EP3545182B1 - Steel piston for an internal combustion engine - Google Patents

Steel piston for an internal combustion engine Download PDF

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Publication number
EP3545182B1
EP3545182B1 EP17758471.1A EP17758471A EP3545182B1 EP 3545182 B1 EP3545182 B1 EP 3545182B1 EP 17758471 A EP17758471 A EP 17758471A EP 3545182 B1 EP3545182 B1 EP 3545182B1
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EP
European Patent Office
Prior art keywords
piston
shank
shank surface
internal combustion
combustion engine
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
EP17758471.1A
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German (de)
French (fr)
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EP3545182A1 (en
Inventor
Ralf Meske
Lukas Merz
Michael Kraemer
Christoffer SCHMOLL
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.)
Federal Mogul Nuernberg GmbH
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Federal Mogul Nuernberg GmbH
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Publication of EP3545182A1 publication Critical patent/EP3545182A1/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
    • 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 
    • F02F3/0084—Pistons  the pistons being constructed from specific materials
    • 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
    • F02F2003/0061—Multi-part pistons the parts being connected by casting, brazing, welding or clamping by welding

Definitions

  • the invention relates to a steel piston for an internal combustion engine.
  • steel pistons are often used, which are generally designed to be rotationally symmetrical with respect to the piston axis.
  • FIG US 2012/0037112 A1 the piston according to FIG US 2012/0037112 A1 called.
  • the US 8,220,432 B2 or from the WO2015 / 024551 A1 a piston emerges which is asymmetrical with regard to its skirt surfaces.
  • the width of the skirt surfaces usually results from the installation space conditions that are specified in the interior of the piston by the small connecting rod eye and the oil spray nozzle position. Due to the high peak cylinder pressures, the small connecting rod eye on heavy-duty pistons is relatively wide.
  • the oil spray nozzle is placed next to the installation space used by the connecting rod pivoting movement, whereby the inner minimum width of the shaft surfaces is specified. This results in a skirt width which is 70-80% of the piston diameter.
  • the connecting walls between the skirt surface and the piston hub are usually straight.
  • the invention is based on the object of creating a steel piston which is improved in terms of friction and fuel consumption.
  • shaft surfaces one of which is 25-50% narrower than the other.
  • the selection of the shaft surface to be reduced in width results from the position of the oil spray nozzle, with the unchanged, wider shaft surface preferably being provided on the side with the oil spray nozzle and the opposite shaft surface representing the side to be reduced.
  • the rotational symmetry usually provided for steel pistons is abandoned, the requirements being further met by the steel piston according to the invention, and advantageously not only the friction but also the weight can be reduced.
  • the steel piston according to the invention is preferably used in heavy-duty diesel engines. Extensive simulation calculations have shown that the friction of a heavy-duty steel piston at a normal operating point for motorway travel is mainly determined by the hydrodynamic component. The hydrodynamic friction depends, among other factors, on the size of the contact surfaces. Therefore, a reduction in fuel consumption is achieved by reducing the width of the skirt contact surfaces of the piston.
  • a cooling channel outlet is to be provided, which is preferably arranged on the side of the smaller skirt area.
  • the cooling duct outlet is provided centrally according to the invention, so that the outflowing oil advantageously reaches the pivoting connecting rod and is thus partially transported in the direction of the small connecting rod eye, so that lubrication takes place here in an advantageous manner.
  • This arrangement also advantageously makes it possible to dispense with a further outlet or drainage bore.
  • the shank surfaces are connected to the pin hub by so-called connecting walls.
  • the invention described here enables the connection of at least one shaft surface to be implemented at an angle, which is advantageous for the rigidity of the connection.
  • the rigidity of the wider shaft surface which is preferably provided on the pressure side, it offers Advantages if this has at least one convexity, a thickening or a bulge.
  • the steel piston according to the invention consists of at least two components connected by friction welding.
  • the lower piston part can be manufactured by forging or casting.
  • a draft angle must be provided for the forging manufacturing process. This results in an embodiment of the skirt surfaces in which the skirt surfaces are each wider at their end facing the piston head than at the opposite end.
  • a skirt surface 12 on the counter-pressure side is significantly smaller, in particular narrower, as in the side view of FIG Fig. 2 recognizable. However, it can also be the shaft surface 14 on the The pressure side can be made smaller if the position of the oil spray nozzle is on the counter pressure side.
  • a cooling channel outlet 16 is arranged essentially centrally, while the cooling channel inlet 24 is provided laterally.
  • the shaft wall has a convexity 22 on this side on its inside at the lower end. However, it preferably extends over the entire "height" of the skirt wall in the direction of the piston axis. In other words, the shaft wall is essentially thickened in the middle or bulged towards the inside.
  • the convexity extends, for example, over approximately one third of the width of the shaft surface 14 and, like the two transitions to the wall thickness of the shaft surface 14, is rounded. In this respect, a concavity is created on both sides of the convexity 22.
  • the smaller skirt surface 12 is somewhat wider at its end directed towards the piston head 18 than at the opposite end.
  • the width measured in the circumferential direction at the upper end is a maximum of 120% of the width at the lower end.
  • the lateral edges of at least one, preferably both, shaft surfaces 12, 14 run largely in a straight line.
  • the larger shaft surface 14 has an essentially identical width at the upper and lower ends.

