EP2151548A1 - Actionneur de soupapes pour un moteur à combustion interne particulièrement avec frein à décompression - Google Patents

Actionneur de soupapes pour un moteur à combustion interne particulièrement avec frein à décompression Download PDF

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Publication number
EP2151548A1
EP2151548A1 EP09164653A EP09164653A EP2151548A1 EP 2151548 A1 EP2151548 A1 EP 2151548A1 EP 09164653 A EP09164653 A EP 09164653A EP 09164653 A EP09164653 A EP 09164653A EP 2151548 A1 EP2151548 A1 EP 2151548A1
Authority
EP
European Patent Office
Prior art keywords
valve
lever
rocker arm
gas exchange
compensation element
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
EP09164653A
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German (de)
English (en)
Other versions
EP2151548B1 (fr
Inventor
Oliver Schnell
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.)
Schaeffler Technologies AG and Co KG
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Schaeffler KG
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Publication date
Application filed by Schaeffler KG filed Critical Schaeffler KG
Publication of EP2151548A1 publication Critical patent/EP2151548A1/fr
Application granted granted Critical
Publication of EP2151548B1 publication Critical patent/EP2151548B1/fr
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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
    • 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
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking

Definitions

  • the invention relates to a valve train for an internal combustion engine, in particular with a decompression brake.
  • the valve train comprises a camshaft with a cam, a tilting or rocking lever for transmitting the cam lift to a gas exchange valve, a tilting or rocker arm supporting swivel bearing and arranged in the power flow between the cam and the gas exchange valve hydraulic valve clearance compensation element.
  • valve engines for decompression brake internal combustion engines usually large volume diesel engines for the commercial vehicle sector - it is envisaged to reopen one or all exhaust valves of a cylinder in the course of the compression stroke during engine braking operation to significantly increase the charge cycle work in favor of negative engine performance.
  • the re-exhaust opening requires as a function of its timing significantly higher valve actuation forces, since the exhaust valves must open against the compression pressure and sometimes against the compression end pressure in the cylinder.
  • the lash adjuster As in the considered as generic US 7,392,772 B2 proposed in such valve trains, the compensation of the valve clearance by means of a hydraulic valve lash adjuster automatically and continuously, the lash adjuster is to be arranged as an alternative to a valve lash mechanically adjusting screw between the valve-side lever portion of a rocker arm disclosed there and the gas exchange valve.
  • this positioning of the lash adjuster may be problematic in that the high valve actuation forces during engine braking operation cause excessive lessening of the lash adjuster due to squeezing hydraulic fluid from its high pressure space.
  • the present invention is therefore based on the object to ensure the operability of a valve train of the type mentioned. Accordingly, it should also be possible in the case of very high valve actuation forces to equip the valve train with a hydraulic valve clearance compensation element of the known type for automatic and continuous adjustment of the valve clearance.
  • valve lash adjuster should be arranged stationarily in the internal combustion engine and the valve train further comprise a secondary lever with a first lever portion and a second lever portion.
  • the secondary lever is articulated between the lever sections on a tilting or rocker arm formed lever support, is supported by the first lever portion on the valve clearance compensation element and operated with the second lever portion of the gas exchange valve.
  • the effective lever arm of the first lever portion is significantly larger than the effective lever arm of the second lever portion.
  • the invention provides for a displacement of the valve lash adjuster in such a way that the valve lash adjuster no longer - as suggested in the cited prior art - moved with the gas exchange valve and the actuation forces is directly exposed, but a force-reducing lever ratio stationary in the Power flow between cam and gas exchange valve is integrated.
  • the effective lever arms have a transmission ratio of at least 2: 1.
  • the valve lash adjuster would be loaded at a valve actuation force of 15 kN and a gear ratio of 3: 1 only with a force of 5 kN.
  • the tilting or oscillating lever and the secondary lever should also be combined to form a captive unit.
  • the fulcrum may be a hinge pin attached to side walls of the rocker arm or rocker arm and spanning the side walls, forming a bolt joint with a hinge eye passing through the secondary lever transversely.
  • the pivot bearing should also be designed as an axis running parallel to the camshaft with a channel carrying a hydraulic medium and with a recess accommodating the valve lash adjuster and connected to the channel.
  • a particularly compact design of such a valve train is also given when the recess for the valve clearance compensation element in the axial region of the axis encompassing Lagerauges the tilting or rocking lever is arranged, wherein the bearing eye with a clearance for the valve clearance compensation element and / or the first lever portion of Secondary lever serving radial opening is provided.
  • the radial opening is preferably designed as a slot oriented in the circumferential direction of the bearing eye. This may be useful, for example, when the valve clearance compensation element protrudes through the radial opening and leads the tilting or rocking lever on the straight inner walls of the radial opening in the transverse direction to the axis.
