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EP2329125B1 - Piston for an internal combustion engine - Google Patents

Piston for an internal combustion engine Download PDF

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Publication number
EP2329125B1
EP2329125B1 EP09736093.7A EP09736093A EP2329125B1 EP 2329125 B1 EP2329125 B1 EP 2329125B1 EP 09736093 A EP09736093 A EP 09736093A EP 2329125 B1 EP2329125 B1 EP 2329125B1
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EP
European Patent Office
Prior art keywords
piston
walls
skirt
thrust face
box walls
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.)
Active
Application number
EP09736093.7A
Other languages
German (de)
French (fr)
Other versions
EP2329125A2 (en
Inventor
Thomas Hettich
Michael Marquardt
Peter Kleinle
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
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Filing date
Publication date
Application filed by Mahle International GmbH filed Critical Mahle International GmbH
Publication of EP2329125A2 publication Critical patent/EP2329125A2/en
Application granted granted Critical
Publication of EP2329125B1 publication Critical patent/EP2329125B1/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 
    • F02F3/0076—Pistons  the inside of the pistons being provided with ribs or fins

Definitions

  • the invention relates to a piston for an internal combustion engine with a piston crown, with a land, with a circumferential ring portion, which has annular grooves, and with a piston skirt, which has two arranged on the pressure side and the counter-pressure side shaft walls and two walls connecting the skirt walls together, wherein the box walls are provided with pin bores having pin bosses, and wherein the arranged on the pressure side of the skirt wall viewed in the circumferential direction of the piston is shorter than the arranged on the counter-pressure side skirt wall.
  • a piston of the type mentioned causes the inclination of a connecting rod under ignition pressure a side force load, which is delivered via the box walls and the shaft to the cylinder wall.
  • the ignition pressure in combination with a Ausachstechnik or eccentricity of the hub bores leads to a tilting moment, which increases the lateral force load.
  • Both mechanisms cause a high stress of the piston in the lower region near the free, kolbenteilabgewandten edge of the shaft-box wall connection.
  • the highest stress is found at or shortly after the ignition pressure maximum on the pressure side of the piston.
  • the shaft-box wall connection on the counter-pressure side of the piston is in this case loaded comparatively low.
  • crank mechanisms which are confined to the pressure side, on the other hand increases the stress of the counter-pressure side shaft-box wall connection.
  • a piston is in the document GB 130 411 A shown. Accordingly, it is an object of the present invention to reduce the stress on the highly stressed, piston bottom facing away region of the pressure and counterpressure side shaft-box wall connection.
  • the pressure-side box walls are rectilinear and oblique, wherein the distance between the box walls in the region of the pin bosses is greater than in the region of the pressure-side skirt wall. Furthermore, the thickness of the box walls decreases starting from their piston bottom facing away, free edges in the direction of the piston head.
  • the thickness of the pressure-side box walls starting from the pin boss in the direction of shaft wall increase linearly, resulting in a further reduction of the stress of the highly stressed, piston bottom facing away region of the pressure and counter pressure side shaft-box wall connection.
  • the wall thicknesses In order to stress the structure homogeneously in the lower area of the shaft-box wall connection, the wall thicknesses must be designed according to the load. This ensures at the same time that unnecessary rigidity disappears and weight can be saved on the strength side.
  • the box wall thickness increases continuously, while the shaft wall thickness, starting from the end remote from the piston bottom, decreases in the direction of the piston crown. Furthermore, the increase in thickness of the box wall is realized in that the inner contour of the box wall is made obliquely than its outer contour. As a positive side effect from this one obtains a slight increase in the box wall inclination.
  • the above-described shaft-box wall connection according to the invention is usually carried out on the pressure side. If the counter-pressure side should be loaded higher than the pressure side due to a restricted crank drive, the design principle is applied on the counterpressure side. The lower loaded side of the shaft-box wall connection is then carried out as that described in the German patent application 10 2007 020 447.9 is called back pressure side.
  • Figures 1 to 3 show an embodiment of the piston 10 according to the invention, which is particularly suitable for use in high-pressure gasoline engines.
  • the piston 10 has a piston bottom 11 and a peripheral land 12 and a circumferential ring portion 13 with annular grooves 14.
  • the piston 10 On the side facing away from the piston crown, the piston 10 has a piston shaft 15, which consists of a shaft wall 16 on the pressure side (DS) and a shaft wall 17 on the counter-pressure side (GDS), wherein the shaft walls 16 and 17 are connected via box walls 18 and 19 with each other.
  • the box walls 18, 19 each have a pin boss 21, each with a hub bore 20.
  • the skirt wall 16 on the pressure side (DS) viewed in the circumferential direction is shorter than the skirt wall 17 on the counter-pressure side (GDS).
  • the shaft walls 16,17 are formed asymmetrically.
  • the thickness "d" of the pressure-side box walls 18, starting from the pin boss 21 toward the skirt wall 16, increases linearly as viewed Figure 2 is apparent.
  • the thickness "b" of the box walls 18, 19, starting from their piston bottom facing away, free edges in the direction of the piston head 11 from, as is apparent from illustration 1 results.

