EP2815088B1 - Agencement de soupape hydraulique pour actionner de façon commandée une soupape d'échange de gaz d'un moteur à combustion interne à piston - Google Patents

Agencement de soupape hydraulique pour actionner de façon commandée une soupape d'échange de gaz d'un moteur à combustion interne à piston Download PDF

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Publication number
EP2815088B1
EP2815088B1 EP13712817.9A EP13712817A EP2815088B1 EP 2815088 B1 EP2815088 B1 EP 2815088B1 EP 13712817 A EP13712817 A EP 13712817A EP 2815088 B1 EP2815088 B1 EP 2815088B1
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Prior art keywords
fluid
piston
valve
fluid chamber
gas exchange
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German (de)
English (en)
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EP2815088A1 (fr
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Håkan NYNÄS
Ilari HYÖTY
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Wartsila Finland Oy
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Wartsila Finland Oy
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Priority to EP15200820.7A priority Critical patent/EP3045689A3/fr
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    • 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

Definitions

  • the present invention relates to a hydraulic valve arrangement for controllably operating a gas exchange valve of an internal combustion piston engine, the arrangement comprising a body part having a working space into which an operating piston is arranged, which operating piston comprises at least a first and a second concentric piston parts, and in which body part a first fluid chamber is arranged bordered by radial surfaces of both the first and the second piston parts and having a volume that increases in response to the piston parts moving relative to the body part in a first direction, and a second fluid chamber is arranged bordered by radial surface of the second piston part having a volume that decreases in response to the second piston part moving relative to the body part in a first direction.
  • An internal combustion engine typically includes a plurality of gas exchange valves. These valves control the intake and exhaust gas flow through the combustion chamber(s) of the engine.
  • a typical engine will include at least one intake valve and at least one exhaust valve for each cylinder or combustion chamber of the engine.
  • the opening of each valve is timed to occur at a predetermined cam or crank shaft angle in the operating cycle of the engine. It's well known that it is beneficial to control the time that gas exchange valves of engine are open while the engine is running.
  • the maximum capacity of the engine may be effected by prolonging the time valves are open when running speed is high and when the maximum capacity is needed, for example.
  • the available engine torque can be increased at partial load and lower revolutions, for example, by choosing suitable opening times for the valves.
  • EP 140347381 B1 discloses an actuation assembly having a body, a valve moving piston arranged slidable relative to the body, and first, second, and third hydraulic chambers defined between the piston and the body, wherein the first and second chambers have volumes that decrease and the third chamber has a volume that increases in response to the piston moving relative to the body in a first direction.
  • US 2004055547 A1 shows a hydraulic actuator in which an operating piston is designed in such a way that the areal surface of at least one of the two effective areas changes along the sliding path of the operating piston. Specifically it shows an arrangement in which the piston has a plurality of parts and has two partial pistons which have different axial lengths and they are concentrically inserted inside each other so as to be movable relative to each another.
  • gas exchange valve may be rapidly opened with great displacement force, which then rapidly drops and remains constant over the rest of the valve lift by means of the inner piston only.
  • Hydraulic actuators provide extensive possibilities for controlling and adjusting the valve opening and closing during the operation of the engine.
  • a challenge of hydraulic gas exchange valve actuation is energy efficiency due to considerably high flow rates of hydraulic fluid.
  • a hydraulic valve arrangement for controllably operating a gas exchange valve of an internal combustion piston engine, the arrangement comprising a body part having a working space into which an operating piston is arranged, which operating piston comprises at least a first and a second concentric piston parts arranged slidably in respect to each other, and in which body part a first fluid chamber is arranged bordered by radial surfaces of both the first and the second piston parts and having a volume that increases in response to the piston parts moving relative to the body part in a first direction, and a second fluid chamber is arranged bordered by radial surface of the second piston part having a volume that decreases in response to the second piston part moving relative to the body part in a first direction. It is characteristic to the invention that the movement of the second piston part in the first direction relative to the body part is arranged independently from the first piston part controllable by a fluid control system arranged in connection with the hydraulic valve arrangement.
