WO2013010667A1 - Centrifugeuse décanteuse - Google Patents

Centrifugeuse décanteuse Download PDF

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Publication number
WO2013010667A1
WO2013010667A1 PCT/EP2012/003028 EP2012003028W WO2013010667A1 WO 2013010667 A1 WO2013010667 A1 WO 2013010667A1 EP 2012003028 W EP2012003028 W EP 2012003028W WO 2013010667 A1 WO2013010667 A1 WO 2013010667A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
motor
output shaft
decanter centrifuge
drive
Prior art date
Application number
PCT/EP2012/003028
Other languages
German (de)
English (en)
Inventor
Harry Gaus
Original Assignee
Harry Gaus
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 Harry Gaus filed Critical Harry Gaus
Publication of WO2013010667A1 publication Critical patent/WO2013010667A1/fr

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Classifications

    • 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
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/19—Arrangements for cooling or ventilating for machines with closed casing and closed-circuit cooling using a liquid cooling medium, e.g. oil
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B9/00—Drives specially designed for centrifuges; Arrangement or disposition of transmission gearing; Suspending or balancing rotary bowls
    • B04B9/02—Electric motor drives
    • B04B9/04—Direct drive
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B9/00—Drives specially designed for centrifuges; Arrangement or disposition of transmission gearing; Suspending or balancing rotary bowls
    • B04B9/12—Suspending rotary bowls ; Bearings; Packings for bearings
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K1/00—Details of the magnetic circuit
    • H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
    • H02K1/22—Rotating parts of the magnetic circuit
    • H02K1/32—Rotating parts of the magnetic circuit with channels or ducts for flow of cooling medium
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/18—Casings or enclosures characterised by the shape, form or construction thereof with ribs or fins for improving heat transfer

