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EP3400381B1 - Monolithischer, kanalfreier kolben und verfahren zur konstruktion davon - Google Patents

Monolithischer, kanalfreier kolben und verfahren zur konstruktion davon Download PDF

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Publication number
EP3400381B1
EP3400381B1 EP17701366.1A EP17701366A EP3400381B1 EP 3400381 B1 EP3400381 B1 EP 3400381B1 EP 17701366 A EP17701366 A EP 17701366A EP 3400381 B1 EP3400381 B1 EP 3400381B1
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EP
European Patent Office
Prior art keywords
undercrown
piston
piston body
combustion
upper wall
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.)
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Application number
EP17701366.1A
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English (en)
French (fr)
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EP3400381A1 (de
Inventor
Jeff Riffe
Michael WEINENGER
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Federal Mogul LLC
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Federal Mogul LLC
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Priority claimed from US14/988,885 external-priority patent/US10738731B2/en
Application filed by Federal Mogul LLC filed Critical Federal Mogul LLC
Publication of EP3400381A1 publication Critical patent/EP3400381A1/de
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Publication of EP3400381B1 publication Critical patent/EP3400381B1/de
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    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition
    • F02B23/06—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston
    • F02B23/0642—Other engines characterised by special shape or construction of combustion chambers to improve operation with compression ignition the combustion space being arranged in working piston the depth of the combustion space being much smaller than the diameter of the piston, e.g. the depth being in the order of one tenth of the diameter
    • 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 
    • F02F3/26—Pistons  having combustion chamber in piston 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
    • F02F2200/04—Forging of engine parts

Definitions

  • This invention relates generally to internal combustion engines, and more particularly to pistons therefor.
  • Engine manufacturers are encountering increasing demands to improve engine efficiencies and performance, including, but not limited to, improving fuel economy, reducing oil consumption, improving fuel systems, increasing compression loads and operating temperatures within the cylinder bores, reducing heat loss through the piston, improving lubrication of component parts, decreasing engine weight and making engines more compact, while at the same time decreasing the costs associated with manufacture.
  • the piston for an internal combustion engine designed to improve engine efficiency and performance.
  • the piston is free of a cooling gallery along and undercrown surface and thus has a reduced weight and related costs, relative to known piston constructions, but still provides for exceptional cooling to maintain the temperature of the piston within workable limits.
  • the piston comprises a piston body extending along a central longitudinal axis.
  • the piston body has an upper wall forming an upper combustion surface and an annular ring belt depending from the upper combustion surface.
  • the upper combustion surface has first and second portions, the first portion extends annularly along an outer periphery of the upper wall, and the second portion forms a combustion bowl depending radially inwardly from the first portion.
  • the piston body further includes a pair of skirt panels depending from the ring belt, and a pair of pin bosses spaced from one another by the skirt panels providing a pair of laterally spaced pin bores.
  • the undercrown surface is formed on an underside of the upper wall and is located opposite the second portion of the upper combustion surface, radially inwardly of the ring belt.
  • the undercrown surface has an exposed 2-dimensional surface area, as viewed looking along the central longitudinal axis, ranging from 25 to 60 percent of a cross-sectional area defined by a maximum outer diameter of the piston body.
  • Another aspect of the invention according to claim 13, provides a method of constructing a piston which is free of a cooling gallery along an undercrown surface.
  • the method comprises forming a piston body extending along a central longitudinal axis by at least one of machining, forging, and casting.
  • the piston body has an upper wall forming an upper combustion surface and an annular ring belt depending from the upper combustion surface.
  • the upper combustion surface has first and second portions, the first portion extends annularly along an outer periphery of the upper wall, and the second portion forms a combustion bowl depending radially inwardly from the first portion.
  • the piston body further includes a pair of skirt panels depending from the ring belt, and a pair of pin bosses spaced from one another by the skirt panels providing a pair of laterally spaced pin bores.
  • the undercrown surface is formed on an underside of the upper wall and is located opposite the second portion of the upper combustion surface, radially inwardly of the ring belt.
