EP1084330B1 - Mecanisme de distribution pour un moteur a combustion interne - Google Patents

Mecanisme de distribution pour un moteur a combustion interne Download PDF

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Publication number
EP1084330B1
EP1084330B1 EP99924907A EP99924907A EP1084330B1 EP 1084330 B1 EP1084330 B1 EP 1084330B1 EP 99924907 A EP99924907 A EP 99924907A EP 99924907 A EP99924907 A EP 99924907A EP 1084330 B1 EP1084330 B1 EP 1084330B1
Authority
EP
European Patent Office
Prior art keywords
valve
control
camshaft
thrust
rocker arm
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
EP99924907A
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German (de)
English (en)
Other versions
EP1084330A1 (fr
Inventor
Gert Fischer
Michael Bidlingmaier
Johannes Hoehl
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke AG
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Publication date
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Publication of EP1084330A1 publication Critical patent/EP1084330A1/fr
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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
    • F01L13/0063—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
    • F01L1/14—Tappets; Push rods
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/356—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear making the angular relationship oscillate, e.g. non-homokinetic drive

Definitions

  • the invention relates to a preamble of claim 1 Valve control for an internal combustion engine, in which a control cam Camshaft acts on a lift valve via a tilting segment in a tappet, wherein the formed with a contact path acted upon by the control cam Tilt segment over a circular arc section concentric to the camshaft axis of rotation is movably guided in the plunger such that by means of a Control device with each valve stroke on the opening and closing phase of the Lifting valve determining engagement of the contact track with the flanks of the rotating Control cam by the same and / or relative to the direction of rotation of the control cam oppositely controlled swivel movement of the tilting segment is achieved.
  • valve control described above is the subject of EP 0 626 035 B1, wherein with the valve control described in this document for an internal combustion engine at lower speeds small valve opening angles with little or small overlap and high valve opening angles at high speeds much overlap of the intake and exhaust valve lift curves to form one high gas dynamics are achieved.
  • each is shown and described valve controls combined with a control device, each one in the transverse direction of the internal combustion engine to the side of the respective one Camshaft arranged control shaft includes.
  • the control shaft on the respective intermediate elements Transmission elements result in an additional in the cylinder head of the internal combustion engine Space requirement, which is not given for example with a given valve angle or leads to a wider cylinder head.
  • the invention has for its object the generic valve control to improve in such a way that these are independent of the available space in a given cylinder head under an unchanged one Cylinder head cover can be arranged.
  • Control device one arranged in the valve stroke direction over a machine housing side first sliding swivel joint and another one provided on the tilting segment side Sliding swivel-guided thrust swing arm encircled with one by one control cam-free section of the camshaft with play-through control opening, on the circumference of a controllable element in / on the camshaft engages with this adjusting device, which is also rotated, that eccentrically in the valve stroke direction with the control opening Camshaft axis of rotation adjustable thrust arm with rotating camshaft For each valve stroke, one that controls the tilting segment, periodic swinging movement transverse to the valve stroke direction in superimposition with a executes thrust movement caused in the valve stroke direction.
  • the invention in advantageously a small-sized control device for changing the valve opening angle achieved in a space-reducing manner in that the Control shaft or an equivalent other adjusting device with associated Adjustment means are arranged in and around the camshaft in close proximity for periodic oscillation drive one driving on the respective tilting segment acting thrust rocker, which is preferably beyond the camshaft over a Sliding swivel joint on a fixed to adjacent camshaft bearing caps Oil pipe is guided.
  • the advantageously small-sized control device according to the invention offers kinematic the advantage of a continuous change in the opening angle, with even small opening angles, large valve lifts with relatively little emigration the contact line between the cam and the contact track of the tilting segment are.
  • the same cylinder head can also be used in an advantageous manner for a valve control with the control device according to the invention and for a Valve control without this control device, in particular with a valve train with two similar, adjacent globe valves if not provided Control device no unnecessary and empty volume is dragged along.
  • a valve control with the control device according to the invention also equipped with a rotation angle adjustment device for spreading the control cam his.
  • a particular advantage of the control device according to the invention is due to the low oscillating mass suitable for high-speed internal combustion engines.
  • a valve control 1 for an internal combustion engine acts Control cam 2 of a camshaft 4 connected to a drive wheel 3 via Tilting segment 5 in a plunger 6 controlling a lift valve 7, with the a contact segment 8 formed by the control cam 2 5 via a circular arc section concentric with the camshaft axis of rotation 9 10 is arranged movably guided in the plunger 6.
