EP2286076B1 - Piston for an internal combustion engine - Google Patents
Piston for an internal combustion engine Download PDFInfo
- Publication number
- EP2286076B1 EP2286076B1 EP09765668.0A EP09765668A EP2286076B1 EP 2286076 B1 EP2286076 B1 EP 2286076B1 EP 09765668 A EP09765668 A EP 09765668A EP 2286076 B1 EP2286076 B1 EP 2286076B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- connecting walls
- counterpressure
- pressure side
- skirt wall
- 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.)
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/02—Pistons having means for accommodating or controlling heat expansion
- F02F3/022—Pistons having means for accommodating or controlling heat expansion the pistons having an oval circumference or non-cylindrical shaped skirts, e.g. oval
Definitions
- the invention relates to a piston for an internal combustion engine according to the preamble of claim 1.
- a piston according to the preamble of claim 1 is known from DE 10 2007 020 447 A1 known.
- the piston coming out of the DE 198 32 091 A1 is known, has skirt wall portions, which are referred to there as a coat, which are larger on the pressure side, as on the counter-pressure side.
- the US 6,345,569 B1 describes a piston with an axially curved piston skirt whose radius is reduced more on the pressure side in the lower region of the shaft than on the counter-pressure side and discloses features which fall under the preamble of claim 1.
- the DE 199 18 328 A1 is another state of the art.
- the invention has for its object to provide a piston for an internal combustion engine having an improved combination of load capacity, especially in the recent trends in the field of engine development, and the piston noise.
- the shaft wall sections can also be referred to as piston coats or piston skirt and are substantially portions of the cylindrical surface corresponding to the inner surface of the cylinder liner.
- piston coats or piston skirt
- piston skirt are substantially portions of the cylindrical surface corresponding to the inner surface of the cylinder liner.
- modern pistons are in those areas where a lateral support is not essential, that is set back in the region of the pin bosses, so that remain in the areas required for the support on both sides of the piston pin, the described shaft wall sections. These may have a shape that changes in the direction of the axis of rotation of the piston.
- the described shaft wall sections are connected by connecting walls, which arise essentially by the resetting of the piston skirt in the area of the pin bosses, and which receive pin bosses.
- the piston according to the invention is characterized in that the connecting walls are curved on the counter-pressure side, and are largely straight on the pressure side. As a result, the counter-pressure side is more elastic than the pressure side.
- the design on the counter-pressure side can be referred to as a " Figure of 8" design and is relatively elastic due to the curvature of the connecting walls. This design has a favorable effect on the noise, since the piston comparatively "soft” strikes on the counter-pressure side. This reduces noise and at the same time is acceptable in terms of component load since it is lower on the back pressure side than on the pressure side.
- the curvature of the connecting walls on the counterpressure side is predominantly in the same direction as the curvature of the skirt wall section on the counterpressure side.
- both the skirt wall portion and the connecting walls on the back pressure side, as seen from the inside of the piston are concavely curved. In the area of the transition of the connecting walls into the pin bosses, viewed from the inside of the piston, an at least slight convex curvature follows.
- the in itself contradictory demands for the absorption of high lateral forces on the one hand and the reduced noise on the other hand combined in an advantageous manner by the different sides of the piston are different and respectively designed according to the local requirements.
- the piston thereby also the increased requirements due to increasing ignition pressures and / or the described shift of the occurrence of the maximum lateral force load is justified.
- the skirt wall section on the counterpressure side is at least partially wider than the skirt wall section on the pressure side.
- the described rigid formation on the pressure side and the more elastic formation on the counter-pressure side is supported by the wall thickness of the connecting walls on the counter-pressure side at least partially reduced compared to the remaining connecting walls, and / or the wall thickness of the shaft wall portion on the pressure side opposite the remaining shaft wall portion at least partially is enlarged.
- a further increase in the elasticity and / or on the pressure side an increase in rigidity can be achieved, which advantageously supports the desired effect according to the invention.
- the figure shows a cross section through the piston according to the invention in the area of the pin bosses.
