[go: up one dir, main page]
More Web Proxy on the site http://driver.im/

EP1608851A1 - Device for the variable actuation of the gas exchange valves of internal combustion engines, and method for operating one such device - Google Patents

Device for the variable actuation of the gas exchange valves of internal combustion engines, and method for operating one such device

Info

Publication number
EP1608851A1
EP1608851A1 EP04721181A EP04721181A EP1608851A1 EP 1608851 A1 EP1608851 A1 EP 1608851A1 EP 04721181 A EP04721181 A EP 04721181A EP 04721181 A EP04721181 A EP 04721181A EP 1608851 A1 EP1608851 A1 EP 1608851A1
Authority
EP
European Patent Office
Prior art keywords
housing
cam
axis
bolt
valves
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.)
Granted
Application number
EP04721181A
Other languages
German (de)
French (fr)
Other versions
EP1608851B1 (en
Inventor
Helmut Schön
Kai-Uwe Keller
Peter Kuhn
Gordon KÖHNE
Frank Obrist
Christian Busch
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.)
Thyssenkrupp Dynamic Components Teccenter AG
Original Assignee
ThyssenKrupp Automotive AG
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 ThyssenKrupp Automotive AG filed Critical ThyssenKrupp Automotive AG
Publication of EP1608851A1 publication Critical patent/EP1608851A1/en
Application granted granted Critical
Publication of EP1608851B1 publication Critical patent/EP1608851B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F01L13/0063—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 cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • 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
    • F01L13/0005—Deactivating valves
    • 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
    • F01L13/0063—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 cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot
    • F01L2013/0068—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 cam contact point by displacing an intermediate lever or wedge-shaped intermediate element, e.g. Tourtelot with an oscillating cam acting on the valve of the "BMW-Valvetronic" type
    • 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
    • F01L2303/00—Manufacturing of components used in valve arrangements
    • F01L2303/01—Tools for producing, mounting or adjusting, e.g. some part of the distribution
    • 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
    • F01L2800/06—Timing or lift different for valves of same cylinder
    • 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
    • F01L2800/13—Throttleless
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/032—Electric motors

Definitions

  • the invention relates to a device for variable actuation of the gas exchange valves of internal combustion engines according to the preamble of claim 1.
  • Such devices are used to design the control of gas exchange valves so that it becomes possible to operate reciprocating engines without the otherwise usual throttle valve.
  • Such a device is known for example from DE 1 01 23 1 86 A1.
  • a rotating cam first drives an intermediate link, which carries out an oscillating, pure rotary movement and carries a control cam, which is composed of a latching area and a stroke area.
  • the control curve transfers the stroke curve required to actuate the valve to the role of a rocker arm-like output member, which in turn actuates the valve.
  • the desired different valve lift curves are generated in that the center of rotation of the intermediate member is shifted on an arc-shaped path which is concentric with the role of the output member in its position when the valve is closed.
  • the center of rotation is formed by a roller provided on the intermediate member, which is non-positively supported on an arc-shaped track in the housing, which is also concentric with the role of the output member, that is forms an aquidistante to the path of the turning center and which is called the backdrop.
  • the roller attached to the intermediate link is supported on a cam disc, the angular position of which determines the position of the center of rotation on its arc-shaped path.
  • the roller attached to the intermediate link only bears against the link if the gas and ace forces of the valve train are directed accordingly and the role is actually supported on the link. If this is not the case, which can happen at overspeed, the frictional connection is lost and lifting takes place, which can lead to noise and even damage when it is replaced. Added to this are the relatively difficult machining of the scenes as segments of an inner cylinder, which cannot be processed continuously, and the inadequate hardness of common housing materials for the roller-scenery contact. With regard to assembly, there is a disadvantage that the control housing cannot be completely pre-assembled on the cylinder head.
  • the solution provides that the centers of rotation of the intermediate elements driven by the cam are guided by positive guides, that is to say in a form-fitting manner on the adjustment curve. This ensures that the center of rotation of an intermediate link cannot leave the adjustment curve, so that noises and damage that could be attributed to leaving are avoided.
  • this feature is preferably realized in that one or more intermediate links are mounted on a cylindrical bolt, on the axis of which the centers of rotation lie, and that the axis of the bolt is inevitably guided on the adjustment curve.
  • the active surface on the output member, to which the control cam of the intermediate member transmits its movement is circular-cylindrical, e.g. is formed by a roller, a circular arc-shaped adjustment curve can be assumed, the center of which coincides with the center of the circular cylindrical active surface or the roller.
  • Such an adjustment curve is realized according to a further proposal according to the invention by pendulum supports which are connected via their respective first joint to the cylinder head or the control housing and with their respective second joint to the bolt.
  • the cylinder head side the joints common axis coincides with the axis of said cylindrical active surfaces ⁇ on the driven member along which the bolt-side joints with the Pin axis.
  • the bolt or its axis can also be positively guided on the adjustment curve with articulated quadrilaterals formed from pendulum supports.
  • the adjustment curve that can be realized in this way comes close to the shape of a circular arc and fulfills this exactly at the design point when the system lines meet at the center of the circular arc.
  • the deviations outside the design point are absorbed by hydraulic lash adjusters, which are to be provided on the rocker arm-like or straight-guided output links.
  • the pin is guided by a slide that is linearly adjustable in the control housing.
  • a slide that is linearly adjustable in the control housing.
  • the position of the bolt or its axis on the respective adjustment curve is preferably determined by direct or indirect contact with one or more cam disks, which are attached in a rotationally fixed manner to one or more adjustment shafts.
  • the cams are attached to an axially displaceable adjustment axis.
  • the adjusting shaft or the adjusting axis can on the one hand, by means of a suitable gear or a connecting element, of an adjusting means, for example an adjusting motor, are rotated or displaced.
  • the adjustment can of course also be carried out by hydraulic elements. If the bolt is guided by a linearly adjustable slide, the adjustment can also be made directly from the adjusting motor via a spindle provided with a movement thread.
  • a particularly advantageous variant of the three embodiments in terms of installation space and variety of parts is to simultaneously design the bolt on which the intermediate members are mounted as an adjusting shaft by providing cam discs, rotatably mounted in the pendulum supports, the four-bar linkage or the slide and by an adjusting means , for example an adjusting motor, is rotated in accordance with the desired valve lift curve.
  • slide pieces for the cam disks made of a material of increased strength must be provided in the control housing. Since the adjustment motor will generally be fixed to the housing, but the bolt or the control shaft moves parallel to itself during the adjustment movement, a connecting element must be arranged between the two, which permits this displacement.
  • this can be a cardan shaft, a Schmidt clutch, an Oldham clutch or a gear or chain gear.
  • a lever mechanism is also suitable for hydraulic actuation.
  • the device according to the invention including an adjusting motor or an adjusting device, can be provided separately for each valve of an engine, so that any combinations of valve strokes or opening angles of the individual valves of an engine are possible, including the deactivation of individual cylinders.
  • a common adjustment of several valves will be provided. This applies particularly to multi-valve engines for the intake and exhaust valves of a cylinder.
  • two intake valves can be actuated by a cam via an intermediate link which has a control curve for each valve. Since there is only one intermediate link and only one pin, both valves are adjusted together and in the same way.
  • two different control curves can also be provided on the common intermediate link, with the result of different lift curves on both valves despite the common adjustment.
  • This variant opens the possibility of opening only one of the two valves, particularly in the lowest load range.
  • the particular advantage of this option is that very small cross-sections must be released in the lowest load range and these can be adhered to more precisely if they are only released by a valve.
  • the possibilities of generating different valve lift curves for two intake or exhaust valves of a cylinder are expanded according to the invention in that two different cams and two intermediate links with different control curves are used. Nevertheless, both valves can be adjusted together, since the two intermediate links can be mounted on a common pin.
  • variable valve control that is also the device according to the invention, to keep the adjustment performance low and because this is higher in the loaded state of the device or its sliding joints and joints than in the non-energized state which largely closed valve
  • an adjustment is provided according to the invention essentially during the common rest phases of all valves to be adjusted together. These are derived from the signal from the crankshaft and the camshaft and become shorter and shorter the more valves are adjusted together. Their number is therefore limited.
  • the joint adjustment of the intake and exhaust valves of only one cylinder results in long, easy-to-adjust rest phases.
  • it also enables individual load control of the individual cylinders with an adjustment strategy according to the invention such that the torques of the individual cylinders are regulated for each load state of the overall engine. This is particularly important in the lower load range for quiet engine operation, since the valve lifts do not normally correspond sufficiently due to tolerances.
  • the signals required for this adjustment strategy are also supplied by the crankshaft angle encoder and assigned to the individual cylinders by the camshaft angle encoder.
  • the largely independent adjustment of the inlet and outlet valves offers the possibility of switching off selected valves by means of a continuous adjustment shaft, that is to say no longer opening or at least setting a smaller valve lift.
  • sections of the described cam disks of the adjusting shaft are designed as a catch for the valves that cannot be switched off.
  • the latching area is a contour which is formed from a circular arc concentric with the center of rotation of the adjusting shaft.
  • Fig. 2 shows a cross section using the parts shown in Fig.1 with a pendulum support and adjusting shaft
  • Fig. 3 is a perspective view of the device according to the invention with a pendulum support and the bolt as an adjusting shaft
  • Fig. 4 shows a cross section through the device with four-bar linkage and adjusting shaft
  • FIG. 5 is a perspective view of the device of FIG .. 4
  • Fig. 6 shows a cross section through the device with slide, adjusting shaft and adjusting motor
  • Fig. 7 shows schematically the interaction of engine management, accelerator pedal, angle encoder, adjusting motors and battery.
  • Fig. 1 shows a camshaft 1 which carries a cam 2. This moves the roller 3 in the end region of the intermediate member 4.
  • the intermediate member 4 has a control cam 5, which is composed of a latching region 5a and a lifting region 5b.
  • the intermediate member 4 is mounted on a bolt 6, the axis 7 of which is guided on an arc-shaped adjusting curve 8.
  • the center of the arc-shaped adjustment curve 8 lies on the axis 9 of the roller 10 of the output member 1 1, which is supported via a joint 1 2 in the housing, not shown, and actuates the valve 1 3. It is clearly evident that an adjustment of the axis 7 on the adjustment curve 8 in the direction of the arrow 14 results in a reduction in the opening angle and stroke of the valve 1 3.
  • Fig. 2 shows an embodiment in which the bolt 6 or its axis 7 is guided in a form-fitting manner on the circular-arc-shaped adjustment curve 8 by a pendulum support 15.
  • the cylinder head-side joint 1 6 of the pendulum support 1 5 or its axis coincides with the axis 9 of the roller 1 0 of the output member 1 1.
  • the adjusting shaft 1 7 carries cams 1 8, which determine the position of the bolt 6 or its axis 7 on the adjusting curve 8 via tappet 1 8a.
  • An adjustment of the axis 7 on the adjustment curve 8, as represented by the directional arrow 14, is caused by a rotation of the cam disk 1 8 or the adjustment shaft 17 in accordance with the directional arrow 14a.
  • the adjustment movement described results in a reduction in the stroke and opening angle of the valve 13.
  • Fig. 3 shows a perspective view of the device according to the invention with a pendulum support 15 for inlet valve 19 and outlet valve 20 of a cylinder, picked out from a series of cylinders or valves.
  • the cylinder head-side joint 1 6 of the pendulum support 1 5 is clearly visible, the axis of which coincides with the axis 9 of the rollers 10 of the output members 11, so that the bolt 6 is positively guided on an arc-shaped adjustment curve.
  • the Bolt 6 according to the invention simultaneously the function of the adjusting shaft. He carries the cams 1 8, which are supported on the attached, hardened sliders 21 and is rotatable in the pendulum support.
  • the bolt 6 is connected to the adjusting motor 23 fixed to the housing via a suitable connecting element.
  • an articulated shaft 22 serves as a connecting element.
  • This embodiment offers considerable advantages with regard to the variety of parts, but also space in the area of the actual valve control. Since other connecting elements, such as Schmitt couplings, Oldham couplings, toothed and chain gears, can also be used in addition to cardan shafts, there is a certain flexibility for accommodating the adjusting motor 23.
  • Fig. 4 shows a further embodiment according to the invention for a valve or. Cylinder arrangement as in Fig. 3 in cross section.
  • the pin 6 is positively guided by four-bar linkages (24, 25, 26, 27) on an adjustment curve 28 which comes close to a circular arc shape. If the system lines 29 and 30 meet on the axis 9 of the roller 10 of the output member 11, the instantaneous center of rotation of the bolt is even there. The deviations in the remaining area must be absorbed by the game compensation element 31.
  • the bolt 6 could assume the function of an adjusting shaft, as shown in FIG. 3. However, as shown, a separate adjusting shaft 17 with cams 18 can also be used.
  • the embodiment shown is particularly suitable for a pre-assembly of valves including springs, levers and play compensation elements in the cylinder head as the lower housing part and a complete pre-assembly of all other parts in the control housing as the upper part.
  • the bearing blocks 32 for the joints 24 and 26 can be screwed in the same plane as the cover 33 of the camshaft bearing.
  • FIG. 5 shows a perspective illustration of the device according to FIG. 4.
  • Inlet valve 19 and outlet valve 20 of the cylinder picked out can be seen better, as well as the direct actuation of the pin 6 by the cam. venusionn 1 8. It can be clearly seen that not only the bolt 6 and the camshaft 1 in the upper part of the housing, the control housing, can be preassembled, but also the adjusting shaft 1 7.
  • FIG. 6 shows a cross section through an embodiment according to the invention using a slide 34, which can be used separately for each valve or pair of valves. Due to the separate application, the longest possible rest phases or common rest phases result, so that an adjustment is only possible during the rest phases. The separate arrangement is even necessary for the regulation of the individual cylinders according to the invention.
  • the bolt 6 is guided in a form-fitting manner in the housing by the slide 34, so that its axis 7 is guided along the adjustment curve 35, a straight line. This straight line only approximates a circular arc about the axis 9 of the roller 10 of the stationary output member 11 more or less well. 6, the deviation is exaggerated.
  • the adjusting shaft 17 and the cam disc 1 8 rotate according to the arrow 38b and the slide 34 together with the bolt 6 in the direction 38c. Due to the deviation of the straight line 35 from the circular arc shape, the play compensation element 31 must sink in by a certain amount, which is represented by the arrow 38d.
  • FIG. 7 schematically shows the interaction of accelerator pedal 40, adjustment motors 23, angle of rotation sensor 42 on the flywheel and angle of rotation sensor 43 on the camshaft with engine management 44.
  • a signal emanating from accelerator pedal 40 or a sensor for its position is input by engine management 44 Signal to the actuators 23 converted to increase or decrease the valve lifts.
  • the engine management 44 evaluates the signals of the high-resolution rotation angle sensor 42 on the flywheel. These will assigned to the individual cylinders with the aid of the low-resolution angle of rotation sensor 43 on the camshaft or on another shaft running at half the crankshaft speed.
  • signals are sent to the individual adjusting motors 23 for leveling the torque peaks or the crankshaft speed by correcting the valve strokes of the cylinders with smaller torques upwards and those of the cylinders with larger torques downwards.
  • adjustment takes place, with or without compensation, during the common rest phases of the valves operated by an adjustment motor.
  • the engine management 44 also takes their phase position from the sensor 43 on the camshaft.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)

