EP1347154B1 - Contrôleur de levée de soupapes d'un moteur à combustion interne - Google Patents

Contrôleur de levée de soupapes d'un moteur à combustion interne Download PDF

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Publication number
EP1347154B1
EP1347154B1 EP03005576A EP03005576A EP1347154B1 EP 1347154 B1 EP1347154 B1 EP 1347154B1 EP 03005576 A EP03005576 A EP 03005576A EP 03005576 A EP03005576 A EP 03005576A EP 1347154 B1 EP1347154 B1 EP 1347154B1
Authority
EP
European Patent Office
Prior art keywords
valve controller
controller according
shaft
stator
rotor
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
EP03005576A
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German (de)
English (en)
Other versions
EP1347154A2 (fr
EP1347154A3 (fr
Inventor
Edwin Palesch
Alfred Trzmiel
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.)
Hilite Germany GmbH
Original Assignee
Hydraulik Ring 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
Application filed by Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
Priority to EP07107909A priority Critical patent/EP1832723B1/fr
Publication of EP1347154A2 publication Critical patent/EP1347154A2/fr
Publication of EP1347154A3 publication Critical patent/EP1347154A3/fr
Application granted granted Critical
Publication of EP1347154B1 publication Critical patent/EP1347154B1/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
    • 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
    • F01L13/0021—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 by modification of rocker arm ratio
    • F01L13/0026—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 by modification of rocker arm ratio by means of an eccentric
    • 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
    • F01L2001/34486—Location and number of the means for changing the angular relationship
    • F01L2001/34493—Dual independent phasing system [DIPS]
    • 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
    • F01L2305/00—Valve arrangements comprising rollers
    • 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism
    • F01L2800/08—Timing or lift different for valves of different cylinders

Definitions

  • the invention relates to a valve control for fully variable adjustment of the stroke of valves in motor vehicles according to the preamble of claim 1.
  • valve controls that are used in gasoline engines and the valve strokes vary continuously to reduce fuel consumption.
  • the valve controls power-controlled the valve lift, so that only that amount of fuel is injected into the combustion chamber of the cylinder, which is required for the instantaneous power consumption.
  • an electric motor is provided, whose pinion cooperates with a setting wheel which sits on an adjusting shaft.
  • Valve controls are known ( EP 0 405 927 A1 ), in which a first roller rocker lever cooperates with a second roller rocker arm.
  • a roller drag shaft can be rotated by an electric motor on eccentric plain bearings.
  • An eccentric bearing of the roller drag shaft converts the rotary motion of the motor into an oval motion via the roller rocker arms.
  • a drag lever is displaced to allow any position for spark plugs in the cylinder head.
  • a cam follower is located between a camshaft and a finger follower which acts on rocker arms which simultaneously and in parallel open two inlet gas selector valves. Above the second cams, connecting elements are adjusted, which thus adjust the drag levers.
  • a control shaft is rotated by a motor.
  • the valve control according to EP 0 780 547 A1 has an electric motor provided on a cylinder head with a motor shaft which drives an eccentric shaft via a transmission.
  • the invention has the object of providing the generic Ventit control in such a way that the valve lift can be easily changed in a cost effective manner.
  • the adjusting shaft is rotated by the hydraulic drive so that the valve lift is adjusted in dependence on the currently required power of the engine.
  • the valve control according to the invention operates fully variable, so that within the adjustment range any desired valve lift can be adjusted.
  • the rotational movement of the adjusting shaft is transmitted to the valve stem via the transmission chain.
  • the transmission chain is reciprocated by the camshaft.
  • the hydraulic drive can be implemented easily and inexpensively and is easy to use.
  • valve controls described below allow fully variable control of the stroke of injection valve valves.
  • the intake valves are opened more or less wide, so that only that amount of air is sucked into the combustion chamber of the engine, which is required for the instantaneous power requirement.
  • the corresponding amount of fuel is supplied in a known manner the amount of air.
  • the valve control according to the Fig. 1 to 3 has an adjusting shaft 1, on the rotatable cam 2 are provided. They act on a two-armed intermediate lever 3, one arm 5 rests by means of a roller 4 on the associated cam 2 and with its other arm 6 on a roller 8 of a roller lever 7.
  • the intermediate lever 3 also carries a further roller 60 which bears against the adjusting shaft 1.
  • the camshaft 61 can be seen, the cam 62 rests against a roller 63 of the intermediate lever 3.
  • the intermediate lever 3 is pivoted back and forth in a known manner, being pivoted about the arm 6 of the roller lever 7 and thereby a valve stem 10 against the force of at least one compression spring 11 is moved.
  • the lower (not shown) end of the valve stem 10 carries the valve, with which the inlet opening is closed in the combustion chamber of the engine cylinder.
  • the valve stem 10 is displaced by the roller lever 7 against the force of at least one compression spring 11 when the valve should be opened.
  • the compression spring 11 ensures that the valve is pushed back with a corresponding position of the roller lever 7 in its closed position.
  • the adjusting shaft 1 is coupled to a rotary drive 12 with which the adjusting shaft 11 is limitedly rotatable. He has a cylindrical stator 13 ( Fig. 2 ), whose two end faces are closed by cover plates 14, 15. In the stator 13, two rotors 16 and 17 are housed, of which the rotor 16 is rotatably connected to the adjusting shaft 1. The other rotor 17 is seated on an axis 18 which is aligned with the adjusting shaft 1 and is mounted in the cylinder head 19.
  • the rotors 16, 17 On the inner wall of the stator 13 are radially inwardly wings 20 (FIG. Fig. 2 ), which are at angular intervals of 120 ° to each other.
  • the rotors 16, 17 have a cylindrical base body 21, 22, the axis of which coincides with the axis of the stator 13 and project from the radially outward wing 23. These wings 23 also have an angular distance of 120 ° to each other.
  • the rotors 16, 17 abut with the end faces of the wings 23 on the inner wall of the stator 13.
  • the wings 20 of the stator 13 in turn abut against the outer wall of the cylindrical base body 21, 22.
  • FIG. 2 shows, in each case a vane 23 of the rotors 16, 17 between two vanes 20 of the stator 13.
  • the wings 23 of the rotors 16, 17 are acted upon in a known manner with hydraulic medium, by (not shown) holes in the spaces 24 of the stator 13th arrives.
  • the wings 23 of the rotors 16, 17 can be acted upon on both sides with pressure medium, so that the rotors 16, 17 in the counterclockwise and counterclockwise direction relative to the stator 13 can be rotated.
  • the two rotors 16, 17 are arranged coaxially with each other, but have no connection with each other.
  • the stator 13 has the corresponding pressure chambers 24 for both rotors 16, 17 Fig. 1 shows, from the inner wall of the stator 13 in half the length of an annular wall 25 from which has a central passage opening 26. In it protrude from both sides tapered portions of the main body 21, 22 of the rotors 16, 17.
  • the annular wall 25 is sealingly connected to the edge of the through hole 26 at the tapered end portions of the main body 21, 22 of the rotors 16, 17.
  • the main body 21, 22, as Fig. 1 shows, on the mutually facing inner sides of the annular wall 25 and the cover plates 14, 15 sealingly.
  • the rotor 16 is formed integrally with the adjusting shaft 1. But it can also be connected as a separate component to the adjusting shaft 1.
  • the adjusting shaft 1 projects in a sealed manner through the cover disk 14.
  • the rotor 17 projects with a tapered end portion 27 sealed by the cover plate 15 and lies frontally on a wall of the cylinder head 19 on.
  • the rotor 17 has a central passage opening into which the axle 18 is inserted.
  • the two rotors 16, 17 are rotated independently, since they are housed with their wings 23 in the separate spaces 24 of the stator 13.
  • the cover plates 14, 15 are fastened with screws 28, 29 releasably attached to the annular wall 25.
  • the rotors 16, 17 can be rotated so far about their axes until their wings 23 come to rest on the wings 20 of the stator 13.
  • the maximum displacement angle 30 of the rotors 16, 17 is 90 °.
  • the adjusting shaft 1 can be rotated a maximum of 180 °.
  • the pressure chambers 24 for the two rotors 16, 17 are each acted upon by hydraulic medium.
  • the shaft-side rotor 16 is in the starting position with its wings 23 on the wings 20 of the stator 13 at.
  • the vanes 23 of the other rotor 17 also abut against the stator vanes 20.
  • both rotors 16, 17 are rotated against each other so that their wings abut different stator blades 20, seen in the axial direction of the rotary drive 12.
  • the pressure chambers 24 for the stator 16 are first held under pressure with the hydraulic medium, so that the rotor blades 23 bear against the stator vanes 20 under the pressure of the hydraulic medium.
  • the hydraulic medium is introduced under pressure so that the stator 12 is rotated relative to the rotor 17.
  • the other rotor 16 is so with his wings 23 on the stator vanes 20, that the stator 12 entrains this rotor 16 during the relative rotation.
  • the adjusting shaft 1 is rotated about its axis.
  • the relative rotation between the stator 5 and the rotor 17 can take place, the wings 23 of the rotor 17 on one side with the hydraulic medium pressure acted upon while the limited by the other side of the rotor blade 23 part of the respective pressure chamber 24 is depressurized.
  • the hydraulic medium is held under pressure, that this stop position is maintained.
  • the hydraulic control for the rotor 16 is switched so that now the rotor 16 can rotate relative to the stator 12.
  • the rotor blades 23 are loaded on one side with the pressurized hydraulic medium, while the limited from the other side of the rotor blades 23 part of the pressure chambers 24 is depressurized.
  • the adjusting shaft 1 is rotated twice by 90 °, so a total of 180 ° maximum about its axis.
  • the roller lever 7 is pivoted so far back that the valve stem 10 is not actuated.
  • the intermediate lever 3 counterclockwise in Fig. 3 pivoted.
  • the roller lever 7 is also pivoted counterclockwise. Since the arm 9 of the roller lever 7 acts on the valve stem 10, depending on the angle of rotation of the adjusting shaft 1, the valve stem 10 is moved more or less far down and thus set the stroke of the valve according to the power requirement.
  • the intake valves when the motor vehicle engine is turned off, can be returned to their original position.
  • the inlet valves in this case go back to a position in which they release the smallest inlet opening.
  • the described fully variable valve control is inexpensive and also simple in construction.
  • Fig. 4 shows that with the adjusting shaft 1 and the rotary drive 12 a plurality of intake valves can be actuated simultaneously. On the adjusting shaft 1 each sit at a distance a plurality of cams 2, in each case via the intermediate drive according to Fig. 3 act on the corresponding valve stems. With the single rotary drive 12, eight cams 2 can be actuated in the exemplary embodiment, which act on corresponding valve stems and, depending on the rotational position of the adjusting shaft 1, control the stroke of the valve.
  • the adjusting shaft 1 sit on the according to the previous embodiment eight cams 2, no longer from one end, but rotatably driven in half the length.
  • the adjusting shaft 1 has in the embodiment in half the length of a circumferential outer toothing 31, in which a rack 32 of the rotary drive 12a engages.
  • the rack 32 is seated on a piston rod 33 which protrudes from a cylinder 34.
  • the piston rod 33 carries within the cylinder 34, a piston 35 which is sealed in the cylinder 34 by means of hydraulic fluid displaced.
  • the adjusting shaft 1 is rotated via the rack 32 in the corresponding direction.
  • the corresponding valve stem is adjusted and thus set the stroke of the intake valve.
  • This embodiment is characterized by its constructive simplicity.
  • the rack and pinion drive ensures an exact stepless rotation of the adjusting shaft 1, so that the stroke of the intake valves can be adjusted according to continuously.
  • a separate rotary drive 12a is provided, which according to the embodiment according to the FIGS. 5 and 6 is trained. Accordingly This fully variable valve control four Verstellwellen 1 with two cams 2.
  • the intake valves can be set independently variable by the respective adjustment shaft 1 is rotated with the rotary drive 12a to the desired extent about its axis.
  • the rotary actuators 12a are supplied independently with hydraulic medium, so that a trouble-free and reliable adjustment of the respective intake valves is ensured.
  • the drive 12b has a coarse adjustment device 36 and fine adjustment means 37.
  • the coarse adjustment device 36, the fine adjustment means 37, for each inlet valve according to the embodiment according to Fig. 7 are provided individually, operated together. With the fine adjustment 37 then the individual adjustment shafts 1 can be finely adjusted to the extent required to individually adjust the stroke of the intake valves.
  • the coarse adjustment device 36 has a drive 38, with which an intermediate shaft 39 can be rotatably driven. It lies parallel to the adjusting shafts 1 lying in alignment with each other and, in the region of a toothed rack 40, has external toothing 41 in which the toothed rack 40 engages. It sits on the end of a piston rod 43 protruding from a cylinder 42, which carries at the other end a piston 44, which is sealed in the cylinder 42. By pressurizing the piston 44 with a hydraulic medium, the piston rod 43 can be extended and retracted so that the intermediate shaft 39 can be rotated via the rack 40 in the desired direction.
  • intermediate shaft 39 supports 45 can be moved, which are formed in the form of a rack and with a corresponding external toothing 46 of the intermediate shaft 39 are engaged.
  • the carrier 45 which are associated with the intake valves, are of identical design and have a pressure chamber 47, in which a piston 48 is displaceable. He sits on the free end of a piston rod 49, which protrudes from the carrier 45 and carries a rack 50. It is in engagement with the external toothing 31 of the associated adjusting shaft 1.
  • the intermediate shaft 39 is first rotated about its axis, whereby the carrier 45 engaged with it are moved depending on the direction of rotation in the direction of the adjusting shafts 1 or away from them. In this way, a coarse adjustment of the stroke of the intake valves of the engine cylinder Z. Subsequently, with the fine adjustment 37, the valve stems 10 of the intake valves are independently adjusted in their exact position, so that the various intake valves run their own optimal stroke. For this purpose, the piston rods 49 of the carrier 45 are extended and retracted, whereby the adjustment shafts 1 are rotated about their axes via the racks 50 in the manner described. About the cam 2 on the adjustment shafts 1, the intermediate lever 3 ( Fig.
  • the embodiment according to the FIGS. 11 and 12 is essentially the same design as the embodiment of the Fig. 8 to 10 , Only the drive 12c has a different configuration than in the previous embodiment.