- FIG. 1 shows a cross section, that is to say a section perpendicular to the axis of rotation of the piston 10 according to the invention. It can be seen the pin bosses 12 and the shaft wall sections 14 and 16, with which the piston is supported in the cylinder liner.
- 14 denotes the skirt wall portion on the back pressure side
- 16 the skirt wall portion on the pressure side.
- the shaft wall portion 16 on the pressure side in the width that is measured substantially in the direction of the piston pin axis A, slightly narrower than the shaft wall portion 14 on the back pressure side.
- the connecting walls 18 and 20 of the two sides differ.
- the connecting walls 20 are largely straight in order to support the shaft wall section 16 on the pressure side as rigidly as possible, so that the loads can be absorbed.
- the connecting walls 18 are curved on the counter-pressure side, so that here a more elastic design is formed, which is advantageous for the piston noises.
- the connecting walls 18 are on the counter-pressure side, starting from the pin bosses 12 initially over a short distance, viewed from the inside 22 of the piston, convexly curved and then go harmoniously into a concave curvature, to which the concave curvature of the shaft wall portion 14 connects on the back pressure side.
- all connecting walls 18 are formed such that they receive the pin bosses 12 on the inside, that is, the side facing the piston interior 22 side. Further, in the illustrated embodiment, the skirt wall portion 16 on the pressure side on the outside extends slightly beyond the connecting walls 20 to provide sufficient area for the support of the piston 10.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Description
Die Erfindung betrifft einen Kolben für einen Verbrennungsmotor nach dem Oberbegriff des Anspruchs 1.The invention relates to a piston for an internal combustion engine according to the preamble of claim 1.
Insbesondere bei den Ottomotoren gibt es in jüngster Zeit einen verstärkten Trend in Richtung Direkteinspritzung in Verbindung mit Turboaufladung. Dies führt zu stetig steigenden Zünddrücken und/oder der Verschiebung des Auftretens der maximalen Seitenkraftbelastung auf den Kolbenschaft in Richtung des Bereichs 20 Grad bis 30 Grad nach dem oberen Totpunkt. Ferner ist stets die Forderung nach möglichst niedrigen Kolbengeräuschen im Auge zu behalten.Particularly in gasoline engines, there has recently been an increased trend towards direct injection in conjunction with turbocharging. This leads to steadily increasing ignition pressures and / or the shift of the occurrence of the maximum side load load on the piston skirt in the direction of the
Ein Kolben nach dem Oberbegriff des Anspruchs 1 ist aus der
Der Erfindung liegt die Aufgabe zugrunde, einen Kolben für einen Verbrennungsmotor zu schaffen, der eine verbesserte Kombination aus Belastbarkeit, insbesondere bei den jüngsten Trends im Bereich der Motorentwicklung, und den Kolbengeräuschen aufweist.The invention has for its object to provide a piston for an internal combustion engine having an improved combination of load capacity, especially in the recent trends in the field of engine development, and the piston noise.
Die Lösung dieser Aufgabe erfolgt durch den im Anspruch 1 beschriebenen Kolben.The solution to this problem is achieved by the piston described in claim 1.
Demzufolge weist dieser zunächst Schaftwandabschnitte auf Druck- und Gegendruckseite auf. Die Schaftwandabschnitte können auch als Kolbenmäntel oder Kolbenhemd bezeichnet werden und stellen im Wesentlichen Abschnitte der zylinderförmigen Fläche dar, die der Innenfläche der Zylinderlaufbuchse entspricht. Moderne Kolben sind jedoch in denjenigen Bereichen, in denen eine seitliche Abstützung nicht unbedingt erforderlich ist, das heißt im Bereich der Bolzennaben, zurückversetzt, so dass in den für die Abstützung erforderlichen Bereichen zu beiden Seiten des Kolbenbolzens die beschriebenen Schaftwandabschnitte verbleiben. Diese können eine sich in Richtung der Rotationsachse des Kolbens verändernde Gestalt aufweisen. Die beschriebenen Schaftwandabschnitte sind durch Verbindungswände verbunden, die im Wesentlichen durch die Zurücksetzung des Kolbenschafts im Bereich der Bolzennaben entstehen, und die Bolzennaben aufnehmen.Consequently, it initially has skirt wall sections on the pressure and counter-pressure side. The shaft wall sections can also be referred to as piston coats or piston skirt and are substantially portions of the cylindrical surface corresponding to the inner surface of the cylinder liner. However, modern pistons are in those areas where a lateral support is not essential, that is set back in the region of the pin bosses, so that remain in the areas required for the support on both sides of the piston pin, the described shaft wall sections. These may have a shape that changes in the direction of the axis of rotation of the piston. The described shaft wall sections are connected by connecting walls, which arise essentially by the resetting of the piston skirt in the area of the pin bosses, and which receive pin bosses.