Abstract

The invention relates to a device for the variable actuation of gas exchange valves for internal combustion engines, wherein at least one cam ( 2 ) pertaining to a camshaft ( 1 ) mounted in a housing rotates according to the engine speed. The cam ( 2 ) first drives an intermediate member ( 4 ) which performs a clear oscillating, rotary movement and has a rotational axis ( 7 ) that can be displaced in the housing parallel to itself along a curve of displacement ( 8 ), said intermediate member comprising a control cam ( 5 ) having a lifting region ( 5 b) and actuating an output member ( 11 ) that, in turn, actuates at least one valve ( 13 ). The aim of the invention is to enable one such device to be reliably controlled. To this end, the control cam ( 5 ) has a catch region ( 5 a), and the intermediate member ( 4 ) is mounted on a bearing having an axis which corresponds to the rotational axis ( 7 ), said bearing being arranged in such a way that it is guided in a forced manner and can be displaced parallel to the curve of displacement ( 8, 28, 35 ), by means of an articulation ( 16, 24, 26 ) connected to the cylinder head or the housing or by a slide ( 34 ) that is guided in the housing in a positively locking manner. The invention also relates to a method for operating an internal combustion engine comprising a plurality of cylinders using at least one of the inventive devices.

Description

Vorrichtung zur variablen Betätigung der Gaswechselventile von Verbrennungsmotoren und Verfahren zum Betreiben einer derartigen Vorrichtung Device for variable actuation of the gas exchange valves of internal combustion engines and method for operating such a device
Beschreibungdescription
Die Erfindung betrifft eine Vorrichtung zur variablen Betätigung der Gaswechselventile von Verbrennungsmotoren entsprechend dem Oberbegriff des Anspruchs 1 .The invention relates to a device for variable actuation of the gas exchange valves of internal combustion engines according to the preamble of claim 1.
Derartige Vorrichtungen dienen dazu, die Steuerung von Gaswechselventilen so zu gestalten, dass es möglich wird, Hubkolbenmotoren ohne die sonst übliche Drosselklappe zu betreiben.Such devices are used to design the control of gas exchange valves so that it becomes possible to operate reciprocating engines without the otherwise usual throttle valve.
Eine derartige Vorrichtung ist beispielsweise aus der DE 1 01 23 1 86 A1 bekannt. Bei dieser Vorrichtung treibt ein umlaufender Nocken zunächst ein Zwischenglied an, welches eine oszillierende, reine Drehbewegung ausführt und eine Steuerkurve trägt, die aus einem Rastbereich und einem Hubbereich zusammengesetzt ist. Die Steuerkurve überträgt die zur Betätigung des Ventils notwendige Hubkurve auf die Rolle eines schlepphebelartigen Abtriebsgliedes, welches seinerseits das Ventil betätigt. Die gewünschten unterschiedlichen Ventilhubkurven werden dadurch erzeugt, dass das Drehzentrum des Zwischengliedes auf einer kreisbogenförmigen Bahn verschoben wird, die zur Rolle des Abtriebsgliedes in deren Lage bei geschlossenem Ventil konzentrisch ist. Das Drehzentrum wird durch eine am Zwischenglied vorgesehene Rolle gebildet, die sich auf eine kreisbogenförmige Laufbahn im Gehäuse kraftschlüssig abstützt, die ebenfalls zur Rolle des Abtriebsgliedes konzentrisch liegt, also eine Aquidistante zur Bahn des Drehzentrums bildet und die als Kulisse bezeichnet wird. Zusätzlich stützt sich die am Zwischenglied angebrachte Rolle an einer Kurvenscheibe ab, deren Winkelstellung die Lage des Drehzentrums auf seiner kreisbogenförmigen Bahn festlegt. Der Vorrichtung nach dem Stand der Technik haften allerdings noch einige Nachteile an.Such a device is known for example from DE 1 01 23 1 86 A1. In this device, a rotating cam first drives an intermediate link, which carries out an oscillating, pure rotary movement and carries a control cam, which is composed of a latching area and a stroke area. The control curve transfers the stroke curve required to actuate the valve to the role of a rocker arm-like output member, which in turn actuates the valve. The desired different valve lift curves are generated in that the center of rotation of the intermediate member is shifted on an arc-shaped path which is concentric with the role of the output member in its position when the valve is closed. The center of rotation is formed by a roller provided on the intermediate member, which is non-positively supported on an arc-shaped track in the housing, which is also concentric with the role of the output member, that is forms an aquidistante to the path of the turning center and which is called the backdrop. In addition, the roller attached to the intermediate link is supported on a cam disc, the angular position of which determines the position of the center of rotation on its arc-shaped path. However, the prior art device still has some disadvantages.
Zunächst liegt die am Zwischenglied angebrachte Rolle an der Kulisse nur dann an, wenn die Gas- und assenkräfte des Ventiltriebs entsprechend gerichtet sind und sich die Rolle an der Kulisse tatsächlich abstützt. Ist dies nicht der Fall, was etwa bei Überdrehzahl geschehen kann, so geht der Kraftschluss verloren und es tritt ein Abheben ein, was beim erneuten Aufsetzen zu Geräuschen und sogar zu Schäden führen kann. Hinzu kommt die verhältnismäßig schwierige Bearbeitung der Kulissen als Segmente eines Innenzylinders, die nicht durchgängig bearbeitet werden können und die ungenügende Härte gängiger Gehäusewerkstoffe für den Rolle-Kulisse-Kontakt. Bezüglich der Montage besteht ein Nachteil darin, dass das Steuergehäuse nicht komplett vormontiert auf den Zγlinderkopf aufgesetzt werden kann.First of all, the roller attached to the intermediate link only bears against the link if the gas and ace forces of the valve train are directed accordingly and the role is actually supported on the link. If this is not the case, which can happen at overspeed, the frictional connection is lost and lifting takes place, which can lead to noise and even damage when it is replaced. Added to this are the relatively difficult machining of the scenes as segments of an inner cylinder, which cannot be processed continuously, and the inadequate hardness of common housing materials for the roller-scenery contact. With regard to assembly, there is a disadvantage that the control housing cannot be completely pre-assembled on the cylinder head.
Es sind weitere Vorrichtungen der gattungsgemäßen Art bekannt geworden, bei welchen der Drehmittelpunkt der vom Nocken angetriebenen Zwischenglieder auf einer Kreisbahn verstellt werden soll (OS 1 95 32 334 A1 ; EP 071 7 1 74 A1 ; DE 1 01 64 493 A1 ) . Die Vorveröffentlichungen enthalten jedoch keine Lehre zur konstruktiven Realisierung einer derartigen Verstellung.Other devices of the generic type have become known in which the center of rotation of the intermediate elements driven by the cam is to be adjusted on a circular path (OS 1 95 32 334 A1; EP 071 7 1 74 A1; DE 1 01 64 493 A1). However, the previous publications do not contain any teaching on the constructive implementation of such an adjustment.
Allen bekannten Vorrichtungen ist der Nachteil gemeinsam, dass toleranzbedingt die Ventilhübe für die einzelnen Zylinder relativ immer unterschiedlicher ausfallen, je weiter diese zum Zwecke einer Laststeuerung herabgesetzt werden. Die der vorliegenden Erfindung zugrunde liegende Aufgabe besteht darin, eine Vorrichtung zu schaffen, welche die Nachteile nach dem Stand der Technik vermeidet und eine sicherere Steuerung erlaubt.All known devices have the disadvantage in common that, due to tolerances, the valve strokes for the individual cylinders turn out to be relatively different the further they are reduced for the purpose of load control. The object on which the present invention is based is to provide a device which avoids the disadvantages of the prior art and permits more reliable control.
Diese Aufgabe wird mit den Merkmalen des Anspruchs 1 gelöst. Vorteilhafte Aus- und Weiterbildungen sind in den Ansprüchen 2 bis 20 beschrieben. Ein Verfahren zum Betreiben einer Brennkraftmaschine mit mehreren Zylindern unter Verwendung einer oder mehrerer erfindungsgemäßer Vorrichtungen wird in den Ansprüchen 21 , 22 und 23 aufgezeigt.This object is achieved with the features of claim 1. Advantageous training and further developments are described in claims 2 to 20. A method for operating an internal combustion engine with a plurality of cylinders using one or more devices according to the invention is set out in claims 21, 22 and 23.
Die Lösung sieht vor, dass die Drehmittelpunkte der vom Nocken angetriebenen Zwischenglieder durch Zwangsführungen, also formschlüssig auf der Verstellkurve geführt sind. Damit wird sichergestellt, dass der Drehmittelpunkt eines Zwischengliedes die Verstellkurve nicht verlassen kann, sodass Geräusche und Schäden, die auf ein Verlassen zurückzuführen wären, vermieden werden. Dieses Merkmal wird konstruktiv vorzugsweise dadurch realisiert, dass ein oder mehrere Zwischenglieder auf einem zylindrischen Bolzen, auf dessen Achse die Drehmittelpunkte liegen, gelagert sind und dass die Achse des Bolzens zwangsläufig auf der Verstellkurve geführt ist. Sofern die Wirkfläche am Abtriebsglied, auf welche die Steuerkurve des Zwischengliedes dessen Bewegung überträgt, kreiszylindrisch ist, also z.B. durch eine Rolle gebildet wird, ist von einer kreisbogenförmigen Verstellkurve auszugehen, deren Mittelpunkt mit dem Mittelpunkt der kreiszylindrischen Wirkfläche bzw. der Rolle zusammenfällt.The solution provides that the centers of rotation of the intermediate elements driven by the cam are guided by positive guides, that is to say in a form-fitting manner on the adjustment curve. This ensures that the center of rotation of an intermediate link cannot leave the adjustment curve, so that noises and damage that could be attributed to leaving are avoided. In terms of design, this feature is preferably realized in that one or more intermediate links are mounted on a cylindrical bolt, on the axis of which the centers of rotation lie, and that the axis of the bolt is inevitably guided on the adjustment curve. If the active surface on the output member, to which the control cam of the intermediate member transmits its movement, is circular-cylindrical, e.g. is formed by a roller, a circular arc-shaped adjustment curve can be assumed, the center of which coincides with the center of the circular cylindrical active surface or the roller.
