US20090263265A1 - Compressor Unit - Google Patents

Compressor Unit Download PDF

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Publication number
US20090263265A1
US20090263265A1 US12/225,517 US22551707A US2009263265A1 US 20090263265 A1 US20090263265 A1 US 20090263265A1 US 22551707 A US22551707 A US 22551707A US 2009263265 A1 US2009263265 A1 US 2009263265A1
Authority
US
United States
Prior art keywords
compressor unit
unit
housing
compressor
automation
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
US12/225,517
Other languages
English (en)
Inventor
Gaston Mathijssen
Mark van Aarsen
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: VAN AARSEN, MARK, MATHIJSSEN, GASTON
Publication of US20090263265A1 publication Critical patent/US20090263265A1/en
Abandoned legal-status Critical Current

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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
    • F04D25/0686—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
    • F04D29/40—Casings; Connections of working fluid
    • F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
    • F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps 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
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/5813—Cooling the control unit
    • 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
    • F04D29/5853—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid pumps heat insulation or conduction
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K11/00—Structural association of dynamo-electric machines with electric components or with devices for shielding, monitoring or protection
    • H02K11/30—Structural association with control circuits or drive circuits
    • H02K11/33—Drive circuits, e.g. power electronics
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/12—Casings or enclosures characterised by the shape, form or construction thereof specially adapted for operating in liquid or gas
    • H02K5/132—Submersible electric motors
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • H02K5/22—Auxiliary parts of casings not covered by groups H02K5/06-H02K5/20, e.g. shaped to form connection boxes or terminal boxes
    • H02K5/225—Terminal boxes or connection arrangements
    • 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 compressor unit, in particular for underwater operation, comprising a compressor with a rotation axis and an electric motor, which compressor unit has a housing which has an inlet and an outlet for a pumping medium, having an automation unit which is designed such that it carries out open-loop and closed-loop control tasks for the compressor unit.
  • Compressor units normally require numerous electrical connections for their operation, in particular for the power supply and for transmission of control signals between a higher-level automation unit and the compressor unit.
  • the higher-level automation units are in this case arranged separately from the compressor unit, at some distance away, on the one hand in order to achieve a high level of modularity of design, and on the other hand to ensure optimum operating conditions for the electronics of the automation unit.
  • numerous signal lines are required between the automation unit and the compressor unit, and transmit various measured values to the automation unit, and transmit corresponding control parameters to the magnetic bearings.
  • the automation unit must be provided with a cooling system by means of which the not-inconsiderable lost power from the components, some of which are in the form of power electronics, must be dissipated.
  • the document WO-A-2005/003512 has already disclosed a compressor unit for underwater operation in which the compressor together with an electric motor is accommodated in a common, gas-tight housing.
  • An automation unit which controls the operation of magnetic bearings, is connected for signal transmission purposes to these bearings.
  • the object of the invention is to provide a better interaction between the automation unit and the compressor unit and, in particular, to reduce the complexity for cooling the automation unit and of the signal and power transmission.
  • a compressor unit is proposed in order to achieve the object according to the invention.
  • the arrangement of an additional housing, in which the automation unit is arranged, on the housing of the compressor unit has, in particular, the advantage that appropriate power supply lines and signal lines between the automation unit and the compressor unit need no longer be designed to comply with a standard which is suitable for direct contact with the environmental conditions.
  • these lines can be designed such that they merely satisfy the always reproducible and exactly predictable operating conditions in the interior of the additional housing and of the housing of the compressor unit.
  • no special plug connections are required for disconnection of lines between the automation unit and the compressor unit.
