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EP2321513B2 - Piston for an internal combustion engine - Google Patents

Piston for an internal combustion engine Download PDF

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Publication number
EP2321513B2
EP2321513B2 EP09776111.8A EP09776111A EP2321513B2 EP 2321513 B2 EP2321513 B2 EP 2321513B2 EP 09776111 A EP09776111 A EP 09776111A EP 2321513 B2 EP2321513 B2 EP 2321513B2
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EP
European Patent Office
Prior art keywords
piston
outer circumferential
friction
weld seam
circumferential
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.)
Not-in-force
Application number
EP09776111.8A
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German (de)
French (fr)
Other versions
EP2321513A1 (en
EP2321513B1 (en
Inventor
Peter Kemnitz
Carmen Klusch
Rainer Scharp
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Mahle International GmbH
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Mahle International GmbH
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Publication date
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Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP2321513A1 publication Critical patent/EP2321513A1/en
Publication of EP2321513B1 publication Critical patent/EP2321513B1/en
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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 
    • F02F3/16—Pistons  having cooling means
    • F02F3/20—Pistons  having cooling means the means being a fluid flowing through or along piston
    • F02F3/22—Pistons  having cooling means the means being a fluid flowing through or along piston the fluid being liquid
    • 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 
    • F02F3/0015—Multi-part pistons
    • F02F3/003—Multi-part pistons the parts being connected by casting, brazing, welding or clamping

Definitions

  • the present invention relates to a piston for an internal combustion engine, having a piston lower part and a piston upper part, which are joined together by friction welding and form an outer circumferential cooling channel, wherein the piston upper part has an outer circumferential land land and a ring groove provided below the land ridge encircling ring whose inner wall delimits the peripheral outer cooling channel, wherein the upper piston part has an outer circumferential support element and the lower piston part has an outer circumferential support element, which form an outer circumferential friction weld below the annular part.
  • a friction welded piston is also used in the US 2003/0051694 A1 shown.
  • the JP 2003/025076 A discloses a generic piston whose supporting elements forming the outer friction weld are arranged radially inwards.
  • the object of the present invention is thus to further develop a generic piston so that the risk of tension is reduced and the stability of the piston is improved.
  • the solution consists in a piston with the features of claim 1. According to the invention it is provided that the width of the outer circumferential friction weld at most is just as large as the wall thickness between the respective groove bottom of the annular grooves and the inner wall of the ring section, and that in the peripheral outer cooling channel in the region of the outer peripheral friction weld a trough is formed, in which a weld bead is received.
  • the width of the inner friction weld is less than previously known in the art. Nevertheless, the piston according to the invention is very stable for the reasons described above.
  • the inner support element (27) of the upper piston part (12) and the inner support element (28) of the piston lower part (15) are formed such that along the inner circumferential friction weld (30, 130) in the outer circumferential cooling channel (19 ) and / or in the inner region (24) a trough (31) is formed, in which a Sch spawulst (32) is received.
  • the piston lower part 15 has a piston shaft 14 and provided with hub bores 17 pin bosses 16.
  • the piston upper part 12 has a piston bottom 13, which is provided in the exemplary embodiment with a combustion bowl 11.
  • an outer circumferential fire bar 18 connects.
  • a circumferential ring portion 20 is provided, which is provided in the embodiment with three circumferential annular grooves 21, 22, 23 for piston rings (not shown).
  • the piston lower part 15 and the piston upper part 12 also together form an outer circumferential cooling channel 19.
  • the inner friction weld 30 has a width b2, which in the embodiment according to the FIGS. 1 and 2A in the context of the usual manufacturing tolerances is smaller than the width b1 of the outer friction weld 29. But the width b2 can also be exactly as large as the width b1.
  • the outer and inner support elements 26, 28 and 25, 27 of the lower piston part 15 and the piston upper part 12 are configured in the embodiment in the region of the friction welds 30, 29 such that the outer circumferential cooling channel 19 and the inner region 24 aligned, in the exemplary embodiment rotating , Troughs 31 are formed.
  • the Sch undulste 32 are added, which may arise during the Reibsch dovorgangs.
  • the surfaces of the walls of the cooling channel 19 are comparatively smooth.
  • the volume of the cooling channel 19 for receiving cooling oil remains unaffected.
  • the cooling oil in the cooling channel 19 can flow substantially without interference. The cooling effect of the cooling oil thus remains substantially preserved in this advantageous embodiment of the piston according to the invention.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Pistons, Piston Rings, And Cylinders (AREA)

