US2819130A - Bearings for rotary cylinders, drums and the like - Google Patents

Bearings for rotary cylinders, drums and the like Download PDF

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Publication number
US2819130A
US2819130A US509081A US50908155A US2819130A US 2819130 A US2819130 A US 2819130A US 509081 A US509081 A US 509081A US 50908155 A US50908155 A US 50908155A US 2819130 A US2819130 A US 2819130A
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US
United States
Prior art keywords
rotary
rollers
furnace
pressure
racering
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
US509081A
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English (en)
Inventor
Kaminsky Fritz
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.)
Fellner and Ziegler GmbH
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Fellner and Ziegler GmbH
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Filing date
Publication date
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Publication of US2819130A publication Critical patent/US2819130A/en
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Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C13/00—Rolls, drums, discs, or the like; Bearings or mountings therefor
    • F16C13/02—Bearings
    • F16C13/04—Bearings with only partial enclosure of the member to be borne; Bearings with local support at two or more points
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C29/00—Bearings for parts moving only linearly
    • F16C29/04—Ball or roller bearings
    • 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 specially adapted for rotary-drum furnaces
    • F27B7/22—Rotary drums; Supports therefor
    • 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
    • F27B7/22—Rotary drums; Supports therefor
    • F27B2007/2246—Support rollers
    • F27B2007/2273—Support rollers with arrangements, e.g. rollers, to maintain the drum against longitudinal movement