  • a compressor unit is of a single-shaft design with a motor and a compressor unit along a single rotation axis, it is normally in an elongated form thus resulting in a temperature profile in the longitudinal extent during operation.
  • the temperature in the axial area of the inlet or of the intake connecting stub is particularly advantageous for thermally conductive fitting of the additional housing for the automation unit.
  • the heat is dissipated from the automation unit by means of thermal conduction in the area of the intake connecting stub of the housing, and introduced into the pumping medium flowing through the compressor unit.
  • a person skilled in the art can decide the circumferential position in the axial area of the intake connecting stub at which the additional housing is fitted, depending on the thermal-conduction conditions between the housing of the compressor unit and the additional housing.
  • the automation unit is expediently connected to components of the compressor unit by means of internal signal lines and/or internal power supply lines.
  • These internal lines can expediently be designed to be disconnectable by means of a plug connection, such that elements can be replaced without any problems even during the course of maintenance tasks.
  • the plug connections need be designed only to satisfy the always reproducible and predictable operating conditions in the housing interior.
  • the components which are connected to the automation unit are, in particular, magnetic bearings for the rotor of the compressor and of the motor, and the electric motor.
  • various temperature measurements and pressure measurements can be provided.
  • the automation unit is expediently connected to a base station by means of an external signal line or an external power supply line, or by means of both.
  • the additional housing to be connected to the housing of the compressor unit by means of welding, which on the one hand ensures good thermal conduction between the housings and on the other hand provides the required gas-tightness, in particular for underwater operation.
  • the additional housing In order to ensure that the components in the additional housing are nevertheless accessible for maintenance tasks, it is advantageous for the additional housing to have an opening which can be closed. This opening which can be closed can be sealed by means of a conventional seal. For relatively long underwater operation phases, it is also feasible for this additional opening to be sealed by means of a weld seam, which in any case withstands the adverse operating conditions.
  • the compressor unit In order to reliably dissipate on the one hand the lost power from the automation unit and on the other hand that from the operation of the compressor unit, it is expedient for the compressor unit itself to have a high-performance cooling system.
  • This cooling system may, in particular during the pumping of natural gas during underwater operation, be designed such that the pumping medium flows around various components of the compressor unit, and the lost heat is in this way emitted to the pumping medium.
  • FIG. 1 shows a longitudinal section through a compressor unit with an automation unit fitted according to the invention, in the form of a schematic illustration.
  • FIG. 1 shows a section along a compressor unit 1 according to the invention which has, as major components, a motor 2 and a compressor 3 in a housing 4 which is designed to be gas-tight.
  • the housing 4 accommodates the motor 2 and the compressor 3 .
  • the housing 4 is provided with an inlet 6 and an outlet 7 , with the fluid to be compressed being sucked in through the inlet 6 by means of an intake connecting stub 8 , and with the compressed fluid flowing out through the outlet 7 .
  • the compressor unit 1 is arranged vertically during operation, with a motor rotor 15 of the motor 2 being combined via a compressor rotor 9 of the compressor 3 to form a common shaft 19 , which rotates about a common vertical rotation axis 60 .
  • the motor rotor 15 is mounted in a first radial bearing 21 at the upper end of the motor rotor 15 .
  • the compressor rotor 9 is mounted in a second radial bearing 22 at a lower position.
  • An axial bearing 25 is therefore provided at the upper end of the motor rotor 15 , at the upper end of the common shaft 19 .
  • the radial bearings 21 , 22 and the axial bearing 25 operate electromagnetically, and are each designed to be encapsulated.
  • the radial bearings 21 , 22 in this case extend in the circumferential direction around the respective bearing point of the shaft 19 , and in this case are designed to revolve through 360° and not to be split.
  • the compressor 3 which is in the form of a centrifugal compressor, has three compressor stages 11 which are each connected by means of an overflow 33 .
