EP1375847A2 - Commande variable de soupapes - Google Patents

Commande variable de soupapes Download PDF

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Publication number
EP1375847A2
EP1375847A2 EP03012206A EP03012206A EP1375847A2 EP 1375847 A2 EP1375847 A2 EP 1375847A2 EP 03012206 A EP03012206 A EP 03012206A EP 03012206 A EP03012206 A EP 03012206A EP 1375847 A2 EP1375847 A2 EP 1375847A2
Authority
EP
European Patent Office
Prior art keywords
intermediate member
engagement
transmission arrangement
cam
stroke
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.)
Withdrawn
Application number
EP03012206A
Other languages
German (de)
English (en)
Other versions
EP1375847A3 (fr
Inventor
Andreas Werler
Michael Seidel
Heiko Neukirchner
Lutz Stiegler
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.)
IAV GmbH Ingenieurgesellschaft Auto und Verkehr
Original Assignee
IAV GmbH Ingenieurgesellschaft Auto und Verkehr
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
Priority claimed from DE10061618A external-priority patent/DE10061618B4/de
Priority claimed from DE10226300A external-priority patent/DE10226300B4/de
Priority claimed from DE20220138U external-priority patent/DE20220138U1/de
Application filed by IAV GmbH Ingenieurgesellschaft Auto und Verkehr filed Critical IAV GmbH Ingenieurgesellschaft Auto und Verkehr
Publication of EP1375847A2 publication Critical patent/EP1375847A2/fr
Publication of EP1375847A3 publication Critical patent/EP1375847A3/fr
Withdrawn legal-status Critical Current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
    • F01L13/0021—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
    • F01L13/0026—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 by means of an eccentric
    • 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
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • 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
    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/20—Control lever and linkage systems
    • Y10T74/20576—Elements
    • Y10T74/20582—Levers

