EP3173593A1 - Commande de soupape variable comprenant un culbuteur - Google Patents

Commande de soupape variable comprenant un culbuteur Download PDF

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Publication number
EP3173593A1
EP3173593A1 EP16002316.4A EP16002316A EP3173593A1 EP 3173593 A1 EP3173593 A1 EP 3173593A1 EP 16002316 A EP16002316 A EP 16002316A EP 3173593 A1 EP3173593 A1 EP 3173593A1
Authority
EP
European Patent Office
Prior art keywords
valve
rocker arm
lever
roller
contour surface
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
EP16002316.4A
Other languages
German (de)
English (en)
Other versions
EP3173593B1 (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
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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
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Publication of EP3173593A1 publication Critical patent/EP3173593A1/fr
Application granted granted Critical
Publication of EP3173593B1 publication Critical patent/EP3173593B1/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
    • F01L13/0021—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 rocker arm ratio
    • 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
    • F01L1/08—Shape of cams
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • 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
    • F01L2013/0068—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 with an oscillating cam acting on the valve of the "BMW-Valvetronic" type

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 that different opening and closing times and different valve opening strokes are not infinitely adjustable. Another disadvantage is that it is not possible with these known approaches to convert an existing valvetrain without variability to a valvetrain with variability, without requiring changes to surrounding components, other than those needed immediately for the realization of variability become.
  • the object of the invention is in particular to provide a variable valve train, which allows a continuous change of the valve opening and closing times and the valve opening strokes.
  • 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 periodically.
  • the lift valve is preferably a charge exchange valve of an internal combustion engine.
  • the valve train comprises a switchable rocker arm arrangement for actuating the lift valve.
  • a switchable rocker arm arrangement is understood to mean a rocker arm arrangement which can be changed by a switching device or actuator in its transmission properties relating to the transmission of the cam movement to the lift valve such that a valve opening and / or closing time and / or a height of the valve opening travel is variable.
  • the rocker arm assembly comprises a first rocker arm, hereinafter referred to as transfer rocker arm, and a second rocker arm, hereinafter referred to as a valve rocker arm, which are mounted pivotably on different rocker arm shafts, which are each parallel to the camshaft axis.
  • the valve rocker arm is in operative contact with the lifting valve at a first end and has a roller, in particular a pressure roller, on a second end.
  • the transfer rocker arm is associated with a cam of the camshaft at a first end, ie, engages the cam to pick up the cam movement. According to the cam movement, the transmission lever tilts.
  • the contour surface is a surface of the transfer rocker arm on which the role of the valve rocker lever in the transmission of the cam movement back and forth to the lift valve and so transmits the movement of the transfer rocker arm to the valve rocker arm or coupled. Due to the design of the surface shape of the contour surface, z. B. the slope in unwinding, the course of the valve lift can be set.
  • the variable valve drive comprises an actuating device for switching the rocker arm arrangement, by means of which the contour surface is rotatable about the rocker arm axis of the transfer rocker arm in order to produce a displacement of a rolling region of the roller of the valve rocker arm on the contour surface.
  • the adjusting device is designed to generate a rotation of the contour surface or of the contour surface of the comprehensive part of the transfer rocker arm relative to the valve rocker arm.
  • variable valve train An advantage of the variable valve train according to the invention is that the construction of rocker arm and camshaft can remain unchanged - with respect to a conventional non-variable valve train. Another advantage is that the variable valve train manages the valve actuation with little moving masses, since the valve rocker arm tilts up and down as usual, the transmission rocker also tilts up and down and rotates the camshaft as usual.
  • variable valve train allows a very robust solution for fully variable control, especially for commercial vehicle and industrial engines.
