US20050028767A1 - Hydraulic engine valve actuator - Google Patents
Hydraulic engine valve actuator Download PDFInfo
- Publication number
- US20050028767A1 US20050028767A1 US10/635,095 US63509503A US2005028767A1 US 20050028767 A1 US20050028767 A1 US 20050028767A1 US 63509503 A US63509503 A US 63509503A US 2005028767 A1 US2005028767 A1 US 2005028767A1
- Authority
- US
- United States
- Prior art keywords
- piston
- cylinder
- housing
- liner
- drive piston
- 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.)
- Granted
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L2800/00—Methods of operation using a variable valve timing mechanism
- F01L2800/17—Maintenance; Servicing
Definitions
- This invention relates to engine valve actuating apparatus and more particularly to a hydraulic engine valve actuator integrated in a separate housing assembly.
- Piston type internal combustion engines generally utilize mechanically driven camshafts and valve gear for operation of intake and exhaust valves.
- Electric and hydraulic valve actuators have also been proposed in order to provide improved control of valve actuation and timing.
- a hydraulic valve system may comprise a hydraulic pump, a controller, a hydraulic fluid manifold, and one or more pistons reciprocable in a hydraulic cylinder provided in the hydraulic fluid manifold.
- the manifold delivers hydraulic fluid to the hydraulic cylinder to reciprocate the pistons and actuate an associated intake or exhaust valve.
- a position sensor may also be mounted to the manifold to feed back the valve position to the controller.
- the present invention provides an integrated hydraulic valve actuator for an internal combustion engine.
- the valve actuator includes a separate bolt-on housing which contains hydraulic pistons and other tiny and difficult to manipulate parts to aid in the assembly, disassembly and service of the actuator. Additionally, the housing can accommodate a variety of interchangeable parts for use in different engine applications.
- a hydraulic supply manifold is machined to accommodate a plurality of integrated hydraulic valve actuators.
- Each actuator includes a housing mountable to the hydraulic supply manifold and internally defining a through opening formed as a stepped bore.
- a cylindrical liner is fitted into the bore at one end of the housing.
- An internal cylinder of the liner provides a riding surface, which coaxially surrounds an outer surface of a tubular boost piston.
- the boost piston defines an inner cylinder, which provides a riding surface for a drive piston fitted within the inner cylinder of the boost piston.
- the boost piston and drive piston are axially reciprocable within the liner.
- a piston position sensor extends radially into the housing and engages a cam on the drive piston to relay the position of the drive piston to a controller.
- valve actuator is preassembled and the housing is attached to the hydraulic supply manifold by inserting a portion of the housing into a recess provided in the manifold and fastening the housing to the manifold.
- the drive piston engages an intake or exhaust valve and the internal cylinder of the liner is positioned to receive hydraulic oil from an associated oil distributor valve in the supply manifold.
- oil is directed to the oil distributor valves, which sequentially distribute pressure oil to the associated valve actuators from the supply manifold. Pressure oil distributed to each valve actuator forces the respective boost piston and the drive piston axially downward in the housing and partially opens the associated engine valve. Part way through the piston stroke, the boost piston engages a stop, while the drive piston continues to move axially downward for a greater distance. The continued motion of the drive piston completes opening of the engine valve. Subsequently, the oil distributor valve reduces the oil pressure in the housing and a valve spring returns the valve to its closed position, thereby moving the drive piston and boost piston back to their original positions against the liner.
- valve actuator may be removed from the supply manifold for service or replacement to maintain optimal valve performance.
- FIG. 1 is a cross-sectioned view of a camless internal combustion engine utilizing integrated hydraulic valve actuators of the invention
- FIG. 2 is an exploded view of a valve actuator assembly according to the present invention
- FIG. 3 is a cross-sectional view of a hydraulic valve system with the interior of one actuator.
- FIG. 4 is a cross-sectional view of the system of FIG. 3 seen from an opposite direction with the exterior of the actuator.
- FIG. 1 of the drawings generally indicates a camless internal combustion engine.
