EP1922479B1 - Piston for an internal combustion engine - Google Patents

Piston for an internal combustion engine Download PDF

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Publication number
EP1922479B1
EP1922479B1 EP06776553.7A EP06776553A EP1922479B1 EP 1922479 B1 EP1922479 B1 EP 1922479B1 EP 06776553 A EP06776553 A EP 06776553A EP 1922479 B1 EP1922479 B1 EP 1922479B1
Authority
EP
European Patent Office
Prior art keywords
piston
region
insert
connecting walls
axis
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.)
Revoked
Application number
EP06776553.7A
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German (de)
French (fr)
Other versions
EP1922479A1 (en
Inventor
Ralf Buschbeck
Albert Haberl
Willi Sikorsky
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.)
KS Kolbenschmidt GmbH
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KS Kolbenschmidt GmbH
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Application filed by KS Kolbenschmidt GmbH filed Critical KS Kolbenschmidt GmbH
Priority to PL06776553T priority Critical patent/PL1922479T3/en
Publication of EP1922479A1 publication Critical patent/EP1922479A1/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D19/00—Casting in, on, or around objects which form part of the product
    • B22D19/0009—Cylinders, pistons
    • B22D19/0027—Cylinders, pistons pistons
    • 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
    • F02F3/04—Pistons  having means for accommodating or controlling heat expansion having expansion-controlling inserts
    • F02F3/08—Pistons  having means for accommodating or controlling heat expansion having expansion-controlling inserts the inserts being ring-shaped
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22D—CASTING OF METALS; CASTING OF OTHER SUBSTANCES BY THE SAME PROCESSES OR DEVICES
    • B22D19/00—Casting in, on, or around objects which form part of the product
    • B22D19/02—Casting in, on, or around objects which form part of the product for making reinforced articles
    • 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 
    • 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 
    • F02F3/28—Other pistons with specially-shaped head
    • 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
    • F02F2200/00—Manufacturing
    • F02F2200/06—Casting

