EP1364108B1 - Systeme de soupape d'echange gazeux pour moteur a combustion interne - Google Patents

Systeme de soupape d'echange gazeux pour moteur a combustion interne Download PDF

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Publication number
EP1364108B1
EP1364108B1 EP02708247A EP02708247A EP1364108B1 EP 1364108 B1 EP1364108 B1 EP 1364108B1 EP 02708247 A EP02708247 A EP 02708247A EP 02708247 A EP02708247 A EP 02708247A EP 1364108 B1 EP1364108 B1 EP 1364108B1
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EP
European Patent Office
Prior art keywords
valve
gas
exchange valve
pressure accumulator
piston
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.)
Expired - Lifetime
Application number
EP02708247A
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German (de)
English (en)
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EP1364108A1 (fr
Inventor
Hermann Gaessler
Udo Diehl
Karsten Mischker
Rainer Walter
Juergen Schiemann
Christian Grosse
Volker Beuche
Stefan Reimer
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Robert Bosch GmbH
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Robert Bosch GmbH
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Filing date
Publication date
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Publication of EP1364108A1 publication Critical patent/EP1364108A1/fr
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Publication of EP1364108B1 publication Critical patent/EP1364108B1/fr
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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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L2013/0089—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque with means for delaying valve closing
    • F01L2013/0094—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque with means for delaying valve closing with switchable clamp for keeping valve open

