EP0175109A2 - Tambour rotatif - Google Patents

Tambour rotatif Download PDF

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Publication number
EP0175109A2
EP0175109A2 EP85109721A EP85109721A EP0175109A2 EP 0175109 A2 EP0175109 A2 EP 0175109A2 EP 85109721 A EP85109721 A EP 85109721A EP 85109721 A EP85109721 A EP 85109721A EP 0175109 A2 EP0175109 A2 EP 0175109A2
Authority
EP
European Patent Office
Prior art keywords
rotary drum
race
ring
ring gear
drive
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
EP85109721A
Other languages
German (de)
English (en)
Other versions
EP0175109B1 (fr
EP0175109A3 (en
Inventor
Heinrich Dipl.-Ing. Henne
Hubert Dipl.-Ing. Grothaus
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
Priority to AT85109721T priority Critical patent/ATE49905T1/de
Publication of EP0175109A2 publication Critical patent/EP0175109A2/fr
Publication of EP0175109A3 publication Critical patent/EP0175109A3/de
Application granted granted Critical
Publication of EP0175109B1 publication Critical patent/EP0175109B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C17/00—Disintegrating by tumbling mills, i.e. mills having a container charged with the material to be disintegrated with or without special disintegrating members such as pebbles or balls
    • B02C17/18—Details
    • B02C17/181—Bearings specially adapted for tumbling mills
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C17/00—Disintegrating by tumbling mills, i.e. mills having a container charged with the material to be disintegrated with or without special disintegrating members such as pebbles or balls
    • B02C17/18—Details
    • B02C17/24—Driving mechanisms
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/19642—Directly cooperating gears
    • Y10T74/19647—Parallel axes or shafts
    • Y10T74/19651—External type