Abstract

A piston for an internal combustion engine has a lower piston part and an upper piston part that are connected with one another by friction welding and form an outer circumferential cooling channel. The upper piston part has a circumferential ring belt provided with ring grooves, the inner wall of which delimits the circumferential outer cooling channel. An outer circumferential friction-weld seam is provided below the ring belt, the width of which seam is less than or equal to the wall thickness between the groove root of the ring grooves and the inner wall of the ring belt.

Description

Die vorliegende Erfindung betrifft einen Kolben für einen Verbrennungsmotor, mit einem Kolbenunterteil und einem Kolbenoberteil, die durch Reibschweißen miteinander verbunden sind und einen äußeren umlaufenden Kühlkanal bilden, wobei das Kolbenoberteil einen äußeren umlaufenden Feuersteg sowie eine unterhalb des Feuerstegs angeordnete, mit Ringnuten versehene umlaufende Ringpartie aufweist, deren Innenwand den umlaufenden äußeren Kühlkanal begrenzt, wobei das Kolbenoberteil ein äußeres umlaufendes Stützelement und das Kolbenunterteil ein äußeres umlaufendes Stützelement aufweist, die unterhalb der Ringpartie eine äußere umlaufende Reibschweißnaht bilden.The present invention relates to a piston for an internal combustion engine, having a piston lower part and a piston upper part, which are joined together by friction welding and form an outer circumferential cooling channel, wherein the piston upper part has an outer circumferential land land and a ring groove provided below the land ridge encircling ring whose inner wall delimits the peripheral outer cooling channel, wherein the upper piston part has an outer circumferential support element and the lower piston part has an outer circumferential support element, which form an outer circumferential friction weld below the annular part.

Ein gattungsgemäßer Kolben ist in der US 6,557,514 B1 offenbart. Die äußere umlaufende Reibschweißnaht zwischen dem Kolbenunterteil und dem Kolbenoberteil ist im Bereich der Ringpartie zwischen zwei Ringnuten angeordnet. Hierbei besteht jedoch die Gefahr, dass beim Reibschweißen Spannungen aufgebaut werden, welche die Stabilität des Kolbens beeinträchtigen.A generic piston is in the US 6,557,514 B1 disclosed. The outer peripheral friction weld between the piston lower part and the piston upper part is arranged in the region of the ring part between two annular grooves. However, there is the risk that stresses are built up during friction welding, which affect the stability of the piston.

Ein reibgeschweißter Kolben wird auch in der US 2003/0051694 A1 gezeigt.A friction welded piston is also used in the US 2003/0051694 A1 shown.

Die JP 2003/025076 A offenbart einen gattungsgemäßen Kolben, dessen die äußere Reibschweißnaht bildende Stützelemente radial nach innen zurückgesetzt angeordnet ist.The JP 2003/025076 A discloses a generic piston whose supporting elements forming the outer friction weld are arranged radially inwards.

Die Aufgabe der vorliegenden Erfindung besteht somit darin, einen gattungsgemäßen Kolben so weiterzuentwickeln, dass die Gefahr von Spannungen verringert und die Stabilität des Kolbens verbessert wird.The object of the present invention is thus to further develop a generic piston so that the risk of tension is reduced and the stability of the piston is improved.

