EP3170997A1 - Commande de soupape variable comprenant un culbuteur - Google Patents

Commande de soupape variable comprenant un culbuteur Download PDF

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Publication number
EP3170997A1
EP3170997A1 EP16002314.9A EP16002314A EP3170997A1 EP 3170997 A1 EP3170997 A1 EP 3170997A1 EP 16002314 A EP16002314 A EP 16002314A EP 3170997 A1 EP3170997 A1 EP 3170997A1
Authority
EP
European Patent Office
Prior art keywords
cam
rocker arm
roller lever
camshaft
valve
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
Application number
EP16002314.9A
Other languages
German (de)
English (en)
Other versions
EP3170997B1 (fr
Inventor
Pham Hai-Son
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.)
MAN Truck and Bus SE
Original Assignee
MAN Truck and Bus SE
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 MAN Truck and Bus SE filed Critical MAN Truck and Bus SE
Publication of EP3170997A1 publication Critical patent/EP3170997A1/fr
Application granted granted Critical
Publication of EP3170997B1 publication Critical patent/EP3170997B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/181—Centre pivot rocking arms
    • 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
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
    • F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
    • F02D13/0203—Variable control of intake and exhaust valves
    • F02D13/0207—Variable control of intake and exhaust valves changing valve lift or valve lift and timing
    • 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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L2001/186—Split rocking arms, e.g. rocker arms having two articulated parts and means for varying the relative position of these parts or for selectively connecting the parts to move in unison
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • F01L2305/02—Mounting of rollers
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/033—Hydraulic engines

