EP2916961B1 - Separator mit direktantrieb - Google Patents

Separator mit direktantrieb Download PDF

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Publication number
EP2916961B1
EP2916961B1 EP13789760.9A EP13789760A EP2916961B1 EP 2916961 B1 EP2916961 B1 EP 2916961B1 EP 13789760 A EP13789760 A EP 13789760A EP 2916961 B1 EP2916961 B1 EP 2916961B1
Authority
EP
European Patent Office
Prior art keywords
separator
lubricant
drive
bearing
stator
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.)
Active
Application number
EP13789760.9A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP2916961A2 (de
Inventor
Jürgen Mackel
Dieter Strauch
Johannes Droste
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
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Application filed by GEA Mechanical Equipment GmbH filed Critical GEA Mechanical Equipment GmbH
Publication of EP2916961A2 publication Critical patent/EP2916961A2/de
Application granted granted Critical
Publication of EP2916961B1 publication Critical patent/EP2916961B1/de
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B15/00—Other accessories for centrifuges
    • B04B15/02—Other accessories for centrifuges for cooling, heating, or heat insulating
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B04—CENTRIFUGAL APPARATUS OR MACHINES FOR CARRYING-OUT PHYSICAL OR CHEMICAL PROCESSES
    • B04B—CENTRIFUGES
    • B04B15/00—Other accessories for centrifuges
    • 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
    • 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

