EP2699355A2 - Centrifugeuse et procédé pour contrôler un couple - Google Patents

Centrifugeuse et procédé pour contrôler un couple

Info

Publication number
EP2699355A2
EP2699355A2 EP12715967.1A EP12715967A EP2699355A2 EP 2699355 A2 EP2699355 A2 EP 2699355A2 EP 12715967 A EP12715967 A EP 12715967A EP 2699355 A2 EP2699355 A2 EP 2699355A2
Authority
EP
European Patent Office
Prior art keywords
centrifuge
torque
input shaft
transmission input
overload
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.)
Granted
Application number
EP12715967.1A
Other languages
German (de)
English (en)
Other versions
EP2699355B1 (fr
Inventor
Volker Knospe
Richard Korzinetzki
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.)
GEA Mechanical Equipment GmbH
Original Assignee
GEA Mechanical Equipment GmbH
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 GEA Mechanical Equipment GmbH filed Critical GEA Mechanical Equipment GmbH
Publication of EP2699355A2 publication Critical patent/EP2699355A2/fr
Application granted granted Critical
Publication of EP2699355B1 publication Critical patent/EP2699355B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B3/00—Centrifuges with rotary bowls in which solid particles or bodies become separated by centrifugal force and simultaneous sifting or filtering
    • B04B3/04—Centrifuges with rotary bowls in which solid particles or bodies become separated by centrifugal force and simultaneous sifting or filtering discharging solid particles from the bowl by a conveying screw coaxial with the bowl axis and rotating relatively to the bowl
    • 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
    • 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
    • B04B9/08—Arrangement or disposition of transmission gearing ; Couplings; Brakes
    • 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