  • the fluid control system comprises a pressure line connected to a source of pressurized fluid and to the first fluid chamber and being provided with a pressure valve, and each of the fluid chambers having a volume that decreases in response to at least one of the piston parts moving relative to the body part in a first direction, is in controllable fluid communication with the pressure line.
  • the fluid control system comprises a fluid line connecting the second fluid chamber controllably to a low pressure part of the fluid control system.
  • a third fluid chamber is arranged being bordered by radial surfaces of at least the first piston part having a volume that decreases in response to the first piston part moving relative to the body part in a first direction.
  • the first and the third fluid chambers are selectively connectable to a pressurized hydraulic fluid source.
  • the radial surface of the first piston part bordering the first fluid chamber is smaller than the radial surface of the first piston part bordering the third fluid chamber and the radial surface of the first piston part bordering the third fluid chamber is smaller than the radial surface of the second piston part bordering the second fluid chamber.
  • first piston part is arranged freely movable in respect to the second piston part in the first direction and it is provided with a mechanical stop which delimits the movement of the second piston part in respect to the first piston part.
  • figure 1 there is schematically shown a hydraulic valve arrangement 10 for an internal combustion piston engine according to an embodiment of the invention.
  • the arrangement comprises a body part 12 into which a working space 14 is arranged.
  • the arrangement comprises further an operating piston 16 which is arranged into the working space.
  • the operating piston is in force transmission connection with a gas exchange valve 18 of the engine.
  • the operating piston 16 is arranged movably in the working space 14 so that it may move in first direction which causes opening movement of the gas exchange valve 18 and respectively in second direction opposite to the first direction which causes closing movement of the gas exchange valve 18.
  • the working space 14 is arranged rotationally symmetrical manner in respect to its central axis 20.
  • the working space extends as a guiding section 22 at its one end which has inner diameter selected in respective to the outer diameter of the operating piston 16 at corresponding area so that desired guiding effect for the piston 16 is achieved.
  • the operating piston 16 comprises at least a first 16.1 and a second 16.2 concentric piston parts.
  • the first and the second piston parts 16.1, 16.2 are arranged slidably in respect to each other so that the movement of the second piston part 16.2 in the first direction relative to the first part is delimited by a mechanical stop 50 arranged to the first piston part 16.1.
  • a second mechanical stop 51 arranged to the body part 12 which cooperates with the second piston part 16.2
  • the second stop limits the movement of the second piston part 16.2 in the second direction to a predetermined position in respect to the body part 12.
  • the second stop defines the initial position of the second piston part 16.2.
  • the piston parts are arranged controllable by a fluid control system 24 arranged in connection with the hydraulic valve arrangement.
  • valve arrangement 10 which identical to that shown in figure 1 described above but which is controllable by a fluid control system 24 which allow more sophisticated control of the valve arrangement.
  • the second piston part 16.2 is assisting the movement of the first piston part 16.1 in the first direction when the valve 18 is to be opened.
  • the first piston part 16.1 pushes the second piston part back to its initial position against the second mechanical stop 51.
  • first fluid chamber 14.1 arranged in the working space partially bordered by radial surfaces 16.1', 16.2' of both the first and the second piston parts 16.1 16.2 at their first ends and having a volume that increases in response to either or both of the piston parts 16.1, 16.2 moving relative to the body part 14 in the first direction, that is downwards in the figures 1 and 2 .
  • the working space includes also a second fluid chamber 14.2 which is arranged in the working space partially bordered at least by radial surface 16.2" of the second piston part at its second end having a volume that decreases in response to the second piston part moving relative to the body part in the first direction being downwards direction in the figures1 and 2 .
