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EP1832723B1 - Valve actuation for adjusting the stroke of valves in an internal combustion engine - Google Patents

Valve actuation for adjusting the stroke of valves in an internal combustion engine Download PDF

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Publication number
EP1832723B1
EP1832723B1 EP07107909A EP07107909A EP1832723B1 EP 1832723 B1 EP1832723 B1 EP 1832723B1 EP 07107909 A EP07107909 A EP 07107909A EP 07107909 A EP07107909 A EP 07107909A EP 1832723 B1 EP1832723 B1 EP 1832723B1
Authority
EP
European Patent Office
Prior art keywords
rotary drive
hydraulic rotary
stator
rotor
adjusting
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
EP07107909A
Other languages
German (de)
French (fr)
Other versions
EP1832723A2 (en
EP1832723A3 (en
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
Publication of EP1832723A2 publication Critical patent/EP1832723A2/en
Publication of EP1832723A3 publication Critical patent/EP1832723A3/en
Application granted granted Critical
Publication of EP1832723B1 publication Critical patent/EP1832723B1/en
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 adjusting 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 control the valve lift in a performance-dependent manner, so that only that amount of fuel is injected into the combustion chamber of the cylinder, which is required for the instantaneous power requirement.
  • an electric motor is provided, whose pinion cooperates with a setting wheel which sits on an adjusting shaft. By means of this adjusting the transmission geometry between the camshaft and the valve is changed, so that different valve strokes can be adjusted.
  • this valve control is extremely complicated and therefore expensive to manufacture.
  • the invention has the object of providing the generic valve 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 preferably operates fully variable, so that within the adjustment range any desired valve lift can be adjusted.
  • 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 inlet 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 cam 62 of the camshaft 61 of 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 is to 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 1 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 clockwise 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 is located on the front side on a wall of the cylinder head 19 at.
  • 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 rest on 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 are acted upon on one side with the hydraulic medium pressure, while the limited from the other side of the rotor blade 23 part of the respective pressure chamber 24 is depressurized.
  • the hydraulic medium is kept under pressure in such a way 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 switched off, can be returned to their initial 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 adjustment 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 stem. With the single rotary drive 12, eight cams 2 can be actuated in the exemplary embodiment, which act on corresponding valve shafts 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 a length 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, thus adjusting the stroke of the inlet 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, each 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 inlet 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, which for each inlet valve according to the embodiment of Fig. 7 are provided individually, operated together. With the fine adjustment 37 then the individual adjustment shafts 1 can be adjusted to the required extent fine 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 acting on 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 carriers 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 into engagement are.
  • the carriers 45 which are assigned to 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.
  • the valve stems 10 of the intake valves can be adjusted independently of each other in their exact position with the fine adjustment 37, so that the various intake valves run their own optimal stroke.
  • 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.
  • the intermediate lever 3 ( Fig. 3 ) pivoted in the manner described, whereby the roller lever 7 are pivoted accordingly.
  • the valve stems 10 of the intake valves are shifted to their required position.
  • the fine adjustment means 37 the intake valves can be adjusted so that knocking of the engine does not occur.
  • 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 12 c has the same construction 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 is 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 °.
  • 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 into the pressure chambers 24 of the stator 13 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 outer toothing 55, with which the outer ring 54 in the external teeth 52 of the intermediate shaft 39 engages. 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 has only one inlet 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 during their rotation a transverse or radial component is generated, which is exploited to move the valve stem 10 in the desired mass via the transmission chain.
  • the transmission chain does not have to be 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)

Abstract

The drive (12) has two rotors (16, 17) that are attached into a cylindrical stator (13). The rotors (16) are connected to an adjustable shaft (1) in a torque proof manner, and the rotor (17) sits on an axle (18), which lies in alignment with respect to the adjustable shaft that is to be connected. Torque proof cams are provided on the adjustable shaft, and blades are provided on an inner wall of the stator. The axis of the rotors and the stator coincide with each other.

Description

Die Erfindung betrifft eine Ventilsteuerung zur Einstellung des Hubes von Ventilen in Kraftfahrzeugen nach dem Oberbegriff des Anspruches 1.The invention relates to a valve control for adjusting the stroke of valves in motor vehicles according to the preamble of claim 1.

Es sind Ventilsteuerungen bekannt, die bei Ottomotoren eingesetzt werden und die Ventilhübe stufenlos variieren, um den Kraftstoffverbrauch zu senken. Die Ventilsteuerungen steuern den Ventilhub leistungsabhängig, so dass stets nur diejenige Menge an Kraftstoff in den Brennraum des Zylinders eingespritzt wird, die für den augenblicklichen Leistungsbedarf erforderlich ist. Bei einer bekannten Ventilsteuerung ist ein Elektromotor vorgesehen, dessen Ritzel mit einem Stellrad zusammenwirkt, das auf einer Verstellwelle sitzt. Mittels dieser Verstellwelle wird die Übertragungsgeometrie zwischen der Nockenwelle und dem Ventil verändert, so dass unterschiedliche Ventilhübe eingestellt werden können. Diese Ventilsteuerung ist allerdings äußerst aufwendig ausgebildet und dementsprechend teuer in der Herstellung.There are known valve controls that are used in gasoline engines and the valve strokes vary continuously to reduce fuel consumption. The valve controls control the valve lift in a performance-dependent manner, so that only that amount of fuel is injected into the combustion chamber of the cylinder, which is required for the instantaneous power requirement. In a known valve control, an electric motor is provided, whose pinion cooperates with a setting wheel which sits on an adjusting shaft. By means of this adjusting the transmission geometry between the camshaft and the valve is changed, so that different valve strokes can be adjusted. However, this valve control is extremely complicated and therefore expensive to manufacture.

Der Erfindung liegt die Aufgabe zugrunde, die gattungsgemäße Ventilsteuerung so auszubilden, dass der Ventilhub in kostengünstiger Weise einfach verändert werden kann.The invention has the object of providing the generic valve control in such a way that the valve lift can be easily changed in a cost effective manner.

Diese Aufgabe wird bei der gattungsgemäßen Ventilsteuerung erfindungsgemäß mit den kennzeichnenden Merkmalen des Anspruches 1 gelöst.This object is achieved according to the invention in the generic valve control with the characterizing features of claim 1.

Bei der erfindungsgemäßen Ventilsteuerung wird die Verstellwelle durch den Hydraulikantrieb so gedreht, dass der Ventilhub in Abhängigkeit von der augenblicklich geforderten Leistung des Motors verstellt wird. Die erfindungsgemäße Ventilsteuerung arbeitet vorzugsweise voll variabel, so dass innerhalb des Verstellbereiches jeder gewünschte Ventilhub eingestellt werden kann. Der Hydraulikantrieb lässt sich einfach und kostengünstig realisieren und ist problemlos im Einsatz.In the valve control according to the invention, 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 preferably operates fully variable, so that within the adjustment range any desired valve lift can be adjusted. The hydraulic drive can be implemented easily and inexpensively and is easy to use.

Weitere Merkmale der Erfindung ergeben sich aus den weiteren Ansprüchen, der Beschreibung und den Zeichnungen.Further features of the invention will become apparent from the other claims, the description and the drawings.