Die Lösung besteht in einem Kolben mit den Merkmalen des Patentanspruchs 1. Erfindungsgemäß ist vorgesehen, dass die Breite der äußeren umlaufenden Reibschweißnaht höchstens genauso groß ist wie die Wanddicke zwischen dem jeweiligen Nutgrund der Ringnuten und der Innenwand der Ringpartie, und dass im umlaufenden äußeren Kühlkanal im Bereich der äußeren umlaufenden Reibschweißnaht eine Mulde gebildet ist, in die ein Schweißwulst aufgenommen ist.The solution consists in a piston with the features of claim 1. According to the invention it is provided that the width of the outer circumferential friction weld at most is just as large as the wall thickness between the respective groove bottom of the annular grooves and the inner wall of the ring section, and that in the peripheral outer cooling channel in the region of the outer peripheral friction weld a trough is formed, in which a weld bead is received.

Im Rahmen der vorliegenden Offenbarung ist der Ausdruck "höchstens genauso groß" so zu verstehen, dass übliche Fertigungstoleranzen mit umfasst sind. Die Breite der äußeren umlaufenden Reibschweißnaht und die Wanddicke liegen also im Rahmen der üblichen Fertigungstoleranzen.In the context of the present disclosure, the expression "at most just as large" is to be understood as meaning that customary manufacturing tolerances are included. The width of the outer circumferential friction weld and the wall thickness are therefore within the usual manufacturing tolerances.

Der erfindungsgemäße Kolben ist trotz der gegenüber dem Stand der Technik deutlich verringerten Breite der Reibschweißnaht (und, damit einhergehend, der deutlich verringerten Wanddicke der Ringpartie im Bereich der Reibschweißnaht) sehr stabil. Zugleich weist der erfindungsgemäße Kolben eine verbesserte Flexibilität auf. Somit kann der erfindungsgemäße Kolben die beim Verbrennungsvorgang auf den Kolbenboden einwirkende Kräfte besser aufnehmen und gleichmäßiger über seine Struktur ableiten. Ein weiterer großer Vorteil des erfindungsgemäßen Kolbens besteht darin, dass durch die Verringerung der Wanddicke im Bereich der äußeren umlaufenden Reibschweißnaht eine Material- und Gewichtsersparnis erzielt wird. Erfindungsgemäß bilden die äußeren Stützelemente von Kolbenoberteil und Kolbenunterteil eine Mulde innerhalb des Kühlkanals, in der ein Schweißwulst aufgenommen ist. Damit wird entlang der Reibschweißnaht eine möglichst gleichmäßige Oberfläche erhalten, und insbesondere wird vermieden, die Größe des Kühlkanals durch einen in diesen hineinragenden Schweißwulst zu reduzieren sowie den Kühlölfluss durch Verwirbelungen u. dgl. zu beeinträchtigen.The piston according to the invention is very stable despite the significantly reduced width of the friction weld seam (and, concomitantly, the significantly reduced wall thickness of the ring section in the area of the friction weld seam) compared with the prior art. At the same time, the piston according to the invention has improved flexibility. Thus, the piston according to the invention can better absorb the forces acting on the piston crown in the combustion process and derive more uniformly about its structure. Another great advantage of the piston according to the invention is that a material and weight saving is achieved by reducing the wall thickness in the region of the outer circumferential friction weld. According to the invention, the outer support elements of piston upper part and lower piston part form a depression within the cooling channel, in which a weld bead is received. Thus, along the friction weld a uniform surface as possible, and in particular it is avoided to reduce the size of the cooling channel by a protruding into this Schweißwulst and the cooling oil flow through turbulence u. Like. Affect.

Vorteilhafte Weiterbildungen ergeben sich aus den Unteransprüchen.Advantageous developments emerge from the subclaims.

