US20110081231A1 - Pump bearing arrangement - Google Patents

Pump bearing arrangement Download PDF

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Publication number
US20110081231A1
US20110081231A1 US12/672,744 US67274408A US2011081231A1 US 20110081231 A1 US20110081231 A1 US 20110081231A1 US 67274408 A US67274408 A US 67274408A US 2011081231 A1 US2011081231 A1 US 2011081231A1
Authority
US
United States
Prior art keywords
vibration element
pump
bearing arrangement
bearing
arrangement according
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
US12/672,744
Other languages
English (en)
Inventor
Rainer Hoelzer
Markus Henry
Robert Stolle
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.)
Leybold GmbH
Original Assignee
Oerlikon Leybold Vacuum GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Oerlikon Leybold Vacuum GmbH filed Critical Oerlikon Leybold Vacuum GmbH
Assigned to OERLIKON LEYBOLD VACUUM GMBH reassignment OERLIKON LEYBOLD VACUUM GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: HENRY, MARKUS, HOELZER, RAINER, STOLLE, ROBERT
Publication of US20110081231A1 publication Critical patent/US20110081231A1/en
Abandoned legal-status Critical Current

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Classifications

    • 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
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/06—Elastic or yielding bearings or bearing supports, for exclusively rotary movement by means of parts of rubber or like materials
    • F16C27/066—Ball or roller 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
    • F04D19/00—Axial-flow pumps
    • F04D19/02—Multi-stage pumps
    • F04D19/04—Multi-stage pumps specially adapted to the production of a high vacuum, e.g. molecular pumps
    • F04D19/042—Turbomolecular vacuum 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
    • F04D29/059—Roller 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
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
    • 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
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/07—Fixing them on the shaft or housing with interposition of an element
    • F16C35/077—Fixing them on the shaft or housing with interposition of an element between housing and outer race ring
    • 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
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/16—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls
    • F16C19/163—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with a single row of balls with angular contact
    • 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
    • F16C2360/45—Turbo-molecular pumps

