EP1199452A1 - In ihrem Verdichtungsverhältnis einstellbare Kolbenbrennkraftmaschine mit integriertem Verstellaktuator - Google Patents
In ihrem Verdichtungsverhältnis einstellbare Kolbenbrennkraftmaschine mit integriertem Verstellaktuator Download PDFInfo
- Publication number
- EP1199452A1 EP1199452A1 EP01112514A EP01112514A EP1199452A1 EP 1199452 A1 EP1199452 A1 EP 1199452A1 EP 01112514 A EP01112514 A EP 01112514A EP 01112514 A EP01112514 A EP 01112514A EP 1199452 A1 EP1199452 A1 EP 1199452A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pinion
- piston
- crankshaft
- internal combustion
- combustion engine
- 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.)
- Withdrawn
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 16
- 230000006835 compression Effects 0.000 title abstract description 10
- 238000007906 compression Methods 0.000 title abstract description 10
- 230000008859 change Effects 0.000 description 7
- 230000005540 biological transmission Effects 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
- 239000000463 material Substances 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000008878 coupling Effects 0.000 description 2
- 238000010168 coupling process Methods 0.000 description 2
- 238000005859 coupling reaction Methods 0.000 description 2
- 238000006073 displacement reaction Methods 0.000 description 2
- 210000001503 joint Anatomy 0.000 description 2
- 238000000034 method Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 229910001060 Gray iron Inorganic materials 0.000 description 1
- 210000000078 claw Anatomy 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 229910052751 metal Inorganic materials 0.000 description 1
- 230000008569 process Effects 0.000 description 1
- 230000002250 progressing effect Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Images
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
- F02B75/00—Other engines
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/047—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of variable crankshaft position
Definitions
- DE-A-198 41 381 discloses further embodiments for such Adjustment devices known. All known embodiments however require special designs of the engine block.
- the invention has for its object a piston internal combustion engine with adjustable compression ratio create that structurally simpler and cheaper to build is finished.
- a piston internal combustion engine of this type has the advantage that through the side next to the crankshaft and parallel for this purpose, the control shaft is mounted in an area of the engine block can be arranged by the between the cylinders effective on the one hand and the crankshaft on the other Forces are practically not burdened.
- the Arrangement can be made so that the outer Dimensions of the crankcase are practically not changed and therefore no enlargement of the engine compartment for the vehicle becomes necessary. It is particularly useful here if the control shaft with its bearings next to each side the main camps is arranged.
- tooth elements from neighboring control arms over a pinion element are interconnected. This is done from one end of the control shaft to the other end of the Control shaft a chain-like transmission of the control torque, because each one of the actuating arms is springy from one side braced pinion and from the other side engages with the control shaft firmly connected pinion.
- arrangement allows that the two pinions of the pinion element via a torsion spring tube are interconnected.
- a pinion element is easy to manufacture and allows a cheap one Design of the tension between the two pinions required springs to use a torsion spring tube, since the length of the pinion element, i.e. H. the distance between the two pinions approximately the distance between two cylinder axes or between two main camps.
- control shaft is hollow and that the pinion elements each connected to it by local expansion are.
- the hollow shaft is expanded with the pinion element only in the area of the pinion that is fixed to the shaft to be connected. This gives you the opportunity to Inner diameter of the torsion spring tube on the one hand and the To dimension the outside diameter of the undeformed hollow shaft so that a plain bearing fit is given and accordingly the relatively rotatable pinion accordingly on the hollow shaft is stored, while the pinion to be fixed by the Widening of the hollow shaft is firmly connected to this.
- control shaft with bearing bodies for storage in Engine block is provided, whose outer diameter is larger than the outer diameter of the pinion.
- the bearings for the Control shaft is always conveniently located next to a main crankshaft bearing are arranged, but there is also Possibility of the bottom of the engine block in full Length covering frame or lattice-shaped bearing component in the form of a so-called bed plate, correspondingly to provide the bearings for the control shaft.
