameter differences is guaranteed.
  • the prestressable spring element acting in the circumferential direction several spring elements are expediently provided, is now connected at one end to the ring and at its other end to the tensioning device, advantageously with a pressure element.
  • the direction of action of the spring force is now designed so that the spring force presses the holding shoes against the outer surface of the rotating body via the pressure elements.
  • the parallelogram arrangement according to the invention has the effect that such an increase in diameter compared to the ring is recorded without any constraint.
  • the changes in diameter that occur here are relatively small in relation to the length changes of the spring elements caused thereby, so that only an insignificant increase in the spring forces is brought about, ie the holding shoes are pressed against the outer circumference of the rotating body with a practically constant contact pressure in every operating state pressed.
  • REPLACEMENT LEAF Contact pressure is selected for a ring, via which the drive torque is also transmitted, such that the friction between the holding shoes on the one hand and the surface of the rotating body on the other hand is sufficient to transmit the drive torque.
  • webs running in the longitudinal direction can also be arranged on the outer surface of the rotating body, against which the holding shoes are supported in the circumferential direction, so that here a positive fit with regard to the transmission of the torque Connection is given.
  • the tensioning element is formed by a tension rod which is preferably adjustable in length. This enables precise adjustment of the tensioning device and thus precise centering of the rotating body with respect to the supporting ring.
  • a plurality of spring elements are provided which are dimensioned such that the sum of the radial forces acting on the holding shoes via the spring elements is at least approximately equal to the proportion by weight of the rotating body with filling which is associated with the ring in question in the operating state plus the force for the required frictional engagement.
  • This dimensioning ensures that there is no load change in the spring learners during operation as a result of the rotation of the rotating body and therefore no relative movements between the rotating body on the one hand and the supporting ring. Only the holding shoes experience a radial displacement if, due to changes in the temperature, the diameter of the rotating body changes compared to the diameter of the ring. If the friction lock is designed accordingly, a required torque can also be transmitted between the holding shoes and the rotating body.
  • the tensioning elements are at least partially formed by spring bodies.
  • the spring bodies forming the tensioning elements which are arranged between the pressure elements, have no or only negligible forces in the radial direction, ie in the direction of the rotating body, in the case of dimensional deviations.
  • This is in turn brought about by the fact that the axis of the respective spring body runs parallel to the connecting line of the articulations of the pressure elements connected by the spring body, so that the system is in equilibrium in every pivoting position of the pressure body, regardless of that between the tensioning device and the ring act- • the spring element.
  • the spring bodies located in the parallelograms arranged next to one another have the same spring force, except for negligible deviations from one another which are brought about by frictional resistances in the individual bearings. It is expedient to provide adjusting means for the articulation of the spring bodies on the pressure elements in order to be able to adjust the tension of the individual spring bodies or to adjust the distance between the articulation points of each spring body to the bearing distance of the two pressure elements assigned to the respective spring body to get the "parallelogram effect". Dimensional deviations on the pressure elements and / or in the region of the articulation of the holding shoes on the pressure elements as well as dimensional deviations of the rotating body are compensated for by the arrangement of such spring bodies.
  • the force in the spring bodies must be at least equal to the sum of the forces of the spring elements acting between the tensioning device and the ring plus the frictional resistances in the bearings of the tensioning device and the transmission means.
  • the holding shoe on its side facing the body is an intermediate piece made of a material with less heat.
  • REPLACEMENT LEAF Has conductivity as steel, preferably made of a ceramic material. This ensures that the contact surfaces between the holding shoe and the wall of the body practically do not act as a "heat sink” and thus no process heat is drawn off. Another advantage is that only a little heat flows into the ring via the holding shoes.
  • FIG. 1 is a side view of a rotary tube
  • Fig. 3 shows the formation of a holding shoe on a larger scale.
  • the rotary tube 1 shown in FIG. 1 has a body 2 which is connected in its end regions to rings 3, 4, which are each supported on a pair of rollers 5 and 6.
  • the pairs of rollers 5 and 6 are here
  • REPLACEMENT LEAF aligned so that the longitudinal axis of the rotary tube runs at an angle to the horizontal of, for example, 5 °.
  • the inclination of the rotary tube can be between 0 ° for rotary tubes with conveyor fittings and 5 ° for rotary tubes with a smooth inner wall.
  • a loading device 8 is connected to the upper end 7.