Die Erfindung wird anhand einiger in den Zeichnungen dargestellter Ausführungsformen näher erläutert. Es zeigen

  • Fig. 1 teilweise in Ansicht und teilweise im Schnitt eine erste Ausführungsform einer erfindungsgemäßen Ventilsteuerung,
  • Fig. 2 einen Axialschnitt durch einen Antrieb der Ventilsteuerung gemäß Fig. 1,
  • Fig. 3 in Seitenansicht eine Verstellwelle der Ventilsteuerung gemäß Fig. 1, die über einen Zwischenhebel auf einen Schlepphebel einwirkt,
  • Fig. 4 in einer Darstellung entsprechend Fig. 1 eine zweite Ausführungsform einer erfindungsgemäßen Ventilsteuerung,
  • Fig. 5 in einer Darstellung entsprechend Fig. 1 eine dritte Ausführungsform einer erfindungsgemäßen Ventilsteuerung,
  • Fig. 6 eine Seitenansicht der Ventilsteuerung gemäß Fig. 5,
  • Fig. 7 in einer Darstellung entsprechend Fig. 1 eine vierte Ausführungsform einer erfindungsgemäßen Ventilsteuerung,
  • Fig. 8 in einer Darstellung entsprechend Fig. 1 eine fünfte Ausführungsform einer erfindungsgemäßen Ventilsteuerung,
  • Fig. 9 in Seitenansicht eine Feineinstelleinrichtung der Ventilsteuerung gemäß Fig. 8,
  • Fig. 10 eine Grobeinstelleinrichtung der Ventilsteuerung gemäß Fig. 8 in Seitenansicht,
  • Fig. 11 in einer Darstellung entsprechend Fig. 1 eine sechste Ausführungsform einer erfindungsgemäßen Ventilsteuerung,
  • Fig. 12 eine Seitenansicht der Ventilsteuerung gemäß Fig. 11,
  • Fig. 13 in einer Darstellung entsprechend Fig. 1 eine siebte Ausführungsform einer erfindungsgemäßen Ventilsteuerung,
  • Fig. 14 eine Seitenansicht der Ventilsteuerung gemäß Fig. 13,
  • Fig. 15 in einer Darstellung entsprechend Fig. 1 eine achte Ausführungsform einer erfindungsgemäßen Ventilsteuerung,
  • Fig. 16 eine Seitenansicht der Ventilsteuerung gemäß Fig. 15,
  • Fig. 17 in einer Darstellung entsprechend Fig. 1 eine neunte Ausführungsform einer erfindungsgemäßen Ventilsteuerung,
  • Fig. 18 in vergrößerter Darstellung eine Feineinstelleinrichtung der Ventilsteuerung gemäß Fig. 17,
  • Fig. 19 im Axialschnitt eine Grobeinstelleinrichtung der Ventilsteuerung gemäß Fig. 17.
The invention will be explained in more detail with reference to some embodiments shown in the drawings. Show it
  • Fig. 1 partly in view and partly in section a first embodiment of a valve control according to the invention,
  • Fig. 2 an axial section through a drive of the valve control according to Fig. 1 .
  • Fig. 3 in side view, an adjustment of the valve control according to Fig. 1 , which acts on a drag lever via an intermediate lever,
  • Fig. 4 in a representation accordingly Fig. 1 a second embodiment of a valve control according to the invention,
  • Fig. 5 in a representation accordingly Fig. 1 a third embodiment of a valve control according to the invention,
  • Fig. 6 a side view of the valve control according to Fig. 5 .
  • Fig. 7 in a representation accordingly Fig. 1 A fourth embodiment of a valve control according to the invention,
  • Fig. 8 in a representation accordingly Fig. 1 A fifth embodiment of a valve control according to the invention,
  • Fig. 9 in side view a fine adjustment of the valve control according to Fig. 8 .
  • Fig. 10 a coarse adjustment device of the valve control according to Fig. 8 in side view,
  • Fig. 11 in a representation accordingly Fig. 1 A sixth embodiment of a valve control according to the invention,
  • Fig. 12 a side view of the valve control according to Fig. 11 .
  • Fig. 13 in a representation accordingly Fig. 1 A seventh embodiment of a valve control according to the invention,
  • Fig. 14 a side view of the valve control according to Fig. 13 .
  • Fig. 15 in a representation accordingly Fig. 1 an eighth embodiment of a valve control according to the invention,
  • Fig. 16 a side view of the valve control according to Fig. 15 .
  • Fig. 17 in a representation accordingly Fig. 1 A ninth embodiment of a valve control according to the invention,
  • Fig. 18 in an enlarged view a fine adjustment of the valve control according to Fig. 17 .
  • Fig. 19 in axial section a coarse adjustment of the valve control according to Fig. 17 ,

Die im Folgenden beschriebenen Ventilsteuerungen ermöglichen eine voll variable Steuerung des Hubes von Ventilen von Einspritzmotoren. Je nach Leistungsbedarf werden die Einlassventile mehr oder weniger weit geöffnet, so dass immer nur diejenige Luftmenge in den Brennraum des Motors angesaugt wird, die für den augenblicklichen Leistungsbedarf erforderlich ist. Die entsprechende Kraftstoffmenge wird in bekannter Weise der Luftmenge zugeführt.The valve controls described below allow fully variable control of the stroke of injection valve valves. Depending on the power requirement, the inlet 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.

Die Ventilsteuerung gemäß den Fig. 1 bis 3 hat eine Verstellwelle 1, auf der drehfest Nocken 2 vorgesehen sind. Sie wirken auf einen zweiarmigen Zwischenhebel 3, dessen einer Arm 5 mittels einer Rolle 4 an der zugehörigen Nocke 2 und mit seinem anderen Arm 6 an einer Rolle 8 eines Rollenhebels 7 anliegt. Der Zwischenhebel 3 trägt außerdem eine weitere Rolle 60, die an der Verstellwelle 1 anliegt. In Fig. 3 ist außerdem die Nockenwelle 61 zu erkennen, deren Nocken 62 an einer Rolle 63 des Zwischenhebels 3 anliegt. Durch den Nocken 62 der Nockenwelle 61 wird der Zwischenhebel 3 in bekannter Weise hin- und hergeschwenkt, wobei über den Arm 6 der Rollenhebel 7 verschwenkt und dadurch ein Ventilschaft 10 gegen die Kraft wenigstens einer Druckfeder 11 verschoben wird. Das untere (nicht dargestellte) Ende des Ventilschaftes 10 trägt das Ventil, mit dem die Einlassöffnung in den Brennraum des Motorzylinders geschlossen wird. Der Ventilschaft 10 wird durch den Rollenhebel 7 gegen die Kraft wenigstens einer Druckfeder 11 verschoben, wenn das Ventil geöffnet werden soll. Die Druckfeder 11 sorgt dafür, dass das Ventil bei entsprechender Lage des Rollenhebels 7 in seine Schließstellung zurückgeschoben wird. Mit der Ventilsteuerung ist es möglich, den Hub des Ventilschaftes 10 zu variieren. Da der Zwischenhebel 3 mit der Rolle 4 am Nocken 2 der Verstellwelle 1 anliegt, kann durch Drehen der Verstellwelle 1 um ihre Achse der Zwischenhebel 3 mehr oder weniger weit geschwenkt werden. Wird beispielsweise in der Darstellung gemäß Fig. 3 die Verstellwelle 1 entgegen dem Uhrzeigersinn gedreht, dann wird infolge der Anlage der Rolle 4 am Nocken 2 der Zwischenhebel 3 ebenfalls entgegen dem Uhrzeigersinn verschwenkt. Dies hat zur Folge, dass der andere Arm 6 des Zwischenhebels 3 den Rollenhebel 7 entsprechend verstellt, so dass der Ventilschaft 10 und damit das entsprechende Ventil einen größeren Hub ausführt. Wird andererseits die Verstellwelle 1 im Uhrzeigersinn aus der Stellung gemäß Fig. 3 gedreht, dann schwenkt der Zwischenhebel 3 infolge seiner Anlage am Nocken 2 im Uhrzeigersinn. Dementsprechend wird auch der Arm 6 des Rollenhebels 3 im Uhrzeigersinn verstellt. Dies führt dazu, dass der Ventilschaft 10 einen entsprechend kleineren Hub ausführt.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. In Fig. 3 In addition, the camshaft 61 can be seen, the cam 62 rests against a roller 63 of the intermediate lever 3. By the cam 62 of the camshaft 61 of 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 is to 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. With the valve control, it is possible to vary the stroke of the valve stem 10. Since the intermediate lever 3 rests with the roller 4 on the cam 2 of the adjusting shaft 1, the intermediate lever 3 can be pivoted more or less far by rotating the adjusting shaft 1 about its axis. For example, in the illustration according to Fig. 3 the adjusting shaft 1 is rotated counterclockwise, then the intermediate lever 3 is also pivoted counterclockwise due to the system of the roller 4 on the cam 2. This has the consequence that the other arm 6 of the intermediate lever 3, the roller lever 7 adjusted accordingly, so that the valve stem 10 and thus the corresponding valve performs a larger stroke. On the other hand, the adjusting shaft 1 in the clockwise direction from the position according to Fig. 3 rotated, then pivots the intermediate lever 3 due to its investment on the cam 2 in a clockwise direction. Accordingly, the arm 6 of the roller lever 3 is adjusted clockwise. This results in that the valve stem 10 performs a correspondingly smaller stroke.

