US3880302A - Drive and support mechanism for rotary and angularly adjustable member - Google Patents

Drive and support mechanism for rotary and angularly adjustable member Download PDF

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Publication number
US3880302A
US3880302A US368867A US36886773A US3880302A US 3880302 A US3880302 A US 3880302A US 368867 A US368867 A US 368867A US 36886773 A US36886773 A US 36886773A US 3880302 A US3880302 A US 3880302A
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United States
Prior art keywords
gear
drive
disc
rotary
support
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Expired - Lifetime
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US368867A
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English (en)
Inventor
Edouard Legille
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Paul Wurth SA
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Anciens Etablissements Paul Wurth SA
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    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21B—MANUFACTURE OF IRON OR STEEL
    • C21B7/00—Blast furnaces
    • C21B7/18—Bell-and-hopper arrangements
    • C21B7/20—Bell-and-hopper arrangements with appliances for distributing the burden
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • 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
    • F16H2700/00—Transmission housings and mounting of transmission components therein; Cooling; Lubrication; Flexible suspensions, e.g. floating frames
    • F16H2700/02—Transmissions, specially for working vehicles

Definitions

  • the drive and [21] Appl support mechanism includes a rotary housing and a pair of oppositely disposed gear boxes carried by the [30] F i A li i P i i D rotary housing
  • the adjustable member is supported June 16 1972 Luxembourg 65537 drive shafts extending from the gear boxes and is thus rotatable with the housing and angularly adjust- [52] CL 214/35 214/17 266/27 able about the axis of rotation of the housing; angular [51 int. Cl. .7. Fi7b 1/20 adjustment being achieved by means of rotating the [58] Field of Search 214/17 CB 35 R 37 36 drive shafts.
  • the angular adjustment producing por- 2l4/35 5 6 tion of the drive mechanism may include elastic gear means for dividing applied torque between the two [56] References Cited boxes 7 UNITED STATES PATENTS 7 Claims, 5 Drawing Figures 1.710.544 4/1929 Lyth 114/17 CB zaflfi 12/2 A2424 221% 2/6 +2/2 Z5? ll Z- 264 252[ j 22 24 226 I 2 0" 242 I 2 52 2 256 I j 260 254 3 27 2% 256 296 24 2m 37! I 55a 5/2 37? ;I Zifl 50 5 50! 254 :2 3:96 585": 564 .ili j 5556 56X 35 592 2 59 255 355 400 aw 292 535 pmgminmzsms 3,880,302
  • the present invention relates to the delivery of material to the interior of a furnace and particularly to the charging of shaft furnaces. More specifically, the present invention is directed to charge distribution devices for controlling the placement of raw material on the hearth of a blast furnace. Accordingly, the general objects of the present invention are to provide novel and improved methods and apparatus of such character.
  • the conventional prior art furnace charging installation was of the bell-type which included compensation chambers and and bells. Although considerable design effort has been directed to improving bell-type charging installations, the improvements in operation obtained have not been commensurate in degree with other furnace improvements. Also, the trend in furance design in recent years has been toward large high output furnaces. Bell-type charging installations for modern large furnaces would have to be such a size that their manufacturing limits would be exceeded. Also, modern furnaces operate with high throat pressures and it is difficult to achieve sealing of the furnace throat relative to the ambient atmosphere when employing a bell-type charging installation; particularly on large size furnaces. A further deficiency of bell-type charging installations is that such apparatus permits only a single charge configuration; namely the so-called characteristic M-curve. Irregular furnace throughgassing and corresponding difficulty in controlling and regulating the operation of the furnace are unavoidable results of the inability to control charge distribution to achieve charge profiles other than the aforementioned M-curve characteristic of bell-type installations.
  • a distribution chute is suspended, in a pitch angle-adjustable manner, from a rotary housing arranged concentrically with the axial charge inlet spout and positioned above the throat of a shaft furnace.
  • the rotary housing is driven via a rotary sleeve and, on the side of the rotary housing positioned remote from the furnace, a pair of oppositely disposed gear boxes are provided.
  • the gear boxes house portions of the drive mechanism for achieving the pitch angle adjustment of the chute.
  • the pitch angle adjustment gear boxes each drive a shaft which passes horizontally through the rotary housing and the distribution chute is fixed. at its two oppositely disposed longitudinal sides, to the ends of these drive shafts.
  • the present invention also contemplates means for rotating the housing and for driving the gear boxes in such a manner that the rotation may be achieved independently of the pitch angle adjustment of the chute.
