EP3665378A1 - Piston pour un moteur à combustion interne à pistons alternatifs ainsi que moteur à combustion interne à pistons alternatifs - Google Patents

Piston pour un moteur à combustion interne à pistons alternatifs ainsi que moteur à combustion interne à pistons alternatifs

Info

Publication number
EP3665378A1
EP3665378A1 EP18745585.2A EP18745585A EP3665378A1 EP 3665378 A1 EP3665378 A1 EP 3665378A1 EP 18745585 A EP18745585 A EP 18745585A EP 3665378 A1 EP3665378 A1 EP 3665378A1
Authority
EP
European Patent Office
Prior art keywords
piston
stiffening rib
ring carrier
guide surface
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.)
Withdrawn
Application number
EP18745585.2A
Other languages
German (de)
English (en)
Inventor
Paulo Ivan URZUA TORRES
Martin Bier
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.)
Volkswagen AG
Original Assignee
Volkswagen AG
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
Application filed by Volkswagen AG filed Critical Volkswagen AG
Publication of EP3665378A1 publication Critical patent/EP3665378A1/fr
Withdrawn legal-status Critical Current

Links

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
    • 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 
    • F02F3/10—Pistons  having surface coverings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J1/00—Pistons; Trunk pistons; Plungers
    • F16J1/04—Resilient guiding parts, e.g. skirts, particularly for trunk 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

