EP1623141A2 - Boite de vitesses et centrifugeuse la comprenant - Google Patents

Boite de vitesses et centrifugeuse la comprenant

Info

Publication number
EP1623141A2
EP1623141A2 EP04730599A EP04730599A EP1623141A2 EP 1623141 A2 EP1623141 A2 EP 1623141A2 EP 04730599 A EP04730599 A EP 04730599A EP 04730599 A EP04730599 A EP 04730599A EP 1623141 A2 EP1623141 A2 EP 1623141A2
Authority
EP
European Patent Office
Prior art keywords
gearbox
gear
housing
bowl
speed
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.)
Withdrawn
Application number
EP04730599A
Other languages
German (de)
English (en)
Inventor
Jan Michaelsen
Raymond John Hicks
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.)
Incentra Ltd
Original Assignee
Incentra Ltd
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 Incentra Ltd filed Critical Incentra Ltd
Publication of EP1623141A2 publication Critical patent/EP1623141A2/fr
Withdrawn legal-status Critical Current

Links

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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F16H3/724—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously using external powered electric machines
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B1/00—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles
    • B04B1/20—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles discharging solid particles from the bowl by a conveying screw coaxial with the bowl axis and rotating relatively to the bowl
    • B04B1/2016—Driving control or mechanisms; Arrangement of transmission gearing
    • 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
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • F16H57/048—Type of gearings to be lubricated, cooled or heated
    • F16H57/0482—Gearings with gears having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B1/00—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles
    • B04B1/20—Centrifuges with rotary bowls provided with solid jackets for separating predominantly liquid mixtures with or without solid particles discharging solid particles from the bowl by a conveying screw coaxial with the bowl axis and rotating relatively to the bowl
    • B04B1/2016—Driving control or mechanisms; Arrangement of transmission gearing
    • B04B2001/2025—Driving control or mechanisms; Arrangement of transmission gearing with drive comprising a planetary gear
    • 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
    • F16H2001/2881—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two axially spaced central gears, i.e. ring or sun gear, engaged by at least one common orbital gear wherein one of the central gears is forming the output