- the bearing body can also be expanded with the Control shaft are firmly connected. Because the control shaft is not is rotated continuously, the arrangement is special Plain bearing bushes or plain bearing shells are not required.
- the actuating shaft with its bearing bodies can be directly in the material the engine block, which is made of gray cast iron or light metal cast can be produced, stored. The oil supply can via so-called catch holes.
- the eccentric ring is composed of two sections is, the division plane through the axis of rotation the crankshaft runs and that at least a portion with an actuating arm is provided with a tooth element.
- each section with an actuator arm is provided with a tooth element, the two actuating arms overlap the bearing housing assigned to the eccentric ring on the side.
- a separate, Actuator controllable via a motor control device be provided with countershaft transmission.
- a Actuator provided, which is formed by a with the Drive shaft connected drive wheel with large outer diameter, the two drive wheels with small diameter in constant engagement are assigned, each with a switchable Coupling are connected, the drive on the opposite side optionally drivable and with a drive with constant direction of rotation is connectable by switching, as well as by a switchable parking brake, each time the Clutch releases.
- a magnetic one is preferred Slip clutch, on the one hand, a smooth rotation of the Actuating shaft causes and on the other in addition to that by given the small drive wheels and the large driven wheel Translation allows a reduction in the adjustment speed.
- crankshaft 1 With its crankshaft bearings 2 in eccentric rings 3 mounted, which in turn can be rotated in corresponding Support bearings 4 of an indicated engine block stored are. With the crankshaft 1 are the connecting rods 5 each connected here only schematically indicated piston 6.
- the Crankshaft 1 is shown in a position in which the pistons 6.1 and 6.4 are in the top dead center position, while the pistons 6.2 and 6.3 are in the bottom dead center are located.
- Each eccentric ring 3 is rigidly connected to an actuating arm 8, which is provided with a tooth element 9 at its free end is.
- the tooth elements 9 each have a pinion element 10 engaged with one in the side of the engine block and connected to the crankshaft 1 mounted actuator shaft 11 are.
- the adjusting shaft 11 is only indicated here Actuator 12 connected.
- FIG. 2 is an end view in a partial vertical section to a main bearing area of the crankshaft in the engine block shown according to Fig.1. A more detailed description it is not necessary because the individual components based on their Reference symbols can be identified in connection with FIG. 1.
- sectional view acc. Fig. 3 leaves the constructive assignment the control shaft 10 and a special embodiment recognize the pinion elements.
- the eccentric rings 3 are each with two parallel Arm 8.1 and 8.2 provided, each at their ends are provided with corresponding tooth elements 9.
- the tooth elements 9 of an eccentric ring 3 are each with axial Spaced from each other. Only the eccentric ring on the end 3.1 is 8.0 with only one control arm and corresponding provided only one tooth element.
- the pinion element 10 formed by two pinions 10.1 and 10.2, the firmly connected to one another via a torsion spring tube 15 are.
- the arrangement is such that the pinion element 10 firmly in the area of its pinion 10.1 the control shaft 11 is connected, for example by a Widen the hollow shaft or by a corresponding connection procedure, during the subsequent Area of the torsion spring 15 and the pinion 10.2 on the Actuating shaft 11 with respect to the pinion firmly connected to this 10.1 is relatively rotatable.
- the adjusting shaft 11 is connected to bearing bodies 16, the Outside diameter is larger than the outside diameter of the pinion elements 10, so that the control shaft 11 with attached pinion elements 10 in total through corresponding holes in Engine block can be pushed through.
- the eccentric rings are each formed from two sections 3.1 (Fig. 4) and 3.2 (Fig. 6).
- the arrangement is made so that starting from the actuating arm 8.0, the one assigned to it Pinion 10.1 is firmly connected to the actuating shaft 11 and Via the torsion spring tube 15, the pinion 10.2 with the tooth element 9 on the actuating arm 8.2 of the adjacent eccentric ring 3 is engaged.
