EP2834481B1 - Actionneur hydraulique - Google Patents

Actionneur hydraulique Download PDF

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Publication number
EP2834481B1
EP2834481B1 EP13711448.4A EP13711448A EP2834481B1 EP 2834481 B1 EP2834481 B1 EP 2834481B1 EP 13711448 A EP13711448 A EP 13711448A EP 2834481 B1 EP2834481 B1 EP 2834481B1
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EP
European Patent Office
Prior art keywords
piston
pressurizing chamber
actuator
input portion
hydraulic
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EP13711448.4A
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German (de)
English (en)
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EP2834481A1 (fr
Inventor
Saku Niinikangas
Magnus Sundsten
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Wartsila Finland Oy
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Wartsila Finland Oy
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Publication of EP2834481A1 publication Critical patent/EP2834481A1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/025—Injectors structurally combined with fuel-injection pumps characterised by the pump drive hydraulic, e.g. with pressure amplification
    • 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 actuator for an internal combustion engine, as defined in the preamble of claim 1.
  • the invention also concerns the use of the hydraulic actuator, as defined in the other independent claims.
  • the gas exchange valves can be either mechanically or hydraulically actuated.
  • the most conventional way to operate the intake and exhaust valves is to use cam-driven valve opening mechanisms, where the valves are opened by the lobe of a rotating cam and closed by valve springs.
  • cam-driven valve opening mechanisms where the valves are opened by the lobe of a rotating cam and closed by valve springs.
  • Valve timing is difficult to adjust and if variable valve closing or opening timing is needed, valve mechanisms become complicated.
  • valve timing can be changed easily. However, the flexibility is often achieved at the cost of reduced reliability. Hydraulic actuators can also be used for actuating other devices of internal combustion engines, such as gas injection valves.
  • An object of the present invention is to provide an improved hydraulic actuator for an internal combustion engine.
  • the characterizing features of the actuator according to the invention are given in the characterizing part of claim 1.
  • the invention also concerns the use of such an actuator.
  • the hydraulic actuator comprises a pressurizing chamber for pressurizing hydraulic fluid, a reciprocating piston that is arranged in the pressurizing chamber and which piston divides the pressurizing chamber into at least one input portion and at least one output portion, at least one inlet port, which inlet port opens into the input portion of the pressurizing chamber for introducing pressurized hydraulic fluid into the input portion for moving the piston, and a fluid outlet for supplying hydraulic fluid from the output portion of the pressurizing chamber to the actuated device.
  • the piston comprises a cylindrical part that is provided with at least one opening on its outer surface, through which opening the hydraulic fluid can be introduced from the inlet port into the input portion of the pressurizing chamber.
  • the construction of the hydraulic actuator provides good possibilities for throttling of the inflow into the pressurizing chamber and/or the outflow from the chamber. This makes the construction durable and allows smooth opening and closing curves of the actuated devices.
  • the cross-sectional flow area between the inlet port and the opening of the piston is smaller at the end of the movement of the piston from the input portion end of the pressurizing chamber to the output portion end than in the middle of the movement. This slows down the piston when it approaches the end of the pressurizing chamber at the end of the pressurizing stroke, and also at the beginning of the return stroke.
  • the flow area can be smaller also at the beginning of the pressurizing stroke for slowing down the piston at the beginning of the pressurizing stroke and when the piston approaches the input portion end of the pressurizing chamber at the end of the return stroke.
  • the inlet can also be used for releasing hydraulic fluid from the inlet portion of the pressurizing chamber during the return stroke of the piston.
  • a separate outlet port is thus not needed.
  • the actuator can also comprise a separate outlet port into which outlet port hydraulic fluid can be introduced through the opening of the piston for releasing hydraulic fluid from the inlet portion of the pressurizing chamber during the return stroke of the piston.
  • the cross-sectional flow area between the outlet port and the opening of the piston is smaller at the end of the movement of the piston from the output portion end of the pressurizing chamber to the input portion end than in the middle of the movement. According to another embodiment, the cross-sectional flow area between the outlet port and the opening of the piston is smaller also at the beginning of the movement of the piston.
