WO2010125235A1 - Aménagement de commande pour soupape d'entrée dans un moteur à piston - Google Patents

Aménagement de commande pour soupape d'entrée dans un moteur à piston Download PDF

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Publication number
WO2010125235A1
WO2010125235A1 PCT/FI2010/050285 FI2010050285W WO2010125235A1 WO 2010125235 A1 WO2010125235 A1 WO 2010125235A1 FI 2010050285 W FI2010050285 W FI 2010050285W WO 2010125235 A1 WO2010125235 A1 WO 2010125235A1
Authority
WO
WIPO (PCT)
Prior art keywords
chamber
inlet valve
control arrangement
control
flow
Prior art date
Application number
PCT/FI2010/050285
Other languages
English (en)
Inventor
Magnus Sundsten
Leif Knipström
Original Assignee
Wärtsilä Finland Oy
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wärtsilä Finland Oy filed Critical Wärtsilä Finland Oy
Priority to EP10718624.9A priority Critical patent/EP2425104B1/fr
Priority to CN201080018262.0A priority patent/CN102414402B/zh
Publication of WO2010125235A1 publication Critical patent/WO2010125235A1/fr

Links

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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/146—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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/08—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for decompression, e.g. during starting; for changing compression ratio
    • 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
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • 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
    • F01L1/20—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
    • F01L1/245—Hydraulic tappets
    • F01L1/255—Hydraulic tappets between cam 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
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
    • 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
    • F01L1/16—Silencing impact; Reducing wear
    • 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
    • F01L2013/0089—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 with means for delaying valve closing
    • 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

