EP2321513A1 - Piston for an internal combustion engine - Google Patents

Piston for an internal combustion engine

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Publication number
EP2321513A1
EP2321513A1 EP09776111A EP09776111A EP2321513A1 EP 2321513 A1 EP2321513 A1 EP 2321513A1 EP 09776111 A EP09776111 A EP 09776111A EP 09776111 A EP09776111 A EP 09776111A EP 2321513 A1 EP2321513 A1 EP 2321513A1
Authority
EP
European Patent Office
Prior art keywords
piston
width
friction weld
outer circumferential
annular
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
Application number
EP09776111A
Other languages
German (de)
French (fr)
Other versions
EP2321513B2 (en
EP2321513B1 (en
Inventor
Peter Kemnitz
Carmen Klusch
Rainer Scharp
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle International GmbH
Original Assignee
Mahle International GmbH
Priority date (The priority date 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 date listed.)
Filing date
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
Application granted granted Critical
Publication of EP2321513B1 publication Critical patent/EP2321513B1/en
Publication of EP2321513B2 publication Critical patent/EP2321513B2/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 annular groove provided with annular ring portion whose inner wall delimiting the peripheral outer cooling channel.
  • a generic piston is disclosed in US 6,557,514 B1.
  • 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.
  • stresses are built up during friction welding, which affect the stability of the piston.
  • 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 having the features of claim 1.
  • the invention provides that below the ring section an outer circumferential friction weld is provided whose width is at most equal to the wall thickness between the respective groove bottom of the annular grooves and the inner wall of the ring section.
  • 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.
  • the piston according to the invention has improved flexibility.
  • 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.
  • 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 portion, whereby an optimal power flow with optimum material utilization can be achieved.
  • 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.
  • the width of the inner circumferential friction weld may be greater than or equal to or less than the width of the outer circumferential friction weld. Both Reibsch spall requireharmen be formed in one operation.
  • 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 piston lower part and the piston upper part form a depression along at least one friction welding seam, into which a possibly formed welding bead is received in order to maximize a possible along the friction welding seam to obtain a uniform surface and in particular not to reduce the size of the cooling channel and the cooling oil flow not by turbulence u.
  • a possibly formed welding bead is received in order to maximize a possible along the friction welding seam to obtain a uniform surface and in particular not to reduce the size of the cooling channel and the cooling oil flow not by turbulence u.
  • FIG. 1 shows a first embodiment of a piston according to the invention in section, wherein the left half of the representation opposite the right half is rotated by 90 °.
  • FIG. 2A is an enlarged fragmentary view of the piston of FIG. 1; FIG.
  • Fig. 2B is an enlarged partial view of another embodiment of a piston according to the invention.
  • Figures 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 and the piston upper part 12 may be made of any metallic material that is amenable to machining by friction welding. ⁇
  • 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 piston upper part 12 is provided with a circumferential outer support member 25 and a circumferential inner support member 27.
  • the lower piston part 15 is likewise provided with a circumferential outer support element 26 and a circumferential inner support element 28.
  • 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
  • the outer Reibsch spat 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.
  • the inner friction weld 30 has a width b2, which is smaller in the embodiment according to Figures 1 and 2A within the usual manufacturing tolerances 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.
  • FIG. 2B shows a further exemplary embodiment of a piston 110 in a representation comparable to 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 within the usual manufacturing tolerances b1 of the outer friction weld 29.

Landscapes

  • 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

The present invention relates to a piston (10) for an internal combustion engine, comprising a piston skirt (15) and a piston crown (12), which are connected to each other by friction welding and form an outer peripheral cooling duct (19), wherein the piston crown (12) has a peripheral annular zone (20) provided with annular grooves (21, 22, 23), the inside wall (20’) of said annular zone delimiting the peripheral outer cooling duct (19). According to the invention, an outer peripheral friction welding seam (29) is provided beneath the annular zone (20), the width (b1) of said seam being no more than exactly the dimension of the wall thickness (d) between the respective groove base (21, 22’, 23’) of the annular grooves (21, 22, 23) and the inside wall (20’) of the annular zone (20).