Definitions

  • the invention relates to a device for variable actuation of valves by means of cams, preferably for internal combustion engines according to the preamble of the main claim.
  • a generic device for the variable actuation of valves by means of cams is described with the following design.
  • a camshaft rotatably mounted in the cylinder head has a fixed position with respect to valves and their associated stroke transmission arrangement in the form of pivoting levers, which preferably act with a play compensation element on the valves closing by means of spring force.
  • An element which is variable in its position for adjusting the valve stroke is arranged so as to be pivotable about an axis which is fixedly positioned in the cylinder head and each has a supporting and control cam which extends one after the other on the circumference.
  • An intermediate member is non-positively supported on the element, which can change its position, while slidingly during the lifting movement. It is in engagement with its U-shaped inner contour on both sides on the outer contour of the support or control curve, is thus pivotably guided and is also in engagement with the cam and the stroke transmission arrangement assigned to the valve.
  • the invention has for its object a device for variable actuation of valves of the generic type to improve cheap kinematic Ratios, reduced mechanical stress and a compact To achieve the design of the hub-transmitting link.
  • control cam on the side facing the stroke transmission arrangement is arranged in a position for zero or little stroke parallel to it or running slightly inclined, there is in principle a favorable loading of the intermediate member by the forces for actuating the valve.
  • a kinematic and for the mechanical stress of the pontic favorable execution can also be achieved in that the intermediate member during of the opening stroke through the opposing engagement areas on the Control curve and the stroke transmission arrangement is pulled.
  • a camshaft 1 possibly driven by the crankshaft via an angle adjustment device, is rotatably mounted in the cylinder head ZK with a fixed axial position and has a fixed position with respect to valves 2 and their associated stroke transmission arrangement 3.
  • the valves 2 arranged in the cylinder head ZK and closing by means of spring force are each assigned a position-controlled stroke transmission arrangement 3, which is provided in the usual way with a play compensation element 31.
  • An element 4 that is variable in its position for valve stroke adjustment is arranged in the cylinder head ZK in a stationary manner, but is pivotable about the fixedly positioned pivot axis A4.
  • An intermediate member 5 is in engagement with a cam 11 of the camshaft 1 mounted in the cylinder head ZK and also via its outer contour 52 with the stroke transmission arrangement 3 associated with the valve 2, in this case a roller lever 32. Furthermore, it is supported on the element 4, which is variable in its position, with its opening inner contour 51 in a force-locking manner and is pivotably guided by it.
  • the element 4 has a support curve 41 and a control curve 42, these curves 41; 42 extend one after the other on the circumference.
  • the intermediate member 5 moves in a sliding or rolling manner on the support 41 and the control cam 42. This ensures prismatic support for all possible positions or positions of the intermediate member 5.
  • the intermediate member 5 is always under the action of the force of a spring F, the direction of action of which keeps the intermediate member 5 in engagement with the cam 11 and the variable element 4.
  • a spring F which is designed as a spiral spiral spring, engages with its end FE5 and is preferably arranged to extend around the pivot axis A4. It continues to be supported directly or indirectly against the cylinder head ZK.
  • a spring F is shown, which is guided in the cylinder head ZK and is effective in the same way as previously described.
  • the control curve 42 on the variable element 4 is arranged on the side facing the stroke transmission arrangement 3 and runs parallel or slightly inclined to the stroke transmission arrangement 3, see FIG. 6.
  • the lines of engagement EL between the control cam 42 and the intermediate member 5 and the stroke transmission arrangement 3 and the intermediate member 5 should advantageously extend in the area in the area of movement that extends around the connecting line VL between the pivot axis A4 of the variable element 4 and the engagement line EL between the stroke transmission arrangement 3 and the intermediate member 5 extends, see FIG. 7.
  • a favorable mechanical load on the intermediate member 5 results if the intermediate member 5 is pulled through the opposing engagement areas on the control cam 42 and the stroke transmission arrangement 3 during the opening stroke, see FIGS. 1 and 2.
  • the line of engagement between the stroke transmission arrangement 3 and the intermediate member 5 should advantageously run between the lines of engagement of the intermediate member 5 on the variable element 4.
  • the play compensation element 31 introduces a force and thus a moment into the intermediate member 5 via the stroke transmission arrangement 3, which ensures a constant contact of the intermediate member 5 with the variable element 4.
  • a rotatably mounted roller 53; 54 arranged, as shown in Fig. 2.
  • a substantial reduction in friction losses can be achieved. Due to the relatively lower forces compared to the aforementioned engagement areas, the intermediate member 5 can be in sliding engagement with the support curve 41.
  • a lubrication device S should be assigned to this engagement area.
  • Such a design is structurally simple and limits the masses that can be moved in the kinematic system.