Definitions

  • the invention relates to a rotary drum according to the preamble of claim 1.
  • Rotary drums of the required type can basically be designed in the form of tube mills, mixing drums, drying drums, rotary tube furnaces and the like, with material to be treated (e.g. to be comminuted, mixed or subjected to heat exchange) being moved in the axial direction through the drum in this rotary drum.
  • material to be treated e.g. to be comminuted, mixed or subjected to heat exchange
  • the invention is therefore based on the object of improving a rotary drum of the type required in the preamble of claim 1 in such a way that, particularly with regard to the drum mounting and the rotary drive, there is a substantial structural simplification compared to known designs, while at the same time being particularly reliable and stable Construction.
  • a race and the ring gear are firmly connected to one another by a radial ring flange, they form an extremely stable structural unit which requires only a relatively small space and in which the ring flange at the same time means a stiffening of the race, which causes radial deformation of the race can be reduced to a minimum.
  • This also results in improvements in the bearing behavior over the bearing width of the race and savings options for the inner stiffening of the race, which are either made weaker or can be omitted entirely.
  • the common assembly of ring gear and race also makes it possible in an extremely advantageous manner to provide a common housing for the bearing elements of the race and the rotary drum drive, which, among other things, further reduces space need and considerable ease of assembly can be achieved.
  • this common housing is also favored by the fact that an axial guide is provided for the assembly of the ring gear and the race. This axial guidance ensures a particularly reliable mode of operation of the rotating drum in the area of the ring gear and the race ring through a consistently good meshing engagement between the drive pinion and the ring gear and through a very reliable mounting of the race ring on its bearing elements.
  • the rotary drum according to the invention is illustrated in the drawing in the form of a tube mill 1.
  • this tube mill 1 can largely be designed and constructed in a manner known per se. It has a rotating drum jacket 2 and - in the illustrated embodiment - at one end, namely the inlet end, a grist inlet 4 leading into a hollow spigot 3 and at the other end (outlet end) another hollow spigot 5, from which sufficiently ground material (arrow 6) from the Mill emerges.
  • a first race 7 is fastened coaxially to it in the region of the inlet end, whereby this first race 7 can be supported on conventional bearing elements, ie either on rollers or - as in FIG. 1 indicated - on hydrostatic or hydrodynamic plain bearing shoes 8.
  • a second race 9 is fastened coaxially to the outer circumferential side of the rotating drum shell 2, which is in the same manner as the first run ring 7 is rotatably supported on known bearing elements, in particular on hydrostatic or hydrodynamic plain bearing shoes 10.
  • a ring gear 11 is arranged in a rotationally fixed manner, which - as will be explained in more detail below - is fastened directly to the second race 9 and thus forms a structural unit.
  • This ring gear 11 is in mesh with at least one drive pinion 12 (see FIG. 3, right half), which is part of a rotary drum drive 13 to be explained.
  • the second race 9 is provided at its two axial ends with a radially extending ring flange 9a and 9b, which - according to FIG. 2 - both protrude radially outwards.
  • the race 9 is screwed to an end flange 2a of the rotating drum shell 2 (as indicated by a dash-dotted line), so that the second race 9 represents an immediate axial extension of the rotating drum shell 2, but has a greater material thickness than the drum shell 2 (see Fig. 2).
  • the ring gear 11 is firmly screwed onto the second ring flange 9b of this race 9 (see dash-dot center line 14 of the screws), the outer diameter of which is kept somewhat larger than the race 9.
  • the ring gear 11 expediently has a T-shaped cross section, the radially inwardly extending web 11a at the same time forms a type of fastening flange and serves as a counter flange to the race flange 9b, while the teeth 11b are provided on the outer circumferential side of the T-shaped flange.
  • the ring gear 11 is thus fixed axially from the outside and yet is easy to install and replace on the outer end of the second race 9 and thus on the axially outer end of the rotating drum shell 2. Because of this arrangement, the ring gear 11 can be expediently designed in the form of an undivided (one-piece) ring which is distinguished by a low overall height. At the same time, the axial end faces of this ring gear 11 and in particular of its T-flange 11c are preferably designed such that they can serve as axial guide surfaces 15, 15a.
  • two brackets 17, 17a are arranged in a stationary manner (for example on the foundation 16), which are in the manner of partial ring flanges can be formed and on their mutually facing sides each carry sliding blocks 18, 18a made of low-friction material, which are in sliding engagement with the axial guide surfaces 15, 15a of the ring gear 11.
  • the axial guide surfaces 15, 15a with the fixedly held sliding blocks 18, 18a form an axial guide for the assembly of the toothed ring 11 and the race 9.
  • a common housing 19 for these slide bearing shoes 10 and the rotary drum drive 13 is also provided in a fixed position.
  • this housing 19 is composed of a number of segment-like housing parts 19 a, which can be easily assembled and disassembled, in such a way that the common housing 19 also protects the assembly of the second race 9 and ring gear 11 surrounds.
  • This common housing 19 or its housing parts 19a is or are provided with axial end walls 19b and 19c, on whose radially inner edges suitable sealing elements 20 are held, which are provided with the outer circumferential side of the race 9 or one on the ring gear 11 accordingly axial, annular extension 21 are in frictional or sealing engagement.
  • the previously described design and arrangement of the housing 19 is a particularly favorable prerequisite for the ring gear 11 and its drive pinion 12 as well as the second race 9 and its bearing elements (slide bearing shoes 10) to have common oil circulation lubrication, which may be of a conventional design and therefore not closer is illustrated.
  • this common housing 19 there are also the stationary sliding blocks 18, 18a.
  • the rotary drum drive 13 is arranged such that it can be adjusted with respect to the ring gear 11 and possibly also the bearing shoes 10 of the race 9 with the common housing 19 with respect to the assembly of the race 9 and ring gear 11, which is particularly useful for assembly, but also has a favorable effect for a later message possibility.
  • the indicated rotary drum drive 13 is designed and arranged in such a way that it has an output pinion which at the same time forms the drive pinion 12 for the ring gear 11.
  • this also means that intermediate drive elements, such as couplings, shafts, separate bearings, etc., can be dispensed with. The torque of the transmission output pinion is thus transferred directly to the ring gear 11 of the tube mill 1 wear.
  • the partial cross section according to FIG. 4 shows an embodiment variant of the rotary drum drive 13 ', the main difference from the previous description is that the rotary drum drive 13' has two driven pinions, each of which simultaneously forms a drive pinion 12 'for the ring gear 11. In an advantageous and space-saving manner, these two drive pinions 12 'can be arranged vertically one above the other. Otherwise, this embodiment variant according to FIG. 4 does not differ from the previously described embodiment.
  • each drive pinion 12 or 12 ' it should be noted that it is preferred to do this with the associated output shaft of the rotary drum drive 13 or 13' itself to perform adjusting. In this way, occasional minor axial displacements or displacements of the rotating drum shell 2 can be compensated for.
  • the race 9 can have an approximately radially inward, web-like pad 23 on its inner circumferential side for the purpose of further stiffening the race.
  • this race 9 - instead of the flange connection with the flanges 2a and 9a - can be welded directly axially against the end of the rotary drum shell 2 facing it (as is known per se), but in any case on the other end of the race 9
  • an annular flange for example 9b
  • this ring flange provided for fastening the ring gear 11 does not necessarily have to be directed radially outward, but can also extend radially inward if necessary).
  • FIG. 1 Another embodiment variant is indicated by dash-dotted lines in FIG.
  • the assembly of the ring gear and the race does not necessarily have to be attached in the area of the outer circumferential side of the drum shell 2, but this assembly can - as in 24 with dash-dot lines interpreted - also on the outer circumferential side of a bearing or hollow pin, in the illustrated case of the hollow pin 5 at the outlet, attached.
  • the training and arrangement can - with appropriate adaptation - be the same as in the previously described cases.