  • FIG. 1 is a perspective view of the improved drive mechanism of U5. Pat. No. 3,814,403, FIG. 1 being included in the present application in the interest of relating the drive mechanism of the present invention to the other components of a charging installation;
  • FIG. 2 is a cross-sectional sidc'elevation view of a portion of a charging installation in accordance with a first embodiment of the present invention
  • FIG. 3 is an enlarged cross-sectional view of a portion of the drive mechanism of FIG. 2;
  • FIG. 4 is an exploded view of the mechanism of FIG. 3;
  • FIG. 5 is a partial cross-sectional view of a second I embodiment of a drive mechanism in accordance with the present invention.
  • the drive mechanism of FIG. 1 includes a main drive motor 1 which is coupled, via gears 4 and 6, to a main drive shaft 8; the coupling mechanism also including a coupling 2 and brake 3.
  • the main drive shaft 8 has affixed thereto, in addition to drive gear 6, gears 10 and 12.
  • the gear 12, via drive means indicated generally at 11, causes rotation of a disc 24 which is concentric with feed spout 62.
  • the drive means 11 comprises a ring gear 14 having a rotary cylinder 16 affixed thereto.
  • the drive means further comprises a further ring gear 18 which is also attached to cylinder 16.
  • the ring gear 18 engages a ring gear 20 affixed to a rotary sleeve 22 mounted coaxially of the central feed spout 62.
  • the rotary sleeve 22 is rigidly connected to the rotary disc 24.
  • the distribution chute is connected, by means not shown, directly to disc 24 at a point opposite to the coupling to drive shaft 60 and thus a desired rotary movement about the blast furnace axis A is imparted to the distribution chute by the main drive motor 1.
  • the gear 10 on main drive shaft 8 also drives, via a planetary gear means indicated generally at 13, an auxiliary drive shaft 42.
  • the auxiliary drive shaft 42 is employed, in the manner to be described below, to achieve independent pitch angle adjustment of the rotating distribution chute.
  • the planetary gear means 13 comprises a planet wheel 13 which is directly engaged by gear 10 on main drive shaft 8.
  • the planetary gear means also includes a pair of intermediate gear wheels 34 and 36 and an inner gear 32.
  • the two intermediate gears 34 and 36 of planetary gear means 13 directly drive a rotary disc 40 via respective intermediate shafts 35 and 37.
  • Rotary disc 40 is rigidly connected to auxiliary drive shaft 42.
  • Auxiliary drive shaft 42 passes through the. intermediate gear means 11 and is provided, at its lower end, with a further gear 44.
  • Gear 44 drives a ring gear 46 which is mounted on rotary disc 24 by means of bearings 48; ring gear 46 being independently rotatable relative to disc 24.
  • the ring gear 46 on rotary disc 24 drives, via pinion gear 50, a shaft 56 which passes through disc 24 and is rotatably mounted therein.
  • Shaft 56 is provided, at its lower end, with a worm thread 54.
  • the worm gear 54 on shaft 56 drives, via an intermediate gear 57, a partial ring gear 58.
  • Partial ring gear 58 is affixed to one end of a shaft 60 and, as noted above. the other end of shaft 60 is connected to the distribution chute by means which permits the pitch angle of the chute to be adheat and flue dust, the worm gear 54 and the gears 57 and 58 are housed in a gear box 52 which is fixed to the underside of disc 24.
  • the inner gear 32 of planet gear means 13 is connected to an auxiliary drive motor 25 via a drive shaft 33, gears 28 and 30, a brake device 27 and a coupling means 26.
  • the main drive motor 1 rotates disc 24 and, with a correctly selected transmission ratio of the various intermediate gears, the-ring gear 46 mounted on rotary disc 24 will rotate at the same speed as disc 24. With no relative speed between disc 24 andring gear 46 the position of pinion gear 50 will remain unchanged relative to its rotary axis.
  • the distribution chute will there-.
  • the auxiliary drive motor 25 is employed, via planet gear means 13, to impart a speed increase or decrease relative to the speed of movement of disc 24 to ring gear 46. Any relative speed between ring gear 46 and rotary disc 24 will cause pinion 50 to be rotated and thereby causing a change in the angle of inclination of the distribution chute.
  • a variation in relative speed between ring gear 46 and rotary disc 24 may be achieved by employing an auxiliary drive motor 25 which can be reversed or through the selection of gear ratios whereby synchronous speed between rotary disc 24 and gear ring 46 exists only at a particular ratio between the rotational speeds of main drive motor 1 and auxiliary motor 25.
  • the inclusion of the protective gear box 52 affixed to the underside of rotary disc 24 may not, under some conditions, provide adequate protection from furnace internal conditions for the components of the drive mechanism positioned therein. Heat surges within the furnace can briefly reach temperatures of 1,000C and, due to thermal expansion, could conceivably lead to locking of gears 54, 57 and 58 located in gear box 52. Of perhaps more significance, the position of gears 54, 57 and 58 precludes their being cooled by the throughflow of inert gas or purified and cooled blast furnace gas.
  • the pitch angle adjusting forces provided by the drive mechanism disclosed in the copending application are applied only at one longitudinal side of the distribution chute; i.e., by means of the shaft 60.