Definitions

  • the invention relates to a separator having the features of the preamble of claim 1.
  • Such separators which are also suitable for industrial use, in particular also in continuous operation, are known per se from the prior art.
  • the power is transmitted from the electric motor to the rotor via a drive belt or by a helical gear.
  • a laboratory centrifuge in which a drive housing is lubricated with a lubricant system and cooled by a coolant system, discloses EP 0 017 344 A1 , However, here the stator is mounted with the rotor as a unit on the drive spindle.
  • the state of the art of laboratory centrifuges is also the DE 39 22 639 A1 called, in which no bearing is provided below the drive motor.
  • the invention has in so far starting from the known prior art, the task of going another way and to realize a separator, which is characterized by a compact design and in particular by low maintenance requirements, as well as an efficient cooling system.
  • the cooling system - a cooling circuit for a cooling fluid, in particular water preferably and completely or partially integrated directly into the drive housing, whereas the electric motor - in particular the stator - has no own built-in liquid cooling per se.
  • the electric motor-in particular the stator as a preassembled structural unit without liquid cooling device-can be designed in a particularly cost-effective manner.
  • there is lubrication with a lubricant in addition to cooling with the coolant, there is lubrication with a lubricant.
  • the lubricant and the coolant are preferably used different liquids.
  • Fig. 1 shows a separator 1 with a centrifugal drum 2 with a vertical axis of rotation D, which is surrounded by a hood assembly 3, which is supported on a machine frame-like drive housing 4.
  • the drive housing 4 can preferably via spring elements, not shown here in sprung execution on a foundation.
  • the centrifugal drum 2 is shown here only schematically. It is preferably designed for continuous operation for the continuous clarification and / or separation of a flowable product into one or two liquid phases and possibly a solid phase, in particular in the industrial process.
  • her interior is preferably provided with a separation plate stack.
  • the Hood assembly 3 is shown only schematically. In particular, it may have a solids catcher and one or more bushings for product feeds and outlets not shown here).
  • the preferably single or double conical centrifugal drum 2 is placed on the vertical upper end of a drive spindle 5 here.
  • This drive spindle 5 is rotatably mounted with a bearing arrangement, which here has a neck bearing 6 and a foot bearing 7.
  • the neck bearing 6 is supported via at least one elastic element radially in a bearing housing 9, which in turn is secured to the drive housing 4.
  • the bearing housing 9 to a flange portion 10 which rests on a first - vertically upper - collar 11 on the inner circumference of the drive housing 4 and secured there, here with circumferentially distributed first screws 12.
  • the elastic element consists here and preferably and in a simple design of two metallic sleeves 8 ', 8 "', which are connected to each other by means of a ring of elastomeric material 8". The outer ring or the outer sleeve 8 'is machined out here, so that it is accurately guided in the housing.
  • the elastic element is fixed here, for example, pressed and thus secured axially and against co-rotation.
  • the inner ring or the inner sleeve 8 '" is machined inside, so that the rolling bearing is guided with its outer ring preferably displaceable.
  • the neck bearing 6 is preferably formed as a rolling bearing, which rests here on a ring 13, which in turn is placed on the spindle 5 and rests there down on a diameter gradation 14 of the spindle 5. In the elastic element, it is guided vertically displaceable and radially supported.
  • the foot bearing 7 is designed as an axial fixed bearing and preferably non-rotatably mounted on the drive spindle 5. It is also articulated on inner ring 18 and outer ring 19, gimbal tiltable but with respect to ring 18 non-rotatably arranged in the drive housing 4 (joint member 15) and / or even formed like a spherical bearing, so that the drive spindle 5 with the drum the precession movements of the centrifugal drum 2 in Operation can follow.
  • the rotation of the foot bearing 7 is achieved here by way of example by a pin 42 which is inserted in each case in an opening of the inner ring 18 and the drive housing.
  • a rolling bearing is preferably used here, which can absorb the resulting axial forces in a suitable manner.
  • Suitable for this example deep groove ball bearings, angular contact ball bearings. If necessary, these bearings can also be arranged in pairs, if required by the male forces.
  • the joint bearing described here takes over the gimbal inclination and support.
  • the entire unit consisting of spherical plain bearings and roller bearings can be replaced with low forces to be absorbed, in particular axial forces by a self-aligning ball bearing or spherical roller bearings.
  • Thetician 7 is here upwards at its inner circumference at a further fürmesserstufung 16 of the drive spindle 5 and downwardly at its outer periphery on a gradation 17 of an outer circumference spherical segment-like inner ring 18, which in turn engages in a correspondingly complementarily shaped outer ring 19 hinged which rests on a gradation 41 of the drive housing 4.
  • This arrangement is compact and allows a simple and reliable way to support the weight of the centrifugal drum 2 via the foot bearing on the drive housing. 4
  • an electric motor 20 with a rotor 21 and a stator 22 is arranged as a drive device. This is completely between the neck bearing 6 and the demandinglager. 7
  • the rotor 21 is arranged and fixed directly on the drive spindle.
  • the rotor 21 and the rotatable drive spindle 5 move fixed coupled together, in particular in precession movements of the drive spindle 5 during operation.
  • the drive spindle 5 can here at its periphery a suitable contouring - e.g. Stages - for fixing or arranging the rotor 21 have.
  • the stator 22 is firmly connected to the drive housing 4. This changes the radial gap width between the stator 22 and the rotor 21 during operation as a result of the movements of the drive spindle 5.
  • the drive spindle 5 also carries out its precession movement between the neck bearing 6 and the foot bearing 7 (as a fixed bearing) as a result of the gyro laws, this is limited in this area (stop), so that with the help of a corresponding air gap between the stator 22 and the Motor rotor 21 can be ensured that the rotor 21 and the stator 22 do not touch during operation in spite of radial relative movement.
  • Such relative movements may be e.g. imbalances, especially in the range of the resonant frequency of the system during startup of the drum, or for example by movements of the entire machine due to wave influence when used on board ships and possibly have their greatest deflections.
  • the bearing formed in the pivot bearing 7 (which essentially takes over the axial support of the centrifugal drum 2) and the elastically supported neck bearing 6 advantageously allows a supercritical operation of the motor rotor 21 with respect to the resonance frequency and the centrifugal drum 2.