Landscapes

  • Engineering & Computer Science (AREA)
  • Food Science & Technology (AREA)
  • Discharging, Photosensitive Material Shape In Electrophotography (AREA)
  • Retarders (AREA)
  • Rolling Contact Bearings (AREA)
  • Structure Of Transmissions (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Centrifugal Separators (AREA)
  • General Details Of Gearings (AREA)
  • Crushing And Grinding (AREA)
EP85109721A 1984-09-14 1985-08-02 Tambour rotatif Expired - Lifetime EP0175109B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85109721T ATE49905T1 (de) 1984-09-14 1985-08-02 Drehtrommel.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3433905 1984-09-14
DE19843433905 DE3433905A1 (de) 1984-09-14 1984-09-14 Drehtrommel

Publications (3)

Publication Number Publication Date
EP0175109A2 true EP0175109A2 (fr) 1986-03-26
EP0175109A3 EP0175109A3 (en) 1988-03-23
EP0175109B1 EP0175109B1 (fr) 1990-01-31

Family

ID=6245474

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85109721A Expired - Lifetime EP0175109B1 (fr) 1984-09-14 1985-08-02 Tambour rotatif

Country Status (7)

Country Link
US (1) US4911554A (fr)
EP (1) EP0175109B1 (fr)
AT (1) ATE49905T1 (fr)
BR (1) BR8504313A (fr)
DE (2) DE3433905A1 (fr)
ES (1) ES8700834A1 (fr)
ZA (1) ZA856059B (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4140388A1 (de) * 1991-12-07 1993-06-09 Deutsche Babcock Energie- Und Umwelttechnik Ag, 4200 Oberhausen, De Rohrmuehle
DE19542563A1 (de) * 1995-11-15 1997-05-22 Flender A F & Co Vorrichtung zur Abdichtung einer Schutzhaube eines Mühlenkörpers
EP0976455A1 (fr) 1998-07-22 2000-02-02 KHD Humboldt-Wedag AG Pignon pour entraínement du type roue dentée/pignon

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE467953B (sv) * 1991-02-05 1992-10-12 Sala International Ab Saett att driva en kvarn som har en laangstraeckt, cylindrisk kvarnkropp samt kvarn foer utfoerande av saettet
DE19753576B4 (de) * 1997-12-03 2007-07-12 Khd Humboldt Wedag Gmbh Zahnkranz für einen Zahnkranzantrieb von Drehtrommeln
DE10114294A1 (de) 2001-03-23 2002-09-26 Kloeckner Humboldt Wedag Antriebseinrichtung für eine Rohrmühle
US6592250B1 (en) * 2001-05-30 2003-07-15 Paul Gement Chamber apparatus for treating waste and removing the waste following treatment
EP1490177A1 (fr) * 2002-04-03 2004-12-29 MAAG Gear AG Dispositif d'entrainement pour corps rotatifs pouvant tourner horizontalement
DE502004000382D1 (de) * 2003-07-10 2006-05-11 Hauni Maschinenbau Ag Vorrichtung zum Herstellen von stabförmigen Tabakproduken mit einem Filter, insbesondere von Filterzigaretten
DE102007031081B4 (de) 2007-07-04 2015-08-06 Büttner Energie- und Trocknungstechnik GmbH Drehtrommel
FR2954964B1 (fr) * 2010-01-06 2012-10-26 Cie Engrenages Et Reducteurs Messian Durand Dispositif d'entrainement pour une couronne dentee et broyeur correspondant.
DE102011009614B4 (de) 2010-02-04 2015-03-05 Takraf Gmbh Antrieb für die Trommel eines Trommelrückladegerätes
EP2542849B1 (fr) * 2010-03-01 2015-04-01 ThyssenKrupp Industrial Solutions AG Entraînement pour un tambour rotatif
CN104583619B (zh) 2012-06-28 2017-12-12 奥图泰（芬兰）有限公司 流体轴承的改进
CN103743224A (zh) * 2014-01-20 2014-04-23 黄石市建材节能设备总厂 零水平推力双驱动重型烘干机
US10967384B2 (en) * 2018-10-19 2021-04-06 Outotec (Finland) Oy Grinding mill

Family Cites Families (27)