  • the outer surface of the cylindrical part of the piston is provided with a circumferential groove that is in flow communication with the opening of the piston.
  • the inner surface of the input portion of the pressurizing chamber is provided with a circumferential groove that is in flow communication with the inlet port. If the actuator is provided with a separate outlet port, the inner surface of the input portion of the pressurizing chamber can be provided with a circumferential groove that is in flow communication with the outlet port. The grooves enable different throttling effects at the end and/or at the beginning of the movements of the piston.
  • the groove of the piston or of the pressurizing chamber comprises at least one edge portion having a smaller depth than the middle part of the groove.
  • the groove comprises a first edge portion, a second edge portion and a middle part that is arranged between the edge portions, each of the edge portions having a smaller depth than the middle part. If the grooves are provided with edge portions with smaller depths than the middle part of the groove, the flow into or out of the pressurizing chamber is very small at the beginning and at the end of the movement of the piston.
  • the hydraulic actuator can be used, for instance, for opening gas exchange valves or fuel injection valves, such as gas injection valves, of an internal combustion engine.
  • the hydraulic actuator according to the invention can be used in large internal combustion engines, such as in main or auxiliary engines of ships or in engines that are used at power plants for producing electricity.
  • the hydraulic actuator can be used, for instance, for opening gas exchange valves or fuel injection valves, such as gas injection valves, of an engine.
  • FIGS 2-6 are shown different gas exchange valve arrangements, which comprise a hydraulic actuator 35 according to the invention.
  • Each gas exchange valve arrangement comprises gas exchange valves 1, 1', which open and close flow communication between a gas exchange duct 2 and a cylinder of the engine.
  • the gas exchange valves 1, 1' can be either intake valves or exhaust valves, and the gas exchange duct 2 is thus either an intake duct or an exhaust duct.
  • the arrangement comprises a first gas exchange valve 1 and a second gas exchange valve 1'.
  • each cylinder of the engine is provided with a gas exchange valve arrangement.
  • the gas exchange valves 1, 1' are arranged in the cylinder head 4 of the respective cylinder.
  • Each gas exchange valve 1, 1' comprises a valve stem 1b, 1b' and a valve head 1a, 1a'.
  • the valve head 1a, 1a' co-operates with a corresponding valve seat 1d, 1d'.
  • a valve spring 16, 16' is arranged around the valve stem 1b, 1b' of each gas exchange valve 1, 1' for closing the gas exchange valve 1, 1'.
  • the cylinder head 4 is provided with valve guides 17, 17' for accommodating the gas exchange valves 1, 1'.
  • each gas exchange valve arrangement comprises a hydraulic actuator 35.
  • the hydraulic actuator 35 comprises a pressurizing chamber 9, in which a piston 7 is arranged.
  • the piston 7 divides the pressurizing chamber 9 into at least one input portion 9a and at least one output portion 9b.
  • the pressurizing chamber 9 is divided into one input portion 9a and into a first and a second output portion 9b, 9b'.
  • the piston 7 can reciprocate in the pressurizing chamber 9. When pressure medium is introduced into the input portion 9a of the pressurizing chamber 9, the piston 7 pressurizes hydraulic fluid on the output side 9b, 9b' of the pressurizing chamber 9.
  • a returning spring 18 is arranged in the pressurizing chamber 9 for pushing the piston 7 towards the input portion 9a of the pressurizing chamber 9.
  • the return stroke of the piston 7 can be implemented by using hydraulic fluid that is introduced into the output portion 9b of the pressurizing chamber 9.
  • the gas exchange valve arrangement comprises a hydraulic valve 10 for opening and closing flow communication between a pressure source, such as a hydraulic pump 12, and the input portion 9a of the pressurizing chamber 9.
  • the hydraulic valve 10 also prevents and allows outflow from the input portion 9a of the pressurizing chamber 9.
  • the hydraulic valve 10 is arranged between a hydraulic pump 12 and the input portion 9a of the pressurizing chamber 9.
  • the hydraulic actuator 35 further comprises fluid outlets 9d, 9d' for supplying hydraulic fluid from the output portions 9b, 9b' of the pressurizing chamber 9 to the gas exchange valves 1, 1'.
  • a driven piston 1c, 1c' is arranged in mechanical connection with the valve stem 1b, 1b' of each gas exchange valve 1, 1'.
  • the gas exchange valve 1, 1' is thus moved together with the driven piston 1c, 1c'.
  • the driven piston 1c, 1c' is arranged in a receiving chamber 5, 5' that is in fluid communication with the output portion 9b, 9b' of the pressurizing chamber 9.