- Engine 10 has a plurality of pistons 12 , reciprocable within engine cylinders 14 .
- Each cylinder 14 has associated intake and exhaust valves 16 , 18 .
- the valves 16 , 18 are hydraulically actuated by valve actuators 20 ( FIG. 2 ) fixed to hydraulic supply manifolds 22 mounted on cylinder heads 24 and closing upper ends of the cylinders 14 .
- the actuators 20 are controlled by oil distributor valves 26 ( FIGS. 3,4 ) which are activated by a controller 27 to deliver pressure oil to or cut off pressure oil from the valve actuators 20 .
- the valves 16 , 18 are opened by hydraulic actuator pistons, not shown, and are closed by valve springs 28 conventionally mounted on the cylinder heads 24 .
- each actuator 20 includes a cylindrical housing 30 which may be formed of metal.
- the housing 30 carries an external seal ring 32 and internally defines a through opening formed as a stepped bore 34 .
- Bore 34 includes a major diameter 36 extending from an upper portion 38 of the housing to an intermediate diameter 40 near a midportion 42 of the housing 30 .
- a minor diameter 44 extends from the intermediate diameter 40 to a bottom end 46 of the housing.
- the major diameter 36 is sized to receive-a cylindrical liner 48 carrying an external seal ring 49 .
- the liner 48 may be formed of various metals depending upon the application.
- the liner 48 internally defines a cylinder 50 which acts as a riding surface for an outer diameter 54 of a piston subassembly 56 .
- the diameter of cylinder 50 may be varied to match the outer diameter 54 of the piston subassembly 56 , which reciprocates in cylinder 50 .
- a lower end 57 of the liner 48 also provides an upper stop for the piston subassembly 56 .
- the piston subassembly 56 comprises the hydraulic actuator pistons, including a tubular boost piston 58 coaxially surrounding a drive piston 60 .
- the boost piston 58 defines an inner riding surface 62 for the drive piston 60 .
- a lower flange 63 of the boost piston is engagable with the stop formed on the lower end 57 of the liner 48 to limit upward travel of the piston subassembly 56 .
- the drive piston 60 has an upper portion 64 received within the riding surface 62 of the boost piston 58 and a tapered lower end or cam 66 extending from upper portion 64 .
- the lower end 66 of the drive piston 60 is engagable with the lower flange 63 of the boost piston 58 to limit upward travel of the drive piston.
- the intermediate diameter 40 of the stepped bore is smaller than the exterior of the cylindrical liner 48 to provide an abutment for the cylindrical liner.
- the intermediate diameter 40 also defines the axial motion or stroke of the boost piston 58 with the piston subassembly 56 .
- the minor diameter 44 of the stepped bore 34 has a smaller diameter than the boost piston 58 , to provide an abutment which stops downward motion of the boost piston 58 at a predetermined point.
- the minor diameter 44 is larger than the lower end 66 of the drive piston 60 to allow axial motion of the piston in the minor diameter 44 .
- a drive piston position sensor 68 extends radially into the housing 30 near the bottom end 46 .
- the position sensor 68 engages the tapered lower end 66 of the drive piston 60 so that, as the drive piston reciprocates within the housing 30 , the position of the drive piston is related to the position of the sensor.
- each supply manifold 22 has bores 70 for receiving the upper portions 38 of the associated valve actuators 20 .
- the external seal ring 32 carried on each valve actuator housing may be an o-ring provided to seal the associated bore 70 against the leakage of oil.
- the similar seal 49 is provided on each liner 48 to seal the major diameter 36 of the housing stepped bore against leakage of oil through the bore.
- oil is directed to the oil distributor valves 26 , which sequentially communicate oil pressure to each valve actuator 20 from the associated hydraulic supply manifold 22 .
- the oil flows into the valve actuator 20 through the internal cylinder 50 of the liner 48 .
- the oil pressure acts against the piston subassembly 56 to force it axially downward within the housing 30 , thereby opening the associated intake or exhaust valve 16 , 18 against the resistance of the valve spring 28 .