Definitions

  • the invention relates to a centrifuge according to the preamble of claim 1 and a method for monitoring a torque.
  • Decanters are known which are used to process drilling mud.
  • a decanter When processing such a sludge, also called drilling mud, a decanter is usually operated at a lower load than when processing other products.
  • One reason for this is that in the event of a failure due to overloading, a costly disassembly and cleaning of the decanter must take place.
  • DE 10 2006 028 804 A1 discloses a generic centrifuge with a drum and a worm, which are driven by a first motor and preferably a second motor, wherein a gear arrangement is arranged between the motors and the drum and the worm, which has a plurality of gear stages, wherein at four shafts torques are introduced into the first and the second gear stage and wherein a first and a second gear stage are driven at least three shafts.
  • the arrangement is used inter alia. for generating a differential speed between the drum and screw.
  • an unregulated drive is realized in DE 10 2006 028 804 A1, in which a transmission input shaft is held. In this context, the possibility is described to realize a torque overload protection on the fixed shaft.
  • DE 94 09 109 U1 discloses a centrifuge with two combined to a superposition gearbox epicyclic gear stages.
  • an input of the epicyclic gear stages is held and determined at this input a signal in response to the torque at the screw.
  • This signal can be used for monitoring, overload indication and / or attenuation measures
  • the FR 81 1 1 786 discloses a solid bowl screw centrifuge with a torque overload protection device having a lever which is held by intermediate elements on a boom of a transmission input shaft. A lever end is held between two rollers, which are connected via a Doppelgelenkarm with a spring support. The lever, if the centrifuge is in operation, presses against one of the two rollers, which is connected to a connected to a meter. This measuring device determines the force exerted by the lever force and outputs when a predetermined limit value is exceeded, a control command to a control device of the centrifuge, which stops the feed of product into the centrifuge. If the overload is too high, the double articulated arm may buckle, releasing the lever from the rollers. Thus, the transmission input shaft of the centrifuge is no longer fixed or released.
  • the object of the invention is to provide a centrifuge which makes it possible to process the product drilling mud in a particularly suitable manner.
  • the Matterlasthebelarm advantageously serves as a torque arm, which dissolves in the overload case of the transmission input shaft or the rotatably connected part such as an arm or a disc.
  • normal operation means that the torque acting on the overload lever arm is less than a predetermined first limit value, and if this first limit value is exceeded, first of all operating parameters are changed in a suitable manner Limit value for the torque is exceeded, the solid bowl centrifuge is turned off and moves to a safe state.
  • the Matterlasthebelarm is preferably formed as a cylinder / piston assembly, which is designed in particular a fluidic - pneumatic or hydraulic - telescopically resilient or has a mechanical spring element such as a coil spring.
  • the centrifuge has means for determining the instantaneous torque load on the cylinder / piston unit. These means can determine, for example, the change in length of the overload lever arm and / or determines the relative or absolute change in the tilt angle of the piston rod to a starting position. This information can be used to assess which operating state is currently present.
  • Torque with the specification of a first and a second limit the percentage of a case of overload occurring can be surprisingly reduced.
  • FIG. 1 shows a sectional, schematic representation of a solid bowl screw centrifuge
  • Figure 2 is a front view of a solid bowl screw centrifuge;
  • Figure 3 is a detail view of a Uberlasthebels of Fig. 2 and
  • Figures 1 to 3 show a solid bowl screw centrifuge with a rotatable drum 1 with preferably horizontal axis of rotation D and disposed within the drum 1, also rotatable screw 2, which has a centrifuge drive 3 for rotating drum 1 and screw 2.
  • the drum is between see a drive-side and a drive-facing drum bearings 4a, 4b arranged.
  • the centrifuge drive 3 has a motor 5 and a gear arrangement arranged between the motor 5 and the drum 1 and the worm 2.
  • the gear arrangement comprises, for example, a single gear, a so-called planetary gear 6, with three or more gear stages 7, 8, 9, which are connected downstream of the motor 5, wherein in the embodiment chosen here, the first two gear stages 7, 8 and the third gear stage 9 on the two axial sides of the drive-side drum bearing 4a are arranged.
  • Alternative embodiments e.g. with all gear stages 7, 8, 9 inside or outside of the drum bearing 4a (relative to the drum 1) are also feasible.
  • the design of the transmission 6 is such that between the rotational speed of the drum 1 and the speed of the screw 2 during operation, a differential speed is adjustable.
  • the first gear stage 7 and the second gear stage 8 of the gear 6 are each planetary gear-like formed, wherein the first gear stage 7 forms a kind of precursor and the second gear 8 forms a kind of main stage, both of which are arranged in a common housing 12.
  • the first and the second gear stage 7, 8 are designed like a circulating gear, wherein the housing 12 is driven with, which in turn drives the drum 1, which is rotatably connected to the housing 12 preferably via a hollow shaft 13.
  • the first gear stage 7 has a sun gear 14 on a sun gear shaft 15, planet wheels 16 on planetary gear shafts 17, which are combined to form a planet carrier 33, and an outer ring gear 18.
  • the second gear 8 also has - also within the housing 12 - a sun gear 19 on a transmission input shaft 20, also known as sun gear, planetary gears 21 on Planetenradachsen 22 which are combined to form a planet carrier 40, and an outer ring gear 23.
  • the motor 5 drives directly (not shown) or indirectly (via a first belt transmission 24 with a pulley 25 on its motor shaft 26, a belt 27 and a pulley 28, non-rotatably with the housing 12 and the Planetenradachsen 17 of the planet gears 16 of The first gear stage 7 is coupled so that it also forms the planet carrier 33 here), the housing 12 and the planetary gears 16.
  • the pulley 28 may also be integrally formed with the housing 12 or formed on the outer circumference.