  • This manner of angular drive imposes extremely stringent strength requirements on the chute material.
  • angular adjusting forces must be absorbed by the chute and must be transferred at the second longitudinal side thereof to a mounting. The previous arrangement thus leads to torsional stresses in the distribution chute which are increased during the charging process when the chute is loaded with raw material being delivered to the furnace.
  • FIG. 2 is a cross-sectional view of a first embodiment of an improved distribution chute drive device in accordance with the present invention.
  • the distribution chute is indicated at 208 in a horizontal position.
  • the opposite disposed longitudinal sides of chute 208 are connected, by means of respective guide memebers 390 and 392, to rotatable shafts 322 and 324.
  • Shafts 322 and 324 are rotatable about a horizontal axis to vary the inclination ofdistribution chute 208.
  • the shafts 322 and 324 are supported in respective gear boxes, indicated generally at 270 and 27 2, and the gear boxes are in turn rigidly mounted within a rotary housing defined by elements 228, 234 and 236. Accordingly, the distribution chute 208 is directly connected to the rotary housing and, in the manner to be explained below, is rotated therewith by means of a suitable drive.
  • a rotary cylinder 200 penetrates the upper wall 202 of a drive chamber indicated generally at 204.
  • the drive chamber 204 is in the form of a superstructure mounted on the blast furnace top or throat.
  • rotary cylinder 200 is drived by main drive motor 1 via gears 4, 6 and 12.
  • the end of rotary cylinder 200 which projects into drive chamber 204 is provided with a gear 206.
  • Gear 206 engages a ring gear 212 located concentrically relative to the central feed spout 210: ring gear 212 being supported by a bearing bracket 214.
  • the bearing bracket 214 is fixed rigidly to the underside of the upper wall 202 of drive chamber 204 and comprises a bearing such as, for example, a "roller rotary connection with groups of rollers 216, 218. 220 for the axial and radial support of ring gear 212.
  • the roller rotary connection is continually supplied with lubricant under pressure from outside the drive chamber 204 by means of conduits 222 and 224.
  • the ring gear 212 is provided, at its underside, with an integral adapting ring 226 which serves to extend the ring gear inwardly toward the central feed spout 210.
  • the rotary housing includes elements 228, 234 and 236; these elements respectively comprising a conical rotary sleeve, a vertical casing and a horizontal rotary disc.
  • the conical rotary sleeve portion 228 of the rotary housing is attached to the adapting ring 226 by means of bolts 230 and 232.
  • the means for achieving pitch angle adjustment of distribution chute 208 are mounted within gear boxes 270 and 272.
  • the gear boxes 270 and 272 are positioned on the side of the rotary housing which is remote from the furnace in the interest of minimizing the influence of the blast furnace environment on the components located in gear boxes 270 and 272.
  • the gear boxes 270 and 272, as well the gears located therein. are designed so as to be homologous to one another with reference to a plane passing through the blast furnace logitudinal axis A.
  • the means by which rotation of shafts 322 and 324 is achieved comprises. referring again to FIG. 1, the planetary gear means 13, auxiliary motor 25, gear 10 and rotary disc 40.
  • the pitch angle adjustment drive further comprises a drive shaft 238 coaxial with rotary cylinder 200, a gear 240 attached to shaft 238 and a pair of ring gears 242 and 246 which are interconnected via an intermediate gear 244.
  • the two ring gears 242 and 246 are mounted by means of a further roller rotary connection on a bearing support ring 254.
  • the bearing support ring 254 is arranged concentrically with the central feed spout 210 and is attached to the underside of the upper wall 202 of drive chamber 204 via a thick-walled circular sheet metal casing 252.
  • the roller rotary connection between ring gears 242 and 246 and bearing support ring 254 comprises three groups of rollers 256, 258 and 260 for absorbing the axial and radial forces of ring gears 242 and 246.
  • a continuous supply of a suitable lubricant is delivered to the rotary roller connection" defined by bearings 256, 258 and 260 via channels 262 and 264 provided in the bearing support ring 254 and in casing 252 whereby the lubricant can be supplied to the roller bearings under an appropriate pressure from outside of drive chamber 204.
  • the circular sheet'metal casing 252 is provided with recesses in the area of the gears 206 and 240 which partially intersect casing 252.
  • the roller rotary connection for ring gears 242 and 246 may be attached to the rotary housing 228 and carried along thereby.
  • the drive for ring gears 242 and 246 will, in either event, be integrally maintained in the same manner as the remaining gear for pitch angle adjustment of the distribution chute 208.
  • the gear box 270 comprises supporting members 282 and 286, walls 274 and 278 and a closure plate 290; the closure plate being welded to the lower ends of support members 282 and 286.