  • control device 11 Via one with the tipping segment 5 control device 11 is in drive connection with each valve lift an engagement determining the opening and closing phase of the lift valve 7 the contact track 8 with the flanks of the rotating control cam 2 by a relative to the direction of rotation of the control cam 2 positively controlled in the same and / or opposite direction Pivoting movement according to arrow "A" of the tilting segment 5 is achieved.
  • the control device 11 comprises a valve lift direction according to FIG Arrow "B" over a first sliding rotary joint arranged on the machine housing side 12 and a further sliding swivel joint provided on the tilting segment side 13 guided thrust rocker 14 with one of a control cam-free section the camshaft 4 with play-through control opening 15 on its circumference a controlled actuatable element in / on the camshaft 4 with this co-rotating adjusting device 16 engages such that the valve lift direction according to arrow "B” with the control opening 15 eccentrically Camshaft axis of rotation 9 adjustable thrust arm 14 when rotating Camshaft 4 for each valve lift one of the positive control of the tilting segment 5 Serving, periodic swinging movement according to arrow "A” across the valve stroke direction according to arrow "B” in superposition with a valve stroke direction according to arrow "B” caused pushing movement executes.
  • control breakthrough is used to achieve preferred symmetrical stroke profiles according to FIG 15 in the thrust arm 14 radially symmetrical with a cylindrical Scope designed.
  • This guide ring 20 forms in this adjusting device 16 Control-actuated element described above, which on the circumference of the Tax breakthrough 15 attacks.
  • a sliding block 21 can be arranged, each sliding block 21 with both the control pin 18 and the respective one End face of the adjusting pin 19 via correspondingly adapted sliding surfaces interacts positively and thus flatly.
  • a control device 11 according to the invention of advantageously low construction costs is achieved in particular in the case of similar, adjacent globe valves 7 whose tilt segments 5 mounted in the plungers 6 with a between the Tappets 6 arranged swing arm 22 are connected, which over the Tilting segments 5 swing-guided swing arm 22 in a shaft 23 - figure 5- equipped with the straight, tilt segment sliding pivot 13 on which the thrust rocker 14 common to both lift valves 7 1 and 4 articulated attacks.
  • This arrangement advantageously enables the straight line with the Slide block 24 of the thrust rocker 14 and the storage of this slide block 24 is lubricated on the bearing bush 25 with oil from the oil pipe 26.
  • FIGS. 1, 3 and 6 they are of the same type Lift valves 7 via box lifters 6 with the interposition of hydraulic valve lash adjusters or HVA 27 actuated, of the opposite arranged guide surfaces 28 of each box tappet 6 from the respective HVA 27 provided oil supply channels 29 are extended beyond the HVA respective mouths 30 in the circular arc section accommodating the tilting segment 5 10.
  • This arrangement is advantageously a simple one Lubrication of the tilting segments 5 in the box tappets 6 is achieved.
  • each tilting segment 5 can be made in one piece with respective contact path or one on a separate part 31 Identify trained contact path 8, the separate part 31 with the Tilting segment is in a detachable connection, for example a plug connection.
  • Thrust arm 14 formed in the area of the control opening 15 divided Inclusion of a guide ring 20 formed with radial flanges 32, via the the thrust rocker 14 in an advantageously simple manner relative to the camshaft 4 in is secured in the axial direction.
  • To lubricate the guide ring 20 in the Control opening 15 is a in the thrust arm 14 on the Lubrication area of the straight guide / sliding block 24 of the machine housing side Sliding rotary joint 12 also provided an extended lubrication hole Supply of oil from the oil pipe 26.
  • the camshaft 4 can one end with a rotation angle adjustment device provided in the area of the drive wheel 3 to change the spread between the intake and exhaust cams be provided.
  • a rotary adjustment device 33 is provided, which is a stepless rotary adjustment the control shaft 17 from 0 ° to 180 ° or ⁇ 180 ° and back.
  • This rotary adjustment device 33 can, for example, in the manner of a vane pump designed and hydraulically controlled.
  • each tilt segment 5 by means of the control device 11 controlled such that each tilt segment 5 relative to the direction of rotation of the control cam 2 in opposite directions for the opening area and for the closing area is moved in the same direction.
  • a valve lift curve with a maximum opening angle is achieved in that the control pin 18 of the control shaft 17 over the Rotary adjustment device 33 by the angle of 90 ° from the respective 0 ° position or 180 ° position is rotated, the control pin 18 over the transverse to the valve lift direction "B" straight lines of the 0 ° and the 180 ° position in the direction sliding swivel joint 12 of the thrust arm 14 on the machine housing side is.
  • a valve stroke curve with a minimum opening angle according to one of the dashed lines 7 is the control pin 18 in a diametrical position to the position relevant to the maximum opening angle below the controlled the aforementioned straight line.
  • this selected position of the control pin 18 is caused by the control device 11 that the respective tilting segment 5th is initially moved in the opening direction in the direction of rotation of the control cam 2 to achieve a later opening point and that the tilting segment 5 subsequently is moved in opposite directions in the closing phase of the lift valve 7 to achieve of an earlier closing point.
  • control device 11 With the control device 11 according to the invention, this results in advantageous kinematic structure the advantage of a continuous change in the opening angle between its maximum and minimum value and one accordingly high number of intermediate valve lift curves.