  • the mass properties of the motor rotor 21 are so small that they do not adversely affect the dynamic behavior of the drive system.
  • the separator drum together with the spindle and neck support, approximates a one-shot oscillator excited by the rotating drum and, in particular, by the co-rotating unbalance.
  • the elastic neck support significantly reduces its natural frequency compared to nearly rigid constructions.
  • the critical speed (or frequency) is that speed at which the forces caused by the rotating drum and co-rotating imbalance cause the machine to resonate. (The excitation frequency (drum speed) is here equal to the natural frequency of the system.) Above this frequency (speed) stabilizes the system, since unbalance and rotor gravity are here on opposite sides of the actual axis of rotation.
  • separators are operated at their operating speed well above the critical speed (resonant frequency), so that even a major imbalance without adverse effects of the machine is endured.
  • suitable fastening means here one or more (circumferentially distributed) screws 27, is provided.
  • stator can be prefabricated in a simple manner as a preassembled unit with the radially outer sleeve body 24 in the drive housing can be attached.
  • Fig. 1 and 2 are largely identical and differ essentially only by the axial length of the electric motors 20 and 20 '.
  • the axial length of the electric motor 20, 20 ' can vary within a considerable range, which advantageously makes it possible to use identical drive housings 4 for electric motors 20, 20' of different length and power.
  • FIG. 1 A comparison of Fig. 1 and 2 makes it clear that with differently long stators 22, the sleeve body 24 used as the interface of the stator 22 to the drive housing 4 still has the same vertical length. Preferably, even an identical sleeve body 24 is used despite a different vertical length.
  • the electric motor may be an asynchronous motor or a synchronous motor.
  • the drive chamber 28 is designed to be upwardly (except for an annular gap 29 to the drive spindle 5 above the neck bearing 6) and downwardly and laterally largely closed.
  • a labyrinth seal or a shaft seal of known design can be used in addition to the annular gap (not shown here).
  • stator 22 and the rotor or motor rotor 21 are arranged open in the drive space 28 between the neck bearing 6 and the foot bearing 7.
  • the drive spindle 5 is hollow or has an inner centric lubricant line or bore 30 which extends axially from an area below the contemplatlagers 7 through the region of the motor rotor 21 of the electric motor 20 into the region of the neck bearing 6, where the lubricant line 30 preferably via a radial Schmierstoffzu GmbHbohrung 31 opens into the drive chamber 28, in such a way that with the exiting from this bore 31 lubricant lubrication of the neck bearing 6 can take place.
  • the lubricant supply bore 31 therefore preferably discharges above the neck bearing 6 into the drive space. Alternatively, it could also open just below the neck bearing 6 in the drive chamber 28, if this ensures sufficient lubrication of the neck bearing 6.
  • a lubricant pump (in particular a suction-pipe pump or a centrifugal pump, here realized with a rib arrangement 32 on the inner circumference of the axial lower end of the lubricant bore 31) is integrated in the lower (preferably open) spindle end.
  • the fin arrangement together with the dimensioning of the inlet diameter to a particularly precise oil quantity control (setting) and can optionally be adapted to the lubricant or the operating conditions such as the site (ambient temperature) and designed to be interchangeable.
  • stator 22 Preferably, outside of the stator 22 one or more in particular vertically extending bores or the like.
  • the foot bearing 7 can be located completely below the lubricant level in the lubricant sump 33 or can be arranged completely in the lubricant bath.
  • the winding head temperature is usually very high.
  • these winding heads are quite far away from the bearings, which is an advantage over the prior art.
  • the foot bearing 7 is here in the oil sump, it can also be kept very cool.
  • the neck bearing 6 is lubricated with flowing lubricant, it is also better cooled than in an oil mist lubrication, as known in the art.
  • the lubricant can flow back through further channels / bores 35 into a region of the drive space 28 lying below the foot bearing 7, to enter the line 30 can.
  • a drain plug 39 allows for draining / changing the lubricant.
  • the lubricant level is preferably just below the electric motor 20 without having this contact.
  • the heat output resulting from the losses of the electric motor can be emitted on the one hand over the surface of the drive housing or a correspondingly designed surface enlargement (for example cooling fins on the outer surface of the drive housing 4 over the entire axial length between the neck bearing and the foot bearing 7 in a correspondingly large configuration).
  • a correspondingly designed surface enlargement for example cooling fins on the outer surface of the drive housing 4 over the entire axial length between the neck bearing and the foot bearing 7 in a correspondingly large configuration.
  • This cooling medium preferably and particularly advantageously cools both the lubricant and the electric motor (in particular the stator 20).
  • Other components such as a coolant pump and possibly a filter to complete the coolant circuit are not shown here, since they are known per se.
  • the lubricant flowing through the lubricant passage 34 is cooled.
  • the stator 20 is cooled particularly effectively. For clarity's sake Fig. 2 directed.
  • the actual electric motor limits here with the sleeve body 24 and the cooling chamber, here the annular chamber 37. But he does not have his own cooling system. This simplifies its installation and also the change, which is also particularly cost-effective by this measure.
  • the stator 22 of the electric motor 20 itself can be provided and changed in a particularly simple manner as a prefabricated module. It would also be conceivable to limit the annular chamber with an additional sleeve inside, but this is less preferred.
  • the cooling circuit in an area, for example in the region of the chamber, in particular the annular chamber 37, adjacent both to the stator 22 - here the sleeve body 24 - as well as close to the at least one of the holes of the lubricant channel, which the lubricant as a liquid-flowing lubricant Passing the electric motor down into the lubricant sump, a double cooling is achieved in a simple manner.
  • one or more seals 40 can advantageously be arranged on the inner circumference of the sleeve body in order to seal the gap between the sleeve body 24 and the collar section 26 (or the cooling chamber).
  • the sleeve body 24 thus forms in a structurally particularly simple manner one of the walls of the annular chamber 37.
  • Sight glasses 43 in the outer wall allow a visual inspection of the lubrication system, in particular, since one of the sight glasses 43 is vertically at the level of the maximum lubricant level, so that the lubricant level can be monitored, with a second (here upper) sight glass 43 the view in allows the lubricant channel 34 and thus the oil return