  • gear box 272 comprises supporting members 284 and 288, walls 276 and 280 and closure plate 292 welded to support members 284 and 288.
  • the gear boxes 270 and 272 are liquid inpervious whereby an oil bath for the gears may be provided within each of the gear boxes.
  • the gear boxes 270 and 272 may, as desired, be permanently or detachably connected to the rotary housing defined by elements 228, 234 and 236. in the embodiment of FIG. 2 the support members 286 and 288, respectively of gear boxes 270 and 272 are attached by suitable fasteners to respective supports 370 and 372 welded to the conical rotary sleeve 228.
  • Drive wheels 298 and 300 are positioned immediately above the upper walls 272 and 276 of respective gear boxes 270 and 272.
  • the drive wheels 298 and 300 are engaged by ring gear 246.
  • Drive and support shafts 294 and 296, respectively for drive wheels 298 and 300, pass into the respective gear boxes and are supported in the top walls of the gear boxes by means of bearings, not shown.
  • a worm drive 302, 306 within gear box 270 transfers the torque of the drive wheel 298 to a shaft 310 and thus to a spur gear 316.
  • the spur gear 316 drives a partial ring gear 319.
  • the partial ring gear 319 has a hollow shaft 326 which is rigidly connected with a hollow spline shaft 330.
  • Spline shaft 330 is rotatably mounted by means of bearings 338, 342 in the supporting members 282, 286 of gear box 270.
  • the inclination angle adjustment drive shaft 332 is inserted in spline shaft 330 and passes through the vertical casing 234 of the rotary housing and partially projects into the blast furnace port. in the same manner.
  • gear box 272 houses a worm drive 304, 308, shaft 312, spur gear 318, partial ring gear 320, hollow ring gear shaft 328 and hollow spline shaft 332.
  • the spline shaft 332 of gear box 272 is rotatably mounted by means of bearings 340, 344 in supporting members 284 and 288.
  • R0- tatable shaft 324 is inserted in spline shaft 332 of gear box 272 and also passes through the vertical casing 234 of the rotary housing and partially projects into the blast furnace port.
  • the portions of shafts 322 and 324 which project into the blast furnace port support respective connecting arms 390 and 392 and, as previously noted, the distribution chute 208 is fixed to these connecting arms via respective bolted joints 394, 396 and 398, 400.
  • the connecting arms 390 and 392 are provided with spline shaft recesses through which the arms are pushed onto respective shafts 322 and 324.
  • the spline shafts 330 and 332 are provided with respective annular projections 346 and 348 which locate the front ends of respective hollow ring gear shafts 326 and 328 relative to ball bearings 342 and 344 in the interest of preventing displacement of the partial ring gears with respect to the spline shafts.
  • Additional spacers 350 and 352 are placed between respective hollow ring gear shafts 326 and 328 and associated bearings 338 and 340.
  • the bearing mountings 354, 358 and 356, 360 are placed on the outside of supporting members 282, 286 and 284, 288.
  • the bearing mountings 354, 358 and 356, 360 serve simultaneously as flanges for the attachment of sealing rings 362, 366 and 364, 368.
  • the drive shafts 322 and 324 are themselves provided, on the ends opposite to the central feed spout 210, with end plates 378 and 380 which serve as stop members; the end plates and thus the drive shafts being held in the proper position by respective clamps 382, 384 and 386, 388.
  • the chute is manipulated into the position where it projects horizontally into a hatch, not shown. provided in the blast furnace throat.
  • the chute is thereupon fixed to a crane yoke.
  • manholes or service ports 434 and 436 provided on drive chamber 204 are opened thereby affording maintenance personnel with access to drive shafts 322 and 324.
  • the clamps 382, 384 and 386, 388 are thereafter removed thus permitting shafts 322 and 324 to be withdrawn to an extent such that the connecting arms 390 and 396 are free.
  • threaded holes 430 and 432 are provided on respective shafts 322 and 324; threaded holes 430 and 432 receiving a withdrawal tool.
  • the ends of the shafts 322 and 324 which engage respective connecting arms 390 and 392 are provided with a conieally shaped lead portion as shown in FIG. 2.
  • the drive mechanism of FIG. 2 is, in the embodiment described, located in the vicinity of the throat of a blast furnace and thus is potentially exposed to blast furnace flue dust and high temperatures.
  • inert gas or purified and cooled blast furnace gas is fed into the drive chamber via a port 438.
  • the supply pressure for this cleaning and cooling gas is selected to be higher than the counter-pressure at the blast furnace throat so that gas from drive chamber 204 flows into the blast furnace top or throat.
  • the gas discharge points from the drive chamber into the furnace throat are indicated by means of arrows 385.
  • each of drive wheels 298 and 300 includes a shaft 294, a drive disc 410, a counter-disc 402 and a ring gear 408.
  • the drive disc 410 is keyed to shaft 294 as indicated at 414.
  • the counter-disc 402 is provided, on its underside.
  • the counter-disc 402 is rigidly connected to drive disc 410 by means of bolts 412, 412' and 412"; the disc 402 and ring gear 408 being provided with elongated slots whereby a limited degree of adjustment of disc 402 relative to disc 410 is permitted.
