EP4194667A1 - Brennkraftmaschinen mit variabler ventilsteuerung - Google Patents

Brennkraftmaschinen mit variabler ventilsteuerung Download PDF

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Publication number
EP4194667A1
EP4194667A1 EP21212949.8A EP21212949A EP4194667A1 EP 4194667 A1 EP4194667 A1 EP 4194667A1 EP 21212949 A EP21212949 A EP 21212949A EP 4194667 A1 EP4194667 A1 EP 4194667A1
Authority
EP
European Patent Office
Prior art keywords
rocker arm
arm part
latch
internal combustion
combustion engine
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.)
Pending
Application number
EP21212949.8A
Other languages
English (en)
French (fr)
Inventor
Gyula Toth
András SZEBÉNYI
Tamás HEIMLER
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.)
Avl Hungary Kft
Original Assignee
Avl Hungary Kft
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 Avl Hungary Kft filed Critical Avl Hungary Kft
Priority to EP21212949.8A priority Critical patent/EP4194667A1/de
Publication of EP4194667A1 publication Critical patent/EP4194667A1/de
Pending 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
    • F01L1/12—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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/205—Adjusting or compensating clearance by means of shims or the like
    • 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
    • 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
    • F01L13/0063—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 by modification of cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • 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
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • 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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F01L2001/467—Lost motion springs
    • 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