  • radial surfaces 16.1', 16.2', 16.2" define effective areas so that 16.1' defines the area of the first end of the first piston part 16.1, 16.2' defines the area of the first end of the second piston part 16.2 and 16.2" defines the area of the second end of the second piston part when being against the mechanical stop 50 arranged to the first piston part in a form of shoulder.
  • the fluid control system 24 comprises a pressure line 26 connected to a source of pressurized fluid 28 and also to the first fluid chamber 14.1 and is provided with a pressure valve 30.
  • a pressure line 26 connected to a source of pressurized fluid 28 and also to the first fluid chamber 14.1 and is provided with a pressure valve 30.
  • the fluid control system 24 comprises a fluid line 38 having a valve 40 connecting the second fluid chamber 14.2 controllably to the low pressure part 36.
  • the valve 40 in the fluid line it is possible to control the flow of fluid from the second fluid chamber 14.2.
  • the fluid flow out from the second chamber defines the state of moving of the second piston part 16.2.
  • the second piston part 16.2 may not move even if the valve 30 is open. In that case only the piston part 16.1 moves and the piston part 16.2 substantially remains its current position representing to position when the valve 30 is closed.
  • the valve 30 may be controlled to be closed at any suitable moment during the movement of the piston 16 so that the movement of the second piston part 16.2 is moved along the first piston part 16.1 only to a desired extent.
  • the second fluid chamber 14.2 is additionally in controllable fluid communication 32 with the first fluid chamber 14.1.
  • this has been realized by controllable fluid communication 32 with pressure line 26 downstream the pressure valve 30 having a valve 31.
  • the pressurized fluid may be caused to effect on both ends of the second piston part 16.2. Since the radial surface 16.2' at the first end of the second piston part is bigger than the radial surface 16.2" at the second end of the second piston part at the initial position shown in figure 2 the force subjected by the second piston part 16.2 to the first piston part 16.1 is defined by the difference of the surface areas 16,2' and 16,2".
  • the effect of the second piston part 16.2 is controlled by opening the fluid flow communication from the second fluid chamber 14.2 to either to pressure line or the low pressure part 36 of the system or closing the fluid flow communication from the second fluid chamber 14.2.
  • the control valve 31 is open and the control valve 40 is closed and hydraulic fluid is fed to the first fluid chamber 14.1 hydraulic fluid is returned from the second fluid chamber 14.2 to the pressure line 26, and thus the needed flow rate from the pressurized hydraulic fluid source is smaller.
  • the stopping of the movement of the second piston part in the first direction relative to the body part is arranged independently from the first piston part. This also means stopping of the transmitting force from the second piston part to the first piston part. This feature is shown in all figures 1 - 3 .
  • the working space 14 and the first piston part 16.1 delimit a third fluid chamber 14.3 which is arranged partially bordered by radial surface 16.1" of at least the first piston part 16.1 the chamber having a volume that decreases in response to the first piston part moving relative to the body part in a first direction.
  • the third fluid chamber is selectively connectable by means of a fluid line 46 having a valve 42 to a pressurized hydraulic fluid source 28 which facilitates the movement of the piston in the second direction i.e. the direction causing the movement of the gas exchange valve 18 in its closing direction.
  • the pressure line i.e. the first chamber 14.1 is also selectively connectable by means of a fluid line having a valve 62 to the low pressure part 36 of the system.
  • the third fluid chamber 14.3 is also in controllable fluid communication 44 with the first fluid chamber 14.1.
  • this has been realized by controllable fluid communication 44 with the pressure line 26 downstream the pressure valve 30 having a valve 43.
  • the pressurized hydraulic fluid may be caused to effect on first end of the first piston part 16.1 and its radial surface 16.1". Since the radial surface 16.1' at the first end of the first piston part is bigger than the radial surface 16.1" bordering the third chamber the force subjected to the first piston part 16.1 is defined by the difference of the surface areas when the communication from the third chamber to the pressure line 26 is open.
  • the effect of the first piston part 16.1 is controlled by opening the fluid flow communication from the third fluid chamber 14.3 to either to pressure line or the low pressure part 36 of the system.
  • the third chamber 14.3 connected to the low pressure part 36 by a line 46 provided with a control valve 48.
  • the second chamber 14.2 is controllably connected to the low pressure part 36 by a fluid line 38 provided with a control valve 40.
