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EP2322805A1 - Ensemble de compresseur de gaz - Google Patents

Ensemble de compresseur de gaz Download PDF

Info

Publication number
EP2322805A1
EP2322805A1 EP09014133A EP09014133A EP2322805A1 EP 2322805 A1 EP2322805 A1 EP 2322805A1 EP 09014133 A EP09014133 A EP 09014133A EP 09014133 A EP09014133 A EP 09014133A EP 2322805 A1 EP2322805 A1 EP 2322805A1
Authority
EP
European Patent Office
Prior art keywords
gas
section
motor
compressor assembly
inlet
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Withdrawn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
EP09014133A
Other languages
German (de)
English (en)
Inventor
Patrick Van Der Span
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
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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, Siemens Corp filed Critical Siemens AG
Priority to EP09014133A priority Critical patent/EP2322805A1/fr
Priority to EP10779528A priority patent/EP2499376A1/fr
Priority to US13/508,383 priority patent/US20120251351A1/en
Priority to PCT/EP2010/067177 priority patent/WO2011058037A1/fr
Priority to CN201080051313XA priority patent/CN102725534A/zh
Publication of EP2322805A1 publication Critical patent/EP2322805A1/fr
Withdrawn legal-status Critical Current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
    • F04D17/00—Radial-flow pumps, e.g. centrifugal pumps; Helico-centrifugal pumps
    • F04D17/08—Centrifugal pumps
    • F04D17/10—Centrifugal pumps for compressing or evacuating
    • F04D17/12—Multi-stage pumps
    • F04D17/122—Multi-stage pumps the individual rotor discs being, one for each stage, on a common shaft and axially spaced, e.g. conventional centrifugal multi- stage compressors
    • 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
    • F04D25/0606—Units comprising pumps and their driving means the pump being electrically driven the electric motor being specially adapted for integration in the pump
    • 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5806—Cooling the drive system
    • 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
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps
    • F04D29/584—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps cooling or heating the machine
    • 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
    • F04D29/70—Suction grids; Strainers; Dust separation; Cleaning
    • F04D29/701—Suction grids; Strainers; Dust separation; Cleaning especially adapted for elastic fluid pumps
    • 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