  • the first output portion 9b of the pressurizing chamber 9 is connected with a first connecting duct 6 to the receiving chamber 5 of the first gas exchange valve 1, and the second output portion 9b' of the pressurizing chamber 9 is connected with a second connecting duct 6' to the receiving chamber 5' of the second gas exchange valve 1'. Since the hydraulic actuator 35 is provided with an own output portion 9b, 9b' for each of the gas exchange valves 1, 1', the pressurized hydraulic fluid is supplied simultaneously to both of the gas exchange valves 1, 1'.
  • an intermediate duct 20 is arranged between the hydraulic valve 10 and the pressurizing chamber 9 for connecting the input portion 9a of the pressurizing chamber 9 to the hydraulic valve 10.
  • the hydraulic valve 10 is a hydraulically actuated slide valve.
  • the hydraulic valve 10 is a three-way valve that comprises a first port 10a that is connected to the inlet duct 15, a second port 10b that is connected to the outlet duct 21, and a third port 10c that is connected to the intermediate duct 20.
  • An inlet port 20a connects the intermediate duct 20 to the input portion 9a of the pressurizing chamber 9.
  • the hydraulic valve 10 comprises a spindle 22 that has a first position and a second position.
  • the hydraulic valve 10 is provided with a spring 19 that keeps the spindle 22 in the first position when the hydraulic valve 10 is not actuated.
  • a control valve 11 is a hydraulic valve that is operated with a solenoid.
  • the control valve 11 could also be some other kind of electrically actuated valve.
  • the receiving chamber 5, 5' is arranged around the valve stem 1b, 1b' and the driven piston 1c, 1c' is a projection of the valve stem 1b, 1b'. This arrangement enables compact design of the cylinder head 4.
  • the output portion end of the piston 7 is formed a solid cylindrical part 7b and the input portion end of the piston 7 is formed of a hollow cylindrical part 7a.
  • the input portion end of the solid cylinder 7b forms a surface onto which the pressure of the hydraulic fluid is applied.
  • the hydraulic fluid is introduced into the input portion 9a of the pressurizing chamber 9 through the surface of the hollow cylindrical part 7a.
  • the hollow cylindrical part 7a is therefore provided with at least one opening 13b.
  • the piston 7 is also provided with a circumferential groove 13a that is in fluid communication with the opening 13b of the piston 7.
  • the inlet port 20a of the hydraulic actuator 35 is thus in fluid communication with the opening 13b through the groove 13a. Because of the groove 13a that is arranged around the whole outer circumference of the hollow cylindrical part 7a, flow through the drillings 13b is allowed in any angular position of the piston 7.
  • the groove 13a widens towards the outer surface of the hollow cylindrical part 7a and is only partially aligned with the inlet port 20a when the piston 7 is at the input portion end of the pressurizing chamber 9.
  • the cross-sectional flow area between the inlet port 20a and the opening 13b of the piston 7 is smaller at the beginning of the movement of the piston 7 from the input portion end of the pressurizing chamber 9 to the output portion end than in the middle of the movement. Therefore, the flow into the input portion 9a of the pressurizing chamber 9 is throttled when the hydraulic valve 10 is moved into the second position and fluid supply from the hydraulic pump 12 into the pressurizing chamber 9 is allowed. Consequently, the piston 7 accelerates smoothly.
  • the piston 7 further comprises a boring 39, which connects the input portion 9a of the pressurizing chamber 9 to the output portion 9b.
  • a second boring 40 connects the input portion 9a to the second output portion 9b'.
  • the input portion 9a and the output portions 9b, 9b' of the pressurizing chamber 9 are also provided with air removal ports 41, 42, 43 for removing air from the hydraulic system.
  • the diameters of the air removal ports 41, 42, 43 are small for preventing excessive leakage of the hydraulic fluid.
  • the air removal ports 41, 42, 43 can also be provided with throttles 41a, 42a, 43a for reducing leaking of the hydraulic fluid, as shown in figure 4 .
  • the arrangement shown in figure 3 differs from the arrangement of figures 1 and 2 in terms of the construction of the hydraulic valve 10.
  • the hydraulic valve 10 of figure 3 comprises a fourth port 10d.
  • the hydraulic actuator 35 comprises a first intermediate duct 20 and a second intermediate duct 28.
  • the first port 10a of the hydraulic valve 10 is connected to the inlet duct 15 and the third port 10c is connected to the first intermediate duct 20.
  • the second port 10b is connected to the outlet duct 21 and the fourth port 10d is connected to the second intermediate duct 28.
  • An outlet port 28a connects the input portion 9a of the pressurizing chamber 9 to the second intermediate duct 28.
  • the spindle 22 In the first position of the hydraulic valve 10, the spindle 22 allows flow from the inlet duct 15 into the first intermediate duct 20 and prevents flow from the second intermediate duct 28 into the outlet duct 21. In the second position of the hydraulic valve 10, the spindle 22 allows flow from the second intermediate duct 28 into the outlet duct 21 and prevents flow from the inlet duct 15 into the second intermediate duct 28. Hydraulic fluid is introduced into the input portion 9a of the pressurizing chamber 9 through the first intermediate duct 20. The hydraulic fluid is released from the input portion 9a of the pressurizing chamber 9 through the outlet port 28a and the second intermediate duct 28. In the arrangement of figure 3 , separate fluid supply to the control valve 11 is not needed.