- the boost piston 58 is stopped by the abutment formed by the minor diameter bore 44 . Thereafter, the drive piston continues to move axially downward, at a slower rate, until the associated intake or exhaust valve 16 , is fully opened by the force of oil pressure on the smaller drive piston alone. At the desired interval, the oil distributor valve 26 is actuated to reduce the oil pressure to the valve actuator 20 , allowing the valve spring 28 to return piston subassembly 56 and the valve 16 or 18 to the closed position.
- the position sensor 68 relays the position of the drive piston 60 to controller 27 . Based upon the position of the drive piston 60 relative to the piston position sensor 68 , the controller 27 determines the proper amount of oil pressure required from the oil distributor valve 26 to properly actuate the valve 16 .
- a valve actuator 20 may be removed from its hydraulic supply manifold for service or replacement. Servicing of the valve actuator 20 is accomplished by removing the liner 48 and piston subassembly 56 from the housing 30 . If the liner 48 becomes worn over time, it may be replaced with a new liner. If needed, the piston subassembly 56 may also be replaced. If desired the liner 48 may be replaced with a liner having a larger diameter opening to accommodate a piston subassembly having a larger diameter than the original piston subassembly 56 . After the valve actuator 20 is reassembled with new parts, the valve actuator may be reinstalled to the supply manifold 22 and reused.
Abstract
Description
- This invention relates to engine valve actuating apparatus and more particularly to a hydraulic engine valve actuator integrated in a separate housing assembly.
- Piston type internal combustion engines generally utilize mechanically driven camshafts and valve gear for operation of intake and exhaust valves. Electric and hydraulic valve actuators have also been proposed in order to provide improved control of valve actuation and timing.
- A hydraulic valve system may comprise a hydraulic pump, a controller, a hydraulic fluid manifold, and one or more pistons reciprocable in a hydraulic cylinder provided in the hydraulic fluid manifold. The manifold delivers hydraulic fluid to the hydraulic cylinder to reciprocate the pistons and actuate an associated intake or exhaust valve. A position sensor may also be mounted to the manifold to feed back the valve position to the controller.
- Mounting of the hydraulic cylinder and pistons and the position sensor in the manifold increases its complexity and complicates assembly, disassembly and serviceability of the assembly. Modification of the hydraulic components is also complicated by the expense of changes required in design and manufacture of the manifold. A more cost effective and serviceable hydraulic valve actuator for engine valves was desired.
- The present invention provides an integrated hydraulic valve actuator for an internal combustion engine. The valve actuator includes a separate bolt-on housing which contains hydraulic pistons and other tiny and difficult to manipulate parts to aid in the assembly, disassembly and service of the actuator. Additionally, the housing can accommodate a variety of interchangeable parts for use in different engine applications.
- To utilize the present invention, a hydraulic supply manifold is machined to accommodate a plurality of integrated hydraulic valve actuators. Each actuator includes a housing mountable to the hydraulic supply manifold and internally defining a through opening formed as a stepped bore. A cylindrical liner is fitted into the bore at one end of the housing. An internal cylinder of the liner provides a riding surface, which coaxially surrounds an outer surface of a tubular boost piston.
- The boost piston defines an inner cylinder, which provides a riding surface for a drive piston fitted within the inner cylinder of the boost piston. The boost piston and drive piston are axially reciprocable within the liner. A piston position sensor extends radially into the housing and engages a cam on the drive piston to relay the position of the drive piston to a controller.
- In a preferred embodiment, the valve actuator is preassembled and the housing is attached to the hydraulic supply manifold by inserting a portion of the housing into a recess provided in the manifold and fastening the housing to the manifold. Upon subsequent assembly of the hydraulic manifold to an engine cylinder head, the drive piston engages an intake or exhaust valve and the internal cylinder of the liner is positioned to receive hydraulic oil from an associated oil distributor valve in the supply manifold.