Die Breite der äußeren umlaufenden Reibschweißnaht ist vorzugsweise genauso groß ist wie die Wanddicke zwischen dem jeweiligen Nutgrund der Ringnuten und der Innenwand der Ringpartie, wodurch ein optimaler Kraftfluss bei optimaler Materialausnutzung erzielt werden.The width of the outer circumferential friction weld is preferably the same as the wall thickness between the respective groove bottom of the annular grooves and the inner wall of the ring part, whereby an optimal power flow with optimum material utilization can be achieved.

Der erfindungsgemäße Kolben weist zwischen einem Innenbereich und dem äußeren umlaufenden Kühlkanal Stützelemente auf, die über eine innere umlaufende Reibschweißnaht miteinander verbunden sind.The piston according to the invention has between an inner region and the outer circumferential cooling channel supporting elements, which are connected to each other via an inner circumferential friction weld.

Die Breite der inneren umlaufenden Reibschweißnaht kann größer/gleich oder kleiner als die Breite der äußeren umlaufenden Reibschweißnaht sein. Beide Reibschweißverbindungen werden in einem Arbeitsgang ausgebildet.The width of the inner peripheral friction weld may be greater than or equal to or less than the width of the outer circumferential friction weld. Both Reibschweißverbindungen be formed in one operation.

Auch bei dieser bevorzugten Ausgestaltung der vorliegenden Erfindung ist die Breite der inneren Reibschweißnaht geringer als bisher im Stand der Technik bekannt. Dennoch ist der erfindungsgemäße Kolben aus den oben beschriebenen Gründen sehr stabil.Also in this preferred embodiment of the present invention, the width of the inner friction weld is less than previously known in the art. Nevertheless, the piston according to the invention is very stable for the reasons described above.

Es ist zweckmäßig, dass auch das innere Stützelement (27) des Kolbenoberteils (12) und das innere Stützelement (28) des Kolbenunterteils (15) derart ausgebildet sind, dass entlang der inneren umlaufenden Reibschweißnaht (30, 130) im äußeren umlaufenden Kühlkanal (19) und/oder im Innenbereich (24) eine Mulde (31) gebildet ist, in die ein Schweißwulst (32) aufgenommen ist.It is expedient that the inner support element (27) of the upper piston part (12) and the inner support element (28) of the piston lower part (15) are formed such that along the inner circumferential friction weld (30, 130) in the outer circumferential cooling channel (19 ) and / or in the inner region (24) a trough (31) is formed, in which a Schweißwulst (32) is received.

Ausführungsbeispiele der vorliegenden Erfindung werden im Folgenden anhand der beigefügten Zeichnungen näher erläutert. Es zeigen in einer schematischen, nicht maßstabsgetreuen Darstellung:

Figur 1
ein erstes Ausführungsbeispiel eines erfindungsgemäßen Kolbens im Schnitt, wobei die linke Hälfte der Darstellung gegenüber der rechten Hälfte um 90° gedreht ist;
Figur 2A
eine vergrößerte Teildarstellung des Kolbens gemäß Figur 1;
Figur 2B
eine vergrößerte Teildarstellung eines weiteren Ausführungsbeispiels eines erfindungsgemäßen Kolbens.
Embodiments of the present invention are explained in more detail below with reference to the accompanying drawings. In a schematic, not to scale representation:
FIG. 1
a first embodiment of a piston according to the invention in section, wherein the left half of the representation with respect to the right half is rotated by 90 °;
FIG. 2A
an enlarged partial view of the piston according to FIG. 1 ;
FIG. 2B
an enlarged partial view of another embodiment of a piston according to the invention.

Die Figuren 1 und 2A zeigen ein erstes Ausführungsbeispiel eines erfindungsgemäßen Kolbens 10. Der Kolben 10 weist ein Kolbenunterteil 15 und ein Kolbenoberteil 12 auf, die durch Reibschweißen miteinander verbunden sind. Das Kolbenunterteil 15 und das Kolbenoberteil 12 können aus jedem metallischen Werkstoff bestehen, der einer Bearbeitung durch Reibschweißen zugänglich ist.The FIGS. 1 and 2A show a first embodiment of a piston 10 according to the invention. The piston 10 has a piston lower part 15 and a piston upper part 12, which are interconnected by friction welding. The piston lower part 15 and the upper piston part 12 may consist of any metallic material that is accessible for machining by friction welding.