Eine solche Verstellkurve wird nach einem weiteren, erfindungsgemäßen Vorschlag durch Pendelstützen realisiert, die über ihr jeweils erstes Gelenk mit dem Zylinderkopf bzw. dem Steuergehäuse verbunden sind und mit ihrem jeweils zweiten Gelenk mit dem Bolzen. Dabei fällt die den zylinderkopfseitigen Gelenken gemeinsame Achse mit der Achse der genannten, zylindrischen Wirk¬ flächen am Abtriebsglied zusammen, die der bolzenseitigen Gelenke mit der Bolzenachse. Auf diese Weise wird erreicht, dass der Kraftfluss ausschließlich über flächige Berührstellen auf kürzestem Wege vom Bolzen zum Zylinderkopf bzw. zum Steuergehäuse verläuft. Insbesondere werden keine Kräfte über Hertzsche Pressung auf Zylinderkopf bzw. Steuergehäuse übertragen.Such an adjustment curve is realized according to a further proposal according to the invention by pendulum supports which are connected via their respective first joint to the cylinder head or the control housing and with their respective second joint to the bolt. Here, the cylinder head side the joints common axis coincides with the axis of said cylindrical active surfaces ¬ on the driven member along which the bolt-side joints with the Pin axis. In this way it is achieved that the power flow runs exclusively over flat contact points in the shortest possible way from the pin to the cylinder head or to the control housing. In particular, no forces are transmitted to the cylinder head or control housing via Hertzian pressure.
Falls zwischen den Abtriebsgliedern benachbarter Ventile, seien diese schlepp- hebelartig ausgebildet oder gerade geführt, nicht genügend Bauraum für die obige Lösung zur Verfügung steht, so kann der Bolzen bzw. seine Achse erfindungsgemäß auch mit aus Pendelstützen gebildeten Gelenkvierecken auf der Verstellkurve zwangsgeführt werden. Die auf diese Weise realisierbare Verstellkurve kommt der Kreisbogenform nahe und erfüllt diese im Auslegungspunkt exakt, wenn die Systemlinien sich im Mittelpunkt des Kreisbogens treffen. Die Abweichungen außerhalb des Auslegungspunktes werden durch hydraulische Spielausgleichselemente aufgenommen, die an den schlepphebelarti- gen oder auch geradegeführten Abtriebsgliedern vorzusehen sind.If there is not enough space available for the above solution between the output members of adjacent valves, whether they are designed as drag levers or just guided, the bolt or its axis can also be positively guided on the adjustment curve with articulated quadrilaterals formed from pendulum supports. The adjustment curve that can be realized in this way comes close to the shape of a circular arc and fulfills this exactly at the design point when the system lines meet at the center of the circular arc. The deviations outside the design point are absorbed by hydraulic lash adjusters, which are to be provided on the rocker arm-like or straight-guided output links.
In einer dritten Ausführungsform der erfindungsgemäßen Vorrichtung ist die Führung des Bolzens durch einen im Steuergehäuse linear verstellbaren Schieber vorgesehen. Mit dieser Ausführungsform können weitere, spezielle Bauraumanforderungen erfüllt werden. Es sind verhältnismäßig große Berührflächen zwischen Schieber und Steuergehäuse zu realisieren, sodass die Festigkeitseigenschaften des Gehäusematerials auf jeden Fall ausreichen. Als Verstellkurve ergibt sich eine Gerade, deren Abweichungen von der Kreisbogenform ebenfalls durch die Spielausgleichselemente aufgenommen werden.In a third embodiment of the device according to the invention, the pin is guided by a slide that is linearly adjustable in the control housing. With this embodiment, further, special installation space requirements can be met. Relatively large contact surfaces between the slide and the control housing are to be realized, so that the strength properties of the housing material are sufficient in any case. A straight line results as an adjustment curve, the deviations of which from the circular arc shape are also taken up by the play compensation elements.
Bei allen drei Ausführungsformen wird die Lage des Bolzens bzw. seiner Achse auf der jeweiligen Verstellkurve vorzugsweise durch die direkte oder indirekte Anlage an einer oder mehreren Kurvenscheiben festgelegt, die drehfest verbunden auf einer oder mehreren Verstellwellen angebracht sind. In einer weiteren Ausführungsform sind die Kurvenscheiben an einer axial verschiebbaren Verstellachse angebracht. Die Verstellwelle bzw. die Verstellachse kann ihrer- seits über ein geeignetes Getriebe bzw. ein Verbindungselement von einem Verstellmittel, beispielsweise einem Verstellmotor, verdreht bzw. verschoben werden. Selbstverständlich kann die Verstellung auch durch Hydraulikelemente erfolgen. Im Falle der Führung des Bolzens durch einen linear verstellbaren Schieber kann die Verstellung vom Verstellmotor aus auch direkt über eine mit Bewegungsgewinde versehene Spindel erfolgen.In all three embodiments, the position of the bolt or its axis on the respective adjustment curve is preferably determined by direct or indirect contact with one or more cam disks, which are attached in a rotationally fixed manner to one or more adjustment shafts. In a further embodiment, the cams are attached to an axially displaceable adjustment axis. The adjusting shaft or the adjusting axis can on the one hand, by means of a suitable gear or a connecting element, of an adjusting means, for example an adjusting motor, are rotated or displaced. The adjustment can of course also be carried out by hydraulic elements. If the bolt is guided by a linearly adjustable slide, the adjustment can also be made directly from the adjusting motor via a spindle provided with a movement thread.
Ferner ist allen Ausführungsformen gemeinsam, dass die Zwischenglieder bzw. deren Nockenrollen durch besondere Federn mit den Nocken in Kontakt gehalten werden müssen. Dies wird anhand der Situation bei Nullhub, die bei Zylinderabschaltung vorliegt, unmittelbar einsichtig.Furthermore, it is common to all embodiments that the intermediate links or their cam rollers must be kept in contact with the cams by means of special springs. This is immediately apparent from the situation at zero stroke, which occurs when the cylinder is deactivated.
Eine hinsichtlich Bauraum und Teilevielfalt besonders vorteilhafte Variante der drei Ausführungsformen besteht darin, den Bolzen, auf dem die Zwischenglieder gelagert sind, gleichzeitig als Verstellwelle auszubilden, indem er mit Kurvenscheiben versehen, drehbar in den Pendelstützen, dem Gelenkviereck oder dem Schieber gelagert und von einem Verstellmittel, beispielsweise einem Verstellmotor, entsprechend der gewünschten Ventilhubkurve verdreht wird. Bei dieser Variante müssen im Steuergehäuse Gleitstücke für die Kurvenscheiben aus einem Material erhöhter Festigkeit vorgesehen werden. Da der Verstellmotor in der Regel gehäusefest angeordnet sein wird, der Bolzen bzw. die Steuerwelle sich aber bei der Verstellbewegung parallel zu sich selbst verlagert, muss zwischen beiden ein Verbindungselement angeordnet werden, welches diese Verlagerung zulässt. Dieses kann je nach Bauraumbedingungen eine Gelenkwelle, eine Schmidt-Kupplung, eine Oldham-Kupplung oder auch ein Zahnrad- oder Kettengetriebe sein. Bei hydraulischer Betätigung bietet sich auch ein Hebelmechanismus an.A particularly advantageous variant of the three embodiments in terms of installation space and variety of parts is to simultaneously design the bolt on which the intermediate members are mounted as an adjusting shaft by providing cam discs, rotatably mounted in the pendulum supports, the four-bar linkage or the slide and by an adjusting means , for example an adjusting motor, is rotated in accordance with the desired valve lift curve. In this variant, slide pieces for the cam disks made of a material of increased strength must be provided in the control housing. Since the adjustment motor will generally be fixed to the housing, but the bolt or the control shaft moves parallel to itself during the adjustment movement, a connecting element must be arranged between the two, which permits this displacement. Depending on the installation space, this can be a cardan shaft, a Schmidt clutch, an Oldham clutch or a gear or chain gear. A lever mechanism is also suitable for hydraulic actuation.
Die erfindungsgemäße Vorrichtung kann einschließlich eines Versteilmotors bzw. einer Versteilvorrichtung für jedes Ventil eines Motors separat vorgesehen werden, sodass beliebige Kombinationen von Ventilhüben bzw. Öffnungs- winkeln der einzelnen Ventile eines Motors möglich sind, einschließlich der Abschaltung einzelner Zylinder. In der Regel wird man aber eine gemeinsame Verstellung mehrerer Ventile vorsehen. Dies gilt insbesondere bei mehrventiligen Motoren für die Ein- und Auslassventile eines Zylinders. Beispielsweise können zwei Einlassventile von einem Nocken über ein Zwischenglied betätigt werden, welches für jedes Ventil eine Steuerkurve aufweist. Da nur ein Zwischenglied und nur ein Bolzen vorhanden ist, werden beide Ventile gemeinsam und gleichartig verstellt. Erfindungsgemäß können an dem gemeinsamen Zwischenglied aber auch zwei unterschiedliche Steuerkurven vorgesehen werden mit dem Ergebnis unterschiedlicher Hubkurven an beiden Ventilen trotz gemeinsamer Verstellung. Diese Variante eröffnet insbesondere im untersten Lastbereich die Möglichkeit der Öffnung nur noch eines der beiden Ventile. Der besondere Vorteil dieser Möglichkeit liegt darin, dass im untersten Lastbereich sehr kleine Querschnitte freigegeben werden müssen und sich diese genauer einhalten lassen, wenn sie nur durch ein Ventil freigegeben werden. Zusätzlich besteht die Möglichkeit, durch die Öffnung nur eines der Einlassventile einen Drall der Zylinderladung zu erzeugen. Die Möglichkeiten der Erzeugung unterschiedlicher Ventilhubkurven für zwei Ein- oder auch Auslassventile eines Zylinders werden erfindungsgemäß dadurch erweitert, dass zwei unterschiedliche Nocken und zwei Zwischenglieder mit unterschiedlichen Steuerkurven verwendet werden. Dennoch können beide Ventile gemeinsam verstellt werden, da die beiden Zwischenglieder auf einem gemeinsamen Bolzen gelagert sein können.The device according to the invention, including an adjusting motor or an adjusting device, can be provided separately for each valve of an engine, so that any combinations of valve strokes or opening angles of the individual valves of an engine are possible, including the deactivation of individual cylinders. As a rule, however, a common adjustment of several valves will be provided. This applies particularly to multi-valve engines for the intake and exhaust valves of a cylinder. For example, two intake valves can be actuated by a cam via an intermediate link which has a control curve for each valve. Since there is only one intermediate link and only one pin, both valves are adjusted together and in the same way. According to the invention, however, two different control curves can also be provided on the common intermediate link, with the result of different lift curves on both valves despite the common adjustment. This variant opens the possibility of opening only one of the two valves, particularly in the lowest load range. The particular advantage of this option is that very small cross-sections must be released in the lowest load range and these can be adhered to more precisely if they are only released by a valve. In addition, there is the possibility of generating a swirl of the cylinder charge by opening only one of the intake valves. The possibilities of generating different valve lift curves for two intake or exhaust valves of a cylinder are expanded according to the invention in that two different cams and two intermediate links with different control curves are used. Nevertheless, both valves can be adjusted together, since the two intermediate links can be mounted on a common pin.