Definitions

  • Piston for a reciprocating internal combustion engine and reciprocating internal combustion engine
  • the invention relates to a piston for a reciprocating internal combustion engine and a
  • Reciprocating internal combustion engine with such a piston in particular for use in motor vehicles. It is also explicitly referred to motor vehicles with such reciprocating piston.
  • a piston for an internal combustion engine wherein the piston referred to as an annular ring carrier ring and designated as a shaft
  • the invention has for its object to provide a piston for a reciprocating internal combustion engine and a reciprocating internal combustion engine available, which are thermally functional improved with sufficient rigidity and have a low weight.
  • An inventive piston for a reciprocating internal combustion engine comprises a
  • Ring carrier with an outer piston crown and with an inner piston crown.
  • the outer piston crown is that side which, in the installed state of the piston, faces a combustion chamber and immediately limits it.
  • the inner piston head is the opposite side of the piston head referred to, which is remote from the combustion chamber in the installed state.
  • a piston skirt Starting from the inner piston crown extends in the axial direction of the piston, a piston skirt, which at least one, at least partially having arcuately shaped guide surface.
  • the piston skirt two each having an arc portion - as viewed in the circumferential direction of the piston - extending guide surfaces, for example, on opposite sides of the piston.
  • the at least one guide surface is in the piston according to the invention in the arcuate region with respect to the in the axial direction
  • the piston skirt and the ring carrier are further interconnected by at least one stiffening rib extending transversely across the inner piston crown.
  • the part of the piston skirt with one or more guide surfaces and the ring carrier can be interconnected only indirectly via the stiffening rib in this case.
  • the stiffening rib By means of at least one such stiffening rib can be
  • a partially high stiffness of the piston can be achieved with simultaneously advantageous thermal properties and low component weight. It has been found that the thermal decoupling achieved with the piston according to the invention is so good that the piston warmth play substantially corresponds to the piston installation play, i. that take place in the entire map and temperature range of a reciprocating internal combustion engine only minor relative changes in the clearance between the piston and cylinder wall. This allows the installation play and the resulting
  • tilting of the piston can be reduced to a minimum, which also results in low oil consumption.
  • the above-mentioned gap between the guide surface and the ring carrier is in particular a continuous gap, ie it extends over the entire arcuate guide surface.
  • the guide surface is separated over its entire arcuate extent of the ring carrier through the gap.
  • a corresponding gap is preferably formed between each guide surface and the ring carrier, so that no direct connection in the axial direction between the guide surfaces and the
  • Ringbearer exists.
  • the guide surfaces are then thermally decoupled from the ring carrier at least insofar as a direct heat transfer is prevented. This is particularly advantageous against the background that the guide surfaces by the in the area of
  • Heat ring wear occurring heat carrier which can lead to increased friction between the guide surfaces and the cylinder wall due to the thermal expansion, especially when the heating of the guide surfaces and the cylinder wall takes place at different speeds and / or if the expansion due to different materials and different coefficients of thermal expansion is different degrees , This can lead to piston coverage (i.e., the piston diameter becomes larger than the cylinder diameter) and thereby, in extreme cases, even to a so-called
  • a stiffening rib extending transversely across the inner piston bottom is understood to mean in particular a stiffening rib which extends transversely from an outer point of the piston crown to another outer point of the piston crown. It is preferred if the stiffening rib over a majority of this
  • Extension length across the inner piston head is firmly connected to the inner piston crown.
  • a particularly secure, secant-like connection of the stiffening rib to the piston can be realized and a total stiff overall structure can be created.
  • the stiffening rib extends so far in particular secant above the inner piston crown.
  • the term "secant-like" is intended to express that the stiffening rib is not limited to linear stiffening rib configurations between two outer points of the circumference.Secilateral stiffening ribs in the sense of the invention are also considered stiffening ribs which have an arcuate or otherwise curved course Also, the thickness extending transversely to the direction of extension of the stiffening rib and the height of the stiffening rib (s) may vary, but preferably it is transverse to the
  • Length of the stiffening rib extending piston crown greater than the width and / or extending in the axial direction of the piston height of the stiffening rib. It has been shown that by the combination of the at least one gap between guide surface (s) and ring carrier on the one hand (in particular two gaps between each guide surface and the ring carrier) and the formation of at least one, extending transversely over the inner piston crown stiffening rib on the other (In particular, two stiffening ribs, each one stiffening rib is assigned to a guide surface) a piston according to the invention with low material usage can be constructed as required with high rigidity and yet saving material with low weight. It has been found that the construction according to the invention even makes it possible to produce and use a particularly weight-reduced aluminum piston. It is particularly preferred if the piston according to the invention is manufactured in one piece from aluminum.
  • the at least one stiffening rib extends in a central portion in the axial direction from the inner piston head so far that a piston pin hub is formed in the stiffening rib.
  • the middle section in particular the region within two on oppositely arranged guide surfaces is referred to as the middle section.
  • two or more stiffening ribs in particular two mutually parallel stiffening ribs, extend in the axial direction so far that in this
  • Stiffening ribs itself each have a piston pin hub is formed.
  • piston pin bosses are transmitted, in particular via an inserted piston pin, from the piston to a connecting rod in order to drive a crankshaft in a known manner.
  • a stiffening rib two stiffening ribs or more stiffening ribs a material-saving, but at the same time stiff overall structure can be achieved, by means of which the piston is guided well in the cylinder even at high piston forces, whereby a low-loss power transmission is possible.
  • the piston skirt is in particular on the at least one stiffening rib with the
  • connecting portions which are also connected to the ring carrier.
  • connecting portions which are also connected to the ring carrier.
  • two oppositely disposed guide surfaces are connected to one another via two connecting sections to form a frame-like structure and the connecting sections are each connected at least partially to the inner piston head. This can be the
  • Piston bottom of the ring carrier in addition to a connecting section or two
  • connection can be realized only indirectly via a further element, in particular via a stiffening rib, and / or be realized directly by the connecting portions are at least partially connected directly to the piston crown. In this case, it is preferred if such a connection is limited to areas spaced from the outer circumference of the piston, in particular to central areas around a piston pin hub or two or more piston pin bosses.
