US20110150628A1 - Fluid energy machine - Google Patents

Fluid energy machine Download PDF

Info

Publication number
US20110150628A1
US20110150628A1 US13/058,602 US200913058602A US2011150628A1 US 20110150628 A1 US20110150628 A1 US 20110150628A1 US 200913058602 A US200913058602 A US 200913058602A US 2011150628 A1 US2011150628 A1 US 2011150628A1
Authority
US
United States
Prior art keywords
motor
energy machine
fluid energy
rotor
shaft
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.)
Abandoned
Application number
US13/058,602
Other languages
English (en)
Inventor
Norbert Wagner
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
Assigned to SIEMENS AKTIENGESELLSCHAFT reassignment SIEMENS AKTIENGESELLSCHAFT ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WAGNER, NORBERT
Publication of US20110150628A1 publication Critical patent/US20110150628A1/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F04D13/0633—Details of the 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
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/0606—Canned motor pumps
    • F04D13/064—Details of the magnetic circuit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/06—Units comprising pumps and their driving means the pump being electrically driven
    • F04D13/08—Units comprising pumps and their driving means the pump being electrically driven for submerged use
    • F04D13/086—Units comprising pumps and their driving means the pump being electrically driven for submerged use the pump and drive motor are both submerged
    • 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
    • F04D29/04—Shafts or bearings, or assemblies thereof
    • F04D29/046—Bearings
    • F04D29/048—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
    • F04D29/058—Bearings magnetic; 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
    • 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
    • F16C32/0474—Active magnetic bearings for rotary movement
    • F16C32/0493—Active magnetic bearings for rotary movement integrated in an electrodynamic machine, e.g. self-bearing motor
    • F16C32/0497—Active magnetic bearings for rotary movement integrated in an electrodynamic machine, e.g. self-bearing motor generating torque and radial force
    • 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
    • F16C37/00—Cooling of bearings
    • F16C37/005—Cooling of bearings of 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
    • F16C39/00—Relieving load on bearings
    • F16C39/06—Relieving load on bearings using magnetic means
    • 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
    • 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
    • F16C32/0474—Active magnetic bearings for rotary movement
    • F16C32/0489—Active magnetic bearings for rotary movement with active support of five degrees of freedom, e.g. two radial magnetic bearings combined with an axial bearing