Definitions

  • the invention relates to a piston for an internal combustion engine according to the features of the respective preamble of the independent claims.
  • a piston for internal combustion engines is of the generic type EP 0 902 180 A2 known.
  • the hubs are reset in the bolt axis direction so that the outer hub clearance is 60 to 65% of the piston diameter or less.
  • the hub outer surfaces which connect the two sliding surfaces with each other, have a linear (linear) course over the height of the sliding surfaces.
  • the hub outer surfaces also called box walls
  • the hub outer surfaces are not basically flat, but also curved both in sections parallel and perpendicular to the piston axis.
  • the curvature of the surface in sections perpendicular to the piston axis is always the same for the whole surface of the box wall. This results in upward (in the direction of the piston head) decreasing distance of the box walls an upward decreasing width of the bearing sliding surface.
  • the disadvantage here is that with the width of the box walls widening upwards, the potential of weight saving due to the undercut of the ring field in the bolt direction can not be fully utilized.
  • the support of the piston crown is not optimal due to the box walls due to the lowering of the bottom tensile stresses. In the upward (in the direction of the piston crown) decreasing distance of the box walls is lost to the upper edge of the shaft surface, which is required for the Kolbengerad Entry and the production of seizure safety.
  • due to the lack of support of the ring field by the piston skirt high stresses in the transition areas arise between the piston skirt and the Ringfeldumguß.
  • connecting walls are known in pistons, which are formed as mutually parallel planes or curved surfaces with only one radius of curvature and only one direction of curvature.
  • Pistons are known in cylinder design, wherein in a piston crown a ring field is arranged and connects a piston stem cylindrically starting from the ring field.
  • piston head reinforcements are provided in each case in the region of the uppermost annular groove, which can accommodate the uppermost ring.
  • the invention is therefore based on the object to provide a piston with which the described disadvantages are avoided.
  • the invention is in various designs of the piston, concerning the course of the shaft wall sections and their connecting walls (the advantages in the DE 101 45 589 A1 are described), provided that in the region of the piston crown radially circumferential behind the ring field, a gain is provided.
  • This reinforcement has the advantage that it increases the piston crown area, in which the scree is located, in order to meet the loads resulting from the combustion temperatures and pressures during the operation of the piston in the cylinder chamber of an internal combustion engine. Since the clearance (undercut) is present in this area, this reinforcement is particularly advantageous and particularly important, especially as the shaft is freely suspended under the ring field and can not contribute to the reinforcement (support).
  • the reinforcement is formed as an insert that inserted before casting a piston blank into the casting tool, fixed there and surrounded with molten casting.
  • the insert is made of the same or different material than the material from which the piston blank is cast.
  • the insert is one or more parts, preferably one-piece annular, formed.
  • the multi-part design has the advantage that the insert can be arranged at the points behind the ring field and approximately at the height of the Freigusses, where a special reinforcement is to take place. It is particularly advantageous if the insert is integrally formed annular, so that it can be handled very easily when inserted into the casting tool. Moreover, this is one Particularly good continuous reinforcement, especially a radial support, given in the area of the ring field.
  • the insert before insertion into the casting tool has an outer diameter which is smaller than or equal to the inner diameter of the casting tool at the point at which the insert is fixed.
  • the inner diameter of the insert is greater than or equal to the outer diameter of the Freigusses.
  • the crop (undercut) is formed by a correspondingly shaped molding (slide) of the casting tool, which is pulled out vertically, obliquely or at right angles to the Kolbenhubachse after solidification of the casting melt depending on the shape of the Freigusses.
  • the insert according to the invention is designed so that it serves to reinforce the piston crown and after the production of the piston (pouring the piston blank, which is finished) appears on the radial surface of the piston in the region of the ring field.
  • the axial height of the insert is selected so that it extends above and below at least one annular groove, preferably the uppermost annular groove, or may extend over a plurality of annular grooves. It is possible that the insert already before casting has a groove for receiving an oil ring or this groove (ring groove) is introduced during the finishing of the piston blank.
  • the insert has a cooling channel forming one or more parts cooling channel plate, which is integrally formed on the insert.
  • FIG. 1 shows a piston 1, which is in particular a light metal piston, in particular for an internal combustion engine is.
  • This piston 1 has a piston skirt 2 and a cylindrically shaped piston crown 3, which is particularly adapted to the type of internal combustion engine (diesel or gasoline engine).
  • the piston head On the formation of the piston head, which may be arbitrary, it does not matter in this invention.
  • pin bosses 4 are present, which are set back in the direction of a pin axis to a piston axis and are part of the piston skirt 2.
  • the pin bosses 4 are located in two rear connection walls 5, which connect two opposite leg wall sections 7 together.
  • a ring field 6 is provided in the piston head 3.
  • the reference numeral 8 designates the lower edge of the connecting wall 5
  • the reference numeral 9 designates the lower edge of the piston crown 3 and the annular field 6, respectively.
  • the construction of the piston 1 is such that the curvature functions, their relative offset to each other in the bolt direction and the nature of their connection in the piston longitudinal direction is chosen so that surfaces of the shaft wall portions 7 with constant shaft width or 15 tapered upper or bottom shaft width result in the piston longitudinal direction ,
  • FIG. 2 shows to illustrate the invention, the view of the piston 1 from below, viewed in the interior of the piston 1 inside.
  • the connecting walls 5 have in their peripheral lower edge 8 a convex radius of curvature, relative to an axis 10 (perpendicular to the pin axis) (solid line).
  • the connecting walls 5 In the region of the lower edge 9 of the ring field 6, the connecting walls 5 have a concave radius of curvature with respect to the axis 10 (dashed line).
  • Reference numeral 11 designates a projection (ring-field projection) of the lower edge of the ring field 6 beyond the connecting walls 5, wherein this region is in particular at least partially hollowed out in order to realize a further weight saving.
  • This hollowing of the projection 11 can also extend into the regions in which the skirt wall sections 7 are arranged, and possibly extend into the inner region of the ring field 6, ie, until just before the end of the piston crown 3.
  • a reinforcement 15 which serves to reinforce the piston crown.
  • weight is saved by the combination of mortar 12 and reinforcement 15, but on the other hand increases the strength.
  • the weight which makes up the volume of the die 12
  • the weight of the reinforcement that is to say the one-piece or multi-part insert.
  • This can be achieved, for example, in that the material of the insert part has a lower specific density than that of the surrounding piston material. Alternatively or additionally, this effect can be achieved even with the same materials over different volumes (volume of the insert smaller than the volume of the Freigusses).

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

Description

Die Erfindung betrifft einen Kolben für eine Brennkraftmaschine gemäß den Merkmalen des jeweiligen Oberbegriffes der unabhängigen Patentansprüche.The invention relates to a piston for an internal combustion engine according to the features of the respective preamble of the independent claims.

