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US20090277167A1 - Method for regulating the maximum speed of a working machine and associated hydrodynamic coupling - Google Patents

Method for regulating the maximum speed of a working machine and associated hydrodynamic coupling Download PDF

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Publication number
US20090277167A1
US20090277167A1 US11/721,262 US72126205A US2009277167A1 US 20090277167 A1 US20090277167 A1 US 20090277167A1 US 72126205 A US72126205 A US 72126205A US 2009277167 A1 US2009277167 A1 US 2009277167A1
Authority
US
United States
Prior art keywords
working
working space
hydrodynamic coupling
impeller
port
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
US11/721,262
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English (en)
Inventor
Markus Kley
Kurt Adleff
Reinhold Pittius
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.)
Voith Turbo GmbH and Co KG
Original Assignee
Voith Turbo GmbH and Co KG
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 Voith Turbo GmbH and Co KG filed Critical Voith Turbo GmbH and Co KG
Assigned to VOITH TURBO GMBH & CO. KG reassignment VOITH TURBO GMBH & CO. KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ADLEFF, KURT, PITTIUS, REINHOLD, KLEY, MARKUS
Publication of US20090277167A1 publication Critical patent/US20090277167A1/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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type
    • F16D33/06—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit
    • F16D33/16—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit by means arranged externally of the coupling or clutch
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type
    • F16D33/06—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit
    • F16D33/08—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit by devices incorporated in the fluid coupling, with or without remote control
    • F16D33/10—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit by devices incorporated in the fluid coupling, with or without remote control consisting of controllable supply and discharge openings
    • 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
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D33/00—Rotary fluid couplings or clutches of the hydrokinetic type
    • F16D33/06—Rotary fluid couplings or clutches of the hydrokinetic type controlled by changing the amount of liquid in the working circuit