Der erfindungsgemäße Kolben zeichnet sich dadurch aus, dass die Verbindungswände auf der Gegendruckseite gekrümmt, und auf der Druckseite weitgehend gerade sind. Hierdurch ist die Gegendruckseite elastischer als die Druckseite. Die Gestaltung auf der Gegendruckseite kann als "Figure of 8"-Gestaltung bezeichnet werden und ist durch die Krümmung der Verbindungswände vergleichsweise elastisch. Diese Gestaltung wirkt sich günstig auf die Geräuschentwicklung aus, da der Kolben vergleichsweise "weich" auf der Gegendruckseite anschlägt. Dies vermindert die Geräuschentwicklung und ist gleichzeitig im Hinblick auf die Bauteilbelastung akzeptabel, da diese auf der Gegendruckseite geringer ist als auf der Druckseite.The piston according to the invention is characterized in that the connecting walls are curved on the counter-pressure side, and are largely straight on the pressure side. As a result, the counter-pressure side is more elastic than the pressure side. The design on the counter-pressure side can be referred to as a "Figure of 8" design and is relatively elastic due to the curvature of the connecting walls. This design has a favorable effect on the noise, since the piston comparatively "soft" strikes on the counter-pressure side. This reduces noise and at the same time is acceptable in terms of component load since it is lower on the back pressure side than on the pressure side.
Auf der Druckseite wird durch die weitgehend geraden Verbindungswände, durch die der Schaftwandabschnitt auf der Druckseite abgestützt wird, eine vergleichsweise hohe Steifigkeit erreicht. Diese Gestaltung kann als "Slipper Design" bezeichnet werden, und ist in vorteilhafter Weise geeignet, die infolge der beschriebenen Trends im Rahmen der Motorenwicklung auftretenden hohen Seitenkräfte aufzunehmen.On the pressure side, a comparatively high rigidity is achieved by the largely straight connecting walls, by which the shaft wall section is supported on the pressure side. This design may be referred to as "slipper design", and is advantageously adapted to absorb the high side forces occurring as a result of the described trends in the context of the motor winding.
Ferner ist für eine harmonische und dauerhafte Gestaltung der Gegendruckseite die Krümmung der Verbindungswände auf der Gegendruckseite überwiegend gleichsinnig mit der Krümmung des Schaftwandabschnitts auf der Gegendruckseite. Mit anderen Worten geht die gekrümmte Gestaltung des Schaftwandabschnitts auf der Gegendruckseite an derjenigen Stelle, an der sich der Schaftwandabschnitt von der "gedachten" vollständigen Zylinderform löst, und die Verbindungswände beginnen, in harmonisch nach innen gekrümmte Verbindungswände über. Anders ausgedrückt sind sowohl der Schaftwandabschnitt als auch die Verbindungswände auf der Gegendruckseite, von der Innenseite des Kolbens gesehen, konkav gekrümmt. Im Bereich des Übergangs der Verbindungswände in die Bolzennaben schließt sich, von der Innenseite des Kolbens betrachtet, eine zumindest geringfügige konvexe Krümmung an.Further, for a harmonious and durable design of the counter-pressure side, the curvature of the connecting walls on the counterpressure side is predominantly in the same direction as the curvature of the skirt wall section on the counterpressure side. In other words, the curved configuration of the skirt wall portion on the counter-pressure side at the point where the skirt wall portion disengages from the "imaginary" full cylinder shape and the connecting walls begin to merge into harmonically inwardly curved connecting walls. In other words, both the skirt wall portion and the connecting walls on the back pressure side, as seen from the inside of the piston, are concavely curved. In the area of the transition of the connecting walls into the pin bosses, viewed from the inside of the piston, an at least slight convex curvature follows.
