EP2279351A1 - Machine à énergie fluidique - Google Patents

Machine à énergie fluidique

Info

Publication number
EP2279351A1
EP2279351A1 EP09738169A EP09738169A EP2279351A1 EP 2279351 A1 EP2279351 A1 EP 2279351A1 EP 09738169 A EP09738169 A EP 09738169A EP 09738169 A EP09738169 A EP 09738169A EP 2279351 A1 EP2279351 A1 EP 2279351A1
Authority
EP
European Patent Office
Prior art keywords
bearing
machine
fluid energy
rotor
radial
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Withdrawn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
EP09738169A
Other languages
German (de)
English (en)
Inventor
Theo Nijhuis
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Publication of EP2279351A1 publication Critical patent/EP2279351A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/08—Structural association with bearings
    • H02K7/09—Structural association with bearings with magnetic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D25/0686—Units comprising pumps and their driving means the pump being electrically driven specially adapted for submerged use
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/057—Bearings hydrostatic; hydrodynamic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/058—Bearings magnetic; electromagnetic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/05—Shafts or bearings, or assemblies thereof, specially adapted for elastic fluid pumps
    • F04D29/056—Bearings
    • F04D29/059—Roller bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C32/00—Bearings not otherwise provided for
    • F16C32/04—Bearings not otherwise provided for using magnetic or electric supporting means
    • F16C32/0406—Magnetic bearings
    • F16C32/044—Active magnetic bearings
    • F16C32/0442—Active magnetic bearings with devices affected by abnormal, undesired or non-standard conditions such as shock-load, power outage, start-up or touchdown
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C39/00—Relieving load on bearings
    • F16C39/02—Relieving load on bearings using mechanical means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2240/00—Components
    • F05D2240/50—Bearings
    • F05D2240/51—Magnetic
    • F05D2240/515—Electromagnetic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps
    • F16C2360/44—Centrifugal pumps
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/14—Structural association with mechanical loads, e.g. with hand-held machine tools or fans