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Publication number Priority date Publication date Assignee Title
DE7433008U (de) * 1975-01-16 Koppatz R Drehofen mit Antrieb für mindestens zwei Laufrollen
CH19706A (de) * 1899-06-10 1900-08-31 Herman Hinz Rollenlager für rotierende Trommeln
US694565A (en) * 1899-10-25 1902-03-04 Taylor Iron And Steel Co Revolving screen.
US1520537A (en) * 1923-03-16 1924-12-23 Markus Louis De Method and apparatus for pulverizing
US2298016A (en) * 1941-03-29 1942-10-06 Allis Chalmers Mfg Co Rotary scrubber and method of scrubbing ore
DE738695C (de) * 1942-03-03 1943-08-27 Kloeckner Humboldt Deutz Ag Antrieb fuer Drehtrommeln, insbesondere Rohrmuehlen
US2420217A (en) * 1943-04-16 1947-05-06 Allen Sherman Hoff Co Automatic dust removing system
US2396057A (en) * 1943-10-11 1946-03-05 Smidth & Co As F L Mill
US2399122A (en) * 1944-07-15 1946-04-23 Allis Chalmers Mfg Co Adjustable mounting for ring gears
US2447605A (en) * 1944-08-24 1948-08-24 Smidth & Co As F L Mill bearing construction
DE894036C (de) * 1945-06-20 1953-10-22 Joseph Elliott Kennedy Rohrmuehle mit Hohlzapfen
DE888640C (de) * 1946-02-09 1953-09-03 Smidth & Co As F L Zahnkranzantrieb fuer Drehtrommeln von Trommelmuehlen
US2441901A (en) * 1946-02-09 1948-05-18 Smidth & Co As F L Mill
US2661813A (en) * 1948-06-10 1953-12-08 Joseph E Kennedy Lubricating means for tube mills
US2908179A (en) * 1957-08-16 1959-10-13 Vulcan Iron Works Rotary kiln
US3036823A (en) * 1959-06-18 1962-05-29 Simon Srybnik Rotary kiln
DE1433871A1 (de) * 1962-06-07 1968-10-17 Srybnik Simon Antriebs- und Laengsschubaufnahmemechanismus fuer umlaufende OEfen
GB1038157A (en) * 1962-07-12 1966-08-10 Niehaus Engineering S A Improvements in and relating to mixing devices
FR2186115A5 (fr) * 1972-05-25 1974-01-04 Creusot Loire
GB1381583A (en) * 1973-04-06 1975-01-22 Smidth & Co As F L Rotary drums
DE2446941A1 (de) * 1974-10-02 1976-04-22 Rudolf Koppatz Antrieb fuer einen drehofen
DE2607594C2 (de) * 1976-02-25 1985-01-31 Thyssen Industrie Ag, 4300 Essen Zahntriebbaureihe für den Antrieb von Drehtrommeln, insbesondere Rohrmühlen
US4234237A (en) * 1977-03-29 1980-11-18 Maschinenfabrik Andritz Aktiengesellschaft Bearing for heavy steel drums, in particular decorticating drums
DE2758293C3 (de) * 1977-12-27 1982-04-22 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 4200 Oberhausen Mischerwagen für den Transport von geschmolzenen Metallen
DE2855307A1 (de) * 1978-12-21 1980-07-10 Rtl Contactor Holding Sa Vorrichtung zur kontaktbehandlung von fluessigkeiten und feststoffen mit fluessigkeiten
CA1129197A (fr) * 1979-02-16 1982-08-10 Dominion Engineering Works Limited Entrainement pour tambour chauffe de sechoir
US4470324A (en) * 1981-10-19 1984-09-11 Carol A. MacKay Gear case

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4140388A1 (de) * 1991-12-07 1993-06-09 Deutsche Babcock Energie- Und Umwelttechnik Ag, 4200 Oberhausen, De Rohrmuehle
DE4140388C2 (de) * 1991-12-07 2002-04-18 Babcock Energie Umwelt Rohrmühle
DE19542563A1 (de) * 1995-11-15 1997-05-22 Flender A F & Co Vorrichtung zur Abdichtung einer Schutzhaube eines Mühlenkörpers
EP0976455A1 (fr) 1998-07-22 2000-02-02 KHD Humboldt-Wedag AG Pignon pour entraínement du type roue dentée/pignon

Also Published As

Publication number Publication date
DE3433905A1 (de) 1986-03-27
ES546903A0 (es) 1986-11-16
ES8700834A1 (es) 1986-11-16
BR8504313A (pt) 1986-07-01
ZA856059B (en) 1986-04-30
ATE49905T1 (de) 1990-02-15
EP0175109B1 (fr) 1990-01-31
DE3575682D1 (de) 1990-03-08
EP0175109A3 (en) 1988-03-23
US4911554A (en) 1990-03-27

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