Definitions

  • the present invention relates to a gas exchange valve device for an internal combustion engine, according to the preamble of claim 1.
  • Such a gas exchange valve device is known from DE 198 26 047 A1.
  • Such a gas exchange valve device is used when the internal combustion engine has no camshaft.
  • Such an internal combustion engine has the advantage that the timing of the intake and exhaust valves are independent of the position of the piston of the respective cylinder. Depending on the operating state of the internal combustion engine, e.g. high speed, and depending on the driver's desired torque valve opening and closing times can be realized, which allow a particularly emission and consumption optimized operation of the internal combustion engine.
  • the known hydraulic device operates with a hydraulic circuit, which consists of a hydraulic reservoir powered by a high pressure hydraulic pump.
  • the actuating device comprises a piston which can be acted upon hydraulically in both directions of movement and which is connected to the valve stem of the valve element of a gas exchange valve.
  • By means of 2/2 shift valves one of the two chambers of the hydraulic cylinder can in each case be subjected to a higher pressure, which leads to a corresponding movement of the piston and thereby of the valve element on the engine block.
  • the hydraulic circuit is connected to a hydraulic pressure accumulator, which is designed as a spring-loaded piston accumulator and serves to dampen vibrations in the hydraulic system. Further, a similarly constructed emergency accumulator is connected to one of the two chambers in the hydraulic cylinder, which still provides enough pressure and fluid volume at a drop in pressure in the hydraulic line, that the valve can be moved to its closed rest position. Both accumulators work with different pressure levels, which are set by different stiffnesses of their return springs.
  • an emergency closing spring is provided in the known gas exchange valve device, which presses the piston of the actuator and thus also the valve element in the closed position when no hydraulic pressure is present.
  • the valve element does not project into the combustion chamber in such a way that it can, for example, collide with other valve elements or even with the piston of the internal combustion engine moving in the combustion chamber.
  • the disadvantage of such Notschplifeder is, however, that it is provided only for this one special purpose and otherwise has no function.
  • the integration of Notschegafeder in the gas exchange valve device may prove problematic due to the available space.
  • the emergency closing spring increases the necessary hydraulic opening pressure of the valve element of the gas exchange valve, since its closing force must be additionally overcome. Therefore, a higher hydraulic pressure and thus a higher energy consumption is required to open the gas exchange valve in normal operation.
  • the present invention therefore has the object, a gas exchange valve device of the type mentioned in such a way that it can be made cheaper and easier and operated with the least possible expenditure of energy.
  • the invention assumes that the pressure accumulator in Each case is designed so that it can still provide such a sufficient fluid volume at a drop in the hydraulic pressure in the fluid circuit, that the actuator is able to bring the valve element of the gas exchange valve in a substantially closed position.
  • the piston of the pressure accumulator moves due to its bias in the direction of its non-pressurized rest position: This he achieved when the fluid circuit and thus the pressure accumulator are substantially depressurized.
  • this movement of the valve element of the pressure accumulator is additionally used for the blocking operation of the valve element.
  • the pressure accumulator is arranged so that its piston releases the valve element of the gas exchange valve when it is pressurized via the fluid circuit and pushed out of its rest position. In such an operating state in which the fluid circuit and thus also the pressure accumulator are pressurized, the valve element can move freely and consequently the internal combustion engine can also be operated normally.
  • the hydraulic fluid is forced out of the pressure accumulator by the spring action of the piston and the valve element of the gas exchange valve is closed via the actuating device.
  • the pressure accumulator according to the invention arranged so that it, when the piston reaches its non-pressurized rest position and the pressure accumulator thus no fluid volume for closing or holding the closed state of the valve element can be already provided, the valve element of the gas exchange valve in this substantially closed Position blocked.
  • an emergency closing spring is no longer required, since the locking of the valve element of the gas exchange valve is taken over by the piston of the pressure accumulator in a substantially closed position in the event of a pressure loss.
  • the gas exchange valve device according to the invention can thus be made considerably cheaper and easier.
  • a lower hydraulic pressure is required for movement of the valve element in an open position, since in addition to the inertial forces of the valve element no further forces must be overcome.
  • valve stem of the valve element of the gas exchange valve at least indirectly applied.
  • the valve stem of the valve member generally has a certain length, so that the positioning of the pressure accumulator so that its piston can act on the valve stem, is relatively easily possible. It is also conceivable, however, that the piston of the pressure accumulator, for example, acts directly on the actuating device, and blocks there, for example, the piston of a hydraulic cylinder in a certain position.
  • At least indirectly connected to the piston of the pressure accumulator contact surface and at least indirectly connected to the valve element of the gas exchange valve contact surface in the approximately unpressurized state of the pressure accumulator cooperate in frictional engagement.
  • frictional engagement in the Generally only very small forces are required for a blockage of the valve element of the gas exchange valve.
  • the valve element of the gas exchange valve can move due to its weight from the closed position to the open position. This is reliably possible by a simple frictional engagement. Such is very inexpensive and easy to implement.
  • the at least indirectly connected to the piston of the pressure accumulator contact surface with the at least indirectly indirectly connected to the valve element of the gas exchange valve contact surface in the approximately unpressurized state of the pressure accumulator in positive engagement.
  • This training is possible alternatively or in addition to the above-mentioned frictional engagement.
  • a positive connection allows even more secure blocking of the valve element in the desired position.
  • a recess is present in the valve stem of the valve element of the gas exchange valve, in which a at least indirectly connected to the piston of the accumulator engaging portion engages in the approximately unpressurized state of the pressure accumulator.
  • a positive engagement is easy and inexpensive to implement. It is Of course, the reverse case is also conceivable, namely that a recess in a part connected to the piston moves to an existing on the valve stem of the valve element bulge.
  • the positive connection for example, with the actuating device is possible, which acts on the valve element.
  • the recess may be arranged so that the gas exchange valve is blocked in the approximately unpressurized state of the pressure accumulator in a slightly open position.
  • This has the advantage that the start of the internal combustion engine is facilitated. The reason for this is, in turn, that the starter of the internal combustion engine initially only the.
  • the necessary for the pressure build-up in the hydraulic circuit compression work must be provided. It is of course important to ensure that the position of the valve element in which the blocking takes place, is chosen so that there is no risk of collision of the valve element with the piston moving in the combustion chamber of the internal combustion engine and not with the valve elements of other gas exchange valves.
  • a gas exchange valve device as a whole carries the reference numeral 10. It comprises a gas exchange valve, which in the present case is designed as an inlet valve 12 of an internal combustion engine 14.
  • the intake valve 12 is actuated by a hydraulic cylinder 16.
  • This comprises a housing 18 in which a piston 20 is slidably guided with a piston rod 22.
  • the piston rod 22 is passed through the housing 18 and connected to a valve stem 24, which in turn is integrally formed on a plate-shaped valve element 26.
  • a portion of the surface of the valve stem 24 is designed as a friction surface 25 (see Fig. 2).
  • the valve element 26 is close to a valve seat 28 in the upper region of a combustion chamber 30 of the internal combustion engine 14 at.
  • the gas exchange valve device 10 further comprises a reservoir 34 from which hydraulic fluid from a high-pressure pump 36 is conveyed into a high-pressure hydraulic line 38.
  • the high-pressure hydraulic line 38 branches into a branch 42, which opens directly into a lower working space 44 of the hydraulic cylinder 16 in FIG. 1 (the terms “top” and “bottom” in this description refer only to the illustrations in FIG It will be appreciated that the parts of the gas exchange device 10 can be installed in any position.
  • Another branch 46 of the high-pressure hydraulic line 38 leads to a 2/2-way switching valve 48, which is pressed in the de-energized state by a spring 50 in its closed position.
  • the branch 46 of the high-pressure hydraulic line 38 leads after the 2/2-way switching valve 48 to an upper working space 52 of the hydraulic cylinder 16 in FIG. 1. From there, a high-pressure hydraulic line 54 leads via a further 2/2-way switching valve 56 and a check valve 58 back to the reservoir 34.
  • the 2/2-way switching valve 56 is open when de-energized.
  • a stub 60 opens, which is connected to a pressure accumulator 62.
  • the accumulator 62 includes a housing 64 in which a piston 66 is slidably held. The piston 66 is acted upon by a spring 68 in the direction of the end of the pressure accumulator 62, which is connected to the stub 60.
  • the stiffness and the spring travel of the spring 68 are chosen so that the pressure accumulator 62 as a vibration damper for in the Hydraulic lines 38, 42, 46 and 54 occurring pressure fluctuations can work.
  • a housing 70 of a further pressure accumulator 72 is formed. Its design can be seen in detail from FIG. 2:
  • a cavity 74 is formed in which a piston 76 is movably supported.
  • the outer surface of the piston 76 is sealed relative to the inner wall of the cavity 74 via a sealing ring 78 which lies in an annular groove 80 in the outer circumferential surface of the piston 76.
  • the cavity 74 is closed by a lid 82.
