WO2006094693A2 - Proportional-druckregelventil mit drucksprung in seiner p/l-kennlinie - Google Patents

Proportional-druckregelventil mit drucksprung in seiner p/l-kennlinie Download PDF

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Publication number
WO2006094693A2
WO2006094693A2 PCT/EP2006/001881 EP2006001881W WO2006094693A2 WO 2006094693 A2 WO2006094693 A2 WO 2006094693A2 EP 2006001881 W EP2006001881 W EP 2006001881W WO 2006094693 A2 WO2006094693 A2 WO 2006094693A2
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
characteristic
closing
diameter
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.)
Ceased
Application number
PCT/EP2006/001881
Other languages
German (de)
English (en)
French (fr)
Other versions
WO2006094693A3 (de
Inventor
Karlheinz Mayr
Thilo Schmidt
Markus Moosmann
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.)
ZF Friedrichshafen AG
Original Assignee
ZF Friedrichshafen 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 ZF Friedrichshafen AG filed Critical ZF Friedrichshafen AG
Priority to CN2006800077115A priority Critical patent/CN101137946B/zh
Priority to KR1020077022900A priority patent/KR101249226B1/ko
Priority to JP2008500093A priority patent/JP4914887B2/ja
Priority to EP20060707358 priority patent/EP1856587B1/de
Priority to US11/908,003 priority patent/US7905249B2/en
Publication of WO2006094693A2 publication Critical patent/WO2006094693A2/de
Publication of WO2006094693A3 publication Critical patent/WO2006094693A3/de
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/20—Control of fluid pressure characterised by the use of electric means
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0686—Braking, pressure equilibration, shock absorbing
    • F16K31/0689—Braking of the valve element
    • 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
    • F16H61/0251—Elements specially adapted for electric control units, e.g. valves for converting electrical signals to fluid signals
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/0624—Lift valves
    • F16K31/0634—Lift valves with fixed seats positioned between movable valve members
    • F16K31/0637—Lift valves with fixed seats positioned between movable valve members with ball shaped valve members
    • 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
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0686—Braking, pressure equilibration, shock absorbing
    • F16K31/0693—Pressure equilibration of the armature
    • G—PHYSICS
    • G05—CONTROLLING; REGULATING
    • G05D—SYSTEMS FOR CONTROLLING OR REGULATING NON-ELECTRIC VARIABLES
    • G05D16/00—Control of fluid pressure
    • G05D16/20—Control of fluid pressure characterised by the use of electric means
    • G05D16/2006—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means
    • G05D16/2013—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means
    • G05D16/2024—Control of fluid pressure characterised by the use of electric means with direct action of electric energy on controlling means using throttling means as controlling means the throttling means being a multiple-way valve
    • 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0202—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
    • F16H61/0251—Elements specially adapted for electric control units, e.g. valves for converting electrical signals to fluid signals
    • F16H2061/0258—Proportional solenoid valve
    • 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
    • F16H—GEARING
    • F16H61/00—Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/0021—Generation or control of line pressure
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87169—Supply and exhaust
    • Y10T137/87217—Motor