  • the first motor 5 directly or indirectly (for example via a second belt drive 29 with a pulley 30 on its motor shaft 26, a belt 31 and a pulley 32) drives the (hollow) shaft 15 for the sun gear 14 of the first gear stage 7th
  • the ring gear 18 is also rotatably coupled via an intermediate piece with a ring gear 23 of the second gear 8 to an intermediate shaft 39 or designed in one piece with this.
  • the Planetenradachsen 22 of the planetary gears 21 of the second gear 12 drive via the Planetenradzan 40 an intermediate shaft 41 to the third gear stage 9, which (as a single or turn multiple output gear stage) drives the screw 2 (indicated only schematically here).
  • the transmission input shaft 20 is set to zero in the present embodiment. This arrangement may also be referred to as zero point drive.
  • the speed of the intermediate shaft 39 is determined by the speed of the sun gear 15 of the sun gear 14 of the first gear 7 and thus is also dependent on the output speed of the (drum) motor 5.
  • Both the sun gear 15 and the housing 1 2 have a different speed from zero, wherein the rotational speed of the housing 12 is fixedly coupled to the rotational speed of the sun gear 15. It is also advantageous that the two first gear stages 7, 8 are arranged within the common (rotatable) housing 12, since this is cost-effective and compact.
  • the first gear 7 forms a kind of precursor, which acts with the second gear stage 8 as a kind of primary primary gear stage.
  • the two first gear stages 7, 8 can also be arranged completely together (possibly with further stages) between the drive-side drum bearing 4a and the drum 1 or be arranged relative to the drum 1 outside the drive-side drum bearing 4a.
  • An advantage of the constructions is to mention that the dependence of the differential speed on the slip and the load state of the decanter is low. By changing the belts or pulleys, the predetermined differential speed range can be easily adjusted.
  • the differential rotational speed can be preselected by replacing the belt pulley of the belt drive, wherein during operation within the ranges by regulating or controlling the engine 5, the differential speed can be varied within the given bandwidths.
  • the transmission input shaft 20 has in FIGS. 1 and 2 a disk 46 at its free end.
  • a Matterlasthebelarm 47 is supported outside the axis of rotation D.
  • This Matterlasthebelarm 47 may be formed in different ways and prevented in its function as a torque arm rotational movement of the transmission input shaft 20.
  • the Kochlasthebelarm 47 in a preferred embodiment as a cylinder / piston unit or as a compression spring with a cylinder housing 49 and a linearly movable piston rod 50th educated.
  • a force is exerted in the manner of a restoring force, in particular a spring force or a pressure by a fluid, such. a gas or a liquid. Acts a force on the piston rod 50, so this moves relative to the cylinder housing 49th
  • the overload lever arm is, for example, a pneumatic cylinder which opposes a restoring force by a gas pressure to the force which transmits the worm via the disc to the pneumatic lever.
  • the Matterlasthebelarm exercises during operation of the centrifuge a restoring force against the rotational direction R of the drum 1 and the screw 2 and holds the transmission input shaft 20 at rest with this force.
  • the force acting on the Matterlasthebelarm by the transmission input shaft measured by a load cell 51, which is set on Studentslasthebelarm 47.
  • the measurement can be carried out in various ways, such as by measuring the change in length of the mutually movable elements of Matterlasthebelarmes or by measuring the angle of the lever arm to the ground or frame to which it is fixed.
  • a pneumatic cylinder gas spring
  • various control commands can be issued.
  • the feed of product into the centrifuge can be throttled or completely stopped.
  • the load cell 51 outputs a signal, which is passed on to a computing unit 52 and is adjusted with a limit value or limit value.
  • the load cell 51 is arranged in the present example in a compact manner directly on Automated Device 47 or integrated into this.
  • the overload lever arm 47 has a receptacle 53, here for example a metal clip, which presses against a coupling means 54, preferably a bolt of the disk 46 and thus keeps the transmission input shaft 20 at a standstill.
  • a coupling means 54 preferably a bolt of the disk 46
  • the force is measured which acts on the overload lever arm and determines the torque therefrom. If the solid bowl screw centrifuge is in normal operation, the drilling mud is clarified. This clarification is carried out by supplying drilling mud into the centrifuge. In the centrifuge field of the centrifuge, the drilling mud is converted into liquid phase and a solid phase, which are removed by various processes from the centrifuge.
  • the overload lever arm remains in its original position, although operating parameters are changed.
  • the inlet is switched off and thus creates a safe state.
  • the piston rod 50 has at its end a receptacle 53 which is rigidly connected to the piston rod 50 or end formed on the piston rod 50.
  • the receptacle may preferably be formed in the form of a groove 58 with a shoulder 59 for guiding the bolt 54.
  • the pin 54 of the disc 46 is located in the groove 58 of the receptacle 53.
  • the disc 46 exerts a force in the direction of rotation R of the drum 2 on the pin 54 during operation of the centrifuge.
  • the disc 46 is decoupled from the Gölasthebelarm 47 and moves in the direction of rotation R.
  • the bolt 54 dissolves during the rotational movement of the coving 58 of the receptacle 53, which for decoupling the disc 46 and the associated screw 2 leads.
  • the Matterlasthebelarm is pivotally mounted about the pivot pin 55 of a tilting joint 61. By decoupling the transmission input shaft 20 is free and rotates with.
  • the present invention has the advantage that only when reaching the third limit, so in case of failure, an emergency stop and thus cleaning the screw and a renewed decoupled Matterlasthebelarms is necessary.
  • the force measurement or the determination of the torque and the matched operating parameters, such as. the drive power of the engine 6 reaches an optimal utilization of the centrifuge.
  • vibrations or resonant vibrations may occur. These can be damped by damping feet 56 and damping plates 57, so that the centrifuge transmits no vibrations to a machine frame 60 or the ground.
  • the operation of the centrifuge may additionally be adjusted and monitored by means for detecting vibrations 62, for example a vibration sensor.