Definitions

  • the invention relates to a control arrangement for an inlet valve in a piston en- gine according to preamble of claim 1.
  • the timing of the inlet valves needs to be such that the inlet valve is closed early before the bottom dead centre of the piston, while the boost pressure is raised accord- ingly so as to get a sufficient amount of air to the cylinder.
  • This kind of arrangement is, however, problematic with low engine loads, when the boost pressure of the turbocharger is still relatively low.
  • One solution could be intensified supply of inlet air during the opening phase of the inlet valve under such special situations.
  • Another solution is to provide for a delay in the closing of the inlet valve for prolonging the opening time of the inlet valve when needed.
  • VIP variable inlet valve closure
  • An object of the invention is to provide a further improved control arrangement for delaying the closing of the inlet valve in a piston engine.
  • a particular aim is to enable selection of different delaying times to comply with different situations, especially when combustion engines are operated under low engine loads and during start of the engines.
  • the body part is provided with two or more flow ducts for arranging different routes for the flow of hydraulic medium from the first chamber to the second chamber.
  • control means are provided for selecting the route of flow to be utilised in each case to provide different closing delay.
  • a route may here include one or more flow ducts depending on the application in each case.
  • the two or more flow ducts are with advantage arranged to open in a common chamber or the like connection duct arranged in communication with the first chamber. Then the control means are arranged to operate in said common chamber or the like connection duct.
  • the second chamber is provided within a guide member arranged between the cam device and the piston device to be movably responsive with the movements of cam device.
  • the two or more flow ducts are arranged to open into the second chamber at different positions along the track of movement of the guide member.
  • the guide member is arranged to directly act on the piston device only in the direction for opening the inlet valve, when the delaying function is utilised.
  • the flow of hydraulic medium is arranged via one of said flow ducts at a time and that the control means include a control valve with a movable valve member provided with a releasing means to be arranged at the position of one of said flow ducts.
  • the releasing means can be a narrowing portion dimensioned to allow flow only through one duct at a time.
  • control arrangement includes a separate control valve for each of the flow ducts providing for a shortened delaying time.
  • the control means are with advantage arranged to be operated pneumatically by making use of the control systems included in the engine. Specifically charge air from a turbocharger of said piston engine can be utilised for controlling the control means.
  • the operating pressure is with advantage arranged to occur against the force of a spring providing uncomplicated construction and control.
  • FIG. 1 shows a piston engine and a skeleton diagram of its valve mechanism
  • FIG. 5 shows an enlarged view of a first embodiment of control means ac- cording to the invention
  • FIG. 6a and 6b show an enlarged view of a second embodiment of control means according to the invention in two operation positions
  • Figure 7 shows a relative opening curve of the inlet valve relating to the embodiment of figure 6a
  • FIG. 8 shows an enlarged view of a third embodiment of control means according to the invention.
  • FIG. 1 shows a schematic view of a piston engine 1 as far as it is relevant to the understanding of the invention.
  • the gas exchange of the cylinders (not shown) in the piston engine 1 is carried out under the control of gas exchange valves, i.e. inlet valves and exhaust valves, located on a cylinder head 2. Only inlet valves 3 are shown and they are operated by means of valve mechanisms
  • each valve mechanism 6 which are typically guided by cam profiles 5' of cam devices 5 arranged on a camshaft 4 of the engine.
  • the force transmission connection between each valve mechanism 6 and the corresponding cam device 5 is realised by a control arrangement 7.
  • the control arrangement 7 is shown in more detail in Figures 2 - 4, of which Figure 2 shows it in a non-operating state, whereby the inlet valve 3 in connection therewith is closed.
  • the control arrangement 7 comprises a body part 8, which is typically attached to the engine body.
  • a piston device 9 is movably arranged within the body part 8.
  • the upper end of the piston device 9 is arranged in force transmission connection with the valve mechanism 6. This connection is in this case mechanical, but it could be hydraulic as well.
  • the movements of the piston device 9 are controlled by a guide member 10 arranged at the lower end of the piston device within the body part 8.
  • the guide member 10 is in engagement with and urged by a spring 11 towards a roller 12, which receives its guidance from the cam profile 5' of the cam device 5.
  • the roller 12 follows the cam profile 5' of the cam device 5, and the changes in the cam profile 5' are transmitted so as to affect the opening and closing of the inlet valve 3.
  • the body part 8 and the piston device 9 together define a first chamber 13, into which hydraulic medium can be selectively fed via a feed duct 14, as indicated by arrow, for providing a delay in the closing of the inlet valve 3.
  • the feed duct is with advantage provided with a shut-off valve and a non-return valve, not shown.
  • the shut-off valve By means of the shut-off valve the feed line to the first chamber 13 may be connected or disconnected, depending on whether or not the aim is to use the delay function for the delayed closing of the inlet valve 3. Due to the non-return valve the control arrangement cannot cause any pulsations in the source of hydraulic medium. This is of importance when lubricating oil is used as a hydraulic medium.
  • the body part 8 is additionally provided with ducts 15 and 18 by means of which the first chamber 13 can be connected with a second chamber 19, which is located in the guide member 10.
  • the guide member 10 is provided with an aperture 10a.
  • the aperture 10a is at the position of the downward end opening of the duct 18 the flow connection between the cham- bers 13 and 19 is established.
  • a chamber 16 or the like duct which includes control means 17 in accordance with the invention, the construction and operation of which is described more in detail below.
  • FIG. 5 shows a first embodiment of control means 17 according to the invention.
  • the chamber 16 is provided with three ducts 18a, 18b and 18c which each can be arranged in communication with the chamber 19 via the aperture 10a by means of the control means 17, which include a control valve 17a movable in a chamber 20 located in the body part 8.
  • the control valve 17a is provided with a valve member 17b and releasing means 17c, which in this case is a groove circumventing the valve member 17b.
  • the releasing means 17c is at the position of the duct 18b, whereby communication between the chambers 13 and 19 is established through this duct 18b.
  • the end openings of the ducts 18a, 18b and 18c are at different height.
  • valve means 17 can with advantage be accomplished pneumatically by feeding pressure air into the chamber 20, as indicated by the arrow, which will result in urging the control valve 17a with the valve member 17b to the left in the figure against the force of a spring 21.
  • the movement of the control valve 17a and the selection of the respective duct 18a, 18b and 18c is dependent on the pressure of the air to be fed into the chamber 20.
  • the control systems of the engine should be availed of so that for instance the charge air from a turbocharger of the engine is utilised.
  • variation in inlet valve closing can be accomplished more or less automatically as a function of the charge air pressure being dependent on the load of the engine in each case.
  • Figures 6a and 6b disclose another embodiment of the control means 17'.
  • the chamber 16' which is formed as a connection duct is operationally connected with a control valve 17'a, a control member 17'b of which controlling the communication between the chamber 16' and a second duct 18'b.
  • the con- trol valve 17'a is located in a chamber 20' into which pressure air is fed to urge it against the force of a spring 21 '.
  • FIG 7 shows the relative opening curve of the inlet valve as a function of the cam angle of the engine.
  • Curve C shows a situation, in which hydraulic medium is not led at all to the chamber 13, whereby the inlet valve control is carried out merely determined by the cam profile 5'.
  • Curves A and B relate to the situation, in which hy- draulic medium is led to the chamber 13, while the piston device 9 moves in the opening direction of the inlet valve. It is thus possible to provide a delay in the closing of the inlet valve in relation to its normal operation e.g. in different load situations of the engine.
  • the curve A relates to a situation when the delay is affected by selecting the communication between the chambers 13 and 19 via the duct 18'a, the control valve 17'a thus being in a position closing the duct 18'b as shown in figure 6b.
  • the curve B then represents a situation corresponding to figure 6a, according to which the control valve 17'a is open and allows communication via the duct 18'b.
  • the releasing of pressure in the chamber 13 occurs earlier and the inlet valve, thus, is closed earlier as well, but the closing is still delayed in comparison with the normal situation depicted by the curve A.
  • Figure 8 discloses a third embodiment of the control means according to the invention.
  • This is a variation of the embodiment of figures 6a and 6b, which in- dudes a third duct 18"c in addition to the ducts 18"a and 18"b.
  • the end openings of each of these ducts is located at different height, that is at different position along the return movement of the guide member 10, thereby providing a possibility for changing the delay of the closing of the inlet valve.
  • a number of further ducts 18" could be provided as well depending on the need for closer variation of the delay available in each case for the closing of the inlet valve in question, and the space available in the body part 8 in the engine respectively.
  • control valves 17, 17' and 17" can be operated by means of any pressure medium preferably available in the engine, i.e. pneumatic, hydraulic, or also electrically.
  • the control of the control valves and the selection of the flow duct in each case can be arranged by making use of pressure sensors for each control valve and due control logic so as to determine the needed delay in each case and to ensure cor- rect operation of the control valves accordingly.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