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)

Description

Technisches GebietTechnical area

Die Erfindung betrifft einen Stahlkolben für einen Verbrennungsmotor.The invention relates to a steel piston for an internal combustion engine.

Stand der TechnikState of the art

Insbesondere für heavy-duty Verbrennungsmotoren werden häufig Stahlkolben eingesetzt, die in der Regel rotationssymmetrisch bezüglich der Kolbenachse ausgeführt sind. Als Beispiel sei der Kolben gemäß der US 2012/0037112 A1 genannt. Ergänzend geht aus der US 8,220,432 B2 oder aus der WO2015/024551 A1 ein Kolben hervor, der im Hinblick auf seine Schaftflächen asymmetrisch ist.In particular for heavy-duty internal combustion engines, steel pistons are often used, which are generally designed to be rotationally symmetrical with respect to the piston axis. As an example, consider the piston according to FIG US 2012/0037112 A1 called. In addition, the US 8,220,432 B2 or from the WO2015 / 024551 A1 a piston emerges which is asymmetrical with regard to its skirt surfaces.

Die Breite der Schaftflächen ergibt sich üblicherweise aus den Bauraumbedingungen, die im Innenbereich des Kolbens durch das kleine Pleuelauge und die Ölspritzdüsenposition vorgegeben sind. Aufgrund der hohen Zylinderspitzendrücke ist das kleine Pleuelauge bei Heavy-Duty Kolben relativ breit. Neben dem durch die Pleuelschwenkbewegung verbrauchten Bauraum wird die Ölspritzdüse platziert, wodurch die innere Mindestbreite der Schaftflächen vorgegeben ist. Damit ergibt sich eine Schaftbreite, welche 70-80% des Kolbendurchmessers beträgt. Die Verbindungswände zwischen Schaftfläche und Kolbennabe wird üblicherweise gerade ausgeführt.The width of the skirt surfaces usually results from the installation space conditions that are specified in the interior of the piston by the small connecting rod eye and the oil spray nozzle position. Due to the high peak cylinder pressures, the small connecting rod eye on heavy-duty pistons is relatively wide. The oil spray nozzle is placed next to the installation space used by the connecting rod pivoting movement, whereby the inner minimum width of the shaft surfaces is specified. This results in a skirt width which is 70-80% of the piston diameter. The connecting walls between the skirt surface and the piston hub are usually straight.

Bei Kolben ohne Ventiltaschen und ohne Desachsierung der Bolzenbohrung erlaubt eine rotationssymmetrische Gestaltung bezüglich der Kolbenachse einen verdrehsicheren Einbau im Motor.In the case of pistons without valve pockets and without offsetting the pin bore, a rotationally symmetrical design with respect to the piston axis allows rotation-proof installation in the engine.

Darstellung der ErfindungPresentation of the invention

Der Erfindung liegt die Aufgabe zu Grunde, einen im Hinblick auf Reibung und Kraftstoffverbrauch verbesserten Stahlkolben zu schaffen.The invention is based on the object of creating a steel piston which is improved in terms of friction and fuel consumption.

Die Lösung der Aufgabe erfolgt durch den im Anspruch 1 beschriebenen Stahlkolben.The object is achieved by the steel piston described in claim 1.