  • the contour surface has a first rolling region which does not generate a valve lift when the roller of the valve rocker roll rolls on the first rolling region.
  • the first rolling area forms a base circle contour and is also referred to below as the base circle area.
  • the roll-off points on the base circle region have a preferably constant radial distance to the rocker arm axis of the transmission lever.
  • the contour surface further has a second rolling region adjoining the first rolling region, which has a ramp contour.
  • a ramp contour predetermines a valve lift such that the further the roller of the valve rocker roll rolls off the first roll-off area on the second roll-off area, the greater the valve lift.
  • a ramp contour is thus understood to mean a region which has an increasing radial distance to the rocker arm axis of the transmission lever in a direction of movement of the roller. In the opposite direction of movement of the roller, the radial distance on the second rolling area consequently decreases.
  • a rolling region is understood to be a region of the contour surface on which the roller of the valve rocker arm can be unrolled during a tilting movement of the transmission rocker arm.
  • the contour surface has a third rolling region adjoining the second rolling region.
  • the third roll-off region preferably generates a valve position with a predetermined constant valve lift, for example a valve position with maximum valve lift, when the roller of the valve rocker roll rolls on the third roll-off region.
  • the roll-off points on the third rolling range preferably have a constant radial distance to the rocker arm axis of the transmission lever. However, the radial distance of the third rolling area is greater than that of the first rolling area.
  • the area of the contour surface unrolled by the rocker roller remains constant in the angular amount. Due to the rotation of the contour surface by means of the adjusting device relative to the valve rocker arm, however, the area of the contour surface actually tapped from the roller will be moved, that is, unrolled. For example, if the contour surface is rotated by means of the adjusting device relative to the valve rocker arm so that the rocker arm rolls a smaller distance on the first area and instead a greater distance on the second area, the valve lift increases.
  • the valve lift and / or the valve opening and closing times which result from the rolling of the valve rocker arm on the contour surface, can be set.
  • the lifting valve can be kept completely closed, for example, for example, if the role of the valve rocker only on the first Abroll Scheme back and forth.
  • a valve operation in which the lift valve is kept open for a short time on the maximum valve lift. This can be achieved, for example, if the contour surface is fixed by the adjusting device in a twisting position, in which the rolling movement of the roller of the valve tilting lever also at least partially surrounds the third region. During unwinding on the third area, the lift valve is briefly kept open at the maximum valve lift.
  • the contour surface has a fourth rolling region adjoining the third rolling region, which in turn forms a ramp contour, and a fifth region, which adjoins the fourth rolling region.
  • the roll-off points on the fifth Abroll Scheme have a constant radial distance to the rocker arm axis of the transmission lever.
  • the radial distance of the fifth Abroll Schemes is greater than the radial distance of the third Abroll Studentss and greater than the radial distance of the first Abroll Studentss.
  • the third area forms a middle position in which the lift valve geometry, d. H. is kept open during the rolling of the roll on the third area, in an opening position with a constant lifting height, which is smaller than the maximum lifting height.
  • the transfer rocker arm comprises a first lever, which engages the cam of the camshaft, and a second lever, comprising the contour surface which is in operative connection with the roller of the valve rocker arm.
  • the first lever and the second lever are coupled to each other in movement, in particular such that a tilting movement of the first lever generated by the cam leads to a corresponding tilting movement with the same angular amount of the second lever about the tilt lever axis of the transfer rocker arm.
  • a twisting position of the second lever relative to the first lever changeable to change a Abroll Scheme the role of the valve rocker arm on the contour surface.
  • the first lever and the second lever are then coupled to each other again so that they are jointly pivoted back and forth about the rocker shaft axis when excited by the cam.
  • the adjusting device is designed to continuously change a rotational position of the second lever relative to the first lever.
