WO2010075207A1 - Ensemble piston pourvu d'un passage s'étendant jusqu'à la seconde gorge de segment - Google Patents

Ensemble piston pourvu d'un passage s'étendant jusqu'à la seconde gorge de segment Download PDF

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Publication number
WO2010075207A1
WO2010075207A1 PCT/US2009/068705 US2009068705W WO2010075207A1 WO 2010075207 A1 WO2010075207 A1 WO 2010075207A1 US 2009068705 W US2009068705 W US 2009068705W WO 2010075207 A1 WO2010075207 A1 WO 2010075207A1
Authority
WO
WIPO (PCT)
Prior art keywords
ring groove
piston
ring
passage
land
Prior art date
Application number
PCT/US2009/068705
Other languages
English (en)
Inventor
Mark W. Jarrett
Craig P. Hittle
Cletus M. Kinsey, Jr.
Original Assignee
Caterpillar Inc.
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 Caterpillar Inc. filed Critical Caterpillar Inc.
Priority to DE112009004401T priority Critical patent/DE112009004401T5/de
Priority to JP2011542479A priority patent/JP2012513571A/ja
Publication of WO2010075207A1 publication Critical patent/WO2010075207A1/fr

Links

Classifications

    • 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
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details
    • F16J9/20—Rings with special cross-section; Oil-scraping rings
    • 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
    • F16J1/09—Pistons; Trunk pistons; Plungers with means for guiding fluids
    • 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
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/12—Details
    • F16J9/22—Rings for preventing wear of grooves or like seatings
    • 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
    • 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 
    • F02F3/0015—Multi-part pistons
    • F02F3/003—Multi-part pistons the parts being connected by casting, brazing, welding or clamping