- the individual are correspondingly continuous successive eccentric rings 3 each via pinion elements 10 connected together. Because the gearing of the pinion 10.1 compared to the pinion 10.2 of a pinion element 10 offset by a small amount in the circumferential direction is arranged, there is the possibility of mounting each the tooth elements connected to one another via the pinion element to brace against each other and so the backlash excluded.
- the two small drive wheels 18.1 and 18.2 each with one switchable coupling 19.1 and 19.2 connected as magnetic Slip clutches are formed.
- the driving part 20.1 and 20.2 of the slip clutches is in the unswitched state freely rotatable relative to the part to be driven 21.1 and 21.2, each connected to the drive wheel 18.1 or 18.2 is.
- the driving part 20 of the two slip clutches is over a pulley 23 and connected to the crankshaft 1 a belt 22 driven, the belt 22 on the two driving parts 20.1 and 20.2 is passed so that with the belt 22 running in the same direction (arrow 24) by switching the clutches the drive wheels 18.1 or 18.2 are turned in opposite directions can.
- Eccentric rings 3 is through a corresponding belt tensioning device compensated, which is not shown here.
- the driven wheel 17 is, as indicated in FIG. 9, a switchable parking brake 25 assigned by the in operation via the driven wheel 17, the control shaft 11 in each their set position is held and so that each set compression ratio is fixed. Should the compression ratio will be changed depending on the adjustment direction specified by the control device one of the two clutches 20.1 or 20.2 activated and the Parking brake 25 released, so that to change the Compression ratio specified by the control device Pivoting can be performed. Once the end position the parking brake is applied and the clutch switched off, so that the driving part 20.1 or 20.2 is again free in the direction of flow of the belt 22 can rotate predetermined direction of rotation without that via the drive wheels 18.1 and 18.2 a force effect takes place on the driven wheel 17.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10051271 | 2000-10-16 | ||
DE10051271.2A DE10051271B4 (de) | 2000-10-16 | 2000-10-16 | In ihrem Verdichtungsverhältnis einstellbare Kolbenbrennkraftmaschine mit integriertem Verstellaktuator |
Publications (1)
Publication Number | Publication Date |
---|---|
EP1199452A1 true EP1199452A1 (de) | 2002-04-24 |
Family
ID=7659987
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01112514A Withdrawn EP1199452A1 (de) | 2000-10-16 | 2001-05-23 | In ihrem Verdichtungsverhältnis einstellbare Kolbenbrennkraftmaschine mit integriertem Verstellaktuator |
Country Status (4)
Country | Link |
---|---|
US (1) | US6588384B2 (ja) |
EP (1) | EP1199452A1 (ja) |
JP (1) | JP2002174132A (ja) |
DE (1) | DE10051271B4 (ja) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007039103A1 (de) * | 2005-10-01 | 2007-04-12 | Daimler Ag | Brennkraftmaschine mit variablem verdichtungsverhältnis |
