EP3656990A1 - Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement - Google Patents

Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement Download PDF

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Publication number
EP3656990A1
EP3656990A1 EP18207848.5A EP18207848A EP3656990A1 EP 3656990 A1 EP3656990 A1 EP 3656990A1 EP 18207848 A EP18207848 A EP 18207848A EP 3656990 A1 EP3656990 A1 EP 3656990A1
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EP
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Prior art keywords
valve
pressure
drive
gas exchange
piston
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Pending
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EP18207848.5A
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German (de)
English (en)
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Erfindernennung liegt noch nicht vor Die
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Wolfgang Schneider Ingenieurbuero
Eidgenoessische Materialprufungs und Forschungsanstalt EMPA
Original Assignee
Wolfgang Schneider Ingenieurbuero
Eidgenoessische Materialprufungs und Forschungsanstalt EMPA
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Application filed by Wolfgang Schneider Ingenieurbuero, Eidgenoessische Materialprufungs und Forschungsanstalt EMPA filed Critical Wolfgang Schneider Ingenieurbuero
Priority to EP18207848.5A priority Critical patent/EP3656990A1/fr
Publication of EP3656990A1 publication Critical patent/EP3656990A1/fr
Pending legal-status Critical Current

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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 invention relates to a hydraulic drive for accelerating and braking dynamically moving components, in particular valves in gas exchange controls of internal combustion engines and other piston machines, according to the preamble of claim 1, as well as inventive methods for operating such a hydraulic drive.
  • Variable valve controls on internal combustion engines are known as suitable means both to improve the torque curve over the rotational speed and to improve the overall efficiency of the engine and to reduce the pollutant emissions.
  • the variety of optimization options is described in the literature.
  • Today, a large number of mechanical, electromechanical, pneumatic and hydraulic construction options for partially or fully variable valve controls are known, but due to their high energy consumption or high technical complexity and the associated manufacturing costs, they were only able to assert themselves selectively.
  • there is no full variability in many such systems For example, the time of opening and the duration of opening or the duration of opening and opening stroke can be permanently coupled to one another, which can considerably limit the possibilities for optimizing the internal combustion engine or another piston engine.
  • Hydraulic systems in particular can be built to save space due to their high energy density (SAE-1996-0581), are not tied to a cam profile and are therefore particularly suitable for variable valve controls on internal combustion engines if both low energy consumption and low energy consumption are achieved Achieve system effort and high reliability.
  • control tasks can be performed on a fully variable valve control system on an internal combustion engine today: Free, namely independent setting of opening and closing times, i.e. the so-called control times, of intake and exhaust valves, if required also cylinder-selective.
  • Free namely independent setting of opening and closing times, i.e. the so-called control times, of intake and exhaust valves, if required also cylinder-selective.
  • the amount of air or mixture can be controlled via the opening duration of the intake valves, fast opening and closing of the valves even at low engine speeds, i.e.
  • Hydraulic valve actuators in particular for gas exchange valves in the working area of an internal combustion engine, have long been known, for example, from the German Offenlegungsschrift DE 1,940,177 A known. They were used as a replacement for the camshaft-controlled opening of a gas exchange valve, while the valve was still closed by a spring mechanism.
  • the resetting of the gas exchange valves by means of spring means is still by far the most frequently used closing method, since it ensures secure closing.
  • the aim of these systems was to optimize the control times of the gas exchange valve and to open and close the valves more steeply / quickly, whereby an optimization of the own energy requirement was mostly not yet explicitly provided.
  • a stroke adjustment was not provided in DE 1'940'177 A, but it was thought to dampen hard strikes on the mechanical stroke limitation and in the point of contact at the valve seat of the gas exchange valve by displacing the medium through a throttle cross-section.
  • WO 93/01399 A1 it is shown that even with systems with a simple, one-way spring return as in DE 1 '940'177 A, a minimization of the own energy requirement is possible.
  • the kinetic kinetic energy resulting from the hydraulic drive is temporarily stored in the compression work of the one-sided, resilient spring accumulator before it is used again for the closing movement.
  • This principle can therefore also be referred to as an "asymmetrical pendulum system".
  • a disadvantage of the proposal of WO 93/01399 A1 is, for example, that one of the actuating movements of the controlling hydraulic valve takes place in the middle of the movement phase, namely while the drive piston of the gas exchange valve is moving at high speed and a high volume flow is flowing through the hydraulic valve.
  • the control valve In order to avoid high throttle losses in this situation, the control valve must be very fast. It also has to switch precisely and reliably at the opening end point of the gas exchange valve movement so that the kinetic energy can be fully captured and retained in the spring. These requirements therefore require very complex, high-speed control valves and complex control electronics.
  • Another such asymmetrical pendulum system is described in SAE 2007-24-008. The opening stroke can be adjusted via the level of the hydraulic operating pressure regardless of the activation duration.
  • the system In contrast to WO93 / 01399 A1 the system dispenses with high-speed switching operations of the hydraulic control valve in the middle of the movement phase.
  • the actuating movement of the control valve as a whole must also be precise with the movement of the gas exchange valve be coordinated.
  • the flow path for opening must close precisely when the gas exchange valve has released its kinetic energy to the return spring. If the control valve cross-section closes too early, the movement of the gas exchange valve is braked with loss, if it closes too late, the gas exchange valve is already pushed back by the spring, is not held in the desired position, and is then braked again in the return movement with losses.
  • a precisely defined volume flow of a pilot valve is applied to a main slide.
  • the pilot valve is fed by a separate constant pressure system in order to provide the defined volume flow for controlling the main valve.
  • deviations in the pilot volume flow due to wear or clogging of the pilot valve openings have an effect on the speed of the main valve and thus on the quality of the time coordination with the drive piston or gas valve movement.
  • EP 17172231.7 discloses a hydraulic system for accelerating and decelerating components to be moved dynamically, in particular valves in gas exchange controls of internal combustion engines and other at least one component to be driven, in particular a gas exchange valve or several gas exchange valves of an internal combustion engine or another piston machine that can be operated together via a valve bridge, a working cylinder with a pressure active surface of a drive piston, at least one first pressure reservoir, for providing a first pressure p 1 of a hydraulic pressure medium, at least one, preferably designed as a spring, engaging on the component or on the gas exchange valve, resetting energy store with a biasing force F FV , at least one hydraulic base pressure reservoir , which has a lower pressure p 0 than the first pressure reservoir, one in a first connecting line between the first hydraulic pressure reservoir and the working cylinder controllable opening of a first valve with at least one is arranged in the flow path upstream, in or behind, in series, preferably spring-loaded check valve, which allows the pressure medium to flow
  • the drive pressure can also deviate from the planned value as a result of a malfunction.
  • a typical example of this is with exhaust valves of internal combustion engines.
  • At the time of opening towards the end of the expansion phase after combustion has taken place, there is usually still a considerable cylinder pressure which, in the case of a conventional poppet valve type, acts against the opening direction of the valve.
  • an increased drive pressure or a larger pressure effective area of the drive piston is required.
  • the pressure prevailing in the cylinder is often reduced after a short opening distance, while a high driving force is still present.
  • valve overshoots to an undesirably large stroke and in many cases to such an extent that it hits a mechanical stop or the spring is pressed onto a block, which can cause noise and damage.
  • the effect is exacerbated when the valve opening force is at a high cylinder pressure was voted at the time of opening, but this does not occur, for example, as a result of a misfire.
  • the object of the invention is therefore to provide a hydraulic drive for accelerating and braking of components to be moved dynamically, in which the above-mentioned disadvantages of the prior art, in particular the unpublished European patent application EP 17172231.7 can be overcome.
  • the invention achieves this object by means of a hydraulic drive according to claim 1.
  • the measures of the invention initially have the consequence that the fact that the drive piston has at least one control edge corresponding to an inflow opening leads to the inflow of drive pressure p 1 when a certain stroke is reached into the drive chamber or a low-loss outflow of pressure medium from the brake chamber to the base pressure level can be prevented and the remaining hydraulic drive force disappears, becomes low or changes the sign when the stroke (h ab ) is reached, even if the drive pressure or the pressure deviates Disturbance pressure from the planned value as a result of a disturbance, reliable operation can be guaranteed.
  • These measures also solve the problems of misfires in internal combustion engines.
  • the advantageous effect is achieved in particular in that, in this method, the (hydraulic) drive piston itself engages with the hydraulic path. Therefore, the device and the corresponding method are particularly advantageous in internal combustion engines because they are inherently safe and reliable.
  • the present invention is particularly applicable in gas exchange controls of internal combustion engines and other piston machines.
  • the drive according to the invention is generally advantageous, that is to say also in other applications in which masses have to be moved in a highly dynamic manner.
  • the invention can also be used as an independent stroke control, which can partially supplement or completely replace the known stroke control by means of the drive pressure level (see SAE 2008-24-008). This means that the pressure in the hydraulic system does not have to be adjusted quickly or not at all.
  • the invention can also use the known stroke controls, which adjust the stroke by closing an inflow control valve in the opening phase (examples WO 93/01399 A1 , DE 10 2004 022 447 A1 ) partially, for example as a safety device, or replace it completely.
  • the special type of stroke control can thus advantageously be applied not only to hydraulic valve actuators based on the pendulum principle, but quite generally to hydraulic controls of gas exchange valves.
  • the insensitivity of the set gas exchange valve stroke to gas forces acting on the valve plate also allows this drive to be used for engine brake functions.
  • the exhaust valve can be opened a gap, as a result of which the cylinder filling has to be pushed out against the resistance of the valve and the stored energy is thus dissipated into the exhaust.
  • the drive side and - if available - the brake side of the cylinder are each connected to the drive pressure reservoir via at least one check valve, the check valves opening in the direction of this reservoir but blocking in the direction of the cylinder spaces or via at least one check valve each with the base pressure reservoir are connected, the check valves opening in the direction of the cylinder spaces and blocking in the direction of the reservoir.
  • the drive piston stroke at which the cutting process occurs is adjustable or adjustable.
  • the piston control edge can be designed obliquely and the inflow chamber in the cylinder can be designed in a punctiform manner, so that twisting between the piston and the working cylinder, preferably twisting the piston relative to a stationary working cylinder, changes the cut-off travel.
  • the drain control valve is designed as a 2/2-way valve with two additional intermediate positions, which are passed through in a time-controlled manner when switching to the open drain position, the first intermediate position being an open one which initiates the closing movement of the gas exchange valve and the second is a closed, when it is reached in the drive cylinder due to the kinetic energy of the moving mass, a pressure is built up for a certain time, which allows pressure medium to be pushed back into the drive pressure reservoir, even if it is charged to a higher pressure level than the pressure , with which the return spring presses statically on the working piston.
  • This special valve design enables the system to recover energy from the unfavorable pressure situation - for example high pressure level in the working pressure reservoir due to high cylinder pressure to be overcome - during the resetting process.
  • the pressure medium is pressed by a throttle over a pressure effective surface of the valve, so that the intermediate positions of the valve are passed slowly and / or with a time delay and that a bypassing of the throttle can be provided by a check valve in the other actuation direction.
  • the invention allows the use of comparatively slow and correspondingly inexpensive control valves. It is also sufficient that the hydraulic control valves only initiate the opening and closing process of a gas exchange valve, as it were, since the movement process then takes place automatically, without external control interventions. This makes the system easy to use.
  • the hydraulic drive can be divided into a core part including one or more gas exchange valves 11 and a supply part.
  • the pressure for the proposed pressure reservoirs (40, 41) is provided, in a manner known per se, preferably with controllable pumps, which allow the flow to be adapted to the volume flow and pressure requirement.
  • the pressure is regulated using conventional hydraulic means, for example also using pressure sensors and electronics.
  • the control electronics also take over the electrical control of the electrical switchable control valves 46, 76. For the sake of simplicity, electronics and connecting lines are also not shown.
  • control valves 46 and 76 are designed as directly controlled, solenoid-operated directional valves.
  • a slightly raised base pressure p 0 was chosen compared to tank pressure p T in order to keep the system largely free of gas bubbles which could impair the function.
  • leaks collecting in the spring chamber 93 are fed to a central tank with pressure p T via a leak collecting line 94. If the valve stem seal 17 is sufficient for this, the leakage line can also be connected to the somewhat higher base pressure level p 0 . It is also possible to design the base pressure reservoir 40 as a normal, ambient-ventilated tank.
  • Fig. 4 The phases of the movement sequence, the pressure p AK which arises in the drive chamber and the associated valve and control edge openings are shown in Fig. 4 shown.
  • gas exchange valve closed - the inflow control valve 46 is closed (position 1a) and the outflow control valve 76 is open (position 2a), as a result of which the drive chamber of the single-acting working cylinder 22, in which the drive piston 23 with the pressure active surface 24 of the area A is movably arranged , is connected to the base pressure reservoir 40 at the pressure level p 0 .
  • the relief drain control valve 76 is closed (position 2d).
  • the inflow control valve 46 is then opened (position 1b).
  • the pressure active surface 24 of the drive piston 23 is thus acted upon by the pressure p 1 from the drive pressure reservoir 41.
  • the flow path from the inflow control valve into the drive chamber takes place here via the open connection in this position via channel 32, piston annulus 34 and overflow channel 35.
  • the gas exchange valve 20 will open when the compressive force present in the drive chamber 27 exceeds the biasing spring force F FV of the spring 25. It is clear that the actual force at which opening takes place can vary according to the additional forces mentioned. In particular, if high opposing forces are expected, for example, from the side of the motor cylinder 15, due to the action on the valve plate surface 21, the pressure p 1 will be set so high that reliable opening is ensured.
  • the spring 25 used as an energy store is designed with a high spring constant c, so that a rapid movement of the mass is achieved.
  • the pressure p 1 has to be set comparatively very high in order to overcome difficult conditions, in particular higher than would be necessary to achieve the maximum desired or permissible stroke, it is immediately apparent that the maximum gas exchange stroke becomes very large and can lead to damage, especially if the high counterforce collapses during the movement of the gas exchange valve and does not occur unexpectedly.
  • the considerable pressure from the engine cylinder occurring at valve plate surface 21 is typically 5 - 10 bar and then often drops sharply after a short time, so that suddenly a considerable excess of acceleration force at the drive piston is available; or the expected cylinder pressure does not occur at all due to a misfire and the acceleration takes place from the beginning with the extra high pressure p 1 .
  • Hydraulic drive systems that are not referred to as "pendulum systems" in the sense of this document are typically characterized by a lower spring constant c. Since this would result in very large strokes, the pressure is not primarily used to adjust the stroke, but rather the acceleration process is typically carried out by closing the inflow control valve to the drive chamber ended. The problem with the influence of gas forces exists in the same way in these systems.
  • the working piston thus takes over the function of a third control valve.
  • the fact that this is stroke-controlled by the gas exchange valve means that the control intervention is quasi passive or automatic. This is a very safe stroke limitation method compared to hydraulic controls that require active control intervention at this point.
  • the check valve 67 closes automatically. Particularly when the pressure p 1 is high, it happens that the spring is tensioned so much that in this stroke position it is able to generate a pressure p AK with the working piston surface 24 of size A in the drive chamber 27 that is greater than that Pressure level p 1 in the working pressure reservoir. In this case, also shown in Figure 4 , pushes the spring with the drive piston pressure medium through the check valve 47 back into the working memory until there is pressure equilibrium.
  • the associated reduction in stroke is usually easily coped with when changing gas from combustion engines. For example, a large initial stroke is advantageous for the exhaust valve, while the later stroke is less important.
  • the stroke reduction is accompanied by energy recovery, because the returned pressure medium can be used again later.
  • the gas exchange valve then remains in the swung-back position.
  • the described stroke reduction does not always take place.
  • Conditions can also occur in which the spring does not have the force to push pressure medium into the working pressure reservoir. This can be the case, for example, if the pressure p1 has been set comparatively high in order to open the gas exchange valve. In any case, the working piston and thus the gas exchange valve remains in the position found (phase III) until the closing process IV is initiated by resetting the valve 76.
  • the peculiarity of the valve 76 is that it switches back at an approximately constant speed. This is achieved in that the spring 73 has to push pressure medium through the throttle 72 over the control surface 71, in which In a different actuation direction, the throttle can be bypassed by a check valve 74.
  • a spring is ideal for this process due to its constancy.
  • An alternative embodiment variant would be, for example, a correspondingly designed rotary slide valve.
  • the switchback time is - as in EP 17172231.7 shown - matched to about half the period T 1/2 of the spring mass system, here in particular until position 2b is reached. Different than in the EP 17172231.7 pressure medium is first discharged from the drive chamber (position 2c) in order to accelerate the gas exchange valve at all.
  • the spring in the holding phase has at most approximately pressure p 1 in the working chamber. As it would lose more force due to its spring characteristics, it would not be able to push out pressure medium by itself. With the intermediate position 2c, the gas exchange valve is thus in a position to initially build up kinetic energy, which it can then release again at the higher pressure level p 1 after completion of the pendulum process.
  • the throttle of the drain valve spool is dimensioned such that the drain control valve reaches its closed position 2b after about half the period of this vibration.
  • a pressure builds up in the drive chamber 27 which, as long as greater than p 1 , is pushed back into the drive pressure reservoir via the check valve 47.
  • the drain control valve then moves further to its rest position, the open position 2a, to initiate the complete closing of the gas exchange valve.
  • the second embodiment according to Fig. 2 differs from the first on the one hand essentially only by the adjustability of the cutting stroke h ab by rotating the drive piston 23, on the other hand by a mechanical coupling of the valves 46 and 76 to a combined valve 86, by means of which it is possible with only one electric actuating actuator 88 get along.
  • the coupling can be similar to that in EP 17172231.7 described.
  • the adjustment of the cutting stroke h ab takes place here by means of an oblique control edge 37 on the drive piston in relation to a rather punctiform opening 33 of the inflow channel 32, preferably a bore, and can thereby be changed via the angle of rotation ⁇ .
  • the overflow channel 35 was laid in the piston.
  • Fig. 7 shows an embodiment in which the drive piston is not rotatable, but the sleeve in which the drive piston runs is designed to be rotatable.
  • the inclined edge is carried out on the drive piston and the preferably round counter surface in the liner. It is clear to the person skilled in the art that the corresponding edges of the drive piston and liner can also be interchanged. A particularly clear solution that does not require an inclined edge can also be achieved by means of an axially displaceable sleeve in which the piston runs.
  • the drive piston is 95 with longitudinal grooves equipped, in which an axially immovable gear 97 engages with lugs 96, which can be adjusted, for example, by a self-locking drive worm 98. In this way, the drive piston 23 can be rotated without its longitudinal movement being influenced.
  • the stroke adjustment can be used very well to reduce the energy requirements of the hydraulic drive, since small gas exchange valve strokes are sufficient for a low-loss gas exchange on the internal combustion engine at low speed.
  • the hydraulic energy requirement generally drops proportionally or disproportionately with the gas exchange valve stroke, because at least the requirement for pressure medium decreases with the stroke.
  • the embodiment according to Fig. 2 is to be equipped with a path-controlled braking device, which as in Fig. 4 a short peak of the pressure p AK is generated in the drive chamber 27.
  • a path-controlled braking device which as in Fig. 4 a short peak of the pressure p AK is generated in the drive chamber 27.
  • the drive piston closes the channel 62 when approaching its rest position and the pressure medium is pressed via the channel 63 through the throttle 64. If p AK assumes a higher value than p 1 , pressure medium is also pushed back into the drive pressure reservoir 41 through the check valve.
  • FIG 3 shows an embodiment in which the brake side of a double-acting working cylinder 50 is used to limit the stroke.
  • the working cylinder 50 here has a brake chamber 29 in addition to the drive chamber 27.
  • the drive chamber 27 is not cut off from the drive pressure inflow, but rather the brake chamber 29 is generated from the outflow into the base pressure reservoir 40 and a braking force counteracting the movement.
  • the net driving force from a Abschneidehub h from significantly reduced.
  • the movement of the gas exchange valve 20 is initially initiated in a known manner.
  • the brake chamber 29 is connected to the base pressure reservoir 40 via a connection channel 52 and an inflow channel 54.
  • pressure medium is pushed out through the connection channel 52 to the base pressure reservoir. This continues until the drain control edge 51 closes the opening 53 of the connecting channel in the cylinder wall. This creates a brake pressure in the brake chamber. If the kinetic energy of the moving components is sufficient, the brake pressure exceeds the pressure p 1 and the pressure medium is fed back into the drive pressure reservoir 41 via the feedback channel 56 and a check valve 58. The braking energy can be used again in this way.
  • the drive piston is braked, in this exemplary embodiment it is held in position by a check valve 58 in the inflow line.
  • the closing process is initiated by reducing the pressure in the drive chamber 27 and can, as in FIG Figure 1 are controlled by valve 76.
  • the check valve 55 is in the inflow channel 54 so that no negative pressure can develop in the brake chamber 29 at the beginning of the closing process intended.
  • Fig. 5 uses idealized, friction-free force-displacement diagrams to show how the method according to the invention works and copes with disruptive forces.
  • the hydraulic drive force p ⁇ A, the stroke-dependent spring force F F as well as the associated hydraulic work W h and the spring work W F are shown in each case.
  • Diagram F1 represents an asymmetrical pendulum system, in which - based on the drive pressure p 1 - the maximum stroke h max (p 1 ) is twice the stroke compared to the theoretical equilibrium point with stroke h stat (as in EP 17172231.7 applied).
  • F2 shows an example of the application of the inflow cut-off method according to the invention. with which the amount of energy supplied is limited.
  • Fig. 6 shows the measured valve lift curve of a drive implemented according to embodiment 2 on a fired internal combustion engine.
  • the figure shows that the opening time and the closing time (until the kinetic energy is reduced) represent the same time constant T 1/2 .
  • the hump in the middle of the closing process represents the end of the closing swing process, which is associated with the energy gain from the kinetic energy.
  • the recognizable vibrations, especially after the opening process are the regular, in Figure 4 shown sequence overlaid. They are of little importance for the overall function.
  • a general movement back of the gas exchange valve immediately after opening before taking a stable stroke takes place, as in Fig. 4 drawn, less with a small stroke. On the last tenths of a millimeter before the touchdown point, you can see the application of the soft touchdown brake.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP18207848.5A 2018-11-22 2018-11-22 Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement Pending EP3656990A1 (fr)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2021121639A1 (fr) * 2019-12-20 2021-06-24 Empa Eidgenössische Materialprüfungs- Und Forschungsanstalt Entraînement hydraulique pour des constituants d'accélération et de freinage qui doivent être déplacés de manière dynamique

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DE1940177A1 (de) 1968-08-08 1970-02-19 Kaiser Aluminium Chem Corp Verfahren zur Gewinnung von Aluminium
JPS58150296A (ja) 1982-03-01 1983-09-06 クロイ電機株式会社 放電灯調光装置
JPS6073004A (ja) * 1983-09-28 1985-04-25 Yanmar Diesel Engine Co Ltd 内燃機関の油圧動弁装置
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EP0520633A2 (fr) * 1991-06-24 1992-12-30 Ford Motor Company Limited Dispositif de commande hydraulique de soupapes pour moteurs à combustion interne
WO1993001399A1 (fr) 1991-07-12 1993-01-21 Caterpillar Inc. Systeme de soupape de moteur a recuperation et son procede de fonctionnement
JPH0726925A (ja) * 1993-07-07 1995-01-27 Zexel Corp 内燃機関のバルブ制御装置
DE10024268A1 (de) 2000-05-17 2001-11-22 Bosch Gmbh Robert Vorrichtung zur Benzindirekteinspritzung in einer Kolbenbrennkraftmaschine
WO2001096715A1 (fr) * 2000-06-13 2001-12-20 Pueski Attila Appareillage de commande de soupape hydraulique pour moteur a combustion interne
DE102004022447A1 (de) 2004-05-06 2005-12-01 Robert Bosch Gmbh Hydraulischer Steller und Verfahren zum Betreiben eines hydraulischen Stellers
WO2006138368A2 (fr) 2005-06-16 2006-12-28 Lgd Technology, Llc Actionneur de soupape variable
WO2007138057A1 (fr) 2006-05-26 2007-12-06 Robert Bosch Gmbh Procédé de commande de l'échange gazeux d'un moteur à combustion interne
JP2009150296A (ja) 2007-12-20 2009-07-09 The Ship Machinery Manufacturers Association Of Japan 吸排気弁駆動装置
CN102278161B (zh) * 2011-07-19 2013-07-24 天津大学 可变气门用缓冲液压缸
WO2014179906A1 (fr) 2013-05-07 2014-11-13 江苏公大动力技术有限公司 Commande à levée variable

Patent Citations (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1940177A1 (de) 1968-08-08 1970-02-19 Kaiser Aluminium Chem Corp Verfahren zur Gewinnung von Aluminium
JPS58150296A (ja) 1982-03-01 1983-09-06 クロイ電機株式会社 放電灯調光装置
JPS6073004A (ja) * 1983-09-28 1985-04-25 Yanmar Diesel Engine Co Ltd 内燃機関の油圧動弁装置
JPS62253911A (ja) * 1986-03-31 1987-11-05 Tech Res Assoc Highly Reliab Marine Propul Plant 往復動内燃機関用油圧駆動給気弁および排気弁
EP0520633A2 (fr) * 1991-06-24 1992-12-30 Ford Motor Company Limited Dispositif de commande hydraulique de soupapes pour moteurs à combustion interne
WO1993001399A1 (fr) 1991-07-12 1993-01-21 Caterpillar Inc. Systeme de soupape de moteur a recuperation et son procede de fonctionnement
JPH0726925A (ja) * 1993-07-07 1995-01-27 Zexel Corp 内燃機関のバルブ制御装置
DE10024268A1 (de) 2000-05-17 2001-11-22 Bosch Gmbh Robert Vorrichtung zur Benzindirekteinspritzung in einer Kolbenbrennkraftmaschine
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WO2021121639A1 (fr) * 2019-12-20 2021-06-24 Empa Eidgenössische Materialprüfungs- Und Forschungsanstalt Entraînement hydraulique pour des constituants d'accélération et de freinage qui doivent être déplacés de manière dynamique

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