Definitions

  • the invention relates to a pump bearing arrangement which is suitable particularly for rapidly rotating pumps such as e.g. turbomolecular pumps.
  • Pumps such as e.g. turbomolecular pumps, comprise a pump rotor connected to a rotor shaft.
  • the rotor shaft is supported in a shaft housing via two bearing arrangements.
  • Said two bearing arrangements usually comprise respectively one ball bearing.
  • the inner bearing rings and respectively bearing shells of the two ball bearings are fixedly connected to the rotor shaft.
  • the outer bearing rings and respectively bearing shells are connected to the shaft housing in the axial direction, or are arranged in abutment e.g. on an annular projection of the shaft housing in the axial direction.
  • the two bearing arrangements are axially biased.
  • the outer bearing rings are usually not arranged in direct abutment on the shaft housing. Instead, an annular gap is provided between the outer bearing rings and the shaft housing.
  • an O-ring is arranged, serving particularly as a vibration element for damping and radially holding each of the two bearing arrangements.
  • vibration elements use is made e.g. of O-rings manufactured from silicone. This, however, gives rise to the problem that the heat dissipation effected via silicone O-rings will be merely poor.
  • Heat dissipation from the bearing is difficult to achieve particularly because the axial surfaces of the ball bearings used, which preferably are angular-contact ball bearings, are small and thus will contribute only little to heat dissipation.
  • the outer bearing rings are usually arranged at a distance from the shaft housing for allowing the axial bias to be realized. Consequently, heat dissipation in the radial direction will not be sufficient.
  • the bearings are operated at low pressures of usually 1 ⁇ 10 ⁇ 3 to 10 ⁇ 10 mbar, heat dissipation in the radial direction is extremely poor.
  • the vibration element serving for damping is designed and/or arranged to have a thermal conductivity of at least 0.3 W/mK.
  • the vibration element is located between the bearing ring and the shaft housing.
  • the vibration element surrounds the outer bearing ring and consequently is arranged between the outer bearing ring and the shaft housing.
  • the vibration element thus fulfills two functions, i.e. on the one hand, damping the movements of the bearing ring and, on the other hand, dissipating the heat from the bearing ring particularly into the shaft housing.
  • This inventive dual function of the vibration element makes it possible to realize a good heat dissipation from the bearing. Thereby, the operating life of the bearing is extended.
  • said at least one vibration element has a thermal conductivity of at least 0.35 W/mK and more preferably at least 0.4 W/mK.
  • the vibration element comprises an elastomeric material or is made of elastomeric material. Tests have shown that the material Elastosil R840 is especially well-suited for use in the realization of the invention.
  • the inventive thermal conductivity of the material is guaranteed not by admixture of particles such as e.g. metal or copper powder but, instead, by the elastomeric material itself.
  • the properties of the material are influenced particularly by the length and the structure of the macromolecules.
  • the material to be used comprises a silicone rubber mass.
  • vibration elements can be provided for each bearing arrangement.
  • two annular vibration elements are provided, surrounding the outer bearing ring so as to take up radial forces.
  • vibration elements preferably again of an annular shape—can be provided also in the axial direction.
  • the vibration elements which preferably are of a rectangular or circular cross-sectional shape, are respectively arranged in a groove.
  • said groove is arranged in the shaft housing, with the vibration element preferably extending beyond the groove so that there will always be a gap formed between the shaft housing and the bearing ring.
  • the vibration element preferably has a Shore A hardness of 40-80 Shore A.
  • the invention further relates to the use of a vibration element having a thermal conductivity of at least 0.3 W/mK in pump bearing arrangements.
  • the vibration element is preferably designed in the above described manner.
  • the FIGURE shows a schematic lateral view of an upper and respectively rotor-side bearing arrangement according to the invention.
  • FIG. 1 A preferred embodiment of the bearing arrangement 12 arranged in an upper position, i.e. facing toward a rotor 10 , is illustrated in the FIGURE.
  • Rotor 10 is connected to a rotor shaft 14 for common rotation therewith.
  • an inner bearing shell 16 of a grooved ball bearing Arranged on rotor shaft 14 for common rotation therewith is an inner bearing shell 16 of a grooved ball bearing, which is held in position by the rotor and the shaft stub 18 .
  • the upper bearing arrangement 12 is arranged in a shaft housing 20 which in the illustrated embodiment has a substantially cylindrical shape.
  • An outer bearing ring 22 is arranged internally of shaft housing 20 .
  • bearing bodies in the form of balls are arranged between said two bearing rings 16 , 22 .
  • outer bearing ring 22 is connected to shaft housing 20 by two radial vibration elements 26 formed as elastic O-rings. Further provided is an axial vibration element 28 , preferably also formed as an elastic O-ring. Said two radial vibration elements 26 are respectively arranged in an edge region of outer bearing ring 22 in a respective groove 30 . Said groove 30 is provided in shaft housing 20 . The depth of groove 30 is smaller than the diameter of said O-rings 26 so that the latter projects beyond an inner side 32 of shaft housing 20 and are located in abutment on outer bearing ring 22 .
  • the axial vibration element 28 is arranged in an axial annular groove 34 which also is provided in shaft housing 20 . Also here, the depth of groove 34 is smaller than the diameter of O-ring 28 so that the latter projects in the direction of outer bearing ring 22 .
  • a force transmission element 36 is provided between axial vibration element 28 and outer bearing ring 22 .
  • Said force transmission element 36 particularly has the function of a friction damper.
  • a further function of force transmission element 36 resides in allowing for movement of outer bearing ring 22 in the radial direction without causing shear forces or radial forces to act on axial vibration element 28 . At least, the corresponding forces that occur can be significantly reduced.
  • a venting bore 38 formed as a transverse bore can be provided.
  • the annular vibration elements 26 , 28 provided in the illustrated embodiment serve for heat dissipation from the bearing arrangement 12 .
  • the heat, generated especially by the rolling friction of the balls 24 is thus dissipated via outer bearing ring 22 as well as via vibration elements 26 , 28 into shaft housing 20 .
  • vibration elements 26 , 28 have a good thermal conductivity, preferably higher than 0.3 W/mK.
  • a further ball bearing is provided to support the lower end of rotor shaft 14 .
  • Said two bearings are tensioned for providing an axial bias in the longitudinal direction of rotor shaft 14 .

