EP1463874A1 - Device for variably actuating the gas exchange valves in reciprocating engines - Google Patents
Device for variably actuating the gas exchange valves in reciprocating enginesInfo
- Publication number
- EP1463874A1 EP1463874A1 EP02799714A EP02799714A EP1463874A1 EP 1463874 A1 EP1463874 A1 EP 1463874A1 EP 02799714 A EP02799714 A EP 02799714A EP 02799714 A EP02799714 A EP 02799714A EP 1463874 A1 EP1463874 A1 EP 1463874A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- cam
- joint
- housing
- valve
- intermediate member
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0021—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of rocker arm ratio
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0063—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
- F01L2013/0068—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "BMW-Valvetronic" type
Definitions
- valve lift curve that is continuously variable during engine operation. Both a change in the stroke profile of intake and exhaust valves and a change only in the intake valves can be advantageous.
- four-part valve gears are known (e.g. DE 26 29 554 AI, DE 38 33 540 C2, DE 43 22 449 AI, DE 42 23 172 CI, BMW-valvetronic). These valve gears enable a continuous change in the valve stroke during engine operation. - r-
- the invention specified in claim 1 is based on the object of meeting the engine requirements for variable valve control better than according to the prior art. These requirements are described in the design of the individual valve lift profiles, the family of valve lift profiles that can be generated, in the size of the mechanical losses due to friction when driving the valves and in the simplicity of the structural design of the valve gear and the associated adjustment mechanism.
- the individual valve lift profiles and the family of valve lift profiles that can be generated must be designed as freely as possible with regard to the opening angle, closing angle, valve lift, valve acceleration profile and phase angle to the crank angle. This is particularly the case with small valve strokes
- the constructive 'design of the valve gear and the adjusting device must be as simple executable. It is particularly important to take into account here that no play o is generated between the transmission links when the valve stroke curve is adjusted. Furthermore, for manufacturing reasons and because of the different thermal expansion of the components, it must be possible to mount the output member in the cylinder head by means of a play compensation element.
- the gearbox consists of a housing (G), a cam (N), an intermediate link (Z) and an output link (A).
- the cam (N) is guided in the: 5 housing (G), for example in the cylinder head in a swivel joint (ng), and actuates the intermediate link (Z) via a cam joint (zn), which in a swivel joint (zg) in the Housing (G) is clearly managed.
- the intermediate link (Z) is operatively connected to the driven link (A) via a cam joint (za).
- This cam joint (za) has a section (Kzar) and a control section (Kzas) on the intermediate member (Z). The one that forms the rest
- the center of the circle coincides with the center of rotation of the swivel joint (zg) between the intermediate member (Z) and the housing (G).
- the output member (A) is clearly guided in the housing (G) in a swivel joint (ag) and transmits the movement to at least one valve (V).
- the invention provides for the position of the cam joint (za) to be changed by a displacement (Vzg) of the position of the swivel joint (zg) or by a displacement (Vag) of the position of the swivel joint (ag).
- the change in the position of the cam joint (za) is described in the area of the valve catch by a
- the output member (A) Due to the design of the output member (A) as in the well-known three-link cam-lever gearboxes (rocker arm and rocker arm gearboxes), the equally well-known and well-tried compensating elements, which play between the gearbox members due to ' manufacturing-related tolerances and / or different thermal deformation of the gearbox members balance, be used.
- the design of the transmission according to the invention enables direct power transmission from the cam (N) to the valve (V).
- the transmission members (Z, A), which cause mass forces and mass moments due to their reciprocating movement, can be designed small, light and dimensionally stable according to the invention.
- the design of the transmission according to the invention also has the advantage of not requiring more space than in the prior art.
- Claim 2 describes the advantageous design of the cam joint (za) between the intermediate member (Z) and the output member (A), in which the curve-defining contour (Kzarl, Kzasl) is attached exclusively to the intermediate member (Z).
- the cam joint (za) on the output link (A) is formed by a rotating body (RA) that can be driven (see Figures 2 and 3).
- RA rotating body
- the contact partners roll around in this cam joint and the tangential movement is shifted onto the bearing of the rotatable roller (RA). Due to the materials and lubrication conditions known from plain bearings and the use of a small friction radius, the friction in this cam joint is reduced.