  • This drive 12c has the same training as the drive 12 according to the Fig. 1 to 3 ,
  • the rotor 16 is provided at one end of the intermediate shaft 39, advantageously integrally formed with it.
  • the drive 12c is otherwise the same design as the rotary drive 12 according to the Fig. 1 to 3 , With the two rotors 16, 17 in the stator 13, the intermediate shaft 39 can be rotated a maximum of 180 ° about its axis.
  • the drive 12d is provided to drive the adjusting shaft 1. He has the cylindrical stator 13 in which a rotor 17 is rotatably mounted. He sits on the axle 18 which is mounted in the cylinder head 19 ( Fig. 13 ). In the pressure chambers 24 of the stator 13, the hydraulic medium is introduced. Thereby, the stator 13 is rotated relative to the rotor 17 in the manner described.
  • the stator 13 carries on its outer casing a toothing 51 which is in engagement with an external toothing 52 of the adjusting shaft 1.
  • the adjusting shaft 1 is rotated to the required extent.
  • the angle of rotation of the stator 13 In contrast to the embodiment of the Fig. 1 to 3 is the angle of rotation of the stator 13 only 90 °.
  • the transmission ratio between the teeth 51 of the stator 13 and the external teeth 52 of the adjusting shaft 1 is selected so that the adjusting shaft rotates at a rotational angle of 90 ° of the stator 13 by 180 °.
  • the transmission of the rotation of the adjusting shaft 1 on the valve stems 10 via the intermediate drive, as he said Fig. 3 has been described.
  • each adjusting shaft 1 is associated with a rotary drive 12e. He is the same as the rotary drive 12d according to the Fig. 13 and 14 .
  • the adjusting shafts 1 can be driven independently of one another to the required extent rotatably.
  • the valve stems of the intake valves of the engine cylinders Z can therefore be moved independently of each other optimally.
  • the 17 to 19 shows a rotary drive 12f, similar to the embodiment of the Fig. 8 to 10 a coarse adjustment means 36f and fine adjustment 37f for the individual adjustment shafts 1 has.
  • the coarse adjustment device 36 f has the stator 13, in which the rotor 17 is housed, which sits on the axis 18. It is stored in the cylinder head 19.
  • the stator 13 has the external teeth 51.
  • the hydraulic medium is introduced so that the stator 13 is rotated relative to the rotor 17.
  • the maximum angle of rotation of the stator 13 is 90 ° in the embodiment.
  • each pivot motor 53 has an outer ring 54 (FIG. Fig. 19 ), which is provided with an external toothing 55, with which the outer ring 54 engages in the external toothing 52 of the intermediate shaft 39. From the inner wall of the outer ring 54 are radially inwardly from wings 56 which abut with their end faces on a cylindrical base body 57 of a rotor 58. He has radially outwardly directed wings 59 which abut with their end faces on the inner wall of the outer ring 54.
  • the rotor 58 can be rotated by a small angle of rotation within the outer ring 54 until its wings 59 come to rest on the side surfaces of one of the adjacent vanes 56 of the outer ring 54.
  • the rotor 58 is rotatably connected to the respective adjusting shaft 1.
  • hydraulic medium is introduced under pressure, so that the relative rotation of the rotor 58 relative to the outer ring 54 can be performed.
  • each cylinder of the engine In the illustrated embodiments, two intake valves are provided for each cylinder of the engine. Depending on the type of engine, additional intake valves per cylinder may be provided. In the simplest case, each cylinder has only one intake valve.
  • valve controls have been described with reference to the embodiments for controlling the lift of intake valves.
  • the valve controls can of course also be used for exhaust valves in the same way to change their stroke accordingly.
  • the adjusting shaft 1 is provided with cams 2 respectively.
  • the adjusting shaft 1 can also be an eccentric shaft, for example, which carries no cams in this case. It is essential for the adjustment that a transverse or radial component is generated during their rotation, which is exploited to move the valve stem 10 via the transmission chain to the desired extent.
  • the transmission chain need not, as exemplified in Fig. 3 is shown formed by mechanical components, but may for example also be a hydraulic transmission chain. It only has to be ensured that the normal stroke of the valve stem 10 generated by the camshaft of the engine can be varied by the adjusting shaft 1.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)