Die Verstellwelle 1 ist mit einem Drehantrieb 12 gekoppelt, mit dem die Verstellwelle 1 begrenzt drehbar ist. Er hat einen zylindrischen Stator 13 (Fig. 2), dessen beide Stirnseiten durch Deckscheiben 14, 15 geschlossen sind. Im Stator 13 sind zwei Rotoren 16 und 17 untergebracht, von denen der Rotor 16 drehfest mit der Verstellwelle 1 verbunden ist. Der andere Rotor 17 sitzt auf einer Achse 18, die fluchtend zur Verstellwelle 1 liegt und im Zylinderkopf 19 gelagert ist.The adjusting shaft 1 is coupled to a rotary drive 12 with which the adjusting shaft 1 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.

An der Innenwand des Stators 13 stehen radial nach innen Flügel 20 (Fig. 2) ab, die in Winkelabständen von 120° zueinander liegen. Die Rotoren 16, 17 haben einen zylindrischen Grundkörper 21, 22, dessen Achse mit der Achse des Stators 13 zusammenfällt und von dem radial nach außen Flügel 23 abstehen. Diese Flügel 23 haben ebenfalls einen Winkelabstand von 120° zueinander. Die Rotoren 16, 17 liegen mit den Stirnseiten der Flügel 23 an der Innenwand des Stators 13 an. Die Flügel 20 des Stators 13 ihrerseits liegen an der Außenwand des zylindrischen Grundkörpers 21, 22 an.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.

Wie Fig. 2 zeigt, liegt jeweils ein Flügel 23 der Rotoren 16, 17 zwischen zwei Flügeln 20 des Stators 13. Die Flügel 23 der Rotoren 16, 17 werden in bekannter Weise mit Hydraulikmedium beaufschlagt, das durch (nicht dargestellte) Bohrungen in die Räume 24 des Stators 13 gelangt. Die Flügel 23 der Rotoren 16, 17 können auf beiden Seiten mit Druckmedium beaufschlagt werden, so dass die Rotoren 16, 17 im und entgegen dem Uhrzeigersinn gegenüber dem Stator 13 gedreht werden können.As 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 clockwise and counterclockwise direction relative to the stator 13 can be rotated.

Die beiden Rotoren 16, 17 sind achsgleich zueinander angeordnet, haben untereinander jedoch keine Verbindung. Der Stator 13 hat für beide Rotoren 16, 17 die entsprechenden Druckräume 24. Wie Fig. 1 zeigt, steht von der Innenwand des Stators 13 in halber Länge eine Ringwand 25 ab, die eine zentrale Durchgangsöffnung 26 aufweist. In sie ragen von beiden Seiten verjüngte Abschnitte der Grundkörper 21, 22 der Rotoren 16, 17. Die Ringwand 25 liegt mit dem Rand der Durchgangsöffnung 26 dichtend an den verjüngten Endabschnitten der Grundkörper 21, 22 der Rotoren 16, 17 an. Außerdem liegen die Grundkörper 21, 22, wie Fig. 1 zeigt, an den einander zugewandten Innenseiten der Ringwand 25 und der Deckscheiben 14, 15 dichtend an. Im dargestellten Ausführungsbeispiel ist der Rotor 16 einstückig mit der Verstellwelle 1 ausgebildet. Er kann aber auch als gesondertes Bauelement an die Verstellwelle 1 angeschlossen werden. Die Verstellwelle 1 ragt abgedichtet durch die Deckscheibe 14.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. In addition, 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. In the illustrated embodiment, 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.

Der Rotor 17 ragt mit einem verjüngten Endabschnitt 27 abgedichtet durch die Deckscheibe 15 und liegt stirnseitig an einer Wand des Zylinderkopfes 19 an. Der Rotor 17 hat eine zentrale Durchgangsöffnung, in welche die Achse 18 eingesetzt ist.The rotor 17 projects with a tapered end portion 27 sealed by the cover plate 15 and is located on the front side on a wall of the cylinder head 19 at. The rotor 17 has a central passage opening into which the axle 18 is inserted.

Die beiden Rotoren 16, 17 werden unabhängig voneinander gedreht, da sie mit ihren Flügeln 23 in den voneinander getrennten Räumen 24 des Stators 13 untergebracht sind. Die Deckscheiben 14, 15 sind mit Schrauben 28, 29 lösbar an der Ringwand 25 befestigt.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.

Die Rotoren 16, 17 können so weit um ihre Achsen gedreht werden, bis ihre Flügel 23 an den Flügeln 20 des Stators 13 zur Anlage kommen. Wie Fig. 2 beispielhaft zeigt, beträgt der maximale Verstellwinkel 30 der Rotoren 16, 17 90°.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. As Fig. 2 by way of example, the maximum displacement angle 30 of the rotors 16, 17 is 90 °.