  • the lid 82 is provided with a not visible in the figure ventilation opening.
  • a coil spring 84 is tensioned, which acts on the piston 76 in Figure 2 to the left.
  • a blocking rod 86 is formed, which extends in the unpressurized state of the pressure accumulator 72 shown in Figure 2 through a passage 88 into a working space 90.
  • the valve stem 24 of the valve element 26 of the inlet valve 12 extends perpendicular to the longitudinal axis of the piston 76 and the blocking rod 86 also through the working space 90 therethrough. It is sealed off from the working space 90 by sealing rings 92 and 94.
  • the valve stem 24 facing axial end of the blocking rod 86 is formed as a friction surface 87th From the working space 90, a branch line 96 leads to the lower working space 44 of the hydraulic cylinder 16.
  • the coil spring 84 of the accumulator 72 has a lower rigidity and a greater spring travel than the spring 68 of the pressure accumulator 62.
  • the pressure accumulator 72 does not work as vibration damper, but as Not horrept8:00.00, a pressure drop in the hydraulic lines 38, 42, 46 and 54 provides a fluid volume sufficient to the valve member 26 of the Inlet valve 12 to move to its closed position.
  • the gas exchange valve device 10 shown in FIGS. 1 and 2 operates as follows:
  • the high-pressure pump 36 delivers hydraulic fluid from the reservoir 34 in the hydraulic line 38 and from there via the branch line 42 in the lower working space 44 of the hydraulic cylinder 16.
  • the switching valve 48 geöff and the switching valve 56 is closed, and the upper working chamber 52 of the hydraulic cylinder 60th pressurized by hydraulic fluid. Since the engagement surface in the axial direction on the upper side of the piston 20 of the hydraulic cylinder 16 is greater than on its underside, in this case the piston 20 is pressed down and the inlet valve 12 is opened.
  • the switching valve 48 is closed and the switching valve 56 is opened, the upper working chamber 52 is connected via the branch line 54 with the ambient pressure, whereby the piston 20 moves up again and the inlet valve 12 is closed.
  • very fast opening and closing times of the intake valve 12 can be achieved without requiring mechanical actuation of the intake valve 12 by, for example, a camshaft of the internal combustion engine 14.
  • valve element 26 can be moved freely via the valve stem 74 and the piston rod 22 from the piston 20 of the hydraulic cylinder 16. Since neither the piston 20 nor the valve member 26 are pressed by a spring in one or the other position, only a small hydraulic force is required for the movement of the valve member 26.
  • the pressure in the cavity 74 of the pressure accumulator also drops as a result 72.
  • the coil spring 84 can push the piston 76 of the pressure accumulator 72 in Figure 2 to the left.
  • the stored hydraulic fluid in the cavity 74 is therefore forced through the passage 88, the working space 90 and the stub 96 into the lower working space 44.
  • the incoming hydraulic fluid in turn pushes the piston 20 of the hydraulic cylinder 16 upwards.
  • the switching valve 56 is open when the engine 14 is turned off and therefore the upper working chamber 52 of the hydraulic cylinder 16 is depressurized. As a result, in turn, the valve element 26 is moved or pushed upwards against the valve seat 28 via the piston rod 22 and the valve stem 24, so the valve element 26 is ultimately brought into its closed position by the work of the piston 76 of the pressure accumulator 72.
  • the piston 76 When the pressure in the cavity 74 drops to ambient pressure, the pressure accumulator 72 is thus depressurized, the piston 76 reaches its extreme left position, which is defined by the fact that the friction surface 87 on the side facing away from the piston 76 of the locking rod 86 against the friction surface 25th on the valve stem 24 of the valve member 26 presses.
  • the spring travel of the spiral spring 84 is chosen so that even in this position of the piston 76 of the accumulator 72, the coil spring 84 is not fully relaxed, so it still exerts a force on the piston 76.
  • the length of the blocking rod 86 is in turn chosen so that when its friction surface 87 rests against the friction surface 25 of the valve stem 24, the piston 76 does not yet come to rest on the left in Figure 2 boundary wall of the cavity 74 into abutment.
  • the friction surface 87 of the blocking rod 86 is thus ultimately pressed by the coil spring 84 against the friction surface 25 on the valve stem 24 and thereby produces a frictional engagement between these two elements.
  • the axial position of the annular groove 25 in the valve stem 24 is selected so that when the tip 87 of the blocking rod 86 engages in the annular groove 25 in the valve stem 24, the inlet valve 12 is not completely closed, but slightly open. This means, the valve element 26 is lifted off the valve seat 28.
  • the annular groove 25 is positioned in the valve stem 24 such that the opening stroke h of the valve element 26 is approximately 0.5 to 1.0 mm.
  • the gas exchange valve device comprises no separate pressure accumulator for the vibration damping. Instead, the vibration damping function is integrated in those pressure accumulator, which blocks the valve element in the unpressurized state. This is achieved by the fact that the existing in this pre-tensioning device operates in two stages: In a harder area of the pretensioner it provides the vibration damping function, in a softer area the emergency pressure and the blocking function. This is possible, for example, the series connection of two springs with different stiffness.