Description

Kolben für einen Verbrennungsmotor Piston for an internal combustion engine
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 eine mit Ringnuten versehene umlaufende Ringpartie aufweist, deren Innenwand den umlaufenden äußeren Kühlkanal begrenzt.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 annular groove provided with annular ring portion whose inner wall delimiting the peripheral outer cooling channel.
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 disclosed in US 6,557,514 B1. 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.
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 unterhalb der Ringpartie eine äußere umlaufende Reibschweißnaht vorgesehen ist, deren Breite höchstens genauso groß ist wie die Wanddicke zwischen dem jeweiligen Nutgrund der Ringnuten und der Innenwand der Ringpartie.The solution consists in a piston having the features of claim 1. The invention provides that below the ring section an outer circumferential friction weld is provided whose width is at most equal to the wall thickness between the respective groove bottom of the annular grooves and the inner wall of the ring section.
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 great" is to be understood as meaning that customary manufacturing tolerances are included in. The width of the outer circumferential friction weld and the wall thickness therefore lie within the usual manufacturing tolerances.
BESTATIGUNGSKOPIE 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.BESTATIGUNGSKOPIE 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.
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 portion, 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 klei- ner als die Breite der äußeren umlaufenden Reibschweißnaht sein. Beide Reibschweißverbindungen werden in einem Arbeitsgang ausgebildet.The width of the inner circumferential 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 das Kolbenunterteil und das Kolbenoberteil entlang mindestens einer Reibschweißnaht eine Mulde bilden, in die ein eventuell ausgebildeter Schweißwulst aufgenommen ist, um entlang der Reibschweißnaht eine möglichst gleichmäßige Oberfläche zu erhalten und insbesondere die Größe des Kühlkanals nicht zu reduzieren sowie den Kühlölfluss nicht durch Verwirbelungen u. dgl. zu beeinträchtigen.It is expedient that the piston lower part and the piston upper part form a depression along at least one friction welding seam, into which a possibly formed welding bead is received in order to maximize a possible along the friction welding seam to obtain a uniform surface and in particular not to reduce the size of the cooling channel and the cooling oil flow not by turbulence u. Like. Affect.
Ausführungsbeispiele der vorliegenden Erfindung werden im Folgenden anhand der beigefügten Zeichnungen näher erläutert. Es zeigen in einer schematischen, nicht maßstabsgetreuen Darstellung: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 ein erstes Ausführungsbeispiel eines erfindungsgemäßen Kolbens im Schnitt, wobei die linke Hälfte der Darstellung gegenüber der rechten Hälfte um 90° gedreht ist;1 shows a first embodiment of a piston according to the invention in section, wherein the left half of the representation opposite the right half is rotated by 90 °.
Fig. 2A eine vergrößerte Teildarstellung des Kolbens gemäß Figur 1 ;FIG. 2A is an enlarged fragmentary view of the piston of FIG. 1; FIG.
Fig. 2B eine vergrößerte Teildarstellung eines weiteren Ausführungsbeispiels eines erfindungsgemäßen Kolbens.Fig. 2B is 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 und das Kolbenoberteil 12 können aus jedem metallischen Werkstoff bestehen, der einer Bearbeitung durch Reibschweißen zugänglich ist. ιFigures 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 and the piston upper part 12 may be made of any metallic material that is amenable to machining by friction welding. ι
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. 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. 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 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. 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. 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 is smaller in the embodiment according to Figures 1 and 2A within the usual manufacturing tolerances 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. 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. 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. FIG. 2B shows a further exemplary embodiment of a piston 110 in a representation comparable to 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 within the usual manufacturing tolerances b1 of the outer friction weld 29.

