EP2702253B1 - Ventiltrieb für gaswechselventile einer brennkraftmaschine mit einer grundnockenwelle und zwischen drehlagern der grundnockenwelle in zwei oder mehr diskrete verschiebestellungen verschiebbaren nockenträgern - Google Patents

Ventiltrieb für gaswechselventile einer brennkraftmaschine mit einer grundnockenwelle und zwischen drehlagern der grundnockenwelle in zwei oder mehr diskrete verschiebestellungen verschiebbaren nockenträgern Download PDF

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Publication number
EP2702253B1
EP2702253B1 EP12716256.8A EP12716256A EP2702253B1 EP 2702253 B1 EP2702253 B1 EP 2702253B1 EP 12716256 A EP12716256 A EP 12716256A EP 2702253 B1 EP2702253 B1 EP 2702253B1
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EP
European Patent Office
Prior art keywords
cam
valve train
cam carrier
train according
carrier
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.)
Active
Application number
EP12716256.8A
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German (de)
English (en)
French (fr)
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EP2702253A1 (de
Inventor
Michael Gross
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
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Audi AG
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Filing date
Publication date
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Publication of EP2702253A1 publication Critical patent/EP2702253A1/de
Application granted granted Critical
Publication of EP2702253B1 publication Critical patent/EP2702253B1/de
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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
    • F01L1/047—Camshafts
    • F01L1/053—Camshafts overhead type
    • 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
    • F01L1/185—Overhead end-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
    • F01L1/22—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
    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0471—Assembled camshafts
    • F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
    • 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
    • F01L2001/0476—Camshaft bearings
    • 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 for gas exchange valves of an internal combustion engine according to the preamble of claim 1, as well as an internal combustion engine with such a valve train.
  • thermodynamic properties of internal combustion engines mechanical devices are known which influence the working cycle of the valve train and, for example, allow a speed-dependent change in the opening times and / or the stroke of gas exchange valves of cylinders of the internal combustion engine.
  • a valve train in which a plurality of cam carrier rotatably and axially displaceably arranged on a base camshaft.
  • two axially offset cam groups are provided on each cam carrier, each of which has two cams with different cam profiles.
  • the axial displacement of the cam carrier on the base camshaft is carried out by means of two worm gears, which are arranged at an axial distance from each other.
  • Each worm drive comprises an actuator mounted in the cylinder head housing of the internal combustion engine with an extendable driver pin engageable with an opposing cam or gate on the cam carrier.
  • the cam or shift gate has a left-handed helical groove in one of the two worm gears and a right-handed helical groove in the other of the two worm gears, so that the cam carrier can be moved back and forth between the two discrete shift positions by actuating the corresponding actuator.
  • In each of the two displacement positions of the cam carrier is pressed from one side against a arranged between the cam groups stationary pivot bearing in which the cam carrier rotatably mounted is.
  • the cam carrier is held in each of the two displacement positions by a ball inserted into a bore of the base camshaft locking device which is pressed by a spring against an inclined edge on the inner circumference of the cam carrier and thereby presses one of the cam groups from one side against the pivot bearing.
  • each cam carrier has two cam groups, each with three cams and is displaceable between three discrete shift positions.
  • the cam carrier is held in the three displacement positions by a stationary mounted in the housing of the internal combustion engine locking device which acts on a together with the cam carrier axially displaceable pivot bearing.
  • the spring-loaded ball of the locking device engages in the three displacement positions in three recesses of a mounted on the outside of the rotary bearing locking bar, which are separated by two projections.
  • the ball In the two outer displacement positions, the ball is pressed in each case against an outer edge of one of the two projections in order to press the cam carrier against a stationary stop of the cylinder head housing.
  • the ball In the middle displacement position, the ball engages in a complementary shaped recess of the locking bar between the two projections.
  • the invention has the object to improve a valve train of the type mentioned in that a movable pivot bearing is unnecessary and less space is needed.
  • the invention is based on the idea of arranging the fixed pivot bearings for rotatably supporting the camshaft and the stops serving to fix the two outer discrete shift positions not in the region of the cam carriers but beyond the front ends of the cam carriers, ie between adjacent cam carriers.