Definitions

  • the present invention relates to a gearbox and to a centrifuge incorporating such a gearbox, and in particular to a decanter type of centrifuge with a conveyer and a bowl interconnected by the gearbox used for rotation of the conveyer.
  • Decanter centrifuges are centrifugal machines employed for separating particulate solids (and/or different density liquids) from liquids. They comprise a tubular bowl which is rotated at high speed to effect separation, forming an outer layer of solids against the inner surface of the bowl, and an internally therein mounted screw conveyer which is rotated relative to the bowl to displace the solids axially towards an outlet at one end of the bowl, while the cleaned liquid flows to an outlet in the opposite end of the bowl.
  • the present invention is concerned with a gearbox for coupling the screw conveyer of a decanter centrifuge to the bowl to provide the desired relative rotation between the bowl and the conveyer.
  • the transmission comprises at least two gear stages, because one planetary stage alone is less capable of dealing with the high torques and high tooth speeds than two stages.
  • Such gearboxes comprise three members, an input member, an output member and a reaction member, the latter of which is either fixed to the machine frame or rotated at a slower speed than the rotor to adjust the relative speed of the conveyer to the bowl.
  • a reaction member the latter of which is either fixed to the machine frame or rotated at a slower speed than the rotor to adjust the relative speed of the conveyer to the bowl.
  • This braking can be provided by either a pulley drive connected to the centrifuge drive motor, an electrical brake, i.e. an eddy-current brake, or by an electrical motor with a frequency converter attached to control the speed and the possibility to regain some of the brake energy.
  • the conveyer rotating slower than the bowl influences the interior flow of the suspension inside the bowl when the incoming suspension is accelerated up to the speed of the bowl. This influence is positive, if the suspension is fed into the bowl at a position near the solids outlet end of the bowl, but it is negative, if the feed point is near the liquid outlet, which is desirable for certain applications.
  • a solution to this problem of relative motion could be to use a three-stage planetary gearbox, which would make the conveyer rotate faster than the bowl, as well as providing a higher transmission ratio, but such a solution is not practicable because such a gearbox would be heavier and longer and would therefore penalise the maximum operational speed of the centrifuge.
  • WO 91/10846 describes a planetary gearbox comprising a double planetary gear train having a first stage comprising a sun gear, a ring gear coupled to the bowl for rotation therewith and planet gears mounted on a carrier, the second stage comprising a sun gear fast with the first stage carrier, a ring gear coupled to the bowl for rotation therewith, and planet gears mounted on a carrier which is coupled to the screw conveyer, and wherein one of the said stages comprises idler gears which couple the sun gear of that stage to the corresponding planet gears.
  • centrifuges For very stable processes, i.e. for processes with high flow rates like thickening or classification, the conveying speed can be kept constant.
  • Such centrifuges have a simple conveyer drive comprising an epicyclic (i.e. planetary) type of gear transmission between the conveyer and the bowl, with the reaction member (i.e. sun wheel shaft) being fixed to the machine frame.
  • the reaction member i.e. sun wheel shaft
  • a maximum load mechanism releases the fixture and lets the reaction member rotate with the bowl, thus reducing the conveying speed to zero, and the centrifuge can be cleaned and restarted after re-engagement of the release mechanism.
  • the reaction member may be engaged by a fixed ratio pulley transmission, thus giving a means of changing the conveying speed by changing the pulleys. This adjustment can, however, only be done, when the centrifuge is at a stand-still.
  • a disadvantage of the above mentioned fixed-ratio solutions is that it cannot be changed while the centrifuge is operating, and that if the speed of the bowl is decreased (in order to ease the G-force on the solids and thereby ease the conveying-out of the solids), the speed of the conveyer decreases at the same rate as the bowl speed, thus reducing the speed of removal of solids from the bowl. It is desirable to have the conveying speed constant, or to increase, during such relief-actions, and a solution to this is provided by applying a controlled braking mechanism to the sun wheel.
  • Such a controlled brake mechanism causes the reaction member (sun wheel) to rotate at a speed between zero and the speed of the bowl, thereby adjusting the conveying speed between maximum speed (given by the transmission ratio of the gearbox) and zero.
  • the braking causes power to leave the rotor system, and it will dissipate from the braking component as heat. If a conveying speed close to zero is needed, the speed of the reaction sun wheel will be high (close to the bowl speed), and the resulting power loss in the brake will be similarly high.
  • the braking power is depending on the gearbox ratio and the torque generated between the conveyer and the bowl. If the generated torque is of the order of 8000 Nm at a bowl speed of 4000 rpm, and the ratio is 80:1 (which is a quite common ratio found in the market today), the resulting relative speed of the conveyer to the bowl is 50 rpm with fixed sunwheel. The maximum needed relative speed, however, is about 15 rpm, and the maximum torque would be occurring at about 1 rpm.