  • the outer contour of the support curve 41 of the element 4, which is variable in its position, is formed in a region which is in engagement with the cam 11 during the passage of the base circle by an arc around the pivot axis A4.
  • the circular arc in the region of the stroke can merge into an increasing contour 41A, which together with the control curve 42 influences the movement of the intermediate member 5 for generating the stroke from the valve 2, see FIG. 2.
  • the variable element 4 can be mounted in an advantageous and stable manner with a circle segment 40 in the cylinder head ZK, which is arranged opposite the area of engagement of the intermediate member 5 on the control curve 42, see FIG. 2.
  • a kinematically similar device as in Fig. 1, but simplified and schematic, is shown.
  • the stroke transmission arrangement 3 can of course also be provided with a play compensation element 31, as shown in FIG. 1.
  • the element 4, which is variable in its position, has a support 41 and a control curve 42, each extending one after the other on the circumference. On these two curves 41; 42, the intermediate member 5 with its opening inner contour 51 is non-positively supported during the lifting movement. This always results in prismatic support with different positions of the intermediate member 5.
  • the outer contour of the support curve 41 of the element 4, which is variable in its position, forms an arc around the pivot axis A4.
  • the intermediate member 5 is under the action of a spring F, which is advantageously supported in the area of the roller 53 in a sliding manner on the intermediate member 5 and is supported on the cylinder head ZK. 4, the device according to the invention is shown with the valve in the closed position.
  • the respective engagement planes on the intermediate member 5 between the control cam 42 and the stroke transmission arrangement 3 run approximately parallel to one another, the engagement lines EL lying on the connecting line VL between the swivel axis A4 and the axis A33 of a roller 33 on the swivel or roller lever 32.
  • a structurally advantageous design results if the support of the stroke transmission arrangement 3 is arranged in an area under the camshaft 1, but this is not shown separately.
  • Fig. 3 shows a valve train in the basic setting with the valve closed.
  • the Roller 53 still rolls on the base circle of cam 11. With further rotation this aforementioned position counterclockwise, the roller 53 of the Elevation of the cam 11 steadily in the direction of the valve opening until the outermost cam contour, see Fig. 5.
  • the intermediate member 5 slides with the line contact on the support 41 and the control curve 42 and in the direction of the longitudinal extent via the roller 33 of the stroke transmission arrangement 3.
  • the position shown in FIG. 5 arises with Fully open valve - maximum stroke - in the mechanism.
  • a variably adjustable opening of the valve can be achieved.
  • Fig. 6 the setting for a permanently closed valve is shown.
  • the variable element 4 with the support 41 and the control cam 42 has been changed in its rotational position compared to FIG. 5, with which another area on the control cam 42 for the engagement of the intermediate member 5 during the movement initiated by the cam 11 is swept, whereby however, no stroke of the valve 2 results.
  • the cam 11 rotates counterclockwise from the effective range of the base circle, the roller 53 and thus the intermediate member 5 are continuously urged by the elevation of the cam 11 in the direction of valve opening until the highest cam contour is reached.
  • the now pivoted-back contour of the control cam 42 causes the intermediate member 5 to slide only in the direction of the longitudinal extent over the rocker or roller lever 32, without forcing it towards the valve 2.
  • the intermediate member 5 pivots on a circular arc contour KB, which extends around the pivot axis A4 of the variable element 4, between this circular arc contour KB and the rocker or roller lever 32, see FIG. 6. From the comparison of the position of the end FE5 of the spring F in Figures 4; 5 and 6, the respective positions of the intermediate member 5 can be seen when the cam 11 passes through the base circle and at the maximum cam stroke.
  • a valve train according to the invention is shown in the closed position of the valve during the passage of the cam base circle.
  • the intermediate member 5 has a roller 54 which is in engagement with the control cam 42 of the element 4 which is variable in its position.
  • the line of engagement EL between the intermediate member 5 and the stroke transmission arrangement 3 lies on the connecting line VL between the pivot axis A4 and the axis A33 of the roller 33 on the stroke transmission arrangement 3.
  • the engagement planes EE on the intermediate member 5 between the control curve 42 and the stroke transmission arrangement 3 run slightly inclined to one another, thereby the line of engagement EL between the roller 54 and the cam 42 lies in an area near the connecting line VL.
  • the support curve 41 is radially set back and axially offset with respect to the control curve 42. However, this is irrelevant to the inventive features of this document.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP03012206A 2000-12-11 2003-06-06 Commande variable de soupapes Withdrawn EP1375847A3 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10061618A DE10061618B4 (de) 2000-12-11 2000-12-11 Einrichtung zur variablen Betätigung von Ventilen mittels Nocken für Verbrennungsmotoren
DE10226300A DE10226300B4 (de) 2002-06-10 2002-06-10 Einrichtung zur variablen Betätigung von Ventilen mittels Nocken für Verbrennungsmotoren
DE10226300 2002-06-10
DE20220138U 2002-12-20
DE20220138U DE20220138U1 (de) 2002-12-20 2002-12-20 Ventiltrieb mit Nocken zur variablen Betätigung von Ventilen für Verbrennungsmotoren

