JP2004278793A - Bearing for high speed rotating shaft - Google Patents

Bearing for high speed rotating shaft Download PDF

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Publication number
JP2004278793A
JP2004278793A JP2004067285A JP2004067285A JP2004278793A JP 2004278793 A JP2004278793 A JP 2004278793A JP 2004067285 A JP2004067285 A JP 2004067285A JP 2004067285 A JP2004067285 A JP 2004067285A JP 2004278793 A JP2004278793 A JP 2004278793A
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Japan
Prior art keywords
bearing
bush
contact support
floating
bearing according
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JP2004067285A
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Japanese (ja)
Inventor
Hermann Link
リンク ヘルマン
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MAN B&W Diesel GmbH
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MAN B&W Diesel GmbH
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Publication of JP2004278793A publication Critical patent/JP2004278793A/en
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    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/103—Construction relative to lubrication with liquid, e.g. oil, as lubricant retained in or near the bearing
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • 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
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/12—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load
    • F16C17/18—Sliding-contact bearings for exclusively rotary movement characterised by features not related to the direction of the load with floating brasses or brushing, rotatable at a reduced speed
    • 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
    • F16C27/02—Sliding-contact bearings
    • 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
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/02—Parts of sliding-contact bearings
    • F16C33/04—Brasses; Bushes; Linings
    • F16C33/06—Sliding surface mainly made of metal
    • F16C33/10—Construction relative to lubrication
    • F16C33/1025—Construction relative to lubrication with liquid, e.g. oil, as lubricant
    • F16C33/1045—Details of supply of the liquid to the bearing
    • 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
    • F16C43/00—Assembling bearings
    • F16C43/02—Assembling sliding-contact bearings
    • 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
    • F16C2300/00—Application independent of particular apparatuses
    • F16C2300/20—Application independent of particular apparatuses related to type of movement
    • F16C2300/22—High-speed rotation

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Support Of The Bearing (AREA)
  • Sliding-Contact Bearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To form a bearing for a high speed rotating shaft to cause it in a simple means to dampen so as to excite vibration surely and successfully in the bearing for the high speed rotating shaft provided with floating bushes (3, 4) which is disposed within a housing. <P>SOLUTION: Each floating bushes (3, 4) includes annular recesses (11, 12) radially outward extending in axial side end of end faces (8, 10) of both their sides. Inner diameter of a shaft through hole (13) existing in contacting support walls (6, 7, 9) adjacent to the end faces of the both sides of each floating bushes is made smaller than the radial height of the annular recesses. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明はハウジング内に配置された浮動ブッシュを備える高速回転軸用軸受に関する。   The present invention relates to a bearing for a high-speed rotation shaft including a floating bush disposed in a housing.

浮動ブッシュ付き軸受は既に公知である。   Bearings with floating bushes are already known.

本発明の課題は、冒頭に述べた形式の軸受を単純な手段で、振動励起の確実で良好な減衰が起こるように形成することにある。   The object of the present invention is to form a bearing of the type mentioned at the outset with a simple means so that reliable and good damping of vibration excitation takes place.

この課題は、本発明に基づき、各浮動ブッシュがその両側端面の軸側端に、半径方向外側に延びる環状凹所を有し、各浮動ブッシュの両側端面に隣接する接触支持壁に存在する軸貫通孔の内径が、前記環状凹所の半径方向高さより小さいことで解決される。   This object is based on the present invention, in which each floating bush has an annular recess extending radially outward at the axial end of its both end faces, and the shaft existing in the contact support wall adjacent to both end faces of each floating bush. This is solved by the fact that the inner diameter of the through hole is smaller than the radial height of the annular recess.

この形態では、凹所に油溜まりが生じ、該油溜まりは、浮動ブッシュの振動運動時、浮動ブッシュのハウジング側面の良好な潤滑を保証する。油溜まりは、接触支持壁と浮動ブッシュの間の隙間に空気が侵入するのを防ぐ。空気の侵入は、減衰作用を悪化させる。   In this configuration, an oil puddle is created in the recess, which guarantees good lubrication of the housing side of the floating bush during the oscillating movement of the floating bush. The oil sump prevents air from entering the gap between the contact support wall and the floating bush. Intrusion of air exacerbates the damping effect.

本発明の１実施態様では、浮動ブッシュの両側端面および／又は接触支持壁に、半径方向に延びる溝を配置する。これにより、接触支持壁と浮動ブッシュの間の隙間が小さい場合も、外側油膜に対する十分な油量供給を保証できる。   In one embodiment of the present invention, radially extending grooves are disposed on both end faces and / or contact support walls of the floating bush. Thereby, even when the gap between the contact support wall and the floating bush is small, it is possible to guarantee a sufficient oil supply to the outer oil film.