Definitions

  • the invention relates to a decanter centrifuge with a motor-driven, rotating centrifuge drum and a mounted therein, rotatable relative to the centrifuge drum extruder screw, wherein a drive for the extruder screw is provided which has an electric motor and a reduction gear, in a connected to the centrifuge drum and with this are arranged with the rotating housing, wherein a first motor part (stator or rotor) of the electric motor is connected to the housing and runs with the centrifuge drum and a second motor part (rotor or stator), which rotates with the motor shaft drives the reduction gear and wherein the output shaft of the Reduction gear with the extruder screw in drive ⁇ compound is.
  • a drive for the extruder screw is provided which has an electric motor and a reduction gear, in a connected to the centrifuge drum and with this are arranged with the rotating housing, wherein a first motor part (stator or rotor) of the electric motor is connected to the housing and runs with the centrifuge drum and
  • Decanter centrifuges serve to separate an emulsion into a liquid and a solid phase in a continuous process.
  • the liquid phase is water
  • the solid phase is a specific heavy matter that is sentimentally sent to the inner wall by the rotation of the centrifuge drum as the liquid phase accumulates toward the center of rotation.
  • the solid phase is transported axially to an outlet, further compressed, dewatered and extruded from the outlet.
  • the liquid phase can move the centrifuge drum against the movement of the extruder screw through an overflow at the other
  • the extruder screw must perform a rotation at low speed, but large torque relative to the centrifuge drum.
  • the relative speed between the centrifuge drum and extruder screw should be adjustable and independent of the speed of the centrifuge drum. Decanter centrifuges are known in numerous designs.
  • DE-AS 1 086 181 discloses a decanter centrifuge in which one part, for example the centrifuge drum, is driven by a motor and the other part, in this case the extruder screw, is braked via an intermediate epicyclic gearbox with a larger reduction.
  • US Pat. No. 5,772,573 A discloses a decanter centrifuge in which the central shaft of a Harmony Drive with the characteristic elliptical roller bearing is fixed in space or driven by a stationary motor at low speed, while the flexible spline and the Ring gear of the Harmony Drive are co-rotated with the centrifuge drum, the extruder screw is rotatably connected to the ring gear.
  • DE 30 02 449 C2 shows and describes a device for controlling the relative rotational speed between the centrifuge drum and the extruder screw with two series-connected hydraulic motors and a planetary gear.
  • the moments of the centrifuge drum and extruder screw are each based on a space-fixed machine frame, whereby the undesirable reaction arises.
  • DE 25 25 280 C2 proposes directly driving the centrifuge drum by means of a drive motor by means of drive belts, while the extruder screw can be driven independently by means of a co-rotating hydraulic motor with rotary unions for the hydraulic fluid.
  • the motor shaft is designed as a hollow shaft, that at least a portion of the output shaft is arranged in the motor shaft, that the output shaft has a central channel to form a lubricant circuit and that in the lubricant - Circulation a delivery wheel is provided, which receives lubricant from an inner side of the centrifuge drum for supplying the lubricant circuit, wherein the feed wheel against the motor shaft and the output shaft is arranged freely rotatably.
  • the electric motor can be cooled from the inside via the lubricant flowing through the central channel.
  • the Decoupling the feed wheel from the motor shaft and from the output shaft has the advantage that the feed wheel does not necessarily have to rotate with the rotational speed of the centrifuge drum or the motor. As a result of the decoupling of the delivery wheel from the drive, it is thus possible to avoid centrifugal forces which would otherwise counteract the radially inwardly directed delivery rate of the delivery wheel.
  • the delivery wheel is rotatably mounted relative to the shaft on a shaft of a drive train comprising the motor shaft and the output shaft. It is particularly advantageous if the feed wheel is rotatably mounted on the output shaft.
  • the feed wheel is rotatably mounted on the output shaft.
  • on a seat of the feed wheel on the or a shaft circumferentially circumferential, closed to the outside ring groove is formed, on the one hand with at least one transport channel of the feed wheel and on the other connected to the central channel.
  • the annular groove is formed on the feed wheel and / or on the shaft. The formation of an annular groove has the advantage that a transport of the lubricant from the transport channel into the central channel at any rotational positions of the feed wheel on the shaft is possible.
  • the conveyor wheel is arranged fixed in space.
  • claws of a space-fixed fixed to a machine frame hollow shaft engage in recesses of the feed wheel to fix this spatially fixed.
  • the feed wheel has at least one conveying arm, which in a transversely oriented to the longitudinal or conveying direction cross-section at least in a dipped into a formed on the inside of the housing lubricant sump portion a streamlined or teardrop-shaped profile or a having oval profile.
  • the profile has a length along the flow of lubricant flowing past the delivery arm, which length is greater than the width of the profile transversely to the flow direction. It can also be provided that the flowed surface of the conveying arm has a convex curvature in the profile and / or that the profile in the region of the stall has a tip to prevent eddies.
  • the advantage here is that a trailed by the delivery arm in the lubricant sump furrow quickly closes again, so that the delivery arm does not turn empty after a full turn, but can absorb new lubricant.
  • the lubricant circuit has a pressure relief valve. Thus, bearing seals and the like can be relieved. It is particularly favorable when the pressure relief valve is provided on the delivery wheel.
  • the pressure limiting valve may be formed by a radially displaceable on the feed wheel, acted upon by a return spring valve body which seals a connected to the annular groove or annular groove monitoring channel tightly, as long as the lubricant pressure in the annular groove does not exceed a preset threshold.
  • the central channel is connected to a preferably cylindrical ring shape having a gap between the motor shaft and the output shaft.
  • This can be set up, for example, via at least one radial passage opening in the output shaft.
  • the reduction gear is designed as a circular thrust gear or Zyklogetriebe.
  • the reduction gear is designed as a circular thrust gear or Zyklogetriebe.
  • the reduction gear at least two eccentrically revolving cams or gears on ⁇ 2 utilizat, which can be arranged offset in rotation to each other for balancing.