Publications (2)

Publication Number Publication Date
EP1375847A2 true EP1375847A2 (fr) 2004-01-02
EP1375847A3 EP1375847A3 (fr) 2006-08-23

Family

ID=29713128

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03012206A Withdrawn EP1375847A3 (fr) 2000-12-11 2003-06-06 Commande variable de soupapes

Country Status (2)

Country Link
US (1) US6955146B2 (fr)
EP (1) EP1375847A3 (fr)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004008389A1 (de) * 2004-02-20 2005-09-08 Bayerische Motoren Werke Ag Hubvariabler Ventiltrieb für eine Brennkraftmaschine
DE102004011639A1 (de) * 2004-03-10 2005-09-29 Ina-Schaeffler Kg Variable mechanische Ventiltriebsteuerung
DE102005035315B4 (de) * 2005-07-28 2007-05-10 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Variabler Ventiltrieb für Verbrennungskraftmaschinen
DE102005035314B4 (de) * 2005-07-28 2013-03-14 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Ventiltrieb für Ladungswechselventile von Viertaktverbrennungsmotoren
JP2007127117A (ja) * 2005-10-04 2007-05-24 Masaaki Yoshikawa ４ストローク内燃機関の動弁系装置
KR100667394B1 (ko) * 2005-11-15 2007-01-10 현대자동차주식회사 엔진의 연속 가변 밸브 리프트 장치
US7121241B1 (en) * 2006-01-10 2006-10-17 Eaton Corporation Valve control system including deactivating rocker arm
KR100868209B1 (ko) * 2006-11-16 2008-11-11 현대자동차주식회사 연속 가변 밸브 리프트 장치
EP2025888A1 (fr) * 2007-08-06 2009-02-18 Iveco S.p.A. Dispositif d'actionnement de frein de moteur de décompression dans un moteur à combustion interne doté de poussoirs hydrauliques
KR100909497B1 (ko) * 2007-09-19 2009-07-27 고려대학교 산학협력단 엔진의 연속 가변 밸브 리프트 장치
KR20090056602A (ko) * 2007-11-30 2009-06-03 현대자동차주식회사 가변 밸브 리프트 장치
CN106523067A (zh) * 2016-12-20 2017-03-22 江苏三能动力总成有限公司 一种发动机连续可变气门升程结构

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10061618A1 (de) 2000-12-11 2002-06-27 Iav Gmbh Einrichtung zur variablen Betätigung von Ventilen mittels Nocken, vorzugsweise für Verbrennungsmotoren

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US2934052A (en) * 1958-11-17 1960-04-26 Irvin R Longenecker Valve operating mechanism
DE2629554A1 (de) 1976-07-01 1978-01-12 Daimler Benz Ag Lastregelung fuer gemischverdichtende brennkraftmaschinen mit ventilsteuerung
JPS6226562Y2 (fr) * 1981-03-10 1987-07-08
FR2519375B1 (fr) * 1981-12-31 1986-07-11 Baguena Michel Distribution variable pour moteur a quatre temps
US4723515A (en) * 1983-05-05 1988-02-09 Investment Rarities Incorporated Mechanism utilizing a single rocker arm for controlling an internal combustion engine valve
GB8723256D0 (en) * 1987-10-03 1987-11-04 Jaguar Cars Valve mechanisms
DE3833540A1 (de) 1988-10-01 1990-04-12 Peter Prof Dr Ing Kuhn Vorrichtung zur betaetigung der ventile an verbrennungsmotoren mit veraenderlicher ventilerhebungskurve
US5205247A (en) * 1992-01-29 1993-04-27 Hoffman Christopher J Infinitely variable lift cam follower with consistent dwell position
DE4326331A1 (de) * 1992-07-15 1995-02-09 Bayerische Motoren Werke Ag Ventiltrieb einer Brennkraftmaschine
GB9320204D0 (en) * 1993-09-30 1993-11-17 Lotus Car Valve operating mechanism for internal combustion engines
DE19913742A1 (de) 1999-03-26 2000-09-28 Bayerische Motoren Werke Ag Vorrichtung zur Hubverstellung eines Gaswechselventils im Zylinderkopf einer Brennkraftmaschine
GB2357131A (en) * 1999-12-09 2001-06-13 Mechadyne Internat Plc Valve actuating mechanism
DE10006016B4 (de) * 2000-02-11 2009-08-06 Schaeffler Kg Variabler Ventiltrieb zur Laststeuerung einer fremdgezündeten Brennkraftmaschine
DE10006015B4 (de) * 2000-02-11 2009-09-17 Schaeffler Kg Variabler Ventiltrieb zur Laststeuerung einer fremdgezündeten Brennkraftmaschine
DE10119686B4 (de) * 2001-04-20 2006-03-30 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Variabler Ventiltrieb
DE10123186A1 (de) 2001-05-12 2002-11-14 Bayerische Motoren Werke Ag Ventiltrieb-Vorrichtung zur variablen Hubverstellung eines Gaswechselventils einer Brennkraftmaschine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10061618A1 (de) 2000-12-11 2002-06-27 Iav Gmbh Einrichtung zur variablen Betätigung von Ventilen mittels Nocken, vorzugsweise für Verbrennungsmotoren

Also Published As

Publication number Publication date
EP1375847A3 (fr) 2006-08-23
US6955146B2 (en) 2005-10-18
US20030226530A1 (en) 2003-12-11

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Effective date: 20101221