EP1143120A2 - Ventildeaktivierungsmechanismus einer Brennkraftmaschine - Google Patents

Ventildeaktivierungsmechanismus einer Brennkraftmaschine Download PDF

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Publication number
EP1143120A2
EP1143120A2 EP01302059A EP01302059A EP1143120A2 EP 1143120 A2 EP1143120 A2 EP 1143120A2 EP 01302059 A EP01302059 A EP 01302059A EP 01302059 A EP01302059 A EP 01302059A EP 1143120 A2 EP1143120 A2 EP 1143120A2
Authority
EP
European Patent Office
Prior art keywords
valve
plunger
rocker arm
engagement
assembly
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP01302059A
Other languages
English (en)
French (fr)
Other versions
EP1143120A3 (de
Inventor
Keith Hampton
Richard Lee Madden
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Eaton Corp
Original Assignee
Eaton Corp
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 Eaton Corp filed Critical Eaton Corp
Publication of EP1143120A2 publication Critical patent/EP1143120A2/de
Publication of EP1143120A3 publication Critical patent/EP1143120A3/de
Withdrawn legal-status Critical Current

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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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005—Deactivating valves
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm

Definitions

  • the present invention relates to an improved valve train for an internal combustion engine, and more particularly, to a valve deactivator assembly for use therein.
  • valve deactivator assembly of the present invention may be utilized to introduce some additional lash into the valve train, such that the valves open and close by an amount less than the normal opening and closing
  • the invention is especially suited for introducing into the valve train sufficient lash (also referred to hereinafter as "lost motion"), such that the valves no longer open and close at all (i.e., the valves are "deactivated"), and the invention will be described in connection therewith.
  • Valve deactivators of the general type to which the invention relates are known in connection with various types of internal combustion engine valve gear train, including overhead valve (“OHV”) gear train of the pushrod type. Valve deactivators are also known in connection with overhead cam (“OHC”) type valve gear train of both the center pivot rocker arm type and the end pivot rocker arm type.
  • OHC overhead cam
  • the particular structure of the present invention is not necessarily limited to use in the OHC, end pivot rocker arm type of valve gear train, it is especially suited for use therewith, and will be described in connection with that type of valve gear train.
  • the rocker arm pivots about a pivot location defined by the rocker arm.
  • the pivot location engages the ball plunger of an HLA (hydraulic lash adjuster), the HLA being disposed in a bore in the cylinder head.
  • HLA hydroaulic lash adjuster
  • the added structure referred to herein is typically some sort of latching and lost motion mechanism, by means of which, for example, the plunger assembly of the HLA either may be latched to the body for normal operation, or may be unlatched, and engage in lost motion, for operation in a valve deactivation mode.
  • Such added structure would obviously add substantially to the overall size and complexity and cost of the conventional HLA.
  • the latching mechanism involves latch members which move radially under the influence of either a spring or hydraulic pressure to latch or unlatch the body and the plunger assembly. It is apparent that in such a valve deactivator, the overall diameter of the device will be substantially greater than that of a conventional HLA, which needs only the conventional wall thickness for the body and the plunger. In addition, the presence of a plunger which must be able to move between a latched position and an unlatched position, relative to the body, increases the overall length required for the bore in the cylinder head which contains the HLA body.
  • valve deactivator assembly which is especially suited for use in an end pivot rocker arm type of valve gear train, wherein the addition of valve deactivation capability does not substantially increase the overall size of the hydraulic lash adjuster.