Definitions

  • the invention concerns a process to regulate the maximum rotation speed of a working machine, where the working machine is powered by a motor via a hydrodynamic coupling.
  • the invention concerns specifically a process to regulate the maximum rotation speed of an air compressor in a vehicle, where the compressor is powered by the motor of the vehicle, specifically an internal combustion engine, via a hydrodynamic coupling and is embodied, for example, as a reciprocating piston air compressor to supply the compressed air system of the vehicle.
  • the known adjustment of the fill level is complicated in terms of the apparatus required and requires various adjustment components, such as pressure sensors, valves and/or scoop tubes.
  • various adjustment components such as pressure sensors, valves and/or scoop tubes.
  • a hydrodynamic coupling in a vehicle advantageously in the drive train between air compressor and the motor of the vehicle, in order to be able to turn the air compressor on and off and simultaneously dampen the vibrations and avoid a transmission of torque from the air compressor to the vehicle motor or the transmission of the vehicle motor
  • the known design of fill-adjusted hydrodynamic couplings is too complicated and not optimally suited to the rotation speed control of the working machine, specifically the air compressor.
  • a further option to limit the maximum rotation speed of a vehicle air compressor would be to use the motor control to limit or lower the motor rotation speed.
  • the vehicle motor serves primarily to propel the vehicle, where the motor should operate to save energy to the extent possible, such a modification of the motor speed based on the parameters of the vehicle air pressure system is undesirable.
  • the invention is based on the objective to propose a process to adjust the maximum rotation speed of a working machine, which improves on the state of the arts, which is particularly reliable and which reduces the requirements for apparatus relative to known solutions.
  • a hydrodynamic coupling is to be proposed, which is suitable for use in such a process.
  • the process of the invention is intended to limit the maximum rotation speed of an air compressor in a vehicle, where the air compressor is embodied specifically as a reciprocating piston air compressor and is advantageously powered by the vehicle motor, specifically an internal combustion engine.
  • the invention is used specifically for an air compressor powered by the internal combustion engine of a motor vehicle, where the compressor supplies the vehicle compressed air system. Due to the wide range of rotation speeds of the motor and the requirement that the air compressor is powered at sufficiently high rotation speeds even at low motor speeds, normally the gear ratio of a transmission, which is situated in the drive train between the motor and the impeller of the hydrodynamic
  • the coupling is chosen high enough such that the working machine, i.e. the air compressor, is operated at a sufficiently high rotation speed, even if the motor and thus the output shaft of the transmission that drives the impeller operate at low rotation speeds. It needs to be noted here that there will be considerable slip between the impeller and the turbine wheel of the hydrodynamic coupling at a low rotation speed of the impeller of the hydrodynamic coupling, which means that the impeller will rotate at considerably higher speed that the turbine wheel. For example, the impeller rotates at last twice as fast as the turbine wheel. If now the current operating characteristics of the vehicle lead to a higher rotation speed of the motor, possibly doubling or tripling, the rotation speed of the impeller of the hydrodynamic coupling will increase in proportion.
  • the process of the invention or the coupling of the invention acts at this juncture as a regulator such that excessive speeds of the working machine, specifically the air compressor, which may be embodied as a reciprocating piston air compressor, will be prevented with certainty.
  • the process of the invention determines a suitable rotation speed in the shaft between the motor and the working machine. For example, this may be the rotation speed of the working machine, the output side of the hydrodynamic coupling, the input side of the hydrodynamic coupling and/or the rotation speed of the motor.
  • the rotation speed of the motor is defined here as the rotation speed of a suitable shaft of the motor or of a transmission powered by this motor, specifically the output side of the transmission, which drives the impeller of the hydrodynamic coupling directly or indirectly.
  • a maximum value is established and is set as the upper limit for the operating speed range of the working machine.
  • the current rotation speed of the working machine will be monitored continuously or in intervals and will be compared to the established maximum value. Once the monitored rotation speed exceeds the established maximum value, the amount of working medium in the working space of the hydrodynamic coupling is reduced automatically by actively opening an outlet connected to the working space or by suitably modifying the flow to the same.
  • the hydrodynamic coupling is embodied as a clutch, which means that it can be filled and emptied with working material in a controlled manner.
  • Filling is defined here as a complete or at least a partial filling.
  • Emptying includes in this invention a complete emptying or an emptying down to a specified remainder of working medium in the working space. This makes it feasible to transfer torque from the impeller to the turbine wheel in a first situation, namely when the working space is partially or completely filled, and to transfer no or essentially no torque from the impeller to the turbine wheel in a second situation, namely when the working space is completely empty or is emptied except for a specified remainder of medium.
  • a predetermined (small) amount of working medium is fed through the hydrodynamic coupling, even if the working machine is not powered, in order to cool the hydrodynamic coupling.
  • the hydrodynamic coupling will normally be emptied completely, because such cooling is often not needed.
  • the amount of working medium in the working area of the hydrodynamic coupling is automatically reduced in reaction to a signal of excessive rotation speed by automatically opening a centrifugally controlled valve, which is at least connected to the working space such that it conducts fluids or which opens into the working space.
  • this centrifugally controlled valve may rotate with the rotation speed of the impeller, and the centrifugal forces automatically open the valve after a pre-specified maximum rotation speed has been reached, such that working medium exits from the working space. Because the rotation speed of the turbine wheel thus will always be less than the trigger rotation speed of the centrifugally controlled valve in the impeller, a sure rotation speed check of the working machine, which is in a mechanical connection with the turbine wheel, can be achieved.
  • a hydrodynamic coupling according to the invention which may be used in the process of the invention, will thus have a centrifugally controlled valve that is included most advantageously in the impeller, that opens above a certain rotation speed and that permits the removal of working medium from the working space.
  • a second embodiment of the process of the invention may control the rotation speed without the assistance of a valve.
  • This embodiment of the invention is based on the insight that the meridian flow in the working space of the hydrodynamic coupling is modified by the rotation speed of the hydrodynamic coupling, specifically the impeller of the hydrodynamic coupling.
