US20080008606A1 - Axially Driven Piston/Cylinder Unit - Google Patents

Axially Driven Piston/Cylinder Unit Download PDF

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Publication number
US20080008606A1
US20080008606A1 US11/794,026 US79402605A US2008008606A1 US 20080008606 A1 US20080008606 A1 US 20080008606A1 US 79402605 A US79402605 A US 79402605A US 2008008606 A1 US2008008606 A1 US 2008008606A1
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US
United States
Prior art keywords
piston
cylinder
cylinder unit
unit according
axially driven
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
US11/794,026
Other languages
English (en)
Inventor
Michael Muth
Georg Slotta
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.)
BSH Hausgeraete GmbH
Original Assignee
Aerolas GmbH
BSH Bosch und Siemens Hausgeraete 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 Aerolas GmbH, BSH Bosch und Siemens Hausgeraete GmbH filed Critical Aerolas GmbH
Assigned to AEROLAS GMBH, BSH BOSCH UND SIEMENS HAUSGERATE GMBH reassignment AEROLAS GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: MUTH, MICHAEL, SLOTTA, GEORG
Publication of US20080008606A1 publication Critical patent/US20080008606A1/en
Assigned to BSH BOSCH UND SIEMENS HAUSGERAETE GMBH reassignment BSH BOSCH UND SIEMENS HAUSGERAETE GMBH ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: AEROLAS GMBH
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B71/00—Free-piston engines; Engines without rotary main shaft
    • F02B71/04—Adaptations of such engines for special use; Combinations of such engines with apparatus driven thereby
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F04B35/04—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric
    • F04B35/045—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for the means being electric using solenoids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B35/00—Piston pumps specially adapted for elastic fluids and characterised by the driving means to their working members, or by combination with, or adaptation to, specific driving engines or motors, not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B53/00—Component parts, details or accessories not provided for in, or of interest apart from, groups F04B1/00 - F04B23/00 or F04B39/00 - F04B47/00
    • F04B53/14—Pistons, piston-rods or piston-rod connections
    • F04B53/144—Adaptation of piston-rods
    • F04B53/146—Piston-rod guiding arrangements
    • 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
    • F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings

Definitions

  • the invention relates to an axially driven piston-cylinder unit and compressors comprising the same.
  • Such a piston-cylinder unit is disclosed in U.S. Pat. No. 5,525,845.
  • This piston-cylinder unit of prior art comprises a piston driven by a linear drive, the piston being connected to the linear drive by means of a piston rod.
  • This piston rod is rigid in the axial direction and is flexible in the lateral direction, i.e. in the radial direction.
  • This design of the piston rod is intended to ensure that the piston is guided free from friction in the air bearing of the cylinder even when the drive axis does not run parallel with the cylinder axis.
  • This unspecific flexible design of the piston rod may, however, lead to a situation where transverse forces act on the piston causing the piston to tilt in the cylinder or giving rise to a lateral offset of the piston axis relative to the cylinder axis.
  • the object of this invention is to further develop a generic piston-cylinder unit so that reliable operation of the fluid bearing, and hence reliable guidance of the piston in the cylinder, is guaranteed even when there is a lateral offset between the drive axis and the piston axis or where there is an inclination of both these axes relative to each other.
  • the second piston-side joint is preferably provided in the direction of the longitudinal axis of the piston at a point which lies level with the rear region of the piston-side bearing surface. This guarantees that any transverse forces introduced by the piston rod into the piston are directly supported at this point in the piston-side bearing surface on the fluid bearing.
  • Each joint section is preferably pivotable about at least one axis. However, it is also preferable for each joint section to be pivotable about two axes which are orthogonal to each other.
  • a particularly preferred design comprises joint sections which move in the manner of a ball and socket joint. This ensures that any offset relative to the radial direction between the drive axis and the cylinder axis can be compensated for without special alignment of the piston in the circumferential direction.
  • the fluid bearing preferably has a plurality of outlet nozzles for the fluid provided in the inner circumferential wall of the cylinder.
  • outlet nozzles are arranged, in a particularly preferred embodiment, so that when the piston is in its second piston position, first outlet nozzles supply the front region of the piston-side bearing surface relative to the longitudinal extension of the piston, and second discharge nozzles supply the central or rear region of the piston-side bearing surface relative to the longitudinal piston extension, with pressure fluid.
  • outlet nozzles are provided in the front and rear regions of the piston-side bearing surface, an extremely uniform support of the piston over its longitudinal extension is achieved in the compression position of the piston.
  • first outlet nozzles to be provided in the front region and the second outlet nozzles to be provided in the central region, whereby the centre of gravity of the bearings extends forwards, i.e. towards the piston crown.
  • outlet nozzle are arranged so that when the piston is in its first piston position, the second outlet nozzles supply the front region of the piston-side bearing surface relative to the longitudinal piston extension with pressure fluid, and third outlet nozzles supply the rear region of the piston-side bearing surface relative to the longitudinal piston extension with pressure fluid.
  • third outlet nozzles in the rear region can provide improved support of the piston in its retracted position, particularly during the action of a transverse force.
  • the fluid bearing prefferably be formed by a gas pressure bearing, the outlet nozzles being formed by gas outlet nozzles; an advantageous and particularly preferred embodiment is that of an air bearing.
  • a plurality of outlet nozzles preferably form nozzle devices.
  • the nozzle devices are preferably arranged annularly about the cylinder axis, preferably separated from each other in the axial direction of the piston-cylinder unit. As a result of this an extremely uniform fluid or gas cushion is developed between the piston and the cylinder.
  • each nozzle ring For the formation of an extremely uniform fluid or gas cushion between the piston and the cylinder it is also advantageous for each nozzle ring to have a plurality of outlet nozzles uniformly separated from each other in the circumferential direction.
  • the outlet nozzles are preferably formed by micro holes drilled by means of an energy-rich jet, which bores are preferably of a conical design, their narrowest cross-section being located on the opening into the cylinder-side bearing surface.
  • the micro holes produced in this manner generate a fluid or gas cushion of high uniformity and high load carrying capacity.
  • micro holes are preferably drilled by means of a laser jet.
  • the pressure fluid for supplying the outlet nozzles is derived from a fluid flow generated by compression of the cylinder volume, from the outlet duct, for example, a simple structure of the piston-cylinder unit can be achieved and at the same time an additional pressure generator for the pressure fluid for supplying the outlet nozzles may be dispensed with, thereby contributing to low cost production of such a piston-cylinder unit.
  • This piston-cylinder unit is particularly preferred when the piston is loaded by a moving part of a linear drive for the back and forth drive movement.
  • a particularly noteworthy and advantageous application of the piston-cylinder unit according to the invention takes place in a compressor for generating a pressure fluid, preferably in a linear compressor driven by a linear motor.
  • FIG. 1 shows a piston-cylinder unit according to the invention with the piston in a retracted position
  • FIG. 2 shows the same piston-cylinder unit with the piston in the vicinity of the compression position.
  • FIG. 1 shows a longitudinal section through a piston-cylinder unit 1 with a cylinder 2 and a piston 3 .
  • Cylinder 2 is provided with a cylinder bore 10 in which piston 3 is accommodated so that it can be displaced back and forth in the direction of the longitudinal axis X of cylinder bore 10 and is freely guided.
  • the head-side end wall 12 of cylinder bore, formed on a cylinder head 23 , inner circumferential wall 14 of cylinder bore 10 and piston crown 16 delimit cylinder volume 18 .
  • An inlet duct 22 provided with a valve 20 shown diagrammatically, opens into head-side end wall 12 of cylinder bore 10 .
  • an outlet duct 24 which has a corresponding valve 26 ; this outlet duct also opens into cylinder bore 10 .
  • Piston-cylinder unit 1 shown is part of a piston working machine in which the expelled fluid is gaseous, as is the case with a compressor. In principle, however, the invention may also be used in other piston working machines such as pumps.