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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)

Claims (11)

  1. Commande de soupape d'un moteur à combustion interne dans laquelle :
    une came de commande (2) d'un arbre à cames (4) agit dans le sens de la commande par un segment basculant (5) d'un poussoir (6) sur une soupape (7) à mouvement de translation,
    le segment basculant (5) réalisé avec un chemin de contact (8) soumis à l'action de la came de commande (2) est guidé de manière mobile dans le poussoir (6) par un segment d'arc de cercle (10) concentrique à l'axe de rotation (9) de l'arbre à came de façon que
    un dispositif de commande (11) puisse à chaque course de soupape, agir dans le sens définissant la phase d'ouverture et de fermeture de la soupape (7), du chemin de contact (8) avec les flancs de la came de commande (2), rotative, par un mouvement de basculement (flèche A) du segment basculant (5), commandé de force, dans le même sens ou dans le sens opposé, par rapport au sens de rotation de la came de commande (2),
    caractérisée en ce que
    le dispositif de commande (11) comporte une première articulation coulissante (12) du bloc moteur, dans la direction de translation des soupapes (flèche B) et une autre articulation coulissante (13) prévue du côté du segment basculant comprend une bielle coulissante (14) guidée, avec une ouverture de commande (15) traversée avec du jeu par un segment sans came de commande de l'arbre à cames (4), ouverture dont la périphérie est soumise à l'action d'un élément d'actionnement commandé (bague de guidage 20) d'une installation de réglage (16) montée sur ou dans l'arbre à cames (4) et entraínée en rotation par celle-ci de façon que
    la bielle coulissante (14) réglable dans la direction de translation des soupapes (flèche B) de manière excentrée par rapport à l'axe de rotation (9) de l'arbre à cames dans l'ouverture de commande (15), lorsque l'arbre à cames (54) tourne, de façon qu'à chaque course de soupape un mouvement oscillant (flèche A) périodique, servant à la commande forcée du segment basculant (5), exécute transversalement à la direction de translation de la soupape (flèche B) en combinaison avec un mouvement coulissant dans la direction de translation des soupapes (flèche B).
  2. Commande de soupape selon la revendication ,
    caractérisée en ce que
    l'ouverture de commande (15) est de forme radiale symétrique avec une périphérie cylindrique.
  3. Commande de soupape selon la revendication 1 ou 2,
    caractérisée en ce que
    l'installation de réglage (16) comprend un arbre de commande (17) mobile en rotation coaxialement dans un arbre à came creux (4) avec un tourillon de commande (18) concentrique,
    ce tourillon coopère avec un tourillon de réglage (19) guidé de manière radiale mobile, diamétralement dans l'arbre à came (4),
    chaque tourillon de réglage (19) est en liaison solidaire avec un segment de moitié (20', 20") d'une bague de guidage (20) montée à rotation dans l'ouverture de commande (15) de la bielle coulissante (14).
  4. Commande de soupape selon la revendication 3,
    caractérisée en ce que
    entre le tourillon de commande (18) et chaque tourillon de réglage (19), il est prévu chaque fois un coulisseau (21) et
    chaque coulisseau (21) coopère à la fois avec le tourillon de commande (18) et avec la surface frontale respective du tourillon de réglage (19) par des surfaces de glissement adaptées de manière correspondante, la coopération se faisant par une liaison de forme.
  5. Commande de soupape selon une ou plusieurs des revendications 1 à 4,
    caractérisée en ce que