Definitions

  • the invention relates to a fluid energy machine, in particular a compressor or pump, having a housing, a motor, at least one impeller, at least two radial bearings, at least one shaft which extends along a shaft longitudinal axis and supports the at least one impeller and a rotor of the motor, wherein the shaft is borne in the radial bearings, wherein the motor has a stator which at least partially surrounds the rotor in the area of the motor, and a gap which extends in the circumferential direction and along the shaft longitudinal axis and is at least partially filled with a fluid is formed between the rotor and the stator, as well as between the rotor and the radial bearings.
  • Fluid energy machines such as these are the object of particularly intensive research efforts at the moment, because they offer the capability to be embodied without seals.
  • the motor which is generally in the form of an electrical drive
  • the impeller of the fluid energy machine for example a compressor impeller
  • without any seals means that no shaft seal has to seal a gap between a moving component and a stationary component from the environment. Nevertheless, some seals are required, for example in the area of the impellers, and are normally in the form of labyrinth seals.
  • the rotor and the stator of the motor are surrounded by the process fluid since, preferably, no shaft seal is also provided between the compressor and the motor in the housing.
  • the process fluid is correspondingly located in the gaps between the rotor and the stationary components—that is to say between the stator of the motor and the rotor, in the bearings and in the back-up bearings.
  • the rotor or the split cage is excited to oscillate, with the oscillation changing the gap height in one of the circumferential gaps at a circumferential position, and if the fluid has a significant circumferential velocity in the gap between the rotor and the split cage, then the local reduction in the gap height results in acceleration in the resultant Couette flow which, in accordance with Bernoulli's flow law, leads to a local pressure reduction, as a result of which the forces which reduce the gap height are increased in addition to the stimulated reduction of the gap height.
  • These aerodynamic or hydrodynamic forces increase as the fluid density increases and, if sufficiently pronounced, can lead to a contact between rotating and stationary parts, even resulting in damage. It is essential to prevent a reduction such as this in the availability of the fluid energy machine.
  • a split-cage motor which has at least one motor without any bearings and drives a pump impeller arranged at the side is known from WO 97/08808.
  • the arrangement proposed there is suitable only for operation of small fluid energy machines, since the impeller, which is in each case arranged at a free shaft end, has a restricted size and mass, from the rotor-dynamic point of view.
  • a multistage embodiment is not feasible in the described manner. Hydrodynamic instability in the gap flow is not discussed.
  • the object of the invention is to provide a fluid energy machine of the type mentioned initially, which has particularly high availability, in particular with the aim of improving the operational reliability of a large fluid engine machine.
  • an impeller should be understood as meaning a rotating component which feeds a process fluid depending on the purpose of the machine, or is driven thereby.
  • this could be an impeller of a compressor.
  • a plurality of centrifugal impellers may be arranged in-line or back-to-back in a centrifugal compressor.
  • a gas-tight housing for the purposes of the invention should be understood as meaning that there is no need to provide a shaft seal in order to pass the shaft out of the housing.
  • At least one axial bearing is provided for defined bearing of the shaft in an axial position.
  • This axial bearing is preferably in the form of a magnetic bearing, in the same way as the at least two separate radial bearings.
  • the process fluid may be natural gas, which is compressed under water and, in addition to the chemically aggressive nature, also results in the difficulties of a widely fluctuating pressure and coarse impurities.
  • a so-called split cage can be provided in the gap between the rotor and the stator, which separates an area in which the process fluid flows around the rotor from an area in which the interior of the stator is arranged.
  • stator is advantageously kept at a suitable operating temperature by a separate cooling system by means of a cooling fluid, with the rest of the components of the machine preferably being cooled by means of the process fluid.
  • bearings which are preferably in the form of magnetic bearings, can be cooled by means of the process fluid.
  • the split cage is subject to particular requirements. In order to prevent it from being excessively heated, because of eddy currents being induced in the alternating magnetic fields of the stator, it should be electrically non-conductive. In addition, it must be sufficiently mechanically robust, since high pressure differences can occur between the process fluid and the stator cooling fluid, which is generally separated from the process fluid by means of the split cage. For acceptable efficiency, the wall thickness of the split cage must not be excessively thick. Furthermore, the split cage must be chemically resistant to the process fluid.
  • components of the fluid energy machine are cooled by means of the fluid to be fed, or the process fluid, in particular the bearings, which are in the faun of magnetic bearings.
  • the fluid energy machine is preferably designed such that the process fluid at least partially flows around the rotor.
  • the motor In order to allow the motor to exert lateral forces in order to stabilize the concentricity of the rotor with respect to the split cage, it is expedient for the motor to have at least two winding systems with different numbers of pole pairs.