  • annular ducts 30 , 32 , 34 are separated from each other in the direction of longitudinal axis X of cylinder bore 10 .
  • Each of annular ducts 30 , 32 , 34 is provided with a multiplicity of micro holes 30 ′, 32 ′, 34 ′ which, distributed uniformly around the circumference of cylinder bore 10 , connect each annular duct 30 , 32 , 34 to the inside of cylinder bore 10 and in doing so penetrate inner wall 14 of the cylinder.
  • Micro holes 30 ′, 32 ′, 34 ′ of each annular duct 30 , 23 , 34 therefore form a corresponding annular nozzle arrangement 30 ′′, 32 ′′, 34 ′′.
  • Compressed gas which is conveyed through connecting duct 28 into annular ducts 30 , 32 , 34 can therefore escape through micro holes 30 ′, 32 ′, 34 ′ and form a gas cushion laterally supporting the piston between a cylinder-side bearing surface 15 on the inner circumferential wall 14 of cylinder 2 and a piston-side bearing surface 38 on the outer circumferential wall 36 of piston 3 .
  • First annular duct 30 with micro holes 30 ′ assigned to it, is located in a region in which the piston only covers micro holes 30 ′ when it is in the vicinity of the compression position, i.e. when cylinder volume 18 is minimised, as shown in FIG. 2 .
  • piston 3 covers the front, first micro holes 30 ′ with bearing surface 38 in front region 3 ′′.
  • micro holes 30 ′ do not contribute to the formation of a gas cushion between inner circumferential wall 14 of cylinder 2 and outer circumferential wall 36 of the piston. Because of the extremely small cross-section of micro holes 30 ′, however, the pressure loss that therefore occurs is not serious. However, a valve arrangement (not shown). which loads first annular duct 30 with compressed gas when piston 3 covers micro holes 30 ′, may also be provided.
  • Second annular duct 32 is arranged so that micro holes 32 ′ assigned to it are always covered by piston 3 , so that micro holes 32 ′ contribute to the formation of the gas cushion between inner circumferential wall 14 of cylinder 2 and outer circumferential wall 36 of piston 3 throughout the axial path of movement of piston 3 .
  • Third annular duct 34 is furthest away from head-side end wall 12 of cylinder bore 10 .
  • Micro holes 34 ′, assigned to third annular duct 34 are therefore not covered by piston 3 , i.e. by bearing surface 38 in rear region 3 ′ of the piston, until piston 3 is located in the region of its retracted position in which cylinder volume 18 is at a maximum.
  • the provision of third annular channel 34 with micro holes 34 ′ assigned to it is optional and only serves to improve the running properties of piston 3 in cylinder bore 10 .
  • annular nozzle arrangements in inner wall 14 of cylinder bore 10 may be provided between annular ducts 30 , 32 , 34 with micro holes 30 ′, 32 ′, 34 ′ assigned to them, which holes each form the annular nozzle devices 30 ′′, 32 ′′, 34 ′′.
  • Piston 3 is driven by drive element 50 of a linear drive 5 that is longitudinally displaceable back and forth along an axis Y, in a vibrating manner, which drive is only represented diagrammatically in the figure.
  • Moving drive element 50 is connected mechanically to piston 3 by means of a piston rod 4 .
  • Piston rod 4 is non-elastic in the axial direction and is therefore capable of transmitting axial forces from drive element 50 to piston 3 . This force transmission presents no problems if longitudinal axis Y of drive element 50 and longitudinal axis X′ of piston 3 and longitudinal axis X of cylinder 2 are identical.
  • longitudinal axis X of drive element 50 can be inclined to longitudinal axis X of cylinder 2 or offset parallel with it.
  • axis X′ of piston 3 is not aligned exactly with axis X of cylinder 2 either, so that according to the state of the art piston 3 is positioned slightly obliquely in cylinder 2 , thus giving rise to contact between the piston and cylinder, which under certain circumstances cannot even be supported by gas pressure bearing.
  • piston rod 4 is provided with a first drive-side joint section 40 and a second piston-side joint section 42 .
  • these joint sections 40 , 42 are designed as sections with a diameter that is reduced relative to the remaining piston rod sections. Piston rod 4 is therefore more flexible in joint sections 40 , 42 than in the remaining piston rod sections, with the result that they are able to be bent into joint sections 40 , 42 .
  • piston rod 4 compensates for the angular offset of these two axes relative to each other or the lateral offset of these two axes relative to each other, denoted in the figures by d, which means that longitudinal axis X′ of piston 3 is aligned essentially with axis X of the cylinder.
  • d longitudinal axis X′ of piston 3 is aligned essentially with axis X of the cylinder.
  • small transverse forces are introduced into the piston, which forces act essentially perpendicularly to axis X′ of piston 3 and can be supported by the gas cushion formed between cylinder-side bearing surface 15 and piston-side bearing surface 38 .
  • Piston-side joint section 42 of piston rod 4 is arranged in rear region 3 ′ of piston 3 .
  • the rear region is here defined as the region facing away from piston crown 16 with respect to a central plane M situated orthogonally on piston-side bearing surface 38 .
  • Front piston region 3 ′′ is therefore that region between central plane M and the front, piston-crown-side end of piston 3 .
  • the design of the axially driven piston-cylinder unit according to the invention provides improved guidance of piston 3 in cylinder 2 due to the special position of piston-side joint section 42 in rear piston region 3 ′, and results in a high degree of operational reliability.
  • the front, first nozzle arrangement 30 ′′ reinforces this higher degree of reliability by strengthening the gas cushion formed by the fluid bearing at this point in the compressed condition of the piston-cylinder unit.
  • the invention is not limited to the above exemplary embodiment, which serves merely as a general explanation of the core concept of the invention.
  • the device according to the invention may instead assume embodiments other than those described above.
  • the device may, in particular, have features which represent a combination of the individual features described in the claims.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Actuator (AREA)
  • Compressor (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)
  • Radiation-Therapy Devices (AREA)
  • Fluid-Damping Devices (AREA)
  • Chairs Characterized By Structure (AREA)
  • Braking Systems And Boosters (AREA)
  • Reciprocating Pumps (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
US11/794,026 2004-12-22 2005-12-22 Axially Driven Piston/Cylinder Unit Abandoned US20080008606A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102004061941.7A DE102004061941B4 (de) 2004-12-22 2004-12-22 Axial angetriebene Kolben-Zylinder-Einheit
DE102004061941.7 2004-12-22
PCT/EP2005/013865 WO2006069731A1 (de) 2004-12-22 2005-12-22 Axial angetriebene kolben-zylinder-einheit