  • each of the fluid chambers which has a volume that decreases in response to at least one of the piston parts moving relative to the body part in a first direction is in controllable fluid communication with the pressure line downstream the pressure valve, that is at the side of the first fluid chamber.
  • figure 1 and figure 2 Since the arrangement of figure 1 and figure 2 includes two piston parts, and it is possible to select the way their effective areas are utilized in applying different forces to the piston 16 by several combinations of suitably opened and closed control valves. In practise the benefit in this arrangement is to have selectable effective area i.e. combined radial surfaces in the working space 14. This way, depending e.g. on the engine load, the engine automation may select what effective area is used. When the effective area is chosen so that the force produced by the hydraulic pressure equals the restricting forces, the required hydraulic flow is minimized, thus saving energy. If the effective area is bigger than what is required by the forces, the needed hydraulic flow is also bigger and the system consumes extra energy, which is minimized by the present invention.
  • the hydraulic cylinder has at least three fluid chambers 14.1, 14.2, 14.3.
  • the chamber 14.1 on top in the figure 1 and figure 2 is for pressing the piston 16 down which movement opens the gas exchange valve 18.
  • the third chamber 14.3 in the figure is used also for pressing the piston up which closes the gas exchange valve.
  • the second i.e. middle chamber 14.2 is a control volume.
  • the hydraulic fluid e.g. oil
  • the hydraulic fluid in the second chamber 14.2 may not flow out while the inner piston tends to move down.
  • the second piston part 16.2 cannot move, and so the only member doing the work is the first piston part 16.1.
  • the produced force is the surface area 16.1' hydraulic pressure in the chamber 14.1.
  • the third chamber 14.3 volume is connected to the low pressure part 36 (tank). If a greater force is required (engine load is for example maximum), the second volume 14.2 control valve 40 is opened connecting the second volume 14.2 to the low pressure part 36 and both piston parts move down, the outer piston part 16.2 pressing the inner piston part 16.1. Now the effective force is obtained by the combined piston areas 16.1' and 16.2'.
  • the system may be provided with more pistons part and radial surfaces than two.
  • the third chamber 14.3 is pressurized when the piston is returned to the initial position.
  • the first chamber 14.1 is connected to the low pressure part 36 (tank).
  • the valve 31 is opened. This makes is possible that fluid from both chambers 14.1 and 14.2 may flow to the low pressure part 36 either through the valve 62 or the valve 40 (or both), This way the piston 16 may be return back to its initial position even if either of the valve 62 or 40 is inoperative.
  • the first chamber 14.1 and the second chamber 14.2 are selectably and/or controllably connected the low pressure part 36 because operational selections may be made by means of the control valve 31.
  • the returning of the gas exchange valve requires much less force because there isn't an engine pressure restricting the movement. Because of that, the area causing the return movement may be smaller than the area causing the movement in the first direction.
  • the arrangement of the figure 1 and figure 2 allows adjusting the actuator effective area for each load case.
  • Valve 30 is open in all combinations. Available forces depend on the actual dimensioning of the areas and also hydraulic pressure used.
  • pressure accumulator system 55 selectively connectable by means of valve 56 and 57 to the pressure line 26 and the line 46 in connection with the low pressure part 36 of the system.
  • FIG 3 there is shown another embodiment of the invention where three piston parts, the first part 16.1, the second piston part 16.2, and a third piston part 16.3, are arranged in coaxial manner.
  • corresponding reference numbering to those in figure 1 and figure 2 for corresponding elements.
  • Each of the fluid chambers 14.2, 14.3 and 14.4 which have a volume that decreases in response to at least one of the piston parts moving relative to the body part in a first direction is in controllable fluid communication 27,32,44 having a control valve 29,31,43 with the pressure line 26 downstream the pressure valve.
  • the fluid control system 24 comprises a fluid line 23 having a valve 25 connecting also the fourth fluid chamber 14.4 controllably to the low pressure part 36.
  • An inner coaxial piston part and an outer coaxial piston part are so arranged that the movement of the outer coaxial piston part is limited to a predetermined longitudinal position in respect to the inner coaxial piston part.
  • the movement of the outer coaxial piston part is limited preferably by the form of the opposing surfaces of the inner coaxial piston part and the outer coaxial piston part.
  • the arrangement may be provided with a spring element 60 urging the piston to move in the second direction for example in the third fluid chamber.