Definitions

  • the present invention relates to a proportional pressure regulating valve according to the preamble of patent claim 1.
  • the pressure in the hydraulic circuit is regulated as required.
  • the pressure level for the lubricating oil supply of the transmission components can be kept low.
  • certain consumers sometimes need a pressure that is above a certain threshold. For example, during the switching operations, the pressure in the hydraulic circuit must be raised in order to quickly fill the switching elements with pressure medium.
  • pressure control valves which control controls for clutch actuation.
  • the control of the controls takes place within the pressure control valve by means of a proportional magnet, which consists inter alia of a magnetic core, a magnetic coil and a magnet armature.
  • the proportional solenoid controls the coil current in proportion to the output quantity of force; the armature and thus the control for clutch control are controlled according to the coil current. From the resulting characteristic magnetic force-current characteristics of the pressure control valve, the pressure-current characteristics p / l characteristics desired for coupling adaptation are generated in an electrohydraulic control of automatic transmissions.
  • a proportional pressure regulating valve which consists of a magnetic part and a hydraulic part exists.
  • the magnetic part consists inter alia of a magnetic coil, a magnet armature and a magnetic core.
  • the armature has two magnetic armature parts, wherein a first part is fixedly connected to an anchor rod and a second part is arranged axially displaceably on the anchor rod. Both parts of the armature are connected together by a spring.
  • the pressure to be output of the proportional pressure control valve can be set very accurately.
  • Some consumers such as As clutches in motor vehicles, need to control the application of a pressure which is always above a first threshold. Only when concerns a pressure that is higher than this threshold, a regulation of the consumer can be performed. This threshold is called filling pressure.
  • the very flat region of the p / l characteristic curve would be required to achieve the filling pressure in the case of a characteristic according to the prior art.
  • On the flat course of the p / l characteristic then follows a steeper course of the characteristic.
  • this characteristic is used to first set the filling pressure at the switching element and then start the regulation, the high-resolution area, in which the pressure can be regulated very accurately, is much smaller. The switching element can therefore not be controlled so accurately with such a characteristic.
  • the object of the invention is to enable a proportional pressure control valve which regulates the pressure to be dispensed quickly to a first threshold value and then provides a progressive p / l characteristic.
  • This object is achieved by a proportional pressure regulating valve having the features of patent claim 1. Further embodiments and advantages will become apparent from the dependent claims.
  • a proportional pressure control valve which consists of a magnetic part and a hydraulic part.
  • the magnetic part consists at least of a magnetic coil, a magnetic armature and a magnetic core, wherein the lv ⁇ ägnetanker is firmly connected to an anchor rod.
  • the hydraulic part is in turn connected via a push rod with the anchor rod, wherein between the anchor rod and the push rod, an elastic member is attached.
  • Firmly connected to the push rod is a first closing element.
  • This first closing element has a seat surface which forms a flat seat with a first closing surface. The distance from the closing surface in the de-energized state of the seat is called cover.
  • a second closing element is actuated by the push rod.
  • This second closing element advantageously has the shape of a ball and forms a ball seat with a second closing surface.
  • the ball seat closes an aperture, which is flowed through by the pressure medium with the flow direction in the direction of the magnetic part. If the proportional pressure control valve is energized, the push rod opens the ball seat.
  • the second closing surface which can be closed by the ball, thus corresponds to a circular area with the diameter of the diaphragm. In the direction of flow in front of the flat seat extends a cylindrical space, which is also flowed through by the pressure medium. The diameter of this space is called the nominal size of the valve.
  • the geometry of the hydraulic part must be specially designed. This is inventively achieved in that in de-energized state in which the ball seat is closed, the coverage of the flat seat is greater than the seventh part of Nominal diameter. Furthermore, the second closing surface must be larger than a circular area with twice the coverage as a diameter. In addition, the diameter of the part of the push rod, which protrudes into the aperture when opening the ball seat in the aperture must be smaller than 0.7 times the aperture diameter.
  • a proportional pressure control valve which has a p / l characteristic with ei ⁇ eT ⁇ Dr ⁇ cksprung. This pressure jump occurs at a certain current value, the pressure rising from zero to a threshold value, which advantageously corresponds to the filling pressure of the consumer. After this pressure jump, the p / l characteristic has a progressive course. This means that the p / l characteristic after the pressure jump, in the range of low current has a flat and in the range of high current has a steep course.
  • a proportional pressure control valve according to the invention therefore, a consumer can be controlled, which responds only when a certain threshold is exceeded, wherein the consumer after reaching the threshold fine adjustment of the pressure is possible.
  • FIG. 1 shows a partial section through a valve according to the invention.
  • FIG. 2 shows a partial section through the magnetic part of a valve according to the invention.