L'invention se rapporte à un aménagement de commande destiné à une soupape d'entrée dans un moteur à piston adapté entre un dispositif de cames (5) d'un arbre à cames (4) du moteur (1) et un mécanisme de soupape d'entrée (6) conçu pour ouvrir et fermer la soupape d'entrée (3) en association avec un cylindre du moteur. Ledit aménagement de commande (7) comprend une partie corps (8), dans laquelle un dispositif de piston (9) est agencé mobile pour se trouver en liaison de transmission de force avec l'arbre à cames (4) et le mécanisme de soupape (6), ladite partie corps (8) et le dispositif piston (9) délimitant ensemble une première chambre (13), dans laquelle un fluide hydraulique peut être sélectivement introduit, et une seconde chambre (19) reliée à la première chambre par l'intermédiaire d'un moyen de conduit (18, 18', 18"), l'écoulement de fluide hydraulique de la première chambre (13) vers la seconde chambre (19) étant commandé pour assurer un délai dans la fermeture de la soupape d'entrée (3). La partie corps (8) est équipée de deux conduits d'écoulement, ou plus, (18a,18b,18c ; 18'a,18'b ; 18"a,18"b,18"c) destinés à mettre en place différents chemins pour l'écoulement de fluide hydraulique de la première chambre (13) vers la seconde chambre (19). Un moyen de commande (17, 17', 17") permet de sélectionner le chemin d'écoulement à utiliser dans chaque cas pour assurer un délai de fermeture différent.
PCT/FI2010/050285 2009-04-27 2010-04-09 Aménagement de commande pour soupape d'entrée dans un moteur à piston WO2010125235A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP10718624.9A EP2425104B1 (fr) 2009-04-27 2010-04-09 Mécanisme de contrôle de distribution pour une soupape d'admission dans un moteur à combustion interne
CN201080018262.0A CN102414402B (zh) 2009-04-27 2010-04-09 用于活塞式发动机中的进气阀的控制设备