- the design according to the invention also offers the possibility of using a roller bearing in this contact point. In this way, the tangential movement is carried out entirely by rolling movements. Sliding then no longer occurs in this curve joint (za) and the friction is further reduced.
- the advantageous design of the transmission for changing the valve lift curve in this embodiment is described in claims 3 and 4.
- a bearing of the swivel joint (zg) between the intermediate member (Z) and the housing (G) is described, in which the swivel joint (zg) is variably positioned in an eccentric in the housing (G) to change the valve lift curve.
- the center of the eccentric coincides with the center of the rotatable body (RA) attached to the output member (A) during the valve stop. Twisting the eccentric thus causes the position of the swivel joint (zg) to be shifted (zg) along the circular arc KbVZ (see Figures 2 and 3).
- Claim 4 describes a bearing of the swivel joint (ag) between the output member (A) and the housing (G), in which the position of the swivel joint (ag) can be positioned in an eccentric in the housing (G) in order to change the valve lift curve.
- the center of the eccentric coincides with the center of the swivel joint (zg) between the intermediate member (Z) and the housing (G). Twisting the eccentric causes a displacement (Vagl) of the position of the swivel joint (ag) along the circular arc KbVAl (see Figures 2 and 3).
- a change in the valve lift curve is achieved without a game being generated between the transmission members.
- the advantageous design of the intermediate member (Z) is described as a rocker arm, in which the direction of force in the curve joint (za) between the intermediate member (Z) and the output member (A) substantially opposite the force direction in the curve joint (zn) between the intermediate member (Z) and the cam (N) shows (see Figure 2).
- This embodiment offers the advantage of making the overall height of the transmission and thus of the cylinder head small.
- the advantageous design of the intermediate member (Z) is described as a rocker arm, in which the direction of force in
- Curved joint (za) between the intermediate link (Z) and the driven member (A) is essentially the same as the direction of force in the curved joint (zn) between the intermediate link (Z) and the cam (N) (see Figure 3).
- This embodiment offers the advantage of directly designing the power line from the cam (N) to the valve (V). As a result, the forces acting in the transmission are reduced. This achieves a higher rigidity of the gearbox and at the same time reduces the friction.
- a further advantageous design of the transmission for variable actuation of the charge exchange valves in reciprocating engines which consists of a housing (G), a cam (N), an intermediate member (Z) and an output member (A).
- the cam (N) is guided in a rotatable manner in the housing (G), for example in the cylinder head in a swivel joint (ng) and actuates the intermediate member (Z) via a cam joint (zn), which is connected in a swivel joint (zg) in the housing ( G) is clearly managed.
- the intermediate link (Z) is operatively connected to the driven link (A) via a cam joint (za).
- the curved joint (za) has a section (Kazrl) and a control section (Kazsl) on the output member (A).
- the section forming the rest (Kazrl) is formed by a circular arc, the center of the circle with the center of rotation of the swivel joint (zg) between the
- Curve joint (za) describes itself in the area of the valve catch by a displacement (Vaz) of the curve joint (za) along the section (Kazrl) of the contour of the output member (A) forming the catch.
- the direction of the displacement (Vag2) of the swivel joint (ag) is therefore that of the tangents
- valve lift curve is achieved without any play being generated between the transmission links. This includes for o to achieve high engine speed and quiet operation.
- Claim 8 describes the advantageous design of the cam joint (za) between the intermediate member (Z) and the output member (A), in which 5 the curve-defining contour (Kazrl, Kazsl) is attached exclusively to the output member (A).
- the cam joint (za) is formed by a rotating body (RZ) that can be driven around (see Figure 4).
- RZ rotating body
- the contact partners roll around in this cam joint and the tangential movement is shifted onto the bearing of the circulating roller (RZ). Due to the materials and lubrication conditions known from plain bearings and the use of a small friction radius, the friction in this cam joint is reduced.
- the design according to the invention also offers the possibility of using a roller bearing in this contact point. In this way, the tangential movement is carried out entirely by rolling movements. Sliding then no longer occurs in this curve joint (za) and the friction is further reduced.
- the advantageous arrangement of the transmission members is described, in which the inlet valves (VE1) and the outlet valves (VA1) of a cylinder are driven with only one camshaft (WEA1).