Definitions

  • the invention concerns an internal combustion engine having a camshaft and valves for charging and discharging combustion chambers comprising a first rocker arm part and a second rocker arm part, wherein the first rocker arm part and the second rocker arm part are pivotably mounted.
  • variable valve actuation i.e. valve actuation with variable valve lift
  • valve actuation with variable valve lift are becoming more and more important in reciprocating internal combustion engines, especially in four-stroke and six-stroke reciprocating internal combustion engines.
  • Variable valve trains can be used to meet the need of internal combustion engine designers and the desire of thermodynamics to alternatively transmit different valve lift curves to one or more valves, in particular depending on the operating situation of the internal combustion engine, whereby both the valve lift and the opening and closing times can be adjusted.
  • Stroke changeover and stroke shutdown systems with switchable cam followers such as bucket tappets, roller tappets or rocker arms, are in series production in various applications.
  • the rule here is that for each additional alternative valve stroke, there must also be a corresponding cam as a stroke-generating element - unless the alternative stroke is a zero stroke.
  • Stroke switching enables the use of at least two different valve lifts depending on the operating point.
  • a smaller valve lift is especially adapted to the part-load range, improving the torque curve and reducing consumption and emissions.
  • the large valve lift can be optimized to further increase performance.
  • a smaller valve lift with lower maximum lift and shorter event length enables a reduction in charge change work (Miller cycle) due to a significantly earlier intake closing time and throttling in the intake tract. Similar results are possible with the Atkinson cycle, i.e., extremely late intake closing. Optimum filling of the combustion chamber still results in a torque increase in the part-load range.
  • Cylinder deactivation is used primarily for large-volume, four-stroke engines (for example with four, eight, ten or twelve engine cylinders). In this process, selected engine cylinders are shut down by stroke deactivation at the intake and exhaust valves; complete decoupling from the cam lift takes place. Due to equidistant firing sequences, common V8 and V12 engines can be switched to A4 or R6 engines. The purpose of engine cylinder deactivation is to minimize charge exchange losses and perform an operating point shift toward higher center pressures and thus higher thermodynamic efficiencies, resulting in significant fuel savings.
  • Engine braking operation Engine braking systems that enable engine braking operation are becoming increasingly important in vehicle internal combustion engines, especially for commercial vehicles, as they are cost-effective and space-saving auxiliary braking systems that can relieve the wheel brakes, especially on longer downhill journeys.
  • the increase in the specific power of modern commercial vehicle engines also requires an increase in the braking power to be achieved.
  • valve lift Various systems and concepts are known for changing the valve lift.
  • document US 2014/0326212 A1 shows a system for variable valve control, in particular for generating an engine braking effect, which has a "lost motion" device with hydraulically actable locking elements for selectively locking or releasing a valve actuation mechanism so that valve actuation movements are selectively transmitted or not transmitted to one or more valves in order to change the valve lift and thereby generate an engine braking effect.
  • a "lost motion" device with hydraulically actable locking elements for selectively locking or releasing a valve actuation mechanism so that valve actuation movements are selectively transmitted or not transmitted to one or more valves in order to change the valve lift and thereby generate an engine braking effect.
  • a valve actuating device for actuating at least a first valve of a reciprocating engine, in particular an internal combustion engine, which can be used for engine braking and which comprises a first rocker arm part, a second rocker arm part, and a first switching element for changing the valve lift of the at least one first valve, wherein the first rocker arm part and the second rocker arm part are pivotably mounted and are arranged in such a way that at least one first valve control movement can be transmitted from a first camshaft via the first rocker arm part and the second rocker arm part to the at least one first valve.
  • Document WO 2019/025511 A1 relates to a coupling device for a valve actuating device for actuating at least one valve of a reciprocating engine with variable valve lift, in particular for a valve actuating device of a reciprocating internal combustion engine, a valve actuating device and a reciprocating engine.
  • the coupling device comprises a first coupling element, a second coupling element and a locking device.
  • the first coupling element and the second coupling element can be displaced relative to one another at least within defined limits along a first axis. It is possible to block the relative displacement of the two coupling elements with respect to one another along the first axis at least in a first direction by means of the blocking device.
  • the blocking device comprises a blocking element rotatable about the first axis at least in a defined range in the circumferential direction, wherein the relative displacement of the two coupling elements along the first axis is blocked at least in the first direction when the blocking element is in a blocking position.
  • Document AT 50710/2020 relates to a valve actuating device for actuating a valve of a reciprocating engine, comprising a coupling device with a blocking element which can be brought into a first and second position by means of a mechanical switching device for actuating the coupling device, wherein the valve actuating device transmits an actuating movement for the valve in the first position
  • the switching device comprises: a guide rod and a parallel, relatively movable actuating rod; a gate guide element movably mounted on the guide rod for moving the locking element between the positions; a release element coupled to the gate guide element, the gate guide element and the release element being clamped by means of spring elements between two stops of an actuating rod, to each of which a spring element is assigned, the gate guide element and the release element being displaceable with the actuating rod in the direction along and/or parallel to the guide rod, and a blocking element cooperating with the release element, so that in a first state the blocking element, upon displacement of the actuating rod in the
  • An aspect of the invention concerns an internal combustion engine having a camshaft and valves for charging and discharging combustion chambers, comprising:
  • the invention relies on the approach to realize a variable valve actuation by a split rocker arm, wherein a first rocker arm part and a second rocker arm part can be blocked with respect to each other by a pivotable mechanical element.
  • this is realized by a pivotably mounted latch which is fixed to one of the rocker arm parts and form-fittingly engages with a contact surface of the other rocker arm part when in a locked position.
  • the pivotably mounted latch allows a switching of the variable valve actuation during only one combustion cycle. Furthermore, the latch can be realized that it is itself-locking in the locked position, such that no additional force is needed to keep the latch in its locked position.
  • a nose of the latch and the contact surface cooperating with this nose can be formed in such a manner, that the latch is blocked when being in the locked position.
  • the latch provides a simple and easy mechanism to block and unblock the relative movement of a first rocker arm part and a second rocker arm part of a split rocker arm.
  • the latch comprises a first lever and a second lever extending at least partially in radial direction with respect to a rotational axis of the latch, wherein the second rocker arm part comprises a first spring engaging with the first lever and the first hydraulic or pneumatic means engaging with the second lever, wherein the first hydraulic or pneumatic means works against a spring force to set the rotational position of the latch.
  • the switching of the variable valve actuation can be achieved by a comparatively low oil volume flow. Furthermore, by the use of a spring together with a latch engaging form-fittingly with a contact surface, and therefore a relatively small spring force, the pressure to open the blocking mechanism realized by the latch can be kept relatively small, such as only 2 bar and below.
  • extremal switch position of the first hydraulic or pneumatic means define the first and second rotational positions of the latch, respectively.
  • the latch occupies the first rotational position, in which the first rocker arm part and the second rocker arm part are blocked in movement with respect to each other, if the first hydraulic or pneumatic means is in a relaxed state.
  • a regular engine operation with an activated valve is set as default. This is especially important at engine start when the oil pump of the internal combustion engine does not yet deliver pressure.
  • the provision of a pump or reservoir to build up pressure before the engine start can be omitted.
  • the latch further comprises a first nose extending at least partially in radial direction with respect to a rotational axis of the latch and adapted to engage with the contact surface of the first rocker arm part.
  • a nose is particularly advantageous in a self-blocking arrangement of the contact surface and the first nose.
  • the first rotational position and the second rotational position of the latch define a rotation angle of approximately 10 degrees, preferably approximately 5 degrees. With such small rotation angles, only a small movement of the latch is needed to change the operating mode of the rocker arm.
  • the first rocker arm part engages with the camshaft, and the rocker arm part engages with a valve or a valve bridge.
  • the internal combustion engine further comprises a phaser unit, the phaser unit comprising a phaser shaft, a phaser lever, and a cart, wherein the cart has a first wheel arrangement engaging with the first cam of the camshaft and a second wheel arrangement engaging with a second cam of the camshaft, wherein the phaser lever connects the phaser shaft of the cart in such a manner that a change of position of the phaser lever changes the rotational position of the cart with respect to the camshaft.
  • the phaser unit By providing the phaser unit, the valve lift curve with respect to the cam angle can be modified. In particular, the timing and the maximum opening of the valve can be modified. This is particularly advantageous during engine warm-up.
  • first rocker arm engages with a tread of the cart
  • second rocker arm engages with a valve or a valve bridge
  • the internal combustion engine comprises a third rocker arm pivotably mounted besides the first rocker arm and having the same rotational axis as the first rocker arm, wherein the latch has a second nose and a third lever, both extending at least partially in radial direction with respect to a rotational axis of the latch, wherein the latch is pivotably mounted on the second rocker arm part and engages with second pneumatic or hydraulic means of the second rocker arm part and wherein the second nose, in a third rotational position of the latch, form-fittingly engages with a contact surface of the third rocker arm part such that a valve actuation motion is transmittable from the camshaft of the internal combustion engine via the third rocker arm part and the second rocker arm part to the at least one valve.
  • an extremal switch position of the second hydraulic or pneumatic means defines the third rotational position of the latch.
  • the second hydraulic or pneumatic means comprises a second spring and works against the spring force generated by the second spring to set the rotational position of the latch.
  • the contact surface and/or the surface of the first and/or second nose is hardened. By this, wear of the stressed surface and nose can be reduced.
  • the first rotational position and the third rotational position of the latch define a rotation angle of approximately 15 degrees, preferably 10 degrees.
  • Figure 1 depicts an embodiment of an internal combustion engine 1 comprising a camshaft 2 for actuating valve 3. Actuation motion is transmitted from camshaft to the valves 3 via a split rocker arm 4/5 comprising a first rocker arm part 4 and a second rocker arm part 5.
  • Figure 2 depicts a first embodiment of a split rocker arm 4/5 comprising a phaser shift mechanism 13 for transmitting a valve motion from the camshaft to a valve bridge 12 actuating the valves 3.
  • the mechanism shown in Figure 2 has a first rocker arm part 4 and a second rocker arm part 5.
  • the second rocker arm part 5 has a pivotable latch 6, which is able to block, depending on its rotational position, a relative movement between the first rocker arm part 4 and the second rocker arm part 5. In the rotational position shown in Figure 2 , the latch 6 blocks the relative movement.
  • the latch 6 has a first nose 11 and a first lever 7. As shown in Figure 2 , these extend at least partially in radial direction with respect to a rotational axis of the latch 6.
  • the first rocker arm part 4 cooperates with the phaser shift mechanism, in particular with a cart 16 of a phaser shift mechanism.
  • a cart 16 cooperates with a first cam 19 and a second cam 20 on the camshaft 2.
  • cam 19 may be a two-fold cam, where both cams 19 interact with the cart 16.
  • the cart 16 is connected via a phaser connection 15 to a phaser lever 14 which is actuated by a phaser shaft 26.
  • the phaser connection 15 converts the rotational movement of the phaser lever 14 in a linear movement of the phaser connection 15 changing the position of the cart 16 with respect to the camshaft 2.