Definitions

  • the present invention relates to a gas compressor assembly according to the preamble of claim 1; such a gas compressor is known from US Pat. No. 7,156,627 B2 .
  • US Pat. No. 7,156,627 B2 discloses a gas compressor assembly for such gas compression which usually comprises a rotor with an axis of rotation, a centrifugal compressor for compressing a gas, and an electric motor arranged on a common rotor shaft, a first bearing section and a second bearing section including bearings arranged in the vicinity of both ends of the rotor shaft to support the rotor.
  • the gas compressor assembly herein includes an inlet positioned between the motor and the compressor to supply the gas to the compressor.
  • the compressor compresses the gas and the compressed gas is passed through a filter to remove the impurities present in the gas and is then provided to the motor, the first bearing section and the second bearing section through separate passageways running from the compressor for cooling these sections.
  • the temperature of the compressed gas herein may be high which decreases the capacity of the cooling gas to cool the motor and the bearing sections.
  • the underlying idea of the invention is to increase the cooling of the motor section by supplying the gas directly to the motor section before getting compressed.
  • the compression of the gas increases the pressure of the gas by expending energy leading to an increase in the temperature of the gas.
  • providing the uncompressed gas helps to improve the cooling of the motor section as the uncompressed gas has higher capacity to carry-over the heat away from the motor section.
  • the inlet is positioned adjacent to the side of the motor section distant from the compressor section. This reduces the length of the motor passageway thereby making the design compact.
  • the gas compressor assembly further includes a bearing section arranged along the rotational axis of the rotor at the side of the motor section distant from the compressor section, wherein the inlet is connected to the bearing section through a first bearing passageway to supply the gas for cooling the bearing section.
  • the bearing section includes a second bearing passageway to direct the gas from the bearing section to the motor section. This helps to provide additional gas flow to increase the rate of gas flowing through the motor section for cooling of the motor.
  • the inlet is arranged such that the main flow of the gas is directed to the motor section. The increased gas flow through the motor section helps to carry away a higher amount of heat, thereby improving cooling of the motor during compressor operation.
  • the gas compressor assembly further comprising a second motor passageway to direct the gas to a motor gap between the rotor and a stator for cooling the motor section.
  • the passageway provides for supplying the cooling gas to the space between the rotor and the stator so as to effectively cool the motor.
  • the first motor passageway supplies the gas radially outside the stator for cooling the motor section. This helps to establish direct gas contact with the stator to transfer heat from the stator to ensure desired cooling of the motor section.
  • the inlet is arranged so as to channel the gas to the compressor section through the motor section. This helps to cool the motor section before compression of the gas, thereby providing increased cooling of the motor and stator.
  • all the gas supplied through the inlet is used for cooling the motor section. This provides for increased cooling of the motor section and eliminates the need for additional cooling devices such as fans, radiators or the like.
  • the inlet is connected to a separation unit to separate at least one of a liquid and solid particle from the gas before providing for cooling. This helps to prevent any damage of the motor or bearings due to the presence of corrosive particles. Also it increases the efficiency of the compressor as the gas supplied to the compressor section is substantially free of impurities.
  • the separation unit comprises an annular chamber positioned circumferentially around the axis of the rotor for the passage of the gas, wherein the gas is rotated inside the chamber such that at least one of the liquid and solid particles is separated from the gas.
  • the annular chamber is simple in design with a big radius which yields high centrifugal forces leading to a good separation of the impurities from the gas. Also, this does not require any auxiliary device for operation, which in turn provides for cleaning the gas in a cost-effective manner.
  • the annular chamber includes an outer section and an inner section for the passage of the gas, wherein the outer section is connected to receive the gas from the inlet to and the inner section is adapted to supply the purified gas to the motor section.
  • This helps to separate the impurities from the gas at the outer section itself, thereby helps to supply the gas substantially free of impurities to the motor section, , which in turn prevents the damage of the motor and also increases its efficiency.
  • the annular chamber further includes a barrier element positioned between the outer section and the inner section, wherein the barrier element deflects the liquid and solid particles from the outer section to the inner section. By this deflection liquid and other solid particles can be separated from the gas to be provided for cooling.
  • the separation unit further includes a drain line extending out of the compressor to expel the separated liquid and solid particle from the gas.