  • the ring gear 408 is provided with three radially inwardly projecting members 422, 422 and 422". With the gear means assembled, the projections 424 on disc 402 loosely mesh with the projections 422 of ring gear 408.
  • the projecting members 422 and the projections 424 are separated from one another by means of helical springs 416, 416', 416", 416', 416, and 416".
  • the ring gear is capable of a limited degree of elastic rotary movement relative to drive disc 410 and counter-disc 402.
  • thrust bearings 404 and 406 are respectively inserted between disc 402 and gear 408 and between gear 410 and gear 408. In operation, torque resulting from the driving of ring gear 408 is transmitted, by means of the helical springs 416, to disc 402 and thus to drive disc 410.
  • the helical springs 416 thus permit an elastic transfer of torque from ring gear 242 to worm gears 302 and 304.
  • the torque is transferred approximately uniformly through the helical springs so that a uniform elastic force is exerted on shafts 322 and 324 and the substantially evenly divided force is transmitted to both sides of the distribution chute for adjusting the angle of inclination thereof.
  • FIG. 5 depicts a further embodiment of a distribution chute drive mechanism in accordance with the present invention; only one half of the drive unit being shown in FIG. 5.
  • the principal difference between the embodiments of FIGS. 2 and 5 resides in the replacement, in the FIG. 5 embodiment. of the inclination drive shafts 322 and 324 with hollow spline shafts as indicated at 530.
  • the use of the hollow spline shaft 530 requires that the manner of connecting the other members of the drive mechanism and the distribution chute 208 to the drive shafts be changed.
  • the hollow shaft 326 of partial ring gear 319 is, in the FIG. 5 embodiment, held on the spline shaft 530 by means of spacing and sealing rings 532 and 534.
  • the spacing and sealing rings 532 and 534 are, in turn, mounted relative to the fixed walls 282 and 286 of the gear box by means of bearings 536 and 538.
  • the attachment of distribution chute 208 to spline shaft 530 is achieved through the use vof an adapter disc S42; chute 208 being detachably connected to disc 542 by means of bolts.
  • the distribution chute 208 includes an outer casing 544 of thick-walled heat-resistant steel sheeting and an inner cladding 546 of wear-resistant material.
  • a sealing flange 548 having projections 550 and 552 is attached to outer casing and outer casing 544, adapting disc 542 and spline shaft 530.
  • the sealing flange 548 has a further projection 554 which is located in the continuation of the longitudinal axis of the hollow spline shaft 530.
  • the shaft 530 is supported on the projection 554 of sealing flange 548 shown.
  • the spline shaft is provided, at the end disposed away from the blast furnace feed spout, with a removable plate 564 having openings 566 and 568 therein.
  • a bolt 570 arranged coaxially with shaft 530 connects plate 564 to projection 554 of sealing flange 548.
  • the spline shaft 530 is provided with an annular slot 572 which will be engaged by a suitable removal tool.
  • the hollow spline shaft 530 is provided, at the end facing the sealing flange 548, with openings 558 and 560.
  • An inert gas flow through shaft 530 between openings 566, 568 and 558, 560, as well as through space 553, will achieve desirable cooling and cleaning of hollow spline shaft 530.
  • a drive and support mechanism for a rotary and angularly adjustable material distribution chute positioned internally of a furnace comprising:
  • first and second gear box means mounted on said support means and movable therewith, said gear box means being oppositely disposed with respect to the distribution chute and each other and supporting drive gear means;
  • drive shaft means extending from each of said gear box means, said drive shaft means being operatively associated with said drive gear means and being disposed in the same plane for rotation about an axis transverse to the axis of rotation of said support means;
  • gear box means each comprise:
  • enclosure means supported from said annular support means, said enclosure means being mounted from said annular support means on the side thereof disposed away from the furnace, said enclosure means being adapted to contain a reservoir of lubricant for the drive gear means disposed therein.
  • a main drive motor positioned remotely from said support means and having an output shaft
  • transmission means including a rotary sleeve for coupling said main drive motor output shaft to said support means;
  • bearing means for supporting said support means for the furnace superstructure.
  • planetary gear means including a planet gear, intermediate gear means and an inner gear
  • first and second elastic gear means for dividing and transmitting the torque provided by said generating means to the drive gear means disposed in said first and second gear box means.
  • planetary gear means including a planet gear, intermediate gear means and an inner gear
  • said elastic gear means each comprise:
  • ring gear being coupled to said planetary gear means intermediate gear means and being provided with projections thereon which mesh with said counter-disc projections;