  • the undercrown surface has an exposed 2-dimensional surface area, as viewed looking along the central longitudinal axis, ranging from 25 to 60 percent of a cross-sectional area defined by a maximum outer diameter of the piston body.
  • the piston 10 is "galleryless” in that it does not have a cooling gallery floor or other features bounding or partially bounding a cooling gallery.
  • the piston body being made of steel, is strong and durable to meet the high performance demands, i.e. increased temperature and compression loads, of modern day high performance internal combustion engines.
  • the steel (i.e., the steel alloy) used to construct the body can be SAE 4140 grade or different, depending on the requirements of the piston 10 in the particular engine application. Due to the piston 10 being galleryless, and the novel configuration of the body, among other things discussed below, minimizes the weight and compression height (CH) of the piston 10, thereby allowing an engine in which the pistons 10 are deployed to achieve a reduced weight and to be made more compact. Further yet, even though being galleryless, the novel construction discussed below and shown in the Figures allows the piston 10 to be sufficiently cooled during use to withstand the most severe operating temperatures.
  • the piston body has an upper head or top section providing an upper wall 14, which provides an upper combustion surface 16 that is directly exposed to combustion gasses within the cylinder bore of the internal combustion engine.
  • the upper combustion surface 16 includes an annular first portion 18 formed as a substantially planar surface extending along an outer periphery of the upper wall 14 and a second portion 20 forming a combustion bowl.
  • the second portion 20 of the upper combustion surface 16, which forms the combustion bowl, typically has a non-planar, concave, or undulating surface that depends from the planar first portion 18.
  • the piston 10 also includes an undercrown surface 24 formed on an underside of the upper wall 14, directly opposite the second portion 20 of the upper combustion surface 16 and radially inwardly of the ring belt 32.
  • the undercrown surface 14 is preferably located at a minimum distance from the combustion bowl and is substantially the surface on the direct opposite side from the combustion bowl.
  • the undercrown surface 24 is defined here to be the surface that is visible, excluding the pin bores 40, when observing the piston 10 straight on from the bottom.
  • the undercrown surface 24 can also be defined in view of a thickness t of the upper wall 14.
  • the thickness t of the upper wall 14 extends from the upper combustion surface 16 to the underside of the upper wall 14.
  • the portion of the underside of the upper wall 14 which is considered to be the undercrown surface 24 is typically a portion that is located a certain distance away from the second portion 20 of the upper combustion surface 16, and that distance is no more than two times the minimum thickness t of the upper wall 14 along the second portion 20.
  • the undercrown surface 24 can also be define as a portion of the underside of the upper wall 14 which is located at a distance not greater than 10 mm away from the upper combustion surface 16. Accordingly, the undercrown surface 24 is generally form fitting to the combustion bowl of the upper combustion surface 16.
  • the undercrown surface 24 is also openly exposed, as viewed from an underside of the piston 10, and it is not bounded by an enclosed or partially enclosed cooling gallery, or any other features tending to retain oil or a cooling fluid near the
  • the annular first portion 18 of the upper wall 14 forms an outer periphery of the upper wall 14 and surrounds the second portion forming the combustion bowl, which depends therefrom.
  • the second portion 20, including the combustion bowl is recessed below the uppermost first portion 18 of the upper combustion surface 16.
  • the combustion bowl of the second portion 20 also extends continuously through a central axis 30 and across the entire diameter of the piston 10, between opposite sides of the annular first portion 18.
  • the combustion bowl typically comprises a concave surface extending continuously between the opposite sides of the annular first portion 18.
  • the combustion bowl wall can be contoured, for example to provide an upper apex, also referred to as center peak (not shown), which may lie coaxially along the central axis 30 of the piston 10, or may be axially offset relative to the piston central axis 30.
  • the top section of the piston 10 further includes a ring belt 32 that depends from the upper combustion surface 16 to provide one or more ring grooves 34 for receipt of one or more corresponding piston rings (not shown).
  • at least one valve pocket 29 having a curved profile is formed in the annular first portion 18 of the upper wall 14. The combustion bowl does not include the valve pockets 29.