  • at least one port of at least one outlet is situated in the working space of the hydrodynamic coupling on the inner circumferential surface such that the meridian flow largely or fully moves past this port at low rotation speed of the impeller, specifically in the direction of the radial circumference, such that no or at worst very little working medium enters into the port and thus exits from the working space.
  • the meridian flow in the working space adjusts such that the port is in line with the tangential direction of the meridian flow, such that working medium is pressed into the port by the meridian flow and thus exits from the working space via the outlet.
  • low slip implies that the meridian flow is further to the outside of the paddle profile of impeller and turbine wheel, which means that the tangential direction on the radial inner circumference of the meridian flow in the working space moves radially to the outside, the working medium will flow directly into the port of this outlet, given the positioning described by the invention for this one or more outlets, which is precluded at lower rotation speeds by the fact that there is no or essentially no dynamic pressure of working medium into the port.
  • a hydrodynamic coupling of the invention which is suitable for use in the second embodiment of the process of the invention, has the port of an outlet on the inner circumference of its working space, where the port is situated in the second rising quadrant of the impeller.
  • This location specification derives from a theoretical subdivision of the circumference of the working space in an axial cross section through the hydrodynamic coupling into four quadrants, starting with the first quadrant on the radial interior of the impeller; then the second quadrant follows in the direction of the established meridian flow at the propulsion of the impeller on the radial exterior of the impeller.
  • the working medium then flows from the second quadrant into the third quadrant, which extends to the radial exterior of the turbine wheel and is subsequently slowed radially to the interior into the fourth quadrant, which extends to the radial interior of the turbine wheel.
  • Advantageous positions of at least one port in the second quadrant of the impeller are positions between 120 and 150 degrees, specifically between 130 and 140 degrees, preferably at exactly or roughly 135 degrees.
  • the degree specifications refer to the radian measure, viewed from the radial interior in the impeller, beginning in a manner of speaking at the foot of the working space in the impeller continuing in a circumferential direction radially to the exterior to the radial outer edge of the impeller, where 180 degrees are reached.
  • FIG. 1 three schematic operating conditions of a hydrodynamic coupling of the invention, starting with a low rotation speed and progressing to a medium rotation speed to a high rotation speed;
  • FIG. 2 an enlarged detail from FIG. 1 , where the port of the invention in the impeller can be seen;
  • FIG. 3 the rotation speed of an air compressor (compressor) relative to the rotation speed of the motor of the vehicle
  • FIG. 4 the associated diagram of the characteristic curve of the hydrodynamic coupling of the invention.
  • FIG. 1 depicts a schematic of hydrodynamic coupling 11 , which is part of the power transfer from motor 10 to working machine 12 .
  • Motor 10 includes here an internal combustion engine 10 . 1 with an associated transmission 10 . 2 .
  • An output shaft of transmission 10 . 2 is connected to the input side 11 . 1 of hydrodynamic coupling 11 , consisting of impeller 1 .
  • the output side 11 . 2 of the hydrodynamic coupling, consisting of turbine wheel 2 is connected to working machine 12 , which is an air compressor.
  • working machine 12 which is an air compressor.
  • FIG. 1 a depicts schematically the situation of hydrodynamic coupling 11 , where impeller 1 is powered by motor 10 at a relatively low rotation speed.
  • impeller 1 is powered by motor 10 at a relatively low rotation speed.
  • there will be considerable slip between impeller 1 and turbine wheel 2 for example, and a ratio of rotation speeds between motor 10 and the working machine 12 (the compressor) as is depicted on the left side of the graph shown in FIG. 3 .
  • FIG. 1 b depicts schematically the situation of the same hydrodynamic coupling 11 as is shown in FIG. 1 a, but at a higher rotation speed. There is a noticeable meridian flow within working space 3 , but this meridian flow still covers the entire inner surface of working space 3 , viewed in an axial cross section.
  • FIG. 1 c depicts the same coupling 11 at a high rotation speed, specifically a higher rotation speed than is depicted in FIG. 1 b. It is easy to see that the meridian flow in working space 3 has shifted radially towards the outside compared to the situation in FIG. 1 b, which means that the inner circumference of the meridian flow in working space 3 has migrated radially towards the outside. Viewed in an axial cross section through working space 3 , the resulting meridian flow 5 has a tangential flow to its inner circumference that points directly into the port of outlet 6 , such that the resulting dynamic pressure presses the working medium into the port of outlet 6 and thus through outlet 6 .
  • FIG. 2 shows an enlarged detail of working space 3 in the area of impeller 1 . It is easy to see that there is a protuberance on the inner circumference of working space 3 in impeller 1 just ahead of port 6 . 1 of outlet 6 viewed in a radial direction, which extends radially into the interior of working space 3 .
  • This protuberance 7 which has the shape of a ramp, has the function of ensuring that no or essentially no working medium exits through outlet 6 at rotation speeds below the maximum permissible rotation speed of the impeller, but rather to ensure that meridian flow 5 flows across port 6 . 1 in the radial circumference direction.
  • working space 3 can be sectioned into quadrants in the depicted axial cross section through working space 3 , of which the first quadrant I and the second quadrant II divide the area of working space 3 , which is located in impeller 1 , into two equal parts.
  • the first quadrant I is here radially within the second quadrant II, where the two quadrants I, II are mirror images of each other on a mirror plane parallel to the axis.
  • port 6 . 1 of outlet 6 is roughly or precisely in the center of the arc that forms the inner surface of the outer circumference of working space 3 in the second quadrant II. Expressed in degrees, this means that port 6 . 1 will be located at roughly 135 degrees, namely in the center between the radial inner start of the second quadrant II at 90 degrees and the radial outer end of quadrant II at 180 degrees.
  • FIG. 4 shows that the Lambda value, which is also known as the coefficient of performance of hydrodynamic couplings, decreases at increasing rotation speeds of the impeller or the turbine wheel, where the rotation speed of the turbine wheel is a function of the rotation speed of the impeller and the slip of the hydrodynamic coupling. At a slip of just below 10 percent, which means that the turbine wheel runs with a rotation speed that is one-tenth of the rotation speed of the impeller, the characteristic curve breaks down and there is no additional reduction of slip.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Control Of Fluid Gearings (AREA)
US11/721,262 2004-12-10 2005-12-08 Method for regulating the maximum speed of a working machine and associated hydrodynamic coupling Abandoned US20090277167A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102004059833A DE102004059833A1 (de) 2004-12-10 2004-12-10 Verfahren zum Regeln der maximalen Drehzahl einer Arbeitsmaschine und hydrodynamische Kupplung hierfür
DE102004059833.9 2004-12-10
PCT/EP2005/013149 WO2006061221A1 (de) 2004-12-10 2005-12-08 Verfahren zum regeln der maximalen drehzahl einer arbeitsmaschine und hydrodynamische kupplung hierfür