Definitions

  • the invention relates to a variable valve train for a lift valve, in particular for a charge exchange valve of an internal combustion engine, which is periodically movable between a closed and an open position by a cam via a rocker arm.
  • variable valve trains offer the advantageous possibility of targeted adjustment of the course of the valve lift over the cam angle as a function of operating parameters of the device equipped with the respective lift valve, that is, for example, depending on the speed, load or temperature of an internal combustion engine.
  • a camshaft block with two different cam contours is rotatably but axially displaceably arranged on a camshaft. According to the axial position of the cam block is a cam contour via an intermediate member (transmission lever) with the lifting valve in operative connection. The axial displacement of the cam block to change the valve parameters takes place during the Grundnikphase against the action of a return spring by means of a pressure ring.
  • a disadvantage of the cited prior art is the high space requirement, which is required for adjusting the cam block or for the axial adjustment of the camshaft.
  • a rocker arm assembly for a variable valve train wherein a first rocker arm of each rocker arm is associated with a cam with a small cam lift and a second rocker cam with a large cam lift, each with a locking device for each pair of rocker, through which only the larger cam lift when switched on having cam for both rocker arm is effective.
  • a disadvantage of this known valve train is the need for an external spring stop to ensure the return of the second rocker arm. This and the independent storage of the second rocker arm also allow no pre-assembly.
  • the two levers need a driving point, which leads to the fact that the two cam profiles must be symmetrical to each other or the apex of the two cams have no angular offset from each other. This prevents the possibility of varying the phase position of the valve lifts.
  • variable valve train with a rocker arm, with which disadvantages of conventional techniques can be avoided.
  • the invention is based in particular on the object of a structurally compact and easy-to-install design of such a variable valve train.
  • a variable valve drive is provided for a lift valve.
  • the lift valve is between a closed and an open position, in particular against the force of a return spring, indirectly movable by a cam of a camshaft via a rocker arm periodically.
  • the lift valve is preferably a charge exchange valve of an internal combustion engine.
  • the valve train comprises a camshaft, comprising at least one first cam and at least one offset in the longitudinal direction of the camshaft second cam, wherein the at least one first cam and the at least one second cam are designed differently in their cam contour.
  • the cam contour of the at least one first cam to the cam contour of the at least one second cam may have a different cam lobe and / or a different phase position.
  • the at least one second cam has a larger cam lift (cam lift) than the at least one first cam.
  • the cam contours each determine, taking into account the valve clearance according to their training, the opening and closing time and / or the opening stroke of the lift valve.
  • a second cam may be disposed immediately adjacent to a first cam.
  • the valve drive further comprises a rocker arm mounted pivotably about a rocker arm axis, which is assigned at its camshaft-side end via a roller, in particular a pressure roller, of the first cam and is in operative connection with the lift valve at its valve-side end.
  • a rocker arm mounted pivotably about a rocker arm axis, which is assigned at its camshaft-side end via a roller, in particular a pressure roller, of the first cam and is in operative connection with the lift valve at its valve-side end.
  • One arm of the rocker arm thus serves to actuate the lift valve, the other lever arm is driven by a cam.
  • the rocker arm is preferably mounted on a central region on the rocker shaft.
  • the valve drive further comprises a roller lever which is assigned at its camshaft-side end to the at least one second cam via at least one roller, d. H. the movement of the / the second cam (s) picks up, and is articulated at its other end on the rocker arm about the rocker arm pivotally.
  • valvetrain comprises a switchable hydraulic locking means by which the rocker arm and the roller lever can be selectively locked together, wherein rocker arms and roller levers follow the movement of the at least one second cam or can be unlocked from each other, wherein rocker arms and roller levers are independently rotatable and both independently follow the respective associated cam.
  • the second cam In the unlocked state, the second cam is ineffective - it actuates the roller lever, but only performs tilting movements, without influencing the valve.
  • Rocker arm and roller lever rotatably connected to each other, so that both can only be pivoted together about the rocker arm axis.
  • a particular advantage of the valve train according to the invention lies in the compact design, which does not or at least hardly affects the space in height and length of a conventional toggle lever-based valve train.
  • the rocker arm only becomes wider, but moves in the size range of a conventional two-valve rocker arm.
  • the invention makes it possible to convert an existing valve train without variability, without requiring changes to surrounding components, apart from those which are needed directly for the realization of the variability.
  • Another advantage is in particular that no changes to the cylinder head are necessary if a conventional non-variable rocker arm valve drive to be replaced by the variable valve train according to the invention.
  • the roller lever is formed so that it has two arms which extend on both sides of the camshaft-side end of the rocker arm and tap the cam contour of the two second cam. The two arms engage their associated second cam each with a roller, z. B. a pressure roller from, which rolls on the second cam.