Ein Kolben für Brennkraftmaschinen ist aus der gattungsbildenden EP 0 902 180 A2 bekannt. Bei diesem Kolben sind die Naben in Bolzenachsrichtung derart zurückgesetzt, dass der äußere Nabenabstand 60 bis 65% des Kolbendurchmessers oder weniger beträgt. Die Nabenaußenflächen, die die beiden Gleitflächen miteinander verbinden, haben über die Höhe der Gleitflächen betrachtet einen geradlinigen (linearen) Verlauf. Bei diesem Kolben sind die Nabenaußenflächen (auch Kastenwände genannt) nicht grundsätzlich eben, sondern auch gekrümmt sowohl in Schnitten parallel als auch senkrecht zu der Kolbenachse. Dabei ist jedoch der Krümmungssinn der Fläche in Schnitten senkrecht zur Kolbenachse immer für die ganze Fläche der Kastenwand gleichbleibend. Dadurch ergibt sich bei nach oben (in Richtung des Kolbenbodens) geringer werdendem Abstand der Kastenwände eine nach oben abnehmende Breite der tragenden Gleitfläche. Nachteilig dabei ist, dass sich bei nach oben verbreiterndem Abstand der Kastenwände zueinander das Potential der Gewichtseinsparung durch den Hinterschnitt des Ringfeldes in Bolzenrichtung nicht vollständig genutzt werden kann. Die Unterstützung des Kolbenbodens ist durch die Kastenwände aufgrund der Absenkung der Bodenzugspannungen nicht optimal. Bei sich nach oben (in Richtung des Kolbenbodens) verringerndem Abstand der Kastenwände geht an der Schaftoberkante Schaftfläche, die für die Kolbengeradführung und die Herstellung der Freßsicherheit benötigt wird, verloren. Außerdem ergeben sich zwischen dem Kolbenschaft und dem Ringfeldumguß aufgrund der mangelnden Unterstützung des Ringfeldes durch den Kolbenschaft hohe Spannungen in den Übergangsbereichen.A piston for internal combustion engines is of the generic type EP 0 902 180 A2 known. In this piston, the hubs are reset in the bolt axis direction so that the outer hub clearance is 60 to 65% of the piston diameter or less. The hub outer surfaces, which connect the two sliding surfaces with each other, have a linear (linear) course over the height of the sliding surfaces. In this piston, the hub outer surfaces (also called box walls) are not basically flat, but also curved both in sections parallel and perpendicular to the piston axis. However, the curvature of the surface in sections perpendicular to the piston axis is always the same for the whole surface of the box wall. This results in upward (in the direction of the piston head) decreasing distance of the box walls an upward decreasing width of the bearing sliding surface. The disadvantage here is that with the width of the box walls widening upwards, the potential of weight saving due to the undercut of the ring field in the bolt direction can not be fully utilized. The support of the piston crown is not optimal due to the box walls due to the lowering of the bottom tensile stresses. In the upward (in the direction of the piston crown) decreasing distance of the box walls is lost to the upper edge of the shaft surface, which is required for the Kolbengeradführung and the production of seizure safety. In addition, due to the lack of support of the ring field by the piston skirt high stresses in the transition areas arise between the piston skirt and the Ringfeldumguß.

Ebenso sind Verbindungswände bei Kolben bekannt, die als zueinander parallele Ebenen oder gekrümmten Flächen mit nur einem Krümmungsradius und nur einer Krümmungsrichtung ausgebildet sind.Similarly, connecting walls are known in pistons, which are formed as mutually parallel planes or curved surfaces with only one radius of curvature and only one direction of curvature.

Eine Verbesserung bietet ein Kolben, wie er aus der DE 101 45 589 A1 bekannt ist. Dieser weist im Kolbenboden einen Freiguss (Hinterschnitt) auf, der sich radial umlaufend hinter dem Ringfeld erstreckt. Dieser Freiguss hat zwar den Vorteil einer Gewichtsersparnis, aber gleichzeitig auch den Nachteil, dass der Bereich des Kolbenbodens dadurch geschwächt wird.An improvement offers a piston, as he from the DE 101 45 589 A1 is known. This has in the piston head on a Freiguss (undercut), which extends radially circumferentially behind the ring field. Although this advantage has the advantage of weight savings, but at the same time the disadvantage that the area of the piston crown is thereby weakened.

Aus der EP-A-0 877 160 , der JP 60166158 A . der US 2003/140885 A1 oder der DE 901 104 C sind Kolben in Zylinderbauform bekannt, wobei In einem Kolbenboden ein Ringfeld angeordnet ist und sich ein Kolbenschaft zylinderförmig ausgehend von dem Ringfeld anschließt. Im Kolbenboden sind jeweils im Bereich der obersten Ringnut Verstärkungen vorgesehen, die den obersten Ring aufnehmen können.From the EP-A-0 877 160 , of the JP 60166158 A , of the US 2003/140885 A1 or the DE 901 104 C Pistons are known in cylinder design, wherein in a piston crown a ring field is arranged and connects a piston stem cylindrically starting from the ring field. In the piston head reinforcements are provided in each case in the region of the uppermost annular groove, which can accommodate the uppermost ring.

