EP1440225B1 - Actionneur hydraulique pour soupape de moteur - Google Patents

Actionneur hydraulique pour soupape de moteur Download PDF

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Publication number
EP1440225B1
EP1440225B1 EP02762231A EP02762231A EP1440225B1 EP 1440225 B1 EP1440225 B1 EP 1440225B1 EP 02762231 A EP02762231 A EP 02762231A EP 02762231 A EP02762231 A EP 02762231A EP 1440225 B1 EP1440225 B1 EP 1440225B1
Authority
EP
European Patent Office
Prior art keywords
valve
chamber
piston
gas exchange
actuator according
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
EP02762231A
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German (de)
English (en)
Other versions
EP1440225A2 (fr
Inventor
Udo Diehl
Karsten Mischker
Uwe Hammer
Volker Beuche
Peter Lang
Stefan Reimer
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from DE10228702A external-priority patent/DE10228702A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1440225A2 publication Critical patent/EP1440225A2/fr
Application granted granted Critical
Publication of EP1440225B1 publication Critical patent/EP1440225B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the invention relates to a hydraulic actuator for a Gas exchange valve for internal combustion engines (see, for example, SE-B-353575).
  • the opening and closing of the gas exchange valve should as possible done quickly to the flow losses of the Gas exchange valve when sucking the combustion air or to minimize when pushing out the exhaust gases from the combustion chamber.
  • the invention is based on the object, a hydraulic Actuator for a gas exchange valve to provide a great force at the beginning of the opening movement on the Gas exchange valve can exercise, the fast control movements allows the gas exchange valve and in which the Gas exchange valve with low speed on the Valve seat impinges.
  • a hydraulic actuator for a gas exchange valve one Internal combustion engine with a cylinder bore, with a Piston and an annular piston, the piston and the Ring piston are guided in the cylinder bore, wherein the Piston, the ring piston and the cylinder bore in axial Limit a first chamber whose volume increases, when the actuator opens the gas exchange valve, wherein the Ring piston and the cylinder bore in the axial direction a second chamber limit, whose volume decreases when the Actuator opens the gas exchange valve, the piston and the Cylinder bore limit a third chamber whose volume decreases when the actuator opens the gas exchange valve, wherein a device for limiting the volume decrease of second chamber is provided and the first chamber and the second chamber via a throttle communicate with each other.
  • the hydraulic actuator according to the invention is at the beginning the opening movement of the gas exchange valve a large hydraulic force from the actuator to the gas exchange valve transferred so that despite the back pressure from the combustion chamber on the valve plate of the gas exchange valve the Gas exchange valve safely and quickly lifted off the valve seat can be.
  • the Ring piston stops moving and it works As a result, only a lower hydraulic force the piston of the actuator, in turn, on the gas exchange valve is transmitted.
  • With reduction of hydraulic power reduces the adjustment of the actuator piston required energy, so that the total energy demand for the valve control of the internal combustion engine decreases. Simultaneously with the reduction of this force changes also the positioning speed of the gas exchange valve.
  • the Piston has a puncture that the annular piston a Outer surface and a stepped center hole with a larger diameter and a smaller diameter has, and that the annular piston with the larger diameter the center hole on the piston can be pushed, so that on simple way the ratio of the operating forces of the Actuator when opening the gas exchange valve and during the remaining adjusting movement is adjustable.
  • This effect can be further increased by the fact that the Diameter of the piston on both sides of the groove are different and that the ring piston on the larger Diameter is pushed.
  • the means for limiting the decrease in volume of the second chamber is hydraulically connected to the second chamber pressure accumulator with a piston and that the path of the piston can be limited, so that in a simple manner by hydraulic means of Ring piston can be locked. Since the accumulator does not reach the high temperatures of the gas exchange valve and the cylinder head of the internal combustion engine, the position in which the annular piston is locked after the opening of the gas exchange valve, regardless of the thermal expansion of the gas exchange valve and the cylinder head. Further embodiments of the invention provide that the pressure accumulator is a spring accumulator or a gas storage and / or that the way of the piston by a stop, in particular an adjustable stop, can be limited, so that the actuator according to the invention can be easily adjusted.