  • the pressure differences which result across the compressor stages 11 ensure a thrust on the compressor rotor 9 , which is transmitted via a coupling to the motor rotor 15 and is in the opposite direction to the force produced by the weight of the entire resultant rotor comprising the compressor rotor 9 and the motor rotor 15 , such that this results in a very high degree of thrust matching during rated operation.
  • This allows the axial bearing 25 to be designed to be comparatively smaller than in a horizontal arrangement.
  • the electromagnetic bearings 21 , 22 , 25 are cooled to operating temperature by means of a cooling system 31 , with the cooling system 31 providing a tap 32 in an overflow of the compressor 3 .
  • a portion of the pumping medium which is preferably natural gas, is passed from the tap 32 by means of pipelines through a filter 35 , and is then passed through two separate pipelines to the respective outer bearing points (first radial bearing 21 and second radial bearing 22 as well as the axial bearing 25 ). This cooling by means of the cold pumping medium saves additional supply lines.
  • the motor rotor 15 is surrounded by a stator 16 which has an encapsulation 39 , such that the aggressive pumping medium does not damage the windings of the stator 16 .
  • the encapsulation 39 is in this case preferably designed such that it can withstand the full operating pressure. This is also because a separate stator cooling arrangement 40 is provided, which pumps a dedicated cooling medium 41 via a heat exchanger 43 by means of a pump 42 .
  • At least the encapsulation 39 is designed such that the section which extends between the stator 16 and the motor rotor 15 admittedly has a thin wall thickness, but is able to withstand the design pressure when the stator cooling arrangement 40 is completely filled by means of the cooling medium 41 . This avoids relatively major eddy current losses in this area, and improves the efficiency of the overall arrangement.
  • the compressor rotor 9 expediently has a compressor shaft 10 on which the individual compressor stages 11 are mounted. This can preferably be achieved by means of a thermal shrink fit. An interlock, for example by means of polygons, is likewise possible. Another embodiment provides for the various compressor stages 11 to be welded to one another, thus resulting in an integral compressor rotor 9 .
  • An additional housing 56 is thermally conductively fitted to the housing 4 of the compressor unit 1 by means of a weld seam 58 .
  • the additional housing 56 has an opening 57 through which the interior of the additional housing 56 is accessible, and which is closed by means of screws 59 and a cover 70 .
  • the cover 70 is welded by means of a sealing joint 63 to the adjacent elements of the additional housing 56 in order that the surrounding medium cannot enter during underwater operation.
  • An automation unit 51 comprising power electronics 52 and further components, is located in the interior of the additional housing 56 .
  • the automation unit 51 is thermally conductively connected to the housing 4 of the compressor unit by means of a thermal-conduction element 64 , such that the lost power that is created is dissipated by means of thermal conduction to the housing 4 .
  • the additional housing 56 is arranged in the axial area 50 of the inlet 6 , or of the intake connecting stub 8 , of the compressor unit such that the thermal conditions which prevail there ensure particularly efficient cooling of the automation unit 51 .
  • a specific temperature profile occurs along the rotation axis 60 of the compressor unit during operation, and essentially has a low point in the area of the intake connecting stub 8 .
  • the automation unit 51 is connected by means of external signal lines 66 and external power supply lines 68 to a station 65 which on the one hand controls, and on the other hand supplies, the compressor unit 1 .
  • the external signal lines 66 and power supply lines 68 are designed such that they can be disconnected by means of external plug connections 69 .
  • a bushing 53 seals the inlet of the external lines ( 66 , 68 ) into the additional housing 56 .
  • the automation unit 51 is connected to components of the compressor unit 1 by means of internal signal lines 55 and internal power supply lines 67 .
  • the components comprise an axial bearing 25 , radial bearings 21 , 22 and the motor 2 .
  • further sensors and components are also provided and are connected to the automation unit 51 , although they will not be explained in any more detail here.
  • the additional housing is formed from stainless steel, in particular for underwater operation.
  • the power supply originating from the base station 65 is 400 V.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Power Engineering (AREA)
  • Microelectronics & Electronic Packaging (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Compressor (AREA)
US12/225,517 2006-03-24 2007-02-15 Compressor Unit Abandoned US20090263265A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP06006059 2006-03-24
EP06006059.7 2006-03-24
PCT/EP2007/051474 WO2007110275A1 (de) 2006-03-24 2007-02-15 Verdichtereinheit

