US20030075137A1 - Closed gallery monobloc piston having oil drainage groove - Google Patents
Closed gallery monobloc piston having oil drainage groove Download PDFInfo
- Publication number
- US20030075137A1 US20030075137A1 US10/253,786 US25378602A US2003075137A1 US 20030075137 A1 US20030075137 A1 US 20030075137A1 US 25378602 A US25378602 A US 25378602A US 2003075137 A1 US2003075137 A1 US 2003075137A1
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- United States
- Prior art keywords
- piston
- oil
- drainage groove
- oil drainage
- pin bosses
- Prior art date
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Classifications
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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
- F02F3/20—Pistons having cooling means the means being a fluid flowing through or along piston
-
- 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
- F16J1/08—Constructional features providing for lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F3/00—Pistons
- F02F3/16—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
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/08—Lubricating systems characterised by the provision therein of lubricant jetting means
- F01M2001/083—Lubricating systems characterised by the provision therein of lubricant jetting means for lubricating cylinders
-
- 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
- F02F2003/0007—Monolithic pistons; One piece constructions; Casting of pistons
Definitions
- This invention relates generally to monobloc pistons for diesel engine applications in which the piston head is formed with an internal oil cooling gallery and includes a piston skirt fixed to the pin bosses and ring belt of the head, and more particularly to the management of lubricating oil scraped from the cylinder walls of the engine during operation of the piston.
- Diesel engines often employ so-called monobloc pistons in which the piston head and skirt are unitized, such that the skirt is immovable relative to the head.
- the piston head is formed with an internal cooling gallery in which cooling oil is circulated to cool the head during operation.
- the piston head includes an outer ring belt in which a number of circumferentially continuous ring grooves are formed.
- the ring grooves accommodate corresponding piston rings that ride against the wall of the piston cylinder during operation, in known manner.
- the lowest of the ring grooves accommodates an oil scrapper ring which serves to scrape oil from the walls of the cylinder in order to limit the amount of oil that passes by the remaining compression rings to minimize “blow-by” and thus hydrocarbon emissions of the engine.
- a certain amount of oil does get by the compression rings.
- the oil that is scraped from the walls builds up ahead of the rings and gets trapped between the walls of the piston and the cylinder. Consequently, it is believed that a hydro-dynamic film of captured oil builds at the inner face between the oil scrapper ring and, despite high contact pressure, it is caused to escape past the rings.
- a monobloc piston constructed according to a presently preferred embodiment of the invention includes a piston head having a combustion bowl formed in an upper surface of the head and an outer ring belt formed with a plurality of ring grooves in an outer surface of the ring belt.
- a cooling gallery is formed in the piston head having an outer wall provided at least in part by the ring belt.
- a pair of pin bosses extend from the piston head opposite the combustion bowl and are formed with axially aligned pin bores. The pin bosses have outer side faces that are spaced laterally inwardly of the outer surface of the ring belt.
- a piston skirt is fixed at its upper end to the ring belt and is formed as one piece with the pin bosses.
- the piston head is formed with at least one oil drainage groove below the lowest of the ring grooves which is free of piston rings and open to the outer surfaces of the pin bosses.
- the invention also contemplates a method of forming a monobloc piston having such features.
- the invention has the advantage of providing a monobloc piston with improved oil scrapping management, and more particularly improved drainage of the oil scraped from the walls of the piston to minimize escapement past the rings.
- the improved oil drainage reduces the buildup and back pressure of oil ahead of the oil scraping ring during the downstroke of the piston, thus allowing more of the oil to be scraped from the walls and less of the oil to escape past the rings, for a recognized reduction in the emission of hydro-carbons from such diesel engines.
- FIG. 1 is a perspective view of a piston constructed according to a presently preferred embodiment of the invention
- FIG. 2 is a cross-sectional view of the piston of FIG. 1 taken along lines 2 - 2 of FIG. 1;
- FIG. 3 is a cross-sectional view of the piston of FIG. 1 taken along lines 3 - 3 of FIG. 1.
- FIGS. 1 - 3 show a closed gallery monobloc piston generally at 10 constructed according to a presently preferred embodiment of the invention.
- the piston 10 includes an upper head portion or piston head 12 having an outer generally cylindrical ring belt 14 extending between an upper face or surface 16 of the head portion 12 and a lower region 18 spaced from the upper face 16 .