    pour des soupapes (7), voisines de même type, dont les segments basculants (5) montés dans les poussoirs (6) sont reliés à une bielle oscillante (22) installée entre les poussoirs (6), et
    la bielle oscillante (22) guidée en oscillation par les segments basculants (5) est équipée de l'articulation coulissante (13) du côté des segments basculants, guidée suivant une trajectoire rectiligne dans une cage (23), articulation soumise à l'action d'une bielle coulissante (14) commune aux deux soupapes (7).
  6. Commande de soupape selon l'une des revendications 1 à 5,
    caractérisée en ce que
    la bielle coulissante (14) coopère de manière mobile au niveau de son autre zone d'extrémité, de l'autre côté de l'arbre à came (4) par un moyen de guidage rectiligne en forme de fourche avec un coulisseau (24) de l'articulation coulissante (12) du bloc moteur, et
    le coulisseau (24) est monté de manière mobile angulairement par une douille de palier (25) sur un tuyau d'huile (26) fixé dans un couvercle de palier de l'arbre à cames.
  7. Commande de soupape selon la revendication 6,
    caractérisée en ce que
    le guidage rectiligne par le coulisseau (24) pour la bielle coulissante (14) et le montage du coulisseau (24) dans le palier (25) est graissé par l'huile de la conduite d'huile (26).
  8. Commande de soupape selon une ou plusieurs des revendications 1 à 7,
    caractérisée en ce que
    les soupapes (7) de même type sont actionnées par l'intermédiaire de poussoirs à caisson (6) avec interposition de compensateurs hydrauliques de jeu (27),
    partant des surfaces de guidage (28) opposées de chaque poussoir en forme de caisson (26), les canaux d'alimentation en huile (29) prévus pour chaque compensateur (27) sont prolongés au delà des compensateurs (27) vers les embouchures respectives (30) dans le segment d'arc de cercle (10) qui reçoit et loge le segment basculant (5).
  9. Commande de soupape selon l'une des revendications 1 à 8,
    caractérisée en ce que
    le segment basculant (5) comporte un chemin de contact (8) formé sur une pièce particulière (31), et
    la pièce (31) de réalisation particulière, sans usure est reliée le cas échéant de manière amovible au segment basculant (5).
  10. Commande de soupape selon l'une des revendications 1 à 9,
    caractérisée en ce que
    la bielle coulissante (14) est divisée au niveau de son ouverture de commande (15) pour recevoir une bague de guidage (20) munie de brides radiales (32),
    cette bague assurant l'alimentation en huile venant du tuyau d'huile (26) par un perçage de graissage prolongé dans la bielle oscillante (14) au delà de la zone de graissage entre le coulisseau (24) et le guidage droit.
  11. Commande de soupape selon l'une des revendications 1 à 10,
    caractérisée en ce que
    l'arbre à cames (4) comporte à une extrémité une installation de réglage d'angle de rotation, et
    à l'autre extrémité l'arbre est muni d'une installation de réglage en rotation (33) pour l'arbre de commande (17),
    cette installation servant à réaliser un réglage en rotation, continu de l'arbre de commande (17), cet angle étant compris entre 0° et 180° ou est inférieur à 180° et inversement.
EP99924907A 1998-06-05 1999-05-07 Mecanisme de distribution pour un moteur a combustion interne Expired - Lifetime EP1084330B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19825307 1998-06-05
DE19825307A DE19825307A1 (de) 1998-06-05 1998-06-05 Ventilsteuerung für eine Brennkraftmaschine
PCT/EP1999/003154 WO1999064729A1 (fr) 1998-06-05 1999-05-07 Mecanisme de distribution pour un moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1084330A1 EP1084330A1 (fr) 2001-03-21
EP1084330B1 true EP1084330B1 (fr) 2002-10-30