  • the closed-loop control system can be connected to position and/or oscillation sensors, and to use their signals as input signals to drive the motor. These sensors can likewise be used for closed-loop control of radial magnetic bearings, as a result of which there is no need for additional components. Additionally or alternatively, the closed-loop control system can be linked to measurements of the electrical currents through the motor windings or to measurements of the magnetic fluxes on the motor, and these can be used as an input signal for exerting lateral forces on the rotor, in order to drive the motor.
  • the shaft can be borne by means of two separate radial bearings, which are arranged at the shaft ends and enclose the combination of the motor and compressor between them.
  • the motor and/or the impellers prefferably be arranged along a shaft longitudinal axis, and for a radial bearing to be provided in each case at both ends of the motor along this shaft longitudinal axis, and for a further radial bearing to be provided on the side of the impeller or of the impellers facing away from the motor.
  • This arrangement which comprises three separate radial bearings, is ideally suitable for good rotor dynamics for multistage compressors.
  • the invention also relates to a method for operation of a fluid energy machine of the abovementioned type, in which an additional drive for production of radial forces with respect to a shaft longitudinal axis is superimposed by means of a closed-loop control system for driving the motor for controlling a drive torque, and in which at least two further radial bearings are provided adjacent to the motor.
  • FIG. 1 shows a schematic illustration of a longitudinal section through a fluid energy machine according to the invention, with components of a closed-loop control system according to the invention, which is illustrated in simplified foam, by means of block symbols.
  • the figure shows a longitudinal section through a fluid energy machine 1 , and a closed-loop control system 2 , in the form of a block diagram, each illustrated in a simplified form.
  • the fluid energy machine 1 has a compressor 3 and a motor 4 , connected by means of a common shaft 5 and arranged along a shaft longitudinal axis 6 in a housing 7 which provides an external gas-tight seal.
  • the gas-tight housing 7 is gas-tight to the extent that no bushing is provided for the shaft 5 , which would have to be sealed by means of a shaft seal.
  • the fluid energy machine 1 can be described as having no seals, although shaft seals are located between the individual stages of the compressor 3 , in order to cope with the pressure difference produced in the stages.
  • the housing 7 has an inlet 8 and an outlet 9 for process fluid 10 , which is compressed by means of the compressor 3 .
  • process fluid 10 flows from the last impeller 11 along a secondary flow path 12 as far as the first impeller 11 .
  • the motor 4 has a rotor 15 and a stator 16 , with the rotor 15 being supported by the shaft 5 .
  • the shaft 5 is borne in a first radial bearing 17 and a second radial bearing 18 , as well as an axial bearing 19 . Dashed lines in the figure show a third radial bearing 20 , which can optionally be provided.
  • the shaft 5 can also be formed by means of a quill shaft 21 (illustrated by dashed lines) in the area between the compressor 3 and the motor 4 , such that it bends easily.
  • the compressor 3 has three stages, and correspondingly has three impellers 11 , but may also have fewer or more stages.
  • the bearings 17 , 18 , 19 and 20 are in the form of magnetic bearings, and the secondary flow path 12 extends along these bearings, in order to cool them.
  • the process fluid 10 along the secondary flow path 12 cools not only the magnetic bearings 17 - 20 but also the rotor 15 of the motor 4 .
  • the stator 16 is separated from the rotor 15 by a gap 22 , with the secondary flow path 12 extending through the gap 22 .
  • split cage 24 In order to ensure that the interior of the stator 16 is not subjected to the process fluid 10 , it is encapsulated, and is separated toward the gap 22 by a so-called split cage 24 .
  • the stator 16 is cooled by means of separate stator cooling 25 .
  • the cooling fluid 26 which circulates in the stator cooling may be at a different pressure than the process fluid 10 which is present in the gap, with the split cage 24 absorbing the pressure difference.
  • the motor 4 transmits a torque 30 to the compressor 3 , in order to drive the compression process.
  • the closed-loop control system 2 controls the rotation speed of the fluid energy machine 1 , with a rotation speed sensor 31 measuring the rotation speed on the shaft 5 , and passing on the measured value to an inverter 40 in the closed-loop control system 2 .
  • the inverter 40 supplies the stator 16 with the appropriate drive for the nominal rotation speed value, and with a current at the required voltage and frequency.
  • a combined regulator and amplifier 41 in the closed-loop control system 2 passes the appropriate nominal values for the rotation speed to the inverter 40 .
  • the combined regulator and amplifier 41 is furthermore connected to two position sensors, a first radial position sensor 50 and a second radial position sensor 51 , whose measured values are used by the combined regulator and amplifier 41 to appropriately drive the first radial bearing 17 and the second radial bearing 18 such that the shaft 5 remains in its nominal spatial position.
  • the combined regulator and amplifier 41 uses the signals from the radial position sensors 50 , 51 in order to cause the inverter 40 to produce a drive for the stator 16 of the motor 4 , which is superimposed on the drive for driving the compressor, resulting in a discrepancy in the concentric position of the shaft 5 with respect to the split cage 24 , and which drive results in additional radial forces 60 on the shaft 5 .
  • a first winding system 71 and a second winding system 72 are provided in the stator 16 , which winding systems 71 , 72 have different numbers of pole pairs.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
US13/058,602 2008-08-13 2009-08-11 Fluid energy machine Abandoned US20110150628A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008038787.8 2008-08-13
DE102008038787A DE102008038787A1 (de) 2008-08-13 2008-08-13 Fluidenergiemaschine
PCT/EP2009/060383 WO2010018171A1 (de) 2008-08-13 2009-08-11 Fluidenergiemaschine