Publications (1)

Publication Number Publication Date
US20090263265A1 true US20090263265A1 (en) 2009-10-22

Family

ID=38016605

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/225,517 Abandoned US20090263265A1 (en) 2006-03-24 2007-02-15 Compressor Unit

Country Status (7)

Country Link
US (1) US20090263265A1 (de)
EP (1) EP1999374A1 (de)
CN (1) CN101410623B (de)
BR (1) BRPI0709128A2 (de)
NO (1) NO20084450L (de)
RU (1) RU2396466C2 (de)
WO (1) WO2007110275A1 (de)

Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090220362A1 (en) * 2006-02-03 2009-09-03 Rainer Gausmann Compressor Unit
US20110150628A1 (en) * 2008-08-13 2011-06-23 Norbert Wagner Fluid energy machine
JP2013007378A (ja) * 2011-05-25 2013-01-10 Nuovo Pignone Spa オイルフリーの低電圧のコンジットのための方法およびシステム
CN103208895A (zh) * 2012-01-17 2013-07-17 阿斯莫有限公司 驱动装置
DE102012204403A1 (de) * 2012-03-20 2013-09-26 Man Diesel & Turbo Se Radialverdichtereinheit
WO2014151967A1 (en) 2013-03-15 2014-09-25 Fmc Technologies, Inc. Submersible well fluid system
US20160277045A1 (en) * 2015-03-20 2016-09-22 Intel IP Corporation Adjusting Power Amplifier Stimuli Based on Output Signals
US9954414B2 (en) 2012-09-12 2018-04-24 Fmc Technologies, Inc. Subsea compressor or pump with hermetically sealed electric motor and with magnetic coupling
US10161418B2 (en) 2012-09-12 2018-12-25 Fmc Technologies, Inc. Coupling an electric machine and fluid-end
US10393115B2 (en) 2012-09-12 2019-08-27 Fmc Technologies, Inc. Subsea multiphase pump or compressor with magnetic coupling and cooling or lubrication by liquid or gas extracted from process fluid
US10801309B2 (en) 2012-09-12 2020-10-13 Fmc Technologies, Inc. Up-thrusting fluid system

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008057472B4 (de) * 2008-11-14 2011-07-14 Atlas Copco Energas GmbH, 50999 Mehrstufiger Radial-Turboverdichter
EP2290241A1 (de) * 2009-07-13 2011-03-02 Siemens Aktiengesellschaft Turbokompressoreinheit mit einem Kühlsystem
DE102011002627A1 (de) * 2011-01-13 2012-07-19 Continental Automotive Gmbh Abgasturbolader mit einem Verdichtergehäuse mit integriertem Wastegate-Steller
ITCO20120030A1 (it) * 2012-06-06 2013-12-07 Nuovo Pignone Srl Compressori ad alto rapporto di pressione con intercooler multiplo e relativi metodi
CN107250548B (zh) * 2014-12-05 2019-11-05 诺沃皮尼奥内股份有限公司 具有磁性轴承的马达压缩机单元
FI128651B (en) * 2017-06-30 2020-09-30 Lappeenrannan Teknillinen Yliopisto System for an electric machine
IT201700097796A1 (it) * 2017-08-31 2019-03-03 Nuovo Pignone Tecnologie Srl Sistemi di turbomacchine con refrigerazione di cuscini magnetici attivi e metodo

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3568771A (en) * 1969-04-17 1971-03-09 Borg Warner Method and apparatus for lifting foaming crude by a variable rpm submersible pump
US3963367A (en) * 1974-08-21 1976-06-15 International Harvester Company Turbine surge detection system
US4969803A (en) * 1987-09-03 1990-11-13 Man Gutehoffnungshutte Gmbh Compressor unit