Landscapes

  • Centrifugal Separators (AREA)
  • Earth Drilling (AREA)

Abstract

L'invention concerne une centrifugeuse à vis à bol plein pour traiter des boues de forage, pourvue d'un bol (1) rotatif et d'une vis sans fin (2) rotative, cette centrifugeuse présentant un dispositif d'entraînement qui sert à entraîner le bol et la vis sans fin et qui comprend un moteur d'entraînement et un système de transmission pour créer un différentiel de vitesse de rotation entre le bol (1) et la vis sans fin (2) pendant le fonctionnement de la centrifugeuse. Un arbre d'entrée (20) du système de transmission est fixé de façon solidaire en rotation par un bras de levier de surcharge (47) pouvant être libéré en cas de surcharge de couple, ce bras de levier de surcharge (47) étant relié de manière libérable par une de ses extrémités, à distance radialement par rapport à l'axe de rotation de l'arbre d'entrée, directement à l'arbre d'entrée (20) ou à un élément relié à celui-ci de façon solidaire en rotation. L'invention concerne en outre un procédé pour contrôler le couple.
EP12715967.1A 2011-04-18 2012-04-17 Centrifugeuse et procédé pour contrôler un couple Active EP2699355B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011002126A DE102011002126A1 (de) 2011-04-18 2011-04-18 Zentrifuge und Verfahren zur Überwachung eines Drehmoments
PCT/EP2012/056976 WO2012143342A2 (fr) 2011-04-18 2012-04-17 Centrifugeuse et procédé pour contrôler un couple

Publications (2)

Publication Number Publication Date
EP2699355A2 true EP2699355A2 (fr) 2014-02-26
EP2699355B1 EP2699355B1 (fr) 2020-03-18

Family

ID=45998334

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12715967.1A Active EP2699355B1 (fr) 2011-04-18 2012-04-17 Centrifugeuse et procédé pour contrôler un couple

Country Status (8)