Der Erfindung liegt daher die Aufgabe zugrunde, einen Kolben bereitzustellen, mit dem die geschilderten Nachteile vermieden werden.The invention is therefore based on the object to provide a piston with which the described disadvantages are avoided.

Diese Aufgabe ist durch die Merkmale des jeweiligen unabhängigen Patentanspruches gelöst.This object is solved by the features of the respective independent claim.

Erfindungsgemäß ist bei verschiedenen Bauformen des Kolbens, betreffend den Verlauf der Schaftwandabschnitte und deren Verbindungswände (deren Vorteile in der DE 101 45 589 A1 beschrieben sind), vorgesehen, dass im Bereich des Kolbenbodens radial umlaufend hinter dem Ringfeld eine Verstärkung vorgesehen ist. Diese Verstärkung hat den Vorteil, dass dort der Kolbenbodenbereich verstärkt wird, in dem auch der Freiguss sich befindet, um den Belastungen zu genügen, die aus den Verbrennungstemperaturen und -drücken während des Betriebes des Kolbens im Zylinderraum einer Brennkraftmaschine resultieren. Da in diesem Bereich der Freiguss (Hinterschnitt) vorhanden ist, ist diese Verstärkung von besonderem Vorteil und besonders wichtig, zumal der Schaft unter dem Ringfeld freihängend angeordnet ist und nicht zur Verstärkung (Abstützung) beitragen kann.According to the invention is in various designs of the piston, concerning the course of the shaft wall sections and their connecting walls (the advantages in the DE 101 45 589 A1 are described), provided that in the region of the piston crown radially circumferential behind the ring field, a gain is provided. This reinforcement has the advantage that it increases the piston crown area, in which the scree is located, in order to meet the loads resulting from the combustion temperatures and pressures during the operation of the piston in the cylinder chamber of an internal combustion engine. Since the clearance (undercut) is present in this area, this reinforcement is particularly advantageous and particularly important, especially as the shaft is freely suspended under the ring field and can not contribute to the reinforcement (support).

In Weiterbildung der Erfindung ist die Verstärkung als Einlegeteil ausgebildet, dass vor dem Giessen eines Kolbenrohlings in das Gießwerkzeug eingelegt, dort fixiert und mit Gießschmelze umgeben wird. Das Einlegeteil ist aus dem gleichen oder einem anderen Werkstoff als der Werkstoff, aus dem der Kolbenrohling gegossen wird. Dadurch können Gewichtsersparnis durch den Freiguss einerseits und Verstärkung durch das Einlegeteil andererseits optimal aufeinander abgestimmt werden.In a further development of the invention, the reinforcement is formed as an insert that inserted before casting a piston blank into the casting tool, fixed there and surrounded with molten casting. The insert is made of the same or different material than the material from which the piston blank is cast. As a result, weight savings by the approval on the one hand and reinforcement by the insert on the other hand can be optimally matched.

In Weiterbildung der Erfindung ist das Einlegeteil ein- oder mehrteilig, vorzugsweise einteilig ringförmig, ausgebildet. Die mehrteilige Ausgestaltung hat den Vorteil, dass das Einlegeteil an den Stellen hinter dem Ringfeld und etwa auf Höhe des Freigusses angeordnet werden kann, an denen eine besondere Verstärkung stattfinden soll. Von besonderem Vorteil ist es, wenn das Einlegeteil einteilig ringförmig ausgebildet ist, so dass es beim Einsetzen in das Gießwerkzeug sehr einfach gehandhabt werden kann. Außerdem ist dadurch eine besonders gute durchgängige Verstärkung, vor allem eine radial Abstützung, im Bereich des Ringfeldes gegeben.In a further development of the invention, the insert is one or more parts, preferably one-piece annular, formed. The multi-part design has the advantage that the insert can be arranged at the points behind the ring field and approximately at the height of the Freigusses, where a special reinforcement is to take place. It is particularly advantageous if the insert is integrally formed annular, so that it can be handled very easily when inserted into the casting tool. Moreover, this is one Particularly good continuous reinforcement, especially a radial support, given in the area of the ring field.