Das Kolbenunterteil 15 weist einen Kolbenschaft 14 sowie mit Nabenbohrungen 17 versehene Bolzennaben 16 auf. Das Kolbenoberteil 12 weist einen Kolbenboden 13 auf, der im Ausführungsbeispiel mit einer Brennraummulde 11 versehen ist. An den Kolbenboden 13 schließt sich ein äußerer umlaufender Feuersteg 18 an. Unterhalb des Feuerstegs 18 ist eine umlaufende Ringpartie 20 vorgesehen, die im Ausführungsbeispiel mit drei umlaufenden Ringnuten 21, 22, 23 für Kolbenringe (nicht dargestellt) versehen ist. Das Kolbenunterteil 15 und das Kolbenoberteil 12 bilden ferner gemeinsam einen äußeren umlaufenden Kühlkanal 19.The piston lower part 15 has a piston shaft 14 and provided with hub bores 17 pin bosses 16. The piston upper part 12 has a piston bottom 13, which is provided in the exemplary embodiment with a combustion bowl 11. At the piston head 13, an outer circumferential fire bar 18 connects. Below the top land 18, a circumferential ring portion 20 is provided, which is provided in the embodiment with three circumferential annular grooves 21, 22, 23 for piston rings (not shown). The piston lower part 15 and the piston upper part 12 also together form an outer circumferential cooling channel 19.

Zur Bildung der Reibschweißverbindungen ist das Kolbenoberteil 12 mit einem umlaufenden äußeren Stützelement 25 und einem umlaufenden inneren Stützelement 27 versehen. In korrespondierender Weise ist das Kolbenunterteil 15 ebenfalls mit einem umlaufenden äußeren Stützelement 26 und einem umlaufenden inneren Stützelement 28 versehen. Hierbei weisen die äußeren Mantelfläche 25a des Stützelements 25 des Kolbenoberteils 12, die äußere Mantelfläche 26a des Stützelements 26 des Kolbenunterteils 15 sowie die äußere Mantelfläche 12a des Feuerstegs 12 denselben Außendurchmesser D auf.To form the Reibschweißverbindungen the piston upper part 12 is provided with a circumferential outer support member 25 and a circumferential inner support member 27. In a corresponding manner, the lower piston part 15 is likewise provided with a circumferential outer support element 26 and a circumferential inner support element 28. In this case, the outer circumferential surface 25a of the support element 25 of the upper piston part 12, the outer lateral surface 26a of the support element 26 of the lower piston part 15 and the outer circumferential surface 12a of the top land 12 have the same outer diameter D.

Die äußeren Stützelemente 25, 26 bilden unterhalb der Ringpartie 20 eine äußere umlaufende Reibschweißnaht 29, während die inneren Stützelemente 27, 28 unterhalb des Kolbenbodens 13 eine innere umlaufende Reibschweißnaht 30 bilden. Die inneren Stützelemente 27, 28 trennen den äußeren umlaufenden Kühlkanal 19 von einem Innenbereich 24 des Kolbens 10. Die Innenwand 20' der Ringpartie 20 bildet die äußere Wand des äußeren umlaufenden Kühlkanals 19.The outer support elements 25, 26 form an outer circumferential friction weld 29 below the ring section 20, while the inner support elements 27, 28 form an inner circumferential friction weld 30 below the piston head 13. The inner support elements 27, 28 separate the outer circumferential cooling channel 19 from an inner region 24 of the piston 10. The inner wall 20 'of the annular portion 20 forms the outer wall of the outer circumferential cooling channel 19th

Die äußere Reibschweißnaht 29 weist eine Breite b1 auf, die im Ausführungsbeispiel im Rahmen der üblichen Fertigungstoleranzen gleich groß ist wie die Wanddicke d der Ringpartie 20 zwischen dem jeweiligen Nutgrund 21', 22', 23' der Ringnuten 21, 22, 23 und der Innenwand 20' der Ringpartie 20.The outer Reibschweißnaht 29 has a width b1, which is the same in the embodiment in the context of the usual manufacturing tolerances as the wall thickness d of the ring portion 20 between the respective groove bottom 21 ', 22', 23 'of the annular grooves 21, 22, 23 and the inner wall 20 'of the ring section 20.