Country Link
US (1) US9855565B2 (fr)
EP (1) EP2699355B1 (fr)
BR (1) BR112013026647B1 (fr)
CA (1) CA2833426C (fr)
DE (1) DE102011002126A1 (fr)
MX (1) MX338692B (fr)
RU (1) RU2581372C2 (fr)
WO (1) WO2012143342A2 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011002126A1 (de) * 2011-04-18 2012-10-18 Gea Mechanical Equipment Gmbh Zentrifuge und Verfahren zur Überwachung eines Drehmoments
CN103801463B (zh) * 2013-12-30 2016-06-29 山东联重机械有限公司 一种卧式筛网沉降离心机
CN105013628A (zh) * 2015-06-25 2015-11-04 王海燕 一种钻井泥浆沙石分离机
USD893741S1 (en) * 2017-08-30 2020-08-18 Gea Mechanical Equipment Gmbh Housing for a centrifuge
RU2756225C1 (ru) * 2020-07-16 2021-09-28 Федеральное государственное бюджетное образовательное учреждение высшего образования "Красноярский государственный аграрный университет" Привод шнековой центрифуги
CN113814073A (zh) * 2021-09-14 2021-12-21 南京中船绿洲机器有限公司 一种卧螺机扭矩检测装置及其控制方法
CN116251682B (zh) * 2023-02-14 2026-03-10 合肥通用机械研究院有限公司 用于长悬臂卧式离心机的偏心称重式进料装置

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US4334647A (en) * 1980-12-03 1982-06-15 Bird Machine Company, Inc. Centrifuges
FR2507798B1 (fr) 1981-06-11 1985-05-31 Robatel Slpi Dispositif limiteur de couple pour machine a cuve tournante et a vis transporteuse interieure
EP0376919B1 (fr) * 1988-12-30 1997-04-09 Flottweg Gmbh Décanteur à élément de construction suspendu élastiquement
DE9409109U1 (de) 1994-06-03 1995-09-28 Flottweg Gmbh, 84137 Vilsbiburg Zentrifuge mit stufenloser Steuerung der Differenzdrehzahl zwischen Trommel und Räumwerkzeug
DE69618989T2 (de) * 1995-12-01 2002-09-26 Baker-Hughes Inc., Houston Verfahren und vorrichtung zum regeln und überwachen einer durchlaufzentrifuge
US8172740B2 (en) * 2002-11-06 2012-05-08 National Oilwell Varco L.P. Controlled centrifuge systems
CN100393423C (zh) * 2003-04-22 2008-06-11 维斯科特尔姆股份公司 带有液力转速差确定的离心机
DE102006028804A1 (de) * 2006-06-23 2007-12-27 Westfalia Separator Ag Schneckenzentrifuge mit Antriebsvorrichtung
DE102009023555A1 (de) * 2009-05-30 2010-12-02 Gea Westfalia Separator Gmbh Verfahren zum Ermitteln des Drehmomentes einer Schnecke eines Dekanters
DE102011002126A1 (de) * 2011-04-18 2012-10-18 Gea Mechanical Equipment Gmbh Zentrifuge und Verfahren zur Überwachung eines Drehmoments
US20140235420A1 (en) * 2014-04-28 2014-08-21 HilFlo, LLC Control system for a decanter centrifuge

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Title
See references of WO2012143342A2 *

Also Published As

Publication number Publication date
BR112013026647A2 (pt) 2016-12-27
MX2013012109A (es) 2014-01-24
US9855565B2 (en) 2018-01-02
US20140315706A1 (en) 2014-10-23
WO2012143342A3 (fr) 2012-12-20
BR112013026647B1 (pt) 2020-10-27
CA2833426A1 (fr) 2012-10-26
EP2699355B1 (fr) 2020-03-18
MX338692B (es) 2016-04-27
CA2833426C (fr) 2019-01-15
RU2013150334A (ru) 2015-05-27
RU2581372C2 (ru) 2016-04-20
WO2012143342A2 (fr) 2012-10-26
DE102011002126A1 (de) 2012-10-18

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