In Weiterbildung der Erfindung weist das Einlegeteil vor dem Einsetzen in das Gießwerkzeug einen Außendurchmesser auf, der kleiner oder gleich dem Innendurchmesser des Gießwerkzeuges an der Stelle, an der das Einlegeteil fixiert wird, ist. Der Innendurchmesser des Einlegeteiles ist größer oder gleich dem Außendurchmesser des Freigusses. Vorzugsweise ist eine Beabstandung zwischen dem Einlegeteil und dem Freiguss gegeben zwecks Verstärkung und Vermeidung von Problemen beim Giessen. Dabei ist diese Beabstandung so zu wählen, dass sich beim Einfüllen der Gießschmelze in das Gießwerkzeug ausreichend Gießschmelze zwischen Einlegeteil und Freiguss verteilen kann und Lücken vermieden werden. Der Freiguss (Hinterschnitt) wird dabei von einem entsprechend ausgebildeten Formteil (Schieber) des Gießwerkzeuges gebildet, das je nach Form des Freigusses senkrecht, schräg oder im rechten Winkel zur Kolbenhubachse nach dem Erstarren der Gießschmelze ausgezogen wird. Insgesamt ist das Einlegeteil gemäß der Erfindung so gestaltet, dass es der Verstärkung des Kolbenbodens dient und nach der Herstellung des Kolbens (Kolbenrohling gießen, der fertig bearbeitet wird) an der radialen Oberfläche des Kolbens im Bereich des Ringfeldes erscheint. Dabei ist die axiale Höhe des Einlegeteiles so gewählt, dass es sich ober- und unterhalb zumindest einer Ringnut, vorzugsweise der obersten Ringnut, erstreckt oder auch über mehrere Ringnuten erstrecken kann. Dabei ist es möglich, dass das Einlegeteil schon vor dem Giessen eine Nut zur Aufnahme eines Ölringes aufweist oder diese Nut (Ringnut) bei der Fertigbearbeitung des Kolbenrohlings eingebracht wird.In a further development of the invention, the insert before insertion into the casting tool has an outer diameter which is smaller than or equal to the inner diameter of the casting tool at the point at which the insert is fixed. The inner diameter of the insert is greater than or equal to the outer diameter of the Freigusses. Preferably, there is a spacing between the insert and the grit for reinforcement and avoidance of casting problems. In this case, this spacing is to be chosen so that when pouring the molten casting into the casting mold sufficient casting melt between insert and Freiguss can be distributed and gaps are avoided. The crop (undercut) is formed by a correspondingly shaped molding (slide) of the casting tool, which is pulled out vertically, obliquely or at right angles to the Kolbenhubachse after solidification of the casting melt depending on the shape of the Freigusses. Overall, the insert according to the invention is designed so that it serves to reinforce the piston crown and after the production of the piston (pouring the piston blank, which is finished) appears on the radial surface of the piston in the region of the ring field. The axial height of the insert is selected so that it extends above and below at least one annular groove, preferably the uppermost annular groove, or may extend over a plurality of annular grooves. It is possible that the insert already before casting has a groove for receiving an oil ring or this groove (ring groove) is introduced during the finishing of the piston blank.

In Weiterbildung der Erfindung weist das Einlegeteil ein einen Kühlkanal bildendes ein- oder mehrteiliges Kühlkanalblech auf, welches an dem Einlegeteil angeformt ist. Damit ist eine Kühlung des Kolbenbodens durch ein in dem Kühlkanal zirkulierendes Kühlmedium, insbesondere Motoröl, möglich, um den hohen Belastungsanforderungen an den Kolben im Betrieb gerecht zu werden.In a further development of the invention, the insert has a cooling channel forming one or more parts cooling channel plate, which is integrally formed on the insert. Thus, a cooling of the piston head by a circulating in the cooling channel cooling medium, in particular engine oil, is possible to meet the high load requirements on the piston during operation.

In Weiterbildung der Erfindung steht im Bereich der Verbindungswände der untere Rand des Ringfeldes über die Verbindungswände über diese über (Überstand) und ist dort zumindest teilweise ausgehöhlt. Durch diesen Überstand, sowie die Aushöhlung des Überstandes wird eine weitere Gewichtsreduzierung in einem Bereich, der für die Festigkeit des Kolbens unkritisch ist, erzielt. Der Bereich, der ausgehöhlt ist, richtet sich insbesondere nach der Anordnung der Bolzennabe und des Übergangsbereiches des Kolbenbodens in die Kolbenschäfte.In a further development of the invention is in the region of the connecting walls of the lower edge of the ring field on the connecting walls on this over (supernatant) and there is at least partially hollowed out. By this supernatant, as well as the excavation of the supernatant, a further weight reduction in a range which is not critical for the strength of the piston, achieved. The area which is hollowed out depends in particular on the arrangement of the pin boss and the transition area of the piston crown into the piston stems.