  • the power loss is therefore much less than above, and the drive motor for the centrifuge can be reduced in size by the difference.
  • the limit ratio is somewhere between 120 and 150, and thus the optimum gearbox layout is not possible within the frames of the present technology.
  • a basic object of the invention is the provision of a gearbox and a centrifuge incorporating such a gearbox with which it is possible to establish a relative speed difference between the bowl and the conveyer of a centrifuge with smaller losses than previously known.
  • a gearbox for a centrifuge such as a decanter centrifuge, comprising a rotatable bowl connected to a housing of the gearbox drivable at a first speed by a first external driving means and a helical conveyer coaxially arranged for rotating therein at a second rotational speed, wherein the gearbox comprises a compound planet epicyclic gear train, and compound planet wheels of the epicyclic gear train are radially supported by one or more rings to counteract the centrifugal forces acting on them.
  • the present invention provides an efficient, compact and uncomplicated gearbox for operating a decanter centrifuge, because the efficiency of the gearbox of the invention is higher than the conventionally applied gearboxes, and because the number of parts needed for the duty is kept at a minimum. By a simple exchange of parts, it can be made to provide a faster or slower movement of the conveyer relative to the bowl.
  • the present invention comprises a compound-planet epicyclic gearbox, "compound” referring to the fact that each planet is meshing with two internal gears and therefore has a set of (usually different) gears at each end, in which a number of compound planet gears are supported by bearings on a common carrier, and each set of gears on the compound planets are meshed with a ring gear, of which one is fast with the housing which is attached to the bowl, and the other is fast with a shaft connected to the conveyer.
  • One of the sets of gears on the compound planets are meshed with a sun wheel acting as the reaction member.
  • the planet gears are designed to be as light as possible to reduce the large centrifugal forces created by the rotation of the gearbox, when the centrifuge operates.
  • the planet wheels are supported by a ring acting as support on roller diameters on the planet gears in the same way as rollers are supported by the outer race ring in a roller bearing.
  • This feature makes it possible to use rolling element bearings that only need a small amount of lubrication compared with journal bearings and thus is less vulnerable and less complicated than a similar design with journal bearings.
  • a section of the (hollow) shaft is made thin in
  • (both) ring gears are designed with as thin sections as possible with regard to the fatigue strength of the material. This in combination
  • the planet wheels and the ring gears are exchangeable and can be
  • the two rows of gears on the compound planets are identical, in which case the problem of timing the gears during manufacture and mounting is avoided, and the gearbox can be changed
  • An optional built-in oil pump is either based on the centripetal pump ("pitot tube”) principle, and is therefore dependent on the direction of rotation to build up lubrication pressure, or it is a set of positive displacement pumps incorporated into the carrier utilising the relative motion of the planet wheel shafts in relation to the carrier.
  • Fig. 1 shows a general arrangement of a decanter centrifuge with a differential gear conveyor drive according to the invention.
  • Fig. 2 shows a first embodiment of the invention as a diagrammatic axial cross-section of the gearbox;
  • Fig. 3 shows a second embodiment of the invention with a built-in pitot tube oil pump
  • Fig. 4 shows a third embodiment of the invention with built-in gear type oil pumps driven by the movement of the planets relative to the carrier;
  • Fig. 5 shows a fourth embodiment of the invention with a built-in Gerotor type oil pump driven by the movement of the carrier relative to the housing.
  • Fig. 6 shows a detailed cross-section of one embodiment of the invention to clearly illustrate the key feature in the design: the light weight planet wheels supported by the support ring, the flexible conveyer shaft to enable self-alignment of the gear meshes, and the attachment of the ring gears to housing and conveyer shaft, resp., with screws, enabling a simple swap of the ring gears.
  • Fig. 1 shows a general arrangement of a decanter centrifuge with gearbox conveyer drive, comprising a bowl 1 rotatably supported by bearings 12, and a helical conveyer 2 mounted therein, supported by bearings 13. At one end a shaft 23 extending from the conveyor 2 is connected to the bowl 1 through a planetary gear transmission 7, the reaction member 15 of which is connected via a pulley transmission 20 to a braking motor 10 controlled by a frequency converter 8. The bowl 1 is driven by a motor 11 via a pulley transmission 9 providing a fixed speed of the bowl 1.
  • the conveyor 2 is brought to rotate within the bowl 1 at a speed slightly different to the bowl, thus creating a screw conveying action towards the conical end 5 of the bowl 1 to any matter 14 deposited onto the inner wall of the bowl 1.
  • the conveying action requires quite a high driving torque which is provided by the gear transmission 7.
  • the decanter centrifuge functions in the following way:
  • the slurry or suspension 21 that is to be separated is fed to the centrifuge through a feed pipe 3 and a feed chamber 4 in the interior of the conveyor.
  • the feed is contained within the bowl 1 forming an annular liquid ring 19, from which the solids particles are precipitated towards the inner face of the bowl 1 forming a cake 14, which is subsequently conveyed towards the conical end 5 of the bowl 1 by the conveyor 2.
  • the cake compresses and dewaters during passage of the dry part of the bowl and leaves the centrifuge through apertures 16 in the bowl wall.
  • the cleaned liquid 6 leaves the bowl 1 through another set of apertures 17.
  • FIG. 2 shows a cross-sectional view of a gearbox housing 31 attached to the bowl of the centrifuge 1 with a ring gear 28, and a second ring gear 27 fast with a shaft 23 attached to the conveyer of the centrifuge.
  • a number of compound planet wheels 29 mesh with the ring gears and are supported by a common carrier 34.
  • One of the gears on the compound planets 29 mesh with a sun wheel 15, which works as the reaction member.
  • a ring 36 supports the planet wheels 29 against the centrifugal forces acting on the planet wheels.
  • the planet wheels are made lightweight by making them hollow and only with adequate material to carry the loads.
  • the supporting action of the ring 36 makes it possible to use rolling element bearings for the planets, as they only have to withstand the forces from the torque load. As rolling element bearings do not need pressurised oil for lubrication, the splashing from the teeth will provide adequate lubrication for all the moving elements inside the housing 31.
  • the shaft 23 has a thin section 24 which enables the self-centering forces from the gear mesh 39 to align the ring gear 27 relative to the planet wheel mesh, which in turn is governed by the planet wheel contact with the support ring 36.
  • the gearbox In a conventional 2-stage epicyclic gearbox, the gearbox is filled to a level (when the gearbox rotates) inside of the planet centres in order to provide lubricant to the highly loaded planet Qournal) bearings. Journal bearings are used because rolling element bearings are not able to withstand the comparatively high forces from the centrifugal loads on the planets. The oil is therefore subject to centrifugal forces, creating a high pressure near the peripheral wall of the gearbox. When a pair of teeth in a ring gear and a planet gear engages, the oil has to be pumped to the sides (distance: half a gear width) against this pressure, thereby causing a considerable loss that is dissipated as heat.
  • the compound planet gears 29 have the same number of teeth on the two gear meshes 39 and 40.
  • the two ring gears having different number of teeth, so that one revolution of the carrier causes the output shaft 23 to move relative to the housing 7 by an amount given by the difference of teeth numbers on the gear meshes 39 and 40.
  • the difference in working pitch circle diameters caused by the different numbers of teeth on the two ring gears are compensated by different correction factors in the manufacturing of the gears.
  • Fig. 3 shows a gearbox similar to fig. 2, but with a built-in oil scoop type oil
  • the oil pump 38 shown is a scoop-type pump exploiting the high rotational speeds of the housing.
  • the scoop 37 which skims the surface of the oil shown as
  • a dashed line 46 in figure 3 is attached to a reaction shaft 35 kept stationary by
  • the lubrication is provided by a centripetal pump 38, which takes advantage of the high rotating speed difference between the
  • centripetal pump delivers the pressurised oil via an oil transfer bushing/bearing to
  • Fig. 4 shows a gearbox similar to fig. 2, but with a built-in gear type oil pump
  • a disadvantage of the gearbox shown in figure 3 is that the oil pump only works when the gearbox is turning in the right direction, and the oil pressure is
  • the pressure generated is also high, i.e. about 30 bar, which is much more than
  • FIG. 4 An alternative, but more expensive solution is shown is figure 4.
  • a set of gears 42, 43 are mounted in a pump housing 44 attached to the end face of the carrier 34.
  • One of the gears, 43 is connected to a planet wheel and rotates at the same speed as the planet wheel,
  • gear pumps there is one set of gears for each planet, for balancing reasons. Some of the pumps could, however,
  • housing of the pump is designed in such a way that by dismantling it, turning it 180 degrees and mounting it using the other side as a mounting face, the pumping
  • Fig. 5 shows a gearbox similar to fig. 2, but with a built-in gerotor type oil
  • gerotor pump principle offers such a possibility
  • a set of lobe rotors 52, 53 are mounted in a pump housing 54 attached to the end face of the housing 31.
  • the inner lobe rotor, 53 is connected to the carrier 34 and rotates at the same speed as that, while the outer lobe rotor 54 is mounted in an eccentrically placed cavity 55 in the housing 54 and rotates therein driven by the inner lobe rotor 53, thus creating a pumping action as shown by arrows 61 (suction) and 62 (pressure).
  • the flow is guided by pockets 56 (suction) and 57 (pressure side) in the housing at either side of the lobe rotor cavity.
  • Fig. 6 shows a detailed cross-section of one embodiment of the invention (without oil pump) that clearly illustrates the key features of the design: - the light weight planet wheels 25 mounted in roller element bearings 26 and supported radially by
  • the support ring 26 (here shown as a separate, hardened ring connected to the housing 31 by a shrink fit),