Claims (25)

  1. Commande de soupapes pour le réglage de la course d'élévation de soupapes dans des véhicules automobiles, avec au moins un arbre de réglage à l'aide duquel une tige de soupape de la soupape peut coulisser par l'intermédiaire d'au moins une chaîne de transmission,
    caractérisée en ce que,
    l'arbre de réglage (1) peut être tourné de façon limitée autour de son axe par au moins un entraînement hydraulique (12, 12a à 12f) prenant la forme d'un entraînement en rotation,
    l'entraînement en rotation comportant un stator (13) pouvant tourner par rapport à au moins un rotor (16, 17) logé dans le stator et relié fixement sans rotation à l'arbre de réglage (1),
    et des pales (20) saillant hors de la paroi intérieure du stator (13), entre lesquelles reposent les pales (23) saillant hors d'un corps de base (21, 22) du rotor (16, 17).
  2. Commande de soupapes selon la revendication 1,
    caractérisée en ce que le stator (13) prend une forme cylindrique.
  3. Commande de soupapes selon la revendication 2,
    caractérisée en ce que de façon avantageuse, les pales de rotor (23) et les pales de stator (20) peuvent tourner les unes par rapport aux autres de façon limitée.
  4. Commande de soupapes, notamment selon l'une quelconque des revendications 2 ou 3,
    caractérisée en ce que deux rotors (16, 17) voisins dans le plan axial et séparés l'un de l'autre sont disposés dans le stator (13).
  5. Commande de soupapes selon la revendication 4,
    caractérisée en ce que le stator (13) peut tourner de façon limitée par rapport à l'autre rotor (17) par application de pression grâce à l'entraînement d'un rotor (16) situé du côté de l'arbre de réglage.
  6. Commande de soupapes selon la revendication 4 ou 5,
    caractérisée en ce que le rotor (16) situé du côté de l'arbre de réglage peut tourner de façon limitée par rapport au stator (13) par application de pression.
  7. Commande de soupapes selon la revendication 1,
    caractérisée en ce que l'entraînement hydraulique (12a, 12b) est un entraînement par coulissement.
  8. Commande de soupapes selon la revendication 7,
    caractérisée en ce que l'entraînement par coulissement (12a, 12b) comporte au moins une tige dentée (32) pouvant être coulissée perpendiculairement à l'arbre de réglage (1) et s'engrenant dans un engrènement extérieur (31) de l'arbre de réglage (1).
  9. Commande de soupapes selon la revendication 8,
    caractérisée en ce que la tige dentée (32) repose sur une tige de piston (33) comportant un piston (35) pouvant être déplacé dans un cylindre (34).
  10. Commande de soupapes selon l'une quelconque des revendications 1 à 9,
    caractérisée en ce que l'arbre de réglage (1) comporte au moins une came (2) pour plusieurs soupapes.
  11. Commande de soupapes selon l'une quelconque des revendications 1 à 9,
    caractérisée en ce que l'arbre de réglage (1) comporte plusieurs cames (2) pour plusieurs soupapes.
  12. Commande de soupapes selon l'une quelconque des revendications 1 à 9,
    caractérisée en ce qu'un arbre de réglage (1) pouvant tourner de façon limitée à l'aide d'un entraînement hydraulique (12a, 12c) propre est respectivement prévu pour chaque cylindre du véhiculé automobile.
  13. Commande de soupapes selon la revendication 12,
    caractérisée en ce que chaque arbre de réglage (1) présente deux cames (2) pour deux soupapes.
  14. Commande de soupapes, notamment selon l'une quelconque des revendications 1 à 13,
    caractérisée en ce que l'entraînement hydraulique (12b, 12c, 12d, 12f) comporte un dispositif de réglage approximatif (36, 36f) et au moins un dispositif de réglage de précision (37, 37f).
  15. Commande de soupapes selon la revendication 14,
    caractérisée en ce que le dispositif de réglage approximatif (36, 36f) comporte un arbre intermédiaire (39) par l'intermédiaire duquel l'arbre de réglage (1) peut tourner de façon limitée.
  16. Commande de soupapes selon la revendication 14 ou 15,
    caractérisée en ce que le dispositif de réglage approximatif (36) comporte un entraînement par coulissement (40 à 44).
  17. Commande de soupapes selon la revendication 16,
    caractérisée en ce que l'entraînement par coulissement (40 à 44) comporte une tige dentée (40) qui s'étend perpendiculairement à l'arbre intermédiaire (39) et s'engrène dans un engrènement (41) de l'arbre intermédiaire (39) et repose sur une tige de piston (43) supportant un piston (44) pouvant coulisser dans un cylindre (42).
  18. Commande de soupapes selon la revendication 17,
    caractérisée en ce qu'au moins un support (45) comportant un entraînement par coulissement (45, 47 à 50) du dispositif de réglage de précision (37) s'engrène dans l'engrènement (41) de l'arbre intermédiaire (39).
  19. Commande de soupapes selon la revendication 18,
    caractérisée en ce que l'entraînement par coulissement (45, 47 à 50) comporte une tige dentée (50) s'engrenant dans l'engrènement extérieur (31) de l'arbre de réglage (1) et reposant sur une tige de piston (49) supportant un piston (48) pouvant coulisser dans une chambre de compression (47) du support (45).
  20. Commande de soupapes selon l'une quelconque des revendications 14 à 19,
    caractérisée en ce qu'en cas de multiples arbres de réglage (1), l'arbre intermédiaire (39) est prévu pour le réglage approximatif commun des arbres de réglage (1).
  21. Commande de soupapes selon l'une quelconque des revendications 14 à 20,
    caractérisée en ce qu'en cas de multiples arbres de réglage (1), chaque arbre de réglage (1) est associé à un dispositif de réglage de précision (37).
  22. Commande de soupapes selon la revendication 15,
    caractérisée en ce que le dispositif de réglage approximatif (36f) comporte un entraînement en rotation (13, 17).
  23. Commande de soupapes selon la revendication 22,
    caractérisée en ce que l'entraînement en rotation (13, 17) comporte un stator (13) s'engrenant avec un engrènement extérieur (51) dans un engrènement (52) de l'arbre intermédiaire (39) et un rotor (17), les deux éléments pouvant tourner l'un par rapport à l'autre.
  24. Commande de soupapes selon la revendication 23,
    caractérisée en ce qu'un engrènement extérieur (55) d'une bague extérieure (54) du dispositif de réglage de précision (37f) s'engrène avec l'engrènement extérieur (50) de l'arbre intermédiaire (39).
  25. Commande de soupapes selon la revendication 24,
    caractérisée en ce qu'un rotor (58) est disposé dans la bague extérieure (54) du dispositif de réglage de précision (37f), ledit rotor étant relié fixement sans rotation à l'arbre de réglage (1), pouvant tourner de façon limitée par rapport à la bague extérieure (54) et présentant des pales (56) saillant vers l'intérieur entre lesquelles reposent les pales (59) orientées vers l'extérieur du rotor (58).
EP03005576A 2002-03-20 2003-03-12 Contrôleur de levée de soupapes d'un moteur à combustion interne Expired - Lifetime EP1347154B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP07107909A EP1832723B1 (fr) 2002-03-20 2003-03-12 Commande de soupape pour régler la levée des soupapes dans un moteur à combustion interne