Publications (1)

Publication Number Publication Date
US20110150628A1 true US20110150628A1 (en) 2011-06-23

Family

ID=41258491

Family Applications (1)

Application Number Title Priority Date Filing Date
US13/058,602 Abandoned US20110150628A1 (en) 2008-08-13 2009-08-11 Fluid energy machine

Country Status (7)

Country Link
US (1) US20110150628A1 (zh)
EP (1) EP2315946B1 (zh)
CN (1) CN102187099B (zh)
BR (1) BRPI0918436A2 (zh)
DE (1) DE102008038787A1 (zh)
RU (1) RU2500924C2 (zh)
WO (1) WO2010018171A1 (zh)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130302184A1 (en) * 2011-05-31 2013-11-14 Carrier Corporation Compressor Windage Mitigation
US20140356138A1 (en) * 2012-01-23 2014-12-04 Danfoss Turbocor Compressor B.V. Variable-speed multi-stage refrigerant centrifugal compressor with diffusers
IT201600120314A1 (it) * 2016-11-28 2018-05-28 Nuovo Pignone Tecnologie Srl Turbo-compressore e metodo di funzionamento di un turbo-compressore
US20180231006A1 (en) * 2017-02-14 2018-08-16 Danfoss A/S Oil free centrifugal compressor for use in low capacity applications
US10208740B2 (en) 2012-09-04 2019-02-19 Carrier Corporation Reciprocating refrigeration compressor suction valve seating
US20220136744A1 (en) * 2014-07-31 2022-05-05 Mitsubishi Heavy Industries Thermal Systems, Ltd. Turbo chiller

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1399171B1 (it) 2009-07-10 2013-04-11 Nuovo Pignone Spa Unita' di compressione ad alta pressione per fluidi di processo di impianti industriali e relativo metodo di funzionamento
BE1019030A5 (nl) 2009-08-03 2012-01-10 Atlas Copco Airpower Nv Turbocompressorsysteem.
DE102010026678B4 (de) * 2010-07-09 2016-05-19 Siemens Aktiengesellschaft Überwachungs-und Diagnosesystem für ein Fluidenergiemaschinensystem sowie Fluidenergiemachinensystem
FR2969722B1 (fr) 2010-12-22 2013-01-04 Thermodyn Groupe motocompresseur a accouplement torsible place dans un arbre creux du compresseur
DE102012207019B4 (de) * 2012-04-27 2015-12-24 Siemens Aktiengesellschaft Strömungsmaschine sowie Verfahren zur Kühlen einer solchen
AT513640B1 (de) * 2012-12-04 2014-08-15 Tech Universität Wien Lager- und Antriebs-System
WO2018033945A1 (ja) * 2016-08-18 2018-02-22 ダイキン工業株式会社 磁気軸受装置、及びそれを用いた流体機械システム
DE102018204619A1 (de) * 2018-03-27 2019-10-02 Robert Bosch Gmbh Strömungsmaschine, insbesondere Verdichtereinrichtung
DE102018108827B3 (de) * 2018-04-13 2019-05-29 Trumpf Schweiz Ag Verfahren zur Steuerung von zumindest einem Radialgebläse in einer Kälteanlage sowie Radialgebläse
DE102018115781B4 (de) 2018-06-29 2020-04-09 Maximilian Geisberger Verfahren zum Regeln einer Fluidenergiemaschine und eine Regelungsanordnung, insbesondere zum Durchführen des Verfahrens
DE102018128827A1 (de) * 2018-11-16 2020-05-20 Bayerische Motoren Werke Aktiengesellschaft Kompressor für einen Ansaugtrakt einer Verbrennungskraftmaschine eines Kraftfahrzeugs, Verbrennungskraftmaschine für ein Kraftfahrzeug sowie Kraftfahrzeug
CN114526244B (zh) * 2022-01-26 2023-06-27 清华大学 屏蔽式旋转流体机械
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