  • first Chamber via a first switching valve with a pump is connectable
  • second chamber via a second Switching valve with an oil sump is connectable
  • third chamber with the delivery pressure of the pump acted upon is, so that by operating two switching valves the Gas exchange valve with the hydraulic according to the invention Actuator can either be opened or closed, with the increased force when lifting the gas exchange valve from Valve seat and the delay of the gas exchange valve before the Impact on the valve seat automatically from the be realized according to the invention hydraulic actuator.
  • the inventive effect of the actuator is further characterized supports that the first chamber and the second chamber via an adjustable throttle, hydraulically communicate with each other and / or that one Check valve between the second chamber and the first chamber is provided, which is the hydraulic connection of the first chamber to the second chamber locks.
  • the throttle has decisive influence on the deceleration of the gas exchange valve before hitting the valve seat.
  • the device for limiting the volume decrease in the second chamber with an opening in the second chamber in Connection standing on shut-off valve the opening in its one switching position closes and in its other Switching position releases fluid outflow.
  • the ring piston With closing the Shut-off valve, the ring piston is fixed so that the Closing time of the shut-off valve the stroke of the Determines annular piston. From the stroke of the ring piston is turn the time of onset of braking effect Closing the gas exchange valve dependent, the at a larger stroke of the ring piston earlier and a smaller one Hub starts later.
  • the shut-off valve can thus the Brake start regardless of manufacturing tolerances or Material expansion due to temperature fluctuations be set.
  • the shut-off valve not as an additional unit but its function anyway for the Initiation of the closing process of the gas exchange valve assigned required second switching valve.
  • the throttle can indeed on this flow-controlled valve can be dispensed with, since only small amounts of fluid flow through the throttle, but at larger throttle opening to achieve only a small Braking effect on the gas exchange valve is the flow-controlled Valve to shut off the throttle to avoid larger Leakage essential.
  • FIG. 1 represents a hydraulic actuator with a housing 1 in longitudinal section.
  • the housing 1 has a stepped cylinder bore 3. to Simplification of the production is in the housing 1 a sleeve 5 pressed, the inner bore part of the stepped Cylinder bore 3 is. In the area of the sleeve 5 is in the Cylinder bore 3 an annular piston 7 and a piston 9 out. In the position of the piston 9 shown in Fig. 1 is the not shown gas exchange valve closed.
  • the cylinder bore 3, the piston 9 and the annular piston 7 limit in the direction of a longitudinal axis 11 of the piston 9 a first chamber 13. So between cylinder bore 3 and piston 9 no fluid or fluid can escape, is a first Sealing ring 15 at the left in Fig. 1 end of the first chamber thirteenth arranged.
  • the piston 9 has a recess 17.
  • the diameter of the piston 9 on both sides of the groove 17 are of different sizes.
  • the piston 9 has a smaller diameter d 1
  • the piston 9 has a larger diameter d 2 .
  • the annular piston 7 is arranged between the sleeve 5 and the piston 9, the annular piston 7 is arranged.
  • the annular piston 7 is fitted in the cylinder bore 3 so that it is displaceable on the one hand in the axial direction and that on the other hand, a good sealing effect between the cylinder bore 3 and the annular piston 7 is achieved.
  • the annular piston 7 has a stepped center hole 19 with a smaller diameter d 3 and a larger diameter, which is as large as d 2 , on.
  • the fit between the annular piston 7 and the larger diameter d 2 of the piston 9 is also chosen so that the annular piston 7 and piston 9 are movable relative to each other in the axial direction and still a good sealing effect is achieved.
  • the cylinder bore 3 and the annular piston 7 define a second chamber 27.
  • the cylinder bore 3 has a diameter d 4 in this area, which corresponds to the outer diameter of the annular piston 7.
