US3587338A - Mechanism for driving rotary kilns - Google Patents

Mechanism for driving rotary kilns Download PDF

Info

Publication number
US3587338A
US3587338A US810509A US3587338DA US3587338A US 3587338 A US3587338 A US 3587338A US 810509 A US810509 A US 810509A US 3587338D A US3587338D A US 3587338DA US 3587338 A US3587338 A US 3587338A
Authority
US
United States
Prior art keywords
gear
bearings
drive gear
pinion
driving
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.)
Expired - Lifetime
Application number
US810509A
Other languages
English (en)
Inventor
Georges Henriot
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.)
Compagnie Engrenages et Reducteurs Messian Durand SA
Original Assignee
Engrenages & Reducteurs
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 Engrenages & Reducteurs filed Critical Engrenages & Reducteurs
Application granted granted Critical
Publication of US3587338A publication Critical patent/US3587338A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
    • 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 specially adapted for rotary-drum furnaces
    • F27B7/26—Drives
    • 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 specially adapted for rotary-drum furnaces
    • F27B7/26—Drives
    • F27B2007/261—Drives working with a ring embracing the drum
    • F27B2007/262—A gear ring combined with a dented wheel drive
    • 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 specially adapted for rotary-drum furnaces
    • F27B7/26—Drives
    • F27B2007/268—Details of the motor or the pinions
    • 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
    • Y10T74/19628—Pressure distributing