  • the required space can be considerably reduced.
  • the spring-loaded ball in these displacement positions expediently engages in an opposite recess on the inner circumference of the cam carrier, which is arranged between the two recesses with the oblique flanks.
  • the cam carrier has on its inner circumference at least three axially successively arranged recesses, of which at least the two outer are each delimited by an oblique flank and are separated by projections of at least one interposed recess.
  • the spring-loaded ball successively moves over the projections and through the inner recess (s).
  • all recesses are preferably formed as grooves which rotate around the inner circumference of the cam carrier, wherein the axial center distance of the recesses corresponds to the axial center distance of the associated cam or cam profiles.
  • the devices for axially displacing the cam carrier preferably comprise a worm drive with at least one stationary actuator, from which at least one driver can extend and engage in an opposite helical groove of a cam or shift link of the cam carrier.
  • the cam carrier is moved accordingly on the base camshaft to the left or to the right.
  • the or each cam carrier expediently has two cam groups, which are arranged at an axial distance corresponding to the distance between the valves. Since due to the storage of the basic camshaft between adjacent cam carriers in the region between the two cam groups of each cam carrier not as in the prior art according to EP 1 608 849 B1 or DE 10 2007 010 150 A1 a pivot bearing must be provided, the curve or shift gate of the worm drive according to a further preferred embodiment of the invention can be arranged between the two cam groups each cam carrier, which allows a significant reduction in the length of each cam carrier. In addition, unlike in this prior art, a single worm gear with a continuous curve or shift gate for displacement of the cam carrier is sufficient.
  • the curve or shift gate and the at least one actuator of the means for axially displacing the cam carrier in their execution can be arbitrarily adapted to the axial distance of the valves or to the available space.
  • the cam carrier is pressed in the two outer displacement positions below the base camshaft against the pivot bearing or against a bearing block of the pivot bearing, which above the camshaft sufficient space for the at least one actuator is provided.
  • a further advantageous embodiment of the invention provides that the central cam of each cam group is slightly wider than the two outer cam of each cam group, since the caused by thermal expansion of the cylinder head and the basic cam shaft tolerances of the displacement there are greater than in the outer cam.
  • valve train 1 for pairs of intake valves 2 of cylinders (not shown) of an internal combustion engine with an overhead, in rotary bearings 3 of a cylinder head housing (not shown) of the engine rotatably mounted camshaft base 4, as well as several, on the base camshaft 4 axially displaceable cam carriers 5, the stroke and / or the opening times of the intake valves 2 of each cylinder can be adjusted independently of the stroke and / or the opening times of the intake valves 2 of the remaining cylinders.
  • the valve train 1 comprises, for each pair of inlet valves 2, one of the displaceable cam carriers 5 which is non-rotatably connected to the base camshaft 4 and has two cam groups 6, 7 arranged at an axial distance from each other.
  • Each of the two cam groups 6, 7 interacts with a roller 8 of a pivotally mounted roller cam follower 9 of one of the valves 2.
  • About the role 8 is an in Fig. 1 shown, at the lower end with a valve plate 10 'provided valve member 10 is actuated, which opposes the opening of the respective valve 2 against the force of a valve spring 11 (FIG. Fig. 2 ) can be pushed down in the cylinder head.
  • the valve train 1 also includes a valve for each of the valves 2 also in Fig. 1 illustrated hydraulic valve clearance compensation element 12th
  • Each of the two cam groups 6, 7 of each cam carrier 5 has three cams 13, 14, 15 which project beyond the outer circumference of the cam carrier 5 on one side and have different cam profiles or cam contours.
  • the degree of projection of the cams 13, 14, 15 over the base circle portion 16 varies according to the desired lift height of the valve member 10, while the angular position of a vertex of the cams 13, 14, 15 in the direction of rotation of the base camshaft 4 corresponding to the desired time of maximum opening of the valve 2 varies.
  • the cam profiles or cam contours of the cams 13, 14, 15 of the two cam groups 6, 7 can each be shaped and / or dimensioned differently. In both cam groups 6, 7, the central cam 14 is slightly wider than the two outer cams 13 and 15, as will be explained later.
  • the three cams 13, 14, 15 of both cam groups 6, 7 can be brought by axial displacement of the cam carrier 5 on the base camshaft 4 between three discrete shift positions either with the roller 8 of the finger lever 9 of the cam group 6 and 7 associated valve 2 in abutting contact ,
  • the three displacement positions are in Fig. 2 shown by the example of three cam carriers 5.