- In operation, oil is directed to the oil distributor valves, which sequentially distribute pressure oil to the associated valve actuators from the supply manifold. Pressure oil distributed to each valve actuator forces the respective boost piston and the drive piston axially downward in the housing and partially opens the associated engine valve. Part way through the piston stroke, the boost piston engages a stop, while the drive piston continues to move axially downward for a greater distance. The continued motion of the drive piston completes opening of the engine valve. Subsequently, the oil distributor valve reduces the oil pressure in the housing and a valve spring returns the valve to its closed position, thereby moving the drive piston and boost piston back to their original positions against the liner.
- Whenever needed, the valve actuator may be removed from the supply manifold for service or replacement to maintain optimal valve performance.
- These and other features and advantages of the invention will be more fully understood from the following description of certain specific embodiments of the invention taken together with the accompanying drawings.
-
FIG. 1 is a cross-sectioned view of a camless internal combustion engine utilizing integrated hydraulic valve actuators of the invention; -
FIG. 2 is an exploded view of a valve actuator assembly according to the present invention; -
FIG. 3 is a cross-sectional view of a hydraulic valve system with the interior of one actuator; and -
FIG. 4 is a cross-sectional view of the system ofFIG. 3 seen from an opposite direction with the exterior of the actuator. - Referring now to
FIG. 1 of the drawings in detail,numeral 10 generally indicates a camless internal combustion engine.Engine 10 has a plurality ofpistons 12, reciprocable withinengine cylinders 14. Eachcylinder 14 has associated intake andexhaust valves valves FIG. 2 ) fixed tohydraulic supply manifolds 22 mounted oncylinder heads 24 and closing upper ends of thecylinders 14. Theactuators 20 are controlled by oil distributor valves 26 (FIGS. 3,4 ) which are activated by acontroller 27 to deliver pressure oil to or cut off pressure oil from thevalve actuators 20. Specifically, thevalves valve springs 28 conventionally mounted on thecylinder heads 24. - In accordance with the present invention, the
valve actuators 20 comprise integral assemblies, as shown inFIG. 2 . Eachactuator 20 includes acylindrical housing 30 which may be formed of metal. Thehousing 30 carries anexternal seal ring 32 and internally defines a through opening formed as astepped bore 34. Bore 34 includes amajor diameter 36 extending from anupper portion 38 of the housing to anintermediate diameter 40 near amidportion 42 of thehousing 30. Aminor diameter 44 extends from theintermediate diameter 40 to abottom end 46 of the housing. Themajor diameter 36 is sized to receive-acylindrical liner 48 carrying anexternal seal ring 49. - The
liner 48 may be formed of various metals depending upon the application. Theliner 48 internally defines acylinder 50 which acts as a riding surface for anouter diameter 54 of apiston subassembly 56. The diameter ofcylinder 50 may be varied to match theouter diameter 54 of thepiston subassembly 56, which reciprocates incylinder 50. Alower end 57 of theliner 48 also provides an upper stop for thepiston subassembly 56. - The
piston subassembly 56 comprises the hydraulic actuator pistons, including atubular boost piston 58 coaxially surrounding adrive piston 60. Theboost piston 58 defines aninner riding surface 62 for thedrive piston 60. Alower flange 63 of the boost piston is engagable with the stop formed on thelower end 57 of theliner 48 to limit upward travel of the piston subassembly 56. Thedrive piston 60 has anupper portion 64 received within theriding surface 62 of theboost piston 58 and a tapered lower end orcam 66 extending fromupper portion 64. Thelower end 66 of thedrive piston 60 is engagable with thelower flange 63 of theboost piston 58 to limit upward travel of the drive piston. - The