Demzufolge weist dieser Schaftflächen auf, von denen eine um 25-50% schmäler ist als die andere. Besonders bevorzugt wird eine Verringerung der Schaftbreite um 30-35%, insbesondere etwa 33%. Hierdurch wird eine Verringerung der hydrodynamischen Reibung erzielt, die nach Erkenntnis der Erfinder im Hinblick auf den Kraftstoffverbrauch relevant ist. Die Auswahl der in ihrer Breite zu reduzierenden Schaftfläche ergibt sich aus der Lage der Ölspritzdüse, wobei auf der Seite mit Ölspritzdüse bevorzugt die unveränderte, breitere Schaftfläche vorgesehen wird und die gegenüberliegende Schaftfläche die zu reduzierenden Seite darstellt. Gemäß der Erfindung wird die bei Stahlkolben üblicherweise vorgesehene Rotationssymmetrie aufgegeben, wobei die Anforderungen durch den erfindungsgemäßen Stahlkolben weiterhin erfüllt werden, und in vorteilhafter Weise nicht nur die Reibung, sondern auch das Gewicht verringert werden kann.As a result, it has shaft surfaces, one of which is 25-50% narrower than the other. A reduction in the shaft width by 30-35%, in particular approximately 33%, is particularly preferred. This achieves a reduction in hydrodynamic friction, which, according to the inventors' knowledge, is relevant with regard to fuel consumption. The selection of the shaft surface to be reduced in width results from the position of the oil spray nozzle, with the unchanged, wider shaft surface preferably being provided on the side with the oil spray nozzle and the opposite shaft surface representing the side to be reduced. According to the invention, the rotational symmetry usually provided for steel pistons is abandoned, the requirements being further met by the steel piston according to the invention, and advantageously not only the friction but also the weight can be reduced.

Hierdurch lässt sich beispielsweise der Kraftstoffverbrauch senken. Bevorzugt wird der erfindungsgemäße Stahlkolben in heavy-duty Dieselmotoren eingesetzt. Umfangreiche Simulationsrechnungen haben gezeigt, dass die Reibung eines Heavy-Duty Stahlkolbens in einem üblichen Betriebspunkt für eine Autobahnfahrt überwiegend durch den hydrodynamischen Anteil bestimmt wird. Die hydrodynamische Reibung hängt neben weiteren Faktoren stark von der Größe der Kontaktflächen ab. Daher wird eine Verringerung des Kraftstoffverbrauchs durch eine Reduktion der Breite der Schaftkontaktflächen des Kolbens erreicht.This can, for example, reduce fuel consumption. The steel piston according to the invention is preferably used in heavy-duty diesel engines. Extensive simulation calculations have shown that the friction of a heavy-duty steel piston at a normal operating point for motorway travel is mainly determined by the hydrodynamic component. The hydrodynamic friction depends, among other factors, on the size of the contact surfaces. Therefore, a reduction in fuel consumption is achieved by reducing the width of the skirt contact surfaces of the piston.

Nachdem der erfindungsgemäße Stahlkolben zumindest einen Kühlkanal aufweist, ist ein Kühlkanalauslass vorzusehen, der bevorzugt auf der Seite der kleineren Schaftfläche angeordnet wird. Unabhängig davon wird der Kühlkanalauslass erfindungsgemäß zentral vorgesehen, so dass in vorteilhafter Weise das ausfließende Öl auf das schwenkende Pleuel gelangt und somit teilweise in Richtung des kleinen Pleuelauges transportiert wird, so dass hier in vorteilhafter Weise eine Schmierung erfolgt. Durch diese Anordnung kann ferner in vorteilhafter Weise eine weitere Auslass- oder Drainagebohrung entfallen.After the steel piston according to the invention has at least one cooling channel, a cooling channel outlet is to be provided, which is preferably arranged on the side of the smaller skirt area. Regardless of this, the cooling duct outlet is provided centrally according to the invention, so that the outflowing oil advantageously reaches the pivoting connecting rod and is thus partially transported in the direction of the small connecting rod eye, so that lubrication takes place here in an advantageous manner. This arrangement also advantageously makes it possible to dispense with a further outlet or drainage bore.

Bevorzugte Weiterbildungen der Erfindung sind in den weiteren Ansprüchen beschrieben.Preferred developments of the invention are described in the further claims.

Insbesondere im Hinblick auf die Entformung, beispielsweise aus einem Schmiedegesenk, werden Ausführungsformen bevorzugt, bei denen die kleinere Schaftfläche an ihrem zu dem Kolbenboden gerichteten Ende breiter ist, als an dem entgegengesetzten Ende.Particularly with regard to demolding, for example from a forging die, embodiments are preferred in which the smaller skirt surface is wider at its end directed towards the piston head than at the opposite end.