Definitions

  • the invention relates to a fluid energy machine for increasing the pressure of a process fluid, in particular a pump or a compressor, with a flow machine that increases the pressure of the process fluid, with a drive that drives the Stromungsmaschine, the Stromungsmaschine has a rotor, the rotating Stromungsleitiata the Stromungsmaschine carries, with at least one thrust bearing, which is designed as a magnetic bearing and by means of which the rotor is mounted, with at least two radial bearings, a first radial bearing and a second radial bearing, as
  • Magnetic bearings are formed and by means of which the rotor is mounted and between which the flow machine is arranged.
  • a special field of application for such machines is the compression of natural gas, which is no longer required by means of a platform from maritime occurrences, but is compressed directly undersea at the seabed and is preferably directed by means of a pipeline to a land station.
  • This application is of particular economic attractiveness, since conventional platforms can be saved, and accordingly their immense operating costs.
  • Process medium and the surrounding medium and not take place between other working fluids and the surrounding medium.
  • a particular challenge is the storage of a rotor of such a Fluidenergymaschme, which preferably should not need working fluid, since any treatment or replacement with a land station were too expensive.
  • the invention has for its object to provide a Fluidenergymaschme of the type mentioned, which is equipped with a storage, with low maintenance and special high availability even at high dynamic stress reliable operation at the same time
  • auxiliary bearings according to the invention has the particular advantage that for the exclusively radial bearing a robust sliding bearing is selected, which can be selected in the support surface such that only a lower surface load arises.
  • a radial bearing clearance of preferably 25/100 mm to 3/10 mm, the machine is sufficiently dirt-resistant and the rotor remains at the location of the auxiliary bearing enough space for the resulting vibrations during operation or that the auxiliary bearing is taken.
  • the rolling bearing is able to absorb axial forces as well as the resulting radial forces, so that a more compact machine results at this point for the more complex bearing task.
  • the inner diameter of the rolling bearing is preferred to the rotor with a radial clearance of about 25/100 mm up to
  • roller bearing For nondestructive absorption of the resulting bearing loads even with savings of any lubricant, it is expedient to form the roller bearing as a ball bearing that is able to accommodate both the axial and the radial bearing loads.
  • a preferred embodiment of the plain bearing provides that this is made of steel and is therefore not damaged, in particular by the exposure to the chemically aggressive media.
  • the slide bearing is not damaged in case of emergency stop or trip the machine by example, high vibrations, it is expedient to the sliding surface of the Sliding bearing segmented form and resiliently store the individual segments.
  • the drive of the Fluidenergymaschme is preferably designed as an electric motor, so that in particular a
  • such an electric motor is located on a shaft with the flow machine and forms together with this a single rotor.
  • Such an arrangement is particularly compact.
  • This arrangement also has a positive effect on the dimensioning of the radial auxiliary bearing, which even with an outlet of, for example, 12,000 revolutions per
  • the vertical arrangement unfolds particular advantages when a radial bearing and the axial bearing at the upper end of the rotor and a radial bearing at the lower end of the rotor is arranged and at the same time designed as a slide bearing auxiliary bearing at the lower end of the rotor and trained as a rolling bearing auxiliary bearing on Upper end of the rotor is provided.
  • the slide bearing located at the bottom is exposed to a greater dirt load than the rolling bearing located at the top, the slide bearing being better suited for these adverse operating conditions.
  • auxiliary bearings are preferably arranged further out on the rotor than the radial bearings designed as magnetic bearings and the axial bearing. This in particular because this results in a better rotor dynamics, in particular results in better vibration in normal operation.
  • the previously described bearing concept if no additional radial bearing is provided between the engine and the Stromungsmaschine or the engine and the flow machine are located between the two radial bearings.
  • An alternative storage results when both the flow machine and the engine each have two own radial bearings and the rotor between the two located between the engine and the engine radial bearings has a limp area, which essentially transmits the torsional moments (also referred to as Quillschaft ).
  • the Fluidenergymaschme comprises a control unit which communicates with at least one axial and / or radial position and / or vibration measuring point on the rotor and / or a current and / or voltage measuring point on at least one magnetic bearing and is configured such that at least one measured value of the measuring point, which differs from the normal operation by a certain amount, the power supply to the motor changed such that the engine decelerates the rotor.
  • the braking effect can be caused by eddy currents or by a magnetic field counteracting the current rotation. In this way, it is possible to brake a rotor weighing several tons from a speed of about 12,000 revolutions per minute to standstill within less than 10 seconds.
  • FIG. 1 shows a schematic representation of a
  • the figure shows a fluid energy machine 1 according to the invention with a flow machine 2 and a drive 3, which is designed as an electric motor 4.
  • the drive 3 and the flow machine 2 have a common rotor 5 and a common shaft 6, which rotates about a vertical axis of rotation 7.
  • the shaft 6 carries in the region of the flow machine 2 Stromungsleiticide 8, as
  • Laufrader a centrifugal compressor are formed.
  • a lower first radial bearing 11 and an upper, second radial bearing 12 and a thrust bearing 13 also arranged at the top are provided.
  • the two radial bearings 11, 12 and the thrust bearing 13 are encapsulated magnetic bearings.
  • auxiliary bearings 15, 16 which are respectively positioned in the further outward region relative to the magnetic bearings 11, 12, 13 on the shaft 6.
  • first auxiliary bearing 15 for radial support
  • second auxiliary bearing 16 for radial and axial support. Accordingly, the bearing distance of the auxiliary bearings 15, 16 is greater than that of the magnetic bearings 11, 12, 13.
  • the arranged on the vertical shaft 6 below the first auxiliary bearing 15 is designed as a plain bearing with a radial wave play of about 25/100 mm, so that in Normal operation, the rotor 5 can rotate freely in the plain bearing without any contact.
  • the same bearing clearance has the second auxiliary bearing 16 located at the upper end of the vertical shaft 6, which is designed as a rolling bearing 22 or ball bearing.
  • the rolling bearing 22 has radial 25/100 mm game.
  • Axial is a sum game of about 5/10 mm to 6/10 mm provided.
  • the bearings 15, 16, 21, 11, 12, 13, 22, the flow machine 2 and the drive 3 are located in a gas-tight housing 30 which has an inlet 31 and an outlet 32 for process fluid 33 to be compressed.
  • the magnetic bearings 11, 12, 13, the first auxiliary bearing 15 and a gap between the stator 36 and the rotating member 37 of the electric motor 4 are cooled by means of the process fluid 33, which consists of an overflow line 40 between a first stage 41 and a second stage 42 of taken as a compressor 45 running machine 2 is taken. From this tap 46, the process fluid 33 is supplied to the bearings 15, 11, 12, 13 and the gap 38, wherein it then again enters the first stage 41 of the compressor 45.
  • the stator 36 still has its own cooling circuit 55.
  • a control to the control unit CU supplies the radial bearings 11, 12 and the thrust bearing 13 each with an operating current IB and the drive 3 with an operating current IM.
  • the axial shaft position X is detected by means of a sensor 61 and the vibration amount Y by means of a sensor 62 and evaluated in the crizungsemheit CU. If the axial position X has an excessive deviation from the normal value or the vibration amplitude Y exceeds specified limit values, the machine is stopped
  • the control unit CU modulates the current to the motor IM in such a way that the rotation of the rotor 5 is braked. In this way, the rotor 5 can be brought to a standstill of a speed of 12,000 revolutions per minute in about 10 seconds. If one or more magnetic bearings 11, 12, 13 have failed, take over the auxiliary bearing 15 storage Although the auxiliary bearings 15 have no lubrication or no separate supply of a lubricant, they can take over the bearing task without damage during the short time of the trip.
  • the lower mounted auxiliary bearing or plain bearing 21 is particularly insensitive to contamination with a radial bearing clearance of 25/100 mm, so that a function is guaranteed despite the settling by gravity dirt particles in the lower machine area.
  • Roller bearing 22 combines the radial bearing with the axial bearing and is exposed due to the arrangement at the upper end of the shaft 6 a less severe contamination.
  • the plain bearing 21 know resilient segments 27 which are designed resilient so that it does not come to a destruction of the steel treads of the bearing at too high a bearing load.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Power Engineering (AREA)
  • Electromagnetism (AREA)
  • Fluid Mechanics (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