  • This two-armed embodiment of the roller lever allows an advantageous power flow to transmit the cam movement of the second cam in the activated state of the hydraulic locking device via the roller lever on the rocker arm and the rocker arm to the lift valve.
  • the camshaft side end of the rocker arm may be provided on both sides of the second cam ever a first cam and the camshaft side end of the rocker arm extend on both sides of the roller lever and tap the cam contour of the two first cam.
  • the camshaft end of the rocker arm thus has two arms, wherein the roller lever is arranged therebetween. The two arms grasp their associated first cam each with a roller, z. B. a pressure roller from, which rolls on the first cam.
  • the roller lever is connected to the rocker arm via a hinge for rotatably securing the roller lever to the rocker arm about the rocker arm axis.
  • the rocker arm and the roller lever each have a hinge pin receptacle, which are arranged in alignment with each other and have an inserted hinge pin.
  • a further advantageous possibility of the realization according to the invention provides that the rocker arm and the roller lever are clamped together by at least one return spring, such that the rollers of roller lever and rocker arm are aligned in a base circle position to each other.
  • the roller lever is pressed by the return spring permanently to the main rocker arm while the camshaft is in a base circle position.
  • These return springs preferably press on a contact point on or of the rocker arm and on a contact point on or of the roller lever. Due to the mutual tension easy pre-assembly of the entire switchable rocker arm is possible.
  • the switchable hydraulic locking device comprises a hydraulically actuable shift pin, which can be brought from a first position (release position) in a second position (locking position) by applying a predetermined hydraulic pressure.
  • the shift pin prevents a relative movement of the rocker arm to the roller lever to each other about the Kipphebelachse, d. h.
  • the roller lever can not be pivoted independently of the rocker arm about the tilt axis.
  • the rocker arm and the roller lever are hydraulically locked, but not in the first position.
  • this embodiment are in the rocker arm in a Gleit Resultssbohrung the rocker arm, a guide pin, a plugged onto the guide pin bolt spring and the shift pin of the hydraulic Verrieglungs noticed, which is bolted to the guide pin arranged.
  • the switching pin is on one for actuation the circuit can be filled with oil-filled pressure chamber with a predetermined oil pressure.
  • the locking direction can be designed according to a first variant so that the switching pin is held in a state not acted upon by the predetermined pressure by acting as a return spring bolt spring and the guide pin in the first position and in a state acted upon by the predetermined pressure in the second position is pressed, in which the switching pin protrudes from the rocker arm in the direction of the roller lever and moves into an aligned Gleit Unitsam the roller lever.
  • the locking direction can be further designed according to a second variant, that the switching pin is held in a state not acted upon by the predetermined pressure by the bolt spring in the second position (locking position), so that roller lever and rocker arms are locked together rotatably and in one pressed state with the predetermined pressure are pressed into the first position in which the shift pin is sunk into the rocker arm and the two levers are unlocked from each other.
  • roller lever is designed to be open, so that the compressed by the retraction of the shift pin compressed air can escape and does not resist the extension movement of the shift pin. This opening is already provided in the blank of the roller lever, so that no additional vent hole is needed.
  • the rocker arm can on its underside, d. H. the cylinder head facing side, have a geometry for axial fixation on a bearing block.
  • the rocker arm may have a mounting for attachment to a Kipphebellagerbock on which the rocker shaft is arranged, on which the rocker arm with an associated bore is pivotally mounted and held by an axial position assurance, wherein the axial position securing a guide connection as an engagement element counter-element connection between the bearing block and the rocker arm, in which a transversely aligned to the axial direction engagement element, for. B. in the form of an annular web, engages pivotally in an associated counter element with axial flank support.
  • Another aspect of the invention relates to a motor vehicle, in particular a commercial vehicle, with a variable valve train, as described in this document.
  • FIGS. 1 to 3 show various perspective views of a variable valve train 1 according to an embodiment of the invention.
  • the valve train 1 is used to actuate a charge exchange valve (not shown) of an internal combustion engine which is periodically movable between a closed and an open position by a cam via a rocker arm.
  • the camshaft 7 has a central cam 3, also referred to as first cam in this document, and two further cams 4, 5 arranged staggered in the longitudinal direction of the camshaft 7. These cams 4, 5 are also referred to as second cams in this document , The two cams 4, 5 are arranged on both sides of the central cam and adjacent to this. The central cam 3 and the two second cams 4, 5 are designed differently in their cam contour. The second cams 4, 5 have a larger cam lift than the middle cam 3.
  • phase angle of the central cam 3 with respect to the second cam 4, 5 may differ.
  • the first cam may also be designed as a zero cam, so that the valves remain closed.
  • the valve train further comprises a rocker arm assembly comprising a rocker arm 10 pivotably mounted about a rocker shaft 2 and associated with its camshaft end 11 via a pressure roller 13 of the first cam 3 for tapping it and at its valve end 12 in operative communication with at least one Lift valve is stopped.
  • a rocker arm assembly comprising a rocker arm 10 pivotably mounted about a rocker shaft 2 and associated with its camshaft end 11 via a pressure roller 13 of the first cam 3 for tapping it and at its valve end 12 in operative communication with at least one Lift valve is stopped.