  • valve deactivator assembly for an internal combustion engine having valve means for controlling the flow to and from a combustion chamber, drive means for providing cyclical motion for opening and closing the valve means in timed relationship to the events in the combustion chamber, and valve gear means operative in response to the cyclical motion to effect cyclical opening and closing of the valve means.
  • the valve gear means includes a rocker arm having a valve contact portion in engagement with the valve means, and a pivot location about which the rocker arm normally pivots in response to the cyclical motion of the drive means.
  • the valve deactivator assembly includes a hydraulic lash adjuster adapted to be disposed in a bore in a cylinder head and serving as the pivot point for the pivot location of the rocker arm.
  • the hydraulic lash adjuster is characterized by a body member being disposed in the bore, and a plunger assembly operably associated with the body member and reciprocable relative thereto.
  • the plunger assembly includes a plunger portion and an engagement portion surrounding the plunger portion and being in engagement with the pivot location of the rocker arm.
  • a latch mechanism is operable to latch the engagement portion relative to the plunger portion, in an extended position, during operation in a normal mode, and being operable to unlatch the engagement portion relative to the plunger portion during operation in a deactivated mode.
  • the lash adjuster includes means biasing the engagement portion toward the extended position.
  • FIG. 1 is a somewhat schematic, fragmentary, cross-section taken through a vehicle internal combustion engine, illustrating a typical valve gear train of the type with which the present invention may be utilized.
  • FIG. 2 is a greatly enlarged, fragmentary, cross-section, taken on line 2-2 of FIG. 1, illustrating the valve deactivator assembly of the present invention in its normal, latched condition.
  • FIG. 3 is a fragmentary, perspective view, similar to FIG. 1, illustrating the valve gear train with the valve deactivator assembly of the present invention in its unlatched condition.
  • FIG. 4 is a further enlarged, fragmentary cross-section, similar to FIG. 2, illustrating in greater detail the valve deactivator of the present invention in the latched condition.
  • FIG. 1 illustrates a valve actuating drive train of the end pivot rocker arm type, which is especially suited use of the present invention.
  • FIG. 1 illustrates a cylinder head 11 defining a flow passage 13, by means of which there may be a flow to or from a combustion chamber, generally designated 15.
  • the flow to or from the combustion chamber 15 is controlled by means of an engine poppet valve 17 which is biased, by means of a valve spring 19 from the open position shown in FIG. 1 toward a closed position.
  • the poppet valve 17 includes a valve seat 21 which, when the poppet valve 17 is closed, is in engagement with a valve seat insert, not shown herein, but well known to those skilled in the art.
  • a cam shaft 25 includes a cam profile, generally designated 27 which defines a base circle portion 29 and a lift portion 31. As is well known to those skilled in the art, the function of the cam shaft 25 is to provide cyclical motion for opening and closing the engine poppet valve 17 in timed relationship to the events in the combustion chamber 15.
  • the cyclical motion of the cam shaft 25 is transmitted to the engine poppet valve 17 by means of a rocker arm 33, illustrated herein as being of the end pivot type. It may be seen by comparing FIGS. 1 and 3 that in FIG. 1, the view of the rocker arm 33 is an axial cross section taken through the rocker arm 33.
  • the rocker arm 33 includes a valve contact portion ("pad") 35 which is in engagement with the upper end of the stem of the poppet valve 17.
  • the rocker arm 33 also includes a rotatable cam follower 37, mounted on a shaft 38, such that the cam follower 37 remains in engagement with the cam profile 27.
  • the rocker arm 33 includes a pivot portion, generally designated 39, which defines a pivot location (also to be referred to hereinafter by "39"), i.e., a location about which the rocker arm 33 normally pivots as the cam follower 37 engages, alternately, the base circle portion 29 and then the lift portion 31.
  • the pivot portion 39 comprises the rocker arm 33 having a pair of side walls 40, each of which defines a generally half-circular support surface 40s, shown best in FIG. 2.
  • HLA hydroaulic lash adjuster
  • the rocker arm 33 and the hydraulic lash adjuster 41 together comprise a valve deactivator assembly, generally designated 43.