  • a discharge housing 10 is assigned to the lower end 9. The rotary tube 1 is sealed off from the charging device 8 and the discharge housing 10 by means of appropriate seals, depending on the intended use and type of heating, in a dustproof and / or gas-tight manner.
  • the longitudinal thrust caused by the inclination is intercepted by at least one support roller 11 which, in the exemplary embodiment shown, rests on the end face of the ring 4.
  • the support roller 11 can be displaceably mounted in the direction of the longitudinal axis of the furnace via a corresponding drive, in order to periodically move the furnace back and forth in the longitudinal direction in order to "run in" the
  • the rotary tube is driven via one of the rings 3, 4, which at the same time have a toothed part in a manner not shown here, which takes place on the end face or also via a tooth part with a corresponding toothed pinion and drive motor, which is offset in diameter from the running surface 12 of a ring can.
  • the drive can also take place via a corresponding chain drive.
  • the bearing and / or the drive can also be designed in the form of a large roller bearing or a ball slewing ring.
  • the ring 3 which is supported on the pair of rollers 5, is with the body 2 over several, evenly over the circumference.
  • REPLACEMENT LEAF Distributed holding shoes 13 connected, which rest on the outer surface of the body 2. Two holding shoes are shown in FIG. The total number depends essentially on the diameter of the body used, generally for preventing deformations and for
  • the holding shoes 13 each have a shoulder 14, by means of which they are articulated to a pressure element 15, which forms the transmission means between the tensioning device to be described in more detail below and the holding shoe 13.
  • the pressure elements 15 are pivotally mounted about an A steering point 16 in the plane of rotation of the ring.
  • the pressure elements 15 are connected to one another via clamping elements 17.
  • the tensioning elements 17 are designed as length-adjustable tensioning rods which each connect two adjacent pressure elements 15 to one another via articulation points 18.
  • spring elements 21 are now provided, in the illustrated embodiment there are tension spring elements , which are fixed at their one end to an adjustable holding device 22 on the ring 3 and with their other end to a pressure element 15.
  • the spring elements 21 now try to pivot the pressure elements 15 in the direction of the arrow 23 and thus cause the holding shoes 13 to be pressed onto the outer surface of the rotating body 2, that is to say the tensioning device is "closed”.
  • the connecting line between two adjacent articulation points 16 runs parallel to the alignment of the connecting line between two adjacent articulation points 18 and the quadrilateral joint formed by the adjacent articulation points 16 and 18 forms a parallelogram, as is indicated in the drawing by the dash-dotted lines.
  • the "parallelogram chain" thus formed enables the entire tensioning device to move freely without any constraint, so that the articulation points 16 and 18 as well as the articulation 19 of the holding shoe 13 can be designed as play-free bearings.
  • tensioning elements 17, which are designed as tension rods in the illustrated embodiment, are preferably designed to be longitudinally adjustable, for example as a threaded sleeve with opposing threads at both ends, into which eye bolts forming the articulation are screwed.
  • the spring bodies serving as tensioning elements 17 must, however, be much harder in relation to the spring elements 21, so that the set force of a spring body must be at least the same as the sum of the forces applied by the spring elements 21 with greater prestressing plus the frictional resistances in the articulations 16, 18 and 19, wherein the different radial spacing of the fastening of the spring elements 21 to the pressure elements 15 and the articulation of the spring bodies forming the tensioning elements 17 and the resulting lever ratio must be taken into account.
  • the holding shoes 13 are constructed in two parts. The part lying directly on the rotating body 2 is separated by an intermediate
  • HE 13 pieces 24 made of a material with a lower thermal conductivity than steel, for example a ceramic material, which is connected via a cup-shaped holder 25 made of metal to the attachment 14, which is also made of metal. This on the one hand ensures a reduction in the heat flow and on the other hand gives the possibility of also producing the rotary tube from ceramic, which enables operating temperatures of, for example, 1,500 ° C.
  • the intermediate piece 24 ensures that heat is transferred to the metal holder 25 only to a reduced extent and that no damage can occur.
  • the rotating body 2 can be provided on its outer surface with two circumferential webs 26, by means of which the holding shoes 13 can be supported in the axial direction.
  • the webs 26 can be welded on. In the case of a ceramic body, these webs can be molded directly onto the outer surface of the rotating body 2.
  • ring in the sense of the invention encompasses both the classic races described in the exemplary embodiment and corresponding drive sprockets, as well as large roller bearings, sprockets for a chain drive or the like.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Heat Treatment Of Articles (AREA)
  • Holding Or Fastening Of Disk On Rotational Shaft (AREA)
  • Spinning Or Twisting Of Yarns (AREA)
  • Clamps And Clips (AREA)
  • Support Of The Bearing (AREA)