Claims

Patentansprüche claims
1. Kolben (10, 110) für einen Verbrennungsmotor, mit einem Kolbenunterteil (15) und einem Kolbenoberteil (12), die durch Reibschweißen miteinander verbunden sind und einen äußeren umlaufenden Kühlkanal (19) bilden, wobei das Kolbenoberteil (12) eine mit Ringnuten (21 , 22, 23) versehene umlaufende Ringpartie (20) aufweist, deren Innenwand (20') den umlaufenden äußeren Kühlkanal (19) begrenzt, dadurch gekennzeichnet, dass unterhalb der Ringpartie (20) eine äußere umlaufende Reibschweißnaht (29) vorgesehen ist, deren Breite (b1 ) höchstens genauso groß ist wie die Wanddicke (d) zwischen dem jeweiligen Nutgrund (21 ', 22', 23') der Ringnuten (21 , 22, 23) und der Innenwand (20') der Ringpartie (20).A piston (10, 110) for an internal combustion engine, having a piston lower part (15) and a piston upper part (12), which are joined together by friction welding and form an outer circumferential cooling channel (19), wherein the piston upper part (12) one with annular grooves (21, 22, 23) provided peripheral annular portion (20) whose inner wall (20 ') delimiting the peripheral outer cooling channel (19), characterized in that below the annular portion (20) an outer circumferential friction weld (29) is provided whose width (b1) is at most equal to the wall thickness (d) between the respective groove bottom (21 ', 22', 23 ') of the annular grooves (21, 22, 23) and the inner wall (20') of the annular part (20) ,
2. Kolben nach Anspruch 1 , dadurch gekennzeichnet, dass die Breite (b1) der äußeren umlaufenden Reibschweißnaht (29) genauso groß ist wie die Wanddicke (d) zwischen dem jeweiligen Nutgrund (21', 22', 23') der Ringnuten (21 , 22, 23) und der Innenwand (20') der Ringpartie (20).2. Piston according to claim 1, characterized in that the width (b1) of the outer circumferential friction weld (29) is equal to the wall thickness (d) between the respective groove bottom (21 ', 22', 23 ') of the annular grooves (21 , 22, 23) and the inner wall (20 ') of the ring part (20).
3. Kolben nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass zwischen einem Innenbereich (24) des Kolbens (10, 110) und dem äußeren umlaufenden Kühlkanal (19) eine innere umlaufende Reibschweißnaht (30, 130) vorgesehen ist.3. Piston according to claim 1 or 2, characterized in that between an inner region (24) of the piston (10, 110) and the outer circumferential cooling channel (19) an inner circumferential friction weld (30, 130) is provided.
4. Kolben nach Anspruch 3, dadurch gekennzeichnet, dass die Breite (b3) der inneren umlaufenden Reibschweißnaht (130) mindestens genauso groß ist wie die Breite (b1 ) der äußeren umlaufenden Reibschweißnaht (29).4. Piston according to claim 3, characterized in that the width (b3) of the inner circumferential friction weld (130) is at least as large as the width (b1) of the outer circumferential friction weld (29).
5. Kolben nach Anspruch 3, dadurch gekennzeichnet, dass die Breite (b2) der inneren umlaufenden Reibschweißnaht (30) kleiner ist als die Breite (b1) der äußeren umlaufenden Reibschweißnaht (29). 5. Piston according to claim 3, characterized in that the width (b2) of the inner circumferential friction weld (30) is smaller than the width (b1) of the outer circumferential friction weld (29).
6. Kolben nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Kolbenunterteil (15) und das Kolbenoberteil (12) entlang mindestens einer Reibschweißnaht (29; 30, 130) eine Mulde bilden (31 ), in die ein eventuell ausgebildeter Schweißwulst (32) aufgenommen ist. 6. Piston according to one of the preceding claims, characterized in that the piston lower part (15) and the piston upper part (12) along at least one friction weld (29; 30, 130) form a trough (31) into which a possibly formed weld bead (32 ) is recorded.
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 true EP2321513A1 (en) 2011-05-18
EP2321513B1 EP2321513B1 (en) 2012-02-01
EP2321513B2 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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Also Published As

Publication number Publication date
WO2010025703A1 (en) 2010-03-11
BRPI0918059A2 (en) 2015-12-01
ATE543996T1 (en) 2012-02-15
US8434400B2 (en) 2013-05-07
JP5631314B2 (en) 2014-11-26
EP2321513B2 (en) 2016-12-21
JP2012501408A (en) 2012-01-19
EP2321513B1 (en) 2012-02-01
US20100050862A1 (en) 2010-03-04
CN202165174U (en) 2012-03-14
DE102008045456A1 (en) 2010-03-04

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