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4263540A (en) * 1979-07-05 1981-04-21 General Electric Company Two-speed refrigerant motor compressor
US4792710A (en) * 1986-02-20 1988-12-20 National Research Development Corporation Construction of electrical machines
US4886430A (en) * 1988-07-18 1989-12-12 Westinghouse Electric Corp. Canned pump having a high inertia flywheel
JPH06351282A (ja) * 1993-06-03 1994-12-22 Japan Servo Co Ltd キャンドモータポンプの制御装置
US6147425A (en) * 1998-11-17 2000-11-14 Koyo Seiko Co., Ltd. Controllable magnetic bearing apparatus
US6208051B1 (en) * 1994-03-17 2001-03-27 Seiko Seiki Kabushiki Kaisha Spindle apparatus
US6218749B1 (en) * 1998-11-30 2001-04-17 Reliance Electric Technologies, Llc Electric motor having rotor-embedded sensor
US7156627B2 (en) * 2001-06-05 2007-01-02 Siemens Industrial Turbomachinery B.V. Compressor unit comprising a centrifugal compressor and an electric motor
US20070110595A1 (en) * 2004-12-06 2007-05-17 Ebara Corporation Fluid conveying machine
US20070110596A1 (en) * 2005-11-16 2007-05-17 Weeber Konrad R Methods and apparatus for transporting natural gas through a pipeline
WO2007110275A1 (de) * 2006-03-24 2007-10-04 Siemens Aktiengesellschaft Verdichtereinheit
US20110044832A1 (en) * 2008-04-29 2011-02-24 Theo Nijhuis Fluid Energy Machine

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SU1211465A1 (ru) * 1982-06-22 1986-02-15 Teteryukov Vasilij Агрегат дл перекачивани газов или жидкостей
DE3729486C1 (de) * 1987-09-03 1988-12-15 Gutehoffnungshuette Man Kompressoreinheit
DE4241141A1 (de) * 1992-12-07 1994-06-09 Bhs Voith Getriebetechnik Gmbh Verdichteranlage mit einem im Antriebsstrang zwischen einer Antriebseinheit und einem Verdichterbereich der Anlage eingeschalteten Zahnradgetriebe
EP0846364B1 (de) 1995-08-24 1999-12-15 Sulzer Electronics AG Elektromotor
JPH1084655A (ja) * 1996-09-10 1998-03-31 Ebara Corp 磁気浮上モータ
EP0990798A1 (de) * 1999-07-16 2000-04-05 Sulzer Turbo AG Turboverdichter
EP1069313B1 (de) 1999-07-16 2005-09-14 Man Turbo Ag Turboverdichter
EP1074746B1 (de) 1999-07-16 2005-05-18 Man Turbo Ag Turboverdichter
EP1251624B1 (en) 2001-04-20 2009-01-21 Converteam Ltd Cooling of air gap winding of electrical machines
DE10212693A1 (de) * 2002-03-21 2003-10-02 Hilge Philipp Gmbh Leicht zu reinigende Kreiselpumpe
US9644633B2 (en) * 2003-04-11 2017-05-09 Thermodyn Centrifugal motor-compressor unit
EP1482179B1 (de) 2003-07-05 2006-12-13 MAN TURBO AG Schweiz Kompressorvorrichtung und Verfahren zum Betrieb derselben
JP2005061391A (ja) * 2003-07-30 2005-03-10 Aisin Seiki Co Ltd ポンプ装置
US7791238B2 (en) 2005-07-25 2010-09-07 Hamilton Sundstrand Corporation Internal thermal management for motor driven machinery
DE102006015064B4 (de) 2006-03-31 2008-05-29 Siemens Ag Elektrische Maschine
EP2103810A1 (en) 2008-03-19 2009-09-23 Siemens Aktiengesellschaft Compressor unit
EP2113671A1 (en) 2008-04-28 2009-11-04 Siemens Aktiengesellschaft Arrangement with an electric motor and a pump

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4263540A (en) * 1979-07-05 1981-04-21 General Electric Company Two-speed refrigerant motor compressor
US4792710A (en) * 1986-02-20 1988-12-20 National Research Development Corporation Construction of electrical machines
US4886430A (en) * 1988-07-18 1989-12-12 Westinghouse Electric Corp. Canned pump having a high inertia flywheel
JPH06351282A (ja) * 1993-06-03 1994-12-22 Japan Servo Co Ltd キャンドモータポンプの制御装置
US6208051B1 (en) * 1994-03-17 2001-03-27 Seiko Seiki Kabushiki Kaisha Spindle apparatus
US6147425A (en) * 1998-11-17 2000-11-14 Koyo Seiko Co., Ltd. Controllable magnetic bearing apparatus
US6218749B1 (en) * 1998-11-30 2001-04-17 Reliance Electric Technologies, Llc Electric motor having rotor-embedded sensor
US7156627B2 (en) * 2001-06-05 2007-01-02 Siemens Industrial Turbomachinery B.V. Compressor unit comprising a centrifugal compressor and an electric motor
US20070110595A1 (en) * 2004-12-06 2007-05-17 Ebara Corporation Fluid conveying machine
US20070110596A1 (en) * 2005-11-16 2007-05-17 Weeber Konrad R Methods and apparatus for transporting natural gas through a pipeline
WO2007110275A1 (de) * 2006-03-24 2007-10-04 Siemens Aktiengesellschaft Verdichtereinheit
US20090263265A1 (en) * 2006-03-24 2009-10-22 Gaston Mathijssen Compressor Unit
US20110044832A1 (en) * 2008-04-29 2011-02-24 Theo Nijhuis Fluid Energy Machine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
English Abstract of JP06351282A published on December 22, 1994 *