本発明の他の特徴と利点を、従属請求項と図を参照した本発明の２つの実施例の説明で明らかにする。   Other features and advantages of the invention will become apparent from the description of the two embodiments of the invention with reference to the dependent claims and the figures.

図１において、１は軸受の固定ハウジング、２は軸である。軸２は２つの浮動ブッシュ３、４で支持され、該ブッシュ３、４間に間隔ブッシュ５が配置されている。間隔ブッシュ５は円筒ピン３２で回り止めされている。更に、この軸受は両外側における円板状接触支持壁６、７で外に対し閉じられている。   In FIG. 1, 1 is a fixed housing of a bearing, and 2 is a shaft. The shaft 2 is supported by two floating bushes 3 and 4, and a spacing bush 5 is disposed between the bushes 3 and 4. The spacing bush 5 is prevented from rotating by a cylindrical pin 32. Furthermore, this bearing is closed to the outside by disk-like contact support walls 6 and 7 on both outer sides.

一方の浮動ブッシュ３は、間隔ブッシュ５と接触支持壁６の間に軸方向遊びをもって配置されている。更に、間隔ブッシュ５はハウジングに固定された円筒ピン３２で回り止めされている。このピン３２は、間隔ブッシュ５に存在し、例えば大きな直径の孔又は長孔の形をした少なくとも軸２の軸方向に遊びを与える凹所３３に係合している。   One floating bush 3 is arranged with axial play between the spacing bush 5 and the contact support wall 6. Further, the spacing bush 5 is prevented from rotating by a cylindrical pin 32 fixed to the housing. This pin 32 is present in the spacing bush 5 and engages a recess 33 which provides play in at least the axial direction of the shaft 2, for example in the form of a large diameter hole or slot.

浮動ブッシュ３の接触支持壁６側の端面８と、間隔ブッシュ５の接触支持壁９側の端面１０とに、各々傾斜面で境界づけられた環状凹所１１、１２が存在する。これらの凹所１１、１２は半径方向外側に延びている。接触支持壁６は軸貫通孔１３の内径を有し、該内径は凹所１１の半径方向高さより小さい。この形状の故、凹所１１の軸から離れた箇所に油溜まり１４が生ずる。この油溜まりは、浮動ブッシュ３の振動運動時、浮動ブッシュ３がこれと接触支持壁６の間に空気を吸い込まないように作用する。従ってハウジング１と浮動ブッシュ３の間に、振動励起を減衰する一定の潤滑油膜を維持できる。   There are annular recesses 11 and 12 bounded by inclined surfaces on the end surface 8 of the floating bush 3 on the contact support wall 6 side and the end surface 10 of the spacing bush 5 on the contact support wall 9 side, respectively. These recesses 11 and 12 extend radially outward. The contact support wall 6 has an inner diameter of the shaft through hole 13, and the inner diameter is smaller than the height of the recess 11 in the radial direction. Because of this shape, an oil sump 14 is generated at a location away from the axis of the recess 11. The oil reservoir acts so that the floating bush 3 does not suck air between the floating bush 3 and the contact support wall 6 during the vibration movement of the floating bush 3. Therefore, a certain lubricating oil film that attenuates vibration excitation can be maintained between the housing 1 and the floating bush 3.

軸２の低速回転時に、浮動ブッシュ３とハウジング１の間に十分な潤滑油膜を確保すべく、浮動ブッシュ３の両側端面に半径方向に延びる溝１５、１６を設けている。しかしこれらの溝は、接触支持壁６、７の浮動ブッシュ３側の面に設けてもよい。   Grooves 15 and 16 extending in the radial direction are provided on both end faces of the floating bush 3 in order to ensure a sufficient lubricating oil film between the floating bush 3 and the housing 1 when the shaft 2 rotates at a low speed. However, these grooves may be provided on the surface of the contact support walls 6 and 7 on the floating bush 3 side.

ハウジング１の反対側端で、浮動ブッシュ４に対し、上と同じ構造を採用している。   The same structure as above is adopted for the floating bush 4 at the opposite end of the housing 1.