  • the inlet duct 15 is connected with a control duct 26 to a fluid chamber 27 that is arranged at one end of the spindle 22. Together with the spring 19 of the hydraulic valve 10, the pressure in the fluid chamber 27 keeps the hydraulic valve 10 in the first position, when the control valve 11 is closed. When the control valve 11 is opened, hydraulic fluid is released from the fluid chamber 27 and the hydraulic valve 10 is switched into the second position.
  • the driven piston 1c, 1c' is arranged at the end of the valve stem 1b, 1b'.
  • the hydraulic valve 10 is identical to the hydraulic valve 10 of figure 3 .
  • the first and the second intermediate ducts 20, 28 are merged into a combined intermediate duct 36 before the pressurizing chamber 9.
  • a third intermediate duct 37 and a fourth intermediate duct 38 are branched from the combined intermediate duct 36 and connected to the input portion 9a of the pressurizing chamber 9.
  • the diameters of the third intermediate duct 37 and the fourth intermediate duct 38 are smaller than the diameter of the combined intermediate duct 36.
  • the third and the fourth intermediate ducts 37, 38 are provided with check valves 24, 25. Through the third intermediate duct 37, flow from the combined intermediate duct 36 into the pressurizing chamber 9 is allowed.
  • the third intermediate duct 37 is located so that when the piston 7 is at the input portion end of the pressurizing chamber 9, the groove 13a of the piston 7 is aligned with the end of the third intermediate duct 37 and direct flow from the combined intermediate duct 36 into the pressurizing chamber 9 is prevented.
  • the fourth intermediate duct 38 flow from the pressurizing chamber 9 into the combined intermediate duct 36 is allowed.
  • the fourth intermediate duct 38 is located so that when the piston 7 is at the output portion end of the pressurizing chamber 9, the opening 13a of the piston 7 is aligned with the fourth intermediate duct 38 and direct flow from the pressurizing chamber 9 into the combined intermediate duct 36 is prevented. Flow speed is thus restricted at the beginning and at the end of the stroke of the piston 7 and smooth acceleration and deceleration is achieved.
  • the inlet duct 15 is provided with an adjustable throttle 30.
  • the outlet duct 21 is provided with an adjustable throttle 31.
  • the input portion 9a of the pressurizing chamber 9 is provided with a second piston 7'.
  • the second piston 7' has larger diameter and a shorter stroke than the first piston 7. Since the second piston 7' assists the first piston 7, smaller hydraulic pressure is needed at the beginning of the stroke of the first piston 7. Smaller hydraulic pressure decreases energy consumption of the arrangement.
  • the arrangement of figure 5 differs from the arrangement of figure 4 in that the arrangement is provided with a pressure accumulator 32 for energy recovery.
  • the pressure accumulator 32 is connected to the outlet duct 21 upstream from the throttle 31.
  • the pressure accumulator 32 is also connected to the inlet duct 15 upstream from the throttle 30 and downstream from the hydraulic pump 12 and the pressure accumulator 32.
  • a second hydraulic pump 12b is arranged downstream from the hydraulic pump 12 and from the pressure accumulator 32
  • a check valve 33 is arranged between the pressure accumulator 32 and the outlet duct 21 for preventing flow from the first hydraulic pump 12 or the pressure accumulator 32 into the outlet duct 21.
  • the first hydraulic pump 12 supplies hydraulic fluid at a smaller pressure level than is needed for operating the piston 7.
  • the pressure of the flow from the first hydraulic pump 12 and from the pressure accumulator 32 is raised to the sufficient level by the second hydraulic pump 12b.
  • the hydraulic valve 10 is a solenoid valve. Since the flow capacity of a single solenoid valve is small, the arrangement is provided with a second solenoid valve 10b that is arranged in parallel with the first solenoid valve 10.
  • the valves 10, 10b could also be other electrically actuated valves.
  • the input portion 9a of the pressurizing chamber 9 is provided with a circumferential groove 13c that is in fluid communication with the inlet port 20a.
  • the groove 13c is provided with a first edge portion 13d, a second edge portion 13e and a middle part 13f that is arranged between the edge portions 13d, 13e.
  • Each of the edge portions 13d, 13e has a smaller depth than the middle part 13f.
  • the same shape of the groove could also be applied to a groove 13a that is arranged around the piston 7. If the hydraulic actuator 35 is provided with a separate outlet port 28a, there could be a groove in connection with the outlet port 28a.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Valve Device For Special Equipments (AREA)
  • Actuator (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)