  • two cams or gears can be offset from one another by 180 °
  • three cams or gears against each other by 120 ° are arranged rotationally offset or generally N eccentric rotating cams or gears against each other by 360 ° / N rotationally offset from each other.
  • the reduction gear is arranged on the side facing away from the extruder screw side of the electric motor.
  • the relatively large mass of the electric motor can be arranged as close to the extruder screw, which improves the overall smoothness.
  • the reduction gear rotatably on one with the output shaft connected carrier has a plurality of driving bolts, which engage in recesses at least one eccentrically rotating gear or at least one eccentrically revolving cam for producing a drive connection.
  • the carrier at least one lubricant channel for lubricant supply of bearings is formed on the driving pin and connected to the central channel.
  • the lubricant circuit can be additionally used to lubricate the moving parts of the reduction gear.
  • the abrasive brushes can preferably stand still. About the slip rings and brushes both the electric drive power and operating signals of the electric motor can be transmitted.
  • the slip rings and brushes are preferably concentric with the motor housing arranged one of the output side of the transmission axially opposite housing part.
  • a slip ring package rotating concentrically with the housing can be provided, which is contacted by means of a plurality of grinding brushes offset in the angular direction. This ensures that there is always a contacting of the electric motor during the rotation, even if vibrations occur in the radial direction.
  • slip ring package runs on a part of the motor housing and is connected by means of resilient contacts with the motor cables, this can be easily replaced if necessary and without further connection assemblies.
  • the slip rings for contacting the electric motor of the drive for the extruder screw can be mounted on a hollow pin of the motor housing.
  • FIG. 1 shows a schematic representation of a decanter centrifuge with a device for process control
  • Fig. 2 ne sectional view of an axial section of a
  • FIG. 4 shows an axial section of the feed wheel according to FIG. 3 along A-A, FIG.
  • FIG. 5 is a sectional view of an axial section of another embodiment of a drive for the extruder screw
  • FIG. 6 shows a radial section of the permanently excited rotor in the drive according to FIG. 5, FIG.
  • FIG. 7 is a radial section of the electric motor in the drive according to FIG. 5, FIG.
  • Fig. 8 is an axial section of another invention
  • Fig. 9 is a radial section of a drive according to the invention with additional external cooling.
  • a designated as a whole with 1 decanter centrifuge has, according to FIG. 1, a centrifuge drum 2 and a stored therein, rotatable relative to the centrifuge drum 2 extruder screw 3.
  • the centrifuge drum 2 is driven by a motor 4 and a belt drive 5.
  • the drive of the motor 4 takes place via an inverter 6.
  • the extruder screw 3 is moved independently of a drive 7, which rotatably with the centrifuge drum. 2 is connected and is co-rotated with this.
  • the drive 7 is connected via stationary stationary connection elements 8 with a frequency converter 9.
  • the frequency converter 9 also allows the detection of other operating parameters such as speed, torque, slip, power, temperature, etc. without additional sensors.
  • the control of the frequency converter 9 can via a conventional computer 10, which in turn is connected to a higher-level controller (SCADA).
  • SCADA higher-level controller
  • inverters 6, 9 and the computer 10 By using standardized components for the inverters 6, 9 and the computer 10, they can be replaced quickly in the event of a fault or a defect.
  • FIG. 2 shows an axial section through the drive 7 from FIG. 1.
  • the drive 7 has an electric motor 11 and a reduction gear 12, which are arranged in a housing 13.
  • the housing 13 is rotatably connected to the centrifuge drum 2 and is rotated together with this.
  • the electric motor 11 has an energized stator 14, which is fixed to the inside of the housing 13.
  • the electric motor 11 further comprises an asynhcronen, provided with short-circuit cage rotor 15, which rotates with the motor shaft 16.
  • the motor shaft 16 constitutes the driving shaft of the reduction gear 12.
  • the motor shaft 16 is formed as a hollow shaft, and the output shaft 17 of the reduction gear 12 is passed through the motor shaft 16, so that a portion of the output shaft 17 is disposed in the motor shaft 16.
  • an axially extending central channel 18 is formed in the output shaft 17.
  • This central channel 18 may, as shown in Fig. 2, be arranged centrally in the output shaft 17, but there are also off-center configurations possible.
  • a feed wheel 19 is rotatably mounted with respect to the output shaft 17 on this output shaft 17.
  • This delivery wheel 19 is set up so that lubricant which accumulates in a lubricant sump (not further shown) on the inside 20 of the housing 13 due to the rotation of this housing 13 can receive it and convey it to the central channel 18.
  • Fig. 3 and Fig. 4 show various views of the feed wheel 19.
  • Fig. 3 shows a radial section through the feed wheel 19, while Fig. 4 shows an axial section along the line A-A in Fig. 3.
  • annular collecting channel in the form of an annular groove 21 is formed on the feed wheel 19, which completely rotates the output shaft 17 in the circumferential direction.
  • the annular groove 21 is connected to two transport channels 22 of the delivery wheel 19, via which the lubricant received from the inside 20 is transported to the annular groove 21.
  • the annular groove In the assembled position shown in FIG. 2, the annular groove is connected via star-shaped in the output shaft 17 formed radial bores 23 with the central channel 18.
  • the lubricant adhering to the inner side 20 and forming a lubricant sump can be received by the feed wheel 19 and conveyed via the annular groove 21 into the central channel 18.
  • the housing 13 rotates while the feed wheel 19 remains fixed in space.
  • recesses 24 are formed on the feed wheel 19, in which claws 25 engage in the manner of a dog clutch.
  • the claws 25 are formed at an axial end of a hollow shaft 26 which is rotatably connected at its opposite axial end with a flange 27.
  • the flange 27 is connected via bolts 28 by struts, not shown, with the fixed, stationary machine frame 66 (see Fig. 9).
  • the feed wheel 19 is prevented from rotating relative to a fixed coordinate system and slides on the output shaft 17 when the output shaft 17 rotates.
  • the feed wheel 19 remains in this way independent of the rotation of the motor shaft 16 or the output shaft 17 fixed in space.
  • the brushes 30 for electrical contacting of the electric motor 11 and the connection elements 8 forming the cable connection and the protective hood 31 for these connection elements 8 also remain fixed in space.