  • the left cam carrier 5 is located there in its right outer displacement position in which it rests with its right front end 17 from the left against a bearing block 18 of the adjacent pivot bearing 3, which is arranged between the left and the central cam carrier 5, and in which Rolls 8 of the drag lever 9 of the two valves 2 each with the left outer cam 13 of the cam groups 6, 7 come into abutting contact.
  • the cam carrier 5 shown in the middle is in its middle displacement position, in which its two front ends 17 each have an axial distance from the bearing chairs 18 of the two adjacent, both sides of the cam carrier 5 arranged pivot bearing 3 and in which the rollers 8 of the cam followers 9 of two valves 2 with the central cam 14 of the two cam groups 6, 7 come into abutting contact.
  • the right cam carrier 5 is in its left outer displacement position in which he rests with his left front end 16 from the right against the bearing block 18 of the adjacent pivot bearing 3 between the middle and the right cam carrier 5 and in which the rollers 8 of the drag lever 9 of two valves 2 in each case with the right outer cam 15 of the cam groups 6, 7 come into abutting contact.
  • Fig. 1 only one cam carrier 5, which is in its middle displacement position.
  • an inner longitudinal toothing 19 (FIGS. Fig. 2 ), which with a complementary external longitudinal toothing 20 (FIG. Fig. 1 ) meshes on a part of the basic camshaft 4.
  • the axial displacement of the cam carrier 5 on the base camshaft 4 for adjusting the stroke or opening times of the intake valves 2 takes place as needed and is always carried out when the base circle portion 16 of the cam groups 6, 7 during a rotation angle of the base camshaft 4 of about 180 degrees rolls 8 of the cam follower 9 is opposite.
  • the extent of the axial displacement of a cam carrier 5 between two adjacent displacement positions corresponds to the center distance of adjacent cams 13, 14 and 14, 15 of the cam groups 6, 7.
  • the cam carrier 5 can be moved as needed in any of the three displacement positions, a single worm gear 21 is provided for each cam carrier 5.
  • the worm drive 21 comprises a single cam or gate 22, which is arranged approximately in the axial center of the cam carrier 5 between the two cam groups 6, 7 or between the two valves 2, and a fixedly mounted in the cylinder head housing actuator 23, the Fig. 1 is shown only schematically.
  • the actuator 23 may have one or more driving pins 24 which extend either from the actuator 23 and can be brought with its free end with an opposite groove 25 of the cam or switching gate 22 into engagement with the cam carrier 5 each to the Center distance between two adjacent cams 13, 14 and 14, 15 to move in one of the three discrete shift positions.
  • the outer diameter of the cam or switching gate 22 is dimensioned so that the cam or switching gate 22 at a displacement of the cam carrier 5 from the middle displacement position in one of the two outer displacement positions in the axial direction with one of two brackets 37 (FIGS. Fig. 2 ) overlaps, of which the roller 8 of the roller cam follower 9 is rotatably supported.
  • each locking device 26 is provided for each cam carrier 5.
  • each locking device 26 comprises a ball 28 inserted into a blind blind bore 27 of the base camshaft 4 and extending from between the ground the blind hole 27 and the ball 28 arranged prestressed helical compression spring 29 is pressed radially against an opposite inner circumference of the cam carrier 5.
  • the inner circumference of the cam carrier 5 is not provided with the inner longitudinal teeth 19, but with three circumferential grooves 30, 31, 32 arranged in the axial direction one behind the other are.
  • the central groove 31 has a concave rounded groove cross-section adapted to the shape of the ball and is separated from the adjacent outer grooves 30, 32 on both sides by a projection 33, 34 rounded in cross-section.
  • the ball 28 is pressed in the middle displacement position of the cam carrier 5 of the spring 29 in the middle groove 31, so that the cam carrier 5 alone by the latching engagement of the ball 29 in the recess 31 acting as a groove 31 in this middle shift position is recorded.
  • the two outer grooves 30, 32 are bounded on their side facing the middle groove 31 each by an oblique edge 35, 36.
  • the ball 28 is pressed by the helical compression spring 29 when the cam carrier 5 abuts with a front end 16 in the direction of movement against the bearing block 18 of the adjacent pivot bearing 3, which limits the axial displacement of the cam carrier 5 in the respective outer displacement position ,
  • This axial force component ensures that the cam carrier 5 is pressed in each of the two outer displacement positions with one of its front ends 16 against the bearing seat 18 of the adjacent pivot bearing 3 in the direction of movement and thereby in one defined position is held, in which the cam profile of one of the two outer cam 13, 15 of the roller 8 of the roller cam follower 9 exactly opposite.
  • the width of the two outer cams 13, 15 can each be made slightly narrower than the width of the middle cam 14.
  • the central groove 31 does not necessarily have a matched to the shape of the ball 28 concave rounded groove cross-section, but may for example also have a limited by two flat oblique edges triangular groove cross-section, in which case the located in the central groove 31 ball 28 is pressed by the spring 29 at two points against the two flanks.