  • This drain line isolates the separated particles and liquid from the assembly, thereby preventing the back-mixing of the particles with the gas.
  • the separation unit is positioned on the inlet side in the compressor assembly between the inlet and the motor section. This provides a compact design and helps to reduce the length of the flow path of the gas.
  • the assembly further includes a gas-tight housing enclosing all the components of the assembly.
  • FIG 1 shows a schematic overview in a cross-section of a gas compressor assembly 10 according to an embodiment of the invention.
  • the gas compressor assembly 10 comprises of a rotor 12 having an axis 13 of rotation, a bearing section 14, a motor section 15, and a compressor section 16. These sections are arranged in the order referred herein along the axis 13 of the rotor 12.
  • the bearing section 14 is arranged along the rotational axis 13 of the rotor 12 at the side of the motor section 15 distant from the compressor section 16.
  • the bearing section 14 includes a plurality of active magnetic bearings 18 for supporting the rotor 12.
  • the assembly 10 herein further includes a common gas-tight housing 17 enclosing the rotor 12, the bearing section 14, the motor section 15, and the compressor section 16.
  • the assembly 10 further includes another bearing section 38 enclosed with the gas tight housing 17.
  • the bearing sections 14, 38 are generally disposed at the axial end sections of the rotor 12.
  • the gas compressor assembly 10 herein further includes an inlet 20 designed to provide an unregulated gas input to the assembly.
  • the inlet 20 is positioned adjacent to the side of the motor section 15 distant from the compressor section 16.
  • the gas 11 is drawn through the inlet 20 and is directed through various passages to cool the internal components of the gas compressor assembly 10 in a predetermined sequence to optimize the cooling efficiency and operating life of the assembly 10.
  • the inlet 20 through which the gas 11 enters the gas compressor assembly 10 is placed adjacent to the bearing section 14 for providing the gas 11 to the different sections in the assembly 10.
  • the inlet 20 can be an aperture formed on the compressor housing 17 or can be a line extending from external components to provide gas 11 to the compressor assembly 10.
  • the inlet 20 is connected to the motor section 15 through a first motor passageway 22 to provide the main flow of gas 11 to the motor section 15 for cooling the motor section 15.
  • the gas 11 supplied through the first motor passageway 22 is directed radially outside a stator 19 in the motor section 15.
  • the motor section 15 further includes a motor gap 26 that extends longitudinally between the stator 19 and the rotor 12.
  • the gas 11 from the inlet 20 is supplied to the motor gap 26 through a second motor passageway 23 radially extending from the first motor passageway 22 to cool the motor section 15 to an acceptable operation temperature.
  • the inlet 20 herein is connected to the bearing section 14 through a bearing passageway 21 for guiding the gas 11 from the gas flow path to the bearing section 14.
  • the gas 11 supplied to the bearing section 14 is directed through the bearing gaps 25 between the active magnetic bearings 18 for cooling the active magnetic bearings 18.
  • the gas 11 from the bearing section 14 is further directed to the motor section 15.
  • the inlet 20 is arranged such that majority of the gas 11, for instance 60% to 90%, supplied through the inlet 20 is passed to the motor section 15 for cooling the motor section 15.
  • the gas 11 is supplied directly to the motor section 15, before getting compressed at the compressor section 17.
  • the heat carrying capacity of the uncompressed gas is more, which helps to effectively carry a substantial amount of heat from the motor section 15, thereby reducing the recycling flows.
  • the gas 11 supplied through the inlet 20 has a pressure sufficient enough to provide the required flow rate through the assembly 10.
  • the gas compressor 10 includes a separation unit 27 placed at the inlet 20 side between the inlet 20 and motor section 15.
  • the separation unit 27 removes the liquid or other solid particles present in the gas 11 before providing it for cooling.
  • the inlet 20 is connected to an annular chamber 28 of the separation unit 27.
  • the gas 11 to be filtered enters through the inlet 20 into the annular chamber 28 where it is rotated at a high speed around the axis 13 of the rotor 12. This provides for separating the liquid, solid particle or other impurities which may present in the gas 12 before supplying for cooling to the motor section 15 and bearing section 14.
  • the separated liquid and solid particles are discharged from the annular chamber 28 by a drain line 29 extending out of the gas compressor assembly 10.
  • the motor section 15 and the compressor section 16 are arranged in a fluid-connecting manner in the assembly 10.
  • the gas 11 from the motor section 15 is directed to the compressor section 16 through a compressor passageway 24 for compression.
  • the compressor section 16 includes a compressor 30 which may be a compressor known in the art that is used for gas compression applications, such as axial compressors, radial compressors, and the like.
  • the compressor 30 is connected to a gas outlet 31, through which compressed gas 11 exits the gas compressor assembly 10.
  • the motor section 15 and the compressor section 16 can be accommodated in a single housing. Such an arrangement is particularly useful for subsea applications in which easy installation and retrieval are important.