Es ist weiter möglich, die Zwischenglieder einer größeren Zahl parallel liegender Ventile gemeinsam durch einen Verstellmotor bzw. Mechanismus zu verstellen, insbesondere dann, wenn diese auf einen gemeinsamen Bolzen gelagert sind.It is also possible to adjust the intermediate links of a larger number of parallel valves together by means of an adjusting motor or mechanism, in particular if they are mounted on a common pin.
Da es für die Akzeptanz einer variablen Ventilsteuerung, also auch der erfindungsgemäßen Vorrichtung von großer Bedeutung ist, die Verstellleistung gering zu halten und weil diese im belasteten Zustand der Vorrichtung bzw. deren Gleitfugen und Gelenke höher ist als im kraftfreien Zustand, der bei geschlossenem Ventil weitgehend vorliegt, ist erfindungsgemäß eine Verstellung im Wesentlichen während der gemeinsamen Ruhephasen aller gemeinsam zu verstellender Ventile vorgesehen. Diese werden vom Signal der Kurbelwelle und der Nockenwelle abgeleitet und werden immer kürzer, je mehr Ventile gemeinsam verstellt werden. Deren Zahl ist also begrenzt.Since it is of great importance for the acceptance of a variable valve control, that is also the device according to the invention, to keep the adjustment performance low and because this is higher in the loaded state of the device or its sliding joints and joints than in the non-energized state which largely closed valve, an adjustment is provided according to the invention essentially during the common rest phases of all valves to be adjusted together. These are derived from the signal from the crankshaft and the camshaft and become shorter and shorter the more valves are adjusted together. Their number is therefore limited.
Die gemeinsame Verstellung der Ein- bzw. Auslassventile jeweils nur eines Zylinders ergeben lange, verstellfreundliche Ruhephasen. Sie ermöglicht aber auch eine individuelle Laststeuerung der einzelnen Zylinder mit einer erfindungsgemäßen Verstellstrategie derart, dass für jeden Lastzustand des Gesamtmotors die Drehmomente der einzelnen Zylinder geregelt werden. Dies ist insbesondere im unteren Lastbereich für einen ruhigen Motorlauf wesentlich, da toleranzbedingt die Ventilhübe normalerweise nicht genügend übereinstimmen. Die für diese Verstellstrategie erforderlichen Signale werden ebenfalls vom Drehwinkelgeber der Kurbelwelle geliefert und vom Drehwinkelgeber der Nockenwelle den einzelnen Zylindern zugeordnet.The joint adjustment of the intake and exhaust valves of only one cylinder results in long, easy-to-adjust rest phases. However, it also enables individual load control of the individual cylinders with an adjustment strategy according to the invention such that the torques of the individual cylinders are regulated for each load state of the overall engine. This is particularly important in the lower load range for quiet engine operation, since the valve lifts do not normally correspond sufficiently due to tolerances. The signals required for this adjustment strategy are also supplied by the crankshaft angle encoder and assigned to the individual cylinders by the camshaft angle encoder.
Die weitgehend unabhängige Verstellung der Ein- bzw. Auslassventile bietet die Möglichkeit mittels einer durchgehenden Verstellwelle ausgewählte Ventile abzuschalten, also nicht mehr zu öffnen oder zumindest einen kleineren Ventilhub einzustellen. Hierzu werden Abschnitte der beschriebenen Kurvenscheiben der Verstellwelle bei den nicht abzuschaltenden Ventilen als Rast ausgebildet. Der Rastbereich ist eine Kontur, welche aus einem zur Drehmitte der Verstellwelle konzentrischen Kreisbogen gebildet wird. Bei Verdrehung der Verstellwelle wird der Ventilhub der von den Kurvenscheiben mit Rast gesteuerten Einheiten innerhalb des Wirkungsbereiches der Rast nicht verändert, während der Ventilhub der von den Kurvenscheiben ohne Rast gesteuerten Einheiten verändert wird. Diese Veränderung kann bis zum vollständigen Geschlossenhalten des Ventils ausgeführt werden. Werden alle Einlassventile oder/und Auslassventile des gleichen Zylinders auf diese Weise angesteuert, wird der Ladungswechsel für ausgewählte Zylinder ausgesetzt. Selbstverständlich wird durch Verwendung eines gerade geführten Ziehkeils mit entsprechender Nockenkontur die gleiche Funktion erreicht. Der Rastbereich ist dann eine Kontur, welche aus einem zur Schieberichtung des Ziehkeils Parallelen gebildet wird.The largely independent adjustment of the inlet and outlet valves offers the possibility of switching off selected valves by means of a continuous adjustment shaft, that is to say no longer opening or at least setting a smaller valve lift. For this purpose, sections of the described cam disks of the adjusting shaft are designed as a catch for the valves that cannot be switched off. The latching area is a contour which is formed from a circular arc concentric with the center of rotation of the adjusting shaft. When the adjustment shaft is rotated, the valve stroke of the units controlled by the cam disks with detent is not changed within the effective range of the detent, while the valve stroke of the units controlled by the cam disks without detent is changed. This change can be made until the valve is completely closed. If all intake valves and / or exhaust valves of the same cylinder are actuated in this way, the charge exchange for selected cylinders is suspended. It goes without saying achieves the same function by using a straight wedge with a corresponding cam contour. The latching area is then a contour which is formed from a parallel to the sliding direction of the drawing wedge.
Durch die erfindungsgemäße Lösung wurde vorteilhaft eine exakte, verschleißarme Versteileinrichtung für Gaswechselventile gefunden, die darüber hinaus mit großer Genauigkeit arbeitet.By means of the solution according to the invention, an exact, low-wear adjusting device for gas exchange valves has advantageously been found, which also works with great accuracy.
Die Erfindung wird anhand von Zeichnungen einiger Ausführungsbeispiele näher erläutert. Es zeigtThe invention is explained in more detail with the aid of drawings of some exemplary embodiments. It shows
Fig. 1 die in den Kraftfluss von der Nockenwelle zum Ventil eingeschalteten, beweglichen Teile der erfindungsgemäßen VorrichtungFig. 1 in the power flow from the camshaft to the valve, moving parts of the device according to the invention
Fig. 2 einen Querschnitt unter Verwendung der in Fig.1 dargestellten Teile mit Pendelstütze und VerstellwelleFig. 2 shows a cross section using the parts shown in Fig.1 with a pendulum support and adjusting shaft
Fig. 3 eine perspektivische Darstellung der erfindungsgemäßen Vorrichtung mit Pendelstütze und dem Bolzen als VerstellwelleFig. 3 is a perspective view of the device according to the invention with a pendulum support and the bolt as an adjusting shaft
Fig. 4 einen Querschnitt durch die Vorrichtung mit Gelenkviereck und VerstellwelleFig. 4 shows a cross section through the device with four-bar linkage and adjusting shaft
Fig. 5 eine perspektivische Darstellung der Vorrichtung nach Fig. 45 is a perspective view of the device of FIG .. 4
Fig. 6 einen Querschnitt durch die Vorrichtung mit Schieber, Verstellwelle und VerstellmotorFig. 6 shows a cross section through the device with slide, adjusting shaft and adjusting motor
Fig. 7 schematisch das Zusammenwirken von Motormanagement, Gaspedal, Drehwinkelgeber, VerStellmotoren und Batterie. Fig. 1 zeigt eine Nockenwelle 1 , die einen Nocken 2 trägt. Dieser bewegt die Rolle 3 im Endbereich des Zwischengliedes 4. Das Zwischenglied 4 weist eine Steuerkurve 5 auf, die aus einem Rastbereich 5a und einem Hubbereich 5b zusammengesetzt ist. Das Zwischenglied 4 ist auf einem Bolzen 6 gelagert, dessen Achse 7 auf einer kreisbogenförmigen Verstellkurve 8 geführt ist. Der Mittelpunkt der kreisbogenförmigen Verstellkurve 8 liegt auf der Achse 9 der Rolle 10 des Abtriebsgliedes 1 1 , welches sich über ein Gelenk 1 2 im nicht dargestellten Gehäuse abstützt und das Ventil 1 3 betätigt. Es ist klar ersichtlich, dass eine Verstellung der Achse 7 auf der Verstellkurve 8 in Richtung des Pfeils 14 eine Verringerung von Öffnungswinkel und Hub des Ventils 1 3 zur Folge hat.Fig. 7 shows schematically the interaction of engine management, accelerator pedal, angle encoder, adjusting motors and battery. Fig. 1 shows a camshaft 1 which carries a cam 2. This moves the roller 3 in the end region of the intermediate member 4. The intermediate member 4 has a control cam 5, which is composed of a latching region 5a and a lifting region 5b. The intermediate member 4 is mounted on a bolt 6, the axis 7 of which is guided on an arc-shaped adjusting curve 8. The center of the arc-shaped adjustment curve 8 lies on the axis 9 of the roller 10 of the output member 1 1, which is supported via a joint 1 2 in the housing, not shown, and actuates the valve 1 3. It is clearly evident that an adjustment of the axis 7 on the adjustment curve 8 in the direction of the arrow 14 results in a reduction in the opening angle and stroke of the valve 1 3.
Fig. 2 zeigt eine Ausführungsform, bei der der Bolzen 6 bzw. dessen Achse 7 durch eine Pendelstütze 1 5 formschlüssig auf der kreisbogenförmigen Verstellkurve 8 geführt ist. Das zylinderkopfseitige Gelenk 1 6 der Pendelstütze 1 5 bzw. dessen Achse fällt mit der Achse 9 der Rolle 1 0 des Abtriebsgliedes 1 1 zusammen. Die Verstellwelle 1 7 trägt Kurvenscheiben 1 8, die über Stößel 1 8a die Lage des Bolzens 6 bzw. seiner Achse 7 auf der Verstellkurve 8 festlegen. Eine Verstellung der Achse 7 auf der Verstellkurve 8, wie durch den Richtungspfeil 14 dargestellt, wird durch eine Verdrehung der Kurvenscheibe1 8 bzw. der Verstellwelle 1 7 entsprechend dem Richtungspfeil 14a hervorgerufen. Die beschriebene Verstellbewegung hat eine Verringerung von Hub und Öffnungswinkel des Ventils 1 3 zur Folge.Fig. 2 shows an embodiment in which the bolt 6 or its axis 7 is guided in a form-fitting manner on the circular-arc-shaped adjustment curve 8 by a pendulum support 15. The cylinder head-side joint 1 6 of the pendulum support 1 5 or its axis coincides with the axis 9 of the roller 1 0 of the output member 1 1. The adjusting shaft 1 7 carries cams 1 8, which determine the position of the bolt 6 or its axis 7 on the adjusting curve 8 via tappet 1 8a. An adjustment of the axis 7 on the adjustment curve 8, as represented by the directional arrow 14, is caused by a rotation of the cam disk 1 8 or the adjustment shaft 17 in accordance with the directional arrow 14a. The adjustment movement described results in a reduction in the stroke and opening angle of the valve 13.
Fig. 3 zeigt eine perspektivische Darstellung der erfindungsgemäßen Vorrichtung mit Pendelstütze 1 5 für Einlassventil 1 9 und Auslassventil 20 eines Zylinders, herausgegriffen aus einer Reihe von Zylindern bzw. Ventilen. Gut zu erkennen ist das zylinderkopfseitige Gelenk 1 6 der Pendelstütze 1 5, dessen Achse mit der Achse 9 der Rollen 1 0 der Abtriebsglieder 1 1 zusammenfällt, sodass der Bolzen 6 auf einer kreisbogenförmigen Verstellkurve zwangsgeführt ist. Im Unterschied zu der Ausführungsform nach Fig. 2 übernimmt hier der Bolzen 6 erfindungsgemäß gleichzeitig die Funktion der Verstellwelle. Er trägt die Kurvenscheiben 1 8, die sich auf im Gehäuse angebrachte, gehärtete Gleitstücke 21 abstützen und ist in der Pendelstütze drehbar. Über ein geeignetes Verbindungselement ist der Bolzen 6 mit dem gehäusefesten Verstellmotor 23 verbunden. Im vorliegenden Beispiel dient eine Gelenkwelle 22 als Verbindungselement. Diese Ausführungsform bietet erhebliche Vorteile bezüglich Teilevielfalt, aber auch Bauraum im Bereich der eigentlichen Ventilsteuerung. Da außer Gelenkwellen auch andere Verbindungselemente, wie Schmitt-Kupplungen, Oldham-Kupplungen, Zahn- und Kettgetriebe in Frage kommen, ist eine gewisse Flexibilität für die Unterbringung des Versteilmotors 23 gegeben.Fig. 3 shows a perspective view of the device according to the invention with a pendulum support 15 for inlet valve 19 and outlet valve 20 of a cylinder, picked out from a series of cylinders or valves. The cylinder head-side joint 1 6 of the pendulum support 1 5 is clearly visible, the axis of which coincides with the axis 9 of the rollers 10 of the output members 11, so that the bolt 6 is positively guided on an arc-shaped adjustment curve. In contrast to the embodiment according to FIG. 2, the Bolt 6 according to the invention simultaneously the function of the adjusting shaft. He carries the cams 1 8, which are supported on the attached, hardened sliders 21 and is rotatable in the pendulum support. The bolt 6 is connected to the adjusting motor 23 fixed to the housing via a suitable connecting element. In the present example, an articulated shaft 22 serves as a connecting element. This embodiment offers considerable advantages with regard to the variety of parts, but also space in the area of the actual valve control. Since other connecting elements, such as Schmitt couplings, Oldham couplings, toothed and chain gears, can also be used in addition to cardan shafts, there is a certain flexibility for accommodating the adjusting motor 23.
Fig. 4 zeigt eine weitere, erfindungsgemäße Ausführungsform für eine Ventilbzw. Zylinderanordnung wie in Fig. 3 im Querschnitt. Hier wird der Bolzen 6 durch Gelenkvierecke (24, 25, 26, 27) auf einer Verstellkurve 28 zwangsgeführt, die einer Kreisbogenform nahe kommt. Treffen sich die Systemlinien 29 und 30 auf der Achse 9 der Rolle 10 des Abtriebsgliedes 1 1 , so liegt der Momentandrehpol des Bolzens sogar genau dort. Die Abweichungen im übrigen Bereich müssen vom Spielausgleichselement 31 aufgenommen werden. Auch hier könnte der Bolzen 6 die Funktion einer Verstellwelle übernehmen, wie in Fig. 3 gezeigt. Es kann aber auch, wie gezeigt, eine separate Verstellwelle 1 7 mit Kurvenscheiben 1 8 angewendet werden. Die gezeigte Ausführungsform ist besonders geeignet für eine Vormontage von Ventilen samt Federn, Hebeln und Spielausgleichselementen im Zylinderkopf als Gehäuseunterteil und eine komplette Vormontage aller übrigen Teile im Steuergehäuse als Oberteil. In dieser Hinsicht ist es vorteilhaft, dass die Lagerböcke 32 für die Gelenke 24 und 26 in der gleichen Ebene verschraubt werden können wie der Deckel 33 des Nockenwellenlagers.Fig. 4 shows a further embodiment according to the invention for a valve or. Cylinder arrangement as in Fig. 3 in cross section. Here, the pin 6 is positively guided by four-bar linkages (24, 25, 26, 27) on an adjustment curve 28 which comes close to a circular arc shape. If the system lines 29 and 30 meet on the axis 9 of the roller 10 of the output member 11, the instantaneous center of rotation of the bolt is even there. The deviations in the remaining area must be absorbed by the game compensation element 31. Here, too, the bolt 6 could assume the function of an adjusting shaft, as shown in FIG. 3. However, as shown, a separate adjusting shaft 17 with cams 18 can also be used. The embodiment shown is particularly suitable for a pre-assembly of valves including springs, levers and play compensation elements in the cylinder head as the lower housing part and a complete pre-assembly of all other parts in the control housing as the upper part. In this regard, it is advantageous that the bearing blocks 32 for the joints 24 and 26 can be screwed in the same plane as the cover 33 of the camshaft bearing.
Fig. 5 zeigt eine perspektivische Darstellung der Vorrichtung nach Fig. 4. Es sind Einlassventil 1 9 und Auslassventil 20 des herausgegriffenen Zylinders besser zu erkennen, sowie die direkte Betätigung des Bolzens 6 durch die Kur- venscheiben 1 8. Deutlich zu erkennen ist, dass nicht nur der Bolzen 6 und die Nockenwelle 1 im Gehäuseoberteil, dem Steuergehäuse vormontiert werden können, sondern auch die Verstellwelle 1 7.FIG. 5 shows a perspective illustration of the device according to FIG. 4. Inlet valve 19 and outlet valve 20 of the cylinder picked out can be seen better, as well as the direct actuation of the pin 6 by the cam. venscheiben 1 8. It can be clearly seen that not only the bolt 6 and the camshaft 1 in the upper part of the housing, the control housing, can be preassembled, but also the adjusting shaft 1 7.
Fig. 6 zeigt einen Querschnitt durch eine erfindungsgemäße Ausführungsform unter Benutzung eines Schiebers 34, die separat für jedes Ventil oder jedes Ventilpaar eingesetzt werden kann. Auf Grund der separaten Anwendung ergeben sich die längstmöglichen Ruhephasen bzw. gemeinsamen Ruhephasen, sodass eine Verstellung nur während der Ruhephasen leicht möglich ist. Für die erfindungsgemäße Regelung der einzelnen Zylinder ist die separate Anordnung sogar notwendig. Der Bolzen 6 wird bei dieser Ausführungsform durch den Schieber 34 formschlüssig im Gehäuse geführt, sodass seine Achse 7 entlang der Verstellkurve 35, einer Geraden, geführt wird. Diese Gerade nähert einen Kreisbogen um die Achse 9 der Rolle 10 des ruhenden Abtriebsgliedes 1 1 nur mehr oder weniger gut an. In der Fig. 6 ist die Abweichung übertrieben dargestellt. Dreht sich nun die vom Verstellmotor 23 angetriebene Gewindespindel 36 und verschiebt die Zahnstange 37 um den durch den Pfeil 38a dargestellten Betrag, so dreht sich die Verstellwelle 1 7 und die Kurvenscheibe 1 8 entsprechend dem Pfeil 38b und Schieber 34 samt Bolzen 6 in Richtung 38c. Auf Grund der Abweichung der Geraden 35 von der Kreisbogenform muss das Spielausgleichselement 31 um einen bestimmten Betrag einsinken, der durch den Pfeil 38d dargestellt ist.FIG. 6 shows a cross section through an embodiment according to the invention using a slide 34, which can be used separately for each valve or pair of valves. Due to the separate application, the longest possible rest phases or common rest phases result, so that an adjustment is only possible during the rest phases. The separate arrangement is even necessary for the regulation of the individual cylinders according to the invention. In this embodiment, the bolt 6 is guided in a form-fitting manner in the housing by the slide 34, so that its axis 7 is guided along the adjustment curve 35, a straight line. This straight line only approximates a circular arc about the axis 9 of the roller 10 of the stationary output member 11 more or less well. 6, the deviation is exaggerated. If the threaded spindle 36 driven by the adjusting motor 23 rotates and displaces the rack 37 by the amount represented by the arrow 38a, the adjusting shaft 17 and the cam disc 1 8 rotate according to the arrow 38b and the slide 34 together with the bolt 6 in the direction 38c. Due to the deviation of the straight line 35 from the circular arc shape, the play compensation element 31 must sink in by a certain amount, which is represented by the arrow 38d.
Fig. 7 zeigt schematisch das Zusammenwirken von Fahrpedal 40, Verstell- motoren 23, Drehwinkelsensor 42 am Schwungrad und Drehwinkelsensor 43 an der Nockenwelle mit dem Motormanagement 44. Ein vom Fahrpedal 40 bzw. einem Sensor für dessen Stellung ausgehendes Signal wird vom Motormanagement 44 in ein Signal an die VerStellmotoren 23 zur Erhöhung oder Erniedrigung der Ventilhübe gewandelt. Nach Erreichen des gewünschten Last- zustandes für den Gesamtmotor wertet das Motormanagement 44 die Signale des hochauflösenden Drehwinkelsensors 42 am Schwungrad aus. Diese wer- den mit Hilfe des niedrig auflösenden Drehwinkelsensors 43 an der Nockenwelle oder an einer anderen, mit halber Kurbelwellendrehzahl laufenden Welle, den einzelnen Zylindern zugeordnet. Mit diesen Informationen gehen Signale an die einzelnen VerStellmotoren 23 zur Nivellierung der Drehmomentspitzen oder der Kurbelwellendrehzahl, in dem die Ventilhübe der Zylinder mit kleineren Drehmomenten nach oben korrigiert werden und diejenigen der Zylinder mit größeren Drehmomenten nach unten. Erfindungsgemäß findet eine Verstellung, ob mit oder ohne Ausgleich, während der gemeinsamen Ruhephasen der von einem Verstellmotor bedienten Ventile statt. Deren Phasenlage entnimmt das Motormanagement 44 dem Sensor 43 an der Nockenwelle nebenbei. 7 schematically shows the interaction of accelerator pedal 40, adjustment motors 23, angle of rotation sensor 42 on the flywheel and angle of rotation sensor 43 on the camshaft with engine management 44. A signal emanating from accelerator pedal 40 or a sensor for its position is input by engine management 44 Signal to the actuators 23 converted to increase or decrease the valve lifts. After reaching the desired load state for the entire engine, the engine management 44 evaluates the signals of the high-resolution rotation angle sensor 42 on the flywheel. These will assigned to the individual cylinders with the aid of the low-resolution angle of rotation sensor 43 on the camshaft or on another shaft running at half the crankshaft speed. With this information, signals are sent to the individual adjusting motors 23 for leveling the torque peaks or the crankshaft speed by correcting the valve strokes of the cylinders with smaller torques upwards and those of the cylinders with larger torques downwards. According to the invention, adjustment takes place, with or without compensation, during the common rest phases of the valves operated by an adjustment motor. The engine management 44 also takes their phase position from the sensor 43 on the camshaft.
BezugszeichenlisteLIST OF REFERENCE NUMBERS
1 Nockenwelle1 camshaft
2 Nocken2 cams
3 Rolle3 roll
4 Zwischenglied4 intermediate link
5 Steuerkurve a Rastbereich5 control cam a rest area
5b Hubbereich5b stroke range
6 Bolzen6 bolts
7 Achse7 axis
8 Verstellkurve8 adjustment curve
9 Achse9 axis
10 Rolle10 roll
11 Abtriebsglied11 output link
12 Gelenk12 joint
13 Ventil13 valve
14 Pfeil14 arrow
14a Richtungspfeil14a directional arrow
15 Pendelstütze15 pendulum support
16 Gelenk16 joint
17 Verstellwelle17 adjustment shaft
18 Kurvenscheibe18 cam
18a Stößel18a plunger
19 Einlassventil19 inlet valve
20 Auslassventil20 exhaust valve
21 Gleitstück21 slider
22 Gelenkwelle22 PTO shaft
23 Verstellmotor23 adjusting motor
24 Gelenkviereck24 quadrilateral joint
25 Gelenkviereck Gelenkviereck25 quadrilateral joint bar linkage
Gelenkviereckbar linkage
Verstell kurveAdjustment curve
Systemliniesystem line
Systemliniesystem line
SpielausgleichselementLash adjuster
Lagerbockbearing block
Deckelcover
Schieberpusher
Verstellkurveadjustment curve
Gewindespindelscrew
Zahnstange a Pfeil b Pfeil c Richtung d PfeilRack a arrow b arrow c direction d arrow
Fahrpedalaccelerator
Dreh winkelsensorRotation angle sensor
DrehwinkelsensorRotation angle sensor
Motormanagement engine management

Claims

Patentansprüche claims
1. Vorrichtung zur variablen Betätigung von Gaswechselventilen für Verbrennungsmotoren, bei welcher sich ein oder mehrere Nocken (2) einer in einem Gehäuse gelagerten Nockenwelle (1 ) abhängig von der Motordrehzahl drehen, der Nocken (2) zunächst ein Zwischenglied (4) antreibt, welches eine oszillierende, reine Drehbewegung ausführt, dessen Drehachse (7) im Gehäuse parallel zu sich selbst entlang einer Verstellkurve (8) verschiebbar ist, das eine Steuerkurve (5) mit einem Rastbereich (5a) und einem Hubbereich (5b) aufweist, und über diese Steuerkurve (5) ein Abtriebsglied (1 1 ) betätigt, das seinerseits mindestens ein Ventil (1 3) betätigt, dadurch gekennzeichnet, dass das Zwischenglied (4) auf einer Lagerung mit einer Achse entsprechend der Drehachse (7) gelagert, diese Lagerung über ein mit dem Zylinderkopf oder dem Gehäuse verbundenes Gelenk (1 6, 24, 26) oder einen formschlüssig im Gehäuse geführten Schieber (34) zwangsgeführt und parallel auf der Verstellkurve (8, 28, 35) verschiebbar angebracht ist.1.Device for variable actuation of gas exchange valves for internal combustion engines, in which one or more cams (2) of a camshaft (1) mounted in a housing rotate depending on the engine speed, the cams (2) first drive an intermediate member (4), which executes an oscillating, pure rotary movement, the axis of rotation (7) of which can be displaced in the housing parallel to itself along an adjustment curve (8), which has a control curve (5) with a latching region (5a) and a stroke region (5b), and via this Control cam (5) actuates an output member (1 1), which in turn actuates at least one valve (1 3), characterized in that the intermediate member (4) is mounted on a bearing with an axis corresponding to the axis of rotation (7), this bearing via with the cylinder head or the housing connected joint (1 6, 24, 26) or a positively guided slide (34) in the housing and guided in parallel on the adjustment curve (8, 28, 35) is slidably attached.
2. Vorrichtung nach Anspruch 1 , dadurch gekennzeichnet, dass das Zwischenglied (4) auf einem Bolzen (6) gelagert ist, dessen Achse (7) die Drehachse des Zwischengliedes (4) ist.2. Device according to claim 1, characterized in that the intermediate member (4) is mounted on a bolt (6) whose axis (7) is the axis of rotation of the intermediate member (4).
3. Vorrichtung nach den Ansprüchen 1 oder 2, dadurch gekennzeichnet, dass der Bolzen (6) durch Pendelstützen (1 5) mit dem Gehäuse verbunden und seine Achse (7) auf einer kreisbogenförmigen Verstellkurve (8) geführt wird.3. Device according to claims 1 or 2, characterized in that the bolt (6) by pendulum supports (1 5) connected to the housing and its axis (7) is guided on an arc-shaped adjustment curve (8).
4. Vorrichtung nach den Ansprüchen 1 oder 2, dadurch gekennzeichnet, dass der Bolzen (6) durch Gelenkvierecke (24, 25, 26, 27) mit dem Gehäuse verbunden und seine Achse (7) auf einer annähernd kreisbogenförmigen Verstellkurve (28) geführt wird.4. Device according to claims 1 or 2, characterized in that the bolt (6) by four-bar linkages (24, 25, 26, 27) with the Connected housing and its axis (7) is guided on an approximately circular arc-shaped adjustment curve (28).
5. Vorrichtung nach den Ansprüchen 1 oder 2, dadurch gekennzeichnet, dass der Bolzen (6) über den formschlüssig im Gehäuse geführten Schieber (34) mit dem Gehäuse verbunden ist und seine Achse (7) auf einer Geraden (35) geführt wird.5. Device according to claims 1 or 2, characterized in that the bolt (6) via the positively guided in the housing slide (34) is connected to the housing and its axis (7) is guided on a straight line (35).
6. Vorrichtung nach einem oder mehreren der Ansprüche 3 bis 5, dadurch gekennzeichnet, dass ein hydraulisches Spielausgleichselement (31 ) am Abtriebsglied (1 1 ) angeordnet ist.6. The device according to one or more of claims 3 to 5, characterized in that a hydraulic play compensation element (31) is arranged on the output member (1 1).
7. Vorrichtung nach einem oder mehreren der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass die Position des Bolzens (6) bzw. seiner Achse (7) direkt oder indirekt auf der Verstellkurve (8, 28, 35) mittels mindestens einer Kurvenscheibe (1 8) oder eines Nockens eingestellt wird und sich der Bolzen (6) bzw. seine Achse (7) bezüglich der Verstellkurve (8, 28, 35) im Wesentlichen in tangentialer Richtung gegenüber dem Gehäuse abstützt.7. The device according to one or more of claims 1 to 6, characterized in that the position of the bolt (6) or its axis (7) directly or indirectly on the adjusting curve (8, 28, 35) by means of at least one cam (1 8) or a cam and the bolt (6) or its axis (7) is supported with respect to the adjustment curve (8, 28, 35) essentially in the tangential direction with respect to the housing.
8. Vorrichtung nach einem oder mehreren der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass eine Hydraulikeinheit dem Bolzen (6) bzw. seiner Achse (7) direkt oder indirekt die jeweils verlangte Position auf der Verstellkurve (8, 28, 35) vorgibt und diesen bezüglich der Verstellkurve (8, 28, 35) in tangentialer Richtung gegenüber dem Gehäuse abstützt.8. The device according to one or more of claims 1 to 6, characterized in that a hydraulic unit the bolt (6) or its axis (7) directly or indirectly specifies the required position on the adjustment curve (8, 28, 35) and supports it with respect to the adjustment curve (8, 28, 35) in the tangential direction with respect to the housing.
9. Vorrichtung nach einem oder mehreren der Ansprüche 1 bis 7, dadurch gekennzeichnet, dass die zu verdrehenden Kurvenscheiben (1 8) auf einer Verstellwelle (1 7) angeordnet sind, welche über einen Verstellmotor (23) und, sofern erforderlich, ein Getriebe verstellt wird. 9. The device according to one or more of claims 1 to 7, characterized in that the cam discs to be rotated (1 8) are arranged on an adjusting shaft (1 7), which via an adjusting motor (23) and, if necessary, adjusts a gear becomes.
10. Vorrichtung nach einem der Ansprüche 1 , 2 oder 5 bis 9, gekennzeichnet durch einen Verstellmotor (23) und eine Gewindespindel (36), die den Schieber (34) in die jeweils verlangte Position bringt.10. Device according to one of claims 1, 2 or 5 to 9, characterized by an adjusting motor (23) and a threaded spindle (36) which brings the slide (34) into the position required in each case.
11. Brennkraftmaschine, umfassend mehrere Vorrichtungen nach einem oder mehreren der Ansprüche 1 bis 10, wobei jedem Motorventil separat eine der Vorrichtungen zugeordnet ist.11. Internal combustion engine, comprising a plurality of devices according to one or more of claims 1 to 10, wherein each engine valve is assigned to one of the devices separately.
12. Brennkraftmaschine, umfassend mindestens eine Vorrichtung nach einem oder mehreren der Ansprüche 1 bis 1 0, wobei jeweils zwei benachbarten, parallelen Ventilen eines Zylinders eine Vorrichtung separat zugeordnet ist.12. Internal combustion engine, comprising at least one device according to one or more of claims 1 to 1 0, wherein two adjacent, parallel valves of a cylinder, a device is assigned separately.
13. Vorrichtung nach Anspruch 1 2, gekennzeichnet durch ein gemeinsames Zwischenglied (4) mit zwei verschiedenen Steuerkurven für die beiden Ventile.13. The apparatus of claim 1 2, characterized by a common intermediate member (4) with two different control cams for the two valves.
14. Vorrichtung nach Anspruch 1 2, gekennzeichnet durch zwei verschiedene Nocken (2) und zwei Zwischenglieder (4) mit unterschiedlichen Steuerkurven für die beiden Ventile.14. The apparatus according to claim 1 2, characterized by two different cams (2) and two intermediate members (4) with different control cams for the two valves.
15. Vorrichtung nach einem oder mehreren der Ansprüche 1 bis 1 4, dadurch gekennzeichnet, dass die Getriebeglieder so ausgelegt sind, dass es mindestens eine Verstellposition für das verschiebbare Zwischenglied (4) gibt, in der während des Umlaufens der Nocken (2) mindestens ein Ventil (1 3) geschlossen bleibt.15. The device according to one or more of claims 1 to 1 4, characterized in that the transmission members are designed so that there is at least one adjustment position for the displaceable intermediate member (4), in which at least one during the rotation of the cams (2) Valve (1 3) remains closed.