- the intake valve (VE1) of a cylinder is actuated via a cam (NE1), an intermediate link (ZE1) and an output link (AE1)
- the exhaust valve (VA1) of this cylinder is activated via a cam (NA1)
- an intermediate link (ZA1) and a Output link (AA1) actuated Both cams (NE1, NA1) are attached to a camshaft (WEA1) (see Figure 5).
- Claim 14 describes an advantageous embodiment of the transmission in which two or more valves (Vi) of a cylinder are actuated by a cam (N2) via exactly one intermediate link (Z2) via one or more output links (Ai) (cf. Figure 8).
- Vi valves
- N2 cam
- Z2 intermediate link
- Ai output links
- Claim 14 describes an advantageous embodiment of the transmission in which two or more valves (Vi) of a cylinder are actuated by a cam (N2) via exactly one intermediate link (Z2) via one or more output links (Ai) (cf. Figure 8).
- the number of transmission links per motor is reduced and the total costs are reduced.
- the design effort for the adjustment device is reduced and the space required is reduced.
- the position of the intermediate member (Z) during the valve stop ie when the valve is closed and does not move, is not clearly determined kinematically.
- Claim 15 describes the advantageous embodiment of the transmission, in which the intermediate member (Z) is pressed by a spring to the cam (N) of the camshaft (W). If a spring is attached to the intermediate link (Z) in this way, the spring can be designed so that it essentially controls the moving rotating mass of the intermediate link (Z) and the valve spring then only the moving masses of valve (V) and output member ( A) must check, since both springs have the same effect. In this way it is achieved that the forces in the joints of the transmission remain small and the load in the joints is as small as possible. Furthermore, the friction is advantageously reduced in this way.
- the transmission in which at least one further transmission member (GG) is interposed for transmitting motion from the cam (N3) of the camshaft (W3) to the intermediate member (Z3) (see Figure 9).
- the transmission can also be used with camshafts located below and with the camshafts raised.
- Such arrangements of the camshafts offer the advantage of a particularly simple engine construction with a small space requirement.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Fluid-Driven Valves (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10164493 | 2001-12-29 | ||
DE10164493A DE10164493B4 (en) | 2001-12-29 | 2001-12-29 | Device for the variable actuation of the charge exchange valves in reciprocating engines |
PCT/DE2002/004681 WO2003058039A1 (en) | 2001-12-29 | 2002-12-19 | Device for variably actuating the gas exchange valves in reciprocating engines |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1463874A1 true EP1463874A1 (en) | 2004-10-06 |
EP1463874B1 EP1463874B1 (en) | 2008-01-09 |
Family
ID=7711154
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02799714A Expired - Lifetime EP1463874B1 (en) | 2001-12-29 | 2002-12-19 | Device for variably actuating the gas exchange valves in reciprocating engines |
Country Status (12)
Country | Link |
---|---|
US (1) | US6997153B2 (en) |
EP (1) | EP1463874B1 (en) |
JP (1) | JP4456869B2 (en) |
KR (1) | KR100953463B1 (en) |
CN (1) | CN100580228C (en) |
AT (1) | ATE383499T1 (en) |
AU (1) | AU2002364376A1 (en) |
CA (1) | CA2472179C (en) |
DE (2) | DE10164493B4 (en) |
ES (1) | ES2299632T3 (en) |
MX (1) | MXPA04006403A (en) |
WO (1) | WO2003058039A1 (en) |
Families Citing this family (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10164493B4 (en) | 2001-12-29 | 2010-04-08 | Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. | Device for the variable actuation of the charge exchange valves in reciprocating engines |