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Manufacturing & Machinery (AREA)
  • Materials Engineering (AREA)
  • Metallurgy (AREA)
  • Organic Chemistry (AREA)
  • Mechanical Engineering (AREA)
  • Blast Furnaces (AREA)
  • Vertical, Hearth, Or Arc Furnaces (AREA)
  • Muffle Furnaces And Rotary Kilns (AREA)
US368867A 1972-06-16 1973-06-11 Drive and support mechanism for rotary and angularly adjustable member Expired - Lifetime US3880302A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US05/629,751 US4057616A (en) 1973-06-11 1975-11-07 Metal hydroxide scintigraphic agents and method of preparation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
LU65537 1972-06-16

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US05/629,751 Division US4057616A (en) 1973-06-11 1975-11-07 Metal hydroxide scintigraphic agents and method of preparation

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US368867A Expired - Lifetime US3880302A (en) 1972-06-16 1973-06-11 Drive and support mechanism for rotary and angularly adjustable member

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US (1) US3880302A (de)
JP (1) JPS5631322B2 (de)
AT (1) AT336655B (de)
AU (1) AU469369B2 (de)
BE (1) BE801031A (de)
CA (1) CA1000051A (de)
DE (1) DE2324970C2 (de)
ES (1) ES415716A1 (de)
FR (1) FR2189516B1 (de)
GB (1) GB1403687A (de)
IT (1) IT989196B (de)
LU (1) LU65537A1 (de)
NL (1) NL183039C (de)
SU (1) SU639484A3 (de)
ZA (1) ZA733809B (de)

Cited By (19)