WO2012139616A1 (de) * | 2011-04-15 | 2012-10-18 | Daimler Ag | Stelleinrichtung zum variablen einstellen eines verdichtungsverhältnisses einer verbrennungskraftmaschine |
WO2012139618A1 (de) * | 2011-04-15 | 2012-10-18 | Daimler Ag | Verfahren zum betreiben einer stelleinrichtung zum variablen einstellen eines verdichtungsverhältnisses einer verbrennungskraftmaschine |
WO2012139605A1 (de) * | 2011-04-15 | 2012-10-18 | Daimler Ag | Stelleinrichtung zum variablen einstellen eines verdichtungsverhältnisses einer verbrennungskraftmaschine |
Families Citing this family (28)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3906754B2 (ja) * | 2002-07-12 | 2007-04-18 | トヨタ自動車株式会社 | クランク軸受 |
DE10258872A1 (de) | 2002-12-17 | 2004-07-08 | Robert Bosch Gmbh | Verfahren und Vorrichtung zum Betrieb eines mehrzylindrigen Verbrennungsmotors mit variablem Verdichtungsverhältnis |
DE10319666A1 (de) | 2003-05-02 | 2004-11-18 | Robert Bosch Gmbh | Verfahren und Vorrichtung zur Einstellung einer variablen Verdichtung bei einem Verbrennungsmotor |
US7007640B2 (en) * | 2003-07-25 | 2006-03-07 | Masami Sakita | Engine with a variable compression ratio |
JP4229867B2 (ja) * | 2004-03-31 | 2009-02-25 | 本田技研工業株式会社 | 圧縮比可変機構を備える内燃機関を備える動力装置 |
US7174865B2 (en) * | 2004-07-19 | 2007-02-13 | Masami Sakita | Engine with a variable compression ratio |
US7370613B2 (en) * | 2004-11-30 | 2008-05-13 | Caterpillar Inc. | Eccentric crank variable compression ratio mechanism |
DE102005020270A1 (de) * | 2005-04-30 | 2006-11-09 | Daimlerchrysler Ag | Brennkraftmaschine mit variablem Verdichtungsverhältnis |
US6971342B1 (en) * | 2005-06-01 | 2005-12-06 | Grabbe Wallace W | Adjustable compression ratio apparatus |
JP4822184B2 (ja) * | 2006-09-15 | 2011-11-24 | 本田技研工業株式会社 | ストローク特性可変エンジン |
GB2456941B (en) * | 2006-10-03 | 2011-07-06 | Edward Charles Mendler | Oil Circuit |
US7631620B2 (en) | 2007-03-17 | 2009-12-15 | Victor Chepettchouk | Variable compression ratio mechanism for an internal combustion engine |
JP2009085187A (ja) * | 2007-10-03 | 2009-04-23 | Yamaha Motor Co Ltd | 圧縮比可変エンジン |
US7661396B2 (en) * | 2007-12-08 | 2010-02-16 | Masami Sakita | Actuation subsystem of variable compression ratio control system for internal combustion engine |
CN101910582A (zh) * | 2007-12-31 | 2010-12-08 | Fev电机技术有限公司 | 平行曲柄传动机构 |
DE102008040459A1 (de) * | 2008-07-16 | 2010-01-21 | Zf Friedrichshafen Ag | Verstellvorrichtung eines Verbrennungsmotors |
DE102008050827A1 (de) | 2008-10-08 | 2010-04-15 | Schaeffler Kg | Verstellvorrichtung für eine Kurbelwelle eines Verbrennungsmotors sowie Verfahren zu deren Ansteuerung |
DE102008050826A1 (de) * | 2008-10-08 | 2010-04-15 | Schaeffler Kg | Verstellvorrichtung zur Lageveränderung einer in Exzenterbuchsen gelagerten Kurbelwelle eines Verbrennungsmotors |
KR101090801B1 (ko) * | 2009-06-30 | 2011-12-08 | 현대자동차주식회사 | 가변 압축비 장치 |
FI121283B (fi) * | 2009-08-17 | 2010-09-15 | Aulis Pohjalainen | Moottorin sylinteripaineen säädin |
US8267055B2 (en) * | 2009-09-03 | 2012-09-18 | Manousos Pattakos | Variable compression ratio engine |