Da die beiden Rotoren 16, 17 im Ausführungsbeispiel jeweils um 90° drehbar und miteinander gekoppelt sind, kann die Verstellwelle 1 maximal um 180° gedreht werden. Die Druckräume 24 für die beiden Rotoren 16, 17 werden jeweils mit Hydraulikmedium beaufschlagt. Der wellenseitige Rotor 16 liegt in der Ausgangsstellung mit seinen Flügeln 23 an den Flügeln 20 des Stators 13 an. Die Flügel 23 des anderen Rotors 17 liegen ebenfalls an den Statorflügeln 20 an. Beide Rotoren 16, 17 sind jedoch so gegeneinander verdreht, dass ihre Flügel an unterschiedlichen Statorflügeln 20 anliegen, in Achsrichtung des Drehantriebes 12 gesehen. Die Druckräume 24 für den Stator 16 werden zunächst mit dem Hydraulikmedium unter Druck gehalten, so dass die Rotorflügel 23 an den Statorflügeln 20 unter dem Druck des Hydraulikmediums anliegen. In die Druckräume 24 für den anderen Rotor 17 wird das Hydraulikmedium unter Druck so eingeführt, dass der Stator 12 relativ zum Rotor 17 gedreht wird. Der andere Rotor 16 liegt so mit seinen Flügeln 23 an den Statorflügeln 20 an, dass der Stator 12 diesen Rotor 16 bei der Relativdrehung mitnimmt. Dadurch wird die Verstellwelle 1 um ihre Achse gedreht. Damit die Relativdrehung zwischen dem Stator 5 und dem Rotor 17 stattfinden kann, werden die Flügel 23 des Rotors 17 auf der einen Seite mit dem Hydraulikmediumsdruck beaufschlagt, während der von der anderen Seite der Rotorflügel 23 begrenzte Teil des jeweiligen Druckraumes 24 druckentlastet ist. Sobald die Flügel 23 des Rotors 17 an den Statorflügeln 20 anliegen, wird das Hydraulikmedium so unter Druck gehalten, dass diese Anschlagstellung aufrechterhalten wird. Gleichzeitig wird die Hydrauliksteuerung für den Rotor 16 so umgeschaltet, dass nunmehr der Rotor 16 gegenüber dem Stator 12 drehen kann. Hierzu werden die Rotorflügel 23 auf der einen Seite mit dem unter Druck stehenden Hydraulikmedium belastet, während der von der anderen Seite der Rotorflügel 23 begrenzte Teil der Druckräume 24 druckentlastet wird. Somit wird die Verstellwelle 1 zweimal um 90°, also insgesamt um 180° maximal um ihre Achse gedreht.Since the two rotors 16, 17 are rotatable in the exemplary embodiment in each case by 90 ° and with each other, 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. However, both rotors 16, 17 are rotated against each other so that their wings rest on 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. In the pressure chambers 24 for the other rotor 17, the hydraulic medium is introduced under pressure so that the stator 12 is rotated relative to the rotor 17. Of 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. As a result, the adjusting shaft 1 is rotated about its axis. Thus, the relative rotation between the stator 5 and the rotor 17 can take place, the wings 23 of the rotor 17 are acted upon on one side with the hydraulic medium pressure, while the limited from the other side of the rotor blade 23 part of the respective pressure chamber 24 is depressurized. As soon as the vanes 23 of the rotor 17 bear against the stator vanes 20, the hydraulic medium is kept under pressure in such a way that this stop position is maintained. At the same time, the hydraulic control for the rotor 16 is switched so that now the rotor 16 can rotate relative to the stator 12. For this purpose, 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. Thus, the adjusting shaft 1 is rotated twice by 90 °, so a total of 180 ° maximum about its axis.

Wenn die Verstellwelle 1 so gedreht ist, dass der Arm 5 des Zwischenhebels 3 im Bereich neben den Nocken 2 an der Mantelfläche der Verstellwelle 1 anliegt, dann ist der Rollenhebel 7 so weit zurückgeschwenkt, dass der Ventilschaft 10 nicht betätigt wird. Sobald die Verstellwelle 1 gedreht wird und die Rolle 4 des Armes 5 des Zwischenhebels 3 auf die Außenfläche des zugehörigen Nockens 2 gelangt, wird der Zwischenhebel 3 entgegen dem Uhrzeigersinn in Fig. 3 geschwenkt. Über den Arm 6 wird der Rollenhebel 7 ebenfalls entgegen dem Uhrzeigersinn geschwenkt. Da der Arm 9 des Rollenhebels 7 auf den Ventilschaft 10 einwirkt, wird je nach Drehwinkel der Verstellwelle 1 der Ventilschaft 10 mehr oder weniger weit nach unten verschoben und damit der Hub des Ventils entsprechend dem Leistungsbedarf eingestellt.If the adjusting shaft 1 is rotated so that the arm 5 of the intermediate lever 3 abuts in the area next to the cam 2 on the lateral surface of the adjusting shaft 1, then the roller lever 7 is pivoted so far back that the valve stem 10 is not actuated. Once the adjusting shaft 1 is rotated and the roller 4 of the arm 5 of the intermediate lever 3 reaches the outer surface of the associated cam 2, the intermediate lever 3 counterclockwise in Fig. 3 pivoted. About the arm 6, 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.

Da der Drehantrieb 12 hydraulisch betätigt wird, können die Einlassventile, wenn der Kraftfahrzeugmotor abgeschaltet wird, in ihrer Ausgangsstellung zurückgeführt werden. Die Einlassventile gehen hierbei in eine Position zurück, in der sie die kleinste Einlassöffnung freigeben. Die beschriebene voll variable Ventilsteuerung ist kostengünstig und darüber hinaus einfach im Aufbau.Since the rotary drive 12 is hydraulically actuated, the intake valves, when the motor vehicle engine is switched off, can be returned to their initial 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 zeigt, dass mit der Verstellwelle 1 und dem Drehantrieb 12 mehrere Einlassventile gleichzeitig betätigt werden können. Auf der Verstellwelle 1 sitzen jeweils mit Abstand mehrere Nocken 2, die jeweils über den Zwischenantrieb gemäß Fig. 3 auf die entsprechende Ventilschafte wirken. Mit dem einzigen Drehantrieb 12 können beim Ausführungsbeispiel acht Nocken 2 betätigt werden, die auf entsprechende Ventilschafte einwirken und je nach Drehlage der Verstellwelle 1 den Hub des Ventils steuern. Fig. 4 shows that with the adjustment 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 stem. With the single rotary drive 12, eight cams 2 can be actuated in the exemplary embodiment, which act on corresponding valve shafts and, depending on the rotational position of the adjusting shaft 1, control the stroke of the valve.

Bei der Ausführungsform gemäß den Fig. 5 und 6 wird die Verstellwelle 1, auf der entsprechend der vorherigen Ausführungsform acht Nocken 2 sitzen, nicht mehr von einem Ende aus, sondern in halber Länge drehbar angetrieben. Die Verstellwelle 1 hat beim Ausführungsbeispiel in halber Länge eine umlaufende Außenverzahnung 31, in die eine Zahnstange 32 des Drehantriebes 12a eingreift. Die Zahnstange 32 sitzt auf einer Kolbenstange 33, die aus einem Zylinder 34 ragt. Die Kolbenstange 33 trägt innerhalb des Zylinders 34 einen Kolben 35, der abgedichtet im Zylinder 34 mittels Hydraulikmedium verschiebbar ist. Durch Ein- und Ausfahren der Kolbenstange 33 wird die Verstellwelle 1 über die Zahnstange 32 in entsprechender Richtung gedreht. Über den jeweiligen Nocken 2 und die zugehörige Übertragungskette gemäß Fig. 3 wird der entsprechende Ventilschaft verstellt und damit der Hub des Einlassventiles eingestellt.In the embodiment according to the FIGS. 5 and 6 is 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 a length 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. By retracting and extending the piston rod 33, the adjusting shaft 1 is rotated via the rack 32 in the corresponding direction. About the respective cam 2 and the associated transmission chain according to Fig. 3 the corresponding valve stem is adjusted, thus adjusting the stroke of the inlet valve.

Diese Ausführungsform zeichnet sich durch ihre konstruktive Einfachheit aus. Der Zahnstangentrieb gewährleistet eine exakte stufenlose Drehung der Verstellwelle 1, so dass der Hub der Einlassventile entsprechend stufenlos eingestellt werden kann.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.

Bei der Ausführungsform nach Fig. 7 ist für jeden Motorzylinder Z ein gesonderter Drehantrieb 12a vorgesehen, der entsprechend der Ausführungsform nach den Fig. 5 und 6 ausgebildet ist. Dementsprechend hat diese voll variable Ventilsteuerung vier Verstellwellen 1 mit jeweils zwei Nocken 2. Damit können die Einlassventile unabhängig voneinander variabel eingestellt werden, indem die jeweilige Verstellwelle 1 mit dem Drehantrieb 12a in gewünschtem Maße um ihre Achse gedreht wird. Die Drehantriebe 12a werden unabhängig voneinander mit Hydraulikmedium versorgt, so dass eine problemlose und zuverlässige Einstellung der jeweiligen Einlassventile gewährleistet ist.In the embodiment according to Fig. 7 For each engine cylinder Z, 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, each with two cams 2. Thus, 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 inlet valves is ensured.

Bei der Ausführungsform nach den Fig. 8 bis 10 hat der Antrieb 12b eine Grobeinstelleinrichtung 36 sowie Feineinstelleinrichtungen 37. Mit der Grobeinstelleinrichtung 36 werden die Feineinstelleinrichtungen 37, die für jedes Einlassventil entsprechend der Ausführungsform gemäß Fig. 7 einzeln vorgesehen sind, gemeinsam betätigt. Mit den Feineinstelleinrichtungen 37 können dann die einzelnen Verstellwellen 1 in erforderlichem Maße fein eingestellt werden, um individuell den Hub der Einlassventile einzustellen.In the embodiment of the Fig. 8 to 10 the drive 12b has a coarse adjustment device 36 and fine adjustment means 37. The coarse adjustment device 36, the fine adjustment means 37, which for each inlet valve according to the embodiment of Fig. 7 are provided individually, operated together. With the fine adjustment 37 then the individual adjustment shafts 1 can be adjusted to the required extent fine to individually adjust the stroke of the intake valves.

Die Grobeinstelleinrichtung 36 hat einen Antrieb 38, mit dem eine Zwischenwelle 39 drehbar angetrieben werden kann. Sie liegt parallel zu den fluchtend zueinander liegenden Verstellwellen 1 und weist im Bereich einer Zahnstange 40 eine Außenverzahnung 41 auf, in welche die Zahnstange 40 eingreift. Sie sitzt auf dem aus einem Zylinder 42 ragenden Ende einer Kolbenstange 43, die am anderen Ende einen Kolben 44 trägt, der abgedichtet im Zylinder 42 geführt ist. Durch Beaufschlagung des Kolbens 44 mit einem Hydraulikmedium kann die Kolbenstange 43 ein- und ausgefahren werden, so dass die Zwischenwelle 39 über die Zahnstange 40 in der gewünschten Richtung gedreht werden kann.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 acting on 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.

Mit der Zwischenwelle 39 können Träger 45 verschoben werden, die in Form einer Zahnstange ausgebildet sind und mit einer entsprechenden Außenverzahnung 46 der Zwischenwelle 39 in Eingriff sind.With the intermediate shaft 39 carriers 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 into engagement are.

Wenn die Zwischenwelle 39 durch die Zahnstange 40 um ihre Achse gedreht wird, werden die Träger 45 entsprechend verschoben.When the intermediate shaft 39 is rotated about its axis by the rack 40, the carriers 45 are displaced accordingly.

Die Träger 45, die den Einlassventilen zugeordnet sind, sind gleich ausgebildet und weisen einen Druckraum 47 auf, in dem ein Kolben 48 verschiebbar ist. Er sitzt auf dem freien Ende einer Kolbenstange 49, die aus dem Träger 45 ragt und eine Zahnstange 50 trägt. Sie ist mit der Außenverzahnung 31 der zugehörigen Verstellwelle 1 in Eingriff.The carriers 45 which are assigned to 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.

Durch Betätigen des Antriebes 38 bis 44 (Fig. 10) wird zunächst die Zwischenwelle 39 um ihre Achse gedreht, wodurch die mit ihr in Eingriff befindlichen Träger 45 je nach Drehrichtung in Richtung auf die Verstellwellen 1 oder von ihnen weg bewegt werden. Auf diese Weise erfolgt eine Grobeinstellung des Hubes der Einlassventile des Motorzylinders Z. Anschließend können mit den Feineinstelleinrichtungen 37 die Ventilschäfte 10 der Einlassventile unabhängig voneinander in ihre exakte Lage verstellt werden, so dass die verschiedenen Einlassventile ihren eigenen optimalen Hub ausführen. Hierzu werden die Kolbenstangen 49 der Träger 45 ein- und ausgefahren, wodurch über die Zahnstangen 50 die Verstellwellen 1 in der beschriebenen Weise um ihre Achsen gedreht werden. Über die Nocken 2 auf den Verstellwellen 1 werden die Zwischenhebel 3 (Fig. 3) in der beschriebenen Weise geschwenkt, wodurch die Rollenhebel 7 entsprechend geschwenkt werden. Auf diese Weise werden die Ventilschäfte 10 der Einlassventile in ihre erforderliche Lage verschoben. Mit den Feineinstelleinrichtungen 37 können die Einlassventile so eingestellt werden, dass ein Klopfen des Motors nicht auftritt.By actuating the drive 38 to 44 ( Fig. 10 ), 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, the valve stems 10 of the intake valves can be adjusted independently of each other in their exact position with the fine adjustment 37, 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. 3 ) pivoted in the manner described, whereby the roller lever 7 are pivoted accordingly. In this way, the valve stems 10 of the intake valves are shifted to their required position. With the fine adjustment means 37, the intake valves can be adjusted so that knocking of the engine does not occur.

Die Ausführungsform gemäß den Fig. 11 und 12 ist im Wesentlichen gleich ausgebildet wie das Ausführungsbeispiel nach den Fig. 8 bis 10. Lediglich der Antrieb 12c hat eine andere Ausbildung als bei der vorigen Ausführungsform. Dieser Antrieb 12c hat die gleiche Ausbildung wie der Antrieb 12 gemäß den Fig. 1 bis 3. Der Rotor 16 ist an einem Ende der Zwischenwelle 39 vorgesehen, vorteilhaft einstückig mit ihr ausgebildet. Der Antrieb 12c ist im Übrigen gleich ausgebildet wie der Drehantrieb 12 gemäß den Fig. 1 bis 3. Mit den beiden Rotoren 16, 17 im Stator 13 kann die Zwischenwelle 39 maximal um 180° um ihre Achse gedreht werden. Diese Drehbewegung der Zwischenwelle 39 wird auf die Träger 45 übertragen, die entsprechend der vorigen Ausführungsform senkrecht zur Achse der Verstellwellen 1 verschoben werden. Über die Zahnstangen 50 werden die Verstellwellen 1 in entsprechendem Maße um ihre Achsen gedreht. Zusätzlich ist mit den Feineinstelleinrichtungen 37 eine Feineinstellung des Hubes jedes Einlassventiles der Motorzylinder Z möglich. Wie beim vorigen Ausführungsbeispiel bleiben bei der Grobverstellung mittels des Stators 13 und der beiden Rotoren 16, 17 die Kolben 48 der Feineinstelleinrichtungen 37 durch entsprechende Druckbeaufschlagung in ihrer jeweils eingestellten Lage. Erst wenn die Grobeinstellung beendet ist, werden die Feineinstelleinrichtungen, sofern erforderlich, betätigt, indem die Kolben 48 so mit Hydraulikmedium beaufschlagt werden, dass er in der gewünschten Richtung verschoben wird.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 12 c has the same construction 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. This rotational movement of the intermediate shaft 39 is transmitted to the carrier 45, which are moved perpendicular to the axis of the adjusting shafts 1 according to the previous embodiment. About the racks 50, the adjusting shafts 1 are rotated in a corresponding extent about their axes. In addition, a fine adjustment of the stroke of each intake valve of the engine cylinder Z is possible with the fine adjustment 37. As in the previous embodiment remain in the coarse adjustment by means of the stator 13 and the two rotors 16, 17, the piston 48 of the fine adjustment 37 by appropriate pressurization in their respective set position. Only when the coarse adjustment is completed, the fine adjustment, if required, actuated by the piston 48 are so loaded with hydraulic medium that it is displaced in the desired direction.

Bei der Ausführungsform nach den Fig. 13 und 14 ist für die Einlassventile der Motorzylinder Z die gemeinsame Verstellwelle 1 vorgesehen. Darum können die Ventilschäfte 10 (Fig. 3) der Einlassventile nur gemeinsam verschoben werden. Zum Antrieb der Verstellwelle 1 ist der Antrieb 12d vorgesehen. Er hat den zylindrischen Stator 13, in dem ein Rotor 17 drehbar gelagert ist. Er sitzt auf der Achse 18, die im Zylinderkopf 19 gelagert ist (Fig. 13). In die Druckräume 24 des Stators 13 wird das Hydraulikmedium eingebracht. Dadurch wird der Stator 13 gegenüber dem Rotor 17 in der beschriebenen Weise gedreht. Der Stator 13 trägt an seinem Außenmantel eine Verzahnung 51, die in Eingriff mit einer Außenverzahnung 52 der Verstellwelle 1 ist. Dadurch wird die Verstellwelle 1 im erforderlichen Maße gedreht. Im Unterschied zur Ausführungsform nach den Fig. 1 bis 3 beträgt der Drehwinkel des Stators 13 lediglich 90° . Aus diesem Grunde ist das Übersetzungsverhältnis zwischen der Verzahnung 51 des Stators 13 und der Außenverzahnung 52 der Verstellwelle 1 so gewählt, dass die Verstellwelle bei einem Drehwinkel von 90° des Stators 13 um 180° dreht. Die Übertragung der Drehung der Verstellwelle 1 auf die Ventilschäfte 10 erfolgt über den Zwischentrieb, wie er anhand von Fig. 3 beschrieben worden ist.In the embodiment of the Fig. 13 and 14 is provided for the intake valves of the engine cylinder Z, the common adjustment shaft 1. Therefore, the valve stems 10 ( Fig. 3 ) of the intake valves are only moved together. To drive the adjusting shaft 1, the drive 12d is provided. 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. As a result, the adjusting shaft 1 is rotated to the required extent. In contrast to the embodiment of the Fig. 1 to 3 the angle of rotation of the stator 13 is only 90 °. For this reason, 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.

Im Unterschied zur vorigen Ausführungsform ist beim Ausführungsbeispiel nach den Fig. 15 und 16 für jedes Einlassventil der Motorzylinder Z eine Verstellwelle 1 vorgesehen. Dadurch ist jeder Verstellwelle 1 ein Drehantrieb 12e zugeordnet. Er ist gleich ausgebildet wie der Drehantrieb 12d gemäß den Fig. 13 und 14. Mittels der Drehantriebe 12e können die Verstellwellen 1 unabhängig voneinander im erforderlichen Maße drehbar angetrieben werden. Die Ventilschäfte der Einlassventile der Motorzylinder Z können darum unabhängig voneinander optimal verschoben werden.In contrast to the previous embodiment is in the embodiment of the FIGS. 15 and 16 for each intake valve of the engine cylinder Z an adjusting 1 is provided. As a result, 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 , By means of the rotary actuators 12 e, 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.

Die Fig. 17 bis 19 zeigt einen Drehantrieb 12f, der ähnlich wie die Ausführungsform nach den Fig. 8 bis 10 eine Grobeinstelleinrichtung 36f und Feineinstelleinrichtungen 37f für die einzelnen Verstellwellen 1 aufweist. Die Grobeinstelleinrichtung 36f hat den Stator 13, in dem der Rotor 17 untergebracht ist, der auf der Achse 18 sitzt. Sie ist im Zylinderkopf 19 gelagert. Wie bei den Ausführungsformen nach den Fig. 13 bis 16 ist der Stator 13 stirnseitig durch die Deckscheiben 14, 15 geschlossen. Der Stator 13 hat die Außenverzahnung 51. In die Druckräume 24 des Stators 13 wird das Hydraulikmedium so eingebracht, dass wird der Stator 13 gegenüber dem Rotor 17 gedreht wird. Der maximale Drehwinkel des Stators 13 beträgt im Ausführungsbeispiel 90° .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. As in the embodiments of the Fig. 13 to 16 is the stator 13 frontally closed by the cover plates 14, 15. The stator 13 has the external teeth 51. The hydraulic medium is introduced into the pressure chambers 24 of the stator 13 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.

In die Außenverzahnung 51 des Stators 13 greift die Außenverzahnung 52 der Zwischenwelle 39 ein. Mit der Außenverzahnung 52 der Zwischenwelle 39 kämmen vier Schwenkmotoren 53, die jeweils auf einer Verstellwelle 1 sitzen und Teil der Feineinstelleinrichtungen 37f sind. Jeder Schwenkmotor 53 hat einen Außenring 54 (Fig. 19), der mit einer Außenverzahnung 55 versehen ist, mit welcher der Außenring 54 in die Außenverzahnung 52 der Zwischenwelle 39 eingreift. Von der Innenwand des Außenringes 54 stehen radial nach innen Flügel 56 ab, die mit ihren Stirnseiten an einem zylindrischen Grundkörper 57 eines Rotors 58 anliegen. Er hat radial nach außen gerichtete Flügel 59, die mit ihren Stirnseiten an der Innenwand des Außenringes 54 anliegen. Der Rotor 58 kann um einen geringen Verdrehwinkel innerhalb des Außenringes 54 gedreht werden, bis seine Flügel 59 an den Seitenflächen eines der benachbarten Flügel 56 des Außenringes 54 zur Anlage kommen. Der Rotor 58 ist drehfest mit der jeweiligen Verstellwelle 1 verbunden. Zwischen die Flügel 56, 59 des Außenringes 54 und des Rotors 58 wird Hydraulikmedium unter Druck eingebracht, so dass die Relativdrehung des Rotors 58 gegenüber dem Außenring 54 durchgeführt werden kann.In the external teeth 51 of the stator 13, the external teeth 52 of the intermediate shaft 39 engages. With the external teeth 52 of the intermediate shaft 39 mesh four pivot motors 53, each sitting on an adjusting shaft 1 and part of the fine adjustment 37 f. Each pivot motor 53 has an outer ring 54 (FIG. Fig. 19 ), which is provided with an outer toothing 55, with which the outer ring 54 in the external teeth 52 of the intermediate shaft 39 engages. 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. Between the wings 56, 59 of the outer ring 54 and the rotor 58 hydraulic medium is introduced under pressure, so that the relative rotation of the rotor 58 relative to the outer ring 54 can be performed.