  • the cylinder head 11 defines a bore 45 extending to an upward surface of the cylinder head 11.
  • the head 11 also defines an oil passage 47, which is typically in communication with the engine lubrication oil circuit.
  • the oil passage 47 comprises one "source of pressurized fluid" which is required to operate the HLA 41, in the conventional manner, well known to those skilled in the art of hydraulic lash adjustment.
  • the hydraulic lash adjuster 41 includes a generally cylindrical body 49 disposed within the bore 45, the body 49 defining an internal blind bore 51.
  • a plunger assembly, generally designated 53, is slidably disposed within the blind bore 51, and includes an upper plunger element 55, a lower plunger element 57, and a leakdown plunger 58.
  • the plunger elements 55, 57 and 58 cooperate to define a low pressure chamber 59 (also referred to hereinafter as a "reservoir").
  • the blind bore 51 and the leakdown plunger element 58 cooperate to define a high pressure chamber, which for simplicity will also bear the reference numeral "51", and which is shown in approximately its minimum volume condition in FIG. 2.
  • a check valve assembly is operable to permit fluid communication between the reservoir 59 and the high pressure chamber 51, in a manner generally well known to those skilled in the art.
  • HLA the "conventional leakdown" type
  • the present invention is not necessarily so limited, and could also be used in conjunction with various other types of HLA.
  • the present invention is illustrated in connection with an HLA of the type having the moveable plunger assembly disposed within a stationary body member, it should be understood that the present invention is not so limited. By way of example only, it would be possible within the scope of the invention for the moveable plunger assembly to surround the stationary body member. All that is essential to the present invention is that there be a body member and that there be a plunger assembly which is moveable (reciprocable) relative to the body member.
  • the body 49 defines a fluid port 63, which is in open fluid communication with the oil passage 47.
  • the upper plunger element 55 defines a radial bore 65, in open communication with the port 63, thus permitting pressurized fluid to flow from the passage 47 through the port 63 and bore 65.
  • the lower plunger element 57 defines an axially extending passage 66p, the upper end of which communicates with a port 66 near the upper end of the lower plunger member 57, such that low pressure fluid in the oil passage 47 flows through the passage 66p, then through the port 66 and into the low pressure chamber 59.
  • the cylinder head 11 Disposed to the left in FIG. 2 of the HLA 41, the cylinder head 11 defines an oil passage 11c, which is in fluid communication with an engine oil circuit which is separate from the circuit connected to the oil passage 47.
  • the oil passage 11c comprises the "source of pressurized fluid" which is required to control (operate) the valve deactivator assembly 43 of the present invention. Therefore, it must be possible to control the oil pressure in the passage 11c, selectively providing either a relatively low pressure or a relatively high pressure, as is well known to those skilled in the art of engine hydraulics.
  • the pressure in the passage 11c may be controlled by means of a solenoid valve (not shown herein).
  • the body 49 defines an opening in which is disposed a generally cylindrical member 49m, which could comprise a roll pin or similar structure.
  • the member 49m extends far enough radially inward into an opening 55o defined by the upper plunger element 55, such that the element 55 is substantially prevented from rotating, relative to the body 49.
  • the lower plunger element 57 defines another axially extending passage 57p, by means of which the control pressure in the passage 11c can flow through the interior of the member 49m, then through the opening 55o, then through the passage 57p, for reasons which will be explained subsequently.
  • the upper plunger element 55 would include a ball plunger portion which would engage an adjacent surface of the rocker arm.
  • the upper plunger element 55 includes a separate plunger portion 67 (which is merely the upper end of the element 55) and engagement portion, generally designated 69, the engagement portion 69 surrounding the cylindrical plunger portion 67, and being disposed for movement (in a vertical direction in FIG. 2) relative to the plunger portion 67.