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10213081 2002-03-20
DE10213081A DE10213081A1 (de) 2002-03-20 2002-03-20 Ventilsteuerung zur Einstellung des Hubes von Ventilen in Kraftfahrzeugen

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP07107909A Division EP1832723B1 (fr) 2002-03-20 2003-03-12 Commande de soupape pour régler la levée des soupapes dans un moteur à combustion interne

Publications (3)

Publication Number Publication Date
EP1347154A2 EP1347154A2 (fr) 2003-09-24
EP1347154A3 EP1347154A3 (fr) 2003-12-17
EP1347154B1 true EP1347154B1 (fr) 2008-08-27

Family

ID=27771515

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Application Number Title Priority Date Filing Date
EP03005576A Expired - Lifetime EP1347154B1 (fr) 2002-03-20 2003-03-12 Contrôleur de levée de soupapes d'un moteur à combustion interne
EP07107909A Expired - Lifetime EP1832723B1 (fr) 2002-03-20 2003-03-12 Commande de soupape pour régler la levée des soupapes dans un moteur à combustion interne

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP07107909A Expired - Lifetime EP1832723B1 (fr) 2002-03-20 2003-03-12 Commande de soupape pour régler la levée des soupapes dans un moteur à combustion interne

Country Status (5)

Country Link
US (1) US6814036B2 (fr)
EP (2) EP1347154B1 (fr)
AT (2) ATE406504T1 (fr)
DE (3) DE10213081A1 (fr)
ES (1) ES2312676T3 (fr)

Cited By (4)

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US8453616B2 (en) 2009-10-27 2013-06-04 Hilite Germany Gmbh Vane-type motor cam phaser with a friction disc and mounting method
US8505582B2 (en) 2010-05-03 2013-08-13 Hilite Germany Gmbh Hydraulic valve
US8662040B2 (en) 2010-04-10 2014-03-04 Hilite Germany Gmbh Oscillating-motor camshaft adjuster having a hydraulic valve
US8752514B2 (en) 2010-12-20 2014-06-17 Hilite Germany Gmbh Hydraulic valve for an oscillating motor adjuster

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DE102004020623A1 (de) * 2004-04-27 2005-12-01 Ina-Schaeffler Kg Variable mechanische Ventiltriebsteuerung mit Verstelleinrichtung
DE102004058997A1 (de) * 2004-12-08 2006-07-27 Daimlerchrysler Ag Brennkraftmaschine
DE102006012775B4 (de) * 2006-03-17 2008-01-31 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102006012733B4 (de) * 2006-03-17 2008-03-27 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
EP1996819B1 (fr) 2006-03-17 2012-04-11 Hilite Germany GmbH Circuit hydraulique, destine en particulier a des dispositifs de reglage d'arbre a cames, et element de commande correspondant
DE502007002866D1 (de) 2006-03-17 2010-04-01 Hydraulik Ring Gmbh Hydraulikkreis, insbesondere für nockenwellenversteller, und entsprechendes steuerelement
ITMI20062288A1 (it) 2006-11-28 2008-05-29 Iveco Spa Motore a combustione interna dotato di sistema per la variazione dell'apertura delle valvole e veicolo dotato di tale motore
DE102008033230B4 (de) 2008-01-04 2010-05-27 Hydraulik-Ring Gmbh Doppelter Nockenwellenversteller in Schichtaufbau
US7841311B2 (en) 2008-01-04 2010-11-30 Hilite International Inc. Variable valve timing device
DE102008023098A1 (de) 2008-05-09 2009-12-17 Hydraulik-Ring Gmbh Doppelter Nockenwellenversteller in Schichtaufbau
DE102009022869A1 (de) * 2009-05-27 2010-12-09 Hydraulik-Ring Gmbh Flügelzellennockenwellenverstellersystem
DE102009052841A1 (de) * 2009-11-13 2011-05-19 Hydraulik-Ring Gmbh Nockenwelleneinsatz
EP2386729A1 (fr) * 2010-05-10 2011-11-16 Fiat Powertrain Technologies S.p.A. Moteur à combustion interne multicylindres ayant un actionnement variable des soupapes du moteur
DE102010033296A1 (de) 2010-08-04 2012-02-09 Hydraulik-Ring Gmbh Nockenwellenversteller, insbesondere mit Nockenwelle
DE102011009416B4 (de) * 2011-01-25 2016-11-03 Kolbenschmidt Pierburg Innovations Gmbh Mechanisch steuerbare Ventiltriebanordnung
DE102011006689A1 (de) 2011-04-04 2012-10-04 Schaeffler Technologies Gmbh & Co. Kg Nockenwellenversteller
DE102014114396A1 (de) * 2014-10-02 2016-04-07 Pierburg Gmbh Mechanisch steuerbarer Ventiltrieb sowie mechanisch steuerbare Ventiltriebanordnung
DE102020113219A1 (de) 2020-05-15 2021-11-18 Schaeffler Technologies AG & Co. KG Kipphebelanordnung für einen Ventiltrieb einer Brennkraftmaschine