  • rocker arm 10 is mounted on a rocker arm bearing block (not shown), wherein the rocker arm 2 is arranged on the rocker arm bearing block, on which the rocker arm 10 is pivotally mounted with an associated bore and held by means of an axial position assurance.
  • the axial position assurance can be done for example in a conventional manner via contact surfaces on the Kipphebelflanken. These flanks can be created for example by calibration of the forging blank or by mechanical processing. Bearing side, the fixation can also be done on appropriately machined surfaces and by means of washers and retaining rings.
  • Next axial position locks between a rocker arm and the axle are known. For example, has an area of the axis, which is enclosed by the bore of the rocker arm, an annular groove in which a snap ring extends, which runs at the same time with its outer ring portion in an annular groove of the rocker arm
  • the axial position assurance is designed as an engagement element counter-element connection between the bearing block and the rocker arm, wherein a transversely aligned to the axial direction engagement element, for. B. in the form of an annular web 16, in an associated counter-element (not shown) engages pivotally with axial flank support.
  • the valve-side lever arm 12 of the rocker arm 10 is designed as a two-valve lever arm to actuate two charge exchange valves simultaneously.
  • the valve-side lever arm 12 is fork-shaped.
  • a Recording 15 arranged at each valve-side end of the lever arm 12 .
  • the receptacle 15 can be used for mounting a known hydraulic valve lash adjuster element (not shown). Instead of a hydraulic valve clearance compensation element, a screw with elephant foot can be accommodated in the receptacle 15, by means of which a valve clearance can be readjusted manually.
  • Hydraulic valve clearance compensation elements in internal combustion engines are known per se and serve in particular to compensate for the change over the operating length length dimensions of the charge exchange valves so that in the base circle phase of the valve-actuating cam secure valve closing is ensured.
  • the cam lobe should be transferred without loss to the valve and thus converted into a valve lift.
  • the operation of such hydraulic valve clearance compensation elements which are arranged in the power flow of a valve control, in particular an internal combustion engine, is assumed to be known.
  • valve train 1 further comprises a roller lever 20, which is assigned to the two second cams 4, 5 at its camshaft-side end 21 and is pivoted at its other end to the rocker arm 10 about the rocker shaft 2.
  • the rocker arm 10 is connected via a hinge pin 25 rotatably connected to the roller lever 20.
  • a hinge pin receptacle 14 For this connection is located on the rocker arm 10 is a hinge pin receptacle 14 and the roller lever 20 is a hinge pin receptacle 24.
  • the mutually aligned hinge pin receptacles 14, 24 are on an upper side, d. H. a side facing away from the cylinder head, the rocking lever 10, and that at a central region of the rocker arm 10, which forms the cylindrical recess of the rocker arm, in which the rocker shaft 2 is received.
  • the camshaft side lever arm 11 of the rocker arm 10 carries at its end a pressure roller 13 which is associated with the central cam 3 to tap the cam 3 and its rotational movement.
  • the roller lever has two to the camshaft / down extending, parallel arms 21, which also - in the longitudinal direction of the camshaft / seen - on different sides of the camshaft side lever arm 11 of the rocker arm 10 extend.
  • Each of the two arms 21 also carries at the end a pressure roller 23.
  • Each of the pressure rollers 23 is one of the two second cams 4, 5 assigned to tap these.
  • Both the rocker arm 10 and the roller lever 20 are thus rotatably mounted to the rocker shaft 2 and independently pivotable to the rocker arm axis - at least when rocker arm 10 and roller lever 20 are not locked together by the switchable hydraulic locking device.
  • a basic circle phase or cam base circle phase is to be understood as meaning, in particular, an angular range of the cam unit in which cam contours of all partial cams of the cam unit occupy a common base circle level.
  • variable valve train 1 further comprises a switchable hydraulic locking device or a hydraulic switching element 30, are locked by the rigidly with each other when switching the rocker arm 10 and the roller lever 20 and both of the movement of the second cam 4, 5 follow.
  • the switchable hydraulic locking device 30 comprises a guide pin 34, on which a bolt spring 33 is attached.
  • the guide pin 34 and the bolt spring 33 are located in a Gleit Resultssbohrung 37, which is introduced into the camshaft side lever arm 11 of the rocker arm 10.
  • Gleit Resultssbohrung 37 of the guide pin 34 is screwed to a shift pin 31.
  • the bolt spring 34 comes to a spring stop 32 to the plant.
  • the switching pin 31 also has a zero point system 36. In a basic state (no pressurization), the switching pin 31 is pressed by the bolt spring 33 to the zero point system 36. Behind the switching pin 31 is a pressure chamber 35, which is filled to actuate the circuit with oil.
  • Rocker arm 10 and roller lever 20 are thus rotatably supported independently of each other about the Kipphebelachse 2 when not switched hydraulic locking direction 30, so that the second cam 4, 5 are ineffective, d. that is, the second cams 4, 5 actuate the roller lever 20, but only performs tilting movements, without influencing the valve.
  • the rocker arm and roller lever are rotatably connected to each other when the locking direction is switched on, so that both can only be pivoted together about the rocker shaft axis 2.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP16002314.9A 2015-11-20 2016-10-28 Commande de soupape variable comprenant un culbuteur Active EP3170997B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015015087.1A DE102015015087A1 (de) 2015-11-20 2015-11-20 Variabler Ventiltrieb mit einem Kipphebel