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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)
EP12716256.8A 2011-04-23 2012-04-20 Ventiltrieb für gaswechselventile einer brennkraftmaschine mit einer grundnockenwelle und zwischen drehlagern der grundnockenwelle in zwei oder mehr diskrete verschiebestellungen verschiebbaren nockenträgern Active EP2702253B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110018503 DE102011018503A1 (de) 2011-04-23 2011-04-23 Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit einer Grundnockenwelle und zwischen Drehlagern der Grundnockenwelle in zwei oder mehr diskrete Verschiebestellungen verschiebbaren Nockenträgern
PCT/EP2012/001711 WO2012146361A1 (de) 2011-04-23 2012-04-20 Ventiltrieb für gaswechselventile einer brennkraftmaschine mit einer grundnockenwelle und zwischen drehlagern der grundnockenwelle in zwei oder mehr diskrete verschiebestellungen verschiebbaren nockenträgern

Publications (2)

Publication Number Publication Date
EP2702253A1 EP2702253A1 (de) 2014-03-05
EP2702253B1 true EP2702253B1 (de) 2015-03-18

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EP12716256.8A Active EP2702253B1 (de) 2011-04-23 2012-04-20 Ventiltrieb für gaswechselventile einer brennkraftmaschine mit einer grundnockenwelle und zwischen drehlagern der grundnockenwelle in zwei oder mehr diskrete verschiebestellungen verschiebbaren nockenträgern

Country Status (4)

Country Link
EP (1) EP2702253B1 (ja)
JP (1) JP5901742B2 (ja)
DE (1) DE102011018503A1 (ja)
WO (1) WO2012146361A1 (ja)

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DE102012209026A1 (de) * 2012-05-30 2013-12-05 Schaeffler Technologies AG & Co. KG Schiebenockenelement für Hubkolbenbrennkraftmaschinen
JP5928835B2 (ja) * 2013-07-03 2016-06-01 株式会社デンソー バルブリフト調整装置
DE102015101793B4 (de) 2014-02-14 2022-03-03 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Verbrennungsmotor mit gleitender Nockenwelle
US9500104B2 (en) 2014-09-30 2016-11-22 Hyundai Motor Company Variable valve lift apparatus
DE102014225286A1 (de) * 2014-12-09 2016-06-09 Mahle International Gmbh Nockenwelle
US9518644B1 (en) * 2015-05-26 2016-12-13 GM Global Technology Operations LLC Sliding camshaft with improved compressive residual stress
KR101655221B1 (ko) 2015-11-27 2016-09-07 현대자동차 주식회사 다단 가변 밸브 리프트 장치
KR101655223B1 (ko) 2015-11-27 2016-09-07 현대자동차 주식회사 다단 가변 밸브 리프트 장치
KR102335326B1 (ko) * 2017-05-16 2021-12-03 현대자동차 주식회사 다단 가변 밸브 리프트 장치
KR102310415B1 (ko) * 2017-09-07 2021-10-08 현대자동차 주식회사 다단 가변 밸브 리프트 장치
DE102017219287A1 (de) * 2017-10-26 2019-05-02 Volkswagen Aktiengesellschaft Ventiltrieb für ein Ventil einer Brennkraftmaschine mit einer Arretierungsvorrichtung und einer Verspannungsvorrichtung
DE102021204314A1 (de) * 2021-04-29 2022-11-03 Mahle International Gmbh Schiebenockensystem für eine Brennkraftmaschine

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DE102004011586A1 (de) 2003-03-21 2004-10-07 Audi Ag Ventiltrieb einer einen Zylinderkopf aufweisenden Brennkraftmaschine
DE502004008185D1 (de) * 2003-07-19 2008-11-20 Porsche Ag Ventiltrieb für eine Brennkraftmaschine
DE102007010150A1 (de) 2007-03-02 2008-09-04 Audi Ag Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit Nockenträgerarretierung von außen
DE102007010149A1 (de) * 2007-03-02 2008-09-04 Audi Ag Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit verschiebbarem Nockenträger und Doppelschneckentrieb
DE102007040677A1 (de) * 2007-08-29 2009-03-05 Schaeffler Kg Brennkraftmaschine mit variablem Gaswechselventiltrieb
DE102007061353A1 (de) * 2007-12-21 2009-06-25 Audi Ag Ventiltrieb für Gaswechselventile einer Brennkraftmaschine mit einem verschiebbarem Nockenträger mit Endlosnut
DE102008035935A1 (de) * 2008-07-31 2010-02-11 Audi Ag Zahnwellenverbindung und Ventiltrieb mit Zahnwellenverbindung zwischen einer Nockenwelle und verschiebbaren Nockenträgern
DE102009030373A1 (de) * 2009-06-25 2010-12-30 Schaeffler Technologies Gmbh & Co. Kg Ventiltrieb einer Brennkraftmaschine

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Publication number Publication date
JP2014512486A (ja) 2014-05-22
JP5901742B2 (ja) 2016-04-13
DE102011018503A1 (de) 2012-10-25
WO2012146361A1 (de) 2012-11-01
EP2702253A1 (de) 2014-03-05

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