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

Claims (12)

  1. Agencement de soupape hydraulique (10) pour faire fonctionner de façon contrôlée une soupape d'échange gazeux d'un moteur à pistons à combustion interne, l'agencement comprenant une partie de corps (12) présentant un espace de travail (14) dans lequel un piston en fonctionnement (16) est agencé, lequel piston en fonctionnement comprend au moins des première et seconde parties de piston concentrique (16.1, 16.2), agencées en pouvant coulisser l'une par rapport à l'autre, et dans laquelle partie de corps, une première chambre de fluide (14.1) est agencée, bordée par des surfaces radiales (16.1', 16.2') à la fois des première et seconde parties de piston et présentant un volume qui augmente en réponse au déplacement des parties de piston (16.1, 16.2) par rapport à la partie de corps dans une première direction, et une deuxième chambre de fluide (14.2) est agencée, bordée par une surface radiale (16.2") de la seconde partie de piston, présentant un volume qui décroît en réponse au déplacement de la seconde partie de piston par rapport à la partie de corps dans la première direction, caractérisé en ce que le mouvement de la seconde partie de piston (16.2) dans la première direction par rapport à la partie de corps (12) est agencé en pouvant être commandé indépendamment de la première partie de piston (16.1) par une soupape (31, 40) dans un système de commande de fluide (24) agencé pour commander l'écoulement de fluide de la deuxième chambre de fluide (14.2).
  2. Agencement de soupape hydraulique (10) pour faire fonctionner de façon contrôlée une soupape d'échange gazeux selon la revendication 1, caractérisé en ce que le système de commande de fluide (24) comprend une ligne de pression (26) reliée à une source de fluide pressurisé (28) et également à la première chambre de fluide (14.1) et dotée d'une soupape de pression (30).
  3. Agencement de soupape hydraulique (10) pour faire fonctionner de façon contrôlée une soupape d'échange gazeux selon la revendication 2, caractérisé en ce que l'effet de la seconde partie de piston (16.2) est agencé en pouvant être commandé par l'ouverture de la communication d'écoulement de fluide de la deuxième chambre de fluide (14.2), soit vers la ligne de pression (26), soit vers la partie basse pression (36) du système, ou la fermeture de la communication d'écoulement de fluide de la deuxième chambre de fluide (14.2).
  4. Agencement de soupape hydraulique (10) pour faire fonctionner de façon contrôlée une soupape d'échange gazeux selon la revendication 2, caractérisé en ce que chacune des chambres de fluide (14.2, 14.3, 14.4) présente un volume qui décroît en réponse au déplacement d'au moins une des parties de piston (16.1, 16.2, 16.3) par rapport à la partie de corps (12) dans une première direction, est en communication de fluide pouvant être commandée avec la ligne de pression (26).
  5. Agencement de soupape hydraulique (10) pour faire fonctionner de façon contrôlée une soupape d'échange gazeux selon la revendication 1, caractérisé en ce que le système de commande de fluide (24) comprend une ligne de fluide (38) comprenant une soupape (40) reliant la deuxième chambre de fluide (14.2) par commande à une partie basse pression (36) du système de commande de fluide.
  6. Agencement de soupape hydraulique (10) pour faire fonctionner de façon contrôlée une soupape d'échange gazeux selon la revendication 1, caractérisé en ce que l'agencement comprend une troisième chambre de fluide (14.3) agencée en étant bordée par des surfaces radiales d'au moins la première partie de piston (16.1"), présentant un volume qui décroît en réponse au déplacement de la première partie de piston par rapport à la partie de corps dans une première direction, et en ce que les première et troisième chambres de fluide peuvent être reliées de façon sélective (30, 42) à une source de fluide hydraulique pressurisé (28).