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

Abstract

La présente invention concerne un système de soupape d"échange gazeux (10) destiné à un moteur à combustion interne (14) appartenant notamment à une automobile, ledit système comprenant un dispositif hydraulique (15). Ledit dispositif hydraulique comprend un circuit hydraulique (38, 42, 46, 54), un accumulateur hydraulique (62, 72) relié au circuit hydraulique (38, 42, 46, 54) et comprenant un piston (66, 76) précontraint par un système (68, 84), ainsi qu"un système d"actionnement commandé (16). Le système de l"invention comprend également une soupape d"échange gazeux (12) dont l"élément de soupape (26) est soumis à l"action du système d"actionnement (16). Afin de simplifier la conception du système de soupape d"échange gazeux (10), l"accumulateur hydraulique (72) est disposé de sorte que son piston (76), dans un état sensiblement non pressurisé de l"accumulateur hydraulique (72), bloque au moins indirectement l"élément de soupape (26) de la soupape d"échange gazeux (12) dans une position sensiblement fermée.

Claims (8)

  1. Système de soupape d'échange gazeux (10) pour un moteur à combustion interne (12), en particulier d'un véhicule automobile, a vec un dispositif hydraulique (15) qui comprend un circuit de fluide (38, 42, 46, 54), au moins un accumulateur de pression (62, 72) raccordé au circuit de fluide (38, 42, 46, 54) et ayant un piston (66, 76) précontraint par un dispositif (68, 84), et un dispositif de commande hydraulique réglable (16), et avec une soupape d'échange gazeux (12) dont l'élément de soupape (26) est actionné par le dispositif de commande hydraulique (16) du dispositif hydraulique, dans lequel l'accumulateur de pression (62, 72) est réalisé de telle façon qu'il puisse encore en cas de disparition de la pression hydraulique dans le circuit de fluide (38, 42, 46, 54), mettre à disposition un volume de fluide suffisant pour que le dispositif de commande (16) puisse amener l'élément de soupape (26) de la soupape d'échange gazeux (12) dans une position sensiblement fermée,
    caractérisé en ce que
    l'accumulateur de pression (62, 72) est disposé de sorte que son piston (76) bloque au moins indirectement l'élément de soupape (26) de la soupape d'échange gazeux (12) dans la position sensiblement fermée lorsque l'accumulateur de pression (72) se trouve dans un état sensiblement sans pression.
  2. Système de soupape d'échange gazeux (10) selon la revendication 1,
    caractérisé en ce que
    le piston (76) de l'accumulateur de pression (72) actionne au moins indirectement une tige de soupape (24) de l'élément de soupape (26) de la soupape d'échange gazeux (12) lorsque l'accumulateur de pression (72) se trouve dans l'état sensiblement sans pression.
  3. Système de soupape d'échange gazeux (10) selon l'une quelconque des revendications précédentes,
    caractérisé en ce qu'
    une face de contact (87) reliée au moins indirectement au piston (76) de l'accumulateur de pression (72) et une face de contact (25) reliée au moins indirectement à l'élément de soupape (26) de la soupape d'échange gazeux (12) coopèrent par friction lorsque l'accumulateur de pression (72) se trouve dans l'état sensiblement sans pression.
  4. Système de soupape d'échange gazeux selon la revendication 3,
    caractérisé en ce que
    la face de contact reliée au moins indirectement au piston (76) de l'accumulateur de pression (72) et/ou la face de contact reliée au moins indirectement à l'élément de soupape (26) de la soupape d'échange gazeux (12) est/sont formées par une/des face(s) de friction (25, 87).
  5. Système de soupape d'échange gazeux selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    la face de contact (87) reliée au moins indirectement au piston (76) de l'accumulateur de pression (72) et/ou la face de contact (25) reliée au moins indirectement à l'élément de soupape (26) de la soupape d'échange gazeux (12) coopèrent par emboîtement lorsque l'accumulateur de pression (72) se trouve dans l'état sensiblement sans pression.
  6. Système de soupape d'échange gazeux selon la revendication 5,
    caractérisé en ce qu'
    on prévoit un creux (25) dans la tige de soupape (24) de l'élément de soupape (26) de la soupape d'échange gazeux (12), et une partie d'engagement (87) est reliée au moins indirectement au piston (76) et s'engage dans le creux (25) lorsque l'accumulateur de pression (72) se trouve dans l'état sensiblement sans pression.
  7. Système de soupape d'échange gazeux selon la revendication 6,
    caractérisé en ce que
    le creux (25) est disposé de sorte que la soupape d'échange gazeux (12) soit bloquée dans une position légèrement ouverte lorsque l'accumulateur de pression (72) se trouve dans l'état sensiblement sans pression.
  8. Système de soupape d'échange gazeux selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    le piston (76) de l'accumulateur de pression (72) est relié à une tige de blocage (86), qui agit sur l'élément de soupape (26) de la soupape d'échange gazeux (12) lorsque la soupape d'échange gazeux (12) se trouve dans l'état sensiblement sans pression.
EP02708247A 2001-02-19 2002-02-14 Systeme de soupape d'echange gazeux pour moteur a combustion interne Expired - Lifetime EP1364108B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10107698A DE10107698C1 (de) 2001-02-19 2001-02-19 Gaswechselventileinrichtung für eine Brennkraftmaschine
DE10107698 2001-02-19
PCT/DE2002/000522 WO2002066796A1 (fr) 2001-02-19 2002-02-14 Systeme de soupape d"echange gazeux pour moteur a combustion interne