Definitions

  • ABSTRACT A mechanism for driving an open-ended rotary kiln or grinder carries a drive gear which meshes with a driving [54] MECHANISMS FOR DRIVING ROTARY KILNS 9 Claims, 7 Drawing Figs.
  • the latter is in turn driven by an output shaft of a second of two planetary gear trains.
  • the gear trains are con- 74/410 F1611 57/00 pled through the planet carrier of the first and the drive gear 74/410, of the second.
  • the gear trains are mounted one one either side 801, 750 of the driving pinion.
  • Examples of such mechanisms are used for driving certain grinders and cement kilns, consisting of a toothed ring (gear ring) fixed to the body that is to be driven, the longitudinal centerline of which coincides with its axis of rotation.
  • a toothed ring (gear ring) fixed to the body that is to be driven, the longitudinal centerline of which coincides with its axis of rotation.
  • One or more pinion wheels each driven through reduction gearing by a motor, mesh with the toothed ring, to which rotary motion is thus imparted.
  • the toothed ring and pinions are generally enclosed in a casing.
  • Such a mechanism enables raw material to be loaded and processed material to be removed through the end by which the hollow container is driven. These operations can be carried out continuously, if required, and in any case without the rotation of the container having to be stopped.
  • An object of the present invention is to at least partially overcome the disadvantages.
  • a mechanism for imparting rotary motion to a grinder, a cement kiln or other hollow body comprising at least one speedreducing gear driven by a motor, said speed-reducing gear including two planetary gear trains, the planet-wheel carrier of the first train being connected to the sun gear of the second train so as to rotate with it, the hollow body being provided with an axial opening, at the outer periphery of which is fitted a drive gear coaxial with that opening, the drive gear operating in conjunction with at least one pinion with a central opening and keyed to the output shaft of the speed-reducing gear, the first and second planetary gear trains being disposed on opposite sides of the pinion and one member of one of the trains being connected to one member of the other train by a spindle passing through the opening of the pinion.
  • the planet wheel carrier of the second planetary train is connected so as to rotate with the pinion that drives the drive gear.
  • annulus gears of the two planetary trains prefferably be rigidly connected to the support of the bearings in which the pinions rotate.
  • the motor driving each reducing gear train is rigidly mounted on the substructure and connected to the reduction gear input shaft by a resilient coupling.
  • a number of rolling and guiding components are disposed between, on the one hand, the end, preferably double walled, of the hollow body, fixed to the drive gear, and/or the drive gear, and, on the other hand, the support carrying the bearings in which the pinions rotate.
  • the rolling and guiding components consist of self-aligning roller bearings disposed in pairs, the bearings in one pair being preferably disposed in a single plane passing through the axis of the opening in the hollow body, there being preferably four pairs of bearings mounted at the corners of a square.
  • each rolling and guiding component consists of an external race, of torus section, the axis of the ring being perpendicular to the axis of the opening in the hollow body.
  • the ring may bear on a shoulder rigidly attached to the opening in the hollow body provided with the drive gear, this shoulder consisting preferably of the drive gear itself.
  • more than two planetary gear trains may be employed.
  • FIG. I is an axial section of a grinder driven by mechanism in accordance with the invention.
  • FIG. 2 shows, in outline, the driving arrangements, as seen by an observer looking in the direction of the arrow F in FIG.
  • FIG. 3 is a section on the line III-III of FIG. 2;
  • FIG. 4 is a section of part of a grinder equipped with mechanism in accordance with the invention.
  • FIG. 5 is a partial perspective view of a grinder equipped with mechanism in accordance with the invention.
  • FIGS. 6 and 7 are sections showing bearing and guidance component assemblies. The description and drawings are given, of course, by way of example only, no limitation on the scope of the invention being thereby implied.
  • the equipment includes a cylindrical hollow body I, which contains material 2. It is supported at one end and is driven at one of its axial ends, for which purpose a drive gear 4 is fast with that end, which, in this embodiment, is supported by the bearing 3.
  • the pinions 5 mesh with the drive gear 4 but are supported by structure 6, centered on the axis of rotation of the body and usually serving additionally as a casing to protect the drive gear and pinions.
  • the cylinders 9 are secured to the floor 11, the stops 8 being secured within their upper ends.
  • FIG. 3 shows diagrammatically various parts of a reduction gear driving one pinion.
  • the driving motor 12 has output shaft 140, and a resilient or splined coupling 13 connects the motor output shaft 14a to the reduction gear input shaft 14b.
  • the reduction gear in the preferred embodiment, includes two planetary gear trains l5 and 16, disposed respectively on opposite sides of the casing 6.
  • the shaft 14b is rigid with the sun gear I7 of the first train, while the planet carrier 18 of the first train and the sun gear 21 of the second train are coupled, so as to rotate together, by a spindle 25. It will be observed that the spindle 25 passes through the pinion 5, which is made hollow for that purpose.
  • the planet carrier 22 of the second train 16 is fast with the pinion 5, while the two annulus or ring gears 20 and 24 are fast with the casing 6.
  • the numerals I9 and 23 designate one of the planet wheels in the first and second planetary trains respectively.
  • FIG. 4 Shown in the form of a half section in FIG. 4 is one end portion 26, of the grinder, to which the toothed ring gear 4 is fixed. If the grinder is likely to contain materials heated to high temperatures, the end portion 26 should have a double wall 26a and 26b, spaced apart and stiffened by intermediate members 27. This end portion 26 may be in the form of a single casting.