Definitions

  • the present disclosure is directed to a piston assembly, and more particularly, to a piston assembly for an internal combustion engine.
  • Reciprocating, internal combustion engines generally utilize piston assemblies that reciprocate within a cylinder to convert the energy released during the combustion process into useful rotational energy.
  • piston assemblies generally cooperate with the cylinder liner (or cylinder in the engine block) and head to form a combustion chamber that is capable of changing its volume.
  • the energy released during the combustion process creates significant pressure within the combustion chamber, which forces the piston assembly to move within the cylinder.
  • the piston assembly is coupled to a crankshaft in such a way that the linear movement of the piston assembly is converted into the rotational movement of the crankshaft.
  • the piston assembly also forces the crankshaft to rotate.
  • piston assemblies In order to reduce the amount of pressurized gas and lubricant that is able to leak or move past the piston assembly, many modern piston assemblies include a set of piston rings. Although the number and configurations of the piston rings may vary, one common configuration is to have three piston rings - a top piston ring, an intermediate piston ring, and a lower piston ring.
  • the primary purpose of the top piston ring is to minimize the leakage of combustion gases past the piston assembly.
  • the primary purpose of the lower piston ring is to scrap off excess oil that may be provided on the cylinder wall.
  • the intermediate piston ring normally serves to backup the top piston ring by providing an additional gas seal, and to backup the lower piston ring by scraping off any remaining oil film on the cylinder wall.
  • the piston rings work together to accomplish the desired sealing action. If one ring does not function properly, then the appropriate sealing action will most likely not be achieved.
  • each of the three piston rings may be exposed to different pressures, different portions of a particular piston ring may be exposed to different pressures, and each piston ring may move to different locations within its respective ring groove, both axially and radially. These pressures and locations will be dependent on, among other possible factors, where the piston assembly is within the four-stroke cycle, the acceleration or deceleration of the piston assembly, combustion pressures, and the level of friction between the piston ring and the cylinder wall.
  • the intermediate piston ring may experience a situation where it is pressed against the top of its ring groove (which creates a situation where the face of the intermediate piston ring is exposed to the pressure between the top piston ring and the intermediate piston ring and the back side (or the radially inner side) of the intermediate piston ring is exposed to the pressure between the lower piston ring and the intermediate piston ring)) and the pressure differential between the face of the ring and the back side of the ring is enough to cause the intermediate piston ring to "collapse" or essentially move away from the cylinder wall.
  • the intermediate piston ring is not able to perform its oil scraping function, which may allow oil to pass by the intermediate piston ring and be consumed during the combustion process. This not only leads to the consumption of oil, but also tends to increase unwanted engine emissions.
  • the disclosed piston assembly is directed to overcoming one or more of the problems set forth above or other problems.
  • the cylindrical wall extends away from the top surface and includes a first ring groove, a second ring groove, a third ring groove, a first land, a second land, and a third land.
  • the first ring groove is configured to receive a first ring.
  • the second ring groove is configured to receive a second ring.
  • the third ring groove is configured to receive a third ring.
  • the first land is between the top surface and the first ring groove.
  • the second land is between the first ring groove and the second ring groove.
  • the third land is between the second ring groove and the third ring groove.
  • the at least one passage extends between the second land and the second ring groove.
  • the at least one passage is configured to fluidly couple the second ring groove to a volume surrounding the second land.
  • the cylindrical wall extends from the top surface and includes a first ring groove, a second ring groove, and a first land between the first ring groove and the second ring groove.
  • the first ring is received within the first ring groove.
  • the second ring is received within the second ring groove.
  • the second ring includes an outer surface configured to engage the cylinder and an inner surface opposite the outer surface.
  • the at least one passage fluidly couples a first volume to which the outer surface is exposed to a second volume to which the inner surface is exposed.
  • an internal combustion engine comprises a block, a cylinder head, a crankshaft, and a piston assembly.
  • the block includes at least one cylindrical bore having a first end and a second end.
  • the cylinder head is coupled to the block and substantially encloses the first end of the cylindrical bore.
  • the crankshaft is rotatably received within the block.
  • the piston assembly is received within the cylindrical bore and is configured to reciprocate within the cylindrical bore.
  • the piston assembly is coupled to the crankshaft and is configured to rotate the crankshaft as the piston reciprocates within the cylindrical bore.
  • the piston assembly includes a top surface, a cylindrical wall, a first compression ring, a second compression ring, and an oil ring assembly.