L'invention concerne une machine à énergie fluidique (1), en particulier un compresseur (45) qui possède un rotor commun (5) supporté par des paliers magnétiques (11, 12, 13) pour la turbomachine (2) et pour l'entraînement (3). En plus des paliers magnétiques (11, 12, 13), il est prévu des paliers auxiliaires (15), un palier lisse (21) étant prévu à l'extrémité inférieure du rotor (5) orienté verticalement, et un palier à roulements (22) prenant la forme d'un roulement à billes, à l'extrémité supérieure, qui assure un positionnement radial aussi bien qu'axial.
EP09738169A 2008-04-29 2009-04-29 Machine à énergie fluidique Withdrawn EP2279351A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008021363 2008-04-29
DE102008031994A DE102008031994B4 (de) 2008-04-29 2008-07-07 Fluidenergiemaschine
PCT/EP2009/055168 WO2009133125A1 (fr) 2008-04-29 2009-04-29 Machine à énergie fluidique

Publications (1)

Publication Number Publication Date
EP2279351A1 true EP2279351A1 (fr) 2011-02-02

Family

ID=41131058

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09738169A Withdrawn EP2279351A1 (fr) 2008-04-29 2009-04-29 Machine à énergie fluidique

Country Status (7)

Country Link
US (1) US8579608B2 (fr)
EP (1) EP2279351A1 (fr)
CN (1) CN102016322B (fr)
BR (1) BRPI0911583A2 (fr)
DE (1) DE102008031994B4 (fr)
RU (1) RU2449178C1 (fr)
WO (1) WO2009133125A1 (fr)