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

Description

Die Erfindung betrifft einen Kolben für einen Verbrennungsmotor mit einem Kolbenboden, mit einem Feuersteg, mit einer umlaufenden Ringpartie, die Ringnuten aufweist, und mit einem Kolbenschaft, der zwei auf der Druckseite und der Gegendruckseite angeordnete Schaftwände und zwei die Schaftwände miteinander verbindende Kastenwände aufweist, wobei die Kastenwände mit Nabenbohrungen aufweisenden Bolzennaben versehen sind, und wobei die auf der Druckseite angeordnete Schaftwand in Umfangsrichtung des Kolbens betrachtet kürzer ist als die auf der Gegendruckseite angeordnete Schaftwand.The invention relates to a piston for an internal combustion engine with a piston crown, with a land, with a circumferential ring portion, which has annular grooves, and with a piston skirt, which has two arranged on the pressure side and the counter-pressure side shaft walls and two walls connecting the skirt walls together, wherein the box walls are provided with pin bores having pin bosses, and wherein the arranged on the pressure side of the skirt wall viewed in the circumferential direction of the piston is shorter than the arranged on the counter-pressure side skirt wall.

Bei einem Kolben der eingangs genannten Art bewirkt die Schrägstellung eines Pleuels unter Zünddruck eine Seitenkraftbelastung, die über die Kastenwände und den Schaft an die Zylinderwand abgegeben wird. Außerdem führt der Zünddruck in Kombination mit einer Desachsierung beziehungsweise Exzentrizität der Nabenbohrungen zu einem Kippmoment, das die Seitenkraftbelastung erhöht. Beide Mechanismen verursachen eine hohe Beanspruchung des Kolbens im unteren Bereich nahe dem freien, kolbenbodenabgewandten Rand der Schaft-Kastenwand-Anbindung. Bei ungeschränkten Kurbeltrieben findet man die höchste Beanspruchung beim oder kurz nach dem Zünddruckmaximum auf der Druckseite des Kolbens. Die Schaft-Kastenwand-Anbindung auf der Gegendruckseite des Kolbens ist hierbei vergleichsweise niedrig belastet. Bei Kurbeltrieben, die zur Druckseite geschränkt sind, erhöht sich demgegenüber die Beanspruchung der gegendruckseitigen Schaft-Kastenwand-Anbindung. Ein derartiger Kolben wird im Dokument GB 130 411 A gezeigt. Demgemäß ist es Aufgabe der vorliegenden Erfindung, die Beanspruchung des hoch beanspruchten, kolbenbodenabgewandten Bereichs der druck- und gegendruckseitigen Schaft-Kastenwand-Anbindung zu reduzieren.In a piston of the type mentioned causes the inclination of a connecting rod under ignition pressure a side force load, which is delivered via the box walls and the shaft to the cylinder wall. In addition, the ignition pressure in combination with a Ausachsierung or eccentricity of the hub bores leads to a tilting moment, which increases the lateral force load. Both mechanisms cause a high stress of the piston in the lower region near the free, kolbenbodenabgewandten edge of the shaft-box wall connection. In unrestricted crank mechanisms, the highest stress is found at or shortly after the ignition pressure maximum on the pressure side of the piston. The shaft-box wall connection on the counter-pressure side of the piston is in this case loaded comparatively low. In crank mechanisms, which are confined to the pressure side, on the other hand increases the stress of the counter-pressure side shaft-box wall connection. Such a piston is in the document GB 130 411 A shown. Accordingly, it is an object of the present invention to reduce the stress on the highly stressed, piston bottom facing away region of the pressure and counterpressure side shaft-box wall connection.

Gelöst wird diese Aufgabe dadurch, dass die druckseitigen Kastenwände geradlinig und schräg verlaufen, wobei der Abstand der Kastenwände im Bereich der Bolzennaben größer ist als im Bereich der druckseitigen Schaftwand. Weiterhin nimmt die Dicke der Kastenwände ausgehend von deren kolbenbodenabgewandten, freien Rändern in Richtung Kolbenboden ab.This object is achieved in that the pressure-side box walls are rectilinear and oblique, wherein the distance between the box walls in the region of the pin bosses is greater than in the region of the pressure-side skirt wall. Furthermore, the thickness of the box walls decreases starting from their piston bottom facing away, free edges in the direction of the piston head.