Publications (2)

Publication Number Publication Date
EP3170997A1 true EP3170997A1 (fr) 2017-05-24
EP3170997B1 EP3170997B1 (fr) 2019-10-16

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP16002314.9A Active EP3170997B1 (fr) 2015-11-20 2016-10-28 Commande de soupape variable comprenant un culbuteur

Country Status (6)

Country Link
US (1) US10400639B2 (fr)
EP (1) EP3170997B1 (fr)
CN (1) CN107035451B (fr)
BR (1) BR102016026679B1 (fr)
DE (1) DE102015015087A1 (fr)
RU (1) RU2723650C2 (fr)

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WO2019092245A1 (fr) * 2017-11-10 2019-05-16 Eaton Intelligent Power Limited Double culbuteur de levage à mouvement ajouté
DE102017129719A1 (de) 2017-12-13 2019-06-13 Schaeffler Technologies AG & Co. KG Schaltbare Kipphebelanordnung
DE102017129720A1 (de) 2017-12-13 2019-06-13 Schaeffler Technologies AG & Co. KG Schaltbare Kipphebelanordnung
WO2020020492A1 (fr) * 2018-07-27 2020-01-30 Eaton Intelligent Power Limited Culbuteur de désactivation verrouillé par pivot central
WO2021143995A1 (fr) * 2020-01-17 2021-07-22 Eaton Intelligent Power Limited Systèmes de verrou électromagnétique pour ensembles culbuteurs
WO2024002523A1 (fr) * 2022-06-29 2024-01-04 Eaton Intelligent Power Limited Système de culbuteur avec agencement de butée côté came

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DE102018207459A1 (de) * 2018-05-15 2019-11-21 Mahle International Gmbh Ventilantriebsvorrichtung
US11566544B2 (en) 2018-08-09 2023-01-31 Eaton Intelligent Power Limited Rocker arm assembly with lost motion spring
US11319840B2 (en) * 2018-08-09 2022-05-03 Eaton Intelligent Power Limited Deactivating rocker arm having two-stage latch pin
KR102546519B1 (ko) * 2018-12-07 2023-06-21 자콥스 비히클 시스템즈, 인코포레이티드. 두 로커 암 및 붕괴 기구를 포함하는 밸브 구동 시스템
WO2020118284A1 (fr) 2018-12-07 2020-06-11 Jacobs Vehicle Systems, Inc. Système d'actionnement de soupapes comprenant au moins deux culbuteurs et un mécanisme de couplage unidirectionnel
DE102018132857A1 (de) * 2018-12-19 2020-06-25 Man Truck & Bus Se Schaltbare Betätigungsvorrichtung für ein Hubventil einer Brennkraftmaschine, Brennkraftmaschine und Kraftfahrzeug
CN110109567B (zh) 2019-04-24 2020-07-10 武汉华星光电半导体显示技术有限公司 触控板、触控显示器和触控板的制作方法
EP3935271A4 (fr) 2019-05-10 2022-12-14 Cummins, Inc. Système de commande de soupapes pour ouverture de soupape d'admission à durée prolongée
US20230074370A1 (en) * 2020-02-19 2023-03-09 Eaton Intelligent Power Limited Rocker arm assembly, compliance capsules, actuators, and support structures
CN112360586A (zh) * 2020-11-10 2021-02-12 蔡金洲 一种汽车配气机机构配件
DE112022002610T5 (de) * 2021-07-23 2024-03-14 Eaton Intelligent Power Limited Kipphebelanordnung mit hauptkipphebel und gegabeltem hilfskipphebel
DE102021126256A1 (de) 2021-10-11 2023-04-13 Schaeffler Technologies AG & Co. KG Trägermodul für einen schaltbaren Ventiltrieb einer Schwerlastbrennkraftmaschine

Citations (9)

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US5080054A (en) * 1990-03-07 1992-01-14 Nissan Motor Co., Ltd. Rocker arm arrangement for variable timing valve train
DE4230877A1 (de) 1991-09-30 1993-04-01 Volkswagen Ag Ventilsteuerung fuer ein hubventil mit zwei nocken
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WO2019092245A1 (fr) * 2017-11-10 2019-05-16 Eaton Intelligent Power Limited Double culbuteur de levage à mouvement ajouté
US11136906B2 (en) 2017-11-10 2021-10-05 Eaton Intelligent Power Limited Added motion dual lift rocker arm
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WO2020020492A1 (fr) * 2018-07-27 2020-01-30 Eaton Intelligent Power Limited Culbuteur de désactivation verrouillé par pivot central
US11313253B2 (en) 2018-07-27 2022-04-26 Eaton Intelligent Power Limited Center pivot latched deactivating rocker arm
WO2021143995A1 (fr) * 2020-01-17 2021-07-22 Eaton Intelligent Power Limited Systèmes de verrou électromagnétique pour ensembles culbuteurs
WO2024002523A1 (fr) * 2022-06-29 2024-01-04 Eaton Intelligent Power Limited Système de culbuteur avec agencement de butée côté came

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RU2016145153A (ru) 2018-05-18
RU2723650C2 (ru) 2020-06-17
EP3170997B1 (fr) 2019-10-16
CN107035451A (zh) 2017-08-11
DE102015015087A1 (de) 2017-05-24
US10400639B2 (en) 2019-09-03
BR102016026679A2 (pt) 2018-06-05
CN107035451B (zh) 2020-09-04
BR102016026679B1 (pt) 2022-10-04
RU2016145153A3 (fr) 2020-02-12
US20170145876A1 (en) 2017-05-25

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