Definitions

  • cylindrical bodies of these machines are. mounted 1 on.
  • Rotary furnaces are generally. arranged somewhat inclined relatively to the horizontal, andthe position of arotary furnacewithjits :racerings is maintained onthe"associated support rollers by means of additional pressure-rollers which bear againstithe appropriate side face ofa racering.
  • roller surfaces wheneverthe furnace drum presses with its -racering flank against theupper pressure roller in the course of the'movement which said drum is forced to perform by the helicalforce'; With reduced surface friction; thefurnacedrum then slides slowly downwards. Whenit moves subsequently into the bottom position determined by the bottom pressure roller,a new upward movement is initiated when augmented frictional engagement occurs owing to the small quantities of oil' on the roller surfaces drying out ordeteriorating.
  • Theobject of .the present invention is to obviate the.
  • the presentinvention is characterised in'that two pressurev rollers. are provided one at each side of a racering;
  • the lower ends of theaxles of these pressure rollers being mounted in a cross-member. to which a reciprocating movement. substantially parallel to the longitudinalaxis of .the .rotary cylindrical body, is imparted by automaticallycontrolleddriving means.
  • the latter may be mechani-.- cal, electrical hydraulic, or hydroelectric.
  • the power means is double-act-- tervals of time. ing in thatit positively forces the cylindrical body up the inclination at which saidbody is set and thenapositively forces or controls said body downwards.
  • the cross-member carrying the pressure-rollers can be; mounted byan arrangement of parallel links on a baseplate, and the drive for producing the reciprocating movea ment then acts either directly or through a leverageuponv thiscross-member. Lessfriction is -thereby produced than would be the case with a slide guide arrangement.
  • twin pressure roller system of this kind not only at one racering but at two or more racerings, thereby-scone.
  • the reciprocatingcrossmember may be arranged to actuate an electzicswitchi. which, by way of a lifting magnet arrangement, controls] a valve, for examplea rotary valve, in such manner. as. to produce the alternate to and fro movements of the. ram in the working cylinderand thusthe to and. fromovements of the cross-member coupled thereto.
  • a valve for example a rotary valve
  • the requisite driving energy for the to andfro displacement of the twin pressure roller arrangement can be considerably reduced if the mounting of the pressure roller operative against the dead weight of the rotary furnace or the like is associated with a counter-balance arrangement.
  • one of two links supporting this pressure roller on the base plate may take the form of a lever presenting an arm for suspension of the counter-weight.
  • The-counter-weight itself can be varied, depending on the given circumstances, but it is also possible to shift the point of application of the counter-weight on the said lever arm.
  • This counterweight arrangement can be provided in association with the pressure roller of one racering, whilst the movable and positively reciprocated twin pressure roller arrangement is situated at a second racering. Alternatively, this counterweight arrangement can be associated with the movable and positively reciprocated twin pressure roller arrangement.
  • the bearing surfaces of the pressure rollers, and possibly also of the support rollers, are advantageously slightly rounded and although suchrounded surfaces, when unloaded, make a point or line contact, on the other hand when pressure is exerted a rounded surface which originally was part circular will now be distorted so as to form part of a shallow ellipse; T heresult is that no edge contacts can occur between the rollers and the bearing surfaces of the racerings, a feature which not only contributes to further reducing the driving'power necessary, but which strain-hardens the surface structure both of the rollers and also of the racerings and which, particularly with the use of grease or oil, conserves the said surfaces.
  • thev means according to the invention produce a completely uniform and controllable longitudinal movement in both directions of, for example, a rotary tube furnace, and the rounded construction of the bearing surfaces of the pressure rollers also results in a roll polishing effect, as it were, which imparts a particularly long life to the parts despite the positively effected reciprocatory movement. It is thus a decisive advantage, from the operational point of view, if the surfaces of all supporting rollers as well as pressure rollers themselves are provided with rounded surfaces.
  • Figure 1 is a side view of a cylindrical rotary furnace with two racerings, one in association with counterbalance means and the other in association with driving means for positively reciprocating the furnace longitudinally.
  • Figure 2 is a view, partly in section and to a larger scale, of the means associated with the racering on the right-hand in Fig. 1.
  • Figure 3 is a view, partly in section and to a larger scale, of the counterbalance means associated with the racering on the left-hand in Fig. l, and
  • Figure 4 is a diagram of an electrically controlled hydraulic drive for the automatic and positive production of the reciprocating movement.
  • the tubular body 1 of a rotary furnace is mounted in the usual manner ata slight inclinationof approximately 2 relatively to the horizontal by means of its racerings 2 and 3 bearing upon support rollers 4 and 5.
  • the inclination of the cylindrical rotary furnace is such that the racering 3 lies somewhat lower than the racering 2.
  • a pressure roller 6 which bears against one side face 7 of the racering 2 is mounted on a movable support. This support, as hereinafter explained, is carried upon two vertical parallel links, one of which is formed as a lever presenting an arm 8 on the end of which a counter weight 9 is suspended.
  • Pressure rollers 12 and 13 bear against respective side faces 10 and 11 of the racering
  • the lower ends of the shafts of these pressure rollers are mounted in a guide member 14 and the latter is reciprocated by suitable driving means as indicated by the double arrow in the Figure 1, the path of such reciprocationbeing substantially parallel to the longitudinal axis 15 of the rotary furnace.
  • suitable driving means as indicated by the double arrow in the Figure 1
  • the path of such reciprocation being substantially parallel to the longitudinal axis 15 of the rotary furnace.