  • the piston body further includes a bottom section including a pair of pin bosses 38 depending generally from the upper wall 14.
  • the pin bosses 38 each have a pin bore 40, preferably bushingless given the steel construction, wherein the pin bores 40 are laterally spaced from one another coaxially along a pin bore axis 42 that extends generally transversely to the central longitudinal axis 30.
  • the pin bosses 38 have generally flat, radially outermost surfaces, referred to as outer faces 43, that are spaced from one another along the pin bore axis 40 a distance PB, shown as being generally parallel with one another.
  • the PB dimension is minimized, thereby maximizing an exposed area of a recessed, generally cup-shaped region, referred to hereafter as undercrown pockets 50.
  • the undercrown pockets 50 also extend radially outwardly beyond the undercrown surface 24 along an underside surface of the annular first portion 18 of the upper combustion surface 16 and depend from the upper wall 14 along an inner surface of the ring belt 32. These portions of the undercrown pockets 50 are either located outwardly of the second portion 20 of the upper combustion surface 16, at a distance of greater than two times a minimum thickness of the upper wall 14, and/or at a distance of greater than 10 mm from the upper combustion surface 16, and thus they do not form a portion of the undercrown surface 24.
  • the cooling caused by oil splashing or being sprayed upwardly from the crankcase against the exposed surface of the undercrown pockets 50 is enhanced, thereby lending to further cooling of the upper combustion surface 16, the undercrown surface 24, as well as a portion of the ring belt 34.
  • the pin bores 40 each have a concave uppermost load bearing surface, referred to hereafter as uppermost surface 44, disposed near the ring belt 32. As such, the compression height CH is minimized (the compressing height is the dimension extending from the pin bore axis 42 to the upper combustion surface 16).
  • the pin bosses 38 are joined via outer panels, also referred to as struts 46, to diametrically opposite skirt panels, also referred to as skirt panels 48.
  • the pin bosses 38, skirt panels 48 and struts 46 bound an open region extending from a lowermost or bottom surface 51 of the struts 46 and skirt panels 48 to the undercrown surface 24.
  • no ribs are located along the undercrown surface 24, along the pin bosses 38, along the skirt panels 48, or along the struts 46 in the open region.
  • no closed or partially closed cooling gallery is formed in the open region.
  • the piston 10 can include a stepped region 54 along the uppermost edge of each skirt panel 48 adjacent the undercrown surface 24, as identified in Figures 1 and 2 .
  • the stepped regions 54 are not considered part of the undercrown surface 24.
  • the piston 10 does include a pair of ribs 58 along the undercrown surface 24 to enhance cooling. These ribs 58 extend continuously along the undercrown surface 24 between the opposite skirt panels 38.
  • the open region along the underside of the piston 10 provides direct access to oil splashing or being sprayed from within the crankcase directly onto the undercrown surface 24, thereby allowing the entire undercrown surface 24 to be splashed directly by oil from within the crankcase, while also allowing the oil to freely splash about the wrist pin (not shown), and further, significantly reduce the weight of the piston 10.
  • the generally open configuration of the galleryless piston 10 allows optimal cooling of the undercrown surface 24 and lubrication to the wrist pin joint within the pin bores 40, while at the same time reducing oil residence time on the surfaces near the combustion bowl, which is the time in which a volume of oil remains on the surface.
  • the reduced residence time can reduce unwanted build-up of coked oil, such as can occur in pistons having a closed or substantially closed cooling gallery. As such, the piston 10 remains "clean" over extended use, thereby allowing it to remain substantially free of build-up.
  • the undercrown surface 24 of the piston 10 has greater a total surface area (3-dimensional area following the contour of the surface) and a greater projected surface area (2-dimensional area, planar, as seen in plan view) than comparative pistons having a closed or partially closed cooling gallery.
  • the total exposed surface area defined as the 3-dimensional area A u3D following the contour of the undercrown surface 24, is an expansive area for contact by cooling oil while the piston 10 is in use.
  • the 3-dimensional area A u3D of the undercrown surface 24 is greater than 30 percent of, and typically ranges from 40 to 90 percent of a cross-sectional area A OD defined by the maximum outer diameter OD of the piston 10.