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130302184A1 (en) * 2011-05-31 2013-11-14 Carrier Corporation Compressor Windage Mitigation
US10612551B2 (en) * 2011-05-31 2020-04-07 Carrier Corporation Compressor motor windage loss mitigation
US20140356138A1 (en) * 2012-01-23 2014-12-04 Danfoss Turbocor Compressor B.V. Variable-speed multi-stage refrigerant centrifugal compressor with diffusers
US10072663B2 (en) * 2012-01-23 2018-09-11 Danfoss A/S Variable-speed multi-stage refrigerant centrifugal compressor with diffusers
US10208740B2 (en) 2012-09-04 2019-02-19 Carrier Corporation Reciprocating refrigeration compressor suction valve seating
US20220136744A1 (en) * 2014-07-31 2022-05-05 Mitsubishi Heavy Industries Thermal Systems, Ltd. Turbo chiller
IT201600120314A1 (it) * 2016-11-28 2018-05-28 Nuovo Pignone Tecnologie Srl Turbo-compressore e metodo di funzionamento di un turbo-compressore
US20180231006A1 (en) * 2017-02-14 2018-08-16 Danfoss A/S Oil free centrifugal compressor for use in low capacity applications
US11274679B2 (en) * 2017-02-14 2022-03-15 Danfoss A/S Oil free centrifugal compressor for use in low capacity applications

Also Published As

Publication number Publication date
BRPI0918436A2 (pt) 2015-11-24
RU2011109159A (ru) 2012-09-20
EP2315946B1 (de) 2016-09-28
DE102008038787A1 (de) 2010-02-18
CN102187099A (zh) 2011-09-14
WO2010018171A1 (de) 2010-02-18
RU2500924C2 (ru) 2013-12-10
CN102187099B (zh) 2014-01-22
EP2315946A1 (de) 2011-05-04

Similar Documents

Publication Publication Date Title
US20110150628A1 (en) Fluid energy machine
US7964982B2 (en) Axial in-line turbomachine
US6043580A (en) Rotodynamic machine for the forwarding of a fluid
US9599113B2 (en) Permanent magnet motor pump
US8579608B2 (en) Fluid energy machine
US20040005228A1 (en) Motor driven centrifugal compressor/blower
EP3545197B1 (en) Turbo-compressor and method of operating a turbo-compressor
US10608484B2 (en) Electric motors
CN108488075A (zh) 离心泵与永磁电机安全运行控制装置及其调控方法
EP3358146B1 (en) Turbomachine and method of operating a turbomachine
US20240006958A1 (en) Electric motor system, turbo compressor, and refrigeration device
EP3919769B1 (en) Thrust magnetic bearing and turbo compressor equipped with same
US20070110595A1 (en) Fluid conveying machine
EP3780380B1 (en) Electric motor system, and turbo compressor provided with same
GB2567581A (en) Electric disk motor having media separation in the motor gap
EP4108947A1 (en) Electric motor system, and turbo compressor provided with same
US11105217B2 (en) Turbine generator and method of operating a turbine generator
JP4706523B2 (ja) 燃料電池用圧縮機
JP2005171825A (ja) 流体搬送機械
KR20170103603A (ko) 다기능 베어링레스 전자기 회로 일체형 축류식 자기부상 임펠러를 갖는 유체기기
JP2009191638A (ja) ターボ機械
GB2567582A (en) Electric disc rotor with a pressure reducer for the motor gap
US20120275923A1 (en) Rotor for a turbo-machine
Park et al. Design and evaluation of hybrid magnetic bearings for turbo compressors
Kashin et al. Advanced Axial Pumps for Oil Industry

Legal Events

Date Code Title Description
STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION