EP1967706B1 - Actuateur hydraulique de soupape - Google Patents

Actuateur hydraulique de soupape Download PDF

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Publication number
EP1967706B1
EP1967706B1 EP08002785A EP08002785A EP1967706B1 EP 1967706 B1 EP1967706 B1 EP 1967706B1 EP 08002785 A EP08002785 A EP 08002785A EP 08002785 A EP08002785 A EP 08002785A EP 1967706 B1 EP1967706 B1 EP 1967706B1
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EP
European Patent Office
Prior art keywords
valve
valve drive
drive according
stroke
fluid
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.)
Not-in-force
Application number
EP08002785A
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German (de)
English (en)
Other versions
EP1967706A2 (fr
EP1967706A3 (fr
Inventor
Dieter Chvatal
Andreas Plöckinger
Rudolf Scheidl
Paul Foschum
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.)
Innio Jenbacher GmbH and Co OG
Original Assignee
GE Jenbacher GmbH and Co OHG
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Publication date
Application filed by GE Jenbacher GmbH and Co OHG filed Critical GE Jenbacher GmbH and Co OHG
Publication of EP1967706A2 publication Critical patent/EP1967706A2/fr
Publication of EP1967706A3 publication Critical patent/EP1967706A3/fr
Application granted granted Critical
Publication of EP1967706B1 publication Critical patent/EP1967706B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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 valve drive, in particular for gas exchange valves of internal combustion engines, with a movably mounted in a cylinder actuator, in particular pistons, for driving a valve, wherein in the working cylinder on one side of the actuating element at least one at least a first fluid line with at least a first pressure accumulator fluid-communicating first working volume is provided, wherein an at least two fluid lines switching, actively actuable control valve is disposed in the first fluid line, wherein at least one passive switching element for controlling a fluid flow, preferably non-return valve to the control valve in series or in parallel, wherein on a side of the actuating element opposite the first working volume, at least one fluid communicating with at least one second pressure accumulator for fluid via at least one second fluid line second working volume is provided in the working cylinder, wherein the actively actuable control valve is arranged in the first and in the second fluid line.
  • valve actuators From the EP 1215369 A2 are fully variable valve actuators known. These are predominantly based on the concept of a free oscillator and follow the basic idea to recover energy when braking the valve or the valve drive and store in the form of pressure to this pressure for the drive of the valve in a subsequent stroke, especially at the counter stroke again to use for the acceleration of the valve.
  • the basic idea is therefore to create particularly energy-saving valve drives for the opening and / or closing movement of a valve in the form of quasi-free oscillators.
  • Generic valve actuators reveal, for example, the DE 10 2004 030 306 A1 , the DE 10 2004 040 210 A1 or the WO 2006/108438 A1 ,
  • valve train With more than a single active actuated control valve and without active actuated control valve in the second line out.
  • the valve train has the possibility of Druck Eattang from the free oscillator by recovering the kinetic energy of the valve drive.
  • it is necessary to switch several electrically switched or pressure-controlled or path-controlled actively actuated control valves, if necessary, several times during an opening and closing stroke cycle of the valve drive. This leads to very complex structures.
  • the object of the invention is to minimize the number of required active actuated control valves and the number of switching operations per cycle.
  • valve drive has exactly one actively actuable control valve, wherein preferably during braking, kinetic energy of the valve drive, preferably the valve, by pressure build-up in the first pressure accumulator and / or in the second accumulator for a subsequent stroke of the valve is cacheable ,
  • passive switching elements in particular switching elements which are switched by means of the fluid flowing through them. You do not need an additional actuator, as is provided for actively operable control valves for switching. Frequently used, passive switching elements are for example check valves.
  • the inventive use of passive switching elements favorably only a single actively actuated control valve is needed. Moreover, it is also possible that this actively actuated control valve only has to be moved back and forth between two positions during an opening and closing cycle of the valve to be switched.
  • the working volume is a first working volume and the pressure accumulator is a first pressure accumulator and at least one on the first working volume opposite side of the actuating element at least one at least a second fluid line with at least a second pressure accumulator for fluid related second working volume is provided in the working cylinder wherein the actively actuable control valve is disposed in the first and second fluid conduits.
  • the second working volume and the second pressure accumulator can switch to this side of the actuating element, a spring or a constant back pressure.
  • the valve drive has exactly one actively actuated control valve.
  • the passive switching element (s) are / are arranged to control a fluid flow in the first and the second fluid line, preferably on the side of the actively actuable control valve facing the respective working volume.
  • a parallel connection can be provided in a favorable manner that the passive switching elements or, preferably in each case in at least one leading around the actively actuable control valve bypass line of the first and / or the second fluid conduit are arranged.
  • the actuating elements can be actuated hydraulically and / or pneumatically.
  • a general advantage it is when the valve actuators are designed such that preferably during braking, kinetic energy of the valve drive, preferably the valve, by pressure build-up in the first pressure accumulator and / or in the second pressure accumulator for a subsequent stroke of the valve is cacheable.
  • valve actuators described so far can be used particularly well for opening and closing valves in which approximately the same counterforce acts on the valve during the opening as well as during the closing stroke. This is the case, for example, with intake valves for combustion chambers of internal combustion engines. However, the situation is different for example in exhaust valves of combustion chambers, where in the prior art, a significant additional power consumption is created by the so-called gas counterforce in the combustion chamber.
  • This gas counterforce results from a residual pressure, which is still present when opening the exhaust valve from the previous cycle of the combustion chamber. Depending on the driving style and opening time, this residual pressure varies in size. But it can make up to 10 bars and more on the order of magnitude. against this pressure, the outlet valve must be opened.
  • the additional actuator is designed so that it acts on the valve only a portion, preferably at the beginning of the actuator to be executed by the opening and closing stroke.
  • a stop is provided for the additional actuator, which it reaches before the valve reaches one of its end positions.
  • the additional actuator can not be operated as a driving force with pressure derived from a combustion chamber, preferably an internal combustion engine. This avoids problems with the removal of combustion gases from the combustion chamber, which can lead to failure of such systems due to coking.
  • the additional actuators which can be used to support the actuating element can be designed in many different ways.
  • Favorable variants provide that they can be driven hydraulically and / or pneumatically and / or electrically and / or piezoelectrically and / or magnetically and / or electromagnetically.
  • Fig. 1 shown embodiment, two passive switching elements 30, 31 connected in the form of check valves to the control valve 29 in series.
  • the valve drive shown there serves to carry out the opening and closing stroke of the valve 22.
  • This may be, for example, an inlet valve in a combustion chamber of an internal combustion engine.
  • the shaft of the valve 22 is connected to the actuator 21 formed as a piston of the working cylinder 20.
  • the two pressure accumulators 27 and 28 are connected to the two working chambers 23 and 24 of the working cylinder 20.
  • the second pressure accumulator 28 is connected via the second fluid line 26 directly to the second working chamber 24 on the rod side of the working cylinder 20 and thereby always acts in the direction of the closing stroke of the valve 22.
  • the first pressure accumulator 27 is via the control valve 29 and the check valve as the 30th and 31 executed passive switching elements connected to the first working chamber 23.
  • the two pressure accumulators 27, 28 are brought to system pressure PS before the opening stroke of the valve 22. This is done for the second pressure accumulator 28 via the supply check valve 36 and the first pressure accumulator 27 on the Nach Stirllventilkante 37. This also ensures that the valve 22 is closed, the piston-side, first working volume 23 via the Ablassventilkante 38 and the diaphragm or Throttle 54 is drained into tank T.
  • FIG. 2a the path x (t) of the valve 22 during the opening and closing stroke are shown.
  • Fig. 2b shows the course p z2 of the pressure in the second pressure accumulator 28 and the course p z1 of the pressure in the first accumulator 27.
  • the stroke of the control valve is together with the opening phases of the individual valve edges 37, 38 and 39 over a duty cycle in Fig. 2c shown.
  • the solid line shows the course of the position of the control valve 29.
  • the dashed line shows the course of the connection 1 to 2, so the opening and closing course of the main valve edge 39.
  • the control valve 29 switched.
  • the Nach Glallventilkante 37 and the Ablassventilkante 38 and thus the connections 4 are closed according to 5 and 9 to 10.
  • the connection 1 to 3 from the piston-side first working volume 23 via the check valve 31 (second passive switching element) to the first pressure accumulator 27 at the main valve edge 39 is closed.
  • the connection 1 to 2 from the first pressure accumulator 27 via the check valve 30 (first passive switching element) to the piston-side first working volume 23 of the main valve edge 39 is opened. In this case, the fluid flows into the first working volume 23.
  • the pressure acting on the first pressure surface 40 thus accelerates the valve 22 in the opening direction downward, since the second pressure surface 41 of the actuating element 21 is smaller than the first pressure surface 40.
  • the pressure p z2 in the second pressure accumulator 28 increases.
  • the pressure p z1 in the first pressure accumulator 27 drops during this stroke movement.
  • the flow direction wants to reverse over the main valve edge 39.
  • the first passive switching element in the form of the check valve 30 prevents backflow of the fluid, so that the valve 22 remains in the open position.
  • the time T s for opening and closing the valve 22 corresponds to half the period of a free oscillator.
  • the in Fig. 2c shown closing movement of the control valve 29 to be tuned to this time T s .
  • the closing movement of the control valve 29 should be about twice as long as T s .
  • the closing stroke of the valve 22 does not begin until the control valve 29 has closed the connection 1 according to FIG. 2 at the main valve edge 39 and the connection 1 according to FIG. 3 opens again.
  • the fluid can flow back into the first pressure accumulator 27 via the check valve 31 from the piston-side first working volume 23. Due to dissipative effects, the valve 22 no longer reaches its home position and the lack of energy must be returned to the system. This is done on the one hand via the refilling of the first pressure accumulator 27 via the Nach Glallventilkante 37 and the second pressure accumulator 28 via the Supply check valve 36.
  • Far the piston-side first working volume 23 is placed on the tank T via the discharge valve edge 38. This can be guaranteed that the valve 22 is closed safely.
  • control valve 29 thus has only once from the closed in the in.
  • the valve edges 37, 38 and 39 are physically designed accordingly.
  • Fig. 3 is an implementation example with two parallel passive switching elements 30, 31 - also formed in the form of check valves - shown.
  • the passive switching elements 30, 31 are arranged in the bypass line 32, 33, which lead around the control valve 29, whereby the passive switching elements are connected in parallel to the control valve 29.
  • This implementation is similar to the previously explained system. The main differences are in the mentioned parallel arrangements of the two check valves 30 and 31 to the control valve 29 and in the circuit of the connection to the second pressure accumulator 28 via the control valve 29 (connection 11 and 12).
  • the control valve 29 is switched. Before the main valve edge 39 is opened, the refill valve edge 37 (connection 4 of FIG. 5) and the discharge valve edge 38 (connection 9 of FIG. 10) are closed.
  • connection 1 to 2 When the main valve edge 39 (connection 1 to 2) opens, the opening stroke of the valve 22 begins. When the majority of the stroke is reached, the main valve edge reaches its end position and thus closes the connection 11 to 12. Only a very small part of the volume flow must thus flow over the check valve 31. As soon as the valve 22 reaches the maximum stroke and wants to swing back again, the check valve 31 closes. The valve 22 is held in its open position.
  • the return movement of the valve 22 is triggered by the closing movement of the control valve 29. As soon as the connection 11 to 12 is opened, the valve 22 begins to move back in the form of the closing stroke. Next, the valve edge 39 is closed and the fluid flows through the check valve 30. Just before the reversal point, the refill valve edge 37 opens (connection 4 to 5) and Discharge valve edge 38 (connection 9 to 10). By means of the aperture 54, the impact speed can be adjusted at the seat.
  • a cushioning is realized at the connection between the second working volume 24 and the second fluid line 26.
  • This serves to decelerate the valve 22 when it reaches one of its end positions, in particular its open end position.
  • a throttle or aperture 42 is provided, via which the fluid flows from the second working volume 24 into the second fluid line 26, when the actuating element 21 carries out the residual stroke between x max and x maxmech .
  • the check valve 43 is provided for the return flow of the fluid.
  • This type of end position damping can be provided especially when the valve drive is designed for asymmetrical force distribution or gas counterforce. Usually it is only used when, for example, by a misfire in the combustion chamber of the internal combustion engine no gas counterforce is built up, in which case the valve 22 can be intercepted by the Endlagendämpfung.
  • a soiraktuator 34 is provided in the embodiments according to Fig. 4 and 6 actuation of the valve 22 in addition to the actuating element 21 in each case also a soiraktuator 34 is provided. This is particularly favorable in internal combustion engines when the valve 22 has to be opened against a high backpressure in the combustion chamber. This is especially the case with exhaust valves. In most cases, it is sufficient if the support of the additional actuator 34 at the beginning of the opening movement is thus provided only for a partial stroke h p . The additional force required at the outlet valve to overcome the counter gas forces during the opening stroke or the work done is lost and can not be recovered.
  • auxiliary actuator 34 can exert a force on the valve rod 45 with a limited stroke plunger 44 h p .
  • a spring 46 ensures a defined initial position of the plunger 44.
  • the tank connection is closed and the plunger chamber 47 connected to high pressure (see Fig. 5 ).
  • the plunger 44 thus acts on the actuators and supports the opening movement of the actuating element 21 and thus the valve 22.
  • the force acts only until the plunger 44 has performed the stroke h p and is braked at the stop 35.
  • the valve rod 45 then lifts off the plunger 44 and is only moved by the working cylinder 20 or actuating element 21.
  • Fig. 5a, 5b and 5c are essentially the same diagrams as in the Fig. 2a, 2b and 2c shown. Additionally are in Fig. 5c still the movement of the control valve 29 additionally realized 3/2-way valve edge 48 located. This serves to act on the plunger chamber 47 and opens and closes the connection 7 according to FIGS. 6 and 6 according to FIG.
  • the additional actuator can - as in Fig. 4 shown - hydraulically realized.
  • Such drives are known per se and therefore need not be explained again in detail.
  • the additional actuator 34 as well as the actuator 21 can be operated hydraulically and / or pneumatically and fed from a common system pressure source pS.
  • Fig. 6 An electrical realization, however, is in Fig. 6 shown.
  • the actuation of the actuating element 21 corresponds in this embodiment to Fig. 3 described.
  • new is the additional electric actuator 34. This supports the actuator 21 at the beginning of the opening stroke and is then moved back, for example via a spring or electrically to its original position. Also in this embodiment is thus provided that the additional actuator 34 engages supportive only on a partial stroke.
  • the systems shown in the various embodiments with energy recovery by intermediate storage can be performed both pneumatically and hydraulically.
  • hydraulic vibrators the compression of the fluid is preferably used. It can be dispensed with additional external memory.
  • the disadvantage of this variant, however, is that the pressure accumulators 27 and 28 have a relatively large space requirement. If this is not desired, such as for mobile drives, but can also be using external storage 27 and / or 28, such as gas storage, work to build the actuator itself as small as possible. It is beneficial to resort to memory with a long service life and compact design. Conventional diaphragm accumulators often do not meet these requirements.
  • FIGS. 7 and 8 show two implementation possibilities of gas storage, which are favorable for use according to the invention. The gas 51 is thereby separated from the fluid 53 by the membrane 52. In order to set the life as high as possible, conveniently steel membranes are used.
  • the control valve 29 consists of several stages or valve edges. It thus switches at least two or more Fluid lines.
  • the pressure loss in this generally designed as a 3/2-way valve main valve edge should be kept as low as possible.
  • pressure losses are not so crucial.
  • the main advantage of the multi-stage control valve 29 is that only a single valve or only a single slider is needed. This has a positive effect on both the cost and the reliability of the system.
  • control valve 29 has a hydraulic feedforward control, since with this the timing of the control valve 29 is particularly easy to implement.
  • valve clearance compensation especially for large engines, must be able to compensate for several millimeters - on the order of 4 mm. In this system, one can accommodate this change in length in the piston-side first working volume 23 of the working cylinder 20. This volume change is very small compared to the volumes of the accumulators 27 and 28. As a result, the switching sides and the stroke of the actuator do not change noticeably.
  • a soiraktuators 34 could also be installed in the actuator 21 a valve clearance compensation.
  • valve actuators according to the invention in the embodiments shown focus on the application in gas inlet or -auslassventilen of internal combustion engines, so embodiments of the invention but also for large valve spool in the hydraulic, compressor valves or for Drives of punching machines u. Like. Used to name just a few examples.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Magnetically Actuated Valves (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Servomotors (AREA)

Claims (16)

  1. Actuateur de soupape, en particulier pour des soupapes d'inversion de gaz de machines combustion interne, avec un élément d'actionnement (21), logé de façon mobile dans un vérin (20), notamment un piston, pour l'entraînement d'une soupape (22), dans lequel est prévu dans le vérin (20) sur un côté de l'élément d'actionnement (21) au moins un premier volume de travail (23) se trouvant en lien, par au moins une première conduite de fluide (25), avec au moins un premier accumulateur de pression (27) pour le fluide, dans lequel une soupape de commande (29) commutant au moins deux conduites de fluide (25, 26), pouvant être actionnée de façon active est disposée dans la première conduite de fluide (25), dans lequel au moins un élément de commutation passif (30, 31) pour commander un passage de fluide, de préférence une soupape de retenue, est commuté à la soupape de commande (29) en série ou en parallèle, dans lequel sur un côté, opposé au premier volume de travail (23), de l'élément d'actionnement (21) au moins un deuxième volume de travail (24) se trouvant en lien, par au moins une deuxième conduite de fluide (26), avec au moins un deuxième accumulateur de pression (28) pour le fluide est prévu dans le vérin (20), dans lequel la soupape de commande (29) pouvant être actionnée de façon active est disposée dans la première et dans la deuxième conduite de fluide (25, 26), caractérisé en ce que l'actuateur de soupape présente exactement une soupape de commande (29) pouvant être actionnée de façon active, dans lequel de préférence lors du freinage, une énergie cinétique de l'actuateur de soupape, de préférence de la soupape (22), peut être temporairement retenue par établissement de pression dans un premier accumulateur de pression (27) et/ou dans un deuxième accumulateur de pression (28) pour une poussée consécutive de la soupape (22).
  2. Actuateur de soupape selon la revendication 1, caractérisé en ce que au moins, de préférence exactement, deux éléments de commutation passifs (30, 31) pour commander un passage de fluide vers une soupape de commande (29) pouvant être actionnée de façon active, sont commutés en série et/ou en parallèle.
  3. Actuateur de soupape selon la revendication 1 ou la revendication 2, caractérisé en ce que dans le cas d'une commutation en série le (les) élément(s) de commutation passif(s) (30, 31) pour commander un passage de fluide, est (sont) disposé(s) dans la première (et/) ou la deuxième conduite de fluide (25, 26), de préférence sur le côté orienté vers le volume de travail respectif (23, 24) de la soupape de commande (29) pouvant être actionnée de façon active.
  4. Actuateur de soupape selon la revendication 1 ou la revendication 2, caractérisé en ce que dans le cas d'une commutation en parallèle, le (les) élément(s) de commutation passifs(s) (30, 31) pour commander un passage de fluide, de préférence chacun, est (sont) disposé(s) dans au moins une conduite de dérivation (32, 33), passant autour de la soupape de commande (29) pouvant être actionnée de façon active, de la première (et/) ou de la deuxième conduite de fluide (25, 26).
  5. Actuateur de soupape selon l'une des revendications 1 à 4, caractérisé en ce que l'élément d'actionnement (21) peut être actionné de façon hydraulique et/ou pneumatique.
  6. Actuateur de soupape selon l'une des revendications 1 à 5, caractérisé en ce qu'il prévoit un amortissement de positions finales, de préférence hydraulique et/ou pneumatique, pour au moins une zone, dans laquelle la soupape (22) atteint une de ses positions finales.
  7. Actuateur de soupape selon l'une des revendications 1 à 6, caractérisé en ce que l'élément d'actionnement (21) est prévu pour réaliser une course d'ouverture et une course de fermeture de la soupape (22) et lors d'une partie au moins de la course d'ouverture ou de la course de fermeture, davantage de force de l'élément d'actionnement (21) doit être introduite sur la soupape (22) que lors de l'autre course à chaque fois, dans lequel un actionneur complémentaire (34) est prévu, qui soutient au moins par périodes l'élément d'actionnement (21) lors de la course nécessitant davantage de force.
  8. Actuateur de soupape selon la revendication 7, caractérisé en ce que l'actuateur complémentaire (34) ne peut pas être activé, en tant que force d'actionnement, avec une pression dérivée d'une chambre de combustion, de préférence d'une machine à combustion interne.
  9. Actuateur de soupape selon les revendications 6 ou 7, caractérisé en ce que l'actuateur complémentaire (34) peut être actionné de façon hydraulique et/ou pneumatique et/ou électrique et/ou piézoélectrique et/ou magnétique et/ou électromagnétique.
  10. Actuateur de soupape selon l'une des revendications 7 à 9, caractérisé en ce que non seulement l'actuateur complémentaire (34) mais aussi l'élément d'actionnement (21) peuvent être activés de façon hydraulique et/ou pneumatique et peuvent être alimentés de préférence par une source de pression commune du système (pS).
  11. Actuateur de soupape selon l'une des revendications 7 à 10, caractérisé en ce que l'actuateur complémentaire (34) soutient l'élément d'actionnement (21) lors de la course nécessitant plus de force pendant la course totale.
  12. Actuateur de soupape selon l'une des revendications 7 à 10, caractérisé en ce que l'actuateur complémentaire (34) est conçu de manière telle qu'il influe uniquement sur une section de parcours (hp), de préférence au début, de la course d'ouverture ou de fermeture à effectuer par l'élément d'actionnement (21) sur la soupape (22).
  13. Actuateur de soupape selon l'une des revendications 7 à 10, caractérisé en ce que l'actuateur complémentaire (34) met fin à l'alimentation en énergie, avant que la soupape (22) atteigne l'une de ses positions finales.
  14. Actuateur de soupape selon les revendications 12 ou 13, caractérisé en ce que pour l'actuateur complémentaire (34) une butée (35) est prévue, qu'il atteint avant que la soupape (22) atteigne l'une de ses positions finales.
  15. Actuateur de soupape selon l'une des revendications 1 à 14, caractérisé en ce que l'actuateur de soupape est prévu pour une soupape d'échappement de gaz ou une soupape d'admission de gaz d'une machine à combustion interne.
  16. Machine à combustion interne avec un actuateur de soupape selon l'une des revendications 1 à 15.
EP08002785A 2007-03-06 2008-02-15 Actuateur hydraulique de soupape Not-in-force EP1967706B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ATA353/2007A AT504981B1 (de) 2007-03-06 2007-03-06 Ventilantrieb