  • the drive gear 4, of welded construction, is fixed to the end portion 26 by welds 40, by which the drive gear is secured to the outer end wall 26a.
  • the provision of the walls 26a and 26b enables a cooling fluid to be circulated, which reduces deterioration of the equipment in the course of operation and, of course, reduces the temperature of the walls, especially of the outer wall 26a.
  • the structure 6 must be centered both radially and axially in relation to the end portion 26.
  • each bearing is positioned opposite one of the intermediate members 27 which also acts as a stiffener.
  • the spindle 29 of each bearing 28 is rigid with the structure 6, and the outer race 30 of the bearing bears against the wall 2611.
  • Two seals 31, are fitted between the wall 26a and end portion of the structure 6.
  • the bearings 28 are arranged preferably in pairs, the two bearings in each pair being preferably situated in one and the same plane passing through the axis of the end portion 26 of the hollow body.
  • the bearings of any one pair lie in a line parallel to the axis 32 of the end portion 26; and the axes of the various pairs of bearings 28 in a section taken parallel to the axis 32 are four in number and are situated at the corners of a square.
  • the structure 6 bears against a shoulder integral with the end portion 26, or against the toothed drive gear 4 itself, through the intermediary of bearings 33. There is no need to elaborate on the mounting of such bearings, which is effected in the conventional way, adjustment being obtained by the insertion of shims 34.
  • FIG. 4 a bearing 33 can be seen having its spindle 35 fixed to the structure 6 and its outer race 36 in contact with the drive gear 4.
  • the structure 6 in both directions, in relation to the drive gear 4, it is naturally advisable to provide bearings 33 on each side of the ring 4 i.e. equally spaced around the drive gear.
  • the shape of the inner race 36 should also be noted, with particular reference to the fact that the face of this component bearing against the drive gear 4, resembles that of a torus. In a midplane section of the bearing, this face appears as an arc of a circle. It will be observed that the spindle 35 of the bearing 33 (which is also the axis of the said race) is perpendicular to the axis 32 of the end portion 26.
  • FlGS. 6 and 7 show modifications, in accordance with the invention, in which the bearings 33 bear against a shoulder 37, integral with the end portion 26.
  • This arrangement has the advantage of grouping together the bearings 28 and 33, as well as of making these bearings readily accessible.
  • the sun gear 17 drives the planet wheels 19, which mesh with the teeth on the annulus gear 20, which is stationary in relation to the casing and hence substantially motionless with respect to the ground, and in turn drives the planet wheel carrier 18.
  • the reason for annulus gear being substantially motionless will be apparent from the description given hereinafter.
  • the planet wheel carrier 18 drives the sun gear 21 directly, being rigidly connected to it by the spindle 25.
  • the sun gear 21 drives the planet wheels 23, which, meshing with the teeth on the annulus or ring gear 24, which is substantially motionless with respect to the ground, in turn drives its planet wheel carrier 22.
  • This planet wheel carrier being fixed so as to rotate with the pinion 5, drives through that pinion the drive gear 4 and hence also the grinder.
  • the members fixed to the casing, the annulus gears of both planetary gear trains and the pinion bearings, are substantially motionless with respect to the ground.
  • the rods have a secondary function, which may be mentioned here.
  • the bearing 3 can be relieved of a proportion of the stresses to which it is subjected and can consequently use a bearing of smaller size.
  • the shaft 14! may advantageously be made in the formof two telescopic splined shafts.
  • Axial guidance is provided by the bearings 33.
  • the torusshaped races result in practically point-to-point contact with the drive gear 4 or the shoulder 37. This is important in lengthening the life of the bearings 33, especially of the race 36.
  • this shape eliminates the differences in sliding speed arising over the width of the race when this is externally cylindrical, such differences being the cause of abnormal wear on the conventional cylindrical type.
  • first planetary gear train having a sun gear a plurality of planet wheels, a planet carrier, and an annulus gear
  • second planetary gear train having a sun gear, a plurality of planet wheels, a planet carrier, and an annulus gear
  • the planet carrier of the first planetary gear being coupled to the sun gear of the second planetary gear train, a drive gear fast for rotation with the hollow body and coaxial with the opening thereof
  • a pinion having an opening thereinykeyed to the output shaft of the speed-reducing means, and meshing with the drive gear
  • said first and second planetary gear trains being disposed on opposite sides of the said pinion keyed to the output shaft.
  • a mechanism according the claim 1 comprising,
  • said motor being rigidly mounted on the base structure
  • a mechanism according to claim 1 comprising,
  • said rolling and guiding components being interposed between said mounting structure and said end portion.
  • the bearings in one pair being disposed in a single plane passing through the axis of the opening in the hollow body.
  • each rolling and guiding component has an external race of torus shape in section, the axis of the race being perpendicular to the axis of the opening in the hollow body.
  • a mechanism according to claim 8 in which races of the rolling and guiding components bear against a shoulder rigidly secured to the end portion of the hollow body, said shoulder being provided by the drive gear.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
US810509A 1968-03-27 1969-03-26 Mechanism for driving rotary kilns Expired - Lifetime US3587338A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR145722 1968-03-27
FR182547 1968-12-31