  • a pivot pin inserted in the eye 23 is engaged by the driving means so as to swing the triangular link element 18 about the pivot pin 20a to a certain extent, whereby the cross member 16 with the pressure rollers 12 and 13 carries out a reciprocating movement substantially parallel to the longitudinal axis of the furnace body. With this movement there also occurs a vertical displacement of the bearing surfaces of the pressure rollers 12 and 13 which are rounded as indicated by the reference numerals 24 and 25, relatively to the fiat side faces 10 and 11 of the racering 3.
  • the driving up and down of the pin having a bearing ,inthe eye 23 can be effected, for example, mechanically 'by an eccentric or cam drive, lever drive or the like.
  • a hydraulic drive is provided, a ram cylinder 26 having itsv lower end pivotally mounted in'a bearing bracket 28by means of, the pin 27.
  • the upwardly extending piston rod or ram 29 is pivotally connected at its upper end with the eye 23 of the triangular link 18.
  • the reference numeral 30 designates a pipe line for oil under pressure.
  • the pistonv strokes in the cylinder 26 can be controlled by known means, many ditferent kinds of which are known with hydraulic drives.
  • One such control is illustrated in Fig. 4.
  • the cross-member 16 with its two pressure rollers 12 and 13 is reciprocated in the manner aforesaid and as indicated by the double arrow in Fig. 4.
  • a rod 31 acts upon a switching arrangement 32 which is adapted to switch on and off an auxiliary current for a relay-device 33 which acts upon a switch 34 which opens and closes the main circuit.
  • a lifting magnet 35 is energised and operates a toothed rack 36.
  • This toothed rack 36 meshes wtih a pinion 37 which is mounted on the spindle 38 of a rotary valve 39.
  • the pressure fluid for the working cylinder 26 with its associate piston 26a is delivered by a pump 40 driven from an electric motor 41 which is likewise connected in the main current line.
  • the rotary valve 39 is connected to the pump 40 by means of the pipe 44.
  • FIG 3 the pressure roller 6 bears against a side face 7 of the racering 2, as in Figure 1.
  • the pressure roller 6 is mounted in a guide-member 45 which is supported on a base plate 48 by vertical parallel links 46 and 47.
  • the link pair 46 has connecting pivots 46a and 46b, and the link pair 47 has pivots 47a and 47b.
  • the links of the pair 47 are fashioned as lever arms 49 mo tending laterally for a suitable length.
  • the outer end of each of these lever arms 49 is formed with a slot 50 into which is mounted a suspension pin 51 which can be adjusted along the slots by means of a threaded rod 52 which comprises suitable eyes 53 engaging the pin 51.
  • a rod 54 suspended from the pin 51 carries counter weights 55, 55a, 5512.
  • the position of the lever 49 shown in Fig. 3 is that in which this lever settles when the furnace is in the hot operating condition, when the said furnace is in its highest position.
  • the lever 49 then rises into the position shown in chain lines in Figure 3.
  • the lever 49 is also provided with a hand-wheel 56 and spindle 57.
  • a hand wheel 56 and spindle 57 One purpose of this hand wheel-spindle arrangement is, when necessary, to swing the lever 49 relatively to the base plate 58 in such a manner that the pressure roller 6 no longer bears against the running surface 7 of the racering 2.
  • Another purpose of this hand-wheel adjustment arrangement 56, 57 is to regulate exactly the appropriate application of the pressure roller 6 against the bearing surface 7 of the racering 2.
  • Rotary treatment cylinder fitted with race-rings run ning on support rollers for radial support and operatively engaged by cooperating pressure rollers bearing laterally against said rings for the axial support of said rotary cylinder, wherein two pressure rollers are provided one at each side of a racering each mounted for rotation on a shaft or the like, the lower end of said shafts of said pressure rollers being supported on a guide-member mounted for reciprocating movement substantially parallel to the longitudinal axis of said rotary cylinder and automatically controlled driving means operative to impart reciprocating movement to said guide member, whereby said rotary cylinder is positively forced and controlled in both axial directions.
  • Rotary treatment cylinder according to claim 1, wherein said guide-member carrying said pressure rollers is supported on a base plate by a parallel link arrangement, and said driven means for producing the reciprocation of said cylinder is operatively connected to said guidemember.
  • Rotary treatment cylinder according to claim 2, wherein one member of the parallel link arrangement is defined by a triangular lever pivotally mounted on said base plate and presenting a laterally extending arm operatively engaged by said driving means.
  • Rotary treatment cylinder according to claim 1, wherein said guide-member carrying said pressure rollers is driven by hydraulic means including a piston, and said guide member is fitted with means for actuating switch contacts for the electrical control of a distributor valve controlling the alternate to and fro movement of said piston operative upon said guide-member.
  • Rotary treatment cylinder according to claim 4, wherein the lower end of the working cylinder for said piston is pivotally mounted on a base plate, and said piston is pivotally connected at its upper end with means actuating said guide member.
  • Rotary treatment cylinder according to claim 1, wherein a pressure roller which takes the load resulting from the dead weight component of said cylinder is mounted on a movable base provided with a counter-balance arrangement adapted for compensating said load.
  • Rotary treatment cylinder according to claim 6, wherein said movable base is supported by a link presenting a lever arm adapted for the suspension of a counterweight.
  • Rotary treatment cylinder according to claim 6 in which said counter-balance arrangement is provided at the pressure roller of one racering while said cooperating pressure rollers are situated at a second racering.
  • Rotary treatment cylinder according to claim 1 wherein the bearing surfaces of said pressure rollers are rounded.
  • Rotary treatment cylinder in accordance with claim 9 wherein the bearing surfaces of said support rollers for said racering are rounded.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Paper (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Muffle Furnaces And Rotary Kilns (AREA)
US509081A 1955-03-12 1955-05-17 Bearings for rotary cylinders, drums and the like Expired - Lifetime US2819130A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE1133970X 1955-03-12