- the ring belt 14 is formed with a plurality of piston ring grooves 20 , 22 and 24 machined into an outer surface 26 of the ring belt 14 .
- the outer surface 26 has a predetermined diameter BD, designated as the bore diameter in FIGS. 2 and 3.
- the wall of the ring belt 14 has a predetermined thickness or width, designated RBW, corresponding to the thickness of the ring belt wall inwardly from the base of the ring grooves 20 , 22 and 24 .
- the head portion 12 is formed with a combustion bowl 28 machined into the upper face 16 of the head portion 12 radially inwardly from the ring belt 14 and presenting a contoured combustion bowl wall 30 .
- the head portion 12 has a predetermined top land height designated TLH, measured from the top of the upper ring groove 20 and the upper surface 16 as shown in FIG. 2.
- the piston 10 has an internal, annular oil gallery 32 having an outer wall defined in part by the ring belt 14 and upper wall defined by the combustion bowl wall 30 .
- the oil gallery 32 is further bound by an inner annular support wall 34 which is spaced radially inwardly from the ring belt 14 and extends between the combustion bowl wall 30 and a lower circumferentially extending wall 36 which further extends between the inner support wall 34 and ring belt 14 in spaced relation to the combustion bowl wall 30 and closes off the bottom of the oil gallery 32 .
- the inner support wall 34 has a predetermined inner support wall width, designated ISW, and defines an inner support mean diameter, designated ISMD, of predetermined dimension as illustrated in FIG. 2.
- the top of the oil gallery 32 extends above the top of the upper ring groove 20 by a predetermined distance designated GRP in FIG. 3.
- the oil gallery 32 has a predetermined gallery volume, designated GV in FIG. 3.
- a pair of pin bosses 38 extend downwardly from the head portion 12 and have inner faces 40 which are spaced axially from one another to define a space 42 for receiving the upper end of a connecting rod therein.
- the pin bosses 38 are formed with axially aligned pin bores 42 along a pin bore axis A.
- the pin bores 44 receive a wrist pin (not shown) which couples the piston 10 to the connecting rod (not shown).
- the piston 10 has predetermined compression height, designated CH in FIG. 2, measured between the pin bore axis A and the top surface 16 of the head portion 12 .
- the piston 10 is formed with an integral piston skirt 46 .
- the skirt 46 extends downwardly from the ring belt 14 of the head portion 12 and is coupled or unitized immovably to each of the pin bosses 38 on opposite sides of the piston.
- the piston skirt 46 extends between a lower surface 48 and an upper surface 50 .
- the skirt 46 has a predetermined skirt length, designated SL measured between the lower and upper surfaces 48 , 50 of the skirt, as shown in FIG. 3.
- An oil drainage groove 52 is machined into the outer surface 26 of the ring belt 14 adjacent its lower region 18 , separating the outer surface 26 of the ring belt from an outer surface 54 of the skirt 46 and defining the upper surface 50 of the skirt 46 .
- the groove 52 does not extend through to the gallery 32 nor to the interior of the skirt 46 and is preferably aligned radially with the bottom wall 36 of the gallery 32 .
- a bottom wall 53 of the oil groove 52 extends circumferentially about the piston 10 between the pin bosses 38 , but is interrupted across the region of the pin bosses 38 , such that the oil groove 50 opens up to the recessed outer planar faces 56 of the pin bosses 38 as illustrated in FIG. 2, permitting any oil gathered in the oil groove 52 to drain downwardly back into the crank case across the region of the outer faces 56 .
- An upper wall 55 of the oil drainage groove 52 is preferably continuous about the circumference of the piston body 12 .
- piston rings 58 , 62 and 64 are accommodated in the ring grooves 20 , 22 and 24 , respectively, while the oil groove 52 is free of any piston rings.
- the space 42 between the pin bores is open to the combustion bowl wall 30 .
- the oil gallery 32 is formed with one or more oil inlets, schematically shown at 66 in FIG. 3, that communicate with one or more corresponding oil jets (not shown) in operation of the piston for directing cooling oil into the oil gallery 32 to cool the surrounding walls of the gallery 32 with a known “cocktail-shaker” action of the oil as a result of the reciprocating movement of the piston 10 in operation.
- Oil introduced to the oil gallery 32 is permitted to escape through one or more discharge ports, schematically shown at 68 in FIG. 3, into the inner space 64 for drainage back into the crank case (not shown).