Die innere Reibschweißnaht 30 weist eine Breite b2 auf, die im Ausführungsbeispiel gemäß den Figuren 1 und 2A im Rahmen der üblichen Fertigungstoleranzen geringer ist als die Breite b1 der äußeren Reibschweißnaht 29. Die Breite b2 kann aber auch genau so groß sein wie die Breite b1.The inner friction weld 30 has a width b2, which in the embodiment according to the FIGS. 1 and 2A in the context of the usual manufacturing tolerances is smaller than the width b1 of the outer friction weld 29. But the width b2 can also be exactly as large as the width b1.

Die äußeren und inneren Stützelemente 26, 28 bzw. 25, 27 des Kolbenunterteils 15 und des Kolbenoberteils 12 sind im Ausführungsbeispiel im Bereich der Reibschweißnähte 30, 29 derart ausgestaltet, dass zum äußeren umlaufenden Kühlkanal 19 bzw. zum Innenbereich 24 hin ausgerichtete, im Ausführungsbeispiel umlaufende, Mulden 31 gebildet sind. In den Mulden 31 sind die Schweißwulste 32 aufgenommen, die ggf. während des Reibschweißvorgangs entstehen. Auf diese Weise sind im Ausführungsbeispiel die Oberflächen der Wände des Kühlkanals 19 vergleichsweise glatt. Dadurch bleibt das Volumen des Kühlkanals 19 zur Aufnahme von Kühlöl unbeeinträchtigt. Ferner kann das Kühlöl im Kühlkanal 19 im Wesentlichen störungsfrei strömen. Die Kühlwirkung des Kühlöls bleibt somit bei dieser vorteilhaften Ausgestaltung des erfindungsgemäßen Kolbens im Wesentlichen erhalten.The outer and inner support elements 26, 28 and 25, 27 of the lower piston part 15 and the piston upper part 12 are configured in the embodiment in the region of the friction welds 30, 29 such that the outer circumferential cooling channel 19 and the inner region 24 aligned, in the exemplary embodiment rotating , Troughs 31 are formed. In the wells 31, the Schweißwulste 32 are added, which may arise during the Reibschweißvorgangs. In this way, in the exemplary embodiment, the surfaces of the walls of the cooling channel 19 are comparatively smooth. As a result, the volume of the cooling channel 19 for receiving cooling oil remains unaffected. Furthermore, the cooling oil in the cooling channel 19 can flow substantially without interference. The cooling effect of the cooling oil thus remains substantially preserved in this advantageous embodiment of the piston according to the invention.

Figur 2B zeigt in einer mit der Figur 2A vergleichbaren Darstellung ein weiteres Ausführungsbeispiel eines Kolbens 110. Der Kolben 110 unterscheidet sich vom Kolben 10 nur dadurch, dass die innere Reibschweißnaht 130 eine Breite b3 aufweist, die im Rahmen der üblichen Fertigungstoleranzen größer ist als die Breite b1 der äußeren Reibschweißnaht 29. FIG. 2B shows in one with the FIG. 2A The piston 110 differs from the piston 10 only in that the internal friction weld 130 has a width b3, which is greater than the width b1 of the outer friction weld 29 in the context of the usual manufacturing tolerances.