Publications (3)

Publication Number Publication Date
EP1967706A2 EP1967706A2 (fr) 2008-09-10
EP1967706A3 EP1967706A3 (fr) 2008-11-05
EP1967706B1 true EP1967706B1 (fr) 2011-02-09

Family

ID=39585309

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08002785A Not-in-force EP1967706B1 (fr) 2007-03-06 2008-02-15 Actuateur hydraulique de soupape

Country Status (4)

Country Link
EP (1) EP1967706B1 (fr)
AT (2) AT504981B1 (fr)
DE (1) DE502008002540D1 (fr)
ES (1) ES2360640T3 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010054653A1 (fr) * 2008-11-11 2010-05-20 Man Diesel Filial Af Man Diesel Se, Tyskland Moteur diesel à deux temps de grande dimension avec système d'actionnement de soupape d'échappement commandé électroniquement
US20130152571A1 (en) * 2011-12-16 2013-06-20 Jeffery Modderno Valve activation in compressed-gas energy storage and recovery systems
EP3743602B1 (fr) * 2018-01-26 2021-12-01 Wärtsilä Finland Oy Ensemble actionneur de sécurité et moteur à piston alternatif à combustion interne comportant un tel ensemble actionneur de sécurité

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT411090B (de) 2000-12-12 2003-09-25 Jenbacher Ag Vollvariabler hydraulischer ventilantrieb
US6899068B2 (en) * 2002-09-30 2005-05-31 Caterpillar Inc Hydraulic valve actuation system
US6978747B2 (en) * 2003-04-01 2005-12-27 International Engine Intellectual Property Company, Llc Hydraulic actuator cartridge for a valve
DE102004030306A1 (de) * 2004-06-23 2006-01-12 Robert Bosch Gmbh Verfahren zur Erfassung mindestens einer Ventilhubposition bei einer Brennkraftmaschine mit variabler Ventilsteuerung
DE102004040210A1 (de) * 2004-08-19 2006-03-02 Robert Bosch Gmbh Hydraulischer Steller für ein Gaswechselventil einer Brennkraftmaschine
WO2006108438A1 (fr) * 2005-04-14 2006-10-19 Man B & W Diesel A/S Ensemble soupape d'echappement de gros moteur diesel deux temps

Also Published As

Publication number Publication date
EP1967706A2 (fr) 2008-09-10
AT504981B1 (de) 2013-06-15
ATE498052T1 (de) 2011-02-15
DE502008002540D1 (de) 2011-03-24
AT504981A3 (de) 2012-10-15
AT504981A2 (de) 2008-09-15
EP1967706A3 (fr) 2008-11-05
ES2360640T3 (es) 2011-06-07

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