  • Connecting portion preferably connected via a smaller area to the inner piston crown as a corresponding stiffening rib.
  • the connecting portion is connected to it only in an inner region of the piston crown, i. in a region spaced from the outer circumference of the piston, in particular in a region located at a recess defined by an annular outer edge within the outer edge of the inner piston crown.
  • the connecting portion extends in particular only over a region surrounding the piston pin hub, for example over a length which is slightly larger than the diameter of the piston pin hub, e.g. a maximum of 1, 1-fold, a maximum of 1, 2-fold or a maximum of 1, 3 times the diameter of the piston pin hub, in particular such that the connecting portion extends over the piston pin hub and projects beyond this on both sides in the same length.
  • the piston pin hub is in particular from a perpendicular to the axial direction
  • the thickening is preferably part of
  • Connecting portion which is connected to the inner piston crown. This results in a surface area on a - viewed in the radial direction - central region of the piston crown limited contact area between the connecting portion and the inner piston crown of the ring carrier, which is thermally advantageous.
  • the connecting sections may in particular be arranged such that a frame-shaped structure consists of two oppositely arranged arcuate
  • the two stiffening ribs are in particular each inside of the
  • An additional weight saving can be achieved in connection with a piston according to the invention when the ring carrier is mounted on the surface facing the piston skirt, i. has in the region of the inner piston crown, a depression or more depressions.
  • a depression may in particular be delimited by an outer edge formed on the outside of the inner piston bottom, preferably by an outer edge which has a constant thickness over the entire circumference of the inner piston bottom.
  • One or more recesses may then extend within the outer edge.
  • the piston head thickness in particular by forming depressions, can be reduced and thus additional weight can be saved.
  • the at least one stiffening rib extends across the recess such that they each have a complete secant-like portion on the inner
  • Piston bottom is connected, i. If the secant-like section extends completely over two points of an outer edge, corresponding recesses result on both sides of the reinforcing rib.
  • two or more stiffening ribs extend transversely through the recess, in particular completely secant-like.
  • the formation of a depression or a plurality of depressions reduces the thickness of the annular carrier extending in the axial direction, which saves material and weight of the piston.
  • the at least one stiffening rib and / or the at least one connecting section is longitudinally (ie in its
  • Extending direction considered partially curved.
  • the longitudinal direction refers to the direction in which the stiffening rib or the connecting section has the greatest extent transversely to the axial direction, in particular the direction of extension of a secant-like section which extends transversely through the diameter of the piston.
  • an omega-shaped and / or curved and preferably curved outward course Connecting portion on an omega-shaped and / or curved and preferably curved outward course.
  • an omega-shaped and / or arcuate, in particular outwardly curved course improved flexural rigidity of the reinforcing rib and the piston can be achieved as a whole, in particular for receiving forces to be transmitted from the piston via a piston pin on a connecting rod.
  • the stiffening rib has a profile such that viewed in the longitudinal direction, the stiffening rib in the region of the piston pin hub merges into a thickening surrounding the piston pin hub on the inside and is arranged at a distance from the connecting portion in an outer region of the inner piston crown.
  • the thickness of the stiffening rib is externally enlarged, i. especially where the
  • Stiffening rib approaches the outer edge of the inner piston crown and / or adjacent to the outer edge of the inner piston crown.
  • each piston pin hub extending in each case also by a stiffening rib corresponding to this piston pin boss. Further preferably form the
  • Piston pin hub one unit i. the piston pin hub extends seamlessly through the connecting portion and the corresponding stiffening rib. Forces, which are transmitted via a piston pin between the piston and a connecting rod, are thus distributed to the connecting portion and the corresponding stiffening rib, each providing a common hollow cylindrical bearing surface for the piston pin.
  • each piston pin hub - and optionally also on the inside - extends in a further practical embodiment each one in the direction of the piston pin excellent thickening, in particular over the full circumference of the piston pin hub.
  • the thickening preferably extends from one middle portion of the inner piston crown and is more preferably formed in particular a circular arc around the piston pin hub around.
  • a further weight saving can be achieved if the at least one guide surface of the piston according to the invention has at least one recess, which the
  • Guide surface reduced to two or more partial guide surfaces.
  • weight can be saved on each guide surface of a piston if less material is required by the formation of one or more recesses (for example in the form of recesses, cuts, etc.). It has proven to be particularly advantageous, a first
  • Leaders can be safely absorbed, and to provide a second guide surface, which is exposed due to their arrangement in a cylinder under a low load, with one or more recesses in order to further reduce the weight.
  • the one or more recesses should (s) cause so far that the
  • Guide surface are divided into partial guide surfaces, which are smaller in total than an opposite guide surface.
  • the upper part guide surface is preferably larger than the lower part guide surface.
  • the invention also relates to a reciprocating internal combustion engine with a piston as described above.
  • the invention relates to an internal combustion engine with a piston, wherein at least one guide surface has at least one recess, which reduces the guide surface in two partial guide surfaces.
  • the partial guide surfaces are arranged such that they are arranged on the counter-pressure side.
  • the counter-pressure side is referred to as the side of a piston on which the piston during the
  • Cylinder on which the piston with the guide surface during the expansion phase after the bottom dead center, is referred to as the pressure side.
  • On the pressure side usually higher forces between cylinder wall and piston act.
  • FIG. 1 shows a piston according to the invention in a first embodiment in a
  • FIG. 2 shows the piston of FIG. 1 in a side view according to arrow II of FIG. 1,
  • Fig. 3 shows the piston of Fig. 1 and 2 in a longitudinal section along the section line III-III
  • FIG. 4 shows the piston of FIGS. 1 to 3 in a view from below according to arrow IV of FIG. 1,
  • Fig. 5 shows a second embodiment of a piston according to the invention in one
  • FIG. 5 shows the piston from FIG. 5 in a side view analogous to arrow II from FIG. 1, FIG.
  • Fig. 7 shows the piston of Fig. 5 and 6 in a longitudinal section analogous to the section line III-III in
  • Fig. 8 is a reciprocating internal combustion engine having disposed therein
  • piston 10 according to the invention described.
  • the piston 10 shown is in the
  • Embodiment made in one piece from aluminum. But it can alternatively (not shown) also be made in several parts. Regardless of this he may alternatively or in