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IL109967A (en) * 1993-06-15 1997-07-13 Multistack Int Ltd Compressor
CN1094178C (zh) * 1995-12-28 2002-11-13 株式会社荏原制作所 泵组合体
EP0990798A1 (de) * 1999-07-16 2000-04-05 Sulzer Turbo AG Turboverdichter
NO323324B1 (no) * 2003-07-02 2007-03-19 Kvaerner Oilfield Prod As Fremgangsmate for regulering at trykket i en undervannskompressormodul

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3568771A (en) * 1969-04-17 1971-03-09 Borg Warner Method and apparatus for lifting foaming crude by a variable rpm submersible pump
US3963367A (en) * 1974-08-21 1976-06-15 International Harvester Company Turbine surge detection system
US4969803A (en) * 1987-09-03 1990-11-13 Man Gutehoffnungshutte Gmbh Compressor unit

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8137081B2 (en) * 2006-02-03 2012-03-20 Siemens Aktiengesellschaft Compressor unit
US20090220362A1 (en) * 2006-02-03 2009-09-03 Rainer Gausmann Compressor Unit
US20110150628A1 (en) * 2008-08-13 2011-06-23 Norbert Wagner Fluid energy machine
JP2013007378A (ja) * 2011-05-25 2013-01-10 Nuovo Pignone Spa オイルフリーの低電圧のコンジットのための方法およびシステム
CN103208895A (zh) * 2012-01-17 2013-07-17 阿斯莫有限公司 驱动装置
US20130183175A1 (en) * 2012-01-17 2013-07-18 Asmo Co., Ltd. Driving device
DE102012204403A1 (de) * 2012-03-20 2013-09-26 Man Diesel & Turbo Se Radialverdichtereinheit
US9954414B2 (en) 2012-09-12 2018-04-24 Fmc Technologies, Inc. Subsea compressor or pump with hermetically sealed electric motor and with magnetic coupling
US10801309B2 (en) 2012-09-12 2020-10-13 Fmc Technologies, Inc. Up-thrusting fluid system
US10393115B2 (en) 2012-09-12 2019-08-27 Fmc Technologies, Inc. Subsea multiphase pump or compressor with magnetic coupling and cooling or lubrication by liquid or gas extracted from process fluid
US10161418B2 (en) 2012-09-12 2018-12-25 Fmc Technologies, Inc. Coupling an electric machine and fluid-end
US20160145980A1 (en) * 2013-03-15 2016-05-26 Fmc Technologies, Inc. Submersible Well Fluid System
AU2016235008B2 (en) * 2013-03-15 2018-03-08 Fmc Technologies, Inc. Submersible well fluid system
EP2971764A4 (de) * 2013-03-15 2017-01-11 FMC Technologies, Inc. Tauchfähiges bohrlochfluidsystem
US10221662B2 (en) * 2013-03-15 2019-03-05 Fmc Technologies, Inc. Submersible well fluid system
WO2014151967A1 (en) 2013-03-15 2014-09-25 Fmc Technologies, Inc. Submersible well fluid system
US11352863B2 (en) 2013-03-15 2022-06-07 Fmc Technologies, Inc. Submersible well fluid system
US9571135B2 (en) * 2015-03-20 2017-02-14 Intel IP Corporation Adjusting power amplifier stimuli based on output signals
US20160277045A1 (en) * 2015-03-20 2016-09-22 Intel IP Corporation Adjusting Power Amplifier Stimuli Based on Output Signals

Also Published As

Publication number Publication date
BRPI0709128A2 (pt) 2011-06-28
CN101410623A (zh) 2009-04-15
NO20084450L (no) 2008-12-18
CN101410623B (zh) 2010-12-08
RU2396466C2 (ru) 2010-08-10
WO2007110275A1 (de) 2007-10-04
RU2008142113A (ru) 2010-04-27
EP1999374A1 (de) 2008-12-10

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Owner name: SIEMENS AKTIENGESELLSCHAFT, GERMANY

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:MATHIJSSEN, GASTON;VAN AARSEN, MARK;REEL/FRAME:021620/0492;SIGNING DATES FROM 20080911 TO 20080916

STCB Information on status: application discontinuation

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