Eine beispielhafte Ausführung eines Kolbens, auf die die Erfindung jedoch nicht beschränkt ist, ist im folgenden beschrieben und an hand der Figuren erläutert.An exemplary embodiment of a piston, to which the invention is not limited, is described below and explained with reference to the figures.

Es zeigen:

Figur 1
einen erfindungsgemäßen Kolben in dreidimensionaler Ansicht,
Figur 2
einen Kolben in der Ansicht von unten in den Innenbereich des Kolbens hinein
Figur 3
einen Kolben im Schnitt längs der Kolbenachse.
Show it:
FIG. 1
a piston according to the invention in three-dimensional view,
FIG. 2
a piston in the view from below into the interior of the piston
FIG. 3
a piston in section along the piston axis.

Figur 1 zeigt einen Kolben 1, bei dem es sich insbesondere um einen Leichtmetallkolben, insbesondere für eine Brennkraftmaschine, handelt. Dieser Kolben 1 weist einen Kolbenschaft 2 sowie einen zylindrisch geformten Kolbenboden 3 auf, der insbesondere dem Typ der Brennkraftmaschine (Diesel- oder Otto-Brennkraftmaschine) angepasst ist. Auf die Ausbildung des Kolbenbodens, die beliebig sein kann, kommt es bei dieser Erfindung nicht an. FIG. 1 shows a piston 1, which is in particular a light metal piston, in particular for an internal combustion engine is. This piston 1 has a piston skirt 2 and a cylindrically shaped piston crown 3, which is particularly adapted to the type of internal combustion engine (diesel or gasoline engine). On the formation of the piston head, which may be arbitrary, it does not matter in this invention.

Weiterhin sind Bolzennaben 4 vorhanden, die in Richtung einer Bolzenachse zu einer Kolbenachse zurückgesetzt sind und Bestandteil des Kolbenschaftes 2 sind. Die Bolzennaben 4 befinden sich in zwei zurückliegenden Verbindungswänden 5, die zwei gegenüberliegende Schaftwandabschnitte 7 miteinander verbinden. Weiterhin ist ein Ringfeld 6 im Kolbenboden 3 vorgesehen. Mit der Bezugsziffer 8 ist der untere Rand der Verbindungswand 5 und mit der Bezugsziffer 9 der untere Rand des Kolbenbodens 3 bzw. des Ringfeldes 6 bezeichnet. Die Konstruktion des Kolbens 1 ist derart, dass die Krümmungsfunktionen, ihr relativer Versatz zueinander in Bolzenrichtung und die Art ihrer Verbindung in Kolbenlängsrichtung so gewählt wird, dass sich Flächen der Schaftwandabschnitte 7 mit konstanter Schaftbreite oder sich nach 15 oben oder unten verjüngender Schaftbreite in Kolbenlängsrichtung ergeben.Furthermore, pin bosses 4 are present, which are set back in the direction of a pin axis to a piston axis and are part of the piston skirt 2. The pin bosses 4 are located in two rear connection walls 5, which connect two opposite leg wall sections 7 together. Furthermore, a ring field 6 is provided in the piston head 3. The reference numeral 8 designates the lower edge of the connecting wall 5 and the reference numeral 9 designates the lower edge of the piston crown 3 and the annular field 6, respectively. The construction of the piston 1 is such that the curvature functions, their relative offset to each other in the bolt direction and the nature of their connection in the piston longitudinal direction is chosen so that surfaces of the shaft wall portions 7 with constant shaft width or 15 tapered upper or bottom shaft width result in the piston longitudinal direction ,

Figur 2 zeigt zur Verdeutlichung der Erfindung die Ansicht des Kolbens 1 von unten, in den Innenbereich des Kolbens 1 hinein betrachtet. Hierbei wird erkennbar, dass die Verbindungswände 5 in ihrem umlaufenden unteren Rand 8 einen konvexen Krümmungsradius, bezogen auf eine Achse 10 (senkrecht zu der Bolzenachse) aufweisen (durchgezogene Linie). Im Bereich des unteren Randes 9 des Ringfeldes 6 haben die Verbindungswände 5 einen in Bezug auf die Achse 10 konkaven Krümmungsradius (gestrichelte Linie). FIG. 2 shows to illustrate the invention, the view of the piston 1 from below, viewed in the interior of the piston 1 inside. It can be seen here that the connecting walls 5 have in their peripheral lower edge 8 a convex radius of curvature, relative to an axis 10 (perpendicular to the pin axis) (solid line). In the region of the lower edge 9 of the ring field 6, the connecting walls 5 have a concave radius of curvature with respect to the axis 10 (dashed line).