図２の実施例は、図１のそれと殆ど一致している。ここでは、浮動ブッシュ２０、２１に対する接触支持壁１８、１９を持つハウジング１７を用いている。浮動ブッシュ２０、２１の軸方向外側への動きは、接触支持壁２２、２３で制限している。浮動ブッシュ２０の両側端面２４、２５に各々凹所２６、２７を設けており、両凹所２６、２７は、湾曲境界面付きの溝で形成している。ここでも、接触支持壁１８、２２の軸貫通孔２８、２９の内径は、凹所２６、２７の半径方向高さより小さく、このため油溜まり３０、３１が生じている。これら油溜まり３０、３１は、ハウジング１７と浮動ブッシュ２０の間の潤滑油膜に空気が侵入するのを防ぐ。他方の浮動ブッシュ２１も同様に形成し支持する。   The embodiment of FIG. 2 is almost identical to that of FIG. Here, a housing 17 having contact support walls 18 and 19 for the floating bushes 20 and 21 is used. The axial movement of the floating bushes 20 and 21 is restricted by the contact support walls 22 and 23. Recesses 26 and 27 are provided on both side end surfaces 24 and 25 of the floating bush 20, respectively, and both the recesses 26 and 27 are formed by grooves with curved boundary surfaces. Here too, the inner diameters of the shaft through holes 28, 29 of the contact support walls 18, 22 are smaller than the height in the radial direction of the recesses 26, 27, so that oil reservoirs 30, 31 are produced. These oil sumps 30 and 31 prevent air from entering the lubricating oil film between the housing 17 and the floating bush 20. The other floating bush 21 is similarly formed and supported.

本発明によると、振動励起の良好な減衰だけでなく、軸受の良好な耐摩耗性も生ずる。   According to the present invention, not only good damping of vibration excitation, but also good wear resistance of the bearing occurs.

本発明に基づく軸受の断面図。Sectional drawing of the bearing based on this invention. 本発明に基づく軸受の第２実施例の図１に相当する断面図。Sectional drawing equivalent to FIG. 1 of 2nd Example of the bearing based on this invention.

符号の説明Explanation of symbols

１ ハウジング、２ 軸、３、４、２０、２１ 浮動ブッシュ、５ 間隔ブッシュ、６、７、９、１８、１９、２２、２３ 接触支持壁、８、１０、２４、２５ 端面、１１、１２、２６、２７ 環状凹所、１３、２８、２９ 軸貫通孔、１５、１６ 溝、３２ 円筒ピン DESCRIPTION OF SYMBOLS 1 Housing, 2 axis | shafts 3, 4, 20, 21 Floating bushing, 5 Spacing bushing, 6, 7, 9, 18, 19, 22, 23 Contact support wall, 8, 10, 24, 25 End surface, 11, 12, 26, 27 Annular recess, 13, 28, 29 Shaft through hole, 15, 16 Groove, 32 Cylindrical pin

Claims (8)

ハウジング内に配置された浮動ブッシュを備える高速回転軸用軸受において、各浮動ブッシュ（３、４、２０、２１）がその両側端面（８、１０、２４、２５）の軸（２）側端に、半径方向外側に延びる環状凹所（１１、１２、２６、２７）を有し、各浮動ブッシュの両側端面に隣接する接触支持壁（６、７、９、１８、１９、２２、２３）に存在する軸貫通孔（１３、２８、２９）の内径が、前記環状凹所の半径方向高さより小さいことを特徴とする軸受。   In a bearing for a high-speed rotation shaft provided with a floating bush arranged in a housing, each floating bush (3, 4, 20, 21) is located on the shaft (2) side end of both side end surfaces (8, 10, 24, 25). The contact support walls (6, 7, 9, 18, 19, 22, 23) having annular recesses (11, 12, 26, 27) extending radially outward and adjacent to both end faces of each floating bush A bearing characterized in that an inner diameter of the existing shaft through hole (13, 28, 29) is smaller than a radial height of the annular recess. 浮動ブッシュの両側端面（８、１０、２４、２５）および／又は接触支持壁（６、７、９、１８、１９、２２、２３）に、半径方向に延びる溝（１５、６）が配置されたことを特徴とする請求項１記載の軸受。   Grooves (15, 6) extending in the radial direction are arranged on both end faces (8, 10, 24, 25) and / or contact support walls (6, 7, 9, 18, 19, 22, 23) of the floating bush. The bearing according to claim 1. 凹所（１１、１２）が傾斜面により形成されたことを特徴とする請求項１又は２記載の軸受。   The bearing according to claim 1, wherein the recess is formed by an inclined surface. 凹所（２６、２７）が湾曲境界面を備えた溝により形成されたことを特徴とする請求項１又は２記載の軸受。   3. A bearing according to claim 1 or 2, characterized in that the recess (26, 27) is formed by a groove with a curved interface. 接触支持壁（６、７、２２、２３）が円板として形成されたことを特徴とする請求項１から４の１つに記載の軸受。   5. A bearing according to claim 1, wherein the contact support walls (6, 7, 22, 23) are formed as discs. 接触支持壁（９）が、両浮動ブッシュ（３、４）間に配置された間隔ブッシュ（５）の側壁により形成されたことを特徴とする請求項１から４の１つに記載の軸受。   5. Bearing according to claim 1, wherein the contact support wall is formed by the side wall of a spacing bush arranged between the two floating bushes. 接触支持壁（１８、１９）が、固定ハウジング（１７）の側壁として形成されたことを特徴とする請求項１から４の１つに記載の軸受。   5. Bearing according to one of the preceding claims, characterized in that the contact support walls (18, 19) are formed as side walls of the stationary housing (17). 間隔ブッシュ（５）が、間隔ブッシュ（５）に存在する少なくとも軸方向における遊びを与える凹所（３３）に、大きな直径の孔に係合する円筒ピン（３２）により、ハウジング（１１）に対し回り止めして配置されたことを特徴とする請求項１から４および６の１つに記載の軸受。   The spacing bush (5) is against the housing (11) by a cylindrical pin (32) that engages a large diameter hole in a recess (33) that presents at least axial play in the spacing bush (5). The bearing according to claim 1, wherein the bearing is arranged so as to prevent rotation.
JP2004067285A 2003-03-14 2004-03-10 Bearing for high speed rotating shaft Pending JP2004278793A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE10311202A DE10311202A1 (en) 2003-03-14 2003-03-14 Bearing for shaft turning at high RPM has for each floating bush on end face sides facing shaft ring-form recesses, and inside diameter of locating discs adjacent to end faces is smaller than radial height of recesses