CN102562214B (zh) * | 2010-12-21 | 2014-10-29 | 上海尤顺汽车部件有限公司 | 用于产生发动机的辅助气门运动的复合摇臂装置 |
DE102011017197A1 (de) | 2011-04-15 | 2012-10-18 | Daimler Ag | Hubkolben-Verbrennungskraftmaschine |
WO2013119330A1 (en) * | 2012-02-09 | 2013-08-15 | Edward Charles Mendler | Variable compression ratio engine |
US8671895B2 (en) | 2012-05-22 | 2014-03-18 | Michael Inden | Variable compression ratio apparatus with reciprocating piston mechanism with extended piston offset |
DE102013003813A1 (de) * | 2013-03-04 | 2014-09-04 | GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) | Verbrennungsmotor mit einem Exzenterverstellantrieb einer Kurbelwelle für eine variable Verdichtung |
CN105697142B (zh) * | 2014-11-28 | 2018-08-10 | 上海汽车集团股份有限公司 | 发动机 |
US10989108B2 (en) * | 2018-07-31 | 2021-04-27 | Ford Global Technologies, Llc | Methods and systems for a variable compression engine |
Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3861239A (en) * | 1972-06-05 | 1975-01-21 | Edward M Mcwhorter | Internal combustion engine combustion control crankshaft |
DE2935977A1 (de) | 1979-09-06 | 1981-03-12 | Scherf, geb. Kindermann, Eva, 8431 Kemnath | Hubkolbenmotor. |
DE2935073A1 (de) | 1979-08-30 | 1981-03-12 | Scherf, geb. Kindermann, Eva, 8431 Kemnath | Hubkolbenmotor |
DE3004402A1 (de) | 1980-02-07 | 1981-08-13 | Daimler-Benz Ag, 7000 Stuttgart | Kurbeltrieb einer hubkolben-brennkraftmaschine mit waehrend des betriebes veraenderbarem kompressionsverhaeltnis |
DE3030615A1 (de) | 1980-08-13 | 1982-02-18 | Gerhard 8501 Allersberg Mederer | Hubkolbenmotor |
WO1986007115A1 (en) * | 1985-05-24 | 1986-12-04 | Robert Alan Cooper | Crankshaft crank |
DE3601528A1 (de) | 1986-01-20 | 1987-07-23 | Wolfgang Schwarz | Brennkraft-kolbenmaschine, reihenmotor mit variablem verdichtungsverhaeltnis |
DE3644721A1 (de) | 1986-12-30 | 1988-07-14 | Erich Schmid | Vorrichtung fuer eine hubkolbenmaschine mit variablem brennraum |
DE3715391A1 (de) | 1987-05-08 | 1988-12-01 | Gerhard Mederer | Brennkraftmaschine oder sonstiger antrieb |
DE19841381A1 (de) | 1997-10-31 | 1999-05-06 | Fev Motorentech Gmbh & Co Kg | Kolbenbrennkraftmaschine mit einstellbarem Verdichtungsverhältnis |
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DE1251581B (de) * | 1967-10-05 | Klöckner-Humboldt-Deutz Aktiengesellschaft, Köln-Deutz | Kreiskolbenmaschine | |
US3407628A (en) * | 1967-06-05 | 1968-10-29 | Oreste B. Eccher | Parallel shaft coupling |
FR2479376A1 (fr) * | 1980-03-31 | 1981-10-02 | Glaenzer Spicer Sa | Accouplement entre deux arbres rotatifs |
US4346677A (en) * | 1980-09-02 | 1982-08-31 | Nye Norman H | Combustion engine with substantially constant compression |
US4612882A (en) * | 1983-04-11 | 1986-09-23 | Bonfilio Roberto L | Rotating cylinder internal combustion engine |
US5700186A (en) * | 1995-12-04 | 1997-12-23 | Western Atlas Inc. | Motorized spindle with indexing fixture |
US5845397A (en) * | 1997-02-21 | 1998-12-08 | Cummins Engine Company, Inc. | Static timing method for heavy duty diesel engines |
JPH11218037A (ja) | 1997-10-31 | 1999-08-10 | Fev Motorentechnik Gmbh & Co Kg | 調整可能な圧縮比を有するピストン内燃機関 |