Publications (1)

Publication Number Publication Date
US20090277167A1 true US20090277167A1 (en) 2009-11-12

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US11/721,262 Abandoned US20090277167A1 (en) 2004-12-10 2005-12-08 Method for regulating the maximum speed of a working machine and associated hydrodynamic coupling
US11/721,231 Expired - Fee Related US7681391B2 (en) 2004-12-10 2005-12-12 Hydrodynamic coupling

Family Applications After (1)

Application Number Title Priority Date Filing Date
US11/721,231 Expired - Fee Related US7681391B2 (en) 2004-12-10 2005-12-12 Hydrodynamic coupling

Country Status (8)

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US (2) US20090277167A1 (de)
EP (2) EP1819932B1 (de)
JP (2) JP2008523332A (de)
KR (2) KR20070085658A (de)
CN (1) CN101099049A (de)
DE (3) DE102004059833A1 (de)
RU (2) RU2007125975A (de)
WO (2) WO2006061221A1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110081257A1 (en) * 2008-05-30 2011-04-07 Voith Patent Gmbh Drivetrain and method for providing a supply to a compressed air system
US20140075935A1 (en) * 2011-03-02 2014-03-20 Voith Patent Gmbh Turbo-compound system, in particular of a motor vehicle

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KR100885549B1 (ko) * 2007-06-14 2009-02-26 최쌍석 물을 작동매체로 사용하는 가변속 구동장치
DE102008034976B3 (de) * 2008-07-25 2010-02-11 Voith Patent Gmbh Hydrodynamische Maschine, insbesondere hydrodynamische Kupplung
RU2478802C2 (ru) * 2008-10-30 2013-04-10 Вольво Ластвагнар Аб Способ автоматической регулировки способности турбокомпаундной трансмиссии передавать крутящий момент
DE102009055975A1 (de) * 2009-11-27 2011-06-01 Voith Patent Gmbh Kühlsystem, insbesondere eines Kraftfahrzeugs
DE102010012965A1 (de) * 2010-03-25 2011-09-29 Voith Patent Gmbh Antriebsstrang für ein Kraftfahrzeug
DE102010022849B4 (de) * 2010-06-07 2012-05-03 Voith Patent Gmbh Kompressionsvorrichtung und Verfahren zum Kühlen eines Kompressionsmediums
FR2964714B1 (fr) * 2010-09-13 2012-08-31 Renault Sas Procede de changement de rapports montant pour boite de vitesses automatique d'un vehicule automobile
DE102011116268A1 (de) * 2011-10-19 2013-04-25 Wirtgen Gmbh Selbstfahrende Baumaschine
DE102014201634B4 (de) * 2014-01-30 2022-10-27 Orcan Energy Ag Antriebsstrang und Verfahren zum Betreiben eines solchen
DE102014107126A1 (de) 2014-05-20 2015-11-26 Harald Wenzel Mehrstufige Verdichteranlage zur Erzeugung eines komprimierten Gase
DE102015226519B4 (de) 2015-12-22 2024-11-14 Schaeffler Technologies AG & Co. KG Kupplungseinrichtung und Doppelkupplung
KR101963493B1 (ko) * 2017-03-14 2019-03-28 브이에스이앤지(주) 펌프용 무전원 기계식 속도 제어장치가 내장된 유체 커플링 장치
JP7002986B2 (ja) * 2018-04-16 2022-01-20 本田技研工業株式会社 車両用トルクコンバータ
CN109185182A (zh) * 2018-09-11 2019-01-11 重庆冲能动力机械有限公司 一种能快速响应变速的离心叶轮机械
KR102187184B1 (ko) * 2018-12-27 2020-12-04 주식회사 기원솔루텍 크러셔용 유체 클러치의 오일 순간 배출장치
KR102529960B1 (ko) * 2021-06-04 2023-05-04 재단법인 중소조선연구원 선박용 엔진 구동 시스템