  • the cylindrical wall extends away from the top surface and includes a first ring groove, a second ring groove, a third ring groove, a first land between the first ring groove and the second ring groove, and at least one passage extending between the first land and the second ring groove.
  • the first compression ring is received within the first ring groove.
  • the second compression ring is received within the second ring groove.
  • the oil ring assembly is received within the third ring groove.
  • the at least one passage is conf ⁇ gured to fluidly couple the second ring groove to the volume surrounding the first land.
  • Figure 1 is a partial cross-sectional view of an engine according to one exemplary embodiment.
  • Figure 2 is a partial cross-sectional view of a piston assembly according to one exemplary embodiment.
  • Figure 3 is a partial cross-sectional view of a piston assembly according to another exemplary embodiment.
  • Figure 4 is a partial perspective view of the piston assembly of
  • Figure 5 is a partial cross-sectional view of a piston assembly according to another exemplary embodiment.
  • Engine 10 is a device that converts chemical energy (from a fuel such as diesel fuel, biodiesel, gasoline, etc.) into rotational mechanical energy and that may be used as a power source in a multitude of different applications, such as in vehicles, locomotives, machines, etc.
  • engine 10 includes a block 12, a head assembly 16, a piston assembly 18, a connecting rod 20, and a crankshaft 22.
  • Block 12 is a generally rigid structure or housing that is configured to receive and support head assembly 16, piston assembly 18, connecting rod 20, and crankshaft 22.
  • block 12 defines a generally cylindrical chamber 24 that receives crankshaft 22 and one or more cylindrical bores 26 that extend radially outward from chamber 24.
  • Each of cylindrical bores 26 may be configured to receive a piston assembly 18 directly, or to receive a cylinder liner 28, which in turn is configured to directly receive a piston assembly 18.
  • Each cylinder liner 28 is a generally tubular member that is received within a cylindrical bore 26 and that defines a piston bore 34 along which a piston assembly 18 reciprocates.
  • Block 12 also defines a generally flat face 30 located at the distal end of each cylindrical bore 26 that is configured to facilitate the coupling of head assembly 16 to block 12.
  • Head assembly 16 is an assembly of components that cooperates with cylinder liners 28, block 12, and piston assemblies 18 to define substantially enclosed combustion chambers 32 and that includes the mechanisms that control the flow of air and other gases into and out of combustion chambers 32 as well as the injection of fuel into the combustion chambers 32.
  • head assembly 16 includes a housing 35 that forms the general structure of head assembly 16 and that is configured to receive and support the other components of head assembly 16.
  • Housing 35 includes a lower face that mates against flat face 30 of block 12 to form a generally sealed interface between head assembly 16 and block 12. When coupled to block 12, housing 35 serves to cover or enclose each of piston bores 34.
  • Housing 35 also includes intake ports 36 that direct air into combustion chambers 32, exhaust ports 40 that direct exhaust out of combustion chambers 32, and bores 44 (normally one per combustion chamber 32) that are each configured to receive a fuel injector 46 that injects fuel into the corresponding combustion chamber 32.
  • Head assembly 16 also includes intake valves 34 that correspond to intake ports 36 and that serve to control the flow of air into each combustion chamber 32, and exhaust valves 42 that correspond to exhaust ports 40 and that serve to control the flow of exhaust out of each combustion chamber 32.
  • the head assembly may take one of a variety of different configurations, may include other various components such as various mechanisms to control the actuation of intake valves 38 and exhaust valves 42 (e.g., cams, rocker arms, engine brakes, variable valve actuation systems, etc.), the housing of the head assembly may be provide in one or more individual pieces coupled together, or the head assembly may take one of a variety of other embodiments that are known in the art.
  • Piston assemblies 18, described in more detail below, are received within piston bores 34 (with one piston assembly 18 in each piston bore 34) and generally serve to cooperate with cylinder liners 28 and head assembly 16 to form combustion chambers 32.
  • Each piston assembly 18 is configured to reciprocate within the corresponding piston bore 34 as it completes each engine cycle (e.g, a four-stroke engine cycle or a 2-stroke engine cycle) and continues to repeat the engine cycle for as long as engine 10 operates.
  • Connecting rod or piston rod 20 is a rigid rod or member that couples piston assembly 18 to crankshaft 22.
  • Crankshaft 22 is a shaft that rotates around an axis and that provides the rotational power output of engine 10.
  • Crankshaft 22 includes radially offset "crank pins" to which one end of connecting rods 20 are coupled. As each piston assembly 18 reciprocates within piston bore 34 in a linear fashion, the corresponding connecting rod 20 causes crankshaft 22 to rotate.
  • piston assembly 18 is a rigid device that slides along, or moves within, piston bore 34 of cylinder liner 28 to enable the volume of combustion chamber 32 to change.
  • piston assembly 18 includes a piston 50, a set of piston rings 52, and a pin 54.
  • piston 50 is an articulated piston assembly and includes a head or crown 56 and a skirt 58.
  • head 56 is a generally cylindrical member having a top surface 60, a bowl 62, a cylindrical sidewall or skirt 64, a cooling gallery 66, and pin bosses 68.