Typischerweise sind die Schaftflächen durch sogenannte Verbindungswände mit der Bolzennabe verbunden. Durch die hier beschriebene Erfindung lässt sich die Anbindung zumindest einer Schaftfläche schräg ausführen, was für die Steifigkeit der Anbindung vorteilhaft ist.Typically, the shank surfaces are connected to the pin hub by so-called connecting walls. The invention described here enables the connection of at least one shaft surface to be implemented at an angle, which is advantageous for the rigidity of the connection.

Im Hinblick auf die Steifigkeit der breiteren Schaftfläche, die bevorzugt auf der Druckseite vorgesehen ist, bietet es Vorteile, wenn diese zumindest eine Konvexität, eine Verdickung oder eine Ausbauchung aufweist.With regard to the rigidity of the wider shaft surface, which is preferably provided on the pressure side, it offers Advantages if this has at least one convexity, a thickening or a bulge.

Schließlich wird für den erfindungsgemäßen Stahlkolben bevorzugt, dass er aus zumindest zwei durch Reibschweißen verbundenen Komponenten besteht. Das Kolbenunterteil kann hierbei durch Schmieden oder Gießen gefertigt werden. Beim Fertigungsverfahren Schmieden ist eine Entformungsschräge vorzusehen. Dadurch ergibt sich eine Ausführungsform der Schaftflächen, bei denen die Schaftflächen jeweils an ihrem zu dem Kolbenboden gerichteten Ende breiter sind, als an dem entgegengesetzten Ende.Finally, it is preferred for the steel piston according to the invention that it consists of at least two components connected by friction welding. The lower piston part can be manufactured by forging or casting. A draft angle must be provided for the forging manufacturing process. This results in an embodiment of the skirt surfaces in which the skirt surfaces are each wider at their end facing the piston head than at the opposite end.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Nachfolgend wird die Erfindung anhand eines in den Zeichnungen dargestellten Ausführungsbeispiels näher erläutert.The invention is explained in more detail below on the basis of an exemplary embodiment shown in the drawings.

Es zeigen:

  • Fig. 1 eine Unteransicht des erfindungsgemäßen Kolbens; und
  • Fig. 2 eine Seitenansicht des erfindungsgemäßen Kolbens.
Show it:
  • Fig. 1 a bottom view of the piston according to the invention; and
  • Fig. 2 a side view of the piston according to the invention.

Ausführliche Beschreibung einer bevorzugten Ausführungsform der ErfindungDetailed description of a preferred embodiment of the invention

Wie in Fig. 1 zu erkennen ist, sind eine Schaftfläche 12, die bei dem gezeigten Beispiel auf der Gegendruckseite vorgesehen ist, und eine Schaftfläche 14 auf der Druckseite durch Verbindungswände 20 mit einer Kolbennabe 26, welche die Kolbenbolzenbohrung aufweist, verbunden. Die Schaftfläche 12 auf der Gegendruckseite ist deutlich kleiner, insbesondere schmäler, wie ergänzend in der Seitenansicht von Fig. 2 erkennbar. Es kann jedoch auch die Schaftfläche 14 auf der Druckseite kleiner ausgeführt werden, wenn die Position der Ölspritzdüse auf der Gegendruckseite liegt.As in Fig. 1 As can be seen, a skirt surface 12, which is provided on the counter-pressure side in the example shown, and a skirt surface 14 on the pressure side are connected by connecting walls 20 to a piston hub 26, which has the piston pin bore. The shaft surface 12 on the counter-pressure side is significantly smaller, in particular narrower, as in the side view of FIG Fig. 2 recognizable. However, it can also be the shaft surface 14 on the The pressure side can be made smaller if the position of the oil spray nozzle is on the counter pressure side.

In Fig. 1 ist ergänzend zu sehen, dass ein Kühlkanalauslass 16 im Wesentlichen zentral angeordnet ist, während der Kühlkanaleinlass 24 seitlich vorgesehen ist. Im Hinblick auf die Druckseite ist in Fig. 1 eine bevorzugte Ausführungsform dergestalt gezeigt, dass die Schaftwand an dieser Seite an ihrer Innenseite am unteren Ende eine Konvexität 22 aufweist. Sie erstreckt sich jedoch bevorzugt über die gesamte "Höhe" der Schaftwand in Richtung der Kolbenachse. Mit anderen Worten, ist die Schaftwand im Wesentlichen mittig verdickt oder zur Innenseite ausgebaucht. Die Konvexität erstreckt sich beispielsweise über etwa ein Drittel der Breite der Schaftfläche 14 und ist, ebenso wie die beiden Übergänge zu der Wanddicke der Schaftfläche 14, gerundet ausgeführt. Insoweit entsteht zu beiden Seiten der Konvexität 22 jeweils eine Konkavität.In Fig. 1 it can also be seen that a cooling channel outlet 16 is arranged essentially centrally, while the cooling channel inlet 24 is provided laterally. With regard to the print side, in Fig. 1 a preferred embodiment is shown in such a way that the shaft wall has a convexity 22 on this side on its inside at the lower end. However, it preferably extends over the entire "height" of the skirt wall in the direction of the piston axis. In other words, the shaft wall is essentially thickened in the middle or bulged towards the inside. The convexity extends, for example, over approximately one third of the width of the shaft surface 14 and, like the two transitions to the wall thickness of the shaft surface 14, is rounded. In this respect, a concavity is created on both sides of the convexity 22.