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Non-Positive Displacement Air Blowers (AREA)
  • Support Of The Bearing (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Vibration Prevention Devices (AREA)
  • Mounting Of Bearings Or Others (AREA)
US12/672,744 2007-08-10 2008-07-22 Pump bearing arrangement Abandoned US20110081231A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102007037792A DE102007037792A1 (de) 2007-08-10 2007-08-10 Pumpen-Lageranordnung
DE102007037792.6 2007-08-10
PCT/EP2008/059593 WO2009021809A2 (de) 2007-08-10 2008-07-22 Pumpen-lageranordnung

Publications (1)

Publication Number Publication Date
US20110081231A1 true US20110081231A1 (en) 2011-04-07

Family

ID=40227013

Family Applications (1)

Application Number Title Priority Date Filing Date
US12/672,744 Abandoned US20110081231A1 (en) 2007-08-10 2008-07-22 Pump bearing arrangement

Country Status (6)

Country Link
US (1) US20110081231A1 (ja)
EP (1) EP2174015B1 (ja)
JP (1) JP5384498B2 (ja)
CN (1) CN101809292A (ja)
DE (1) DE102007037792A1 (ja)
WO (1) WO2009021809A2 (ja)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20130071243A1 (en) * 2011-09-20 2013-03-21 Honeywell International Inc. Turbocharger rotating assembly
US20140033859A1 (en) * 2011-03-16 2014-02-06 Jonathan James Robert Hilton High speed flywheel
US20150132109A1 (en) * 2012-04-04 2015-05-14 Shimadzu Corporation Vacuum pump
US20150198084A1 (en) * 2014-01-16 2015-07-16 Bosch Mahle Turbo Systems Gmbh & Co. Kg Exhaust gas turbocharger
US9312736B2 (en) 2010-12-16 2016-04-12 Baumueller Nuernberg Gmbh Electric machine, in particular of a pump unit
US20160326998A1 (en) * 2015-05-06 2016-11-10 Borgwarner Inc. Apparatus for a charging system of an internal combustion engine
EP3115615A1 (en) * 2015-07-08 2017-01-11 Panasonic Intellectual Property Management Co., Ltd. Turbo machine
US20170096763A1 (en) * 2015-10-06 2017-04-06 New Motech Co., Ltd. Driving apparatus for washing machine
US9995342B2 (en) * 2015-11-23 2018-06-12 Cadventures, Inc. Self-adjusting bushing bearing with shaft seal
US10233968B2 (en) * 2015-06-04 2019-03-19 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Bearing device and supercharger
US20190301526A1 (en) * 2018-03-29 2019-10-03 Ge Global Sourcing Llc Bearing assembly and method
US11033915B2 (en) 2016-08-04 2021-06-15 Ntn Corporation Air turbine drive spindle
US11519419B2 (en) 2020-04-15 2022-12-06 Kin-Chung Ray Chiu Non-sealed vacuum pump with supersonically rotatable bladeless gas impingement surface
US20220389955A1 (en) * 2021-06-08 2022-12-08 Aktiebolaget Skf Non-locating bearing assembly
US20240240650A1 (en) * 2011-04-18 2024-07-18 Resmed Motor Technologies Inc. Pap system blower