  • the hollow shaft 26 receives an oil filter 32, which rotatably is connected to the output shaft 17 and in which the central channel 18 opens.
  • the oil filter 32 is screwed into the output shaft 17, whereby a sliding seal can be omitted.
  • the thus co-rotated oil filter 32 has radial outlet openings 33 through which lubricant due to the self-rotation of the oil filter 32 is conveyed to the bearing 34 of the output shaft 17.
  • the aforementioned transport channels 22 are each arranged in a conveying arm 29.
  • the conveying arms extend radially with respect to the center of rotation of a cylindrical base body 34 of the feed wheel 19 and protrude from this cylindrical body 34.
  • a probe portion is arranged in each case as a collection nozzle 35 to the radially foundedseit strength ends of the conveying arms 29, said passage ⁇ channels are directed exclusively tangentially or in the circumferential direction 36 and open into the respective transport channel 22nd
  • the conveying arm 29 is configured with a cross-section, which in the flow direction of the flowing lubricant, ie in the circumferential direction with respect to the center of rotation of the feed wheel 29, has a length which is greater than the width transversely to this length, ie in the axial direction with respect to the center of rotation of the conveyor wheel 19.
  • This oval profile forms a streamline shape for the lubricant passing by, through which a furrow formation is largely avoided behind the conveying arm 29 in the lubricant sump.
  • a pressure relief valve 37 is formed on the feed wheel 19, which has a valve body 38 which closes by means of a return spring 39 a branched off from the annular groove 21 monitoring channel 40. Excess lubricant can exit the lubricant outlet 72 via this pressure limiting valve 37 and be returned to the mentioned lubricant sump.
  • the valve body 38 consists of a cylinder with star-shaped projections 41, wherein the valve body 38 is guided by these star-shaped projections 41. Once the valve body 38 is lifted by the lubricant pressure from the monitoring channel 40, lubricant can flow between the star-shaped projections 41 to the outside.
  • the central channel 18 is connected via radial passage openings 42 with the gap 43 between the motor shaft 16 and the output shaft 17, so that the promoted by the feed wheel 19 lubricant u.a. in this space 43 is promoted, where he can cool the motor shaft 16 and thus the rotor 15 from the inside.
  • the reduction gear 12 is designed as a circular thrust gear or Zyklogetriebe and has two eccentrically rotating gears or cams 44 which are mounted on eccentrics 45 by means of needle roller 74.
  • the eccentrics 45 are formed on the motor shaft 16. Upon rotation of the motor shaft 16 thus the gears or cams 44 are unrolled at a ring gear 46.
  • an outer toothing may be formed on the toothed wheel or the cam disk 44, which meshes with an internal toothing of the ring gear 46, or recesses and projections may be formed on the toothed wheel or cam disk 44 which interact with webs on the ring gear 46 such that the gear or cam 44 rolls on a rotation of the eccentric 45 on the ring gear 46.
  • a support 47 is rotatably disposed on the output shaft 17, which carries driving pin 48.
  • the driving pins 48 engage in a respective bore 49 on the gears or cams 44. As a result, the resulting from the mentioned differential angle slow rotational movements are transmitted to the output shaft 17.
  • a supply channel 50 is formed, which is fed from the central channel 18 and which supplies the bearings 51 with the driving pin 48 with lubricant.
  • the collecting nozzles 35 are designed as adapted according to shape and inlet cross-section probe parts to the amount of entry after the operating data, the viscosity etc. to determine.
  • circumferential cooling fins 53 are formed on the outside relative to the stator 14 and in particular in the region of the stator winding 52, via which the stator 14 can be cooled.
  • Fig. 2 the lubricant flow of the lubricant circuit is shown by arrows.
  • Fig. 2 also shows the electrical connection of the electric motor 11, which is designed in this example with an internal squirrel cage rotor 15 and an external wound stator 14.
  • the slip ring body 55 which rotates with the housing 13 and which is contacted by the grinding brushes 30, which are diametrically opposed in pairs or offset by 90 °.
  • the motor lines 57 are connected, which are guided by a tight passage and the indicated grooves and holes in the stator winding 42.
  • FIG. 5 shows an axial section of a further drive 7 according to the invention, as it can be used in a decanter centrifuge 1 according to the invention according to FIG. 1.
  • the drive 7 according to FIG. 5 differs from the drive 7 according to FIGS. 2 to 4 by the design of the electric motor 11.
  • the permanent magnets 58 are buried in the rotor 15 under the outer surface of the rotor 15.
  • Fig. 6 shows in a radial section, as two magnets 58 in a V-shaped layer form a pole 59 or 60 with opposite polarity and with concentrated magnetic flux, the tooth winding 52 with a usually three-strand single acting on the teeth 62 of the stator 14 together ,
  • This known per se high-pole design results in particularly large torques at a preferred axial length here by the elimination of winding heads.
  • FIG. 8 shows an axial section of a third embodiment according to the invention of a drive 7 for the extruder screw 3 from FIG. 1.
  • Fig. 8 are functionally or constructively to the embodiment of FIG. 2 similar components or details with the same reference numerals and not described again separately. The comments on Fig. 2 apply accordingly.
  • FIG. 8 differs from the embodiments of FIG. 2 and FIG. 5 in that the ring gear 46 of the reduction gear 12 is not fixed to the housing 13, but via a support plate 73 on the output shaft 17.
  • the exemplary embodiment according to FIG. 8 differs further from the exemplary embodiments described above in that the carrier 47 of the driver pin 48 is not fixed to the output shaft 17 but to the housing 13.
  • Fig. 9 shows in an axial section, a solution for supporting the heat release over the outside of the housing 13 of independent inventive importance.
  • the housing 13, which receives the electric motor 11 rotates in the direction of arrow 63.
  • the protective cover 31 with the connecting cable 64 is held by a torque arm 65 which engages the flange 27 on the machine frame 66 fixed space.
  • a constriction or obstruction of the flow channel 70 is formed in the region of the outlet slots 69, through which an air flowing in the flow channel 70 air is passed through the outlet slots 69 to the outside.
  • baffles 71 enhance this effect.
  • the air located in the flow channel 70 is entrained and promoted from the outlet slots 69 because of the constriction at the end of the flow channel 70.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Centrifugal Separators (AREA)