  7. Agencement de soupape hydraulique (10) pour faire fonctionner de façon contrôlée une soupape d'échange gazeux selon la revendication 1, caractérisé en ce que la surface radiale (16.1') de la première partie de piston (16.1) bordant la première chambre de fluide (14.1) est plus petite que la surface radiale (16.1") de la première partie de piston bordant la troisième chambre de fluide (14.3) et que la surface radiale (16.1") de la première partie de piston bordant la troisième chambre de fluide (14.3) est plus petite que la surface radiale (16.2") de la seconde partie de piston (16.2) bordant la deuxième chambre de fluide (14.2).
  8. Agencement de soupape hydraulique (10) pour faire fonctionner de façon contrôlée une soupape d'échange gazeux selon la revendication 1, caractérisé en ce que la première partie de piston (16.1) est agencée en étant mobile librement par rapport à la seconde partie de piston (16.2) dans la première direction et est dotée d'une butée mécanique (50) qui délimite le mouvement de la seconde partie de piston (16.2) par rapport à la première partie de piston (16.1).
  9. Agencement de soupape hydraulique (10) pour faire fonctionner de façon contrôlée une soupape d'échange gazeux selon la revendication 1 ou 6, caractérisé en ce que la partie de corps (12) est dotée d'une seconde butée (51) en coopération avec la seconde partie de piston (16.2) qui limite le mouvement de la seconde partie de piston (16.2) dans la seconde direction vers une position prédéterminée.
  10. Agencement de soupape hydraulique (10) pour faire fonctionner de façon contrôlée une soupape d'échange gazeux selon la revendication 1, caractérisé en ce que l'agencement comprend une communication de fluide pouvant être commandée (32) entre la première chambre de fluide (14.1) et la deuxième chambre de fluide (14.2).
  11. Agencement de soupape hydraulique (10) pour faire fonctionner de façon contrôlée une soupape d'échange gazeux selon la revendication 1, caractérisé en ce que l'agencement comprend une communication de fluide pouvant être commandée (44) entre la première chambre de fluide (14.1) et la troisième chambre de fluide (14.3).
  12. Agencement de soupape hydraulique (10) pour faire fonctionner de façon contrôlée une soupape d'échange gazeux selon les revendications 3, 8 ou 9, caractérisé en ce que la communication de fluide pouvant être commandée (32) entre la première chambre de fluide (14.1) et la deuxième chambre de fluide (14.2) comprend une soupape de commande (31), et la communication de fluide pouvant être commandée (44) entre la première chambre de fluide (14.1) et la troisième chambre de fluide (14.3) comprend une soupape de commande (14.3), et que l'agencement fournit des zones actives avec des combinaisons de soupapes de commande (30, 40, 48, 31, 43) ouvertes et/ou fermées définissant une force appliquée au piston (16) avec une pression fluidique prédéterminée comme suit : Zones actives Soupape Soupape Soupape Soupape Soupape 30 40 48 31 43 16.1' on off on off off 16.1' + 16.2' on on on off off 16.1' + 16.2' - 16.2' on off on on off 16.1' + 16.2' - 16.1' on on off off on 16.1' + 16.2' - 16.2' - 16.1' on off off on on
EP13712817.9A 2012-02-16 2013-02-11 Agencement de soupape hydraulique pour actionner de façon commandée une soupape d'échange de gaz d'un moteur à combustion interne à piston Active EP2815088B1 (fr)