  • this has a shoulder with the diameter d 5 .
  • the annular piston 7, the part of the cylinder bore 3 with the diameter d 4 and the piston define a second chamber 27.
  • the first chamber 13 is hydraulically connectable via a first switching valve 29 to a pump 31.
  • the first switching valve 29 may be formed, for example, as an electrically operated solenoid valve.
  • the pump 31 acts on the third chamber 25 permanently the delivery pressure generated by it.
  • switching valve 33 may be a hydraulic connection between the second chamber 27 and a relief space or oil sump 35 are made.
  • a check valve 39th arranged in a conduit 37, which second chamber 27 and second Switching valve 33 connects.
  • a hydraulic accumulator 41 is connected.
  • Hydraulic reservoir 41 has a piston 43 which extends against the force of a spring 45 moves when the on the Spring 45 facing away from the end face of the piston 43 acting pressure is sufficiently high. This print is the same size as the Pressure in the line 37.
  • the path of the piston 43 against the Force of the spring 45 is by a stop 47, which also can be made adjustable, limited.
  • Between the first chamber 13 and the second chamber 27 is a provided hydraulic connection in which an adjustable Throttle 49 is arranged.
  • the hydraulic force acting on the first annular surface A 1 is reduced by the hydraulic forces acting on a third annular surface A 3 and a fourth annular surface A 4 .
  • the third annular surface A 3 is limited by the shoulder in the piston 9, which is formed by the diameter d 1 of the piston 9 and the diameter d 6 of the recess 17. On the third annular surface A 3 , the hydraulic fluid in the first chamber 13 exerts a force acting in FIG. 1 to the left.
  • the fourth annular surface A 4 is bounded by a shoulder 51 of the piston 9 in the region of the third chamber 25.
  • the heel 51 is formed by the diameter d 2 and the diameter d 5 of the piston 9.
  • the fourth annular surface A 4 always exerts a force acting counter to the opening direction on the piston 9, since, as already mentioned, the third chamber 25 is always acted upon by the pre-pressure of the pump 31.
  • the piston 9 moves to the right when the first chamber 13 is acted upon by the delivery pressure of the pump 31.
  • the annular piston 7 transmits the hydraulic force acting on it via the shoulder of its stepped center hole 19 on the piston 9.
  • the movement of the piston 9 in Fig. 1 to the right has the opening of the gas exchange valve, not shown result.
  • the actuator is shown in a position, in which the gas exchange valve is closed and the full Opening force is available.
  • Fig. 2b the state is shown in which the volume of the second chamber 27 is no longer decreasing, since the pressure accumulator 41, not shown in Fig. 2 no longer receives fluid. As a result, the annular piston 7 no longer moves. If the gas exchange valve is opened further, leaves the piston 9 with its diameter d 2, the stepped center hole 19 of the annular piston 7. From this position, a direct hydraulic connection between the first chamber 13 and second chamber 27 is present. At the opening force, this does not change anything.
  • the position at which the desired deceleration of the gas exchange valve begins before impinging on the valve seat, not shown, is dependent on the stroke of the accumulator piston 43 and thus not on the thermal expansion to which the hydraulic actuator is exposed. Even manufacturing tolerances of the actuator do not influence this position.
  • the ratios of the opening force when lifting the gas exchange valve from the valve seat and the reduced opening force upon further opening of the gas exchange valve and the closing force when closing the gas exchange valve can be matched to an optimum performance of the hydraulic actuator to reach.
  • Fig. 3 is a detail of the actuator according to FIG. 1. only in the scope of interest with housing 1, the first Chamber 13, second chamber 27 and third chamber 25 and its hydraulic connection to the hydraulic pump 31 with the example. as a 2/2-way solenoid valve formed first switching valve 29th and the hydraulic connection between the first chamber 13 and second chamber 27 via the throttle 49 shown. Of the hydraulic discharge chamber or oil sump is still with 35 and the second chamber 27 with the example. As a 2/2-way solenoid valve formed second switching valve 33rd connecting line designated 37.
  • the hydraulic actuator is modified insofar as the device for limiting the decrease in volume of the second chamber 27, the in Fig.
  • the first switching valve 29 are opened. Fluid now flows under the delivery pressure into the chamber 13, so that the piston 9 of the actuator together with the annular piston. 7 is shifted as shown in Fig. 2b. Becomes a any time during the displacement of the annular piston 7, the second switching valve 33 in its blocking position switched, so no fluid from the second chamber 27th flow out and the annular piston 7 is blocked.
  • the hub of the Ring piston 7 is thus by the time of switching of the open at the beginning of the opening movement of the actuator second Changeover valve 33 set.
  • a flow-controlled valve 51 is turned on, the like is formed so that it from the first chamber 13th inflowing fluid is closable.
  • This flow-controlled Valve 51 prevents being in the initial phase to Auf Kunststoffn the gas exchange valve in which both the first switching valve 29 and the second switching valve 33 is opened, fluid directly from the first switching valve 29 via the second Switching valve 33 flows to the oil sump 35; because of the Throttle 49 flowing leakage increases the energy demand for the valve control when it rises unacceptably.
  • FIG. 5 The structure of the flow-controlled valve 51 is shown in FIG. 5 and FIG. 6 shows schematically, FIG. 5 showing the opened one Valve and Fig. 6 shows the closed valve.
  • the flow-controlled valve 51 has a housing 52 with a associated with the chamber 13 of the actuator first Valve terminal 53, with a throttle 49th connected second valve port 54 and one with the Output of the first switching valve 29 connected third Valve connection 55 on.
  • the first valve port 53 is available a lower valve chamber 56, the third valve port 55 with an upper valve space 57 and the second valve port 54th with a between the lower and upper valve chamber 56, 57 itself located annular space 58 in conjunction.
  • valve seat 59 Between the bottom Valve chamber 56 and the annular space 58 is in the housing 52 one of a valve seat 59 surrounded valve opening 60 is formed.
  • a guide sleeve 61 used in a trained as a sliding piston Valve member 62 is slidably guided.
  • the valve member 62nd acts with the valve seat 59 to close and release the Valve opening 60 together, so that the annular space 58 at on the Valve seat 59 seated valve member 62 (Fig. 6) of the lower valve chamber 56 is shut off and at by the Valve seat 59 lifted valve member 62 (Fig. 5) with the lower valve space 56 is connected.
  • valve opening spring 63 In the lower valve chamber 56 is a valve opening spring 63 inserted, acting as a compression spring is formed and on the one hand at one in the bottom Valve chamber 56 trained shoulder 64 and on the other hand on Valve member 62 is supported.
  • the valve opening spring 63 applies this Valve member 62 against a in the guide sleeve 61st trained stop 65 at.
  • the valve member 62 is provided with a central passage opening 66 provided permanently the upper valve chamber 57 with the lower valve chamber 56 connects.
  • the passage opening 66 is designed as a throttle, including its inner contour 67 a having such an embodiment that that of the upper Valve chamber 57 to the lower valve chamber 56 flowing fluid causes a pressure drop in the passage opening 66.
  • FIGS. 5 and 6 has the Through opening 66 in the form of a double truncated cone, at the two truncated cones with their smaller bases are juxtaposed.
  • the first switching valve 29, fluid flows from the outlet of the pump 31 the passage opening 66 in the valve member 62, due to the inner contour 67, a pressure drop between the upper and lower valve space 57, 56 is formed.
  • the pressure is in upper valve space 57 larger than in the lower valve chamber 56, and it arises on the valve member 62 a resultant Displacement force, contrary to the spring force of the Valve opening spring 63, the valve member 62 on the valve seat 59 touches and thus closes the valve opening 60, whereby the connection to the throttle 49 is blocked.
  • first switching valve 29 If the first switching valve 29 is closed again, then flows no more fluid through the passage opening 66. It arises no pressure drop at the inner contour 67, so that the pressures in lower valve chamber 56 and 57 in the upper valve chamber the same size are.
  • the force acting on the valve member 60 is zero, and by the spring force of the valve opening spring 63 is the Valve member 62 to the stop 65 in the guide sleeve 61st created.
  • the valve member 62 is thus from the valve seat 59th lifted and the first chamber 13 of the actuator with the throttle 49 connected.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Fluid-Driven Valves (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Claims (16)

  1. Actionneur hydraulique destiné à une soupape d'échange gazeux dans un moteur à combustion interne et muni d'un perçage cylindrique (3), d'un piston (9) et d'un piston annulaire (7),
    dans lequel
    le piston (9) et le piston annulaire (7) sont guidés dans le perçage cylindrique (3),
    le piston (9), le piston annulaire (7) et le perçage cylindrique (3) délimitent en direction axiale une première chambre (13) dont le volume augmente lorsque l'actionneur (1) ouvre la soupape d'échange gazeux (23),
    le piston annulaire (7) et le perçage cylindrique (3) délimitent en direction axiale une deuxième chambre (27) dont le volume diminue lorsque l'actionneur (1) ouvre la soupape d'échange gazeux (23),
    le piston (9) et le perçage cylindrique (3) délimitent une troisième chambre (25) dont le volume diminue lorsque l'actionneur (1) ouvre la soupape d'échange gazeux (23),
    caractérisé en ce qu'
    une installation est prévue pour limiter la diminution en volume de la deuxième chambre (27), et
    la première chambre (13) et la deuxième chambre (27) sont reliées l'une à l'autre par un étranglement (49).
  2. Actionneur selon la revendication 1,
    caractérisé en ce que
    le piston (9) a une encoche (17),
    le piston annulaire (7) a un perçage central (19) étagé avec un diamètre (d2) plus grand et un diamètre (d3) plus petit, et
    le piston annulaire (7) peut être engagé sur le piston (9) grâce au diamètre (d2) plus grand du perçage central (19).
  3. Actionneur selon la revendication 2,
    caractérisé en ce que
    les diamètres (d1, d2) du piston (9) sont différents de chaque côté de l'encoche (17) et
    le piston annulaire (7) peut être engagé sur le diamètre (d2) plus grand.
  4. Actionneur selon l'une des revendications 1 à 3,
    caractérisé en ce que
    la troisième chambre (25) est reliée directement et la première chambre (13) est reliée par l'intermédiaire d'une première soupape de commande (29) à la sortie d'une pompe (31) qui produit une pression de refoulement et la deuxième chambre (27) est reliée par l'intermédiaire d'une deuxième soupape de commande (33) à une chambre de décharge (35) qui reçoit un fluide.
  5. Actionneur selon l'une des revendications 1 à 4,
    caractérisé en ce que
    l'installation destinée à limiter la diminution en volume de la deuxième chambre (27) est un accumulateur de pression (41) relié à la deuxième chambre (27) et muni d'un piston (43), et
    la course du piston (43) peut être limitée.
  6. Actionneur selon la revendication 5,
    caractérisé en ce que
    l'accumulateur de pression (41) est un accumulateur à ressort (45) ou un accumulateur à gaz.
  7. Actionneur selon la revendication 5 ou 6,
    caractérisé en ce que
    la course du piston (43) peut être limitée par une butée en particulier par une butée (47) mobile.
  8. Actionneur selon l'une des revendications 1 à 4,
    caractérisé en ce que
    l'installation destinée à limiter la diminution en volume dans la deuxième chambre (27) présente une soupape d'arrêt (50), en liaison avec une ouverture dans la deuxième chambre (27), qui ferme l'ouverture dans l'une de ses positions de commande et qui libère l'écoulement du fluide dans son autre position de commande.
  9. Actionneur selon les revendications 4 et 8,
    caractérisé en ce que
    la soupape d'arrêt est formée par la deuxième soupape de commande (33).
  10. Actionneur selon l'une des revendications 1 à 9,
    caractérisé en ce que
    la première chambre (13) et la deuxième chambre (27) sont liées l'une à l'autre par un étranglement (49) réglable.
  11. Actionneur selon l'une des revendications 1 à 9,
    caractérisé en ce que
    un clapet antiretour (39) est prévu entre la deuxième chambre (27) et la première chambre (13) et
    le clapet antiretour (39) bloque la liaison de la première chambre (13) vers la deuxième chambre (27).
  12. Actionneur selon la revendication 10,
    caractérisé en ce que
    il y a entre la première chambre (13) et l'étrangleur (49) une soupape (51) commandée en courant et formée de telle manière que normalement elle est ouverte et qu'elle peut être fermée par le fluide qui s'écoule vers la première chambre (13).
  13. Actionneur selon la revendication 12,
    caractérisé en ce que
    la soupape (51) commandée en courant présente
    un boítier (52) comportant un premier espace de soupape (56) en liaison avec la chambre (13), un deuxième espace de soupape (58) en liaison avec l'étrangleur (49), un troisième espace de soupape (57) en liaison avec la première soupape de commande (29) et une ouverture de soupape (60) disposée entre le premier et le deuxième espace de soupape (56, 58) et entouré par un siège de soupape (59),
    un organe de soupape (62), mobile axialement dans le boítier, qui délimite le troisième espace de soupape (57) et qui coopère avec le siège de soupape (59) pour ouvrir et pour fermer l'ouverture de soupape (60), et
    une ouverture d'étranglement (66), formée dans l'organe de soupape (62), qui relie l'un à l'autre le premier et le troisième espace de soupape (56, 57).
  14. Actionneur selon la revendication 13,
    caractérisé en ce que
    l'étranglement (49) est formé par le contour intérieur (67) d'une ouverture de passage (66) centrale pratiquée dans l'organe de soupape (62) et dont le contour intérieur (67) est formé de telle manière que le fluide qui s'écoule du troisième espace de soupape (57) dans le premier espace de soupape (56) provoque une diminution de pression sur l'organe de soupape (62).
  15. Actionneur selon la revendication 14,
    caractérisé en ce que
    le contour intérieur (67) de l'ouverture de passage (66) et le ressort d'ouverture de soupape (63) sont ajustés l'un à l'autre de telle manière que la force de déplacement qui agit sur l'organe de soupape (62) du fait de la différence de pression est plus importante que la force opposée exercée par le ressort d'ouverture de soupape (63).
  16. Actionneur selon l'une des revendications 13 à 15,
    caractérisé en ce que
    l'ouverture de passage (66) a la forme d'un double cône tronqué dans lequel deux troncs coaxiaux de cône reposent l'un sur l'autre par leur base la plus petite.
EP02762231A 2001-10-19 2002-07-30 Actionneur hydraulique pour soupape de moteur Expired - Lifetime EP1440225B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10151773 2001-10-19
DE10151773 2001-10-19
DE10228702A DE10228702A1 (de) 2001-10-19 2002-06-27 Hydraulischer Aktor für ein Gaswechselventil
DE10228702 2002-06-27
PCT/DE2002/002791 WO2003038246A2 (fr) 2001-10-19 2002-07-30 Actionneur hydraulique pour soupape a deux voies a gaz

