EP1608849B1 - Ventiltrieb einer einen zylinderkopf aufweisenden brennkraftmaschine - Google Patents

Ventiltrieb einer einen zylinderkopf aufweisenden brennkraftmaschine Download PDF

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Publication number
EP1608849B1
EP1608849B1 EP04721147A EP04721147A EP1608849B1 EP 1608849 B1 EP1608849 B1 EP 1608849B1 EP 04721147 A EP04721147 A EP 04721147A EP 04721147 A EP04721147 A EP 04721147A EP 1608849 B1 EP1608849 B1 EP 1608849B1
Authority
EP
European Patent Office
Prior art keywords
cam
camshaft
cam support
axial
cylinder head
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.)
Expired - Lifetime
Application number
EP04721147A
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German (de)
English (en)
French (fr)
Other versions
EP1608849A1 (de
Inventor
Stefan Dengler
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.)
Audi AG
Original Assignee
Audi AG
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 Audi AG filed Critical Audi AG
Publication of EP1608849A1 publication Critical patent/EP1608849A1/de
Application granted granted Critical
Publication of EP1608849B1 publication Critical patent/EP1608849B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01L13/0015—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
    • F01L1/02—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
    • 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
    • F01L13/0042—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 with cams being 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
    • 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
    • F01L2013/0052—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 with cams provided on an axially slidable sleeve