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Application Number Priority Date Filing Date Title
EP15200820.7A EP3045689A3 (fr) 2012-02-16 2013-02-11 Agencement de soupape hydraulique pour faire fonctionner de manière commandée une soupape d'échange gazeux d'un moteur à combustion interne à piston

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20125181A FI124245B (en) 2012-02-16 2012-02-16 Hydraulic valve arrangement for controlled actuation of the gas exchange valve of the reciprocating internal combustion engine
PCT/FI2013/050146 WO2013121100A1 (fr) 2012-02-16 2013-02-11 Agencement de soupape hydraulique pour actionner de façon commandée une soupape d'échange de gaz d'un moteur à combustion interne à piston

Related Child Applications (2)

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EP15200820.7A Division-Into EP3045689A3 (fr) 2012-02-16 2013-02-11 Agencement de soupape hydraulique pour faire fonctionner de manière commandée une soupape d'échange gazeux d'un moteur à combustion interne à piston
EP15200820.7A Division EP3045689A3 (fr) 2012-02-16 2013-02-11 Agencement de soupape hydraulique pour faire fonctionner de manière commandée une soupape d'échange gazeux d'un moteur à combustion interne à piston

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EP2815088A1 EP2815088A1 (fr) 2014-12-24
EP2815088B1 true EP2815088B1 (fr) 2016-02-10

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EP15200820.7A Withdrawn EP3045689A3 (fr) 2012-02-16 2013-02-11 Agencement de soupape hydraulique pour faire fonctionner de manière commandée une soupape d'échange gazeux d'un moteur à combustion interne à piston
EP13712817.9A Active EP2815088B1 (fr) 2012-02-16 2013-02-11 Agencement de soupape hydraulique pour actionner de façon commandée une soupape d'échange de gaz d'un moteur à combustion interne à piston

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EP15200820.7A Withdrawn EP3045689A3 (fr) 2012-02-16 2013-02-11 Agencement de soupape hydraulique pour faire fonctionner de manière commandée une soupape d'échange gazeux d'un moteur à combustion interne à piston

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EP (2) EP3045689A3 (fr)
KR (1) KR101946098B1 (fr)
CN (1) CN104169532B (fr)
FI (1) FI124245B (fr)
WO (1) WO2013121100A1 (fr)

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EP3126643B1 (fr) * 2014-03-06 2018-01-03 Wärtsilä Finland Oy Agencement de soupape d'échange de gaz
CN104632317A (zh) * 2015-01-30 2015-05-20 哈尔滨工程大学 一种大功率船用低速柴油机排气阀装置

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DE10024268B4 (de) * 2000-05-17 2012-11-29 Robert Bosch Gmbh Vorrichtung zur Benzindirekteinspritzung in einer Kolbenbrennkraftmaschine
DE10127205A1 (de) * 2001-06-05 2002-09-05 Bosch Gmbh Robert Nockenwellenlose Steuerung eines Gaswechselventils einer Brennkraftmaschine
DE10134644A1 (de) * 2001-07-17 2003-02-06 Bosch Gmbh Robert Elektrohydraulische Ventilsteuerung
DE10143959A1 (de) 2001-09-07 2003-03-27 Bosch Gmbh Robert Hydraulisch gesteuerter Aktuator zur Betätigung eines Ventils
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US6899068B2 (en) 2002-09-30 2005-05-31 Caterpillar Inc Hydraulic valve actuation system
DE10310300A1 (de) * 2003-03-10 2004-09-23 Robert Bosch Gmbh Verfahren zum Betreiben eines hydraulischen Aktors, insbesondere eines Gaswechselventils einer Brennkraftmaschine
DE102004022447A1 (de) * 2004-05-06 2005-12-01 Robert Bosch Gmbh Hydraulischer Steller und Verfahren zum Betreiben eines hydraulischen Stellers
DE102005025879A1 (de) * 2005-06-06 2006-12-07 Robert Bosch Gmbh Verfahren zur Angabe eines Druckverlaufs
DE102007025619B4 (de) * 2007-06-01 2012-11-15 Robert Bosch Gmbh Verfahren und Vorrichtung zur Steuerung eines hydraulischen Stellers
DE102008040840A1 (de) 2008-07-29 2010-02-04 Robert Bosch Gmbh Hydraulisch gesteuerter Aktor

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Publication number Publication date
EP3045689A2 (fr) 2016-07-20
CN104169532A (zh) 2014-11-26
WO2013121100A1 (fr) 2013-08-22
FI124245B (en) 2014-05-15
FI20125181A (fi) 2013-08-17
KR20140125431A (ko) 2014-10-28
CN104169532B (zh) 2016-06-22
KR101946098B1 (ko) 2019-02-08
EP2815088A1 (fr) 2014-12-24
EP3045689A3 (fr) 2016-11-16

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