Mit der Bezugsziffer 11 ist ein Überstand (Ringfeldüberstand) des unteren Randes des Ringfeldes 6 über die Verbindungswände 5 hinaus bezeichnet, wobei dieser Bereich insbesondere zumindest teilweise ausgehöhlt ist, um eine weitere Gewichtsersparnis zu realisieren. Diese Aushöhlung des Überstandes 11 kann sich auch bis in die Bereiche, in denen die Schaftwandabschnitte 7 angeordnet sind, erstrecken und ggf. bis in den innen liegenden Bereich des Ringfeldes 6, also bis knapp vor Ende des Kolbenbodens 3, erstrecken. In vorteilhafter Weise erfolgt die Aushöhlung als Freiguss 12 (siehe Figur 3) hinter dem Ringfeld 6 in der Fläche des Überstandes 11 und an solchen Stellen, die nicht oder nur geringfügig zur Festigkeit des Kolbens 1, insbesondere des Kolbenbodens 3, beitragen (Bezugsziffer 13 = Kolbenachse, Bezugsziffer 14 = Bolzenachse).Reference numeral 11 designates a projection (ring-field projection) of the lower edge of the ring field 6 beyond the connecting walls 5, wherein this region is in particular at least partially hollowed out in order to realize a further weight saving. This hollowing of the projection 11 can also extend into the regions in which the skirt wall sections 7 are arranged, and possibly extend into the inner region of the ring field 6, ie, until just before the end of the piston crown 3. Advantageously, the cavity is carried out as a mortar 12 (see FIG. 3 ) behind the ring field 6 in the surface of the supernatant 11 and at those points which do not or only slightly to the strength of the piston 1, in particular the piston head 3, contribute (reference numeral 13 = piston axis, reference numeral 14 = pin axis).

Weiterhin ist in Figur 2 und 3 gezeigt, dass im Bereich des Kolbenbodens 3 radial umlaufend hinter dem Ringfeld 6 eine Verstärkung 15 vorgesehen ist, die der Verstärkung des Kolbenbodens dient. Somit wird durch die Kombination aus Freiguss 12 und Verstärkung 15 einerseits Gewicht gespart, andererseits aber die Festigkeit erhöht. Dies ist insbesondere dann der Fall, wenn das Gewicht, das das Volumen des Freigusses 12 ausmacht, größer ist als das Gewicht der Verstärkung, also des ein- oder mehrteiligen Einlegeteils. Dies kann beispielsweise dadurch erzielt werden, dass das Material des Einlegeteils eine geringere spezifische Dichte aufweist als die des umgebenden Kolbenmaterials. Alternativ oder ergänzend kann dieser Effekt auch bei gleichen Materialien über unterschiedliche Volumina (Volumen des Einlegeteils kleiner als das Volumen des Freigusses) erzielt werden.Furthermore, in FIG. 2 and 3 shown that in the region of the piston crown 3 radially behind the ring field 6, a reinforcement 15 is provided, which serves to reinforce the piston crown. Thus, on the one hand weight is saved by the combination of mortar 12 and reinforcement 15, but on the other hand increases the strength. This is the case, in particular, when the weight, which makes up the volume of the die 12, is greater than the weight of the reinforcement, that is to say the one-piece or multi-part insert. This can be achieved, for example, in that the material of the insert part has a lower specific density than that of the surrounding piston material. Alternatively or additionally, this effect can be achieved even with the same materials over different volumes (volume of the insert smaller than the volume of the Freigusses).

Claims (9)