Im Ausführungsbeispiel sind vier fluchtend zueinander angeordnete Verstellwellen 1 vorgesehen, auf denen entsprechend den Ausführungsformen nach den Fig. 7 und 11 bis 16 jeweils zwei mit axialem Abstand voneinander liegende Nocken vorgesehen sind. Mit ihnen werden die Schäfte 10 (Fig. 3) der Einlassventile betätigt, wie anhand von Fig. 3 im einzelnen erläutert worden ist.In the exemplary embodiment, four adjustment shafts 1 arranged in alignment with one another are provided, on which according to the embodiments according to FIGS Fig. 7 and 11 to 16 in each case two axially spaced cams are provided. With them, the shanks 10 ( Fig. 3 ) of the intake valves, as indicated by Fig. 3 has been explained in detail.

Mit der Grobeinstelleinrichtung 36f des Drehantriebes 12f werden zunächst alle Verstellwellen 1 gleichzeitig und um den gleichen Winkel verdreht. Hierzu wird durch unter Druck stehendes Hydraulikmedium, das in die Druckräume 24 eingebracht wird, der Stator 13 gegenüber dem Rotor 17 so weit gedreht, bis die Rotorflügel 20 an den Statorflügeln 23 zur Anlage kommen. Über die Zwischenwelle 39 werden die mit ihr kämmenden Außenringe 54 der Schwenkmotoren 53 um ihre Achse gedreht. Während dieser Grobeinstellung sind die Flügel 56 des Außenringes 54 durch Druckbeaufschlagung in Anlage an den Rotorflügeln 59 gehalten, so dass beim Drehen des Außenringes 54 auch der Rotor 58 in gleichem Drehsinn mitgenommen wird. Auf diese Weise werden sämtliche Verstellwellen 1 durch die Grobeinstelleinrichtung 36f in gleichem Maße um ihre Achse gedreht. Anschließend können die Verstellwellen 1 unabhängig voneinander mittels der Feineinstelleinrichtungen 37f noch um einen kleinen Winkel gedreht werden. Ausgehend von der Stellung gemäß Fig. 19 beispielsweise wird der Druckraum zwischen den Rotorflügeln 59 und den Flügeln 56 des Außenringes 54 entlastet, während in den Bereich zwischen den aneinanderliegenden Flügeln 56, 59 das unter Druck stehende Hydraulikmedium eingebracht wird. Dadurch wird der Rotor 58 im Uhrzeigersinn geringfügig gegenüber dem Außenring 54 gedreht. Da die Rotoren 58 drehfest mit den zugehörigen Verstellwellen 1 verbunden sind, werden diese Verstellwellen noch um einen kleinen Winkel gedreht. Bei dieser Drehbewegung sind die Druckräume 24 des Stators 13 so unter Druck gesetzt, dass eine Relativdrehung zwischen dem Stator 13 und dem Rotor 17 nicht erfolgen kann.With the coarse adjustment device 36f of the rotary drive 12f, initially all adjustment shafts 1 are simultaneously rotated and at the same angle. For this purpose, by means of pressurized hydraulic medium which is introduced into the pressure chambers 24, the stator 13 is rotated relative to the rotor 17 until the rotor blades 20 come to rest on the stator blades 23. About the intermediate shaft 39, the meshing with her outer rings 54 of the pivot motors 53 are rotated about its axis. During this coarse adjustment, the wings 56 of the outer ring 54 are held by pressurization in contact with the rotor blades 59, so that upon rotation of the outer ring 54 and the rotor 58 is taken in the same direction of rotation. In this way, all the adjustment shafts 1 are rotated by the coarse adjustment device 36f to the same extent about its axis. Subsequently, the adjusting shafts 1 can be rotated independently of one another by means of the fine adjustment devices 37f by a small angle. Starting from the position according to Fig. 19 For example, the pressure space between the rotor blades 59 and the wings 56 of the outer ring 54 is relieved, while in the area between the adjacent wings 56, 59, the pressurized hydraulic medium is introduced. As a result, the rotor 58 is rotated slightly clockwise relative to the outer ring 54. Since the rotors 58 are non-rotatably connected to the associated adjusting shafts 1, these adjusting shafts are still rotated by a small angle. During this rotational movement, the pressure chambers 24 of the stator 13 are pressurized so that a relative rotation between the stator 13 and the rotor 17 can not take place.

In den dargestellten Ausführungsbeispielen sind für jeden Zylinder des Motors zwei Einlassventile vorgesehen. Je nach Art des Motors können weitere Einlassventile pro Zylinder vorgesehen sein. Im einfachsten Fall hat jeder Zylinder nur ein Einlassventil.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 inlet valve.

[Die Ventilsteuerungen sind anhand der Ausführungsbeispiele zur Steuerung des Hubes von Einlassventilen beschrieben worden. Die Ventilsteuerungen können selbstverständlich auch für Auslassventile in gleicher Weise eingesetzt werden, um deren Hub entsprechend zu verändern.[The 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.

Bei den beschriebenen Ausführungsformen ist die Verstellwelle 1 jeweils mit Nocken 2 versehen. Die Verstellwelle 1 kann aber bei sämtlichen Ausführungsformen beispielsweise auch eine Exzenterwelle sein, die in diesem Falle keine Nocken trägt. Wesentlich für die Verstellwelle ist, dass bei ihrer Drehung eine Quer- bzw. Radialkomponente erzeugt wird, die dazu ausgenutzt wird, über die Übertragungskette den Ventilschaft 10 im gewünschten Masse zu verschieben. Die Übertragungskette muss nicht, wie beispielhaft in Fig. 3 dargestellt ist, durch mechanische Bauelemente gebildet sein, sondern kann beispielsweise auch eine hydraulische Übertragungskette sein. Es muss lediglich gewährleistet sein, dass der von der Nockenwelle des Motors erzeugte normale Hub des Ventilschaftes 10 durch die Verstellwelle 1 variiert werden kann.In the described embodiments, the adjusting shaft 1 is provided with cams 2 respectively. However, in all embodiments, 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 during their rotation a transverse or radial component is generated, which is exploited to move the valve stem 10 in the desired mass via the transmission chain. The transmission chain does not have to be 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.