  • the first rocker arm part 4 is preferably biased by a spring 27 towards the cart 16 and the camshaft 2. This assures that the first rocker arm part 4 stays in contact with the cart 16 as well as the cart 16 stays in contact with the camshaft 2, in particular the first cam 19 and the second cam 20.
  • Figure 3 depicts a sectional view of the embodiment of the mechanism according to Figure 2 .
  • the cart 16 preferably interacts with the first cam 19 via a first roller 17 being mounted to the cart and with the second cam 20 with a second roller 18 also being mounted to the cart 16.
  • latch 6 has a second lever 8.
  • This lever 8 also extends at least partially in radial direction with respect to the rotational axis of the latch 6. While the first nose 11 interacts with a contact surface 24 of the first rocker arm part 4, the first lever 7 interacts with and is biased by a biasing spring 9 and the second lever 8 interacts with piston 32 of a hydraulic or pneumatic means 10.
  • Figure 4a and Figure 4b depict an augmented sector of Figure 3 around latch 6.
  • Figure 4a shows a rotational position of the latch 6 when a relative movement of the first rocker arm part 4 and the second rocker arm part 5 are unblocked.
  • Figure 4b shows a rotational position of the latch 6 when a relative movement of the first rocker arm part 4 and the second rocker arm part 5 is blocked.
  • a chamber 33 of the pneumatic or hydraulic means 10 is put under pressure such that the latch 6 rotates clockwise and the spring 9 is biased by the first lever 7.
  • the inclination of a phase formed at the tip of the nose 11 and the phase formed by the contact surface 24 are such that latch 6 is self-blocked, if the first rocker arm part 4 and the second rocker arm part 5 are biased towards each other.
  • Figures 5, 6 and 7 depict several views of a split rocker arm to get another embodiment of a latch mechanism for a split rocker arm with a first rocker arm part 4 and a second rocker arm part 5 in order to block and unblock a relative movement.
  • the elements may be identical to the first embodiment of a split rocker arm of the first embodiment depicted in Figure 3 to Figure 4b .
  • the spring 9 is not supported by the second rocker arm part 5 to push the first lever 7 away from the second rocker arm part 5, but the second rocker arm part 5 according to the second embodiment further has a a U-shaped bracket 30 such that spring 9 can be arranged between the U-shaped bracket 30 and the first lever 7 and be supported by the U-shaped bracket 30 in order to bias the lever 7 towards the main body of the second rocker arm part 5.
  • the U-shaped bracket is fixed to the second rocker arm part 5 by two bolts.
  • the latch 6 of the second embodiment preferably only has one single lever 7.
  • the hydraulic or pneumatic means 10 with the piston 32 may be arranged in such a way on the second rocker arm part 5, that it is adapted to exert a force in the contrary direction to the bias of spring 9.
  • the split rocker arm 4/5 may also be used without the phaser shifter 13.
  • the roller 28 being mounted to the first rocker arm part 4 directly interacts with a cam on the camshaft 2.
  • Figure 8 depicts a second embodiment of a phaser unit 13 in a perspective view.
  • rocker arm 4 according to Figures 8 and 9 is not a split rocker arm
  • the embodiment of the phaser unit 13 may also be applied to the split rocker arms depicted in Figures 2 to 7 .
  • Figure 9 shows a side view of the rocker arm arrangement according to Figure 8 , where the cart 16 interacts with cam of a camshaft 2.
  • the first roller 17 interacts with a first cam 19 (not depicted), while a second roller 18 of the cart 16 interacts with a second cam 20.
  • FIG 10a and Figure 11a depict two different phaser positions of the cart 16 with respect to the camshaft 2.
  • the valve opens earlier and stays open longer in the diagram of Figure 11b . It is advantageous that the total opening duration is longer than in the cart's initial position of Fig. 10a . Since according to the thermodynamics, only about 3mm lift is needed to achieve such a valve opening, a "platform" formed by the diagram in Fig. 11b is sufficient.
  • Figure 12 depicts a third embodiment of a split rocker arm.
  • the third embodiment has a third rocker arm part 25.
  • the third rocker arm part 25 can cooperate with the second rocker arm part 5 in order to transmit a valve lift motion from a camshaft to the valves of the internal combustion engine 1.
  • the relative movement between the third rocker arm part 25 and the second rocker arm part 5 is blocked and unblocked by the latch 6.
  • the latch 6 has a second nose 21, which can cooperate with a second contact surface 34 of the third rocker arm part 25.
  • the latch 6 has a third lever 22 to control this motion.
  • the first nose 11 and the second nose 21 have different rotational positions with respect to the axis of rotation of the latch 6.
  • the third embodiment of the split rocker arm also has a second spring 29 to bias the third rocker arm part 25 against the cams of the camshaft 2 (not shown).
  • Figure 13 is a top view of the third embodiment of the split rocker arm according to Figure 12 .
  • Figures 14 to 16 are sectional views along different planes of the third embodiment of the split rocker arm being shown in Figure 13 .
  • Figure 14 is a sectional view in the plane A-A of Figure 13 .
  • the first lever 7 is actuated by a hydraulic or pneumatic means 10a comprising a first pressure chamber 33a and a first piston 32a being arranged to interact with the first lever 7.
  • Figure 15 is a sectional view along the plane B-B of Figure 13 .
  • a piston 35 actuated by a first biasing spring 9 is acting on the second lever 8 and biases the same.
  • Figure 16 is a sectional view along the plane C-C of Figure 13 .
  • a second hydraulic or pneumatic means 10b is arranged in the second rocker arm part 5 in order to act on the third lever 22 of the latch 6.
  • the second hydraulic or pneumatic means 10b has a second pressure chamber 33b and a second piston 32b. Furthermore, this second hydraulic or pneumatic means 10b has also a second biasing spring 23 acting on the piston 32b. In order to release the third lever 22 of bias, the second pressure chamber 33b is open ended and the spring biasing the second piston 32b is compressed.
  • Figs. 14, 15 and 16 show the latch in the regular intake cycle position.
  • the rotational torque provided by the force of spring 23 is higher, preferably double, of the rotational torque provided by the spring 9, so the force provided by spring 23 overcomes the force provided spring 9. That is why the latch remains in a well-defined middle position without any oil pressure being applied.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP21212949.8A 2021-12-07 2021-12-07 Brennkraftmaschinen mit variabler ventilsteuerung Pending EP4194667A1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP21212949.8A EP4194667A1 (de) 2021-12-07 2021-12-07 Brennkraftmaschinen mit variabler ventilsteuerung