Claims (15)

  1. Actionneur hydraulique (35) pour un moteur à combustion interne, lequel actionneur hydraulique (35) comprend
    - une chambre de pressurisation (9) pour pressuriser un fluide hydraulique,
    - un piston d'entraînement (7) qui est disposé dans la chambre de pressurisation (9) et lequel piston d'entraînement (7) divise la chambre de pressurisation (9) en au moins une partie d'entrée (9a) et au moins une partie de sortie (9b),
    - au moins un orifice d'entrée (20a), lequel orifice d'admission (20a) donne dans une partie d'entrée (9a) de la chambre de pressurisation (9) pour introduire le fluide hydraulique pressurisé dans la partie d'entrée (9a) pour déplacer le piston (7), et
    - une sortie de fluide (9d) pour acheminer le fluide hydraulique de la partie de sortie (9b) de la chambre de pressurisation (9) au dispositif actionné (1, 1'),
    caractérisé en ce que le piston (7) comprend une partie cylindrique (7a) qui est dotée d'au moins une ouverture (13b) sur sa surface extérieure, ouverture (13b) à travers laquelle le fluide hydraulique peut être introduit depuis l'orifice d'admission (20a) dans la partie d'entrée (9a) de la chambre de pressurisation (9).
  2. Actionneur (35) selon la revendication 1, caractérisé en ce que la zone d'écoulement transversale entre l'orifice d'admission (20a) et l'ouverture (13b) du piston (7) est plus petite à l'extrémité de la course du piston (7) de l'extrémité de la partie d'entrée de la chambre de pressurisation (9) à l'extrémité de la partie de sortie qu'au centre de la course.
  3. Actionneur (35) selon la revendication 1 ou 2, caractérisé en ce que la zone d'écoulement transversale entre l'orifice d'admission (20a) et l'ouverture (13b) du piston (7) est plus petite au début de la course du piston (7) de l'extrémité de la partie d'entrée de la chambre de pressurisation (9) à l'extrémité de la partie de sortie qu'au centre de la course.
  4. Actionneur (35) selon l'une quelconque des revendications 1 à 3, caractérisé en ce que l'orifice d'admission (20a) est également utilisé pour libérer le fluide hydraulique de la partie d'entrée (9a) de la chambre de pressurisation (9) pendant la course de retour du piston (7).
  5. Actionneur (35) selon l'une quelconque des revendications 1 à 3, caractérisé en ce que l'actionneur (35) comprend un orifice d'évacuation séparé (28a), orifice d'évacuation (28a) dans lequel le fluide hydraulique peut être introduit par l'ouverture (13b) du piston (7) pour libérer le fluide hydraulique de la partie d'entrée de la chambre de pressurisation (9) pendant la course de retour du piston (7) .
  6. Actionneur (35) selon la revendication 5, caractérisé en ce que la zone d'écoulement transversale entre l'orifice d'évacuation (28a) et l'ouverture (13b) du piston (7) est plus petite à l'extrémité de la course du piston (7) de l'extrémité de la partie de sortie de la chambre de pressurisation (9) à l'extrémité de la partie d'entrée qu'au centre de la course.
  7. Actionneur (35) selon la revendication 5 ou 6, caractérisé en ce que la zone d'écoulement transversale entre l'orifice d'évacuation (28) et l'ouverture (13b) du piston (7) est plus petite au début de la course du piston (7) de l'extrémité de la partie de sortie de la chambre de pressurisation (9) à l'extrémité de la partie d'entrée qu'au centre de la course.