Claims (20)

  1. A hydraulic rotary drive (12, 12c) of a valve control in a motor vehicle engine with a cylindrical stator (13) comprising two rotors (16, 17), one of said rotors (16) is fixedly connected to a adjusting shaft (1), the second rotor (17) is arranged on an axis (18) aligned with the adjusting shaft (1) and mounted at a cylinder head (19).
  2. The hydraulic rotary drive (12, 12c) according to claim 1, characterized in that the adjusting shaft (1) is provided with cams (2) being fixedly attached.
  3. The hydraulic rotary drive (12, 12c) according to claim 1 or 2, characterized in that the stator (13) has an inner wall and stator vanes (20) connected to the inner wall, wherein the stator vanes (20) project from the inner wall, wherein the at Least one rotor (16, 17) has a base member (21, 22), especially a cylindrical base member (21, 22), provided with radially projecting rotor vanes (23), wherein the rotor vanes (23) are positioned between the stator vanes (20) wherein especially the axis ofthe stator (13) and the rotors (16, 17) coincide.
  4. The hydraulic rotary drive (12, 12c) according to one ofthe preceding claims, characterized in that two rotors (16, 17) are positioned adjacent to one another within the stator (13) and are separated from one another whereas especially the rotors (16, 17) are with coinciding axes relative to one another.
  5. The hydraulic rotary drive (12, 12c) according to claim 4, characterized in that the rotors (16, 17) are accommodated in separated chambers (24).
  6. The hydraulic rotary drive (12, 12c) according to one of the preceding claims, characterized in that the rotors (16, 17) are rotatable independently of each other.
  7. The hydraulic rotary drive (12, 12c) according to one of the preceding claims, characterized that the stator (13) is rotated by pressure Loading and entrains first rotor (16) is placed towards the adjusting shaft (1) relative to the other rotor (17) to a Limited extent.
  8. The hydraulic rotary drive (12, 12c) according to one of the preceding claims, characterized in that the first rotor (16) is adapted to rotate to a Limited extent relative to the stator (13) under pressure Loading.
  9. The hydraulic rotary drive (12, 12c) according to one of claims 1 to 8, characterized in that the adjusting shaft (1) to be joined has at Least one, preferably several cams (2) adapted to control several valves.
  10. The hydraulic rotary drive (12, 12c) according to one of claims 1 to 9, characterized in that each one of the adjusting shafts (1) to be joined has two cams (2) adapted to control two valves.
  11. The hydraulic rotary drive (12, 12b, 12f), especially according to one claims 1 to 10, characterized in that the hydraulic drive (12, 12b, 12f) comprises a coarse adjusting device (36, 36f) and at Least one fine adjusting device (37, 37f).
  12. The hydraulic rotary drive (12, 12b, 12f) according to claim 11, characterized in that the coarse adjusting device (36, 36f) comprises an intermediate shaft (39) adapted to rotate the at least adjusting shaft (1) to be joined to a limited extent.
  13. The hydraulic rotary drive (12, 12b, 12f) according to claim 11 or 12, characterized in that the coarse adjusting device (36) is a sliding drive (40 to 44).
  14. The hydraulic rotary drive (12, 12b, 12f) according to claim 13, characterized in that the sliding drive (40 to 44) comprises a toothed rack (40) extending transversely to the intermediate shaft (39) and engages in a toothing (41) of the intermediate rack (39) being preferably mounted on a piston rod (43), comprising a cylinder (42) and a piston (44) moveable in the cylinder (42), wherein at least a carrier (45) engages especially in the toothing (41) of the intermediate shaft (39) comprising a sliding drive (45, 47 to 50) of the fine adjusting device (37).
  15. The hydraulic rotary drive (12, 12b, 12f) according to claim 14, characterized in that the sliding drive (45, 47 to 50) comprises a toothed rack (50) which preferably engages in the outer toothing (31) ofthe adjusting shaft (1) to be joined, the toothed rack (50) is mounted is on a piston rod (49) comprising movable pistons (48) in a pressure chamber (47) of the carrier (45).
  16. The hydraulic rotary drive (12, 12a, 12b, 12c, 12d, 12f) according to one of the claims 11 to 15, characterized in that several of the at least one adjusting shafts (1) are provided and wherein the intermediate shaft (39) is configured to carry out a common coarse adjustment ofthe several adjusting shafts (1), wherein each of the several adjusting shafts (1) is connected to one of the at least one fine adjusting device (37), respectively.
  17. The hydraulic rotary drive (12, 12b, 12d, 12f) according to claim 16, characterized in that coarse adjusting device (36f) has a hydraulic rotary drive (13, 17) comprising a stator (13) and a rotor (17) rotatable relative to each other, wherein the stator (13) has an outer toothing (51) engaging a toothing (52) of the intermediate shaft (39).
  18. The hydraulic rotary drive (12, 12b, 12d, 12f) according to claim 17, characterized in that an outer tooting (55) of an outer ring (54) of the fine adjustment device (37f) is meshing with the outer toothing (50) of the intermediate shaft (39).
  19. The hydraulic rotary drive (12, 12b, 12d, 12f) according to claim 18, characterized in that the fine adjusting device (37f) comprises a rotor (58) arranged in the outer ring (54), wherein the rotor (58) is fixedly connected to the adjusting shaft (1) and is rotatable to a limited extent relative to the outer ring (54), the rotor (58) preferably comprising inwardly projecting vanes (56) and having radially outwardly projecting vanes (59) positioned between the inwardly projecting vanes (56) ofthe outer ring (54).
  20. A valve control with a hydraulic rotary drive according to one of claims 1 to 19, characterized in that for each cylinder ofthe motor vehicle one, each, adjusting shaft (1) is provided which can preferably rotate to a limited extent by means of an own hydraulic rotary drive (12a, 12c).
EP07107909A 2002-03-20 2003-03-12 Valve actuation for adjusting the stroke of valves in an internal combustion engine Expired - Lifetime EP1832723B1 (en)

Applications Claiming Priority (2)

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DE10213081A DE10213081A1 (en) 2002-03-20 2002-03-20 Valve control for adjusting the stroke of valves in motor vehicles
EP03005576A EP1347154B1 (en) 2002-03-20 2003-03-12 Valve lift control for internal combustion engine

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EP03005576A Division EP1347154B1 (en) 2002-03-20 2003-03-12 Valve lift control for internal combustion engine
EP03005576.8 Division 2003-03-12

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EP1832723A2 EP1832723A2 (en) 2007-09-12
EP1832723A3 EP1832723A3 (en) 2007-09-26
EP1832723B1 true EP1832723B1 (en) 2010-03-03

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EP03005576A Expired - Lifetime EP1347154B1 (en) 2002-03-20 2003-03-12 Valve lift control for internal combustion engine
EP07107909A Expired - Lifetime EP1832723B1 (en) 2002-03-20 2003-03-12 Valve actuation for adjusting the stroke of valves in an internal combustion engine

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EP (2) EP1347154B1 (en)
AT (2) ATE459789T1 (en)
DE (3) DE10213081A1 (en)
ES (1) ES2312676T3 (en)

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EP1347154A3 (en) 2003-12-17
US20030177991A1 (en) 2003-09-25
EP1832723A2 (en) 2007-09-12
DE50312490D1 (en) 2010-04-15
EP1832723A3 (en) 2007-09-26
ATE406504T1 (en) 2008-09-15
ES2312676T3 (en) 2009-03-01
DE50310394D1 (en) 2008-10-09
EP1347154B1 (en) 2008-08-27
ATE459789T1 (en) 2010-03-15
US6814036B2 (en) 2004-11-09
EP1347154A2 (en) 2003-09-24
DE10213081A1 (en) 2003-10-02

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