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP21212949.8A EP4194667A1 (de) 2021-12-07 2021-12-07 Brennkraftmaschinen mit variabler ventilsteuerung

Publications (1)

Publication Number Publication Date
EP4194667A1 true EP4194667A1 (de) 2023-06-14

Family

ID=78824858

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Application Number Title Priority Date Filing Date
EP21212949.8A Pending EP4194667A1 (de) 2021-12-07 2021-12-07 Brennkraftmaschinen mit variabler ventilsteuerung

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EP (1) EP4194667A1 (de)

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4151817A (en) * 1976-12-15 1979-05-01 Eaton Corporation Engine valve control mechanism
US4829647A (en) * 1987-12-14 1989-05-16 Ford Motor Company Method of making low friction finger follower rocker arms
US5297516A (en) * 1991-10-23 1994-03-29 Atsugi Unisia Corporation Valve actuating apparatus
US7546822B2 (en) * 2004-03-03 2009-06-16 Timken Us Corporation Switching finger follower assembly
AT510527A1 (de) * 2010-09-23 2012-04-15 Avl List Gmbh Viertakt-brennkraftmaschine mit einer motorbremse
US20140326212A1 (en) 2010-07-27 2014-11-06 Jacobs Vehicle Systems, Inc. Lost Motion Valve Actuation Systems with Locking Elements Including Wedge Locking Elements
WO2015022071A1 (de) 2013-08-12 2015-02-19 Avl List Gmbh Ventilbetätigungseinrichtung zur veränderung des ventilhubs
WO2019025511A1 (de) 2017-08-01 2019-02-07 Avl List Gmbh Kopplungsvorrichtung für eine ventilbetätigungsvorrichtung
WO2021083552A1 (en) * 2019-11-01 2021-05-06 Eaton Intelligent Power Limited Rocker arm assemblies

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4151817A (en) * 1976-12-15 1979-05-01 Eaton Corporation Engine valve control mechanism
US4829647A (en) * 1987-12-14 1989-05-16 Ford Motor Company Method of making low friction finger follower rocker arms
US5297516A (en) * 1991-10-23 1994-03-29 Atsugi Unisia Corporation Valve actuating apparatus
US7546822B2 (en) * 2004-03-03 2009-06-16 Timken Us Corporation Switching finger follower assembly
US20140326212A1 (en) 2010-07-27 2014-11-06 Jacobs Vehicle Systems, Inc. Lost Motion Valve Actuation Systems with Locking Elements Including Wedge Locking Elements
AT510527A1 (de) * 2010-09-23 2012-04-15 Avl List Gmbh Viertakt-brennkraftmaschine mit einer motorbremse
WO2015022071A1 (de) 2013-08-12 2015-02-19 Avl List Gmbh Ventilbetätigungseinrichtung zur veränderung des ventilhubs
WO2019025511A1 (de) 2017-08-01 2019-02-07 Avl List Gmbh Kopplungsvorrichtung für eine ventilbetätigungsvorrichtung
WO2021083552A1 (en) * 2019-11-01 2021-05-06 Eaton Intelligent Power Limited Rocker arm assemblies

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