In vorteilhaften Ausgestaltungen der Erfindung kann die Dicke der druckseitigen Kastenwände ausgehend von der Bolzennabe in Richtung Schaftwand linear zunehmen, wodurch sich eine weitere Reduzierung der Beanspruchung des hoch beanspruchten, kolbenbodenabgewandten Bereichs der druck- und gegendruckseitigen Schaft-Kastenwand-Anbindung ergibt.In advantageous embodiments of the invention, the thickness of the pressure-side box walls starting from the pin boss in the direction of shaft wall increase linearly, resulting in a further reduction of the stress of the highly stressed, piston bottom facing away region of the pressure and counter pressure side shaft-box wall connection.

Wie die Seitenkraftbelastung von der Schaft-Kastenwand-Anbindung abgetragen wird, kann anhand eines einfachen Balkenmodells erläutert werden, wobei die Schaft- und Kastenwand als flächige Tragstrukturen dargestellt sind. Die Seitenkraftbelastung wird hierbei konzentriert nahe dem freien Rand der Schaft-Kastenwand-Anbindung eingeleitet.How the side force load is removed from the shaft-box wall connection can be explained with reference to a simple beam model, wherein the shaft and box wall are shown as flat support structures. The lateral force load is thereby initiated concentrated near the free edge of the shaft-box wall connection.

Dabei hat sich gezeigt, dass ideal gerade Kastenwände mit möglichst großer Schrägstellung, die an der Nabenaußenkante angebunden sind, bei realistischer Wahl des Lastangriffspunktes der Seitenkraftresultierenden am geringsten beansprucht werden. Hierbei ist die Schrägstellung der Kastenwände hauptsächlich durch die Schaftwandbreite begrenzt, die groß genug sein muss, um den Kolben über den Schaft sicher führen zu können. Deshalb sind die Kastenwände im Bereich ihres unteren Randes geradlinig ausgestaltet und schräg gestellt. Um eine große Schrägstellung zu erzielen, sind die Kastenwände an der Nabenaußenkante angebunden.It has been found that ideal straight box walls with the greatest possible inclination, which are connected to the hub outer edge are least stressed at realistic choice of the load application point of lateral force resulting. Here, the inclination of the box walls is mainly limited by the shaft width, which must be large enough to safely guide the piston over the shaft can. Therefore, the box walls are designed in a straight line in the region of its lower edge and inclined. In order to achieve a large inclination, the box walls are connected to the hub outer edge.

Um die Struktur im unteren Bereich der Schaft-Kastenwand-Anbindung homogen zu beanspruchen, müssen die Wanddicken entsprechend der Belastung ausgelegt werden. Damit ist gleichzeitig gewährleistet, dass festigkeitsseitig unnötige Steifigkeiten verschwinden und Gewicht eingespart werden kann.In order to stress the structure homogeneously in the lower area of the shaft-box wall connection, the wall thicknesses must be designed according to the load. This ensures at the same time that unnecessary rigidity disappears and weight can be saved on the strength side.

Deshalb nimmt die Kastenwanddicke ausgehend von der Nabe in Richtung Schaftwand kontinuierlich zu, während die Schaftwanddicke ausgehend vom kolbenbodenabgewandten Ende in Richtung Kolbenboden abnimmt. Ferner wird die Dickenzunahme der Kastenwand dadurch realisiert, dass die Innenkontur der Kastenwand schräger gestellt wird als ihre Außenkontur. Als positiven Nebeneffekt hieraus erhält man eine leichte Zunahme der Kastenwandschrägstellung.Therefore, the box wall thickness, starting from the hub in the direction of the shaft wall, increases continuously, while the shaft wall thickness, starting from the end remote from the piston bottom, decreases in the direction of the piston crown. Furthermore, the increase in thickness of the box wall is realized in that the inner contour of the box wall is made obliquely than its outer contour. As a positive side effect from this one obtains a slight increase in the box wall inclination.

Da die Schaft-Kastenwand-Anbindung lediglich in ihrem unteren Bereich eine hohe Seitenkraftbelastung erfährt, wird ihre Dicke nur bis zur Nabenbohrungsmitte reduziert, um das Kolbengewicht gering zu halten.Since the shank-box wall connection undergoes a high lateral force load only in its lower region, its thickness is reduced only to the hub bore center in order to keep the piston weight low.