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202010015593U1 (de) * 2010-11-17 2012-03-01 Oerlikon Leybold Vacuum Gmbh Pumpenlagerung
DE102010054828A1 (de) * 2010-12-16 2012-06-21 Thyssenkrupp Presta Ag Servolenkung mit Spindeltrieb
US8528917B2 (en) * 2011-02-03 2013-09-10 The Raymond Corporation Wheel support assembly for a vehicle
DE202011002794U1 (de) * 2011-02-16 2012-06-06 Oerlikon Leybold Vacuum Gmbh Lageranordnung für schnell drehende Wellen von Vakuumpumpen
KR101709809B1 (ko) * 2012-02-16 2017-02-23 한온시스템 주식회사 연료전지 차량용 공기 블로워
CN103644145B (zh) * 2013-12-04 2016-01-27 江苏大学 一种盘管冷却结构的热水循环泵悬架体
DE102014204608A1 (de) * 2014-03-12 2015-09-17 BSH Hausgeräte GmbH Staubsaugergebläse
DE102014213505B4 (de) * 2014-07-11 2022-05-12 Robert Bosch Gmbh Elektrozylinder, dessen Spindellagerung eine Stützvorrichtung mit einem querbeweglichem Drehlager aufweist
DE102014217794B4 (de) * 2014-09-05 2017-03-16 Robert Bosch Gmbh Feder zum Vorspannen eines Wälzlagers und Baugruppe mit der Feder und dem Wälzlager
JP6458414B2 (ja) * 2014-09-10 2019-01-30 株式会社島津製作所 真空ポンプ
KR102355646B1 (ko) * 2015-06-04 2022-01-27 엘지이노텍 주식회사 모터
CN106246741A (zh) * 2015-11-03 2016-12-21 无锡市三立轴承有限公司 自润滑冷却的轴承安装结构
CN106246740A (zh) * 2015-11-03 2016-12-21 无锡市三立轴承有限公司 轴承的自冷却安装结构
JP6638444B2 (ja) * 2016-02-09 2020-01-29 株式会社島津製作所 真空ポンプ
CN105799774A (zh) * 2016-05-11 2016-07-27 新乡艾迪威汽车科技有限公司 一种汽车转向器齿条支撑套结构
CN110685950B (zh) * 2019-11-13 2021-05-25 上海裕达实业有限公司 分子泵轴承结构
CN112324697B (zh) * 2020-11-20 2022-03-22 浙江海洋大学 一种具有可调节轴承压盖的化工流程泵
CN114215782A (zh) * 2021-12-08 2022-03-22 苏州中科科仪技术发展有限公司 磁悬浮分子泵的主轴结构及磁悬浮分子泵
US11649859B1 (en) * 2021-12-20 2023-05-16 Aktiebolaget Skf Vibration dampening for scanner bearing

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US6664683B1 (en) * 1999-01-29 2003-12-16 Ibiden Co., Ltd Motor and turbo-molecular pump
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US7534098B2 (en) * 2004-03-29 2009-05-19 Weir Minerals Australia, Ltd. Suction distribution and disconnection system for a submersible pump
US20100215475A1 (en) * 2005-06-10 2010-08-26 Barrie Dudley Brewster Vacuum Pump

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GB2415019A (en) * 2004-06-07 2005-12-14 Boc Group Plc A supporting arrangement for a roller bearing
EP1760319A4 (en) * 2004-06-25 2010-07-07 Osaka Vacuum Ltd BEARING SUPPORT STRUCTURE FOR TURBOMOLECULAR PUMP
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Publication number Priority date Publication date Assignee Title
US4695223A (en) * 1985-04-04 1987-09-22 Leybold-Heraeus Gmbh Turbomolecular vacuum pump with a rotor and at least one antifriction bearing
US4821860A (en) * 1986-06-28 1989-04-18 Automotive Products Plc Friction facing material and carrier assembly
US6664683B1 (en) * 1999-01-29 2003-12-16 Ibiden Co., Ltd Motor and turbo-molecular pump
US6709236B1 (en) * 1999-11-18 2004-03-23 Leybold Vakuum Gmbh High-speed turbo pump
US7534098B2 (en) * 2004-03-29 2009-05-19 Weir Minerals Australia, Ltd. Suction distribution and disconnection system for a submersible pump
US20100215475A1 (en) * 2005-06-10 2010-08-26 Barrie Dudley Brewster Vacuum Pump