  • Top surface 60 is a substantially flat, annular region located in a plane that is perpendicular to the axis of cylinder liner 28.
  • Bowl 62 is a recessed region that extends into the plane defined by top surface 60 and is intended to improve combustion efficiency.
  • bowl 62 may take one of a variety of different shapes and sizes depending on the particular characteristics affecting combustion (e.g., injection pressure, injection spray angle, cylinder diameter, etc.).
  • Sidewall 64 extends perpendicularly from the outer edge of top surface 60.
  • sidewall 64 includes, starting at top surface 60 and moving away, a first or top land 70, a first or top ring groove 72, a second or upper intermediate land 74, a second or intermediate ring groove 76, a third or lower intermediate land 78, a third or bottom ring groove 80, and a fourth or bottom land 82.
  • Top ring groove 72 is a generally wedge-shaped or keystone-shaped annular recess that extends radially inwardly into sidewall 64 and is configured to receive one of the piston rings in set 52.
  • Intermediate ring groove 76 is a generally rectangular-shaped annular recess that extends radially inwardly into sidewall 64 and is configured to receive another one of the piston rings in set 52.
  • Intermediate ring groove 76 is defined by two substantially parallel sides 84 and 86 that are substantially parallel to top surface 60 and an inner side 88 that extends between sides 84 and 86.
  • Bottom ring groove 80 is a generally rectangular-shaped annular recess that extends radially inwardly into sidewall 64 and is configured to receive yet another one of the piston rings in set 52.
  • each of ring grooves 72, 76, and 80 may take one of a variety of different configurations suitable for the engine in which they are used.
  • Cooling recess 66 is a cavity or chamber that is configured to receive a cooling fluid, such as engine oil, to facilitate the transfer of heat away from piston assembly 18.
  • cooling recess 66 is defined by an annular recess that extends axially into a bottom surface 90 of head 56. Cooling recess 66 is configured such that it is spaced radially inwardly from sidewall 64 of head 56 and axially below bowl 62.
  • Pin bosses 68 are projections or structures that facilitate the coupling of head 56 to pin 54 and skirt 58. According to one exemplary embodiment, two pin bosses 68 extend downwardly from bottom surface 90 of head 54 and are spaced apart such that a portion of connecting rod 20 may be received between them. Each pin boss 68 includes a bore that is configured to receive pin 54.
  • skirt 58 is a generally tubular member that is coupled to head 56 via pin 54.
  • Skirt 58 includes a bore that extends through skirt 58 in a radial direction. When skirt 58 is assembled to head 56, the bore of skirt 58 is aligned with the bores in pin bosses 68 of head 56 and pin 54 is inserted through all the bores. In this way, pin 54 serves to couple skirt 58 and head 56 together.
  • Set of piston rings 52 refers to the piston rings that are received within ring grooves 72, 76, and 80 of piston 50.
  • set of piston rings 52 includes a first compression ring 92 configured to be placed within top ring groove 72, a second compression ring 94 configured to be placed within intermediate ring groove 76, and an oil ring assembly 96 configured to be placed within bottom ring groove 80.
  • First compression ring 92 and second compression ring 94 generally serve to reduce, minimize, or substantially eliminate the passage of combustion gases and unburned fuel past piston assembly 18 and into the crankcase (a phenomenon known as "blow-by").
  • Pin 54 also known as a wrist pin or gudgeon pin, is a rigid pin that is configured to extend through the bores in skirt 58, the bores in pin bosses 68 of head 56, and a bore in one end of connecting rod 20 to couple skirt 58 and head 56 together and to coupled piston assembly 18 to connecting rod 20.
  • the pin may take any one of a variety of different configurations, such as one of those configurations currently known in the art.
  • the passage is formed by a cylindrical bore 108 that extends diagonally from second land 74 to a portion of side 84 of ring groove 76 that forms a border of cavity 99.
  • the diameter of bore 108 may be equal to or greater than about 0.5 millimeters. In another embodiment, the diameter of bore 108 may be equal to or greater than about 0.75 millimeters. In another embodiment, the diameter of bore 108 may be equal to or greater than about 1 millimeter. In another embodiment, the diameter of bore 108 may be equal to or greater than about 2.5 millimeters. In a further embodiment, the diameter of bore 108 may be in the range of about 0.5 to 1.0 millimeters, for example about 0.75 millimeters.
  • the total area of the passages provided within piston 50 will depend on the shape and configuration of each passage and on the total number of passages provided. In one embodiment, the total area may be equal to or greater than about 0.2 mm 2 . In another embodiment, the total area may be equal to or greater than about 0.44 mm 2 . In another embodiment, the total area may be equal to or greater than about 0.79 mm 2 . In another embodiment, the total area may be equal to or greater than about 4.91 mm 2' In a further embodiment, the total area may be in the range of about 0.2 mm 2 to about 0.79, for example about 0.44 mm 2 . According to another alternative embodiment illustrated in Figure
  • the passage may be in the form of a notch 112 provided in axially upwardly facing surface 104 of second compression ring 94 rather than in piston 50.
  • second compression ring 94 may include just one notch 112 or it may include multiple notches 112 spaced apart around the circumference of second compression ring 94.
  • each notch may take any one of a variety of different configurations.