intermediate diameter 40 of the stepped bore is smaller than the exterior of thecylindrical liner 48 to provide an abutment for the cylindrical liner. Theintermediate diameter 40 also defines the axial motion or stroke of theboost piston 58 with thepiston subassembly 56. - The
minor diameter 44 of thestepped bore 34 has a smaller diameter than theboost piston 58, to provide an abutment which stops downward motion of theboost piston 58 at a predetermined point. However, theminor diameter 44 is larger than thelower end 66 of thedrive piston 60 to allow axial motion of the piston in theminor diameter 44. - A drive
piston position sensor 68 extends radially into thehousing 30 near thebottom end 46. Theposition sensor 68 engages the taperedlower end 66 of thedrive piston 60 so that, as the drive piston reciprocates within thehousing 30, the position of the drive piston is related to the position of the sensor. - After the
valve actuators 20 are assembled, the valve actuators are attached to thehydraulic supply manifolds 22, as shown inFIGS. 3 and 4 . In a preferred embodiment of the present invention, eachsupply manifold 22 hasbores 70 for receiving theupper portions 38 of the associatedvalve actuators 20. Theexternal seal ring 32 carried on each valve actuator housing may be an o-ring provided to seal the associated bore 70 against the leakage of oil. Thesimilar seal 49 is provided on eachliner 48 to seal themajor diameter 36 of the housing stepped bore against leakage of oil through the bore. Once thevalve actuator 20 is inserted into thebore 70, aflange 72 extending from the exterior of thehousing 30 is bolted or attached to thesupply manifold 22. - In operation, oil is directed to the
oil distributor valves 26, which sequentially communicate oil pressure to each valve actuator 20 from the associatedhydraulic supply manifold 22. The oil flows into thevalve actuator 20 through theinternal cylinder 50 of theliner 48. The oil pressure acts against thepiston subassembly 56 to force it axially downward within thehousing 30, thereby opening the associated intake orexhaust valve valve spring 28. - As the
piston subassembly 56 moves toward thebottom end 46 of thehousing 30, theboost piston 58 is stopped by the abutment formed by the minor diameter bore 44. Thereafter, the drive piston continues to move axially downward, at a slower rate, until the associated intake orexhaust valve 16, is fully opened by the force of oil pressure on the smaller drive piston alone. At the desired interval, theoil distributor valve 26 is actuated to reduce the oil pressure to thevalve actuator 20, allowing thevalve spring 28 to returnpiston subassembly 56 and thevalve - As the
piston subassembly 56 reciprocates within thehousing 30, theposition sensor 68, relays the position of thedrive piston 60 tocontroller 27. Based upon the position of thedrive piston 60 relative to thepiston position sensor 68, thecontroller 27 determines the proper amount of oil pressure required from theoil distributor valve 26 to properly actuate thevalve 16. - If desired a
valve actuator 20 may be removed from its hydraulic supply manifold for service or replacement. Servicing of thevalve actuator 20 is accomplished by removing theliner 48 andpiston subassembly 56 from thehousing 30. If theliner 48 becomes worn over time, it may be replaced with a new liner. If needed, thepiston subassembly 56 may also be replaced. If desired theliner 48 may be replaced with a liner having a larger diameter opening to accommodate a piston subassembly having a larger diameter than theoriginal piston subassembly 56. After thevalve actuator 20 is reassembled with new parts, the valve actuator may be reinstalled to thesupply manifold 22 and reused. - While the invention has been described by reference to certain preferred embodiments, it should be understood that numerous changes could be made within the spirit and scope of the inventive concepts described. Accordingly, it is intended that the invention not be limited to the disclosed embodiments, but that it have the full scope permitted by the language of the following claims.