Landscapes

  • Motor Or Generator Frames (AREA)
  • Centrifugal Separators (AREA)
EP13789760.9A 2012-11-12 2013-11-06 Separator mit direktantrieb Active EP2916961B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012110846.3A DE102012110846A1 (de) 2012-11-12 2012-11-12 Separator mit Direktantrieb
PCT/EP2013/073117 WO2014072318A2 (de) 2012-11-12 2013-11-06 Separator mit direktantrieb

Publications (2)

Publication Number Publication Date
EP2916961A2 EP2916961A2 (de) 2015-09-16
EP2916961B1 true EP2916961B1 (de) 2019-10-09

Family

ID=49582728

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13789760.9A Active EP2916961B1 (de) 2012-11-12 2013-11-06 Separator mit direktantrieb

Country Status (12)

Country Link
US (1) US9981275B2 (enrdf_load_stackoverflow)
EP (1) EP2916961B1 (enrdf_load_stackoverflow)
JP (1) JP2016505352A (enrdf_load_stackoverflow)
KR (1) KR20150084034A (enrdf_load_stackoverflow)
CN (1) CN104797343A (enrdf_load_stackoverflow)
AU (1) AU2013343679B2 (enrdf_load_stackoverflow)
BR (1) BR112015010479B1 (enrdf_load_stackoverflow)
CA (1) CA2889766C (enrdf_load_stackoverflow)
DE (1) DE102012110846A1 (enrdf_load_stackoverflow)
RU (1) RU2015121635A (enrdf_load_stackoverflow)
SG (1) SG11201503572QA (enrdf_load_stackoverflow)
WO (1) WO2014072318A2 (enrdf_load_stackoverflow)