  • the first and second motor passageways 23, 24 provide sufficient space for the gas 11 to flow through such that the gas streaming through the motor section 15 is not significantly restricted by the passageways 23, 24. That is the passageways are large enough to handle the stream of gas 11 without producing pressure build up on the inlet 20 side or a pressure drop on the side of the motor section providing gas to the compressor section 16. This provides the benefit of a continuous and relatively uniform supply of gas 11 to the compressor section 16 for compression.
  • FIG 2 illustrates a schematic top view of a separation unit 27 according to an embodiment herein.
  • the separation unit 27 herein is an accessorial unit which can be positioned in the assembly 10 to remove the liquid or solid particles from the incoming gas flow before the gas 11 is directed for cooling the motor section 15 or other internal components.
  • inlet 20 of the gas compressor 10 is connected to the separation unit 27 to provide the gas 11.
  • the gas 11 from the inlet 20 is then fed to an annular chamber 28 in the separation unit 27.
  • the gas 11 flowing through the chamber 28 may include traces of liquid, air or other type of gases containing dust or other particle impurities suspended therein with the impurities to be cleansed from the gas.
  • the annular chamber 29 herein is divided to an outer section 32 and an inner section 33.
  • both sections 32, 33 are separated from each other by a barrier element 34 placed between the inner and outer sections 32, 33.
  • the barrier element 34 herein is preferably in the shape of an annular ring. This geometry is aligned with the flow of gas and thereby reduces the pressure loss of the gas flow.
  • the gas 11 is fed to the annular chamber 28, it is brought into rapid rotation in a direction along the rotational axis of the rotor 12 in the outer section 32. During this rotational movement, a large part of the liquid or other solid particles are flung out against the inner wall 35 of the annular chamber 28 owing to the centrifugal force where they gets collected and consequently drains out by gravity. The collected liquid or particles can be drained off via a drain line 29 without gas being mixed into an appreciable extent.
  • the gas 11 is rotated preferably at a rotational speed of 20,000 to 35,000 revolutions per minute.
  • the gas 11 which is substantially free of the impurities is then passed on the inner section 33 to be circulated to the motor section 15.
  • the separation unit 27 further includes bearing passageway 21 and motor passageways 22, 23 extending from the annular chamber 28 to supply the filtered gas 11 to the bearing section 14 and motor section 15 for cooling.
  • the annular chamber 28 herein combines the function of separation of liquid or other solid particles and distribution of the gas to be compressed over the circumference of the rotation axis 10 in one compact component.
  • the separation unit 27 of FIG. 2 can be placed circumferentially around the axis 13 of rotation of the rotor 12 and can be secured thereto by a securing means 36 such as nuts or the like.
  • the separation unit 27 is simple in design with no moving parts to operate and is substantially easy to install in the gas compressor assembly 10. Also it requires no power to operate and starts working as soon as the gas to be treated is introduced. Moreover, it provides a minimum maintenance operation where the solid deposits can be removed by washing the annular chamber 28 with water or by running a liquid capable of dissolving the solid.
  • the dimensions of the annular chamber 28 determine the gas flow rate and the residence time required for the given separation process.
  • the dimensions of the annular chamber 28 can be determined experimentally so that the higher separation efficiency can be obtained.
  • the separation unit 27 design herein provides for preventing gas turbulence and back-mixing, which in turn prevents reentering of liquid or other particles and results in very high separation efficiencies for most industrial applications.
  • the separation unit 27 is suitable for use with additional pressurization, vacuuming, cooling condensation, etc with little or no design modifications.
  • the inlet is arranged prior to the motor section. This helps to provide for filtering the gas before providing for cooling, thereby avoiding the need for separate scrubber and additional gas/fluid systems.
  • the gas compressor according to the invention finds extensive applications where higher pressure or lower volumes of gas is required. For instance, in pipeline transport of purified natural gas to move the gas from the production site to the consumer, in submarines, to store air for later use in displacing water from buoyancy chambers, for adjustment of depth, in petroleum refineries, natural gas processing plants, petrochemical and chemical plants, and similar large industrial plants for compressing intermediate and end product gases, in turbochargers and superchargers to increase the performance of internal combustion engines by increasing mass flow and the like.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP09014133A 2009-11-11 2009-11-11 Ensemble de compresseur de gaz Withdrawn EP2322805A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP09014133A EP2322805A1 (fr) 2009-11-11 2009-11-11 Ensemble de compresseur de gaz
EP10779528A EP2499376A1 (fr) 2009-11-11 2010-11-10 Ensemble compresseur de gaz
US13/508,383 US20120251351A1 (en) 2009-11-11 2010-11-10 Gas Compressor Assembly
PCT/EP2010/067177 WO2011058037A1 (fr) 2009-11-11 2010-11-10 Ensemble compresseur de gaz
CN201080051313XA CN102725534A (zh) 2009-11-11 2010-11-10 气体压缩机组件