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US3020719A (en) * 1956-06-25 1962-02-13 Voith Gmbh J M Variable slip fluid coupling
US3116608A (en) * 1958-04-07 1964-01-07 Gen Motors Corp Transmission
US3955368A (en) * 1974-03-06 1976-05-11 Cluaran Associates Ltd. Hydraulic coupling with controllable power transmission capacity
US4073139A (en) * 1976-03-04 1978-02-14 Voith Getriebe Kg Hydrodynamic coupling
US5251441A (en) * 1991-03-13 1993-10-12 Sime Industrie Fluid coupling
US5729978A (en) * 1994-08-23 1998-03-24 Mercedes-Benz Ag Supercharged internal combustion engine with capability for mechanical step-up drive of an exhaust gas turbocharger
US6101810A (en) * 1996-04-12 2000-08-15 Voith Turbo Gmbh & Co. Hydrodynamic coupling having constant quantity of working fluid and valve for displacing working fluid between a working space and a storage space
US6357229B1 (en) * 1997-01-22 2002-03-19 Voith Turbo Gmbh & Co., Kg Hydrodynamic clutch and method of operating a hydrodynamic clutch

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US2873831A (en) * 1952-02-04 1959-02-17 Sinclair Harold Power transmission systems embodying hydraulic turbo-transmitters
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3020719A (en) * 1956-06-25 1962-02-13 Voith Gmbh J M Variable slip fluid coupling
US3116608A (en) * 1958-04-07 1964-01-07 Gen Motors Corp Transmission
US3955368A (en) * 1974-03-06 1976-05-11 Cluaran Associates Ltd. Hydraulic coupling with controllable power transmission capacity
US4073139A (en) * 1976-03-04 1978-02-14 Voith Getriebe Kg Hydrodynamic coupling
US5251441A (en) * 1991-03-13 1993-10-12 Sime Industrie Fluid coupling
US5729978A (en) * 1994-08-23 1998-03-24 Mercedes-Benz Ag Supercharged internal combustion engine with capability for mechanical step-up drive of an exhaust gas turbocharger
US6101810A (en) * 1996-04-12 2000-08-15 Voith Turbo Gmbh & Co. Hydrodynamic coupling having constant quantity of working fluid and valve for displacing working fluid between a working space and a storage space
US6357229B1 (en) * 1997-01-22 2002-03-19 Voith Turbo Gmbh & Co., Kg Hydrodynamic clutch and method of operating a hydrodynamic clutch

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20110081257A1 (en) * 2008-05-30 2011-04-07 Voith Patent Gmbh Drivetrain and method for providing a supply to a compressed air system
US20140075935A1 (en) * 2011-03-02 2014-03-20 Voith Patent Gmbh Turbo-compound system, in particular of a motor vehicle

Also Published As

Publication number Publication date
EP1819932A1 (de) 2007-08-22
CN101099049A (zh) 2008-01-02
DE102004059833A1 (de) 2006-06-14
JP2008523332A (ja) 2008-07-03
EP1819932B1 (de) 2010-02-10
RU2007125975A (ru) 2009-01-20
KR20070084546A (ko) 2007-08-24
DE502005009007D1 (de) 2010-03-25
JP2008523333A (ja) 2008-07-03
WO2006061221A1 (de) 2006-06-15
DE502005003359D1 (de) 2008-04-30
EP1778996A1 (de) 2007-05-02
WO2006061252A1 (de) 2006-06-15
EP1778996B1 (de) 2008-03-19
KR20070085658A (ko) 2007-08-27
US20080209901A1 (en) 2008-09-04
RU2007125972A (ru) 2009-01-20
US7681391B2 (en) 2010-03-23

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