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Centrifugal Separators (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)

Abstract

L'invention concerne une boîte de vitesses pour centrifugeuse, telle qu'une centrifugeuse de décantage, qui comprend un cylindre rotatif (1) relié à un logement (31) de la boîte de vitesses entraînée à une première vitesse par un premier dispositif d'entraînement externe (11) et un godet hélicoïdal (2) disposé coaxiallement de manière à tourner à une seconde vitesse de rotation. La boîte de vitesses comprend un train planétaire composé et des roues planétaires composées (29) du train planétaire sont radialement soutenues par au moins un anneau (36), de façon à compenser les forces centrifuges agissant sur elles. Cette invention a aussi trait à une centrifugeuse dotée d'une telle boîte de vitesses.
EP04730599A 2003-05-02 2004-04-30 Boite de vitesses et centrifugeuse la comprenant Withdrawn EP1623141A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GB0310157 2003-05-02
PCT/GB2004/001918 WO2004097255A2 (fr) 2003-05-02 2004-04-30 Boite de vitesses et centrifugeuse la comprenant

Publications (1)

Publication Number Publication Date
EP1623141A2 true EP1623141A2 (fr) 2006-02-08

Family

ID=33397052

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04730599A Withdrawn EP1623141A2 (fr) 2003-05-02 2004-04-30 Boite de vitesses et centrifugeuse la comprenant

Country Status (2)

Country Link
EP (1) EP1623141A2 (fr)
WO (1) WO2004097255A2 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006028804A1 (de) * 2006-06-23 2007-12-27 Westfalia Separator Ag Schneckenzentrifuge mit Antriebsvorrichtung
DE102008015134A1 (de) * 2008-03-20 2009-10-01 Gea Westfalia Separator Gmbh Getriebeanordnung für eine Zentrifuge
US8808154B2 (en) * 2010-09-13 2014-08-19 Hiller Gmbh Drive apparatus in a scroll centrifuge having a gearbox with a housing nonrotatably connected to a drive shaft
DE102011108008A1 (de) * 2011-07-19 2013-01-24 Harry Gaus Dekanterzentrifuge
FR2980546B1 (fr) * 2011-09-27 2014-05-16 Snecma Dispositif de lubrification d'une boite d'engrenage par une came exentrique
CA2889542A1 (fr) * 2014-04-30 2015-10-30 Ge Avio S.R.L. Transmission epyciclique comportant un mecanisme de lubrification
CN105202118A (zh) * 2015-09-16 2015-12-30 贵州群建精密机械有限公司 一种小模数行星齿轮减速器及其制作方法
CN105465285A (zh) * 2016-01-07 2016-04-06 刘朝龙 小型行星减速机构
CN105465286A (zh) * 2016-01-07 2016-04-06 刘朝龙 行星减速机
CN105465288A (zh) * 2016-01-07 2016-04-06 刘朝龙 行星减速机构
CN109027141A (zh) * 2018-10-31 2018-12-18 南京高精齿轮集团有限公司 行星传动系统

Family Cites Families (6)

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Publication number Priority date Publication date Assignee Title
DE3311310C1 (de) * 1983-03-28 1984-06-20 Bhs Bayerische Berg Planetengetriebe,das zwischen einer Stroemungsmaschine und einer elektrischen Maschine in einem Gehaeuse angeordnet ist
JPS61197062A (ja) * 1985-02-28 1986-09-01 Takashi Takahashi 遠心分離機の差動増速装置
DE9409109U1 (de) * 1994-06-03 1995-09-28 Flottweg Gmbh, 84137 Vilsbiburg Zentrifuge mit stufenloser Steuerung der Differenzdrehzahl zwischen Trommel und Räumwerkzeug
GB2354049A (en) * 1999-04-16 2001-03-14 Tim Tod Epicyclic reduction gearbox
WO2001048397A2 (fr) * 1999-12-28 2001-07-05 Diro Gmbh & Co. Kg Dispositif d'ajustement
WO2002081094A1 (fr) * 2001-04-04 2002-10-17 Centriquip Limited Boite de vitesses pour centrifugeuse telle qu'une centrifugeuse de decantation

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004097255A3 *

Also Published As

Publication number Publication date
WO2004097255A2 (fr) 2004-11-11
WO2004097255B1 (fr) 2005-03-24
WO2004097255A3 (fr) 2005-01-13

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