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20095462A FI121512B (fi) 2009-04-27 2009-04-27 Mäntämoottorin imuventtiilin ohjausjärjestely
FI20095462 2009-04-27

Publications (1)

Publication Number Publication Date
WO2010125235A1 true WO2010125235A1 (fr) 2010-11-04

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Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/FI2010/050285 WO2010125235A1 (fr) 2009-04-27 2010-04-09 Aménagement de commande pour soupape d'entrée dans un moteur à piston

Country Status (5)

Country Link
EP (1) EP2425104B1 (fr)
KR (1) KR101628424B1 (fr)
CN (1) CN102414402B (fr)
FI (1) FI121512B (fr)
WO (1) WO2010125235A1 (fr)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2722499A1 (fr) * 2012-10-19 2014-04-23 Hyundai Heavy Industries Co., Ltd. Appareil de contrôle de la synchronisation d'une soupape variable
WO2014060645A1 (fr) * 2012-10-18 2014-04-24 Wärtsilä Finland Oy Agencement de soupape d'échange de gaz
WO2014071936A1 (fr) * 2012-11-12 2014-05-15 Schaeffler Technologies AG & Co. KG Boîtier hydraulique d'une commande de soupapes électrohydraulique
WO2014106681A1 (fr) * 2013-01-03 2014-07-10 Wärtsilä Finland Oy Agencement de soupape d'échappement et procédé de commande de fermeture de soupape d'échappement
KR101623222B1 (ko) 2011-05-16 2016-05-23 현대중공업 주식회사 유압을 이용한 가변밸브 타이밍장치
WO2017173471A1 (fr) * 2016-04-05 2017-10-12 Avl List Gmbh Machine à pistons alternatifs
WO2020058417A1 (fr) * 2018-09-19 2020-03-26 Eaton Intelligent Power Limited Ensemble de train de soupapes
US20220186637A1 (en) * 2019-03-29 2022-06-16 Abb Switzerland Ltd. Valve train with hydraulic delay element for an internal combustion engine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104443595B (zh) * 2014-11-26 2016-08-24 李淑兰 一种改进的气阀结构
DK179120B1 (en) * 2016-02-03 2017-11-13 Man Diesel & Turbo Filial Af Man Diesel & Turbo Se Tyskland A large turbocharged two-stroke compression-ignited internal combustion engine with blow-off control
EP3596317B1 (fr) * 2017-03-17 2023-05-03 Wärtsilä Finland Oy Agencement de commande pour une soupape d'échange de gaz dans un moteur à piston à combustion interne et procédé de fonctionnement d'un agencement de commande pour une soupape d'échange de gaz dans un moteur à combustion interne

Citations (6)

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Publication number Priority date Publication date Assignee Title
US3817228A (en) * 1971-10-25 1974-06-18 J Bywater Cam motion control unit
DE3611476A1 (de) * 1986-04-05 1987-10-08 Irm Antriebstech Gmbh Verfahren zur betaetigung von ventilen zum ladungswechsel bei brennkraftmaschinen mit direkter hydraulischer uebertragung
DE3807699A1 (de) * 1988-03-09 1989-09-21 Audi Ag Regelbare hydraulische ventilsteuerung
US5002022A (en) * 1989-08-30 1991-03-26 Cummins Engine Company, Inc. Valve control system with a variable timing hydraulic link
WO2004033863A1 (fr) * 2002-10-07 2004-04-22 Ricardo, Inc. Appareil permettant de desactiver une soupape de moteur
WO2008000899A1 (fr) * 2006-06-30 2008-01-03 Wärtsilä Finland Oy Dispositif de commande pour une soupape de changement des gaz dans un moteur à piston et procédé de commande d'une soupape de changement des gaz dans un moteur à piston