  • Supplement also be made of other materials, e.g. made of steel materials.
  • the piston 10 comprises a ring carrier 12, which in this embodiment has a total of four depressions in the form of grooves 14 extending over the outer circumference of the ring carrier 12. Three of these grooves 14 - the first (top), the third and the fourth (bottom) - are so-called annular grooves, which serve for the arrangement of piston rings (not shown) and / or other sealing elements (see Fig. 2).
  • the second illustrated groove 14, which has a smaller radial depth than the remaining grooves, is an optional relief groove.
  • the ring carrier 12 has an outer piston head 16, which is directed in the installed state of the piston 10 in a reciprocating internal combustion engine to a combustion chamber and limits this. On the opposite side of the outer piston head 16 an inner piston head 18 is formed, which faces away from the combustion chamber in the installed state of the piston 10 in a reciprocating internal combustion engine.
  • the piston skirt 20 comprises two opposing, each having an arc section in
  • Circumferential direction of the piston 10 considered extending guide surfaces 22.
  • guide surfaces 22 each extend over an arc section of approximately 60 °. As can be clearly seen in FIGS. 2 and 3, the guide surfaces 22 do not touch the inner piston head 18 because the guide surfaces 22 are formed such that a continuous gap 24 is formed between the guide surfaces 22 and the inner piston head 18.
  • the height H s of the gap 24 in the present case is approximately 1-2 mm when viewed in the axial direction A (see FIG. 3).
  • the opposing guide surfaces 22 are connected by two connecting portions 26 which each extend between the guide surfaces 22.
  • Connecting portions 26 each extend between the circumferentially outer ends of the guide surfaces 22.
  • the connecting portions 26 extend substantially parallel to each other and spaced from the center M of the inner piston crown 18.
  • the connecting portions 26 are arcuate and curved outwards.
  • the two guide surfaces 22 and which form between the guide surfaces 22 form
  • connecting portions 26 circular piston pin bosses 28 are formed in cross-section, which serve for introducing a piston pin (not shown). Starting from the connecting portions 26 is on the outside and inside of the connecting portions 26
  • Piston pin bosses 28 an outside thickening 30a and an inside thickening 30b formed.
  • the thickenings 30a, 30b extend from a central one Section of the inner piston crown 18 over the full circumference of the circular piston pin hub 28th
  • the connecting portions 26 are connected to the inner piston crown 18 only in a central region which extends in each case via the piston pin bosses 28 and the thickenings 30a, 30b.
  • two stiffening ribs 32 are formed, which - as can be clearly seen in Fig. 4 - extend transversely across the inner piston crown 18.
  • Stiffening rib 32 approximately the depth T of the recess in the adjacent to an outer edge 36 of the inner piston crown 18 portion so that the stiffening rib 32 on the outside merges into the outer edge 36.
  • the stiffening ribs 32 have an omega-shaped profile in the direction of extent, wherein they are respectively curved outward in a central region.
  • the two stiffening ribs 32 are mirror-symmetrical to one another with respect to a mirror axis extending through the center M.
  • the stiffening ribs 32 In the outer regions, which adjoin the outer edge 36, the stiffening ribs 32 have a greater thickness.
  • the thickness of the stiffening ribs 32 in the embodiment in the outer sections is about 9 mm with a piston diameter between 70 mm and 80 mm.
  • the thickness of the stiffening ribs 32 in the outer regions is between 5 percent and 30 percent of the piston diameter, more preferably between 10 percent and 20 percent.
  • the piston diameter of a piston 10 according to the invention is preferably between 40 mm and 200 mm, more preferably between 60 mm and 150 mm and particularly preferably between 80 mm and 120 mm.
  • the stiffening ribs 32 are formed on the inside of the connecting portions 26 and are oriented substantially parallel to the connecting portions 26. In a middle region, each of the stiffening rib 32 and the inside thickening 30b form one unit, i. they are directly connected to each other, so that inside a
  • continuous piston pin hub 28 is formed with a hollow cylindrical shape.
  • these units each have a thickness D of about 20 percent of the piston diameter.
  • the thickness D is 10 percent to 30 percent of the piston diameter.
  • stiffening ribs 32 are spaced from the outside areas.
  • the stiffening ribs 32 are also spaced from the center M of the inner piston crown 18.
  • the ring carrier 12 has recesses 34 on the surface facing the piston skirt 20.
  • the depressions 34 are formed on the inside of the circular outer edge 36, which extends on the outside over the entire circumference of the piston 12 and has a constant thickness.
  • the recesses 34 are through the stiffening ribs 32 and the
  • connection sections 26 separated from each other. As can be seen in FIG. 4, this results in a total of seven regions with depressions 34, if it is taken into account that the depressions 34, each marked with two connected arrows, also extend over the respective region, which in FIG. 4 extends from the respective outer region of the connecting portion 26 is hidden. Therefore, only one contiguous recess 34 is marked with the connected arrows.
  • Stiffening rib 32 extends on the outside in each case starting from the inside of the outer edge 36 within the recess 34 in the transverse direction and is arc-shaped therebetween such that the piston pin hub 28 is enclosed, so that the
  • Piston pin hub 28 extends through the stiffening rib 32 therethrough.
  • FIGS. 5 to 7 show a second embodiment of a piston 10.
  • the piston 10 according to the second embodiment according to FIGS. 5 to 7 is identical to the piston 10 of the first embodiment according to FIGS. 1 to 4 constructed. In the following, only the differences between the second embodiment and the first embodiment will be discussed.
  • the piston 10 of the second embodiment also has a ring carrier 12 and a piston skirt 20 extending therefrom in the axial direction with two guide surfaces 22 extending over an arc section.
  • One of the guide surfaces 22 is presently divided by a recess 38 into two partial guide surfaces 40, 42, namely an upper part guide surface 40, which is arranged closer to the inner piston head 18, and a lower part guide surface 42, which further from the inner piston bottom 18 is removed.
  • the upper part-guide surface 40 has a greater, extending in the axial direction height than the lower part-guide surface 42. The extending in the axial direction of the height
  • Recess 38 corresponds to approximately the height of the upper part of the guide surface 40 in the embodiment shown.
  • FIG. 8 schematically shows a reciprocating internal combustion engine with a combustion chamber 44 in the form of a cylinder and a piston 10 arranged therein.
  • the piston 10 is connected by means of a connecting rod 46 with a crankshaft 48.
  • the piston 10 according to the second embodiment described above is arranged in the combustion chamber 44 such that the guide surface with the partial guide surfaces 40, 42 is arranged on a counter-pressure side 50, and the continuous guide surface 22 is arranged on a pressure side 52.
  • the pressure side 52 corresponds to that side on which the piston 10 with the continuous guide surface 22 during the expansion phase after passing through the top dead center (TDC) is applied, i. in Fig. 8, the left side when the crankshaft 48 rotates clockwise in the direction of arrow 54.
  • TDC top dead center