ATE241093T1 (de) * | 1999-03-24 | 2003-06-15 | Fev Motorentech Gmbh | Kupplungselement zur verbindung von zwei gleichachsig, hintereinander und mit querabstand zueinander angeordneten, achsparallelen wellen |
JP4062867B2 (ja) * | 2000-07-31 | 2008-03-19 | 日産自動車株式会社 | 可変圧縮比機構を備えた内燃機関 |
-
2000
- 2000-10-16 DE DE10051271.2A patent/DE10051271B4/de not_active Expired - Fee Related
-
2001
- 2001-05-23 EP EP01112514A patent/EP1199452A1/de not_active Withdrawn
- 2001-09-28 JP JP2001300846A patent/JP2002174132A/ja not_active Withdrawn
- 2001-10-05 US US09/971,044 patent/US6588384B2/en not_active Expired - Lifetime
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3861239A (en) * | 1972-06-05 | 1975-01-21 | Edward M Mcwhorter | Internal combustion engine combustion control crankshaft |
DE2935073A1 (de) | 1979-08-30 | 1981-03-12 | Scherf, geb. Kindermann, Eva, 8431 Kemnath | Hubkolbenmotor |
DE2935977A1 (de) | 1979-09-06 | 1981-03-12 | Scherf, geb. Kindermann, Eva, 8431 Kemnath | Hubkolbenmotor. |
DE3004402A1 (de) | 1980-02-07 | 1981-08-13 | Daimler-Benz Ag, 7000 Stuttgart | Kurbeltrieb einer hubkolben-brennkraftmaschine mit waehrend des betriebes veraenderbarem kompressionsverhaeltnis |
DE3030615A1 (de) | 1980-08-13 | 1982-02-18 | Gerhard 8501 Allersberg Mederer | Hubkolbenmotor |
WO1986007115A1 (en) * | 1985-05-24 | 1986-12-04 | Robert Alan Cooper | Crankshaft crank |
DE3601528A1 (de) | 1986-01-20 | 1987-07-23 | Wolfgang Schwarz | Brennkraft-kolbenmaschine, reihenmotor mit variablem verdichtungsverhaeltnis |
DE3644721A1 (de) | 1986-12-30 | 1988-07-14 | Erich Schmid | Vorrichtung fuer eine hubkolbenmaschine mit variablem brennraum |
DE3715391A1 (de) | 1987-05-08 | 1988-12-01 | Gerhard Mederer | Brennkraftmaschine oder sonstiger antrieb |
DE19841381A1 (de) | 1997-10-31 | 1999-05-06 | Fev Motorentech Gmbh & Co Kg | Kolbenbrennkraftmaschine mit einstellbarem Verdichtungsverhältnis |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2007039103A1 (de) * | 2005-10-01 | 2007-04-12 | Daimler Ag | Brennkraftmaschine mit variablem verdichtungsverhältnis |
US7934475B2 (en) | 2005-10-01 | 2011-05-03 | Daimler A G | Internal combustion engine having a variable compression ratio |
WO2012139616A1 (de) * | 2011-04-15 | 2012-10-18 | Daimler Ag | Stelleinrichtung zum variablen einstellen eines verdichtungsverhältnisses einer verbrennungskraftmaschine |
WO2012139618A1 (de) * | 2011-04-15 | 2012-10-18 | Daimler Ag | Verfahren zum betreiben einer stelleinrichtung zum variablen einstellen eines verdichtungsverhältnisses einer verbrennungskraftmaschine |
WO2012139605A1 (de) * | 2011-04-15 | 2012-10-18 | Daimler Ag | Stelleinrichtung zum variablen einstellen eines verdichtungsverhältnisses einer verbrennungskraftmaschine |
Also Published As
Publication number | Publication date |
---|---|
DE10051271B4 (de) | 2015-07-16 |
US20020043229A1 (en) | 2002-04-18 |
DE10051271A1 (de) | 2002-04-25 |
JP2002174132A (ja) | 2002-06-21 |
US6588384B2 (en) | 2003-07-08 |
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