  • the undercrown surface 24 has a projected surface area, defined as the 2-dimensional surface area A u2D seen looking generally along the central longitudinal axis 30 from the bottom of the piston 10 of greater than 25 percent, and typically ranging from 30 to 60 percent of the cross-sectional area defined by the maximum outer diameter OD of the piston 10. More preferably, the 2-dimensional surface area A u2D ranges from 30 to 55 percent of the cross-sectional area defined by the maximum outer diameter OD of the piston 10. As indicated above, a portion of the 2-dimensional surface area A u2D of the undercrown surface 24 is located within the pockets 50.
  • the 2-dimensional surface area A u2D of the undercrown surface 24 can also be measured relative to the 2-dimensional surface area A c2D of the combustion bowl along the upper combustion surface 16.
  • the 2-dimensional surface area A u2D of the undercrown surface 24 ranges from 50 to 125 percent of the 2-dimensional surface area A c2D of the combustion bowl.
  • the valve pockets 29 are not included in the 2-dimensional surface area A c2D of the combustion bowl.
  • the 3-dimensional surface area A u3D of the undercrown surface 24 can also be measured relative to the 3-dimensional surface area A c3D of the combustion bowl along the upper combustion surface 16.
  • the 3-dimensional surface area A u3D of the undercrown surface 24 ranges from 50 to 120 percent of the 3-dimensional surface area A c3D of the combustion bowl.
  • a portion of the 3-dimensional surface area A u3D of the undercrown surface 24 is located within the pockets 50.
  • Figure 7 identifies the outer diameter OD and the 2-dimensional surface area A u2D of the undercrown surface 24 of the piston 10 of Figure 6 ;
  • Figure 8 illustrates the 3-dimensional undercrown surface area A u3d of the piston 10 shown in Figure 6 ;
  • Figure 9 illustrates the 2-dimensional surface area A c2D of the combustion bowl of the piston 10 shown in Figure 6 .
  • the exposed area of the undercrown surface 24 typically has a diameter D u , as shown in Figure 7 , ranging from 75 to 90 percent of the maximum outer diameter OD of the piston 10.
  • the exposed area of the undercrown surface 24 can have a diameter D u ranging from 85 to 140 percent of the diameter D c of the combustion bowl, which is in contrast to a maximum of 100 percent for a piston having a closed or substantially closed cooling gallery.
  • the percentages of relative surface areas and relative diameters can vary from the ranges disclosed above while still providing for enhanced cooling.
  • the percentages of relative surface areas and relative diameters of the exposed undercrown surface 24 of the piston 10 are far in excess of conventional pistons, and in some cases, are upwards to three times greater or more.
  • the upper combustion surface 16 can be cooled directly via oil splashing upwardly from the crankcase, which can be coupled with the assistance from oil jets, if desired.
  • the undercrown pockets 50 of the piston 10 define at least a portion of the undercrown surface 24, as well as a portion of an underside of the first portion 18 and a portion of an inner surface of the annular ring belt 32.
  • the undercrown pockets 50 together have a total 2-dimensional surface area A p2D ranging from 18 to 35 percent of the cross-sectional area A OD defined by the maximum outer diameter of the piston 10.
  • the undercrown pockets 50 also have a total 3-dimensional area A p3D ranging from 50 to 85 percent of the cross-sectional area A OD defined by the maximum outer diameter of the piston 10.
  • An example of the 3-dimesnional area A p3D of the undercrown pockets 50 is also shown in Figure 8 .
  • FIG. 1-11 Another significant aspect of the example pistons 10 shown in Figures 1-11 is that at least a center portion 52 of the undercrown surface 24 of the piston 10 disposed between the opposite skirt panels 38 and the opposite pin bosses 38 is concave in form, when viewing from the bottom of the piston 10.
  • This concave portion 52 has a length extending longitudinally between the skirt panels 38 and a width extending between the pin bosses 38. The length of the concave portion 52 is typically greater than the width.
  • the radius of curvature of the concave portion 52 ranges from 30 to 500 mm.
  • the concave portion 52 is axially offset from the pockets 50 or other surrounding area of the undercrown surface 24.
  • the concave portion 52 can be disposed closer to the pin bosses 38 than the surrounding area.
  • Figure 12 illustrates a piston 10' with an enhanced undercrown surface 24' according to another example embodiment.
  • the piston 10' includes a concave portion 52' which is axially offset from the central longitudinal axis 30' of the piston 10'. This offset concave portion 52' can be used in place of, or in addition to, the concave portion 52.
  • Figure 13 illustrates yet another example piston 10" with an enhanced undercrown surface area 24".
  • the undercrown surface 24" includes a convex portion 56" disposed along the central longitudinal axis 30" of the piston 10" to channel oil during reciprocation of the piston 10".
  • the convex portion 56" extends continuously along the entire undercrown surface 24" between the opposite skirt panels 38".
  • the convex portion 56" could be located along only a portion of the undercrown surface 24", either at the central longitudinal axis or axially offset from the central longitudinal axis 30".
  • the radius of curvature of the convex portion 56" typically ranges from 80 to 300 mm.

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  • 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)

Claims (13)

  1. Kolben (10) für einen Verbrennungsmotor, umfassend:
    einen Kolbenkörper, der sich entlang einer mittleren Längsachse (30) erstreckt;
    wobei der Kolbenkörper eine obere Wand (14), die eine obere Verbrennungsfläche (16) bildet, und eine kreisförmige Ringpartie (32), die von der oberen Verbrennungsfläche (16) herabhängt, aufweist;
    die obere Verbrennungsfläche (16) erste und zweite Abschnitte (18, 20) aufweist, wobei sich der erste Abschnitt (18) kreisförmig entlang einer äußeren Peripherie der oberen Wand (14) erstreckt und der zweite Abschnitt (20) eine Verbrennungsschale bildet, die radial nach innen von dem ersten Abschnitt (18) herabhängt;
    die obere Wand (14) eine Innenfläche (24) aufweist, die an ihrer Unterseite gebildet ist, wobei die Innenfläche (24) gegenüber dem zweiten Abschnitt (20) der oberen Verbrennungsfläche (16) und radial nach innen von der Ringpartie (32) liegt;
    der Kolbenkörper ein Paar Sockelbleche (48) beinhaltet, die von der Ringpartie (32) herabhängen;
    der Kolbenkörper ein Paar Stiftsockel (38) beinhaltet, die durch die Sockelbleche (48) voneinander beabstandet sind und ein Paar seitlich beabstandeter Stiftbohrungen (40) bereitstellen;
    der Kolbenkörper frei von einem Kühlkanal entlang der Innenfläche (24) ist; und
    die Innenfläche (24) eine freiliegende zweidimensionale Oberfläche (Au2D) aufweist, wenn entlang der mittleren Längsachse (30) betrachtet, die von 25 bis 60 Prozent einer Querschnittsfläche (AOD) reicht, die durch einen maximalen Außendurchmesser (OD) des Kolbenkörpers definiert ist,
    wobei der Kolbenkörper Innentaschen (50) beinhaltet, die von den Stiftsockeln (38) radial nach außen liegen, mindestens ein Abschnitt der Innentaschen (50) mindestens einen Abschnitt der Innenfläche (24) bildet und die Innentaschen (50) eine gesamte zweidimensionale Oberfläche (Ap2D) aufweisen, die von 18 bis 35 Prozent der Querschnittsfläche (AOD) reicht, die durch den maximalen Außendurchmesser (OD) des Kolbenkörpers definiert ist,
    wobei die Innenfläche (24) entlang der Unterseite der oberen Wand (14) bei einem Abstand zu der oberen Verbrennungsfläche (16) liegt und der Abstand nicht größer als 10 mm ist,
    dadurch gekennzeichnet, dass
    die Innenfläche (24) einen Durchmesser (Du) aufweist, der von 100 bis 140 Prozent eines Durchmessers (Dc) der Verbrennungsschale reicht.