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP99924907A Expired - Lifetime EP1084330B1 (fr) 1998-06-05 1999-05-07 Mecanisme de distribution pour un moteur a combustion interne

Country Status (6)

Country Link
US (1) US6382149B1 (fr)
EP (1) EP1084330B1 (fr)
JP (1) JP4283999B2 (fr)
DE (2) DE19825307A1 (fr)
ES (1) ES2185349T3 (fr)
WO (1) WO1999064729A1 (fr)

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19911067A1 (de) * 1999-03-12 2000-09-14 Bayerische Motoren Werke Ag Verfahren zur Ausbildung einer Anrißstelle zum Bruchtrennen eines Bauteiles aus einem Kohlenstoffstahl
US6786185B2 (en) * 2002-03-14 2004-09-07 Delphi Technologies, Inc. Variable valve actuation mechanism having partial wrap bearings for output cams and frames
JP4343021B2 (ja) * 2004-04-28 2009-10-14 本田技研工業株式会社 内燃機関の動弁装置
JP4342372B2 (ja) * 2004-04-28 2009-10-14 本田技研工業株式会社 内燃機関の動弁装置
US20080017150A1 (en) * 2004-09-15 2008-01-24 Yamaha Hatsudoki Kabushiki Kaisha Variable Valve Drive Device, Engine, and Motorcycle
FI20080053A0 (fi) * 2007-12-12 2008-01-22 Wallac Oy Laite ja menetelmä optisen komponentin paikan sovittamiseksi
DE102009037270B4 (de) 2009-08-10 2011-04-07 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Ventiltrieb für Brennkraftmaschinen zur Betätigung von Gaswechselventilen
DE102009037269B4 (de) 2009-08-10 2011-06-01 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Ventiltrieb für Verbrennungskraftmaschinen zur Betätigung von Gaswechselventilen
DE102009037268B3 (de) 2009-08-10 2011-04-07 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Variabler Ventiltrieb für Brennkraftmaschinen zur Betätigung von Gaswechselventilen
JP5569423B2 (ja) * 2011-02-09 2014-08-13 トヨタ自動車株式会社 内燃機関の可変動弁装置
DE102011108728B4 (de) 2011-07-27 2013-02-07 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Ventiltrieb für Brennkraftmaschinen zur Betätigung von Gaswechselventilen
KR101628100B1 (ko) 2014-12-09 2016-06-08 현대자동차 주식회사 연속 가변 밸브 듀레이션 장치 및 이를 포함하는 엔진
KR101637296B1 (ko) * 2014-12-09 2016-07-07 현대자동차 주식회사 연속 가변 밸브 듀레이션 장치 및 이를 포함하는 엔진
KR101628088B1 (ko) 2015-07-07 2016-06-08 현대자동차 주식회사 연속 가변 밸브 듀레이션 장치 및 이를 포함하는 엔진
KR101664079B1 (ko) * 2015-09-24 2016-10-10 현대자동차 주식회사 연속 가변 밸브 듀레이션 장치 및 이를 포함하는 엔진
KR102371229B1 (ko) * 2016-12-14 2022-03-04 현대자동차 주식회사 연속 가변 밸브 듀레이션 장치 및 이를 포함하는 엔진
KR102371235B1 (ko) 2016-12-15 2022-03-04 현대자동차 주식회사 연속 가변 밸브 듀레이션 장치 및 이를 포함하는 엔진
CN108625924B (zh) * 2018-06-15 2023-09-22 吉林大学 一种气门正时调节机构
CN112648040B (zh) * 2020-12-22 2022-03-25 东风商用车有限公司 发动机压缩释放式制动器及其制动方法