Publications (2)

Publication Number Publication Date
EP1364108A1 EP1364108A1 (fr) 2003-11-26
EP1364108B1 true EP1364108B1 (fr) 2006-03-15

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Application Number Title Priority Date Filing Date
EP02708247A Expired - Lifetime EP1364108B1 (fr) 2001-02-19 2002-02-14 Systeme de soupape d'echange gazeux pour moteur a combustion interne

Country Status (5)

Country Link
US (1) US6848400B2 (fr)
EP (1) EP1364108B1 (fr)
JP (1) JP2004518845A (fr)
DE (2) DE10107698C1 (fr)
WO (1) WO2002066796A1 (fr)

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7004122B2 (en) * 2002-05-14 2006-02-28 Caterpillar Inc Engine valve actuation system
US6907851B2 (en) 2002-05-14 2005-06-21 Caterpillar Inc Engine valve actuation system
DE10306456B4 (de) * 2003-02-17 2006-11-30 Robert Bosch Gmbh Stellvorrichtung zur elektrohydraulischen Betätigung von Gaswechselventilen einer Brennkraftmaschine
DE10310300A1 (de) * 2003-03-10 2004-09-23 Robert Bosch Gmbh Verfahren zum Betreiben eines hydraulischen Aktors, insbesondere eines Gaswechselventils einer Brennkraftmaschine
EP1520962A1 (fr) * 2003-10-02 2005-04-06 Ford Global Technologies, LLC, A subsidary of Ford Motor Company Système de controle variable de soupape et procédé de controle variable de soupape de moteur à combustion interne
DE102006018588A1 (de) * 2006-04-21 2007-10-25 Schaeffler Kg Ventilbetätigungseinrichtung, insbesondere für Gaswechselventile von Hubkolbenbrennkraftmaschinen
WO2008156913A2 (fr) * 2007-05-11 2008-12-24 Lawrence Livermore National Security, Llc Moteur harmonique
EP2063075A1 (fr) 2007-11-23 2009-05-27 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Commande de soupape entraînée par fluide
JP4831839B2 (ja) * 2008-03-27 2011-12-07 三菱重工業株式会社 エンジンバルブアクチュエータ及び内燃機関
DE102008027650A1 (de) * 2008-06-10 2009-12-17 Man Diesel Se Ventilsteuerung für ein Gaswechselventil in einer Brennkraftmaschine
SE546024C2 (en) * 2022-07-11 2024-04-16 Freevalve Ab An apparatus comprising a plurality of tools, wherein each tool comprises at least one hydraulic chamber

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3739891A1 (de) * 1987-11-25 1989-06-08 Porsche Ag Vorrichtung zum betaetigen eines gaswechsel-tellerventils
US6308690B1 (en) * 1994-04-05 2001-10-30 Sturman Industries, Inc. Hydraulically controllable camless valve system adapted for an internal combustion engine
DE19826047A1 (de) * 1998-06-12 1999-12-16 Bosch Gmbh Robert Vorrichtung zur Steuerung eines Gaswechselventils für Brennkraftmaschinen
US6223846B1 (en) * 1998-06-15 2001-05-01 Michael M. Schechter Vehicle operating method and system
DE19935871C2 (de) * 1999-07-30 2003-02-13 Daimler Chrysler Ag Vorrichtung mit zumindest einem elektromagnetischen Aktuator zum Betätigen eines Gaswechselventils und ein Verfahren zu deren Betreibung

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Publication number Publication date
WO2002066796A1 (fr) 2002-08-29
EP1364108A1 (fr) 2003-11-26
JP2004518845A (ja) 2004-06-24
DE50206078D1 (de) 2006-05-11
DE10107698C1 (de) 2002-08-22
US20040035378A1 (en) 2004-02-26
US6848400B2 (en) 2005-02-01

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