Publications (1)

Publication Number Publication Date
US2819130A true US2819130A (en) 1958-01-07

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US509081A Expired - Lifetime US2819130A (en) 1955-03-12 1955-05-17 Bearings for rotary cylinders, drums and the like

Country Status (6)

Country Link
US (1) US2819130A (de)
AT (1) AT192316B (de)
CH (1) CH337119A (de)
DK (1) DK87715C (de)
FR (1) FR1133970A (de)
GB (1) GB768629A (de)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3468522A (en) * 1966-12-05 1969-09-23 Rene Bovagne Rotatable apparatus,more particularly a rotatable kiln,for the treatment of materials
US3966395A (en) * 1973-11-09 1976-06-29 Klockner-Humboldt-Deutz Aktiengesellschaft Pressure roller stand for forcible longitudinal displacement of large rotating drums
US4226271A (en) * 1978-06-21 1980-10-07 Coleman Thomas R Drum debarker
US4696116A (en) * 1986-06-23 1987-09-29 Guaranty Performance Co., Inc. Mounting structure for rotary drum dryer
US4995561A (en) * 1989-02-23 1991-02-26 Nakaya Jitsugyo Co., Ltd. Ground sand maker
US5373994A (en) * 1993-07-29 1994-12-20 Materials Research Corporation Ball mill can positioning device
FR2772100A1 (fr) * 1997-12-05 1999-06-11 Technip Cie Systeme d'entrainement d'un tambour en rotation
US20080209754A1 (en) * 2004-07-20 2008-09-04 Lg Electronics, Inc. Drying Rack in Dryer
CN102620558A (zh) * 2012-03-28 2012-08-01 新兴能源装备股份有限公司 一种用于大型回转窑窑位的双向液压挡轮自动控制装置

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1161206B (de) * 1959-12-17 1964-01-09 Miag Muehlenbau & Ind Gmbh Einrichtung zur axialen Lagerung eines unter Laengsschub stehenden Drehrohrs
DE1291572B (de) * 1961-10-05 1969-03-27 Kennedy Van Saun Mfg & Eng Cor Axialdrucklager mit UEberlastsicherung fuer einen Drehkoerper, insbesondere fuer Drehrohroefen

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1854570A (en) * 1930-10-21 1932-04-19 Lawrence B West Adjustment for driers
US1925875A (en) * 1931-09-03 1933-09-05 Wilson L Mclaughlin Garbage incinerator

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1854570A (en) * 1930-10-21 1932-04-19 Lawrence B West Adjustment for driers
US1925875A (en) * 1931-09-03 1933-09-05 Wilson L Mclaughlin Garbage incinerator

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3468522A (en) * 1966-12-05 1969-09-23 Rene Bovagne Rotatable apparatus,more particularly a rotatable kiln,for the treatment of materials
US3966395A (en) * 1973-11-09 1976-06-29 Klockner-Humboldt-Deutz Aktiengesellschaft Pressure roller stand for forcible longitudinal displacement of large rotating drums
US4226271A (en) * 1978-06-21 1980-10-07 Coleman Thomas R Drum debarker
US4696116A (en) * 1986-06-23 1987-09-29 Guaranty Performance Co., Inc. Mounting structure for rotary drum dryer
US4995561A (en) * 1989-02-23 1991-02-26 Nakaya Jitsugyo Co., Ltd. Ground sand maker
US5373994A (en) * 1993-07-29 1994-12-20 Materials Research Corporation Ball mill can positioning device
FR2772100A1 (fr) * 1997-12-05 1999-06-11 Technip Cie Systeme d'entrainement d'un tambour en rotation
WO1999030095A1 (fr) * 1997-12-05 1999-06-17 Technip Systeme d'entrainement d'un tambour en rotation
US6186778B1 (en) 1997-12-05 2001-02-13 Technip Device for driving a cylinder in rotation
US20080209754A1 (en) * 2004-07-20 2008-09-04 Lg Electronics, Inc. Drying Rack in Dryer
CN102620558A (zh) * 2012-03-28 2012-08-01 新兴能源装备股份有限公司 一种用于大型回转窑窑位的双向液压挡轮自动控制装置
CN102620558B (zh) * 2012-03-28 2013-10-16 新兴能源装备股份有限公司 一种用于大型回转窑窑位的双向液压挡轮自动控制装置

Also Published As

Publication number Publication date
FR1133970A (fr) 1957-04-04
DK87715C (da) 1959-08-17
GB768629A (en) 1957-02-20
CH337119A (de) 1959-03-15
AT192316B (de) 1957-10-10

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