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3817228A (en) * 1971-10-25 1974-06-18 J Bywater Cam motion control unit
DE3611476A1 (de) * 1986-04-05 1987-10-08 Irm Antriebstech Gmbh Verfahren zur betaetigung von ventilen zum ladungswechsel bei brennkraftmaschinen mit direkter hydraulischer uebertragung
DE3807699A1 (de) * 1988-03-09 1989-09-21 Audi Ag Regelbare hydraulische ventilsteuerung
US5002022A (en) * 1989-08-30 1991-03-26 Cummins Engine Company, Inc. Valve control system with a variable timing hydraulic link
WO2004033863A1 (fr) * 2002-10-07 2004-04-22 Ricardo, Inc. Appareil permettant de desactiver une soupape de moteur
WO2008000899A1 (fr) * 2006-06-30 2008-01-03 Wärtsilä Finland Oy Dispositif de commande pour une soupape de changement des gaz dans un moteur à piston et procédé de commande d'une soupape de changement des gaz dans un moteur à piston

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101623222B1 (ko) 2011-05-16 2016-05-23 현대중공업 주식회사 유압을 이용한 가변밸브 타이밍장치
WO2014060645A1 (fr) * 2012-10-18 2014-04-24 Wärtsilä Finland Oy Agencement de soupape d'échange de gaz
US9200574B2 (en) * 2012-10-19 2015-12-01 Hyundai Heavy Industries Co., Ltd. Variable valve timing apparatus
US20140109849A1 (en) * 2012-10-19 2014-04-24 Hyundai Heavy Industries Co., Ltd. Variable valve timing apparatus
EP2722499A1 (fr) * 2012-10-19 2014-04-23 Hyundai Heavy Industries Co., Ltd. Appareil de contrôle de la synchronisation d'une soupape variable
WO2014071936A1 (fr) * 2012-11-12 2014-05-15 Schaeffler Technologies AG & Co. KG Boîtier hydraulique d'une commande de soupapes électrohydraulique
WO2014106681A1 (fr) * 2013-01-03 2014-07-10 Wärtsilä Finland Oy Agencement de soupape d'échappement et procédé de commande de fermeture de soupape d'échappement
WO2017173471A1 (fr) * 2016-04-05 2017-10-12 Avl List Gmbh Machine à pistons alternatifs
CN109196191A (zh) * 2016-04-05 2019-01-11 Avl里斯脱有限公司 往复活塞式机器
US20190112951A1 (en) * 2016-04-05 2019-04-18 Avl List Gmbh Reciprocating-piston machine
US11466596B2 (en) 2016-04-05 2022-10-11 Avl List Gmbh Reciprocating-piston machine
WO2020058417A1 (fr) * 2018-09-19 2020-03-26 Eaton Intelligent Power Limited Ensemble de train de soupapes
US20220186637A1 (en) * 2019-03-29 2022-06-16 Abb Switzerland Ltd. Valve train with hydraulic delay element for an internal combustion engine

Also Published As

Publication number Publication date
KR101628424B1 (ko) 2016-06-08
CN102414402B (zh) 2014-03-12
EP2425104B1 (fr) 2014-04-09
CN102414402A (zh) 2012-04-11
KR20120016068A (ko) 2012-02-22
FI121512B (fi) 2010-12-15
FI20095462A (fi) 2010-10-28
EP2425104A1 (fr) 2012-03-07
FI20095462A0 (fi) 2009-04-27

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