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9312736B2 (en) 2010-12-16 2016-04-12 Baumueller Nuernberg Gmbh Electric machine, in particular of a pump unit
US9360082B2 (en) * 2011-03-16 2016-06-07 Flybird Automotive Limited High speed flywheel
US20140033859A1 (en) * 2011-03-16 2014-02-06 Jonathan James Robert Hilton High speed flywheel
US20240240650A1 (en) * 2011-04-18 2024-07-18 Resmed Motor Technologies Inc. Pap system blower
US8911202B2 (en) * 2011-09-20 2014-12-16 Honeywell International Inc. Turbocharger rotating assembly
US20130071243A1 (en) * 2011-09-20 2013-03-21 Honeywell International Inc. Turbocharger rotating assembly
US10590961B2 (en) * 2012-04-04 2020-03-17 Shimadzu Corporation Vacuum pump
US20150132109A1 (en) * 2012-04-04 2015-05-14 Shimadzu Corporation Vacuum pump
US9797304B2 (en) * 2014-01-16 2017-10-24 Bosch Mahle Turbo Systems Gmbh & Co. Kg Exhaust gas turbocharger
US20150198084A1 (en) * 2014-01-16 2015-07-16 Bosch Mahle Turbo Systems Gmbh & Co. Kg Exhaust gas turbocharger
US20160326998A1 (en) * 2015-05-06 2016-11-10 Borgwarner Inc. Apparatus for a charging system of an internal combustion engine
US10233968B2 (en) * 2015-06-04 2019-03-19 Mitsubishi Heavy Industries Engine & Turbocharger, Ltd. Bearing device and supercharger
EP3115615A1 (en) * 2015-07-08 2017-01-11 Panasonic Intellectual Property Management Co., Ltd. Turbo machine
US10570775B2 (en) 2015-07-08 2020-02-25 Panasonic Intellectual Property Management Co., Ltd. Turbo machine
US10662569B2 (en) * 2015-10-06 2020-05-26 New Motech Co., Ltd. Driving apparatus for washing machine
US20170096763A1 (en) * 2015-10-06 2017-04-06 New Motech Co., Ltd. Driving apparatus for washing machine
US9995342B2 (en) * 2015-11-23 2018-06-12 Cadventures, Inc. Self-adjusting bushing bearing with shaft seal
US11033915B2 (en) 2016-08-04 2021-06-15 Ntn Corporation Air turbine drive spindle
US10837487B2 (en) * 2018-03-29 2020-11-17 Transportation Ip Holdings, Llc Bearing assembly and method
US20190301526A1 (en) * 2018-03-29 2019-10-03 Ge Global Sourcing Llc Bearing assembly and method
US11519419B2 (en) 2020-04-15 2022-12-06 Kin-Chung Ray Chiu Non-sealed vacuum pump with supersonically rotatable bladeless gas impingement surface
US20220389955A1 (en) * 2021-06-08 2022-12-08 Aktiebolaget Skf Non-locating bearing assembly
US11835087B2 (en) * 2021-06-08 2023-12-05 Aktiebolaget Skf Non-locating bearing assembly

Also Published As

Publication number Publication date
JP2010535969A (ja) 2010-11-25
EP2174015A2 (de) 2010-04-14
JP5384498B2 (ja) 2014-01-08
WO2009021809A2 (de) 2009-02-19
CN101809292A (zh) 2010-08-18
DE102007037792A1 (de) 2009-02-12
EP2174015B1 (de) 2012-10-03
WO2009021809A3 (de) 2009-06-11

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