In Fig. 2 ist ergänzend erkennbar, dass die kleinere Schaftfläche 12 an ihrem zu dem Kolbenboden 18 gerichteten Ende etwas breiter ist als am entgegengesetzten Ende. Mit Ausnahme des deutlich abgeschrägten unteren Endes beträgt jedoch die in Umfangsrichtung gemessene Breite am oberen Ende maximal 120% der Breite am unteren Ende. Im Übrigen verlaufen die seitlichen Ränder von zumindest einer, bevorzugt beiden Schaftflächen 12, 14 weitgehend geradlinig. Schließlich weist die größere Schaftfläche 14 bei dem gezeigten Beispiel am oberen und unteren Ende eine im Wesentlichen übereinstimmende Breite auf.In Fig. 2 it can also be seen that the smaller skirt surface 12 is somewhat wider at its end directed towards the piston head 18 than at the opposite end. With the exception of the clearly sloping lower end, however, the width measured in the circumferential direction at the upper end is a maximum of 120% of the width at the lower end. In addition, the lateral edges of at least one, preferably both, shaft surfaces 12, 14 run largely in a straight line. Finally, in the example shown, the larger shaft surface 14 has an essentially identical width at the upper and lower ends.

Claims (5)

  1. Steel piston (10) for an internal combustion engine with at least one cooling channel and shank surfaces (12, 14) with which, in the installed state, the piston (10) lies against a cylinder bore or a cylinder liner on a pressure side and a counterpressure side,
    wherein one shank surface (12) has a width 25-50% less than the other shank surface, and
    a cooling channel outlet (16) is arranged centrally on the side of the narrower shank surface.
  2. Piston according to claim 1, characterised in that the narrower shank surface (12) is wider at an end pointing towards a piston crown (18) than at an end opposite the piston crown (18).
  3. Piston according to one of the preceding claims, characterised in that the shank surfaces (12, 14) are connected with a piston hub (26) through connecting walls (20), and at least one connecting wall (20) between shank surface (12, 14) and piston hub (26) runs obliquely.
  4. Piston according to one of the preceding claims, characterised in that the wider shank surface (14) has at least once convexity (22) on the inner side.
  5. Piston according to one of the preceding claims, characterised in that this consists of at least two components connected through friction welding.
EP17758471.1A 2016-11-28 2017-08-17 Steel piston for an internal combustion engine Active EP3545182B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016223530.3A DE102016223530A1 (en) 2016-11-28 2016-11-28 Steel piston for an internal combustion engine
PCT/EP2017/070830 WO2018095601A1 (en) 2016-11-28 2017-08-17 Steel piston for an internal combustion engine

Publications (2)

Publication Number Publication Date
EP3545182A1 EP3545182A1 (en) 2019-10-02
EP3545182B1 true EP3545182B1 (en) 2020-11-25

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EP17758471.1A Active EP3545182B1 (en) 2016-11-28 2017-08-17 Steel piston for an internal combustion engine

Country Status (7)

Country Link
US (1) US11131269B2 (en)
EP (1) EP3545182B1 (en)
KR (1) KR102384112B1 (en)
CN (1) CN109996948B (en)
DE (1) DE102016223530A1 (en)
MX (1) MX2019006116A (en)
WO (1) WO2018095601A1 (en)

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Also Published As

Publication number Publication date
EP3545182A1 (en) 2019-10-02
KR20190086501A (en) 2019-07-22
KR102384112B1 (en) 2022-04-06
WO2018095601A1 (en) 2018-05-31
US11131269B2 (en) 2021-09-28
CN109996948B (en) 2022-06-17
CN109996948A (en) 2019-07-09
MX2019006116A (en) 2019-08-01
DE102016223530A1 (en) 2018-05-30
US20210115874A1 (en) 2021-04-22

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