Durch die Erfindung werden die an sich gegenläufigen Forderungen nach der Aufnahme hoher Seitenkräfte einerseits und der verringerten Geräuschentwicklung andererseits in vorteilhafter Weise kombiniert, indem die unterschiedlichen Seiten des Kolbens unterschiedlich und jeweils den dortigen Anforderungen entsprechend gestaltet werden. Insbesondere hat sich bei ersten Versuchen herausgestellt, dass der Kolben hierdurch auch den erhöhten Anforderungen infolge steigender Zünddrücke und/oder der beschriebenen Verschiebung des Auftretens der maximalen Seitenkraftbelastung gerecht wird.By the invention, the in itself contradictory demands for the absorption of high lateral forces on the one hand and the reduced noise on the other hand combined in an advantageous manner by the different sides of the piston are different and respectively designed according to the local requirements. In particular, it has been found in the first tests that the piston thereby also the increased requirements due to increasing ignition pressures and / or the described shift of the occurrence of the maximum lateral force load is justified.
Vorteilhafte Weiterbildungen des erfindungsgemäßen Kolbens sind in den weiteren Ansprüchen beschrieben.Advantageous developments of the piston according to the invention are described in the further claims.
Für die Ausbildung der gewünschten Elastizität auf der Gegendruckseite wird derzeit bevorzugt, den Schaftwandabschnitt auf der Gegendruckseite zumindest bereichsweise breiter auszubilden als den Schaftwandabschnitt auf der Druckseite.For the formation of the desired elasticity on the counterpressure side, it is currently preferred to make the skirt wall section on the counterpressure side at least partially wider than the skirt wall section on the pressure side.
Die beschriebene steife Ausbildung auf der Druckseite und die elastischere Ausbildung auf der Gegendruckseite wird dadurch unterstützt, dass die Wanddicke der Verbindungswände auf der Gegendruckseite zumindest bereichsweise gegenüber den übrigen Verbindungswänden verringert, und/oder die Wanddicke des Schaftwandabschnitts auf der Druckseite gegenüber dem übrigen Schaftwandabschnitt zumindest bereichsweise vergrößert ist. Hierdurch kann auf der Gegendruckseite eine weitere Erhöhung der Elastizität und/oder auf der Druckseite eine Erhöhung der Steifigkeit erreicht werden, was die erfindungsgemäß angestrebte Wirkung in vorteilhafter Weise unterstützt.The described rigid formation on the pressure side and the more elastic formation on the counter-pressure side is supported by the wall thickness of the connecting walls on the counter-pressure side at least partially reduced compared to the remaining connecting walls, and / or the wall thickness of the shaft wall portion on the pressure side opposite the remaining shaft wall portion at least partially is enlarged. In this way, on the counter-pressure side, a further increase in the elasticity and / or on the pressure side an increase in rigidity can be achieved, which advantageously supports the desired effect according to the invention.
Nachfolgend wird ein in der Zeichnung dargestelltes Ausführungsbeispiel näher erläutert.Hereinafter, an embodiment shown in the drawing will be explained in more detail.
Die Figur zeigt einen Querschnitt durch den erfindungsgemäßen Kolben im Bereich der Bolzennaben.The figure shows a cross section through the piston according to the invention in the area of the pin bosses.