16. Vorrichtung nach einem oder mehreren der Ansprüche 1 bis 10, gekennzeichnet durch die gemeinsame, zusammengefasste Betätigung der Ventile mehrerer Zylinder und einen gemeinsamen, durchgehenden Bolzen (6) für alle Zwischenglieder (4) dieser Ventile. 16. The device according to one or more of claims 1 to 10, characterized by the common, combined actuation of the valves of a plurality of cylinders and a common, continuous bolt (6) for all intermediate members (4) of these valves.
17. Vorrichtung nach einem oder mehreren der Ansprüche 1 bis 10 oder 1 6, dadurch gekennzeichnet, dass der Bolzen (6) seitens seiner Führung frei drehbar ist, dass er drehfest verbunden eine oder mehrere der Kurvenscheiben (1 8) trägt und dass er über ein geeignetes Verbindungselement von einem Verstellmotor (23) verdreht werden kann und sich die Kurvenscheiben (1 8) gegenüber dem Gehäuse abstützen.17. The device according to one or more of claims 1 to 10 or 1 6, characterized in that the bolt (6) is freely rotatable on the part of its guide, that it carries one or more of the cams (1 8) in a rotationally fixed manner and that it is about a suitable connecting element can be rotated by an adjusting motor (23) and the cams (1 8) are supported against the housing.
18. Vorrichtung nach Anspruch 1 7, dadurch gekennzeichnet, dass sich die Kurvenscheiben (18) an im Gehäuse vorgesehenen Gleitstücken (21 ) aus einem Material erhöhter Härte abstützen.18. The apparatus according to claim 1 7, characterized in that the cams (18) are supported on sliders (21) provided in the housing and made of a material of increased hardness.
19. Brennkraftmaschine, umfassend mehrere Vorrichtungen nach einem oder mehreren der Ansprüche 1 bis 9 oder 1 6 bis 1 8, gekennzeichnet durch eine gemeinsame Verstellwelle (1 7), welche mindestens eine Kurvenscheibe (1 8) pro Vorrichtung aufweist und die Kurvenscheibe (1 8) für mindestens eine Vorrichtung einen Abschnitt aufweist, in welchem bei Verdrehung der Verstellwelle (1 7) keine Veränderung der Position dieser Vorrichtung erfolgt und die Kurvenscheibe (1 8) bei mindestens einer anderen Vorrichtung während dieser Verdrehung der Verstellwelle (1 7) eine Veränderung der Position dieser anderen Vorrichtung bewirkt.19. Internal combustion engine, comprising a plurality of devices according to one or more of claims 1 to 9 or 1 6 to 1 8, characterized by a common adjusting shaft (1 7), which has at least one cam (1 8) per device and the cam (1 8 ) for at least one device has a section in which when the adjusting shaft (1 7) is rotated there is no change in the position of this device and the cam disc (1 8) in at least one other device during this rotation of the adjusting shaft (1 7) there is a change in the Position of this other device causes.
20. Brennkraftmaschine, umfassend mehrere Vorrichtungen nach einem oder mehreren der Ansprüche 1 bis 9 oder 1 6 bis 1 8, gekennzeichnet durch eine gemeinsame Verstellwelle (1 7), welche mindestens einen Nocken pro Vorrichtung aufweist und die Nockenkontur für mindestens eine Vorrichtung einen Abschnitt aufweist, in welchem bei Verschiebung der Verstellwelle (1 7) keine Veränderung der Position dieser Vorrichtung erfolgt und die Nockenkontur bei mindestens einer anderen Vorrichtung während dieser Verschiebung der Verstell welle (1 7) eine Veränderung der Position dieser anderen Vorrichtung bewirkt. 20. Internal combustion engine, comprising a plurality of devices according to one or more of claims 1 to 9 or 1 6 to 1 8, characterized by a common adjusting shaft (1 7) which has at least one cam per device and the cam contour for at least one device has a section , in which when the adjusting shaft (1 7) is moved there is no change in the position of this device and the cam contour in at least one other device during this displacement of the adjusting shaft (1 7) causes a change in the position of this other device.
21. Verfahren zum Betreiben einer Brennkraftmaschine mit mehreren Zylindern unter Verwendung einer oder mehrerer Vorrichtungen nach einem oder mehreren der Ansprüche 1 bis 20, dadurch gekennzeichnet, dass nach Erreichen eines gewünschten Lastzustandes für den Gesamtmotor21. A method for operating an internal combustion engine with a plurality of cylinders using one or more devices according to one or more of claims 1 to 20, characterized in that after reaching a desired load state for the entire engine
a) Drehwinkelsignale der Kurbelwelle mit einem ersten Drehwinkelsensor (42) am Schwungrad aufgenommen und von einem Motormanagement (44) ausgewertet werden, um Drehungleichförmigkeiten der Kurbelwelle und/oder Drehmomentspitzen zu detektieren, b) diese mit Hilfe eines zweiten, an der Nockenwelle oder an einer anderen mit halber Kurbelwellendrehzahl laufenden Welle angeordneten Drehwinkelsensors (43) den einzelnen Zylindern zugeordnet werden, und c) mit diesen Informationen Signale erzeugt werden, die an einzelne Antriebe zur Nivellierung der Drehmomentenspitzen und/oder der Kurbelwellendrehzahl gehen, wobei die Nivellierung erreicht wird, indem die Ventilhübe der Zylinder mit kleineren Drehmomenten nach oben korrigiert werden und diejenigen der Zylinder mit größeren Drehmomenten nach unten.a) rotation angle signals of the crankshaft are recorded with a first rotation angle sensor (42) on the flywheel and evaluated by an engine management (44) in order to detect rotational irregularities of the crankshaft and / or torque peaks, b) these with the aid of a second one, on the camshaft or on one another rotation angle sensor (43) arranged at half crankshaft speed are assigned to the individual cylinders, and c) this information is used to generate signals which go to individual drives for leveling the torque peaks and / or the crankshaft speed, the leveling being achieved by the Valve strokes of the cylinders with smaller torques are corrected upwards and those of the cylinders with larger torques downwards.
22. Verfahren zum Betreiben einer Brennkraftmaschine mit mehreren Zylindern unter Verwendung einer oder mehrerer Vorrichtungen nach einem oder mehreren der Ansprüche 1 bis 20, dadurch gekennzeichnet, dass a) jedem Zylinder eine separate Vorrichtung und ein Antrieb zur Betätigung der Vorrichtung zugeordnet sind, b) die Phasenlage der Ruhephasen der einzelnen von einem Antrieb bedienten Ventile ermittelt wird, und c) die Verstellbewegungen der jeweiligen Vorrichtungen während der gemeinsamen Ruhephasen der von dem jeweiligen Antrieb bedienten Ventile stattfinden.22. A method for operating an internal combustion engine with a plurality of cylinders using one or more devices according to one or more of claims 1 to 20, characterized in that a) a separate device and a drive for actuating the device are assigned to each cylinder, b) the Phase position of the rest phases of the individual valves operated by a drive is determined, and c) the adjustment movements of the respective devices take place during the common rest phases of the valves operated by the respective drive.
23. Verfahren nach Anspruch 23, dadurch gekennzeichnet, dass die Phasenlage der Ruhephasen der einzelnen von einem Antrieb bedienten Ventile durch ein Motormanagement (44) aus dem Signal eines an der Nockenwelle angeordneten Drehwinkelsensors (43) ermittelt wird. 23. The method according to claim 23, characterized in that the phase position of the rest phases of the individual valves operated by a drive is determined by an engine management system (44) from the signal of a rotation angle sensor (43) arranged on the camshaft.
EP04721181A 2003-03-24 2004-03-17 Device for the variable actuation of the gas exchange valves of internal combustion engines, and method for operating one such device Expired - Lifetime EP1608851B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10312959 2003-03-24
DE10312959A DE10312959B4 (en) 2003-03-24 2003-03-24 Device for the variable actuation of gas exchange valves of internal combustion engines
PCT/EP2004/002743 WO2004085804A1 (en) 2003-03-24 2004-03-17 Device for the variable actuation of the gas exchange valves of internal combustion engines, and method for operating one such device