  • the valve gear should further comprise a push rod, which is arranged in the transmission sense between the second lever portion of the secondary lever and the gas exchange valve.
  • a push rod for the purpose of assembly aid and operational Abspringêt for the push rod is a valve side End portion of the tilting or rocking lever be provided with a running in the direction of the gas exchange valve opening through which the push rod is passed.
  • both ends of the push rod should be designed as a joint head, wherein the lever-side condyle are received in a running on the second lever portion of the secondary lever socket and the valve-side condyle in a socket of the gas exchange valve frontally contacting pressure element.
  • FIG. 1 and 2 is a valve train 1 of an internal combustion engine with decompression brake in side view and in plan view disclosed.
  • One on one Swivel bearing 2 centrally supported rocker arm 3 is on the one hand with a cam 4 of a camshaft 5 in operative connection and on the other hand, a fulcrum 6, on which a secondary lever 7 is articulated between its first lever portion 8 and its second lever portion 9.
  • the secondary lever 7 is supported by the first lever portion 8 on a hydraulic valve clearance compensation element 10 and operated with the second lever portion 9 in the closing direction spring-loaded exhaust-side gas exchange valve, hereinafter referred to briefly as exhaust valve 11.
  • the rocker arm 3 and the secondary lever 7 are combined to form a captive assembly by the lever support 6 is formed as attached to projecting side walls 12 of the rocker arm 3 and the side walls 12 spanning hinge pin, with a secondary lever 7 transversely interspersing joint eye 13 (see FIG. 3 ) forms a pin joint.
  • the pivot bearing 2 is a basically known axis which is parallel to the camshaft 5 and is encompassed by a bearing eye 14 of the rocker arm 3 to form a sliding bearing.
  • the central axial region of the bearing eye 14 is provided with a radial opening 15, which is formed here as an oriented in the circumferential direction of the bearing eye 14 slot and depending on the extended position of the valve clearance compensation element 10 as a clearance for the valve clearance compensation element 10 and / or the first lever portion 8 of the secondary lever 7 is used.
  • the width of the slot 15 is also dimensioned so that the outer periphery of the valve lash adjuster 10 is only a slight axial play to keep the rocker arm 3 in the longitudinal direction of the axle 2 in position.
  • the known valve lash adjuster 10 is received in a recess 16 of the axis 2 and is supplied via a connected to the lubricant supply to the internal combustion engine and the recess 16 intersecting channel 17 with hydraulic fluid.
  • To relieve pressure is a the bottom of the recess 16 intersecting Achsbohrung 18, at least in the stroke-free shown Position of the rocker arm 3 via a Kipphebelbohrung 19 communicates with the environment of the rocker arm 3.
  • valve-side end portion of the rocker arm 3 is provided with an opening extending in the direction of the outlet 11 opening 26, through which the push rod 20 with the required operating clearance passed through.
  • the effective lever arm of the first lever portion 8 is substantially larger than the effective lever arm of the second lever portion 9, wherein the effective lever arms in the illustrated embodiment have a transmission ratio of about 3: 1.
  • the distance between the lever support 6 and the contact point to the valve play compensation element 10 or to the push rod 20 is to be understood as meaning the effective lever arms. Due to the transmission ratio effective in the contact between the pressure piece 25 and the exhaust valve 11 valve actuating forces are reduced to 1/3 part of the supporting valve clearance compensation element 10 so that the caused by the squeezing of hydraulic fluid Absinkwert the valve lash adjuster 10 even at very high valve actuation forces a relatively low level can be maintained.
  • FIG. 4 A schematic overall view of the valve drive 1, which is only partially shown in the previous figures, starts FIG. 4 out.
  • the inventive design of the rocker arm 3 and the secondary lever 7 and the arrangement of the hydraulic valve lash adjuster 10 is the basic structure of the valve train 1 from the above-cited US 7,392,772 B2 known and summarized here only briefly. Shown in plan view are the camshaft 5 with the cam 4, the axle 2, the rocker arm 3, the secondary lever 7, the lash adjuster 10, the fulcrum 6 and the exhaust valve 11.
  • the invention can be found not only in a rocker arm, but also in a rocker arm application.
  • the two lever types are known to differ by the position of the pivot bearing, wherein the rocker arm is not centrally but end-mounted and accordingly there run the cam and the gas exchange valve on the same lever portion.
  • valve drive according to the invention can also be used in cases in which very high valve actuation forces have to be controlled and yet a hydraulic valve clearance compensation is provided.

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)
EP09164653A 2008-08-08 2009-07-06 Actionneur de soupapes pour un moteur à combustion interne particulièrement avec frein à décompression Active EP2151548B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008037158A DE102008037158A1 (de) 2008-08-08 2008-08-08 Ventiltrieb für eine Brennkraftmaschine insbesondere mit Dekompressionsbremse

Publications (2)

Publication Number Publication Date
EP2151548A1 true EP2151548A1 (fr) 2010-02-10
EP2151548B1 EP2151548B1 (fr) 2011-05-18

Family

ID=40940520

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09164653A Active EP2151548B1 (fr) 2008-08-08 2009-07-06 Actionneur de soupapes pour un moteur à combustion interne particulièrement avec frein à décompression

Country Status (4)