In Figur 1 ist ein Querschnitt, das heißt ein Schnitt senkrecht zur Rotationsachse des erfindungsgemäßen Kolbens 10 gezeigt. Es sind die Bolzennaben 12 sowie die Schaftwandabschnitte 14 bzw. 16 zu erkennen, mit denen der Kolben in der Zylinderlaufbuchse abgestützt ist. In der Figur bezeichnet 14 den Schaftwandabschnitt auf der Gegendruckseite, und 16 den Schaftwandabschnitt auf der Druckseite. Wie ein Vergleich der beiden Seiten anhand der Figur zeigt, ist der Schaftwandabschnitt 16 auf der Druckseite in der Breite, das heißt im Wesentlichen in Richtung der Kolbenbolzenachse A gemessen, etwas schmäler als der Schaftwandabschnitt 14 auf der Gegendruckseite. Darüber hinaus unterscheiden sich die Verbindungswände 18 bzw. 20 der beiden Seiten. Auf der Druckseite sind die Verbindungswände 20 weitgehend gerade, um den Schaftwandabschnitt 16 auf der Druckseite möglichst steif abzustützen, so dass die Belastungen aufgenommen werden können. Dagegen sind die Verbindungswände 18 auf der Gegendruckseite gekrümmt, so dass hier eine elastischere Gestaltung ausgebildet wird, welche vorteilhaft für die Kolbengeräusche ist. Bei dem gezeigten Ausführungsbeispiel sind die Verbindungswände 18 auf der Gegendruckseite ausgehend von den Bolzennaben 12 zunächst über ein kurzes Stück, von der Innenseite 22 des Kolbens betrachtet, konvex gekrümmt und gehen dann harmonisch in eine konkave Krümmung über, an die sich die konkave Krümmung des Schaftwandabschnitts 14 auf der Gegendruckseite anschließt.FIG. 1 shows a cross section, that is to say a section perpendicular to the axis of rotation of the
Bei dem gezeigten Ausführungsbeispiel sind sämtliche Verbindungswände 18 derart ausgebildet, dass sie die Bolzennaben 12 an deren Innenseite, das heißt der zu dem Kolbeninneren 22 gerichteten Seite aufnehmen. Ferner erstreckt sich bei dem gezeigten Ausführungsbeispiel der Schaftwandabschnitt 16 auf der Druckseite an der Außenseite ein wenig über die Verbindungswände 20 hinaus, um ausreichend Fläche für die Abstützung des Kolbens 10 zur Verfügung zu stellen.In the embodiment shown, all connecting
Claims (3)
- Piston (10) for an internal combustion engine, having skirt wall sections (14, 16) on pressure-side and counterpressure-side and connecting walls (18, 20) between the skirt wall sections (14, 16), wherein the connecting walls (18) are curved on the counterpressure-side and the connecting walls (20) are substantially straight on the pressure-side, wherein
the curve of the connecting walls (18) on the counterpressure-side is predominantly in the same direction as the curve of the skirt wall section (14) on the counterpressure-side, such that the counterpressure-side is more resilient than the pressure-side,
wherein the connecting walls (18) on the counterpressure-side, starting from pin bosses (12) are curved in a convex manner initially across a short piece, viewed from the inside (22) of the piston, and then transition harmoniously into a concave curve, to which the concave curve of the skirt wall section (14) on the counterpressure-side adjoins, characterised in that
the wall thickness of the connecting walls (20) on the pressure-side is, at least in sections, enlarged in comparison with the rest of the connecting walls. - Piston according to claim 1, characterised in that the skirt wall section (14) on the counterpressure-side is, at least in sections, broader than the skirt wall section (16) on the pressure-side.