Publications (2)

Publication Number Publication Date
EP1440225A2 EP1440225A2 (fr) 2004-07-28
EP1440225B1 true EP1440225B1 (fr) 2005-08-03

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP02762231A Expired - Lifetime EP1440225B1 (fr) 2001-10-19 2002-07-30 Actionneur hydraulique pour soupape de moteur

Country Status (5)

Country Link
US (1) US6776129B2 (fr)
EP (1) EP1440225B1 (fr)
JP (1) JP4314115B2 (fr)
AT (1) ATE301239T1 (fr)
WO (1) WO2003038246A2 (fr)

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DE10321157A1 (de) * 2003-05-12 2004-12-02 Robert Bosch Gmbh Ventilsteller zur Betätigung eines Gaswechselventils einer Brennkraftmaschine
DE102004042925A1 (de) * 2004-09-02 2006-03-09 Heinz Leiber Federnde Aktuatorankopplung
US8776756B2 (en) 2008-07-18 2014-07-15 Grace Capital partners, LLC Sliding valve aspiration
US8210147B2 (en) * 2008-07-18 2012-07-03 Grace Capital partners, LLC Sliding valve aspiration system
DE102013223926B4 (de) * 2013-11-22 2018-02-08 Schaeffler Technologies AG & Co. KG Hydraulische Ventilbremse für einen hydraulisch variablen Ventiltrieb und Verfahren zur Einstellung der hydraulischen Ventilbremse
US10688979B2 (en) * 2015-03-16 2020-06-23 Ipgate Ag Brake system with floating piston-main brake cylinder unit with a novel type of MUX control (MUX 2.0) with at least one outlet valve, and method for regulating pressure
WO2016146224A1 (fr) 2015-03-16 2016-09-22 Ipgate Ag Système de freinage à régulation de montée en pression avec câblage spécial, vannes d'entrée à circuit de freinage/freins et procédé de régulation de pression
WO2016146692A1 (fr) * 2015-03-16 2016-09-22 Ipgate Ag Dispositif de génération de pression et procédé d'actionnement à piston à double effet a commande électrique
CA3013068A1 (fr) * 2016-02-05 2017-08-10 Dura Tap Llc Dispositifs et procedes pour placement de suture
US10941679B2 (en) 2018-02-21 2021-03-09 Grace Capital Partners Llc Enhanced oiling for sliding valve aspiration system
DE102019109865A1 (de) * 2018-05-08 2019-11-14 Schaeffler Technologies AG & Co. KG Hydraulikeinheit einer elektrohydraulischen Gaswechselventilsteuerung

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JP4314115B2 (ja) 2009-08-12
WO2003038246A3 (fr) 2003-08-28
US6776129B2 (en) 2004-08-17
ATE301239T1 (de) 2005-08-15
WO2003038246A2 (fr) 2003-05-08
EP1440225A2 (fr) 2004-07-28
JP2005507046A (ja) 2005-03-10
US20040050350A1 (en) 2004-03-18

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