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SE533089C2 (sv) * 2008-05-13 2010-06-22 Alfa Laval Corp Ab Centrifugalseparator
SE532905C2 (sv) 2008-09-22 2010-05-04 Alfa Laval Corp Ab Centrifugalseparator
DE102013100180B4 (de) * 2012-03-26 2025-05-15 Gea Mechanical Equipment Gmbh Separatoranordnung
DE102012110846A1 (de) * 2012-11-12 2014-05-15 Gea Mechanical Equipment Gmbh Separator mit Direktantrieb
EP3075455B1 (en) * 2015-03-31 2017-12-06 Alfa Laval Corporate AB Cooling or heating of bearings in a centrifugal separator
DE102015108741A1 (de) * 2015-06-02 2016-12-08 Gea Mechanical Equipment Gmbh Separator
CN105057120A (zh) * 2015-09-11 2015-11-18 戴杰 一种转鼓下支承装置
DE102017114649A1 (de) 2017-06-30 2019-01-03 Gea Mechanical Equipment Gmbh Separator mit Direktantrieb
DE102017215784A1 (de) * 2017-09-07 2019-03-07 Zf Friedrichshafen Ag Getriebe für ein Kraftfahrzeug
EP3878559A1 (en) * 2020-03-12 2021-09-15 Alfa Laval Corporate AB A centrifugal separator
CN112564382B (zh) * 2020-12-09 2025-01-07 张志刚 一种纺杯电机及其安装方法
DE102022117310A1 (de) * 2022-07-12 2024-01-18 Gea Westfalia Separator Group Gmbh Verfahren zur Überwachung und Regelung der Kühlmitteltemperatur einer Antriebvorrichtung eines Separators
DE102023105408A1 (de) 2023-03-06 2024-09-12 Gea Westfalia Separator Group Gmbh Zentrifuge

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DE102009022972A1 (de) * 2009-05-28 2010-12-02 Gea Westfalia Separator Gmbh Zentrifuge mit einem Schmiermittelsystem
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DE102013100180B4 (de) * 2012-03-26 2025-05-15 Gea Mechanical Equipment Gmbh Separatoranordnung
DE102012110846A1 (de) * 2012-11-12 2014-05-15 Gea Mechanical Equipment Gmbh Separator mit Direktantrieb

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4322030A (en) 1979-03-14 1982-03-30 Beckman Instruments, Inc. Lubrication and cooling system for a high speed ultracentrifuge drive assembly
US4946433A (en) 1988-07-18 1990-08-07 Gorodissky Boris P Centrifuge drive
US5848959A (en) 1994-03-11 1998-12-15 Westfalia Separator Aktiengesellschaft Lubicated vertical transmission shaft for driving a centrifugal drum
US6527085B1 (en) 2000-11-14 2003-03-04 Tecumseh Products Company Lubricating system for compressor
US20050065010A1 (en) 2002-03-22 2005-03-24 Reinhard Moss Separator
WO2004089550A1 (en) 2003-04-08 2004-10-21 Alfa Laval Corporate Ab A driving device for a centrifugal separator
WO2011101222A1 (de) 2010-02-19 2011-08-25 Magna Powertrain Ag & Co Kg Elektrische antriebseinheit

Also Published As

Publication number Publication date
SG11201503572QA (en) 2015-06-29
RU2015121635A (ru) 2017-01-10
AU2013343679B2 (en) 2018-04-19
WO2014072318A2 (de) 2014-05-15
CA2889766A1 (en) 2014-05-15
KR20150084034A (ko) 2015-07-21
JP2016505352A (ja) 2016-02-25
DE102012110846A1 (de) 2014-05-15
US9981275B2 (en) 2018-05-29
BR112015010479B1 (pt) 2021-08-31
CN104797343A (zh) 2015-07-22
WO2014072318A3 (de) 2014-09-18
US20150283561A1 (en) 2015-10-08
BR112015010479A2 (pt) 2017-07-11
EP2916961A2 (de) 2015-09-16
CA2889766C (en) 2020-06-02
AU2013343679A1 (en) 2015-05-21

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