Claims (11)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/635,095 US6857404B1 (en) | 2003-08-06 | 2003-08-06 | Hydraulic engine valve actuator |
DE102004037863A DE102004037863B4 (en) | 2003-08-06 | 2004-08-04 | Hydraulic engine valve actuator |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/635,095 US6857404B1 (en) | 2003-08-06 | 2003-08-06 | Hydraulic engine valve actuator |
Publications (2)
Publication Number | Publication Date |
---|---|
US20050028767A1 true US20050028767A1 (en) | 2005-02-10 |
US6857404B1 US6857404B1 (en) | 2005-02-22 |
Family
ID=34116155
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US10/635,095 Expired - Fee Related US6857404B1 (en) | 2003-08-06 | 2003-08-06 | Hydraulic engine valve actuator |
Country Status (2)
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US (1) | US6857404B1 (en) |
DE (1) | DE102004037863B4 (en) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006108629A2 (en) * | 2005-04-14 | 2006-10-19 | Man Diesel A/S | A large two-stroke diesel engine with improved fuel efficiency |
USD885439S1 (en) * | 2017-02-17 | 2020-05-26 | Eaton Corporation | Engine valve lifter having anti-rotation plug |
USD896842S1 (en) * | 2015-11-23 | 2020-09-22 | Innio Jenbacher Gmbh & Co Og | Valve for engine |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005047180A1 (en) * | 2005-09-30 | 2007-04-05 | Robert Bosch Gmbh | Electro hydraulic control device for charge-cycle valve, has fluid conducting fluid rails for supplying/discharging fluid to/from valve actuators, where fluid rails and all valve actuators are accommodated in common housing |
FI124350B (en) * | 2012-03-09 | 2014-07-15 | Wärtsilä Finland Oy | Hydraulic actuator |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4050359A (en) * | 1975-09-04 | 1977-09-27 | Brunswick Corporation | Hydraulic power trim and power tilt system supply |
US4162616A (en) * | 1976-04-02 | 1979-07-31 | Tokico Ltd. | Hydraulic master cylinder |
US20020157531A1 (en) * | 1996-11-06 | 2002-10-31 | George Kadlicko | Hydraulic cylinder with position encoder |
US20040050349A1 (en) * | 2002-09-16 | 2004-03-18 | Leman Scott A. | Variable force engine valve actuator |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5275136A (en) * | 1991-06-24 | 1994-01-04 | Ford Motor Company | Variable engine valve control system with hydraulic damper |
US5638781A (en) * | 1995-05-17 | 1997-06-17 | Sturman; Oded E. | Hydraulic actuator for an internal combustion engine |
-
2003
- 2003-08-06 US US10/635,095 patent/US6857404B1/en not_active Expired - Fee Related
-
2004
- 2004-08-04 DE DE102004037863A patent/DE102004037863B4/en not_active Expired - Fee Related
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4050359A (en) * | 1975-09-04 | 1977-09-27 | Brunswick Corporation | Hydraulic power trim and power tilt system supply |
US4162616A (en) * | 1976-04-02 | 1979-07-31 | Tokico Ltd. | Hydraulic master cylinder |
US20020157531A1 (en) * | 1996-11-06 | 2002-10-31 | George Kadlicko | Hydraulic cylinder with position encoder |
US20040050349A1 (en) * | 2002-09-16 | 2004-03-18 | Leman Scott A. | Variable force engine valve actuator |
Cited By (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2006108629A2 (en) * | 2005-04-14 | 2006-10-19 | Man Diesel A/S | A large two-stroke diesel engine with improved fuel efficiency |
WO2006108629A3 (en) * | 2005-04-14 | 2007-04-26 | Man B & W Diesel As | A large two-stroke diesel engine with improved fuel efficiency |
KR100950539B1 (en) | 2005-04-14 | 2010-03-30 | 맨 디젤 필리얼 아프 맨 디젤 에스이, 티스크랜드 | A large two-stroke diesel engine with improved fuel efficiency |
USD896842S1 (en) * | 2015-11-23 | 2020-09-22 | Innio Jenbacher Gmbh & Co Og | Valve for engine |
USD944863S1 (en) | 2015-11-23 | 2022-03-01 | Innio Jenbacher Gmbh & Co Og | Valve for engine |
USD944862S1 (en) | 2015-11-23 | 2022-03-01 | Innio Jenbacher Gmbh & Co Og | Valve for engine |
USD944861S1 (en) | 2015-11-23 | 2022-03-01 | Innio Jenbacher Gmbh & Co Og | Valve for engine |
USD885439S1 (en) * | 2017-02-17 | 2020-05-26 | Eaton Corporation | Engine valve lifter having anti-rotation plug |
Also Published As
Publication number | Publication date |
---|---|
US6857404B1 (en) | 2005-02-22 |
DE102004037863B4 (en) | 2011-06-16 |
DE102004037863A1 (en) | 2005-03-10 |
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