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DE102008038787A1 (de) * 2008-08-13 2010-02-18 Siemens Aktiengesellschaft Fluidenergiemaschine
IT1404158B1 (it) * 2010-12-30 2013-11-15 Nuova Pignone S R L Condotto per turbomacchina e metodo
WO2013109235A2 (fr) 2010-12-30 2013-07-25 Dresser-Rand Company Procédé de détection en ligne de défauts de résistance à la masse dans des systèmes de palier magnétique actif
US8994237B2 (en) 2010-12-30 2015-03-31 Dresser-Rand Company Method for on-line detection of liquid and potential for the occurrence of resistance to ground faults in active magnetic bearing systems
NO333684B1 (no) * 2011-03-07 2013-08-12 Aker Subsea As Undervanns trykkøkningsmaskin
US9551349B2 (en) 2011-04-08 2017-01-24 Dresser-Rand Company Circulating dielectric oil cooling system for canned bearings and canned electronics
WO2012158266A2 (fr) * 2011-05-17 2012-11-22 Dresser-Rand Company Douille de décélération en roue libre pour systèmes de paliers magnétiques
ITCO20110020A1 (it) * 2011-05-25 2012-11-26 Nuovo Pignone Spa Metodi e sistemi per condotti a bassa tensione privi di olio
US8876389B2 (en) 2011-05-27 2014-11-04 Dresser-Rand Company Segmented coast-down bearing for magnetic bearing systems
US8851756B2 (en) 2011-06-29 2014-10-07 Dresser-Rand Company Whirl inhibiting coast-down bearing for magnetic bearing systems
JP5240336B2 (ja) * 2011-09-26 2013-07-17 ダイキン工業株式会社 磁気軸受及びそれを用いた圧縮機
DE102012207019B4 (de) * 2012-04-27 2015-12-24 Siemens Aktiengesellschaft Strömungsmaschine sowie Verfahren zur Kühlen einer solchen
EP2677177B1 (fr) * 2012-06-22 2020-10-14 Skf Magnetic Mechatronics Compresseur centrifuge électrique pour véhicules
JP6155573B2 (ja) 2012-08-28 2017-07-05 株式会社Ihi 遠心圧縮機
WO2014182646A1 (fr) * 2013-05-09 2014-11-13 Dresser-Rand Company Dispositif de protection de palier magnétique
EP2899416A1 (fr) 2014-01-22 2015-07-29 Siemens Aktiengesellschaft Machine électrique dotée d'un système d'aimants
ITUB20152564A1 (it) * 2015-07-28 2017-01-28 Nuovo Pignone Tecnologie Srl Motocompressore e metodo per migliorare l’efficienza di un motocompressore
JP6672056B2 (ja) * 2016-04-22 2020-03-25 三菱重工サーマルシステムズ株式会社 ターボ圧縮機、これを備えたターボ冷凍装置
NO347975B1 (en) * 2016-09-20 2024-06-03 Vetco Gray Scandinavia As Improved arrangement for pressurizing of fluid
DE102017205055A1 (de) * 2017-03-24 2018-09-27 Siemens Aktiengesellschaft Verfahren zur Axialschubregelung eines Rotors einer Strömungsmaschine
IT201700067928A1 (it) * 2017-06-19 2018-12-19 Nuovo Pignone Tecnologie Srl Sistema di controllo per turbomacchina per aree pericolose
DE102018108827B3 (de) * 2018-04-13 2019-05-29 Trumpf Schweiz Ag Verfahren zur Steuerung von zumindest einem Radialgebläse in einer Kälteanlage sowie Radialgebläse
JP7265377B2 (ja) * 2019-03-04 2023-04-26 東芝ライフスタイル株式会社 電動送風機及び電気掃除機
CN110645268B (zh) * 2019-08-20 2020-09-15 江苏理工学院 一种滑块消除间隙保护轴承装置
FR3112172B1 (fr) * 2020-11-30 2023-03-17 Pfeiffer Vacuum Pompe à vide sèche
CN115355181B (zh) * 2022-10-18 2023-01-13 成都凯磁科技有限公司 用于地下资源型气体开采的井下气体压缩系统

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EP0361844A2 (fr) * 1988-09-30 1990-04-04 Nova Corporation Of Alberta Compresseur à gaz ayant des garnitures sèches
US5501583A (en) * 1992-08-19 1996-03-26 Hitachi, Ltd. Turbo vacuum pump
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Title
See also references of WO2009133125A1 *

Also Published As

Publication number Publication date
RU2449178C1 (ru) 2012-04-27
DE102008031994A1 (de) 2009-11-05
CN102016322B (zh) 2015-09-09
WO2009133125A1 (fr) 2009-11-05
DE102008031994B4 (de) 2011-07-07
CN102016322A (zh) 2011-04-13
BRPI0911583A2 (pt) 2016-01-05
US20110044832A1 (en) 2011-02-24
US8579608B2 (en) 2013-11-12

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