Publications (1)

Publication Number Publication Date
US3587338A true US3587338A (en) 1971-06-28

Family

ID=26181910

Family Applications (1)

Application Number Title Priority Date Filing Date
US810509A Expired - Lifetime US3587338A (en) 1968-03-27 1969-03-26 Mechanism for driving rotary kilns

Country Status (4)

Country Link
US (1) US3587338A (enrdf_load_stackoverflow)
BE (1) BE730586A (enrdf_load_stackoverflow)
DE (1) DE1915661A1 (enrdf_load_stackoverflow)
GB (1) GB1232921A (enrdf_load_stackoverflow)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4090416A (en) * 1974-09-04 1978-05-23 Vickers Limited Gear boxes
US4098139A (en) * 1976-12-15 1978-07-04 Marion Power Shovel Company, Inc. Gear train and method of aligning component gears thereof
US4265136A (en) * 1978-01-10 1981-05-05 Voest-Alpine Aktiengesellschaft Torque support arrangement
US4483408A (en) * 1981-10-03 1984-11-20 Nissan Motor Company, Limited Transaxle final drive arrangement for reducing drive torque reaction transmitted to engine and transmission unit

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4090416A (en) * 1974-09-04 1978-05-23 Vickers Limited Gear boxes
US4098139A (en) * 1976-12-15 1978-07-04 Marion Power Shovel Company, Inc. Gear train and method of aligning component gears thereof
US4265136A (en) * 1978-01-10 1981-05-05 Voest-Alpine Aktiengesellschaft Torque support arrangement
US4483408A (en) * 1981-10-03 1984-11-20 Nissan Motor Company, Limited Transaxle final drive arrangement for reducing drive torque reaction transmitted to engine and transmission unit

Also Published As

Publication number Publication date
BE730586A (enrdf_load_stackoverflow) 1969-09-01
GB1232921A (enrdf_load_stackoverflow) 1971-05-26
DE1915661A1 (de) 1969-10-09

Similar Documents

Publication Publication Date Title
US4391163A (en) Planetary gear assembly
US3213714A (en) Planetary gearing for a circular piston machine
US3854349A (en) Multi-stage speed reducer with resilient shaft supports
US20190291575A1 (en) Epicyclic Gearbox
JPH0617900A (ja) 偏心伝動装置
US3587338A (en) Mechanism for driving rotary kilns
US3390585A (en) Drive for rotating drums
US3127791A (en) Power transfer device
US2878692A (en) Variable transmission
US3213713A (en) Planetary gear device
US2566601A (en) Differential transmission gearing
EP0327032A2 (en) Differential gear device incorporating internal meshing type planetary reduction gear
US4417485A (en) Coupled planetary gear speed reducer for use in industrial vehicles
US4381126A (en) Hydrostatic bearing with rotating sleeve
CN110878816A (zh) 一种单/双输入双输出行星齿轮减速器
CN101363516B (zh) 圆形活齿少齿差变速传动装置
US2208614A (en) Shaft coupling
US4663986A (en) Device for driving multi-drum coiler or un-coiler
US3626789A (en) Axial support for a planetary gearing
US5092189A (en) Machine with at least two high operating force working shafts
PL123705B1 (en) Multi-step planetary reduction gear
SU644985A1 (ru) Зубчата передача дл привода вала в услови х ограниченных габаритов
GB926920A (en) Improvements in or relating to epicyclic gears
US2447136A (en) Locomotive reversing gearing apparatus
US3201106A (en) Tipping mechanism for a steelworks converter