* Cited by examiner, † Cited by third party
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US4153140A (en) * 1976-08-06 1979-05-08 S.A. Des Anciens Etablissements Paul Wurth Lubrication technique and apparatus
US4243351A (en) * 1977-06-06 1981-01-06 Paul Wurth S.A. Method of and apparatus for charging a furnace
US4273492A (en) * 1978-08-16 1981-06-16 Paul Wurth, S.A. Charging device for shaft furnaces
US4368813A (en) * 1980-02-15 1983-01-18 Paul Wurth S.A. Distribution chute control apparatus and method
US4941792A (en) * 1988-07-25 1990-07-17 Paul Wurth S.A. Handling device for a distribution chute of a shaft furnace and drive mechanism suitable for this device
DE4216166C2 (de) * 1991-06-12 2001-07-19 Wurth Paul Sa Vorrichtung zur Kühlung einer Verteilerschurre einer Schachtofen-Beschickungsanlage
US6544468B1 (en) 1997-11-26 2003-04-08 Paul Wurth S.A. Method for cooling a shaft furnace loading device
DE4430265B4 (de) * 1993-09-01 2004-05-06 Paul Wurth S.A. Verteilerschurre zum Einbau in einen Ofen
US20100028106A1 (en) * 2006-12-18 2010-02-04 Paul Wurth S.A. Rotary charging device for a shaft furnace
US20100322744A1 (en) * 2008-02-01 2010-12-23 Paul Wurth S.A. Charge distribution apparatus
WO2011023772A1 (en) 2009-08-26 2011-03-03 Paul Wurth S.A. Shaft furnace charging device equipped with a cooling system and annular swivel joint therefore
WO2011092165A1 (en) 2010-01-27 2011-08-04 Paul Wurth S.A. A charging device for a metallurgical reactor
WO2011101313A1 (en) 2010-02-19 2011-08-25 Paul Wurth S.A. Distribution chute for a charging device of a metallurgical reactor
WO2012016818A1 (en) 2010-08-06 2012-02-09 Paul Wurth S.A. Distribution chute
US20120045298A1 (en) * 2009-05-07 2012-02-23 Paul Wurth S.A. Shaft furnace charging installation having a drive mechanism for a distribution chute
US8353660B2 (en) 2008-01-30 2013-01-15 Paul Wurth S.A. Charging device for distributing bulk material
CN115109875A (zh) * 2021-03-19 2022-09-27 上海梅山钢铁股份有限公司 高炉加废钢的控制方法
US11492779B2 (en) * 2019-05-22 2022-11-08 Caterpillar Inc. Circle drive system for a grading machine
EP3329020B2 (de) † 2015-07-30 2022-12-21 Danieli & C. Officine Meccaniche S.p.A. Vorrichtung zur abgabe von füllmaterial in einen hochofen

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
LU83280A1 (fr) * 1981-04-03 1983-03-24 Wurth Paul Sa Procede pour actionner une goulotte oscillante dans une enceinte sous pression,dispositif pour la mise en oeuvre de ce procede et installation de chargement d'un four a cuve equipe d'un tel dispositif
LU84520A1 (fr) * 1982-12-10 1984-10-22 Wurth Paul Sa Dispositif de refroidissement d'une installation de chargement d'un four a cuve
LU84521A1 (fr) * 1982-12-10 1984-10-22 Wurth Paul Sa Dispositif de refroidissement d'une installation de chargement d'un four a cuve
LU87341A1 (fr) * 1988-09-22 1990-04-06 Wurth Paul Sa Installation de chargement d'un four a cuve
FR2692595A1 (fr) * 1992-06-22 1993-12-24 Int Equipement Dispositif d'alimentation pour haut-fourneau.
CN1046552C (zh) * 1997-06-13 1999-11-17 僧全松 钢丝绳传动的高炉炉顶溜槽布料器
AT502479B1 (de) 2005-10-24 2007-04-15 Voest Alpine Ind Anlagen Verfahren und vorrichtung zum chargieren von einsatzstoffen
CN110205471A (zh) * 2019-07-02 2019-09-06 南京长江工业炉科技集团有限公司 一种多层多驱动旋转加热炉

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1710544A (en) * 1924-06-12 1929-04-23 John J Lyth Cloth-piling machine
US3693812A (en) * 1969-07-31 1972-09-26 Wurth Anciens Ets Paul Furnace charging apparatus