  • a compression (lost motion) spring 71 surrounds the lower part of the plunger portion 67, and is operable to bias the engagement portion 69 upward, toward a fully extended position as shown in FIG. 2.
  • the engagement portion 69 is biased into engagement with a snap ring (retaining clip) 72, which limits upward travel of the engagement portion 69.
  • the engagement portion 69 is in engagement with the pivot portion 39, and doesn't permit any vertical movement of the pivot portion 39 when the valve deactivator assembly is in the activated (latched) mode (see FIG. 2), as will be described in greater detail subsequently.
  • the sliding engagement portion 69 is in engagement with the snap ring 72, part of the force exerted by the lost motion spring 71 is transmitted directly to the snap ring 72, i.e., not all of the force of the spring 71 is exerted on the rocker arm 33. Instead, the force transmitted to the rocker arm 33 is equal to approximately the force exerted on the upper plunger member 55 by the pressure in the high pressure chamber 51.
  • the upper plunger element 55 defines an axially extending passage 75 which terminates at, but is in open communication with one or more radially extending bores 79.
  • a generally block-shaped portion Surrounding the plunger portion 67 is a generally block-shaped portion (seen best in FIG. 3) of the engagement portion 69, and extending oppositely from the block-shaped portion is a pair of generally cylindrical latch housing portions 81. Together, the latch housing portions 81 comprise a fulcrum for the surfaces 40s of the rocker arm 33, as is best seen in FIG. 2.
  • Each latch housing portion 81 defines a radially extending bore 83, which are aligned with the bores 79 when the engagement portion 69 is in the extended position shown in FIGS. 2 and 4.
  • Each bore 83 is sealed at its radially outer end by a plug 85. Disposed in each bore 83 for reciprocal movement therein is a latch pin 87, biased toward the latched position shown in FIG. 4 by means of a compression (latching) spring 89, the radially outer ends of the springs 89 being seated against the respective plug 85.
  • a compression (latching) spring 89 biased toward the latched position shown in FIG. 4 by means of a compression (latching) spring 89, the radially outer ends of the springs 89 being seated against the respective plug 85.
  • a pair of pistons 91 Disposed within the bores 79 is a pair of pistons 91 which, in the latched condition shown in FIG. 4, may be biased radially inward into engagement with each other, by the latch pins 87 under the influence of the latching springs 89.
  • the latch pins In this latched condition, the latch pins are biased radially inward into the bores 79, as shown in FIG. 4, thus latching the engagement portion 69 to the plunger portion 67.
  • relatively low pressure fluid is communicated from the control pressure source 11c to the passage 75, and the springs 89 have been selected such that the springs 89 are able to overcome the force of the low pressure fluid acting on the radially inner surfaces of the pistons 91.
  • the springs 89 bias the latch pins 87 and the pistons 91 to the latched position shown.
  • the fulcrum defined by the latch housing portions 81 remains in the position shown in FIGS. 1, 2 and 4, such that the pivot portion 39 of the rocker arm 33 pivots, but does not move vertically.
  • the rocker arm 33 operates in its normal manner, moving the engine poppet valve 17 between its open and closed positions in response to the cyclical motion of the cam shaft 25, as is well known to those skilled in the art.
  • the present invention provides a valve deactivator assembly which permits the use of a hydraulic lash adjuster which is of conventional size, as far as the required size of the bore 45 in the cylinder head 11.
  • all of the mechanism needed to achieve the valve deactivation is disposed external to the main part of the HLA, being associated only with the plunger portion 67, in an area where more space is typically available.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Valve Device For Special Equipments (AREA)
EP01302059A 2000-03-08 2001-03-06 Ventildeaktivierungsmechanismus einer Brennkraftmaschine Withdrawn EP1143120A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US52105400A 2000-03-08 2000-03-08
US521054 2000-03-08