Abstract

L'invention concerne une centrifugeuse décanteuse (1) comportant un tambour de centrifugeuse (2) et une vis d'extrudeuse (3) logée rotative dans le tambour de centrifugeuse (2), la vis d'extrudeuse (3) étant entraînée par un entraînement électrique (7) tournant avec le tambour de centrifugeuse (2). Selon l'invention, une roue transporteuse (19) est disposée dans la chaîne cinématique entre un moteur électrique (11) de l'entraînement (7) et la vis d'extrudeuse (3) pour transporter du lubrifiant du côté intérieur (20) d'un boîtier (13) de l'entraînement (7) par un mouvement relatif de la roue de transport (19) contre le boîtier (13) dans un circuit de lubrification pour lubrifier et refroidir l'entraînement (7), la roue de transport (19) étant logée rotative coulissante sur un arbre (16, 17) de la chaîne cinématique et maintenue spatialement fixe en fonctionnement.
PCT/EP2012/003028 2011-07-19 2012-07-18 Centrifugeuse décanteuse WO2013010667A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011108008.6 2011-07-19
DE102011108008A DE102011108008A1 (de) 2011-07-19 2011-07-19 Dekanterzentrifuge

Publications (1)

Publication Number Publication Date
WO2013010667A1 true WO2013010667A1 (fr) 2013-01-24

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PCT/EP2012/003028 WO2013010667A1 (fr) 2011-07-19 2012-07-18 Centrifugeuse décanteuse

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DE (2) DE102011108008A1 (fr)
WO (1) WO2013010667A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20200208227A1 (en) * 2017-08-31 2020-07-02 Sudzucker Ag Method for reducing the sugar loss in the removal of a coagulate from pre-liming juice and for thickening the coagulate, use of a decanter centrifuge, fraction containing protein, and sugar beet pre-liming juice