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP09014133A EP2322805A1 (fr) 2009-11-11 2009-11-11 Ensemble de compresseur de gaz

Publications (1)

Publication Number Publication Date
EP2322805A1 true EP2322805A1 (fr) 2011-05-18

Family

ID=41600305

Family Applications (2)

Application Number Title Priority Date Filing Date
EP09014133A Withdrawn EP2322805A1 (fr) 2009-11-11 2009-11-11 Ensemble de compresseur de gaz
EP10779528A Withdrawn EP2499376A1 (fr) 2009-11-11 2010-11-10 Ensemble compresseur de gaz

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP10779528A Withdrawn EP2499376A1 (fr) 2009-11-11 2010-11-10 Ensemble compresseur de gaz

Country Status (4)

Country Link
US (1) US20120251351A1 (fr)
EP (2) EP2322805A1 (fr)
CN (1) CN102725534A (fr)
WO (1) WO2011058037A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103917786A (zh) * 2011-08-30 2014-07-09 Ksb股份公司 涡轮压缩机及应用
EP2865896A3 (fr) * 2013-09-25 2015-05-13 Panasonic Intellectual Property Management Co., Ltd. Turbocompresseur et appareil à cycle de réfrigération

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN108386370A (zh) * 2018-03-05 2018-08-10 清华大学 一种离心压缩机
FR3088386B1 (fr) * 2018-11-13 2021-01-08 Thermodyn Dispositif de filtration pour un groupe moto-compresseur
FR3096728B1 (fr) * 2019-05-29 2022-01-28 Thermodyn Cartouche de compresseur, motocompresseur et procédé d’assemblage d’un tel motocompresseur
US20250334123A1 (en) * 2024-04-29 2025-10-30 Garrett Transportation I Inc. Fluid Compressor Device

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DE20011217U1 (de) * 1999-07-16 2000-09-07 Sulzer Turbo Ag Zuerich Turboverdichter
US7156627B2 (en) 2001-06-05 2007-01-02 Siemens Industrial Turbomachinery B.V. Compressor unit comprising a centrifugal compressor and an electric motor
DE602004001156T2 (de) * 2003-04-11 2007-04-19 Thermodyn Verdichtereinheit mit unterstützter Kühlung
US20070110596A1 (en) * 2005-11-16 2007-05-17 Weeber Konrad R Methods and apparatus for transporting natural gas through a pipeline
FR2896101A1 (fr) * 2006-01-10 2007-07-13 Mecanique Magnetique Sa Soc D Dispositif de filtrage de particules dans une machine tournante a paliers magnetiques actifs
EP1826887A2 (fr) * 2006-02-24 2007-08-29 General Electric Company Pompe avec moteur électrique qui peut être utilisée dans des pipelines et procédé correspondant

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US4780061A (en) * 1987-08-06 1988-10-25 American Standard Inc. Screw compressor with integral oil cooling
FI981743A0 (fi) * 1998-08-12 1998-08-12 Neste Oy Menetelmä ja laitteisto kahden faasin erottamiseksi toisistaan
JP3870642B2 (ja) * 1999-12-21 2007-01-24 株式会社デンソー 電動圧縮機
US6592654B2 (en) * 2001-06-25 2003-07-15 Cryogenic Group Inc. Liquid extraction and separation method for treating fluids utilizing flow swirl
KR100414110B1 (ko) * 2001-09-25 2004-01-07 엘지전자 주식회사 터보 압축기의 베어링 냉각구조
US7204670B1 (en) * 2002-10-07 2007-04-17 Mee Industries, Inc. Water removal from a compressor air inlet duct
RU2304233C2 (ru) * 2003-04-11 2007-08-10 Термодин Центробежный компрессорный агрегат

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE20011217U1 (de) * 1999-07-16 2000-09-07 Sulzer Turbo Ag Zuerich Turboverdichter
US7156627B2 (en) 2001-06-05 2007-01-02 Siemens Industrial Turbomachinery B.V. Compressor unit comprising a centrifugal compressor and an electric motor
DE602004001156T2 (de) * 2003-04-11 2007-04-19 Thermodyn Verdichtereinheit mit unterstützter Kühlung
US20070110596A1 (en) * 2005-11-16 2007-05-17 Weeber Konrad R Methods and apparatus for transporting natural gas through a pipeline
FR2896101A1 (fr) * 2006-01-10 2007-07-13 Mecanique Magnetique Sa Soc D Dispositif de filtrage de particules dans une machine tournante a paliers magnetiques actifs
EP1826887A2 (fr) * 2006-02-24 2007-08-29 General Electric Company Pompe avec moteur électrique qui peut être utilisée dans des pipelines et procédé correspondant

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103917786A (zh) * 2011-08-30 2014-07-09 Ksb股份公司 涡轮压缩机及应用
JP2014527598A (ja) * 2011-08-30 2014-10-16 カーエスベー・アクチエンゲゼルシャフトＫｓｂ Ａｋｔｉｅｎｇｅｓｅｌｌｓｃｈａｆｔ ターボ圧縮機および使用
EP2865896A3 (fr) * 2013-09-25 2015-05-13 Panasonic Intellectual Property Management Co., Ltd. Turbocompresseur et appareil à cycle de réfrigération
US9816517B2 (en) 2013-09-25 2017-11-14 Panasonic Intellectual Property Management Co., Ltd. Turbo-compressor and refrigeration cycle apparatus with heated guide vanes

Also Published As

Publication number Publication date
EP2499376A1 (fr) 2012-09-19
WO2011058037A1 (fr) 2011-05-19
CN102725534A (zh) 2012-10-10
US20120251351A1 (en) 2012-10-04

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