Die oben beschriebene, erfindungsgemäße Schaft-Kastenwand-Anbindung ist in der Regel druckseitig auszuführen. Falls durch einen geschränkten Kurbeltrieb die Gegendruckseite höher belastet sein sollte als die Druckseite, wird das Konstruktionsprinzip gegendruckseitig angewendet. Die niedriger belastete Seite der Schaft-Kastenwand-Anbindung wird dann so ausgeführt wie diejenige, die in der Deutschen Patentanmeldung 10 2007 020 447.9 als Gegendruckseite bezeichnet wird.The above-described shaft-box wall connection according to the invention is usually carried out on the pressure side. If the counter-pressure side should be loaded higher than the pressure side due to a restricted crank drive, the design principle is applied on the counterpressure side. The lower loaded side of the shaft-box wall connection is then carried out as that described in the German patent application 10 2007 020 447.9 is called back pressure side.

Ein Ausführungsbeispiel der vorliegenden Erfindung wird im Folgenden anhand der Abbildungen näher erläutert. Es zeigen

Abbildung 1
eine Ausführungsform des erfindungsgemäßen Kolbens im Schnitt A-A in Abbildung 2 und
Abbildung 2
und 3 einen Kolben gemäß Abbildung 1 in Unteransicht in Richtung des Pfeils B in Abbildung 1 um einige Winkelgrade gekippt
An embodiment of the present invention will be explained in more detail below with reference to the figures. Show it
illustration 1
an embodiment of the piston according to the invention in section AA in Figure 2 and
Figure 2
and 3 a piston according to illustration 1 in bottom view in the direction of arrow B in illustration 1 tilted by a few degrees

Die Abbildungen 1 bis 3 zeigen ein Ausführungsbeispiel des erfindungsgemäßen Kolbens 10, der insbesondere zum Einsatz in hoch belasteten Ottomotoren geeignet ist. Der Kolben 10 weist einen Kolbenboden 11 sowie einen umlaufenden Feuersteg 12 und eine umlaufende Ringpartie 13 mit Ringnuten 14 auf.Figures 1 to 3 show an embodiment of the piston 10 according to the invention, which is particularly suitable for use in high-pressure gasoline engines. The piston 10 has a piston bottom 11 and a peripheral land 12 and a circumferential ring portion 13 with annular grooves 14.

Auf der kolbenbodenabgewandten Seite weist der Kolben 10 einen Kolbenschaft 15 auf, der aus einer Schaftwand 16 auf der Druckseite (DS) und einer Schaftwand 17 auf der Gegendruckseite (GDS) besteht, wobei die Schaftwände 16 und 17 über Kastenwänden 18 und 19 miteinander verbunden sind. Die Kastenwände 18, 19 weisen jeweils eine Bolzennabe 21 mit je einer Nabenbohrung 20 auf.On the side facing away from the piston crown, the piston 10 has a piston shaft 15, which consists of a shaft wall 16 on the pressure side (DS) and a shaft wall 17 on the counter-pressure side (GDS), wherein the shaft walls 16 and 17 are connected via box walls 18 and 19 with each other. The box walls 18, 19 each have a pin boss 21, each with a hub bore 20.

Hierbei ist die Schaftwand 16 auf der Druckseite (DS) in Umfangsrichtung betrachtet kürzer ausgebildet als die Schaftwand 17 auf der Gegendruckseite (GDS). Somit sind die Schaftwände 16,17 asymmetrisch ausgebildet.Here, the skirt wall 16 on the pressure side (DS) viewed in the circumferential direction is shorter than the skirt wall 17 on the counter-pressure side (GDS). Thus, the shaft walls 16,17 are formed asymmetrically.

Aus Abbildung 2 ist ersichtlich, dass die druckseitigen Kastenwände 18 geradlinig ausgebildet und schräg gestellt sind. Die Schrägstellung wird durch den Winkel α beschrieben, der größer oder gleich null sein kann. Hierbei ergibt sich somit, dass der Abstand der Kastenwände 18 voneinander im Bereich der Bolzennaben 21 grö-ßer ist als im Bereich der druckseitigen Schaftwand 16.Out Figure 2 It can be seen that the pressure-side box walls 18 are rectilinear and inclined. The skew is described by the angle α, which may be greater than or equal to zero. In this case, it follows that the distance of the box walls 18 from one another in the region of the pin bosses 21 is greater than in the region of the pressure-side skirt 16.