Publications (1)

Publication Number Publication Date
US20080008606A1 true US20080008606A1 (en) 2008-01-10

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Application Number Title Priority Date Filing Date
US11/794,026 Abandoned US20080008606A1 (en) 2004-12-22 2005-12-22 Axially Driven Piston/Cylinder Unit

Country Status (11)

Country Link
US (1) US20080008606A1 (ja)
EP (1) EP1831517B1 (ja)
JP (1) JP2008524505A (ja)
KR (1) KR20070098813A (ja)
CN (1) CN100559020C (ja)
AT (1) ATE406511T1 (ja)
DE (2) DE102004061941B4 (ja)
ES (1) ES2312047T3 (ja)
PL (1) PL1831517T3 (ja)
RU (1) RU2365784C2 (ja)
WO (1) WO2006069731A1 (ja)

Cited By (14)

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US20080240950A1 (en) * 2003-05-30 2008-10-02 Mcgill Ian Campbell Compressor improvements
US20100098356A1 (en) * 2006-11-07 2010-04-22 BSH Bosch und Siemens Hausgeräte GmbH Gas thrust bearing and associated production method
US20120316479A1 (en) * 2011-06-10 2012-12-13 Tyco Healthcare Group Lp Compression device having a pause feature
CN104040177A (zh) * 2011-11-16 2014-09-10 惠而浦股份公司 空气静压线性压缩器的活塞汽缸装置
EP2848810A1 (en) * 2013-09-16 2015-03-18 Lg Electronics Inc. Reciprocating compressor
US20150192117A1 (en) * 2013-08-13 2015-07-09 Bill P. BRIDGES Well Service Pump System
US20150377531A1 (en) * 2014-06-26 2015-12-31 Lg Electronics Inc. Linear compressor and refrigerator including a linear compressor
US9845797B2 (en) 2012-09-03 2017-12-19 Lg Electronics Inc. Reciprocating compressor and method for driving same
CN108397369A (zh) * 2016-07-21 2018-08-14 陕西仙童科技有限公司 一种无油润滑线性压缩机及气体压缩的方法
US10267299B2 (en) * 2016-03-30 2019-04-23 Kabushiki Kaisha Toyota Jidoshokki Double-headed piston type swash plate compressor
CN110701189A (zh) * 2019-09-23 2020-01-17 浙江大学 采用轴向非均匀排布的气体润滑方法及应用
EP3805560A1 (en) * 2019-10-08 2021-04-14 LG Electronics Inc. Linear compressor
US11415127B2 (en) 2018-04-27 2022-08-16 Ameriforge Group Inc. Well service pump system structural joint housing having a first connector and a second connector each including one or more lands and grooves that are configured to mate with corresponding lands and grooves in an end cylinder housing and a ram cylinder housing
US11852133B2 (en) 2018-04-27 2023-12-26 Ameriforge Group Inc. Well service pump power system and methods