  • the adjusting device may be designed to change a rotational position of the second lever relative to the first lever into two or more predetermined positions, so that two or more different rolling regions on the contour surface and thus valve strokes are switchable.
  • the adjusting device is designed as a hydraulic switching unit.
  • the actuating device may comprise a hydraulically actuable and / or actuated shift pin, which is attached at its first end to the first lever and is attached to a second end on the second lever of the transfer rocker arm, wherein an extension of the shift pin is a rotational position of the second lever relative to the first Lever changed.
  • the adjusting device may be designed as an electrical and / or mechanical adjusting device, for example, to actuate the switching pin electrically and / or mechanically.
  • first lever and the second lever can be coupled to one another via a driver.
  • the driver can also form a receptacle for the shift pin and thus form a dual function.
  • the transfer rocker arm may be biased by means of a return spring, such that the transmission lever is pressed against the camshaft.
  • a return spring such that the transmission lever is pressed against the camshaft.
  • valve rocker arm has at its valve-side end a receptacle in which a hydraulic valve clearance compensation element or a screw with elephant foot is added.
  • the rocker arm may further 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 and 2 show a side view and a side perspective view of a variable valve train 1 according to an embodiment of the invention.
  • the valve train 1 is used for actuating charge exchange valves (not shown) of an internal combustion engine, which are periodically movable between a closed and an open position by a cam 2 of a camshaft 3.
  • the valve drive 1 comprises a switchable rocker arm arrangement for actuating the lift valves.
  • the rocker arm assembly comprises a first rocker arm (valve rocker arm) 20, which is pivotally mounted about a rocker shaft 23, and a second rocker arm ( réelleskipphebel) 10 which is pivotally mounted on a further rocker shaft 13.
  • the two rocker shafts 13, 23 are spatially separated, but both parallel to the axis of the camshaft third
  • the valve rocker arm 20 is in operative contact with a valve-side end 21, ie with its valve-side lever arm 21, with two lift valves (not shown).
  • the valve-side lever arm 21 of the valve rocker arm 20 is designed for this purpose as a two-valve lever arm to actuate two charge exchange valves simultaneously.
  • the valve-side lever arm 21 is fork-shaped, which in FIG. 2 is recognizable.
  • two such Ventilkipphebelan kannen 10, 20 are arranged in the axial direction of the camshaft one behind the other to actuate four globe valves.
  • a receptacle 24 is arranged at each valve-side end of the lever arm 21, arranged.
  • the receptacle 24 can be used for mounting a known hydraulic lash adjuster element 25. Instead of a hydraulic valve clearance compensation element, a screw with elephant foot can be received in the receptacle 24 with appropriate processing, 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 the length dimensions which change over the service life the charge exchange valves compensate so that in the base circle phase of the valve-actuating cam safe valve closing is ensured. On the other hand, 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.
  • the valve rocker arm 20 is mounted on a rocker arm bearing block (not shown), wherein the rocker arm shaft 23 is disposed on the rocker arm bearing block, on which the valve rocker arm 20 is pivotally mounted with an associated bore and held by an axial position assurance.
  • 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 a ring land 27, in an associated counter-element (not shown) engages pivotally with axial flank support.
  • the axial position assurance can also be done in a conventional manner via contact surfaces on the Kipphebelflanken.
  • 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.
  • a roller 26 is disposed at the distal end of the lever arm 22.
  • the transfer rocker arm 10 is engaged with the cam 2 of the camshaft 3 at a cam shaft side end 11.
  • the transfer rocker arm 10 is also operatively connected to the roller 26 of the valve rocker arm 20 at the other end 12 with respect to the rocker arm shaft 13 via a stroke-defining surface, ie, the roller 26 of the valve rocker arm 20 rolls at one of the cam movement generated tilting movement of the transfer rocker arm 10 on the contour surface 16, whereby a corresponding tilting movement of the valve rocker arm 20 is generated.
  • the transfer rocker arm 10 transmits by its tilting movement, the cam movement on the valve rocker arm 20, which in turn generates the valve lift by its corresponding resulting tilting movement.
  • Transfer rocker arm 10 and valve rocker arm 20 are connected in series in this manner.
  • Camshaft 3 and valve rocker arm 20 can be designed for this purpose in a conventional manner and are coupled to each other in motion by the transmission lever 10 arranged therebetween.