Definitions

  • the invention relates to a valve train of a cylinder head having an internal combustion engine according to the preamble of claim 1.
  • thermodynamic properties of internal combustion engines mechanical devices which influence the working cycle of the valve train and, for example, allow a speed-dependent change in the opening times or the stroke of the gas exchange valve.
  • a cam carrier rotatably and axially displaceably arranged on a base camshaft.
  • the cam carrier consists of a tubular material, on which at least one cam is arranged, in which emerge from a common base circle axially offset several different cam tracks.
  • a locking device which consists of a arranged in the base camshaft locking means which engages in locking grooves, which worked out in the cam carrier are. According to the three cam tracks, the are formed on a cam, three locking grooves are worked out in the cam carrier.
  • the main disadvantage of this camshaft-centered arrangement of the locking device is that the basic camshaft and the cylinder head of the internal combustion engine are often made of different materials with different thermal expansion coefficients. As a result, the camshaft-centered latching device will not rest precisely either when the engine is cold or when the internal combustion engine is not operating. This effect can be amplified by inaccuracies in production, assembly or operational type so far that reliable operation of the internal combustion engine is not possible.
  • a cylinder-centered locking device for a basic camshaft with axially displaceable cam carriers is known from DE 101 48 243, the bearing of the basic camshaft in the cylinder head of the internal combustion engine being effected by at least one cam carrier bearing comprising the cam carrier.
  • the locking device consists of a arranged in the camshaft bearing locking means which engages in locking grooves, which are worked out in the cam carrier.
  • a cam carrier with two cams, each having two cam tracks two axially adjacent locking grooves are required in the cam carrier, in which engages the locking means.
  • the main disadvantage of this cylinder-head centered locking device is the high wear that occurs in the camshaft bearing, as a substantial part of the bearing sliding surfaces is spent on the locking grooves.
  • the base camshaft and the cam carrier are moved by the locking means to one side of the camshaft bearing. This locking device require a good supply of lubricant, which can not be guaranteed on the custom-fit and often polished Lagergleitclair.
  • the invention has for its object to provide a valve gear according to the features of the preamble of claim 1, wherein the cam carrier are reliably held in position after moving independently of thermal influences.
  • a first axial position of the cam carrier is defined by the fact that a first cam-holder-mounted stop surface abuts against a first cylinder head fixed stop surface.
  • a second axial position of the cam carrier is defined by the fact that a second cam carrier fixed abutment surface bears against a second stopper surface fixed to the cylinder head.
  • the first cylinder-stop-fixed abutment surface and the second cylinder-head-fixed abutment surface are side surfaces of the at least one cam carrier bearing comprising the cam carrier.
  • the means for applying an axial clamping force is formed by the base camshaft on the cam carrier as a locking device.
  • the locking device far a arranged in the camshaft, movably mounted in the radial direction locking means, wherein the locking means is pressed by a force in the radial direction outwardly preferably against the inner surface of the cam carrier.
  • at least two encircling and axially spaced latching grooves are formed on the inside of the cam carrier, wherein the latching grooves are approximately V-shaped in the cam carrier, and whereby both sides of the latching groove form a ramp for the latching means.
  • the locking grooves could basically also be formed in the basic camshaft, wherein the locking device would be arranged in the cam carrier.
  • the radially directed force is the restoring force of a spring element.
  • the locking means is a locking bolt, wherein the locking grooves facing side of the locking bolt is rounded.
  • the locking means is a locking ball.
  • a cam carrier is arranged on the at least one base camshaft for each cylinder of the internal combustion engine.
  • FIGS. 1 to 3 by way of example, there is shown a spark-ignited four-cylinder in-line engine having a cylinder crankcase 30 with a cylinder head 31 mounted thereon and with a cylinder head cover 33 formed in a known conventional manner.
  • Two intake and two exhaust valves are formed per cylinder in a known manner, not shown, wherein the intake valves of an intake camshaft and the exhaust valves are controlled by an exhaust camshaft 16 controlled in a known manner.
  • the intake camshafts and the exhaust camshaft 16 are aligned parallel to the engine longitudinal axis and rotatably mounted in the cylinder head 31 on both sides of the row of cylinders.
  • the exhaust camshaft 16 and the intake camshaft which consists of a base camshaft 1 and four cam carriers 2 are driven in a known, not shown manner.
  • FIG. 4 shows the inlet camshaft, on whose base camshaft 1 the four cam carriers 2 designed as hollow shafts are arranged axially spaced apart.
  • the cam pieces 2 are axially slidably mounted on the base camshaft 1 but rotatably mounted.
  • 5, 6 and 7 is at both ends of each cam carrier 2, a worm gear with a recess formed as an axial curve 10 and 11, respectively, which winds helically around the cam carrier axis.
  • On each cam carrier 2 two cams are arranged, with each cam from the same base circle axially offset two different cam tracks 6, 7 and 8, 9 emerge.
  • the cylindrical region of the lateral surface of each cam piece 2 located between the two cams is designed as a bearing surface for a camshaft bearing 3.
  • each cam carrier 2 is rotatably and axially displaceably mounted with this cylindrical bearing surface in a camshaft bearing block 3 of the cylinder head 31.
  • the two camshaft bearing block 3 facing end faces of the cams are formed as abutment surfaces 18 and 19. Accordingly, the cam facing end faces of the camshaft bearing block 3 are formed as a contact surface 17 and 20 respectively.
  • the distance between the two contact surfaces 17 and 18 of the cam is greater than the distance of the contact surfaces 19 and 20 of the camshaft bearing block third
  • the maximum distance, the contact surfaces 17 and 19, and the contact surfaces 18 and 20 may have from each other, the width of the cam tracks 6, 7, 8, 9, and the distance that a cam carrier by the axial curves 10 and 11 of the Worm gears can be moved.
  • the gas exchange valves 27, 28 of the internal combustion engine are actuated by the cam via cam follower 21, which are designed to reduce friction with a roller 23.
  • cam follower 21 Associated with the follower levers 21, 22 is in a conventional manner a trained in the cylinder head clearance compensation element 25 and 26 respectively.
  • the inside of the cam carrier 2 has two mutually parallel, axially spaced, the entire inner circumference of the cam carrier circumferential locking grooves 34, 35.
  • the locking grooves are approximately V-shaped, wherein the known of the V-shaped locking groove are rounded.
  • the two locking grooves 34, 35 are formed with radially outwardly to radially inwardly inclined groove walls forming the conical surfaces 36 and 37, wherein the conical surface 36 of the groove 34 has a pitch angle ⁇ to the axis of rotation of the camshaft 1 and the surface 37 of the groove 35 has a pitch angle ⁇ to the axis of rotation of the camshaft 1.
  • the distance between the conical surfaces 36 and 37 of the two grooves 34 and 35 to each other and the axial position of the blind bore 38 are coordinated so that when abutment of the contact surface 18 of the cam 8 on the contact surface 20 of the bearing block 3, the locking ball 40 at the conical surface 37 rests - as shown in Figure 7 - and that upon contact of the contact surface 19 of the cam 7 on the contact surface 17 of the cam bearing block 3, the locking ball 40 abuts against the conical surface 36 of the groove 34 - as shown in Figure 5 and Figure 6 is shown.
  • the required axial force in the cam carrier 2 is further introduced via the ball 40 according to the inclination ⁇ or ⁇ of the conical surfaces 36, 37.
  • the adjustment of the Hubventil putung of the operating state shown in Figures 5 and 6 in the operating state shown in Figure 7 is effected in that - as shown in Figure 6 - the driving pin 14 of an arranged in the cylinder head 31 electric actuator, which is associated with the axial curve 10 , engages in the formed as a recess axial cam 10.
  • the cam carrier 2 is displaced axially as far to the left by contact contact between the driver pin 14 and the groove walls of the axial cam 10 until the ball 40 prestressed by the spring 39 overflows into the groove 35 of the cam carrier 2. While the ball 40 rolls on the axial movement of the cam carrier 2 along the conical surface 37, the contact surface 18 of the moves Cam 8 on the contact surface 20 of the bearing block 3 and device with this in axial contact. The ball 40 is still in axial contact with the contact surface 37.
  • the cam carrier 2 is axially fixed.
  • the driving pin 14 is pulled out by means of the electric actuator 12 in a known manner again from the formed as a circumferential groove 10 axial curve.
  • the cam carrier 2 is fixed by the system between the contact surface 17 of the cam 7 and the contact surface 19 of the bearing block 3 on the one hand and by the system between cone 36 and locking ball 40 on the other hand axially in both directions.
  • the driving pin 15 is pulled out by means of the electric actuator 13 in a known manner from the circumferential groove of the axial cam 11.
  • angles .alpha. And .beta. are dimensioned in this way-depending on the individual requirement-that ensures the required axial fixing force in the operating positions for the Hubventil penetrateung and releasing the locking connection after engagement of the driving pins 14 and 15 in the circumferential grooves 10 and 11 during rotation the camshaft 1 is ensured in the operating direction.
  • the angles ⁇ and ⁇ are the same size between 15 ° and 45 °, for example, selected at 30 °.
  • the conical surfaces 36 and 37 along their axial extent each have a constant pitch angle ⁇ and ⁇
  • the four cam carrier 2 of the camshaft 1 shown in Figures 3 and 4 can be adjusted in this way individually by the associated actuators 12 and 13 between their two operating positions for Hubventlisteutation.
  • Such a configuration of the adjustment of the lift valve control is possible both for an intake camshaft 1 controlling only intake valves and also for an exhaust camshaft 16 controlling only exhaust valves. It is also possible to provide such a design also on a camshaft which controls both intake valves and exhaust valves.
  • Such a design of a controlled adjustment of the Hubventil thoroughlyung is also possible on internal combustion engines with more or fewer cylinders than the four cylinders shown in the embodiment. Such a design of the controlled adjustment of the Hubventil thoroughlyung is also possible on different cylinder arrangements of engines, such as in-line engines, V-engines or VR or W motors.
  • the illustrated Hubventil thoroughlyungsver ein is possible both spark-ignition and self-ignited internal combustion engines.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP04721147A 2003-03-21 2004-03-17 Ventiltrieb einer einen zylinderkopf aufweisenden brennkraftmaschine Expired - Lifetime EP1608849B1 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10312582 2003-03-21
DE10312582 2003-03-21
DE10312581 2003-03-21
DE10312581 2003-03-21
PCT/EP2004/002758 WO2004083611A1 (de) 2003-03-21 2004-03-17 Ventiltrieb einer einen zylinderkopf aufweisenden brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP1608849A1 EP1608849A1 (de) 2005-12-28
EP1608849B1 true EP1608849B1 (de) 2006-10-04