  • Fig. 3 is a partial section through the hydraulic part of a valve according to the invention.
  • Fig. 4 is a p / l characteristic of a valve according to the invention.
  • a proportional pressure regulating valve 1 according to the invention for regulating the pressure level comprises a magnet part 2 and a hydraulic part 3.
  • the magnet part has at least one magnet coil 5 and a magnet armature 6, which is fixedly connected to an anchor rod 7.
  • the anchor rod 7 is connected via an elastic element 4 with a push rod 12.
  • a first closing element 8 is fixedly connected to the push rod 12.
  • This first closing element 8 forms a flat seat 10 with a first closing surface.
  • the push rod 12 further actuates a second closing element 9.
  • This second closing element 9 has the shape of a ball and forms with a second closing surface a ball seat 11.
  • the ball seat 11 includes a diaphragm 21, which is flowed through axially by the pressure medium in the direction of the magnetic part. If the proportional pressure control valve 1 is energized, the push rod 12 opens the ball seat 11. Detailed illustrations of the two sections X and Y are shown in FIGS. 2 and 3.
  • FIG. 2 shows a detailed partial section X of the magnetic part 1.
  • the armature 6, which is firmly connected to the anchor rod 7, can be seen.
  • a driving element 20 is firmly connected to the push rod 12.
  • an elastic element 4 preferably a spring attached.
  • the driving element 20 can also have a different shape, for example a purely radial extension.
  • the actuating force from the magnet part 2 is transmitted in a staggered manner to the first closing element 8 mounted on the push rod 12. This reduces the distance a between the anchor and the push rod 7, 12.
  • the spring arrangement is also the risk of seating bounce on the flat seat 10, which occurs by axial vibrations in the push rod 12, significantly reduced.
  • Fig. 3 shows a detailed partial section Y of the hydraulic part 2 of the valve 1 in the de-energized state.
  • the second spherical closing element 9 which closes the second closing surface A_2 and has a diameter 14.
  • the second closing surface A_2 forms the end face of the diaphragm 21 with its diameter b.
  • Fig. 3 shows the push rod 12, with which the first closing element 8 is firmly connected.
  • the push rod 7 has at its second closing element 9 facing the end of a reduced diameter s, which projects into the aperture 21. If the valve 1 is energized, the end of the push rod with the diameter s is pushed further into the aperture 21 and shifts the second closing element 9 against the flow direction 14 of the pressure medium.
  • the first closing element 8 has a seat surface 13 on its side directed counter to the flow direction 14.
  • the seat surface 13 forms a flat seat 10 with the first closing surface A_1 lying opposite it.
  • the distance from the seat surface 13 to the first closing surface A_1 corresponds to the flat seat distance u.
  • the diameter of the cylindrical space, which adjoins the flat seat 10 and expands in the direction of the second closing element 9, is called the nominal width NW.
  • the hydraulic part 2 of the proportional pressure control valve 1 is geometrically designed so that a pressure jump 17 results in the p / l characteristic curve 16 at a certain current intensity. To achieve this, the following conditions must be observed: According to the invention, the coverage ü must be greater than the seventh part of the nominal diameter NW of the valve:
  • the second closing surface A_2 must be larger than a circular area with a diameter which corresponds to the double coverage ü:
  • the output pressure p of the valve 1 jumps suddenly from the value zero to a first pressure value p_1, which advantageously corresponds to the filling pressure of the consumer.
  • FIG. 4 shows a p / l characteristic according to the invention.
  • the pressure p which is output from the proportional pressure control valve 1 to a consumer, on the current I, which is applied to the valve 1, registered.
  • the current I first rises to a certain first current level M without the pressure p changing.
  • the pressure p jumps to a first pressure value p_1, which corresponds to the filling pressure.
  • This jump is called pressure jump 17, which has a current value of 150 to 200 mA, particularly advantageous. way at 17OmA occurs.
  • the pressure increases to 0.2 to 0.7 bar, advantageously to 0.3 bar.
  • the p / I characteristic increases progressively.
  • the p / I characteristic curve has a lower slope in the region of low current intensity 18 and a larger slope in the region of higher current intensity 19.
  • the slope of the p / I characteristic curve in the region of low current intensity 18 is preferably 0 to 4.0 bar / A, in the region of higher current strength 19 up to 16 bar / A.
  • the pressure jump 17 is z. B. advantageous to quickly fill a clutch.
  • a large part of the flat characteristic curve region would be passed through until the clutch charge pressure p_1 was reached.
  • the flat area of the p / I characteristic curve 16 is advantageous in order to be able to set a desired pressure p precisely.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Physics & Mathematics (AREA)
  • Automation & Control Theory (AREA)
  • Magnetically Actuated Valves (AREA)
  • Control Of Transmission Device (AREA)
PCT/EP2006/001881 2005-03-09 2006-03-02 Proportional-druckregelventil mit drucksprung in seiner p/l-kennlinie Ceased WO2006094693A2 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
CN2006800077115A CN101137946B (zh) 2005-03-09 2006-03-02 在p/I特征曲线中具有压力突变的比例调压阀
KR1020077022900A KR101249226B1 (ko) 2005-03-09 2006-03-02 Ｐ/ｉ-특성 곡선 내에 압력 점프를 갖는 비례-압력 조절 밸브와 상기 밸브의 사용 방법
JP2008500093A JP4914887B2 (ja) 2005-03-09 2006-03-02 Ｐ／ｉ特徴線において圧力の突発的変化を有する比例的な圧力調整バルブ
EP20060707358 EP1856587B1 (de) 2005-03-09 2006-03-02 Proportional-druckregelventil mit drucksprung in seiner p/l-kennlinie
US11/908,003 US7905249B2 (en) 2005-03-09 2006-03-02 Proportional pressure control valve comprising a pressure jump in the characteristic p/l curve thereof