  • the contour surface 16, on which the Ventilkipphebelrolle 26 is supported serves as Abroll Scheme on which the Ventilkipphebelrolle 26 back and rolls in the transmission of the tilting movement of the transfer rocker arm 10 on the valve rocker 20 and. Due to the configuration of this contour surface 16 serving as a rolling surface, the stroke behavior of the lifting valve can thus be predetermined and also varied.
  • FIG. 3 shows a detailed view of the coupling between the valve rocker arm 20 and the transfer rocker arm 10 on the contour surface 16.
  • the contour surface 16 has in this embodiment, three different areas 16a, 16b and 16c, which can serve as Abroll Schemee for the roller 26.
  • the first rolling area 16a forms the base circle contour, i. H. when the roller 26 rolls on this area, the valve rocker arm 20 generates no valve lift.
  • the distance of the points on the first rolling surface 16a to the rocker shaft 13, d. H. their radial distance R1, is constant.
  • the contour surface 16 furthermore comprises a second rolling region 16b immediately adjacent to the first rolling region 16a, which has a ramp contour.
  • the radial distance of the roll-off points increases on the second rolling range, starting from a value R1 up to a value R2.
  • a third rolling region 16c Connected to the second rolling region 16b is a third rolling region 16c, which has a constant radial clearance R2 and produces a valve position with maximum valve lift when the roller 26 of the valve rocker arm 20 rolls on the third rolling region 16c.
  • the valve drive 1 further comprises an actuating device 30 for switching the rocker arm assembly 10, 20, by means of which the contour surface 16 about the rocker shaft 13 of the transmission rocker arm 10 is rotatable to produce a displacement of a Abroll Schemes the roller 26 of the valve rocker arm 20 on the contour surface 16.
  • an actuating device 30 for switching the rocker arm assembly 10, 20, by means of which the contour surface 16 about the rocker shaft 13 of the transmission rocker arm 10 is rotatable to produce a displacement of a Abroll Schemes the roller 26 of the valve rocker arm 20 on the contour surface 16.
  • FIG. 1 shown embodiment of the transfer rocker arm 10, a first lever 14, hereinafter referred to as a cam follower lever, which is connected via a roller 18 with the cam 2 of the camshaft 3 in engagement.
  • the transfer rocker arm 10 further comprises a second lever 15, hereinafter referred to as a contour lever, which has the contour surface 16 which is in operative connection with the roller 26 of the valve rocker arm 20.
  • cam follower lever 14 and the contour lever 15 are coupled to each other such that a tilting movement of the cam follower lever 14 generated by the cam 2 results in a corresponding tilting movement of the contour lever 15 about the rocker arm axis 13 of the transfer rocker arm 10.
  • a rotational position of the contour lever 15 relative to the cam follower lever 14 is variable to change a Abroll Scheme the roller 26 of the valve rocker arm 20 on the contour surface.
  • cam follower lever 14 and contour lever 15 are then again motion-coupled with respect to a pivoting movement (tilting movement) about the rocker shaft 13th
  • FIG. 4 shows a side view of the contour lever 15 of the transfer rocker arm 10 according to an embodiment of the invention.
  • the adjusting device the below still using the FIGS. 7 and 8th explained in more detail, be executed to set two different rotational positions of the contour lever 15 relative to the cam follower lever 14, resulting in two different Abroll Schemee a1 and a2 for the roller 26 of the valve rocker arm 10.
  • the roller 26 reciprocates on a first rolling-off area a1 when the tilting movement of the transmission rocker arm 10 or contouring lever 15 is almost the whole of the first rolling-off area 16a and a first partial area of the second rolling area 16b includes.
  • a second set On the other hand, in the case of a tilting movement of the transfer rocker arm 10 or the contour lever 15 generated by the cam 2, the roller 26 rolls back and forth on the second rolling area a2, which comprises almost the entire second rolling area 16b and a partial area of the third rolling area 16c.
  • valve drive 1 If the valve drive 1 is switched over from the rolling area a1 to the rolling area a2, the valve lift that can be generated by the camshaft 3 increases. As in FIG. 4 can be seen, the radial distance at the right end of the area a2 is still equal to the radial distance in the first Abroll Scheme 16a, so that at this point a closed position of the globe valves is generated.
  • the adjusting device can be designed so that it can set a rotational position of the second lever relative to the first lever in two predetermined positions, so that two different, predetermined Abroll Schemee on the contour surface 16 and thus valve strokes are switchable.