DE10228022B4 (en) | 2002-06-20 | 2009-04-23 | Entec Consulting Gmbh | Valve lifting device for stroke adjustment of the gas exchange valves of an internal combustion engine |
DE10237104A1 (en) * | 2002-08-13 | 2004-02-26 | Bayerische Motoren Werke Ag | Valve drive for a piston combustion engine has a variable lift control with transmission and actuator elements fixed together |
DE10312961C5 (en) * | 2003-03-24 | 2009-01-29 | Thyssenkrupp Presta Teccenter Ag | Device for the variable actuation of gas exchange valves of internal combustion engines |
DE10312958B4 (en) | 2003-03-24 | 2005-03-10 | Thyssen Krupp Automotive Ag | Device for vairably actuating the gas exchange valves of internal combustion engines and method for operating such a device |
DE10312959B4 (en) * | 2003-03-24 | 2006-10-05 | Thyssenkrupp Automotive Ag | Device for the variable actuation of gas exchange valves of internal combustion engines |
DE102004006186A1 (en) * | 2004-02-06 | 2005-08-25 | Volkswagen Ag | Valve drive for altering gas exchange valve lift in internal combustion engine, includes guide lever secured to spring for biasing intermediate lever against camshaft |
EP1853797B1 (en) | 2005-03-03 | 2011-02-16 | Hydraulik-Ring GmbH | Variable mechanical valve control for an internal combustion engine |
DE102005012081B4 (en) * | 2005-03-03 | 2021-09-16 | Kolbenschmidt Pierburg Innovations Gmbh | Variable mechanical valve control of an internal combustion engine |
DE102005010182B4 (en) * | 2005-03-03 | 2016-05-25 | Kolbenschmidt Pierburg Innovations Gmbh | Variable mechanical valve control of an internal combustion engine |
US7409934B2 (en) * | 2005-12-05 | 2008-08-12 | Delphi Technologies, Inc. | System for variable valvetrain actuation |
US20080141960A1 (en) * | 2005-12-05 | 2008-06-19 | Rohe Jeffrey D | Variable valve actuation system having a crank-based actuation transmission |
US7363893B2 (en) * | 2005-12-05 | 2008-04-29 | Delphi Technologies, Inc. | System for variable valvetrain actuation |
JP4616295B2 (en) * | 2007-02-22 | 2011-01-19 | 三菱自動車工業株式会社 | Variable valve mechanism for internal combustion engine |
EP1972763B1 (en) | 2007-02-22 | 2011-01-19 | Mitsubishi Jidosha Kogyo Kabushiki Kaisha | Variable valve mechanism for internal combustion engine |
ATE524639T1 (en) * | 2007-07-05 | 2011-09-15 | Schaeffler Technologies Gmbh | TRAVEL LEVER FOR A VALVE DRIVE OF AN INTERNAL COMBUSTION ENGINE |
KR101305820B1 (en) * | 2007-12-17 | 2013-09-06 | 현대자동차주식회사 | Continuously Variable Valve Lift Apparatus of Vehicle |
ITCE20100002A1 (en) * | 2010-02-23 | 2011-08-24 | Ottavio Pennacchia | VARIABLE DISTRIBUTION SYSTEMS OF MECHANICAL TYPE 3 AND 4 ACTIVE ELEMENTS |
WO2013014491A1 (en) * | 2011-07-22 | 2013-01-31 | Renault Trucks | Valve actuation mechanism and automotive vehicle comprising such a valve actuation mechanism |
DE102013013913A1 (en) | 2013-08-16 | 2015-02-19 | Alfred Trzmiel | Valve control for a gas exchange valve of an internal combustion engine |
US10280811B2 (en) * | 2016-03-30 | 2019-05-07 | Steve James Duel | Valve train system |
CN106014521A (en) * | 2016-07-13 | 2016-10-12 | 江西五十铃发动机有限公司 | Self-return cam type valve-clearance-free engine rocker mechanism |
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FR2209395A5 (en) * | 1972-12-01 | 1974-06-28 | Peugeot & Renault | |
DE2629554A1 (en) | 1976-07-01 | 1978-01-12 | Daimler Benz Ag | Charge regulator for mixture compression engine - has valve actuator lever moved by cam with adjustable rotation centre |
DE2951361A1 (en) * | 1979-12-20 | 1981-07-02 | Bayerische Motoren Werke AG, 8000 München | Variable-lift IC engine valve actuating gear - has two facing lever arms in actuating train, one with effective length variable |
DE3243509A1 (en) * | 1982-11-24 | 1984-05-24 | Motorenfabrik Hatz Gmbh & Co Kg, 8399 Ruhstorf | Drive arrangement for the valve rockers of internal combustion engines |