- the piston 10 may be initially formed from two or more component parts machined with the oil gallery features which are subsequently joined to one another to form the closed gallery 32 in a subsequent joining operation.
- the piston 10 is formed from separate upper and lower crown parts which are joined preferably by friction welding across parting line 70 , shown in FIG. 2.
- other forms of welding, brazing, or securing of the crown parts are contemplated by the invention.
- the piston 10 is fabricated of steel and has the following dimensional relationships that enable the piston to operate successfully under high cylinder pressures in the vicinity of 300 bar.
- this is but one exemplary embodiment, and the oil drainage groove 52 could be used with other monobloc piston configurations that do not meet the following dimensional criteria:
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
Abstract
Description
- The disclosure incorporates
provisional patent application 60/355,693, filed Oct. 23, 2001, whose priority is claimed for this application. - 1. Technical Field
- This invention relates generally to monobloc pistons for diesel engine applications in which the piston head is formed with an internal oil cooling gallery and includes a piston skirt fixed to the pin bosses and ring belt of the head, and more particularly to the management of lubricating oil scraped from the cylinder walls of the engine during operation of the piston.
- 2. Related Art
- Diesel engines often employ so-called monobloc pistons in which the piston head and skirt are unitized, such that the skirt is immovable relative to the head. The piston head is formed with an internal cooling gallery in which cooling oil is circulated to cool the head during operation.
- The piston head includes an outer ring belt in which a number of circumferentially continuous ring grooves are formed. The ring grooves accommodate corresponding piston rings that ride against the wall of the piston cylinder during operation, in known manner. Typically, the lowest of the ring grooves accommodates an oil scrapper ring which serves to scrape oil from the walls of the cylinder in order to limit the amount of oil that passes by the remaining compression rings to minimize “blow-by” and thus hydrocarbon emissions of the engine. Despite best efforts, a certain amount of oil does get by the compression rings. During the downstroke, the oil that is scraped from the walls builds up ahead of the rings and gets trapped between the walls of the piston and the cylinder. Consequently, it is believed that a hydro-dynamic film of captured oil builds at the inner face between the oil scrapper ring and, despite high contact pressure, it is caused to escape past the rings.
- It is an object of the present invention to improve upon such monobloc pistons by providing better management of the oil scrapped from the cylinder walls to reduce blow-by and thus hydrocarbon emissions of such pistons.
- A monobloc piston constructed according to a presently preferred embodiment of the invention includes a piston head having a combustion bowl formed in an upper surface of the head and an outer ring belt formed with a plurality of ring grooves in an outer surface of the ring belt. A cooling gallery is formed in the piston head having an outer wall provided at least in part by the ring belt. A pair of pin bosses extend from the piston head opposite the combustion bowl and are formed with axially aligned pin bores. The pin bosses have outer side faces that are spaced laterally inwardly of the outer surface of the ring belt. A piston skirt is fixed at its upper end to the ring belt and is formed as one piece with the pin bosses. According to the invention, the piston head is formed with at least one oil drainage groove below the lowest of the ring grooves which is free of piston rings and open to the outer surfaces of the pin bosses. The invention also contemplates a method of forming a monobloc piston having such features.
- The invention has the advantage of providing a monobloc piston with improved oil scrapping management, and more particularly improved drainage of the oil scraped from the walls of the piston to minimize escapement past the rings. The improved oil drainage reduces the buildup and back pressure of oil ahead of the oil scraping ring during the downstroke of the piston, thus allowing more of the oil to be scraped from the walls and less of the oil to escape past the rings, for a recognized reduction in the emission of hydro-carbons from such diesel engines.
- These and other features and advantages of the present invention will become more readily appreciated when considered in connection with the following detailed description and appended drawings, wherein:
- FIG. 1 is a perspective view of a piston constructed according to a presently preferred embodiment of the invention;
- FIG. 2 is a cross-sectional view of the piston of FIG. 1 taken along lines2-2 of FIG. 1; and
- FIG. 3 is a cross-sectional view of the piston of FIG. 1 taken along lines3-3 of FIG. 1.