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Family Applications (1)

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EP04721147A Expired - Lifetime EP1608849B1 (de) 2003-03-21 2004-03-17 Ventiltrieb einer einen zylinderkopf aufweisenden brennkraftmaschine

Country Status (6)

Country Link
US (1) US7409938B2 (es)
EP (1) EP1608849B1 (es)
JP (1) JP4330618B2 (es)
DE (2) DE102004011586A1 (es)
ES (1) ES2274435T3 (es)
WO (1) WO2004083611A1 (es)

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DE102007010148A1 (de) 2007-03-02 2008-09-04 Audi Ag Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit einem axial beweglichen Lager
DE102007010149A1 (de) 2007-03-02 2008-09-04 Audi Ag Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit verschiebbarem Nockenträger und Doppelschneckentrieb
DE102007010150A1 (de) 2007-03-02 2008-09-04 Audi Ag Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit Nockenträgerarretierung von außen
DE102007016209A1 (de) 2007-04-04 2008-10-09 Audi Ag Reduktion Axialkräfte Grundnockenwelle
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DE102009005731A1 (de) 2009-01-22 2010-08-05 Audi Ag Ventiltrieb für Gaswechselventile mit geneigter und/oder Doppel-Kugelraste
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DE102010004579A1 (de) 2010-01-14 2011-07-21 Audi Ag, 85057 Ventiltrieb einer Brennkraftmaschine
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DE102014007189A1 (de) 2014-05-15 2015-11-19 Audi Ag Ventiltrieb für Gaswechselventile mit Nockenträger- und Grundwellenverzahnung im Rastmittelbereich

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JP5153562B2 (ja) * 2008-10-16 2013-02-27 株式会社オティックス 可変動弁機構
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JP5117475B2 (ja) * 2009-03-23 2013-01-16 株式会社オティックス 可変動弁機構
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JP5277047B2 (ja) * 2009-03-31 2013-08-28 本田技研工業株式会社 エンジンの可変動弁装置
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EP1608849A1 (de) 2005-12-28
DE102004011586A1 (de) 2004-10-07
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