  8. Actionneur (35) selon l'une quelconque des revendications précédentes, caractérisé en ce que la surface extérieure de la partie cylindrique (7a) du piston (7) est dotée d'une rainure circonférentielle (13a) qui est en communication d'écoulement avec l'ouverture (13b) du piston (7) .
  9. Actionneur (35) selon l'une quelconque des revendications précédentes, caractérisé en ce que la surface intérieure de la partie d'entrée (9a) de la chambre de pressurisation (9) est dotée d'une rainure circonférentielle (13c) qui est en communication d'écoulement avec l'orifice d'évacuation (28a).
  10. Actionneur (35) selon l'une quelconque des revendications 5 à 7, caractérisé en ce que la surface intérieure de la partie d'entrée (9a) de la chambre de pressurisation (9) est dotée d'une rainure circonférentielle qui est en communication d'écoulement avec l'orifice d'évacuation (28a).
  11. Actionneur (35) selon l'une quelconque des revendications 8 à 10, caractérisé en ce que la rainure (13a, 13c) du piston (7) ou la chambre de pressurisation (9) comprend au moins une partie de bord (13d, 13e) ayant une profondeur plus petite que la partie centrale (13f) de la rainure (13a, 13c).
  12. Actionneur (35) selon la revendication 11, caractérisé en ce que la rainure (13a, 13c) comprend une première partie de bord (13d), une deuxième partie de bord (13e) et une partie centrale (13f) qui est aménagée entre les parties de bord (13d, 13e), chacune des parties de bord (13d, 13e) ayant une profondeur plus petite que la partie centrale (13f).
  13. Utilisation d'un actionneur hydraulique (35) selon l'une quelconque des revendications 1 à 12 pour actionner une soupape d'échange de gaz (1, 1') d'un moteur à combustion interne.
  14. Utilisation d'un actionneur (35) selon l'une quelconque des revendications 1 à 12 pour actionner une soupape d'injection de carburant d'un moteur à combustion interne.
  15. Utilisation d'un actionneur hydraulique (35) selon la revendication 14, caractérisée en ce que la soupape d'injection de carburant est une soupape d'injection de gaz.
EP13711448.4A 2012-03-09 2013-02-26 Actionneur hydraulique Active EP2834481B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20125255A FI124350B (en) 2012-03-09 2012-03-09 Hydraulic actuator
PCT/FI2013/050214 WO2013132150A1 (fr) 2012-03-09 2013-02-26 Actionneur hydraulique

Publications (2)

Publication Number Publication Date
EP2834481A1 EP2834481A1 (fr) 2015-02-11
EP2834481B1 true EP2834481B1 (fr) 2016-02-24

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EP13711448.4A Active EP2834481B1 (fr) 2012-03-09 2013-02-26 Actionneur hydraulique

Country Status (5)

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EP (1) EP2834481B1 (fr)
KR (1) KR101990275B1 (fr)
CN (1) CN104145092B (fr)
FI (1) FI124350B (fr)
WO (1) WO2013132150A1 (fr)

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JP4686561B2 (ja) * 2008-02-14 2011-05-25 エムエーエヌ・ディーゼル・アンド・ターボ・フィリアル・アフ・エムエーエヌ・ディーゼル・アンド・ターボ・エスイー・ティスクランド 大型２サイクルディーゼルエンジン用の排気弁アクチュエータ

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CN104145092A (zh) 2014-11-12
KR20140129362A (ko) 2014-11-06
KR101990275B1 (ko) 2019-06-19
FI124350B (en) 2014-07-15
FI20125255A (fi) 2013-09-10
WO2013132150A1 (fr) 2013-09-12
EP2834481A1 (fr) 2015-02-11
CN104145092B (zh) 2016-10-12

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