  • the adjusting device can also be designed so that more than two predetermined Vercardpositionen are adjustable or the rotational position is infinitely variable within predetermined limits. In the latter variant, the valve lift can be varied continuously.
  • FIG. 5 shows a side view of the contour lever 515 of the transfer rocker arm 10 according to another embodiment of the invention.
  • the contour lever has a contour surface 516 with five different rolling areas 16a-16e.
  • the first rolling roller 16a again forms the base circle contour with a constant radial distance R1 to the axis 13.
  • the subsequent second Abroll Scheme 16b again forms a ramp contour, with increasing radial distance, which has risen to the value R2 at the end of the second Abroll Schemes.
  • the adjoining third rolling region 16c again forms an area with a constant radial distance R2.
  • the third region 16c forms a middle position in which the lift valve is kept open, ie during the rolling of the roller 26 on the third region 16c, in an open position with a constant lift height, which is smaller than the maximum lift height.
  • FIG. 6 illustrates various stroke curves that can be adjusted with the valve train.
  • the abscissa axis corresponds to the rotational angle ⁇ of the camshaft 3.
  • the ordinate axis corresponds to the valve lift d.
  • the curves 61 to 64 show four different adjustable valve lift curves as a function of the angle of rotation of the camshaft.
  • Each of the four curves 61 to 64 corresponds to a specific set by means of the adjusting device rotational position from the second lever 15 to the first lever 14 of the transfer rocker arm 10.
  • the curve 61 corresponds to a set rotational position, which produces the largest valve lift and the shortest valve closing times
  • the curve 65 on the other hand produces the lowest valve lift and the longest valve closing times.
  • FIGS. 7 and 8th illustrate the operation of the hydraulic actuator. This shows FIG. 7 a perspective view of the two-part construction of the transfer rocker arm 10 in a first switching state.
  • the transfer rocker arm 10 has a two-part construction.
  • the transfer rocker arm 10 includes a first lever (cam follower lever) 14, which engages with the cam 2 of the camshaft 3, and a second lever (contour lever) 15 having the contour surface 16 which is operatively connected to the roller 26 of the valve rocker arm 20 stands.
  • cam follower lever 14 and the contour lever 15 are coupled to each other via the driver 32, which presses against the stop surface 19, such that a tilting movement of the cam follower lever 14 generated by the cam 2 to a corresponding tilting movement of the contour lever 15 about the Kipphebelachse 13 of the transfer rocker 10th leads.
  • This movement coupling of cam follower lever 14 and contour lever 15 can be realized instead of the driver shown by other positive or hydraulic connections, z. B by an internal toothing, a swing motor principle, etc. and can be attached to a location other than the one shown.
  • a rotational position of the contour lever 15 relative to the cam follower lever 14 is variable to change a Abroll Scheme the roller 26 of the valve rocker arm 20 on the contour surface 16.
  • the hydraulic adjusting device 30 comprises a hydraulically actuated pin 31, also referred to in this document as a shift pin 31 which is attached at one end to the cam follower lever 14 and disposed at another end on the contour lever 15.
  • the cam follower lever 14 for this purpose a bolt receptacle 33 for holding the shift pin 31, in which a pressurizable with a hydraulic fluid pressure chamber is arranged (not shown).
  • the hydraulic lines for supplying the pressure chamber and the control lines of the actuator 30 are not shown.
  • the other end of the shift pin is held in a receptacle on the contour lever 15, wherein the recording simultaneously forms the driver 32.
  • the contour lever 15 rotates clockwise in a different rotational position relative to the cam follower lever 14.
  • the contour surface 16 also rotates clockwise.
  • the Abroll Scheme for the roller 26 of the valve rocker arm 20 can be adjusted by controlling the pressure level in the pressure chamber different extension positions of the shift pin 31 and thus different Vercardpositionen.
  • the cam follower lever 15 is biased by means of a return spring 17 via a missionstellfederan Kunststoffddling 17 a, so that the entire transfer rocker arm 10 is pressed by the spring force of the return spring against the camshaft 3.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Mechanically-Actuated Valves (AREA)
EP16002316.4A 2015-11-26 2016-10-28 Commande de soupape variable comprenant un culbuteur Active EP3173593B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015015264.5A DE102015015264A1 (de) 2015-11-26 2015-11-26 Variabler Ventiltrieb mit einem Kipphebel