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Publication number Priority date Publication date Assignee Title
DE102012104163B3 (de) * 2012-05-11 2013-08-08 AeroLas GmbH Aerostatische Lager- Lasertechnik Kolben-Zylinder-Einheit
DE102012104164B9 (de) * 2012-05-11 2013-10-24 AeroLas GmbH Aerostatische Lager- Lasertechnik Kolben-Zylinder-Einheit
DE102012104165B3 (de) * 2012-05-11 2013-08-08 AeroLas GmbH Aerostatische Lager- Lasertechnik Kolben-Zylinder-Einheit
KR102003442B1 (ko) 2012-05-11 2019-07-24 에어로라스 게엠베하, 에어로슈타티쉐 라거- 레이저테크닉 피스톤-실린더 유닛
EP2700816B1 (en) 2012-08-24 2016-09-28 LG Electronics Inc. Reciprocating compressor
KR102087140B1 (ko) * 2013-09-16 2020-03-10 엘지전자 주식회사 왕복동식 압축기
GB2523570A (en) * 2014-02-27 2015-09-02 Agilent Technologies Inc Rigid piston-actuator-assembly supported for performing a pendulum-type tolerance compensation motion
KR102234726B1 (ko) * 2014-06-24 2021-04-02 엘지전자 주식회사 리니어 압축기
KR102178051B1 (ko) * 2014-06-24 2020-11-12 엘지전자 주식회사 리니어 압축기 및 그 제조방법
KR102306857B1 (ko) * 2014-06-24 2021-09-30 엘지전자 주식회사 리니어 압축기
CN105464943A (zh) * 2016-01-22 2016-04-06 珠海格力节能环保制冷技术研究中心有限公司 一种活塞驱动杆、活塞缸组件和压缩机
KR102276365B1 (ko) * 2017-03-21 2021-07-12 대우조선해양 주식회사 왕복동 기체 압축장치 및 방법
KR102453003B1 (ko) * 2017-12-29 2022-10-11 대우조선해양 주식회사 더블타입 오일 프리 왕복동 압축장치 및 방법
KR102075974B1 (ko) * 2018-08-20 2020-02-11 대우조선해양 주식회사 다단 싱글타입 오일 프리 왕복동 압축장치
DE102020114948A1 (de) 2020-06-05 2021-12-09 Aerolas Gmbh, Aerostatische Lager- Lasertechnik Linearkompressor
CN117231467A (zh) * 2023-11-13 2023-12-15 瑞纳智能设备股份有限公司 压缩机

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US2436908A (en) * 1943-02-03 1948-03-02 Hartford Nat Bank & Trust Co Flexible connecting rod
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US3382812A (en) * 1966-09-27 1968-05-14 Gorman Rupp Ind Inc Variable positive displacement pump
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US4569248A (en) * 1983-10-18 1986-02-11 Storage Technology Partners Coupling arm for transmitting linear motion
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CN104040177A (zh) * 2011-11-16 2014-09-10 惠而浦股份公司 空气静压线性压缩器的活塞汽缸装置
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CN101091043A (zh) 2007-12-19
RU2365784C2 (ru) 2009-08-27
DE102004061941B4 (de) 2014-02-13
KR20070098813A (ko) 2007-10-05
CN100559020C (zh) 2009-11-11
DE102004061941A1 (de) 2006-07-06
PL1831517T3 (pl) 2009-02-27
EP1831517B1 (de) 2008-08-27
WO2006069731A1 (de) 2006-07-06
ATE406511T1 (de) 2008-09-15
EP1831517A1 (de) 2007-09-12
JP2008524505A (ja) 2008-07-10
ES2312047T3 (es) 2009-02-16
RU2007121328A (ru) 2009-01-27

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