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015115720A1 (de) * 2015-09-17 2017-03-23 Gea Mechanical Equipment Gmbh Antriebsvorrichtung für eine Vollmantel-Schneckenzentrifuge
DE102018216120A1 (de) * 2018-09-21 2020-03-26 Conti Temic Microelectronic Gmbh Rotorwellenanordnung für eine elektrische Maschine

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DE1086181B (de) 1958-07-26 1960-07-28 Josef Berger Schneckenzentrifuge mit veraenderlicher Differenzdrehzahl zwischen Schleudertrommel und Schnecke
US3734399A (en) 1971-05-28 1973-05-22 Beloit Corp Differential scroll drive
DE2525280C2 (de) 1975-06-06 1983-06-23 Flottweg-Werk Dr. Georg Bruckmayer GmbH & Co. KG, 8313 Vilsbiburg Vollmantel-Schneckenzentrifuge mit gegenüber ihrem Mantelteil mit Differenzdrehzahl umlaufendem Schneckenteil
DE3116749C2 (fr) 1980-05-16 1988-06-23 Glyco-Antriebstechnik Gmbh, 6200 Wiesbaden, De
DE3002449C2 (fr) 1979-02-23 1988-10-06 Alfa-Laval Separation A/S, Soeborg, Dk
US5772573A (en) 1996-02-26 1998-06-30 Baker Hughes Incorporated Decanter centrifuge and gear box with harmonic drive and associated operating method
WO2002081094A1 (fr) * 2001-04-04 2002-10-17 Centriquip Limited Boite de vitesses pour centrifugeuse telle qu'une centrifugeuse de decantation
WO2004097255A2 (fr) * 2003-05-02 2004-11-11 Incentra Limited Boite de vitesses et centrifugeuse la comprenant
DE102004034409A1 (de) 2004-07-16 2006-02-02 Hiller Gmbh Antriebsvorrichtung für Schneckenzentrifugen
DE102008015134A1 (de) * 2008-03-20 2009-10-01 Gea Westfalia Separator Gmbh Getriebeanordnung für eine Zentrifuge

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US20070053790A1 (en) 2003-04-16 2007-03-08 Arkray, Inc. Analyzing tool being reduced in distance of diffusion of reagent and method for manufacture thereof

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1086181B (de) 1958-07-26 1960-07-28 Josef Berger Schneckenzentrifuge mit veraenderlicher Differenzdrehzahl zwischen Schleudertrommel und Schnecke
US3734399A (en) 1971-05-28 1973-05-22 Beloit Corp Differential scroll drive
DE2525280C2 (de) 1975-06-06 1983-06-23 Flottweg-Werk Dr. Georg Bruckmayer GmbH & Co. KG, 8313 Vilsbiburg Vollmantel-Schneckenzentrifuge mit gegenüber ihrem Mantelteil mit Differenzdrehzahl umlaufendem Schneckenteil
DE3002449C2 (fr) 1979-02-23 1988-10-06 Alfa-Laval Separation A/S, Soeborg, Dk
DE3116749C2 (fr) 1980-05-16 1988-06-23 Glyco-Antriebstechnik Gmbh, 6200 Wiesbaden, De
US5772573A (en) 1996-02-26 1998-06-30 Baker Hughes Incorporated Decanter centrifuge and gear box with harmonic drive and associated operating method
WO2002081094A1 (fr) * 2001-04-04 2002-10-17 Centriquip Limited Boite de vitesses pour centrifugeuse telle qu'une centrifugeuse de decantation
WO2004097255A2 (fr) * 2003-05-02 2004-11-11 Incentra Limited Boite de vitesses et centrifugeuse la comprenant
DE102004034409A1 (de) 2004-07-16 2006-02-02 Hiller Gmbh Antriebsvorrichtung für Schneckenzentrifugen
DE102008015134A1 (de) * 2008-03-20 2009-10-01 Gea Westfalia Separator Gmbh Getriebeanordnung für eine Zentrifuge

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20200208227A1 (en) * 2017-08-31 2020-07-02 Sudzucker Ag Method for reducing the sugar loss in the removal of a coagulate from pre-liming juice and for thickening the coagulate, use of a decanter centrifuge, fraction containing protein, and sugar beet pre-liming juice
US11702710B2 (en) * 2017-08-31 2023-07-18 Sudzucker Ag Method for reducing the sugar loss in the removal of a coagulate from pre-liming juice and for thickening the coagulate, use of a decanter centrifuge, fraction containing protein, and sugar beet pre-liming juice

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DE202012012743U1 (de) 2013-10-10
DE102011108008A1 (de) 2013-01-24

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