  1. Piston (1), comprising a piston head (3), a ring zone (6) and a piston skirt (2), consisting of load-bearing skirt wall sections (7) and recessed connecting walls (5), which connect the skirt wall sections (7) to one another, and piston-pin bosses (4), which run in the direction of a pin axis that is set back from a piston axis and penetrate the connecting walls (5), wherein the connecting walls (5) are formed convexly in relation to an axis (10) in the region of their peripheral lower edge (8) and concavely in relation to the axis (10) in the region of their upper edge (9), preferably below the ring zone (6), wherein in the region of the connecting walls (5) the lower edge (8) of the ring zone (6) projects beyond this region and has a projection (11) and is at least partially hollowed out there, characterized in that, in the region of the piston head (3), the piston is provided with a reinforcement (15) running around radially behind the ring zone (6) above the projection (11).
  2. Piston (1), comprising a piston head (3), a ring zone (6) and a piston skirt (2), consisting of load-bearing skirt wall sections (7) and recessed connecting walls (5), which connect the skirt wall sections (7) to one another, and piston-pin bosses (4), which run in the direction of a pin axis that is set back from a piston axis and penetrate the connecting walls (5), wherein the connecting walls (5) are formed convexly in relation to an axis (10) in the region of their peripheral lower edge (8) and straight in relation to the axis (10) in the region of their upper edge (9), preferably below the ring zone (6), wherein in the region of the connecting walls (5) the lower edge (8) of the ring zone (6) projects beyond this region and has a projection (11) and is at least partially hollowed out there, characterized in that, in the region of the piston head (3), the piston is provided with a reinforcement (15) running around radially behind the ring zone (6) above the projection (11).
  3. Piston (1), comprising a piston head (3), a ring zone (6) and a piston skirt (2), consisting of load-bearing skirt wall sections (7) and recessed connecting walls (5), which connect the skirt wall sections (7) to one another, and piston-pin bosses (4), which run in the direction of a pin axis that is set back from a piston axis and penetrate the connecting walls (5), wherein the connecting walls (5) are formed straight in the region of their peripheral lower edge (8) and concavely in relation to the axis (10) in the region of their upper edge (9), preferably below the ring zone (6), wherein in the region of the connecting walls (5) the lower edge (8) of the ring zone (6) projects beyond this region and has a projection (11) and is at least partially hollowed out there, characterized in that, in the region of the piston head (3), the piston is provided with a reinforcement (15) running around radially behind the ring zone (6) above the projection (11).
  4. Piston according to one of the preceding claims, characterized in that a free casting is formed behind the piston-ring grooves in the surface area of the projection (11).
  5. Piston (1) according to one of the preceding claims, characterized in that the reinforcement (15) is formed as an insert, which is inserted into the casting mould before the casting of a piston blank, is fixed there and is surrounded with casting melt.
  6. Piston (1) according to one of the preceding claims, characterized in that the insert is formed as one or more parts, preferably as one part in the form of a ring.
  7. Piston (1) according to one of the preceding claims, characterized in that, before being inserted into the casting mould, the insert has an outside diameter that is less than or equal to the inside diameter of the casting mould at the location at which the insert is fixed, and the inside diameter of the insert is greater than or equal to the outside diameter of the free casting (12).
  8. Piston (1) according to one of the preceding claims, characterized in that the insert appears on the radial surface of the piston (1) in the region of the ring zone (6) and the axial height of the insert is chosen such that it extends above and below at least one piston-ring groove, preferably the uppermost piston-ring groove (16).
  9. Piston (1) according to one of the preceding claims, characterized in that the insert has a one-part or multi-part cooling channel plate, which forms a cooling channel and is integrally formed on the insert.
EP06776553.7A 2005-09-08 2006-08-02 Piston for an internal combustion engine Revoked EP1922479B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL06776553T PL1922479T3 (en) 2005-09-08 2006-08-02 Piston for an internal combustion engine

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005042857A DE102005042857A1 (en) 2005-09-08 2005-09-08 Piston for an internal combustion engine
PCT/EP2006/007638 WO2007028466A1 (en) 2005-09-08 2006-08-02 Piston for an internal combustion engine

Publications (2)

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EP1922479A1 EP1922479A1 (en) 2008-05-21
EP1922479B1 true EP1922479B1 (en) 2016-07-13

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EP06776553.7A Revoked EP1922479B1 (en) 2005-09-08 2006-08-02 Piston for an internal combustion engine

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US (1) US8683913B2 (en)
EP (1) EP1922479B1 (en)
JP (1) JP2009507173A (en)
KR (1) KR20080068805A (en)
DE (1) DE102005042857A1 (en)
PL (1) PL1922479T3 (en)
WO (1) WO2007028466A1 (en)

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US9010296B2 (en) * 2010-06-29 2015-04-21 Kolbenschmidt K. K. Piston for spark-ignition engine
GB2492101B (en) * 2011-06-21 2014-12-10 Jaguar Land Rover Ltd Apparatus and method for embedding an element
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DE102011115048A1 (en) * 2011-10-07 2013-04-11 Mahle International Gmbh A forging apparatus for producing a piston blank and a method for producing the piston blank using the forging apparatus
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US8969197B2 (en) * 2012-05-18 2015-03-03 International Business Machines Corporation Copper interconnect structure and its formation
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WO2007028466A1 (en) 2007-03-15
US8683913B2 (en) 2014-04-01
DE102005042857A1 (en) 2007-03-22
KR20080068805A (en) 2008-07-24
EP1922479A1 (en) 2008-05-21
US20080245229A1 (en) 2008-10-09
PL1922479T3 (en) 2017-05-31
JP2009507173A (en) 2009-02-19

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