Family Cites Families (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR889861A (fr) * 1941-06-14 1944-01-21 Saurer Ag Adolph Dispositif pour faire varier les périodes de chevauchement de l'ouverture des soupapes dans les moteurs à combustion interne
GB1311562A (en) 1969-06-27 1973-03-28 Ass Eng Ltd Device for moving a cam relative to its driving shaft
DE3041864A1 (de) * 1980-11-06 1982-05-13 Audi Nsu Auto Union Ag, 7107 Neckarsulm Vorrichtung zum verschieben der steuerzeit eines gaswechselventils einer brennkraftmaschine
GB2214567B (en) * 1987-12-10 1992-06-24 Martin William Bennett Variable valve timing by rocking cam follower
DE59307123D1 (de) 1992-12-13 1997-09-18 Bayerische Motoren Werke Ag Ventilsteuerung für eine brennkraftmaschine
US5732669A (en) * 1992-12-13 1998-03-31 Bayerische Motoren Werke Aktiengesellschaft Valve control for an internal combustion engine
US5515819A (en) * 1994-11-04 1996-05-14 Eaton Corporation Biasing assembly for a variable valve timing mechanism
DE19532334A1 (de) * 1995-09-01 1997-03-06 Bayerische Motoren Werke Ag Variabler Ventiltrieb, insbesondere für Brennkraftmaschinen
DE19604943C2 (de) * 1996-02-10 2002-10-02 Daimler Chrysler Ag Vorrichtung zum Betreiben von Ventilen einer Brennkraftmaschine
JP3834921B2 (ja) * 1997-04-02 2006-10-18 三菱自動車工業株式会社 可変動弁機構
DE19825308A1 (de) * 1998-06-05 1999-12-09 Bayerische Motoren Werke Ag Variabler Ventiltrieb für eine Brennkraftmaschine
JP2000145422A (ja) * 1998-11-05 2000-05-26 Honda Motor Co Ltd 多気筒内燃機関の動弁装置
US6135075A (en) * 1999-03-10 2000-10-24 Boertje; Brian H. Variable cam mechanism for an engine
US6293238B1 (en) * 1999-04-07 2001-09-25 Caterpillar Inc. Rocker arm and rocker arm assembly for engines
US6314926B1 (en) * 1999-05-24 2001-11-13 Jenera Enterprises Ltd Valve control apparatus
US6311659B1 (en) * 1999-06-01 2001-11-06 Delphi Technologies, Inc. Desmodromic cam driven variable valve timing mechanism

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JP2002517669A (ja) 2002-06-18
US6382149B1 (en) 2002-05-07
DE59903259D1 (de) 2002-12-05
EP1084330A1 (fr) 2001-03-21
JP4283999B2 (ja) 2009-06-24
DE19825307A1 (de) 1999-12-09
WO1999064729A1 (fr) 1999-12-16
ES2185349T3 (es) 2003-04-16

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