Publications (1)

Publication Number Publication Date
JP2004278793A true JP2004278793A (en) 2004-10-07

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JP2004067285A Pending JP2004278793A (en) 2003-03-14 2004-03-10 Bearing for high speed rotating shaft

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JP (1) JP2004278793A (en)
KR (1) KR20040081077A (en)
CN (1) CN100422581C (en)
CH (1) CH697317B1 (en)
DE (1) DE10311202A1 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020070980A1 (en) * 2018-10-05 2020-04-09 株式会社Ihi Bearing structure

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5705665B2 (en) * 2011-06-30 2015-04-22 三菱重工業株式会社 Turbocharger bearing device
JP2017211077A (en) * 2016-05-23 2017-11-30 株式会社ジェイテクト Clutch device
FR3069666B1 (en) * 2017-07-27 2021-11-05 Bernard Controls CAM SYSTEM CONTAINING AT LEAST ONE MOBILE CONTROL MODULE OF A SHAREHOLDER DEVICE
WO2020174611A1 (en) * 2019-02-27 2020-09-03 三菱重工エンジン＆ターボチャージャ株式会社 Floating bush bearing and supercharger

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE713099C (en) * 1939-11-21 1941-10-31 Mitteldeutsche Stahlwerke Akt Bearing made up of two or more floating bushes
US2268770A (en) * 1940-03-08 1942-01-06 Acrotorque Co Bearing
DE6608771U (en) * 1966-08-24 1971-11-11 Wallace Murray Corp BEARING FOR FAST ROTATING MACHINERY, PREFERABLY TURBOCHARGER.
US4256441A (en) * 1979-06-19 1981-03-17 Wallace-Murray Corporation Floating ring bearing structure and turbocharger employing same
DE2945659A1 (en) * 1979-10-16 1981-04-30 BBC AG Brown, Boveri & Cie., Baden, Aargau SEALING ARRANGEMENT AND THEIR USE
JPS57129919A (en) * 1981-02-04 1982-08-12 Hitachi Ltd Floating bush bearing
JPS58119926A (en) * 1982-01-06 1983-07-16 Hitachi Ltd Bearing device for supercharger
CA1285309C (en) * 1985-10-22 1991-06-25 Hooshang Heshmat Bearing assembly
US4902144A (en) * 1989-05-02 1990-02-20 Allied-Signal, Inc. Turbocharger bearing assembly
DE29611964U1 (en) * 1996-07-10 1996-09-05 BPW Bergische Achsen Kommanditgesellschaft, 51674 Wiehl Plain bearing bush
JP2002159158A (en) * 2000-11-17 2002-05-31 Nidec Copal Corp Retaining structure of motor rotor

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2020070980A1 (en) * 2018-10-05 2020-04-09 株式会社Ihi Bearing structure
CN112424457A (en) * 2018-10-05 2021-02-26 株式会社Ihi Bearing structure
US11434783B2 (en) 2018-10-05 2022-09-06 Ihi Corporation Bearing structure including a rotation member with a plurality of extended portions and a bearing member having a plurality of main bodies each including a counterface surface facing one of the plurality of extended portions in an axial direction

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KR20040081077A (en) 2004-09-20
CH697317B1 (en) 2008-08-15
CN100422581C (en) 2008-10-01
CN1530559A (en) 2004-09-22
DE10311202A1 (en) 2004-10-14

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