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EP1143120A2 true EP1143120A2 (de) 2001-10-10
EP1143120A3 EP1143120A3 (de) 2001-10-24

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Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10146131A1 (de) * 2001-09-19 2003-04-03 Ina Schaeffler Kg Schaltelement für einen Ventiltrieb einer Brennkraftmaschine
DE10330510A1 (de) * 2003-07-05 2005-01-27 Ina-Schaeffler Kg Abstützelement für einen schaltbaren Schlepphebel eines Ventiltriebs einer Brennkraftmaschine
GB2413156A (en) * 2004-04-15 2005-10-19 Stanadyne Corp Valve deactivator assembly for an i.c. engine
DE102005010750A1 (de) * 2005-03-09 2006-09-14 Schaeffler Kg Baueinheit eines Ventiltriebs einer Brennkraftmaschine
DE102006045017A1 (de) * 2006-09-23 2008-03-27 Schaeffler Kg Hydraulisches Abstützelement
US7484484B2 (en) * 2006-03-14 2009-02-03 Gm Global Technology Operations, Inc. Cylinder deactivation apparatus incorporating a distributed accumulator
WO2009030564A2 (de) * 2007-09-04 2009-03-12 Schaeffler Kg Schaltbares abstützelement für einen ventiltrieb einer brennkraftmaschine
US20100275864A1 (en) * 2009-04-30 2010-11-04 Schaeffler Technologies Gmbh & Co. Kg Valve drive system
US8136495B2 (en) 2007-01-18 2012-03-20 Schaeffler Kg Switchable support element for a valve train of an internal combustion engine
WO2015197056A1 (de) * 2014-06-26 2015-12-30 Schaeffler Technologies AG & Co. KG Abstützelement
DE102015221042A1 (de) 2015-02-13 2016-08-18 Schaeffler Technologies AG & Co. KG Ventilbetätigungshebel mit Nockenkontaktrolle
DE102007054615B4 (de) 2006-12-15 2020-07-23 Hyundai Motor Company Kipphebelvorrichtung zur Zylinderabschaltung von Motoren
CN113474540A (zh) * 2019-01-24 2021-10-01 伊顿智能动力有限公司 具有用于汽缸停用和引擎制动构型的间隙管理的摇臂组件
WO2022100886A1 (en) * 2020-11-10 2022-05-19 Eaton Intelligent Power Limited Latching pin assembly and deactivating rocker arm assembly
WO2022189042A1 (en) * 2021-03-11 2022-09-15 Eaton Intelligent Power Limited Variable valve lift rocker arm assembly

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US7121241B1 (en) 2006-01-10 2006-10-17 Eaton Corporation Valve control system including deactivating rocker arm
JP4711977B2 (ja) * 2007-01-18 2011-06-29 株式会社オティックス 可変動弁機構及びこれに用いられるラッシュアジャスタ
JP4833142B2 (ja) * 2007-04-17 2011-12-07 株式会社オティックス ラッシュアジャスタ
JP4866328B2 (ja) * 2007-10-05 2012-02-01 株式会社オティックス 可変動弁機構
JP5069140B2 (ja) * 2008-02-08 2012-11-07 株式会社オティックス 可変動弁機構
US20190309663A9 (en) 2008-07-22 2019-10-10 Eaton Corporation Development of a switching roller finger follower for cylinder deactivation in internal combustion engines
US9228454B2 (en) 2010-03-19 2016-01-05 Eaton Coporation Systems, methods and devices for rocker arm position sensing
US11181013B2 (en) 2009-07-22 2021-11-23 Eaton Intelligent Power Limited Cylinder head arrangement for variable valve actuation rocker arm assemblies
US9885258B2 (en) 2010-03-19 2018-02-06 Eaton Corporation Latch interface for a valve actuating device
DE102011104056A1 (de) * 2011-06-11 2012-12-13 Neumayer Tekfor Holding Gmbh Nockenfolger, Abstützelement und Zylinderkopf
JP2019065860A (ja) * 2012-11-05 2019-04-25 イートン コーポレーションＥａｔｏｎ Ｃｏｒｐｏｒａｔｉｏｎ 内燃機関における気筒休止のためのスイッチングローラーフィンガーフォロワーの開発
US9784148B2 (en) 2013-12-06 2017-10-10 Yamaha Hatsudoki Kabushiki Kaisha Valve gear for engine
CN111164279B (zh) * 2017-08-25 2022-04-05 伊顿智能动力有限公司 与两步可变气门升程摇杆臂相结合时的低行程停用间隙调节器

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JPS61201807A (ja) * 1985-03-04 1986-09-06 Honda Motor Co Ltd 内燃機関のバルブ休止装置
DE4323555A1 (de) * 1993-07-14 1995-01-19 Bayerische Motoren Werke Ag Vorrichtung zum Außerbetriebsetzen eines Brennkraftmaschinen-Hubventils
DE19838909A1 (de) * 1998-08-27 2000-03-02 Schaeffler Waelzlager Ohg Schaltbarer Ventiltrieb einer Brennkraftmaschine