  • the notch may be a recess, groove, detent, or any one of a variety of other configurations, and may take the shape of a partial cylinder, sphere, rectangle, or other shapes, or it may be V-shaped, or any other suitable shape or configuration.
  • the notch may be formed in second compression ring 94 using any suitable manufacturing process, including drilling, milling, boring, laser drilling, or other suitable processes or techniques.
  • the passage coupling cavities 98 and 99 may also be provided in a single piece piston or in other piston configurations.
  • the passage coupling cavities 98 and 99 may be used in connection with pistons for gasoline engines or other types of internal combustion engines (e.g., gaseous fuel engines, etc.)
  • piston assembly 18 will travel through an expansion or power stroke, an exhaust stroke, an intake stroke, and a compression stroke.
  • first compression ring 92, second compression ring 94, and oil ring assembly 96 may move within first ring groove 72, second ring groove 76, and third ring groove 80, respectively.
  • second compression ring 94 may move within second ring groove 76.
  • third ring groove 80 There are at least three factors that affect the movement of second compression ring 94 within second ring groove 76. These three factors include the friction between second compression ring 94 and piston bore 34, the acceleration or deceleration of piston assembly 18, and the different pressures of the gases acting upon second compression ring 94.
  • piston assembly 18 will start at a bottom dead center position, and move to a top dead center position. The movement of piston assembly 18 from the bottom dead center position to the top dead center position will take place over 180 degrees of rotation of crankshaft 22. Over this 180 degrees, piston assembly 18 will accelerate for roughly about the first 110 degrees, and will then decelerate the remaining 70 degrees until piston assembly 18 reaches to the top dead center position.
  • the precise location where deceleration begins will depend on the length of connecting rod 20 and the stroke of crankshaft 22, and may vary with different engine configurations. However, for many engine configurations, this location will be roughly 70 degrees before the top dead center position.
  • piston assembly 18 As piston assembly 18 moves from the bottom dead center position to the top dead center position, it will be causing the volume of combustion chamber 32 to decrease. Because intake valves 38 and exhaust valves 42 are generally closed during the compression stroke, the volume reduction caused by piston assembly 18 will cause the pressure within combustion chamber 32 to increase. Some of this pressure is likely to leak past first compression ring 92 and act upon second compression ring 94.
  • second compression ring 94 is still pressed against side 84 (the upper side) of second ring groove 76, a pressure differential may be created between radially outwardly facing surface 100, which is exposed to the pressure in cavity 98 above second compression ring 94, and radially inwardly facing surface 102 of second compression ring 94, which is exposed to the pressure in cavity 99 (which is generally equal to the pressure in a cavity 114 below second compression ring 94). In some situations, this pressure differential is believed to cause second compression ring 94 to collapse (or move away from piston bore 34). When second compression ring 94 collapses during the power stroke, second compression ring 94 is no longer able to perform the function of scraping oil off of piston bore 34.
  • piston assembly 18 More oil is therefore allowed to remain on piston bore 34, and as piston assembly 18 continues to move downward, that remaining oil is burned as part of the combustion process.
  • the burning of the oil not only consumes the oil, but it may also have the effect of increasing certain unwanted exhaust gas constituents, making it more difficult to meet the increasingly stringent emissions regulations. It is believed that the addition of the passages (e.g., bore 108, notch 110, or notch 112) to piston assembly 18 and/or second compression ring 94 may help to reduce or eliminate the collapse of second compression ring 94.
  • the passages are believed to accomplish this by reducing the magnitude of, or eliminating, the pressure differential between radially outwardly facing surface 100 and radially inwardly facing surface 102 of second compression ring 94 by fluidly coupling cavity 98, the pressure within which acts upon radially outwardly facing surface 100, and cavity 99, the pressure within which acts upon radially inwardly facing surface 102.
  • the pressures acting on the opposing faces of second compression ring 94 are equal, or closer to being equal, the collapse of second compression ring 94 is less likely.
  • elements shown as integrally formed may be constructed of multiple parts or elements shown as multiple parts may be integrally formed, the operation of the interfaces may be reversed or otherwise varied, and/or the length, width, or other dimensions of the structures and/or members or connectors or other elements of the system may be varied.
  • the elements and/or assemblies of the piston assembly may be constructed from any of a wide variety of materials that provide sufficient strength or durability, and in any of a wide variety of textures and combinations.
  • the piston assembly may be used in association with any of a wide variety of engines in any of a wide variety of applications. Accordingly, all such modifications are intended to be included within the scope of the present disclosure. Other substitutions, modifications, changes and omissions may be made in the design, operating conditions and arrangement of the exemplary and other alternative embodiments without departing from the spirit of the present disclosure.