Claims (6)

  1. A piston (10, 110) for an internal combustion engine, having a lower piston part (15) and an upper piston part (12), which are connected with one another by means of friction welding and form an outer circumferential cooling channel (19), wherein the upper piston part (12) has an outer circumferential top land (18) as well as a circumferential ring belt (20) disposed below the top land (18) and provided with ring grooves (21, 22, 23), the inner wall (20') of which ring belt delimits the circumferential outer cooling channel (19), wherein the upper piston part (12) has an outer circumferential support element (25) and the lower piston part (15) has an outer circumferential support element (26), which elements form an outer circumferential friction-weld seam (29), characterized in that the width (b1) of the outer circumferential friction-weld seam (29) is maximally at least as great as the wall thickness (d) between the respective groove base (21', 22', 23') of the ring grooves (21, 22, 23) and the inner wall (20') of the ring belt (20), that the outer mantle surfaces (25a, 26a) of the support elements (25, 26) as well as the outer mantle surface (12a) of the top land (12) have the same outside diameter (D), in such a manner that in the circumferential outer cooling channel (19), in the region of the outer circumferential friction-weld seam (29), a trough (31) is formed, in which a weld bead (32) is accommodated.
  2. The piston according to claim 1, characterized in that the width (b1) of the outer circumferential friction-weld seam (29) is equally as great as the wall thickness (d) between the respective groove base (21', 22', 23') of the ring grooves (21, 22, 23) and the inner wall (20') of the ring belt (20).
  3. The piston according to claim 1 or 2, characterized in that an inner circumferential friction-weld seam (30, 130) is provided between an inner region (24) of the piston (10, 110) and the outer circumferential cooling channel (19).
  4. The piston according to claim 3, characterized in that the width (b3) of the inner circumferential friction-weld seam (130) is at least as great as the width (b1) of the outer circumferential friction-weld seam (29).
  5. The piston according to claim 3, characterized in that the width (b2) of the inner circumferential friction-weld seam (30) is less than the width (b1) of the outer circumferential friction-weld seam (29).
  6. The piston according to one of the preceding claims, characterized in that the inner support element (27) of the upper piston part (12) and the inner support element (28) of the lower piston part (15) are configured in such a manner that a trough (31) is formed along the inner circumferential friction-weld seam (30, 130), in the outer circumferential cooling channel (19) and/or in the inner region (24), in which trough a weld bead (32) is accommodated.
EP09776111.8A 2008-09-02 2009-08-26 Piston for an internal combustion engine Not-in-force EP2321513B2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008045456A DE102008045456A1 (en) 2008-09-02 2008-09-02 Piston for an internal combustion engine
PCT/DE2009/001189 WO2010025703A1 (en) 2008-09-02 2009-08-26 Piston for an internal combustion engine

Publications (3)

Publication Number Publication Date
EP2321513A1 EP2321513A1 (en) 2011-05-18
EP2321513B1 EP2321513B1 (en) 2012-02-01
EP2321513B2 true EP2321513B2 (en) 2016-12-21

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EP09776111.8A Not-in-force EP2321513B2 (en) 2008-09-02 2009-08-26 Piston for an internal combustion engine

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US (1) US8434400B2 (en)
EP (1) EP2321513B2 (en)
JP (1) JP5631314B2 (en)
CN (1) CN202165174U (en)
AT (1) ATE543996T1 (en)
BR (1) BRPI0918059A2 (en)
DE (1) DE102008045456A1 (en)
WO (1) WO2010025703A1 (en)

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CN202165174U (en) 2012-03-14
US20100050862A1 (en) 2010-03-04
EP2321513A1 (en) 2011-05-18
DE102008045456A1 (en) 2010-03-04
EP2321513B1 (en) 2012-02-01
BRPI0918059A2 (en) 2015-12-01
US8434400B2 (en) 2013-05-07
ATE543996T1 (en) 2012-02-15
JP2012501408A (en) 2012-01-19
JP5631314B2 (en) 2014-11-26
WO2010025703A1 (en) 2010-03-11

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