Landscapes

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

Abstract

L'invention concerne un piston pour un moteur à combustion interne à pistons alternatifs, comprenant un support annulaire (12) pourvu d'une tête de piston extérieure (16) et d'une tête de piston intérieure (18), et une jupe de piston (20) s'étendant depuis la tête de piston intérieure (18) dans une direction axiale. La jupe de piston (20) comporte au moins une surface de guidage (22) réalisée de manière à présenter au moins en partie une forme d'arc. La ou les surfaces de guidage (22) sont disposées dans la zone réalisée de manière à présenter une forme d'arc en vis-à-vis du support annulaire (12) se raccordant dans la direction axiale à distance de telle manière qu'une fente (24) entre le support annulaire (12) et la surface de guidage (22) en résulte. La jupe de piston (20) et le support annulaire (12) sont reliés entre eux par l'intermédiaire d'au moins une nervure de renforcement (32) qui s'étend de manière transversale au-dessus de la tête de piston intérieure (18).
EP18745585.2A 2017-08-08 2018-07-24 Piston pour un moteur à combustion interne à pistons alternatifs ainsi que moteur à combustion interne à pistons alternatifs Withdrawn EP3665378A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017213831.9A DE102017213831A1 (de) 2017-08-08 2017-08-08 Kolben für eine Hubkolbenbrennkraftmaschine sowie Hubkolbenbrennkraftmaschine
PCT/EP2018/069987 WO2019029982A1 (fr) 2017-08-08 2018-07-24 Piston pour un moteur à combustion interne à pistons alternatifs ainsi que moteur à combustion interne à pistons alternatifs