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

Abstract

L'invention porte sur un ensemble piston configuré pour effectuer un mouvement de va-et-vient à l'intérieur d'un cylindre d'un moteur à combustion interne. L'ensemble piston comprend une surface supérieure, une paroi cylindrique, un premier segment, un second segment et au moins un passage. La paroi cylindrique s'étend à partir de la surface supérieure et comprend une première gorge de segment, une seconde gorge de segment et une première couronne entre la première gorge de segment et la seconde gorge de segment. Le premier segment est reçu dans la première gorge de segment. Le second segment est reçu dans la seconde gorge de segment. Le second segment comprend une surface externe configurée pour venir en contact avec le cylindre et une surface interne opposée à la surface externe. Le ou les passages couplent de manière fluide un premier volume auquel la surface externe est exposée à un second volume auquel la surface interne est exposée.
PCT/US2009/068705 2008-12-22 2009-12-18 Ensemble piston pourvu d'un passage s'étendant jusqu'à la seconde gorge de segment WO2010075207A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE112009004401T DE112009004401T5 (de) 2008-12-22 2009-12-18 Kolbenanordnung mit einer Passage, die sich zu der zweiten Ringnut erstreckt
JP2011542479A JP2012513571A (ja) 2008-12-22 2009-12-18 第２のリング溝に延在する通路を有するピストンアセンブリ

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US13968208P 2008-12-22 2008-12-22
US61/139,682 2008-12-22

Publications (1)

Publication Number Publication Date
WO2010075207A1 true WO2010075207A1 (fr) 2010-07-01

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ID=42288097

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PCT/US2009/068705 WO2010075207A1 (fr) 2008-12-22 2009-12-18 Ensemble piston pourvu d'un passage s'étendant jusqu'à la seconde gorge de segment

Country Status (3)

Country Link
JP (1) JP2012513571A (fr)
DE (1) DE112009004401T5 (fr)
WO (1) WO2010075207A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9091349B2 (en) 2012-07-10 2015-07-28 Hrst, Inc. Self-energizing seal
WO2022208526A1 (fr) * 2021-03-31 2022-10-06 Tvs Motor Company Limited Moteur à combustion interne
WO2024084184A1 (fr) * 2022-10-21 2024-04-25 Cross Manufacturing Company (1938) Limited Ensemble joint d'étanchéité à bague coulissante

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3190273A (en) * 1964-01-03 1965-06-22 Continental Aviat & Eng Corp Piston for internal combustion engine
US5040454A (en) * 1988-10-21 1991-08-20 Caterpillar Inc. Piston assembly and piston member thereof having a predetermined compression height to diameter ratio
US5251915A (en) * 1990-02-12 1993-10-12 General Motors Corporation Piston and ring assembly
US5261362A (en) * 1992-11-30 1993-11-16 Chrysler Corporation Piston assembly having multiple piece compression ring
US6463903B1 (en) * 2001-08-30 2002-10-15 Caterpillar Inc Piston assembly for free piston internal combustion engine

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS60194147U (ja) * 1984-06-05 1985-12-24 トヨタ自動車株式会社 ピストン
JPH0365839U (fr) * 1989-10-30 1991-06-26
JPH11201283A (ja) * 1998-01-16 1999-07-27 Mitsubishi Heavy Ind Ltd ピストン及びピストンリング

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3190273A (en) * 1964-01-03 1965-06-22 Continental Aviat & Eng Corp Piston for internal combustion engine
US5040454A (en) * 1988-10-21 1991-08-20 Caterpillar Inc. Piston assembly and piston member thereof having a predetermined compression height to diameter ratio
US5251915A (en) * 1990-02-12 1993-10-12 General Motors Corporation Piston and ring assembly
US5261362A (en) * 1992-11-30 1993-11-16 Chrysler Corporation Piston assembly having multiple piece compression ring
US6463903B1 (en) * 2001-08-30 2002-10-15 Caterpillar Inc Piston assembly for free piston internal combustion engine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9091349B2 (en) 2012-07-10 2015-07-28 Hrst, Inc. Self-energizing seal
WO2022208526A1 (fr) * 2021-03-31 2022-10-06 Tvs Motor Company Limited Moteur à combustion interne
WO2024084184A1 (fr) * 2022-10-21 2024-04-25 Cross Manufacturing Company (1938) Limited Ensemble joint d'étanchéité à bague coulissante

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Publication number Publication date
DE112009004401T5 (de) 2012-08-16
JP2012513571A (ja) 2012-06-14

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