- FIGS.1-3 show a closed gallery monobloc piston generally at 10 constructed according to a presently preferred embodiment of the invention. The
piston 10 includes an upper head portion orpiston head 12 having an outer generallycylindrical ring belt 14 extending between an upper face orsurface 16 of thehead portion 12 and alower region 18 spaced from theupper face 16. Thering belt 14 is formed with a plurality ofpiston ring grooves outer surface 26 of thering belt 14. Theouter surface 26 has a predetermined diameter BD, designated as the bore diameter in FIGS. 2 and 3. As shown best in FIG. 3, the wall of thering belt 14 has a predetermined thickness or width, designated RBW, corresponding to the thickness of the ring belt wall inwardly from the base of thering grooves - The
head portion 12 is formed with acombustion bowl 28 machined into theupper face 16 of thehead portion 12 radially inwardly from thering belt 14 and presenting a contouredcombustion bowl wall 30. Thehead portion 12 has a predetermined top land height designated TLH, measured from the top of theupper ring groove 20 and theupper surface 16 as shown in FIG. 2. - The
piston 10 has an internal,annular oil gallery 32 having an outer wall defined in part by thering belt 14 and upper wall defined by thecombustion bowl wall 30. Theoil gallery 32 is further bound by an innerannular support wall 34 which is spaced radially inwardly from thering belt 14 and extends between thecombustion bowl wall 30 and a lower circumferentially extendingwall 36 which further extends between theinner support wall 34 andring belt 14 in spaced relation to thecombustion bowl wall 30 and closes off the bottom of theoil gallery 32. Theinner support wall 34 has a predetermined inner support wall width, designated ISW, and defines an inner support mean diameter, designated ISMD, of predetermined dimension as illustrated in FIG. 2. The top of theoil gallery 32 extends above the top of theupper ring groove 20 by a predetermined distance designated GRP in FIG. 3. Theoil gallery 32 has a predetermined gallery volume, designated GV in FIG. 3. - As shown best in FIG. 2, a pair of
pin bosses 38 extend downwardly from thehead portion 12 and haveinner faces 40 which are spaced axially from one another to define aspace 42 for receiving the upper end of a connecting rod therein. Thepin bosses 38 are formed with axially alignedpin bores 42 along a pin bore axis A. Thepin bores 44 receive a wrist pin (not shown) which couples thepiston 10 to the connecting rod (not shown). Thepiston 10 has predetermined compression height, designated CH in FIG. 2, measured between the pin bore axis A and thetop surface 16 of thehead portion 12. - The
piston 10 is formed with anintegral piston skirt 46. Theskirt 46 extends downwardly from thering belt 14 of thehead portion 12 and is coupled or unitized immovably to each of thepin bosses 38 on opposite sides of the piston. Thepiston skirt 46 extends between alower surface 48 and anupper surface 50. Theskirt 46 has a predetermined skirt length, designated SL measured between the lower andupper surfaces oil drainage groove 52 is machined into theouter surface 26 of thering belt 14 adjacent itslower region 18, separating theouter surface 26 of the ring belt from anouter surface 54 of theskirt 46 and defining theupper surface 50 of theskirt 46. Thegroove 52 does not extend through to thegallery 32 nor to the interior of theskirt 46 and is preferably aligned radially with thebottom wall 36 of thegallery 32. Abottom wall 53 of theoil groove 52 extends circumferentially about thepiston 10 between thepin bosses 38, but is interrupted across the region of thepin bosses 38, such that theoil groove 50 opens up to the recessed outerplanar faces 56 of thepin bosses 38 as illustrated in FIG. 2, permitting any oil gathered in theoil groove 52 to drain downwardly back into the crank case across the region of theouter faces 56. Anupper wall 55 of theoil drainage groove 52 is preferably continuous about the circumference of thepiston body 12. As shown in FIG. 3,piston rings ring grooves oil groove 52 is free of any piston rings. - The
space 42 between the pin bores is open to thecombustion bowl wall 30. Thus, there is aspace 64 below thecombustion bowl wall 30 and radially bound by theinner support wall 34 that is open to thespace 42 between the pin bores. Theoil gallery 32 is formed with one or more oil inlets, schematically shown at 66 in FIG. 3, that communicate with one or more corresponding oil jets (not shown) in operation of the piston for directing cooling oil into theoil gallery 32 to cool the surrounding walls of thegallery 32 with a known “cocktail-shaker” action of the oil as a result of the reciprocating movement of thepiston 10 in operation. Oil introduced to theoil gallery 32 is permitted to escape through one or more discharge ports, schematically shown at 68 in FIG. 3, into theinner space 64 for drainage back into the crank case (not shown). - To form the closed
oil gallery 32, thepiston 10 may be initially formed from two or more component parts machined with the oil gallery features which are subsequently joined to one another to form the closedgallery 32 in a subsequent joining operation. In the illustrated embodiment, thepiston 10 is formed from separate upper and lower crown parts which are joined preferably by friction welding acrossparting line 70, shown in FIG. 2. Of course, other forms of welding, brazing, or securing of the crown parts (e.g., bolting) are contemplated by the invention. - The
piston 10 is fabricated of steel and has the following dimensional relationships that enable the piston to operate successfully under high cylinder pressures in the vicinity of 300 bar. Of course, this is but one exemplary embodiment, and theoil drainage groove 52 could be used with other monobloc piston configurations that do not meet the following dimensional criteria: - ISMD=42-55% of BD
- ISW=3-8% of BD
- CH>53% of BD
- TLH>4% of BD
- GRP>0
- SL=30-80% of BD
- SW=2.5-6.5% of BD
- GV=150-250% of BD2 and 5-20% of BD2×CH
- Obviously, many modifications and variations of the present invention are possible in light of the above teachings. It is, therefore, to be understood that within the scope of the appended claims, the invention may be practiced otherwise than as specifically described. The invention is defined by the claims.
Claims (9)
Priority Applications (7)
Application Number | Priority Date | Filing Date | Title |
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US10/253,786 US6557514B1 (en) | 2001-10-23 | 2002-09-24 | Closed gallery monobloc piston having oil drainage groove |
JP2003538543A JP2005520082A (en) | 2001-10-23 | 2002-10-21 | Integrated casting piston with oil drain groove and closed passage |
AT02782187T ATE548539T1 (en) | 2001-10-23 | 2002-10-21 | ONE-PIECE CLOSED CHANNEL PISTON HAVING AN OIL DRAIN GROOVE |
EP02782187A EP1438493B1 (en) | 2001-10-23 | 2002-10-21 | Closed gallery monobloc piston having oil drainage groove |
CNB028236300A CN1296618C (en) | 2001-10-23 | 2002-10-21 | Closed gallery monobloc piston having oil drainage groove |
KR10-2004-7006117A KR20040058233A (en) | 2001-10-23 | 2002-10-21 | Closed gallery monobloc piston having oil drainage groove |
PCT/US2002/033493 WO2003036059A1 (en) | 2001-10-23 | 2002-10-21 | Closed gallery monobloc piston having oil drainage groove |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US35569301P | 2001-10-23 | 2001-10-23 | |
US10/253,786 US6557514B1 (en) | 2001-10-23 | 2002-09-24 | Closed gallery monobloc piston having oil drainage groove |
Publications (2)
Publication Number | Publication Date |
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US20030075137A1 true US20030075137A1 (en) | 2003-04-24 |
US6557514B1 US6557514B1 (en) | 2003-05-06 |
Family
ID=26943571
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/253,786 Expired - Lifetime US6557514B1 (en) | 2001-10-23 | 2002-09-24 | Closed gallery monobloc piston having oil drainage groove |
Country Status (7)
Country | Link |
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US (1) | US6557514B1 (en) |
EP (1) | EP1438493B1 (en) |
JP (1) | JP2005520082A (en) |
KR (1) | KR20040058233A (en) |
CN (1) | CN1296618C (en) |
AT (1) | ATE548539T1 (en) |
WO (1) | WO2003036059A1 (en) |
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DE102019216252A1 (en) | 2019-10-22 | 2021-04-22 | Mahle International Gmbh | Pistons for an internal combustion engine |
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US1953109A (en) * | 1931-11-07 | 1934-04-03 | Sam D Heron | Piston |
US3805677A (en) * | 1972-03-01 | 1974-04-23 | Trw Inc | Two-piece oil-cooled piston with thermal expansion control |
US4608947A (en) * | 1985-07-05 | 1986-09-02 | Klockner-Humboldt-Deutz Aktiengesellschaft | Arrangement for cooling pistons and cylinder sleeves |
JPH0415968Y2 (en) * | 1985-10-18 | 1992-04-09 | ||
JPH11351055A (en) * | 1998-06-11 | 1999-12-21 | Hino Motors Ltd | Engine piston |
US6152016A (en) * | 1999-01-29 | 2000-11-28 | Daimlerchrysler Corporation | Piston with cast passages |
JP2001050107A (en) * | 1999-08-10 | 2001-02-23 | Nissan Motor Co Ltd | Piston for internal combustion engine |
US20010025568A1 (en) * | 2000-03-28 | 2001-10-04 | Mahle Gmbh | One-piece piston |
-
2002
- 2002-09-24 US US10/253,786 patent/US6557514B1/en not_active Expired - Lifetime
- 2002-10-21 EP EP02782187A patent/EP1438493B1/en not_active Expired - Lifetime
- 2002-10-21 WO PCT/US2002/033493 patent/WO2003036059A1/en active Application Filing
- 2002-10-21 KR KR10-2004-7006117A patent/KR20040058233A/en not_active Application Discontinuation
- 2002-10-21 CN CNB028236300A patent/CN1296618C/en not_active Expired - Fee Related
- 2002-10-21 JP JP2003538543A patent/JP2005520082A/en active Pending
- 2002-10-21 AT AT02782187T patent/ATE548539T1/en active
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US6681485B2 (en) * | 2000-02-24 | 2004-01-27 | Volkswagen Ag | Method for casting a piston for a reciprocating internal combustion engine |
US20030009882A1 (en) * | 2000-02-24 | 2003-01-16 | Eduard Lippert | Method for production of a piston for a reciprocating internal combustion engine |
WO2006047601A2 (en) * | 2004-10-25 | 2006-05-04 | Industrial Parts Depot Inc. | One piece cast ferrous crown piston for internal combustion engine |
WO2006047601A3 (en) * | 2004-10-25 | 2006-07-20 | Ind Parts Depot Inc | One piece cast ferrous crown piston for internal combustion engine |
US20090217905A1 (en) * | 2005-01-05 | 2009-09-03 | Yamaha Hatsudoki Kabushiki Kaisha | Direct injection type of diesel engine |
US8695559B2 (en) * | 2007-09-24 | 2014-04-15 | Federal-Mogul Nurnberg Gmbh | Piston having oil supply channel for hub bore holes |
US20100307444A1 (en) * | 2007-09-24 | 2010-12-09 | Roland Bohm | Piston having oil supply channel for hub bore holes |
US20110036322A1 (en) * | 2009-08-12 | 2011-02-17 | Doosan Infracore Co., Ltd. | Piston for engine having stable behavior of piston ring |
US8353267B2 (en) * | 2009-08-12 | 2013-01-15 | Doosan Infracore Co., Ltd. | Piston for engine having stable behavior of piston ring |
CN103423015A (en) * | 2012-05-15 | 2013-12-04 | 安徽华菱汽车有限公司 | Internal combustion engine and piston thereof |
CN104718369A (en) * | 2012-09-18 | 2015-06-17 | 费德罗-莫格尔公司 | Steel piston with counter-bore design |
US9291120B2 (en) * | 2012-09-18 | 2016-03-22 | Federal-Mogul Corporation | Steel piston with counter-bore design |
US20160199952A1 (en) * | 2012-09-18 | 2016-07-14 | Federal-Mogul Corporation | Steel piston with counter-bore design |
US9677500B2 (en) * | 2012-09-18 | 2017-06-13 | Federal-Mogul Llc | Steel piston with counter-bore design |
US10247134B2 (en) | 2013-02-18 | 2019-04-02 | Tenneco Inc. | Complex-shaped forged piston oil galleries |
US10787991B2 (en) | 2013-02-18 | 2020-09-29 | Tenneco Inc. | Complex-shaped forged piston oil galleries |
CN105386891A (en) * | 2015-11-30 | 2016-03-09 | 柳州市恒达动力机械制造有限公司 | Suspension type inner-cooling gas engine piston |
Also Published As
Publication number | Publication date |
---|---|
EP1438493B1 (en) | 2012-03-07 |
KR20040058233A (en) | 2004-07-03 |
EP1438493A1 (en) | 2004-07-21 |
US6557514B1 (en) | 2003-05-06 |
CN1296618C (en) | 2007-01-24 |
EP1438493A4 (en) | 2010-04-21 |
ATE548539T1 (en) | 2012-03-15 |
JP2005520082A (en) | 2005-07-07 |
WO2003036059A1 (en) | 2003-05-01 |
CN1596335A (en) | 2005-03-16 |
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