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Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6595174B2 (en) 2001-09-19 2003-07-22 Ina-Schaeffler Kg Switching element for a valve train of an internal combustion engine
DE10146131A1 (de) * 2001-09-19 2003-04-03 Ina Schaeffler Kg Schaltelement für einen Ventiltrieb einer Brennkraftmaschine
DE10330510A1 (de) * 2003-07-05 2005-01-27 Ina-Schaeffler Kg Abstützelement für einen schaltbaren Schlepphebel eines Ventiltriebs einer Brennkraftmaschine
GB2413156A (en) * 2004-04-15 2005-10-19 Stanadyne Corp Valve deactivator assembly for an i.c. engine
FR2869071A1 (fr) * 2004-04-15 2005-10-21 Stanadyne Corp Ensemble de desactivation de soupape pour moteur a combustion interne
DE102005010750A1 (de) * 2005-03-09 2006-09-14 Schaeffler Kg Baueinheit eines Ventiltriebs einer Brennkraftmaschine
US7484484B2 (en) * 2006-03-14 2009-02-03 Gm Global Technology Operations, Inc. Cylinder deactivation apparatus incorporating a distributed accumulator
DE102006045017A1 (de) * 2006-09-23 2008-03-27 Schaeffler Kg Hydraulisches Abstützelement
DE102007054615B4 (de) 2006-12-15 2020-07-23 Hyundai Motor Company Kipphebelvorrichtung zur Zylinderabschaltung von Motoren
US8136495B2 (en) 2007-01-18 2012-03-20 Schaeffler Kg Switchable support element for a valve train of an internal combustion engine
WO2009030564A2 (de) * 2007-09-04 2009-03-12 Schaeffler Kg Schaltbares abstützelement für einen ventiltrieb einer brennkraftmaschine
WO2009030564A3 (de) * 2007-09-04 2009-05-22 Schaeffler Kg Schaltbares abstützelement für einen ventiltrieb einer brennkraftmaschine
US20100275864A1 (en) * 2009-04-30 2010-11-04 Schaeffler Technologies Gmbh & Co. Kg Valve drive system
US8434437B2 (en) 2009-04-30 2013-05-07 Schaeffler Technologies AG & Co. KG Valve drive system
DE102009019680A1 (de) 2009-04-30 2010-11-11 Schaeffler Technologies Gmbh & Co. Kg Ventiltriebssystem
WO2015197056A1 (de) * 2014-06-26 2015-12-30 Schaeffler Technologies AG & Co. KG Abstützelement
KR20170021336A (ko) * 2014-06-26 2017-02-27 섀플러 테크놀로지스 아게 운트 코. 카게 지지 부재
US10066517B2 (en) 2014-06-26 2018-09-04 Schaeffler Technologies AG & Co. KG Support element
DE102015221042A1 (de) 2015-02-13 2016-08-18 Schaeffler Technologies AG & Co. KG Ventilbetätigungshebel mit Nockenkontaktrolle
CN113474540A (zh) * 2019-01-24 2021-10-01 伊顿智能动力有限公司 具有用于汽缸停用和引擎制动构型的间隙管理的摇臂组件
CN113474540B (zh) * 2019-01-24 2023-09-01 伊顿智能动力有限公司 具有用于汽缸停用和引擎制动构型的间隙管理的摇臂组件
WO2022100886A1 (en) * 2020-11-10 2022-05-19 Eaton Intelligent Power Limited Latching pin assembly and deactivating rocker arm assembly
WO2022189042A1 (en) * 2021-03-11 2022-09-15 Eaton Intelligent Power Limited Variable valve lift rocker arm assembly

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Publication number Publication date
JP2001271620A (ja) 2001-10-05
EP1143120A3 (de) 2001-10-24
KR20010089206A (ko) 2001-09-29

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