Publications (2)

Publication Number Publication Date
EP1608851A1 true EP1608851A1 (en) 2005-12-28
EP1608851B1 EP1608851B1 (en) 2008-10-01

Family

ID=33038742

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04721181A Expired - Lifetime EP1608851B1 (en) 2003-03-24 2004-03-17 Device for the variable actuation of the gas exchange valves of internal combustion engines, and method for operating one such device

Country Status (5)

Country Link
US (1) US7296546B2 (en)
EP (1) EP1608851B1 (en)
AT (1) ATE409801T1 (en)
DE (2) DE10312959B4 (en)
WO (1) WO2004085804A1 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10312961C5 (en) * 2003-03-24 2009-01-29 Thyssenkrupp Presta Teccenter Ag Device for the variable actuation of gas exchange valves of internal combustion engines
DE102005040959A1 (en) * 2005-08-30 2007-03-08 Bayerische Motoren Werke Ag Hubvariabler valve drive for an internal combustion engine
US7363893B2 (en) * 2005-12-05 2008-04-29 Delphi Technologies, Inc. System for variable valvetrain actuation
DE102006022481A1 (en) 2006-05-13 2007-11-15 Bayerische Motoren Werke Ag Cylinder head for an internal combustion engine with a variable-stroke valve drive
JP4766007B2 (en) * 2007-06-14 2011-09-07 トヨタ自動車株式会社 Variable valve gear
US9133735B2 (en) 2013-03-15 2015-09-15 Kohler Co. Variable valve timing apparatus and internal combustion engine incorporating the same
DE102016205805A1 (en) * 2016-04-07 2017-10-12 Bayerische Motoren Werke Aktiengesellschaft Valve drive and motor assembly
CN108068370B (en) * 2017-11-09 2024-01-16 特乐斯特机械(上海)有限公司 Automatic material passing, separating and centering device for tire sidewall belt of tire production line

Family Cites Families (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3261338A (en) * 1964-07-13 1966-07-19 Automobile Racing Club Of Okla Valve timing mechanism
DE2951361A1 (en) * 1979-12-20 1981-07-02 Bayerische Motoren Werke AG, 8000 München Variable-lift IC engine valve actuating gear - has two facing lever arms in actuating train, one with effective length variable
FR2519375B1 (en) * 1981-12-31 1986-07-11 Baguena Michel VARIABLE VALVE FOR FOUR-STROKE ENGINE
DE4209062C1 (en) * 1992-03-20 1993-04-01 Mercedes-Benz Aktiengesellschaft, 7000 Stuttgart, De
DE4326331A1 (en) * 1992-07-15 1995-02-09 Bayerische Motoren Werke Ag Valve gear of an internal combustion engine
DE4223173A1 (en) * 1992-07-15 1994-01-20 Bayerische Motoren Werke Ag Valve mechanism for vehicle IC engine - has different lift curves for each pair of valves per cylinder controlled by roller-actuated eccentrics
EP0717174A1 (en) * 1994-12-12 1996-06-19 Isuzu Motors Limited Valve operating system for internal combustion engine
DE19532334A1 (en) * 1995-09-01 1997-03-06 Bayerische Motoren Werke Ag Variable valve train, especially for internal combustion engines
DE19629349A1 (en) * 1996-07-20 1998-01-22 Dieter Dipl Ing Reitz Valve drive for internal combustion engine
ATE220444T1 (en) * 1999-10-29 2002-07-15 Sts System Technology Services MECHANICAL CONTROL OF THE STROKE ADJUSTMENT OF THE INLET VALVE OF AN INTERNAL COMBUSTION ENGINE
EP1096115B1 (en) * 1999-10-29 2002-07-10 STS System Technology Services GmbH Mechanically controlled intake valve lift in an internal combustion engine
DE19960742B4 (en) * 1999-12-16 2006-09-28 Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr Variable valve train, preferably for internal combustion engines
DE10006015B4 (en) * 2000-02-11 2009-09-17 Schaeffler Kg Variable valve drive for load control of a spark-ignited internal combustion engine
DE10066056B4 (en) * 2000-07-18 2006-02-02 Thyssenkrupp Automotive Ag Hub valve control for engines
DE10046221A1 (en) * 2000-09-19 2002-10-02 Bayerische Motoren Werke Ag Method and device for controlling the cylinder-selective filling in internal combustion engines with variable valve train
EP1205643A1 (en) * 2000-11-13 2002-05-15 Stefan Battlogg Valve drive in an internal combustion engine
DE10106921A1 (en) * 2001-02-15 2002-08-22 Bayerische Motoren Werke Ag Method for synchronizing the filling of cylinders of an internal combustion engine, in particular a reciprocating piston internal combustion engine
DE50103100D1 (en) * 2001-05-03 2004-09-09 Sts System Technology Services Mechanical regulation of the stroke adjustment of the intake valve of an internal combustion engine
DE10123186A1 (en) * 2001-05-12 2002-11-14 Bayerische Motoren Werke Ag Valve gear device for variable lift adjustment is for gas exchange valve of internal combustion engine and has valve vai intermediary of transmission component effectively connected to roller movable around rotary axis
DE10136612A1 (en) * 2001-07-17 2003-02-06 Herbert Naumann Variable lift valve controls
DE10164493B4 (en) * 2001-12-29 2010-04-08 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Device for the variable actuation of the charge exchange valves in reciprocating engines

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2004085804A1 *

Also Published As

Publication number Publication date
DE10312959B4 (en) 2006-10-05
WO2004085804A1 (en) 2004-10-07
DE10312959A1 (en) 2004-11-18
EP1608851B1 (en) 2008-10-01
DE502004008152D1 (en) 2008-11-13
US20060260574A1 (en) 2006-11-23
US7296546B2 (en) 2007-11-20
ATE409801T1 (en) 2008-10-15

Similar Documents

Publication Publication Date Title
DE69921153T2 (en) VARIABLE VALVE CONTROL DEVICE
EP0659232B1 (en) Variable control process and device for an internal combustion engine valve
DE19960742B4 (en) Variable valve train, preferably for internal combustion engines
EP1412621B1 (en) Variable valve-stroke controller
AT408127B (en) Internal combustion engine with at least one camshaft that can be axially displaced by an adjusting device
EP1853797B1 (en) Variable mechanical valve control for an internal combustion engine
DE4301453C2 (en) Variable valve control of internal combustion engines
EP1760278A2 (en) Lift-variable valve-operating system for internal combustion engine
EP1608850B1 (en) Device for the variable actuation of the gas exchange valves of internal combustion engines
EP1608851B1 (en) Device for the variable actuation of the gas exchange valves of internal combustion engines, and method for operating one such device
DE4135257C2 (en) Device for actuating the valves in internal combustion engines by means of rotating cams
EP1608852B1 (en) Device for the variable actuation of gas exchange valves of internal combustion engines and method for operating said device
DE102008027649A1 (en) Valve operation for an internal combustion engine
EP1493902A1 (en) Device for switching off a valve
DE102005048951B4 (en) Diesel engine with four-valve cylinder head and method for swirl control
WO2003078802A1 (en) Method and device for controlling the cylinder charge of an externally ignited internal combustion engine
DE10306154A1 (en) Valve drive mechanism for an internal combustion engine has a drive shaft and cams to rotate coaxially around the drive shaft
DE10237104A1 (en) Valve drive for a piston combustion engine has a variable lift control with transmission and actuator elements fixed together
EP1288451B1 (en) Cylinder head for an internal combustion engine with a variable lift valve controlling device
EP1854967A2 (en) Cylinder head for a combustion engine with a variable stroke valve operating mechanism
EP1276973B1 (en) Control device for an intake valve or exhaust valve of an internal combustion engine
DE20317382U1 (en) Device for variable actuation of gas shuttle valves for internal combustion engines comprises gas shuttle valves of one cylinder in one displacement unit with a displacement that occurs
DE102017200203B4 (en) Sliding piece with pump cam segment
EP1588029B1 (en) Device for actuating the gas exchange valves in reciprocating engines
DE10211969A1 (en) Valve gear for reciprocating piston engine has connecting element in frictional contact with first operating element and form-locking on driven spindle, and with roller between first operating element and connecting element

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20051024

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL LT LV MK

DAX Request for extension of the european patent (deleted)
17Q First examination report despatched

Effective date: 20060201

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: THYSSENKRUPP PRESTA TECCENTER AG

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REF Corresponds to:

Ref document number: 502004008152

Country of ref document: DE

Date of ref document: 20081113

Kind code of ref document: P

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081001

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090101

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090112

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081001

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081001

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090302

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081001

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20090327

Year of fee payment: 6

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081001

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081001

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081001

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081001

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090101

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081001

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081001

26N No opposition filed

Effective date: 20090702

BERE Be: lapsed

Owner name: THYSSENKRUPP PRESTA TECCENTER AG

Effective date: 20090331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081001

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090317

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090102

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100331

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090317

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20090402

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081001

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081001

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20180321

Year of fee payment: 15

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20180323

Year of fee payment: 15

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20190317

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190317

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20190331

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20210319

Year of fee payment: 18

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004008152

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20221001