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1710544A (en) * 1924-06-12 1929-04-23 John J Lyth Cloth-piling machine
US3693812A (en) * 1969-07-31 1972-09-26 Wurth Anciens Ets Paul Furnace charging apparatus

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4153140A (en) * 1976-08-06 1979-05-08 S.A. Des Anciens Etablissements Paul Wurth Lubrication technique and apparatus
US4243351A (en) * 1977-06-06 1981-01-06 Paul Wurth S.A. Method of and apparatus for charging a furnace
US4273492A (en) * 1978-08-16 1981-06-16 Paul Wurth, S.A. Charging device for shaft furnaces
US4368813A (en) * 1980-02-15 1983-01-18 Paul Wurth S.A. Distribution chute control apparatus and method
US4941792A (en) * 1988-07-25 1990-07-17 Paul Wurth S.A. Handling device for a distribution chute of a shaft furnace and drive mechanism suitable for this device
DE4216166C2 (de) * 1991-06-12 2001-07-19 Wurth Paul Sa Vorrichtung zur Kühlung einer Verteilerschurre einer Schachtofen-Beschickungsanlage
DE4430265B4 (de) * 1993-09-01 2004-05-06 Paul Wurth S.A. Verteilerschurre zum Einbau in einen Ofen
US6544468B1 (en) 1997-11-26 2003-04-08 Paul Wurth S.A. Method for cooling a shaft furnace loading device
US8088327B2 (en) 2006-12-18 2012-01-03 Paul Wurth S.A. Rotary charging device for a shaft furnace
US20100028106A1 (en) * 2006-12-18 2010-02-04 Paul Wurth S.A. Rotary charging device for a shaft furnace
US8353660B2 (en) 2008-01-30 2013-01-15 Paul Wurth S.A. Charging device for distributing bulk material
US20100322744A1 (en) * 2008-02-01 2010-12-23 Paul Wurth S.A. Charge distribution apparatus
US20120045298A1 (en) * 2009-05-07 2012-02-23 Paul Wurth S.A. Shaft furnace charging installation having a drive mechanism for a distribution chute
WO2011023772A1 (en) 2009-08-26 2011-03-03 Paul Wurth S.A. Shaft furnace charging device equipped with a cooling system and annular swivel joint therefore
WO2011092165A1 (en) 2010-01-27 2011-08-04 Paul Wurth S.A. A charging device for a metallurgical reactor
WO2011101313A1 (en) 2010-02-19 2011-08-25 Paul Wurth S.A. Distribution chute for a charging device of a metallurgical reactor
WO2012016818A1 (en) 2010-08-06 2012-02-09 Paul Wurth S.A. Distribution chute
EP3329020B2 (de) † 2015-07-30 2022-12-21 Danieli & C. Officine Meccaniche S.p.A. Vorrichtung zur abgabe von füllmaterial in einen hochofen
US11492779B2 (en) * 2019-05-22 2022-11-08 Caterpillar Inc. Circle drive system for a grading machine
CN115109875A (zh) * 2021-03-19 2022-09-27 上海梅山钢铁股份有限公司 高炉加废钢的控制方法
CN115109875B (zh) * 2021-03-19 2024-01-05 上海梅山钢铁股份有限公司 高炉加废钢的控制方法

Also Published As

Publication number Publication date
FR2189516B1 (de) 1976-11-12
LU65537A1 (de) 1972-10-25
AU469369B2 (en) 1976-02-12
NL183039B (nl) 1988-02-01
ES415716A1 (es) 1976-06-01
IT989196B (it) 1975-05-20
FR2189516A1 (de) 1974-01-25
JPS5631322B2 (de) 1981-07-21
BE801031A (fr) 1973-10-01
AU5679973A (en) 1974-12-12
DE2324970A1 (de) 1974-01-03
ZA733809B (en) 1974-04-24
GB1403687A (en) 1975-08-28
SU639484A3 (ru) 1979-04-04
CA1000051A (en) 1976-11-23
JPS4963608A (de) 1974-06-20
AT336655B (de) 1977-05-25
DE2324970C2 (de) 1983-09-22
NL183039C (nl) 1988-07-01
NL7306435A (de) 1973-12-18
ATA339273A (de) 1976-09-15

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