  2. Kolben (10) nach Anspruch 1, wobei die zweidimensionale Oberfläche (Au2D) der Innenfläche (24) von 30 bis 55 Prozent der Querschnittsfläche (AOD) reicht, die durch den maximalen Außendurchmesser (OD) des Kolbenkörpers definiert ist.
  3. Kolben (10) nach Anspruch 1, wobei eine dreidimensionale Oberfläche (Au3D) der Innenfläche (24) von 50 bis 120 Prozent einer dreidimensionalen Oberfläche (Ac3D) der Verbrennungsschale reicht.
  4. Kolben (10) nach Anspruch 1, wobei die Innenfläche (24) eine dreidimensionale Oberfläche (Au3D) aufweist, die von 30 bis 90 Prozent der Querschnittsfläche (AOD) reicht, die durch den maximalen Außendurchmesser (OD) des Kolbenkörpers definiert ist.
  5. Kolben (10) nach Anspruch 1, wobei die Innentaschen (50) eine gesamte dreidimensionale Oberfläche (Ap3D) aufweisen, die von 50 bis 85 Prozent der Querschnittsfläche (AOD) reicht, die durch den maximalen Außendurchmesser (OD) des Kolbenkörpers definiert ist.
  6. Kolben (10) nach Anspruch 1, wobei die Abschnitte der Innentaschen (50), die den Abschnitt der Innenfläche (24) bilden, gegenüber dem zweiten Abschnitt (20) der oberen Verbrennungsfläche (16) und radial nach innen von der Ringpartie (32) und mit einem Abstand von nicht mehr als 10 mm zu der oberen Verbrennungsfläche (16) liegen.
  7. Kolben (10) nach Anspruch 1, wobei die Innenfläche (24) einen konkaven Abschnitt (52) beinhaltet, der entlang der mittleren Längsachse (30) liegt, wobei eine Länge des konkaven Abschnitts (52) größer als eine Breite des konkaven Abschnitts (52) ist.
  8. Kolben (10) nach Anspruch 1, wobei die Innenfläche (24) einen konkaven Abschnitt (52) beinhaltet, der axial von der mittleren Längsachse (30) versetzt ist.
  9. Kolben (10) nach Anspruch 8, wobei der konkave Abschnitt (52) einen Krümmungsradius aufweist, der von 30 bis 500 mm reicht.
  10. Kolben (10) nach Anspruch 1, wobei die Innenfläche (24) einen konvexen Abschnitt (56) beinhaltet, der entlang der mittleren Längsachse (30) liegt, und der konvexe Abschnitt (56) einen Krümmungsradius aufweist, der von 80 bis 300 mm reicht.
  11. Kolben (10) nach Anspruch 1, wobei die obere Wand (14) eine Dicke (t) aufweist, die sich von der Verbrennungsfläche (16) zu der Unterseite der oberen Wand (14) erstreckt, wobei die Innenfläche (24) entlang der Unterseite mit einem Abstand zu der Verbrennungsfläche (16) liegt und der Abstand nicht mehr als ein Zweifaches einer minimalen Dicke (t) der oberen Wand (14) ist.
  12. Kolben (10) nach Anspruch 1, wobei die Innenfläche (24) entlang der Unterseite der oberen Wand (14) bei einem Abstand zu der oberen Verbrennungsfläche (16) liegt und der Abstand nicht größer als 10 mm ist.