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200510010693 DE102005010693A1 (de) 2005-03-09 2005-03-09 Proportional-Druckregelventil mit Drucksprung in seiner p/l-Kennlinie
DE102005010693.5 2005-03-09

Publications (2)

Publication Number Publication Date
WO2006094693A2 true WO2006094693A2 (de) 2006-09-14
WO2006094693A3 WO2006094693A3 (de) 2006-12-07

Family

ID=36914628

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2006/001881 Ceased WO2006094693A2 (de) 2005-03-09 2006-03-02 Proportional-druckregelventil mit drucksprung in seiner p/l-kennlinie

Country Status (7)

Country Link
US (1) US7905249B2 (enExample)
EP (1) EP1856587B1 (enExample)
JP (1) JP4914887B2 (enExample)
KR (1) KR101249226B1 (enExample)
CN (1) CN101137946B (enExample)
DE (1) DE102005010693A1 (enExample)
WO (1) WO2006094693A2 (enExample)

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US20110062364A1 (en) * 2009-09-16 2011-03-17 Scherer Georg J Solenoid

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DE102007035472A1 (de) * 2007-07-26 2009-01-29 Svm Schultz Verwaltungs-Gmbh & Co. Kg Ventil
DE102008044237A1 (de) * 2008-12-01 2010-06-02 Robert Bosch Gmbh Druckregelventil
CN102537475A (zh) * 2010-12-10 2012-07-04 贵州红林机械有限公司 一种改进后的常开式比例压力电磁阀
KR101123016B1 (ko) * 2011-05-11 2012-03-16 주식회사 유니크 압력 제어 밸브
EP2527945A2 (de) * 2011-05-27 2012-11-28 SVM Schultz Verwaltungs-GmbH & Co. KG Druckregelventil mit Blende
EP2528070A3 (de) * 2011-05-27 2017-05-10 SVM Schultz Verwaltungs-GmbH & Co. KG Elektromagnet mit Einstellstift
DE102011079366A1 (de) 2011-07-19 2013-01-24 Zf Friedrichshafen Ag Druckregelventilvorrichtung mit einer Strömungsführungseinrichtung
JP5686201B2 (ja) * 2011-11-04 2015-03-18 トヨタ自動車株式会社 電磁式リニア弁
DE102011087264B4 (de) * 2011-11-29 2023-01-19 Zf Friedrichshafen Ag Druckregelventilvorrichtung
KR101188178B1 (ko) 2012-08-08 2012-10-09 주식회사 유니크 솔레노이드 밸브
DE102012223430A1 (de) * 2012-12-17 2014-06-18 Robert Bosch Gmbh Elektromagnetisches Stellglied
DE102013213713A1 (de) * 2013-07-12 2015-01-29 Zf Friedrichshafen Ag Fluidventil
DE102013220877A1 (de) * 2013-10-15 2015-04-16 Continental Automotive Gmbh Ventil
CN104482196B (zh) * 2014-12-19 2017-07-07 湖南江麓容大车辆传动股份有限公司 用于无级变速器的直驱式液压装置及汽车用无级变速器
SE540880C2 (en) 2016-09-28 2018-12-11 Freevalve Ab Multi-way valve as well as actuator comprising such a multi-way valve
CN111927980A (zh) * 2020-08-05 2020-11-13 北京理工大学 一种车用高速比例电磁阀及液压组件
DE102022202369A1 (de) 2022-03-10 2023-09-14 Zf Friedrichshafen Ag Ventilanordnung für ein Getriebe eines Kraftfahrzeugs

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US20110062364A1 (en) * 2009-09-16 2011-03-17 Scherer Georg J Solenoid
US8641011B2 (en) * 2009-09-16 2014-02-04 SVM Schultz Verwaltungs—GmbH & Co. KG Solenoid with armature having frontal recess

Also Published As

Publication number Publication date
KR101249226B1 (ko) 2013-04-03
EP1856587A2 (de) 2007-11-21
EP1856587B1 (de) 2013-07-24
JP4914887B2 (ja) 2012-04-11
JP2008533391A (ja) 2008-08-21
KR20070116079A (ko) 2007-12-06
US20080272322A1 (en) 2008-11-06
CN101137946A (zh) 2008-03-05
DE102005010693A1 (de) 2006-09-14
CN101137946B (zh) 2010-05-26
US7905249B2 (en) 2011-03-15
WO2006094693A3 (de) 2006-12-07

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