- Piston according to any of the preceding claims, wherein the wall thickness of the skirt wall section (16) on the pressure-side is, at least in sections, enlarged in comparison with the rest of the skirt wall section.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PL09765668T PL2286076T3 (en) | 2008-06-19 | 2009-04-22 | Piston for an internal combustion engine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008002536.4A DE102008002536B4 (en) | 2008-06-19 | 2008-06-19 | Piston for an internal combustion engine |
PCT/EP2009/054816 WO2009153088A1 (en) | 2008-06-19 | 2009-04-22 | Piston for an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2286076A1 EP2286076A1 (en) | 2011-02-23 |
EP2286076B1 true EP2286076B1 (en) | 2019-06-26 |
Family
ID=40908577
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09765668.0A Active EP2286076B1 (en) | 2008-06-19 | 2009-04-22 | Piston for an internal combustion engine |
Country Status (7)
Country | Link |
---|---|
US (1) | US10024269B2 (en) |
EP (1) | EP2286076B1 (en) |
DE (1) | DE102008002536B4 (en) |
ES (1) | ES2739465T3 (en) |
HU (1) | HUE045390T2 (en) |
PL (1) | PL2286076T3 (en) |
WO (1) | WO2009153088A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011002653A1 (en) | 2011-01-13 | 2012-07-19 | Federal-Mogul Nürnberg GmbH | Piston for use in internal combustion engines |
BR102012032765A2 (en) | 2012-12-20 | 2014-09-30 | Mahle Int Gmbh | INTERNAL COMBUSTION ENGINE PISTON |
DE102015217911A1 (en) * | 2015-09-18 | 2017-03-23 | Mahle International Gmbh | Piston for an internal combustion engine |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19918328A1 (en) * | 1998-04-24 | 1999-10-28 | Unisia Jecs Corp | Piston for internal combustion engine |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2149862A (en) * | 1936-07-20 | 1939-03-07 | Adolph L Nelson | Piston |
IT1182507B (en) * | 1985-07-12 | 1987-10-05 | Ae Borgo Spa | PISTONS WITH ASYMMETRIC PROFILE FOR INTERNAL COMBUSTION ENGINES |
US5000078A (en) * | 1987-04-18 | 1991-03-19 | Mahle Gmbh | Light metal trunk piston for internal combustion engines |
DE4109160C3 (en) * | 1991-03-20 | 2000-11-30 | Federal Mogul Nuernberg Gmbh | Pistons for internal combustion engines |
JPH1136978A (en) | 1997-07-16 | 1999-02-09 | Unisia Jecs Corp | Piston of internal combustion engine |
JP2000282951A (en) * | 1999-01-29 | 2000-10-10 | Honda Motor Co Ltd | Piston for internal-combustion engine |
DE19908670C2 (en) * | 1999-02-27 | 2001-02-22 | Federal Mogul Burscheid Gmbh | Pistons for internal combustion engines |
GB2367602B (en) * | 2000-10-07 | 2004-10-27 | Federal Mogul Bradford Ltd | Piston for internal combustion engine |
US7302884B2 (en) * | 2005-11-03 | 2007-12-04 | Dresser, Inc. | Piston |
DE102007020447A1 (en) | 2007-04-27 | 2008-10-30 | Mahle International Gmbh | Piston for an internal combustion engine |
-
2008
- 2008-06-19 DE DE102008002536.4A patent/DE102008002536B4/en not_active Expired - Fee Related
-
2009
- 2009-04-22 ES ES09765668T patent/ES2739465T3/en active Active
- 2009-04-22 US US12/999,719 patent/US10024269B2/en active Active
- 2009-04-22 EP EP09765668.0A patent/EP2286076B1/en active Active
- 2009-04-22 HU HUE09765668A patent/HUE045390T2/en unknown
- 2009-04-22 PL PL09765668T patent/PL2286076T3/en unknown
- 2009-04-22 WO PCT/EP2009/054816 patent/WO2009153088A1/en active Application Filing
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19918328A1 (en) * | 1998-04-24 | 1999-10-28 | Unisia Jecs Corp | Piston for internal combustion engine |
Also Published As
Publication number | Publication date |
---|---|
US20110168124A1 (en) | 2011-07-14 |
HUE045390T2 (en) | 2019-12-30 |
ES2739465T3 (en) | 2020-01-31 |
DE102008002536B4 (en) | 2015-02-12 |
EP2286076A1 (en) | 2011-02-23 |
US10024269B2 (en) | 2018-07-17 |
DE102008002536A1 (en) | 2010-01-07 |
PL2286076T3 (en) | 2019-10-31 |
WO2009153088A1 (en) | 2009-12-23 |
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