Publications (2)

Publication Number Publication Date
EP3173593A1 true EP3173593A1 (fr) 2017-05-31
EP3173593B1 EP3173593B1 (fr) 2019-04-10

Family

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EP16002316.4A Active EP3173593B1 (fr) 2015-11-26 2016-10-28 Commande de soupape variable comprenant un culbuteur

Country Status (6)

Country Link
US (1) US10436079B2 (fr)
EP (1) EP3173593B1 (fr)
CN (1) CN107035452B (fr)
BR (1) BR102016027678B1 (fr)
DE (1) DE102015015264A1 (fr)
RU (1) RU2724811C2 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201800003742A1 (it) * 2018-03-19 2019-09-19 Fpt Motorenforschung Ag Attuazione variabile valvole

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4230877A1 (de) 1991-09-30 1993-04-01 Volkswagen Ag Ventilsteuerung fuer ein hubventil mit zwei nocken
EP0717174A1 (fr) * 1994-12-12 1996-06-19 Isuzu Motors Limited Système de commande de soupape pour moteur à combustion interne
DE19519048A1 (de) 1995-05-24 1996-11-28 Hermann Prof Dr Ing Krueger Variabler Ventiltrieb mit mehreren Nocken
DE19520117C2 (de) 1995-06-01 2002-04-11 Porsche Ag Ventiltrieb einer Brennkraftmaschine
US20070125330A1 (en) * 2005-12-05 2007-06-07 Jongmin Lee System for variable valvetrain actuation

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2730174C2 (de) * 1977-07-04 1981-12-10 Ludwig Merckle Kg Chem. Pharm. Fabrik, 7902 Blaubeuren Aminobenzoesäurederivate und Arzneimittel enthaltend solche Aminobenzoesäurederivate
SE470363B (sv) * 1992-06-17 1994-01-31 Volvo Ab Förfarande och anordning för motorbromsning med en flercylindrig förbränningsmotor
DE10227870A1 (de) * 2002-06-22 2004-01-08 Bayerische Motoren Werke Ag Ventiltrieb für eine Hubkolben-Brennkraftmaschine
JP4093849B2 (ja) 2002-11-29 2008-06-04 株式会社オティックス 可変動弁機構
JP4480669B2 (ja) * 2003-03-11 2010-06-16 ヤマハ発動機株式会社 内燃機関の可変動弁機構
RU2328604C2 (ru) * 2003-12-24 2008-07-10 Хонда Мотор Ко., Лтд. Устройство регулирования подъема клапана двигателя внутреннего сгорания
JP2007127189A (ja) 2005-11-02 2007-05-24 Toyota Motor Corp 回転直動式アクチュエータ、直動軸機構、可変動弁機構及び可変動弁型エンジン
KR100962194B1 (ko) 2007-12-14 2010-06-11 현대자동차주식회사 연속 가변 밸브 리프트 시스템
US8584631B2 (en) * 2011-11-02 2013-11-19 Delphi Technologies, Inc. Continuously variable valve lift system with default mechanism
DE102014001169A1 (de) * 2014-01-31 2015-08-06 Man Truck & Bus Ag Vorrichtung und Verfahren zum Betätigen zumindest eines Auslassventils einer ventilgesteuerten Brennkraftmaschine
CN104847430A (zh) * 2015-03-23 2015-08-19 朱譞晟 双动滑壁式独立可调全可变气门正时和升程机构

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4230877A1 (de) 1991-09-30 1993-04-01 Volkswagen Ag Ventilsteuerung fuer ein hubventil mit zwei nocken
EP0717174A1 (fr) * 1994-12-12 1996-06-19 Isuzu Motors Limited Système de commande de soupape pour moteur à combustion interne
DE19519048A1 (de) 1995-05-24 1996-11-28 Hermann Prof Dr Ing Krueger Variabler Ventiltrieb mit mehreren Nocken
DE19520117C2 (de) 1995-06-01 2002-04-11 Porsche Ag Ventiltrieb einer Brennkraftmaschine
US20070125330A1 (en) * 2005-12-05 2007-06-07 Jongmin Lee System for variable valvetrain actuation

Also Published As

Publication number Publication date
RU2016145412A3 (fr) 2020-02-14
US10436079B2 (en) 2019-10-08
RU2016145412A (ru) 2018-05-22
DE102015015264A1 (de) 2017-06-01
CN107035452B (zh) 2021-10-08
US20170152769A1 (en) 2017-06-01
EP3173593B1 (fr) 2019-04-10
CN107035452A (zh) 2017-08-11
RU2724811C2 (ru) 2020-06-25
BR102016027678A2 (pt) 2017-07-25
BR102016027678B1 (pt) 2023-01-31

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