  13. Verfahren zum Konstruieren eines Kolbens (10), das den folgenden Schritt umfasst:
    Bilden eines Kolbenkörpers, der sich entlang einer mittleren Längsachse (30) erstreckt, durch mindestens eines von maschinellem Bearbeiten, Schmieden und Gießen;
    wobei der Kolbenkörper eine obere Wand (14), die eine obere Verbrennungsfläche (16) bildet, und eine kreisförmige Ringpartie (32), die von der oberen Verbrennungsfläche (16) herabhängt, aufweist;
    die obere Verbrennungsfläche (16) erste und zweite Abschnitte (18, 20) aufweist, wobei sich der erste Abschnitt (18) kreisförmig entlang einer äußeren Peripherie der oberen Wand (14) erstreckt und der zweite Abschnitt (20) eine Verbrennungsschale bildet, die radial nach innen von dem ersten Abschnitt (18) herabhängt;
    die obere Wand (14) eine Innenfläche (24) aufweist, die an ihrer Unterseite gebildet ist, wobei die Innenfläche (24) gegenüber dem zweiten Abschnitt (20) der oberen Verbrennungsfläche (16) und radial nach innen von der Ringpartie (32) liegt;
    der Kolbenkörper ein Paar Sockelbleche (48) beinhaltet, die von der Ringpartie (32) herabhängen;
    der Kolbenkörper ein Paar Stiftsockel (38) beinhaltet, die durch die Sockelbleche (48) voneinander beabstandet sind und ein Paar seitlich beabstandeter Stiftbohrungen (40) bereitstellen;
    der Kolbenkörper frei von einem Kühlkanal entlang der Innenfläche (24) ist; und
    die Innenfläche (24) eine freiliegende zweidimensionale Oberfläche (Au2D) aufweist, wenn entlang der mittleren Längsachse (30) betrachtet, die von 25 bis 60 Prozent einer Querschnittsfläche (AOD) reicht, die durch einen maximalen Außendurchmesser (OD) des Kolbenkörpers definiert ist,
    wobei der Kolbenkörper Innentaschen (50) beinhaltet, die von den Stiftsockeln (38) radial nach außen liegen, mindestens ein Abschnitt der Innentaschen (50) mindestens einen Abschnitt der Innenfläche (24) bildet und die Innentaschen (50) eine gesamte zweidimensionale Oberfläche (Ap2D) aufweisen, die von 18 bis 35 Prozent der Querschnittsfläche (AOD) reicht, die durch den maximalen Außendurchmesser (OD) des Kolbenkörpers definiert ist,
    wobei die Innenfläche (24) entlang der Unterseite der oberen Wand (14) bei einem Abstand zu der oberen Verbrennungsfläche (16) liegt und der Abstand nicht größer als 10 mm ist,
    dadurch gekennzeichnet, dass
    die Innenfläche (24) einen Durchmesser (Du) aufweist, der von 100 bis 140 Prozent eines Durchmessers (Dc) der Verbrennungsschale reicht.
EP17701366.1A 2016-01-06 2017-01-04 Monolithischer, kanalfreier kolben und verfahren zur konstruktion davon Active EP3400381B1 (de)

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US14/988,885 US10738731B2 (en) 2013-11-07 2016-01-06 Monolithic, galleryless piston and method of construction thereof
PCT/US2017/012113 WO2017120179A1 (en) 2016-01-06 2017-01-04 Monolithic, galleryless piston and method of construction thereof

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JPS58142313U (ja) * 1982-03-20 1983-09-26 トヨタ自動車株式会社 内燃機関のピストン油冷却装置
JP4333693B2 (ja) * 2006-05-22 2009-09-16 トヨタ自動車株式会社 内燃機関用ピストンおよび内燃機関
CN101553656B (zh) * 2006-11-08 2011-01-19 费德罗-莫格尔公司 带有扭转裙板的活塞
KR20090064187A (ko) * 2007-12-15 2009-06-18 현대자동차주식회사 피스톤 냉각구조
US20110073061A1 (en) * 2009-09-28 2011-03-31 Jeungsuck Chae Pistons with a rough surface
US20130032120A1 (en) * 2011-08-04 2013-02-07 Caterpillar, Inc. Piston For Internal Combustion Engine And Method
US10184421B2 (en) * 2012-03-12 2019-01-22 Tenneco Inc. Engine piston
CN105940213B (zh) * 2013-11-07 2019-11-26 天纳克股份有限公司 整体式无通道活塞及其构造方法

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BR112018013210A2 (pt) 2018-12-11
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JP2019502856A (ja) 2019-01-31
EP3400381A1 (de) 2018-11-14
WO2017120179A1 (en) 2017-07-13
CN108699997A (zh) 2018-10-23

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