Country Link
US (1) US8042502B2 (fr)
EP (1) EP2151548B1 (fr)
AT (1) ATE510110T1 (fr)
DE (1) DE102008037158A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT505832B1 (de) * 2008-09-18 2011-01-15 Avl List Gmbh Motorbremseinrichtung für eine brennkraftmaschine
EP2900946B1 (fr) * 2012-09-25 2017-02-15 Volvo Lastvagnar Ab Mécanisme d'actionnement de soupape et véhicule automobile équipé de ce type de mécanisme d'actionnement de soupape
DE112015001132T5 (de) * 2014-04-03 2016-12-01 Borgwarner Inc. Stellantrieb für Schließzylinderdruckentlastung
US10626763B2 (en) * 2014-06-10 2020-04-21 Jacobs Vehicle Systems, Inc. Linkage between an auxiliary motion source and a main motion load path in an internal combustion engine
ES2661164T3 (es) * 2015-02-24 2018-03-27 Fpt Industrial S.P.A. Sistema de accionamiento de válvula de un motor de combustión interna
EP3061926B1 (fr) * 2015-02-24 2018-12-26 FPT Industrial S.p.A. Système d'actionnement de soupape d'un moteur à combustion interne
CN114542230B (zh) * 2022-02-23 2022-11-29 湖南道依茨动力有限公司 缸内制动和气门间隙调整方法、调整结构及发动机

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0132786A1 (fr) * 1983-07-21 1985-02-13 Nissan Motor Co., Ltd. Mécanisme de commande variable des soupapes
US4526142A (en) * 1981-06-24 1985-07-02 Nissan Motor Company, Limited Variable valve timing arrangement for an internal combustion engine or the like
US4567861A (en) * 1982-08-17 1986-02-04 Nissan Motor Co., Ltd. Engine valve operating system for internal combustion engine
EP0235981A1 (fr) * 1986-02-28 1987-09-09 General Motors Corporation Mécanisme de commande de soupape avec levée et calage variables
EP0442460A1 (fr) * 1990-02-16 1991-08-21 FERRARI S.p.A. Dispositif de distribution variable, en particulier pour moteur à combustion interne
US20040168660A1 (en) * 2002-11-12 2004-09-02 Volvo Lastvagnar Ab Apparatus for an internal combustion engine
DE102005040649A1 (de) * 2005-08-27 2007-03-01 Schaeffler Kg Variabler Ventiltrieb einer Brennkraftmaschine
DE102006031706A1 (de) 2006-07-08 2008-01-10 Daimlerchrysler Ag Hydraulisches Ventilspielausgleichselement einer Brennkraftmaschine
US7392772B2 (en) 2004-05-06 2008-07-01 Jacobs Vehicle Systems, Inc. Primary and offset actuator rocker arms for engine valve actuation

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1931476A (en) * 1929-12-19 1933-10-17 George E A Hallett Hydraulic valve lash adjusting mechanism
JP3319920B2 (ja) * 1995-10-12 2002-09-03 株式会社ユニシアジェックス エンジンの弁作動装置
JP3764595B2 (ja) * 1998-12-24 2006-04-12 株式会社日立製作所 エンジン補助ブレーキ装置
US7913656B2 (en) * 2007-10-31 2011-03-29 Ford Global Technologies, Llc Variable displacement engine having selectively engageable rocker arm with positioning device

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4526142A (en) * 1981-06-24 1985-07-02 Nissan Motor Company, Limited Variable valve timing arrangement for an internal combustion engine or the like
US4567861A (en) * 1982-08-17 1986-02-04 Nissan Motor Co., Ltd. Engine valve operating system for internal combustion engine
EP0132786A1 (fr) * 1983-07-21 1985-02-13 Nissan Motor Co., Ltd. Mécanisme de commande variable des soupapes
EP0235981A1 (fr) * 1986-02-28 1987-09-09 General Motors Corporation Mécanisme de commande de soupape avec levée et calage variables
EP0442460A1 (fr) * 1990-02-16 1991-08-21 FERRARI S.p.A. Dispositif de distribution variable, en particulier pour moteur à combustion interne
US20040168660A1 (en) * 2002-11-12 2004-09-02 Volvo Lastvagnar Ab Apparatus for an internal combustion engine
US7392772B2 (en) 2004-05-06 2008-07-01 Jacobs Vehicle Systems, Inc. Primary and offset actuator rocker arms for engine valve actuation
DE102005040649A1 (de) * 2005-08-27 2007-03-01 Schaeffler Kg Variabler Ventiltrieb einer Brennkraftmaschine
DE102006031706A1 (de) 2006-07-08 2008-01-10 Daimlerchrysler Ag Hydraulisches Ventilspielausgleichselement einer Brennkraftmaschine

Also Published As

Publication number Publication date
ATE510110T1 (de) 2011-06-15
US20100031907A1 (en) 2010-02-11
EP2151548B1 (fr) 2011-05-18
DE102008037158A1 (de) 2010-02-11
US8042502B2 (en) 2011-10-25

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