Darüberhinaus nimmt die Dicke "d" der druckseitigen Kastenwände 18 ausgehend von der Bolzennabe 21 in Richtung Schaftwand 16 linear zu, wie aus Abbildung 2 ersichtlich ist. Weiterhin nimmt die Dicke "b" der Kastenwände 18, 19 ausgehend von deren kolbenbodenabgewandten, freien Rändern in Richtung Kolbenboden 11 ab, wie sich aus Abbildung 1 ergibt.Moreover, the thickness "d" of the pressure-side box walls 18, starting from the pin boss 21 toward the skirt wall 16, increases linearly as viewed Figure 2 is apparent. Furthermore, the thickness "b" of the box walls 18, 19, starting from their piston bottom facing away, free edges in the direction of the piston head 11 from, as is apparent from illustration 1 results.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

1010
Kolbenpiston
1111
Kolbenbodenpiston crown
1212
Feuerstegtop land
1313
Ringpartiering belt
1414
Ringnutring groove
1515
Kolbenschaftpiston shaft
1616
druckseitige Schaftwandpressure side skirt wall
1717
gegendruckseitige Schaftwandcounter-pressure side skirt wall
1818
Druckseitige KastenwandPressure side box wall
1919
gegendruckseitige Kastenwandcounter-pressure-side box wall
2020
Nabenbohrunghub bore
2121
Bolzennabepin boss

Claims (2)

  1. A piston (10) for an internal combustion engine with a piston head (11), with a top land (12), with a peripheral ring belt (13) that has annular grooves (14), and with a piston skirt (15) that has two skirt walls (16, 17) arranged on the major thrust face (DS) and the minor thrust face (GDS) and two box walls (18, 19) connecting the skirt walls (16, 17) together, the box walls (18, 19) being provided with piston pin bosses (21) having piston pin holes (22), and the skirt wall (16) arranged on the major thrust face (DS) being shorter, when viewed in the peripheral direction of the piston (10), than the skirt wall (17) arranged on the minor thrust face (GDS) and the box walls (18) on the major thrust face running in a straight, sloping line, the separation of the box walls (18) in the area of the piston pin bosses (21) being greater than in the area of the skirt wall (16) on the major thrust face, characterized in that the thickness of the box walls (18, 19) decreases starting from their free edges facing away from the piston head, in the direction toward the piston head (11).
  2. A piston according to claim 1, characterized in that the thickness of the box walls (18) on the major thrust face linearly increases starting from the piston pin boss (21) in the direction of the skirt wall (16).
EP09736093.7A 2008-08-13 2009-08-12 Piston for an internal combustion engine Active EP2329125B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008038931 2008-08-13
DE102009032379A DE102009032379A1 (en) 2008-08-13 2009-07-08 Piston for an internal combustion engine
PCT/DE2009/001119 WO2010017808A2 (en) 2008-08-13 2009-08-12 Piston for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP2329125A2 EP2329125A2 (en) 2011-06-08
EP2329125B1 true EP2329125B1 (en) 2018-02-21

Family

ID=41528325

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09736093.7A Active EP2329125B1 (en) 2008-08-13 2009-08-12 Piston for an internal combustion engine

Country Status (6)

Country Link
US (1) US20110174153A1 (en)
EP (1) EP2329125B1 (en)
JP (1) JP2011530669A (en)
BR (1) BRPI0918437B1 (en)
DE (1) DE102009032379A1 (en)
WO (1) WO2010017808A2 (en)

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US10184421B2 (en) 2012-03-12 2019-01-22 Tenneco Inc. Engine piston
BR102012032765A2 (en) * 2012-12-20 2014-09-30 Mahle Int Gmbh INTERNAL COMBUSTION ENGINE PISTON
CN105940213B (en) * 2013-11-07 2019-11-26 天纳克股份有限公司 Monolithic, channel-free piston and method of construction
DE102015217911A1 (en) * 2015-09-18 2017-03-23 Mahle International Gmbh Piston for an internal combustion engine
DE102016201628A1 (en) * 2016-02-03 2017-08-03 Federal-Mogul Nürnberg GmbH Piston made of steel or gray cast iron for an internal combustion engine and method for producing a piston by means of steel or gray cast iron
DE102018203226A1 (en) 2018-03-05 2019-09-05 Federal-Mogul Nürnberg GmbH Piston for an internal combustion engine
CN108412630B (en) * 2018-04-28 2024-08-16 江西腾勒动力有限公司 Three-cylinder engine piston
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Also Published As

Publication number Publication date
JP2011530669A (en) 2011-12-22
EP2329125A2 (en) 2011-06-08
WO2010017808A3 (en) 2010-04-15
US20110174153A1 (en) 2011-07-21
BRPI0918437A2 (en) 2015-11-24
WO2010017808A2 (en) 2010-02-18
DE102009032379A1 (en) 2010-02-18
BRPI0918437B1 (en) 2019-11-26

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