Abstract

Dans le cas de corps rotatifs, par exemple des tuyaux rotatifs à paliers annulaires, le problème se pose de relier les anneaux (3, 4), qui peuvent également servir d'éléments d'entraînement, au corps tubulaire (2), de sorte que les variations du diamètre du corps tubulaire provoquées par des dilatations thermiques puissent être neutralisées de manière fiable. L'utilisation d'éléments élastiques de soutien a l'inconvénient d'obliger les éléments élastiques à soutenir le poids du tuyau rempli, de sorte que ceux-ci n'ont qu'une vie utile limitée, compte tenu des alternances constantes de l'effort. Au moyen de sabots de retenue (13) radialement mobiles dans l'anneau (3, 4) et qui s'appuient sur le corps tubulaire (2), on peut appliquer sur les sabots de retenue (13) des forces radiales de compression par l'intermédiaire des éléments de serrage (17) montés sur l'anneau (3) et mobiles dans le sens de la circonférence, lorsque les éléments de serrage (17) sont serrés contre l'anneau (13) au moyen d'éléments élastiques (21) susceptibles d'être précontraints. Le dispositif se centre automatiquement et les éléments élastiques ne sont pas soumis à des alternances d'effort, même en cas de variation du diamètre du corps tubulaire (2).
EP92904221A 1991-05-29 1992-02-01 Corps rotatifs Expired - Lifetime EP0542932B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP92904221A EP0542932B1 (fr) 1991-05-29 1992-02-01 Corps rotatifs

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
PCT/EP1991/000997 WO1992021923A1 (fr) 1991-05-29 1991-05-29 Corps de revolution
EP9100997 1991-05-29
PCT/EP1992/000216 WO1992021924A1 (fr) 1991-05-29 1992-02-01 Corps rotatifs
EP92904221A EP0542932B1 (fr) 1991-05-29 1992-02-01 Corps rotatifs

Publications (2)

Publication Number Publication Date
EP0542932A1 true EP0542932A1 (fr) 1993-05-26
EP0542932B1 EP0542932B1 (fr) 1995-09-27

Family

ID=8165591

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92904221A Expired - Lifetime EP0542932B1 (fr) 1991-05-29 1992-02-01 Corps rotatifs

Country Status (4)

Country Link
EP (1) EP0542932B1 (fr)
AT (1) ATE128541T1 (fr)
DE (1) DE59203834D1 (fr)
WO (2) WO1992021923A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9689611B2 (en) * 2014-08-20 2017-06-27 Gencor Industries, Inc. Locking cam stop
FR3029277A1 (fr) * 2014-11-27 2016-06-03 Adv Thermic Dispositif d'entrainement a haute temperature, pour four tournant dont le laboratoire est constitue d'un tube creux traversant de part en part la chambre de chauffe
CN115156193A (zh) * 2022-06-13 2022-10-11 江苏省产品质量监督检验研究院 一种细晶粒化热轧钢筋防腐加工定位装置

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2127721B2 (de) * 1971-06-04 1973-07-05 Verlagerung umlaufender und mit rollen gefuehrter ofenkoerper
GB1482358A (en) * 1975-09-17 1977-08-10 Smidth & Co As F L Rotary drums
SU775585A1 (ru) * 1978-11-24 1980-10-30 За витель Узел креплени бандажа на корпусе вращающегос барабана
SU872922A1 (ru) * 1979-12-14 1981-10-15 За витель И. И. Бесценный Узел креплени бандажа на корпусе вращающегос барабана
SU1250811A1 (ru) * 1984-10-31 1986-08-15 Mikolskij Yurij N Узел креплени бандажа на корпусе вращающейс печи
DE3633892A1 (de) * 1986-10-04 1988-04-07 Hanf Carl Elino Ind Ofenbau Lagerungssystem fuer die trommel einer ofenanlage
DE4023230A1 (de) * 1990-07-21 1992-01-23 Pleq Plant & Equipment Enginee Drehrohr

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9221924A1 *

Also Published As

Publication number Publication date
ATE128541T1 (de) 1995-10-15
WO1992021923A1 (fr) 1992-12-10
EP0542932B1 (fr) 1995-09-27
WO1992021924A1 (fr) 1992-12-10
DE59203834D1 (de) 1995-11-02

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