JPS60159319A (en) | 1984-01-27 | 1985-08-20 | Suzuki Motor Co Ltd | Valve timing changing device for four-cycle engine |
EP0155434A1 (en) * | 1984-02-20 | 1985-09-25 | Willy Ernst Salzmann | Valve gear with an automatic lash-adjusting device for an internal-combustion engine |
DE3833540A1 (en) * | 1988-10-01 | 1990-04-12 | Peter Prof Dr Ing Kuhn | DEVICE FOR ACTUATING THE VALVES OF INTERNAL COMBUSTION ENGINES WITH VARIABLE VALVE LIFTING CURVE |
WO1993008377A1 (en) * | 1991-10-25 | 1993-04-29 | Peter Kuhn | Device for actuating the valves in an internal-combustion engine by means of rotating cams |
DE4223172C1 (en) | 1992-07-15 | 1993-08-19 | Bayerische Motoren Werke Ag, 8000 Muenchen, De | Cylinder head for IC engine - bearing cover for cam shaft bearing also acts for bearing for eccentric shaft |
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JPH07293216A (en) * | 1994-04-26 | 1995-11-07 | Mitsubishi Automob Eng Co Ltd | Valve system of internal combustion engine |
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JP3787462B2 (en) * | 1999-07-08 | 2006-06-21 | 株式会社日立製作所 | Valve operating device for internal combustion engine |
GB2357131A (en) * | 1999-12-09 | 2001-06-13 | Mechadyne Internat Plc | Valve actuating mechanism |
DE19960742B4 (en) * | 1999-12-16 | 2006-09-28 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Variable valve train, preferably for internal combustion engines |
DE10136612A1 (en) * | 2001-07-17 | 2003-02-06 | Herbert Naumann | Variable lift valve controls |
DE10140635B4 (en) * | 2001-08-13 | 2010-12-02 | Entec Consulting Gmbh | Device for variable valve lift adjustment of gas exchange valves of an internal combustion engine |
DE10164493B4 (en) | 2001-12-29 | 2010-04-08 | Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. | Device for the variable actuation of the charge exchange valves in reciprocating engines |
-
2001
- 2001-12-29 DE DE10164493A patent/DE10164493B4/en not_active Expired - Lifetime
-
2002
- 2002-12-19 ES ES02799714T patent/ES2299632T3/en not_active Expired - Lifetime
- 2002-12-19 MX MXPA04006403A patent/MXPA04006403A/en active IP Right Grant
- 2002-12-19 WO PCT/DE2002/004681 patent/WO2003058039A1/en active IP Right Grant
- 2002-12-19 KR KR1020047010265A patent/KR100953463B1/en active IP Right Grant
- 2002-12-19 EP EP02799714A patent/EP1463874B1/en not_active Expired - Lifetime
- 2002-12-19 JP JP2003558320A patent/JP4456869B2/en not_active Expired - Fee Related
- 2002-12-19 US US10/500,241 patent/US6997153B2/en not_active Expired - Lifetime
- 2002-12-19 AT AT02799714T patent/ATE383499T1/en not_active IP Right Cessation
- 2002-12-19 CN CN02826342A patent/CN100580228C/en not_active Expired - Fee Related
- 2002-12-19 AU AU2002364376A patent/AU2002364376A1/en not_active Abandoned
- 2002-12-19 CA CA2472179A patent/CA2472179C/en not_active Expired - Lifetime
- 2002-12-19 DE DE50211534T patent/DE50211534D1/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO03058039A1 * |
Also Published As
Publication number | Publication date |
---|---|
US6997153B2 (en) | 2006-02-14 |
CA2472179A1 (en) | 2003-07-17 |
CA2472179C (en) | 2012-03-13 |
US20050028766A1 (en) | 2005-02-10 |
CN100580228C (en) | 2010-01-13 |
AU2002364376A1 (en) | 2003-07-24 |
DE10164493B4 (en) | 2010-04-08 |
CN1610789A (en) | 2005-04-27 |
KR100953463B1 (en) | 2010-04-16 |
WO2003058039A1 (en) | 2003-07-17 |
ES2299632T3 (en) | 2008-06-01 |
JP4456869B2 (en) | 2010-04-28 |
MXPA04006403A (en) | 2005-05-27 |
EP1463874B1 (en) | 2008-01-09 |
JP2005514553A (en) | 2005-05-19 |
DE50211534D1 (en) | 2008-02-21 |
DE10164493A1 (en) | 2003-07-10 |
ATE383499T1 (en) | 2008-01-15 |
KR20040072685A (en) | 2004-08-18 |
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