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EP0405927A1 (fr) * 1989-06-30 1991-01-02 Suzuki Kabushiki Kaisha Mécanisme d'entraînement de soupapes pour moteur à quatre temps
US5025761A (en) * 1990-06-13 1991-06-25 Chen Kuang Tong Variable valve-timing device
EP0452671A2 (fr) * 1990-03-14 1991-10-23 Suzuki Kabushiki Kaisha Dispositif de commande de soupape pour moteur à quatre temps
US5189998A (en) * 1991-07-23 1993-03-02 Atsugi Unisia Corporation Valve mechanism of internal combustion engine
EP0780547A1 (fr) * 1995-12-22 1997-06-25 Siemens Aktiengesellschaft Dispositif permettant de varier la loi de leveé d'une soupape de moteur à combustion interne

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FI108076B (fi) * 1999-08-17 2001-11-15 Esko Raikamo Voimaelin venttiilien tms. asettamiseksi haluttuun asentoon
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AUPR531501A0 (en) * 2001-05-30 2001-06-21 Bishop Innovation Limited Variable valve timing mechanism for a rotary valve

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EP0405927A1 (fr) * 1989-06-30 1991-01-02 Suzuki Kabushiki Kaisha Mécanisme d'entraînement de soupapes pour moteur à quatre temps
EP0452671A2 (fr) * 1990-03-14 1991-10-23 Suzuki Kabushiki Kaisha Dispositif de commande de soupape pour moteur à quatre temps
US5025761A (en) * 1990-06-13 1991-06-25 Chen Kuang Tong Variable valve-timing device
US5189998A (en) * 1991-07-23 1993-03-02 Atsugi Unisia Corporation Valve mechanism of internal combustion engine
EP0780547A1 (fr) * 1995-12-22 1997-06-25 Siemens Aktiengesellschaft Dispositif permettant de varier la loi de leveé d'une soupape de moteur à combustion interne

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8453616B2 (en) 2009-10-27 2013-06-04 Hilite Germany Gmbh Vane-type motor cam phaser with a friction disc and mounting method
US8794201B2 (en) 2009-10-27 2014-08-05 Hilite Germany Gmbh Vane-type motor cam phaser with a friction disc and method for mounting a friction disc on a rotor
US8662040B2 (en) 2010-04-10 2014-03-04 Hilite Germany Gmbh Oscillating-motor camshaft adjuster having a hydraulic valve
US8505582B2 (en) 2010-05-03 2013-08-13 Hilite Germany Gmbh Hydraulic valve
US8752514B2 (en) 2010-12-20 2014-06-17 Hilite Germany Gmbh Hydraulic valve for an oscillating motor adjuster

Also Published As

Publication number Publication date
EP1347154A2 (fr) 2003-09-24
US6814036B2 (en) 2004-11-09
DE50310394D1 (de) 2008-10-09
ATE406504T1 (de) 2008-09-15
EP1832723A2 (fr) 2007-09-12
DE50312490D1 (de) 2010-04-15
ATE459789T1 (de) 2010-03-15
EP1832723A3 (fr) 2007-09-26
EP1832723B1 (fr) 2010-03-03
DE10213081A1 (de) 2003-10-02
EP1347154A3 (fr) 2003-12-17
ES2312676T3 (es) 2009-03-01
US20030177991A1 (en) 2003-09-25

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