Publications (1)

Publication Number Publication Date
EP3665378A1 true EP3665378A1 (fr) 2020-06-17

Family

ID=63013038

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18745585.2A Withdrawn EP3665378A1 (fr) 2017-08-08 2018-07-24 Piston pour un moteur à combustion interne à pistons alternatifs ainsi que moteur à combustion interne à pistons alternatifs

Country Status (5)

Country Link
US (1) US20200173393A1 (fr)
EP (1) EP3665378A1 (fr)
CN (1) CN110892141A (fr)
DE (1) DE102017213831A1 (fr)
WO (1) WO2019029982A1 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017211335A1 (de) * 2017-07-04 2019-01-10 Federal-Mogul Nürnberg GmbH Verfahren zur Herstellung eines Kolbens für einen Verbrennungsmotor, Kolben für einen Verbrennungsmotor, Kolbenrohling zur Herstellung des Kolbens sowie Gießform oder Schmiedegesenk zur Herstellung eines Kolbenrohlings
USD897373S1 (en) * 2018-09-22 2020-09-29 Chaoming Li Piston
USD1009938S1 (en) * 2022-05-24 2024-01-02 Reme, Llc Elliptical piston for a rotary steerable tool

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US2177574A (en) * 1938-02-25 1939-10-24 Circle Motor Corp Piston

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FR983767A (fr) * 1949-03-29 1951-06-27 Noleiko Norddeutsche Leichtmet Piston pour moteurs à combustion interne présentant des fentes longitudinales et transversales
ZA74945B (en) * 1973-02-22 1974-12-24 Ass Eng Ltd Improvements in pistons
US3987709A (en) * 1975-04-07 1976-10-26 Day Ray E Piston
JP2522909Y2 (ja) * 1988-10-07 1997-01-22 トヨタ自動車株式会社 内燃機関用スケルトン型ピストン
GB8824222D0 (en) * 1988-10-15 1988-11-23 Wellworthy Ltd Pistons
US6840155B2 (en) * 2000-10-18 2005-01-11 Federal-Mogul World Wide, Inc. Multi-axially forged piston
JP4365257B2 (ja) * 2004-04-09 2009-11-18 トヨタ自動車株式会社 内燃機関用ピストン
DE102005043747A1 (de) * 2005-09-14 2007-03-22 GM Global Technology Operations, Inc., Detroit Kolben für eine Brennkraftmaschine
DE102007020447A1 (de) * 2007-04-27 2008-10-30 Mahle International Gmbh Kolben für einen Verbrennungsmotor
WO2014047123A1 (fr) * 2012-09-18 2014-03-27 Federal-Mogul Corporation Piston en acier possédant une conception de contre-alésage
JP2014062507A (ja) * 2012-09-21 2014-04-10 Suzuki Motor Corp 内燃機関用ピストン
DE102015201633A1 (de) 2015-01-30 2016-08-04 Federal-Mogul Nürnberg GmbH Kolben für einen Verbrennungsmotor sowie Verfahren zur Herstellung des Kolbens für einen Verbrennungsmotor
DE102015114952A1 (de) * 2015-09-07 2017-03-09 Volkswagen Aktiengesellschaft Kombination eines Kolbens und eines Pleuels
DE102015217911A1 (de) * 2015-09-18 2017-03-23 Mahle International Gmbh Kolben für eine Brennkraftmaschine

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Publication number Priority date Publication date Assignee Title
US2177574A (en) * 1938-02-25 1939-10-24 Circle Motor Corp Piston

Also Published As

Publication number Publication date
US20200173393A1 (en) 2020-06-04
DE102017213831A1 (de) 2019-02-14
CN110892141A (zh) 2020-03-17
WO2019029982A1 (fr) 2019-02-14

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