EP2585687B1 - Arbres à cames pouvant être déphasé - Google Patents

Arbres à cames pouvant être déphasé Download PDF

Info

Publication number
EP2585687B1
EP2585687B1 EP11758091.0A EP11758091A EP2585687B1 EP 2585687 B1 EP2585687 B1 EP 2585687B1 EP 11758091 A EP11758091 A EP 11758091A EP 2585687 B1 EP2585687 B1 EP 2585687B1
Authority
EP
European Patent Office
Prior art keywords
cam
shaft
camshaft
packages
cams
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.)
Active
Application number
EP11758091.0A
Other languages
German (de)
English (en)
Other versions
EP2585687A1 (fr
Inventor
Roman Weinmeister
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.)
Neumayer Tekfor Holding GmbH
Original Assignee
Neumayer Tekfor Holding GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Neumayer Tekfor Holding GmbH filed Critical Neumayer Tekfor Holding GmbH
Publication of EP2585687A1 publication Critical patent/EP2585687A1/fr
Application granted granted Critical
Publication of EP2585687B1 publication Critical patent/EP2585687B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • 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
    • F01L13/0036—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 the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • 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
    • F01L13/0036—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 the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F01L2013/0052—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 the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction with cams provided on an axially slidable sleeve

Definitions

  • the invention relates to an adjustable camshaft, with at least one shaft, and with at least one cam package, which has at least two different cams and / or cam contours.
  • the cams and / or the cam contours of the cam package have different widths.
  • the cam package is designed axially displaceable along a longitudinal axis of the camshaft by at least one adjusting element is provided, which is axially displaceable along the longitudinal axis, and in that the adjusting element is mechanically coupled via at least one contact element with the cam package.
  • a camshaft has at least one carrier element, also referred to as tube or shaft, and at least one cam.
  • camshafts serve as part of the valvetrain, with the support member rotating about its longitudinal axis.
  • the cams convert the rotary motion into longitudinal movements, thereby controlling the intake and exhaust valves of the engine.
  • adjustment possibilities of camshafts for example which bring different cams into operative engagement with the valves or change the settings, eg the angles of the cams relative to one another.
  • camshaft When adjusting the camshaft is in the prior art usually make sure that the cams are adjusted only when the associated valves run on the base circle of the cam, i. if the cams do not actuate the valves. Therefore, the cams must either be individually adjusted or only groups can be formed from at least during a phase non-engaging with the valves cams. In the latter then the adjustment of the cam is made.
  • the invention has for its object to propose an adjustable camshaft, which allows a greater possibility over the prior art at times for adjusting the camshaft and thus also allows different groupings of the cams of different valves or cylinders.
  • the shaft is designed to be axially displaceable along the longitudinal axis of the camshaft, and that at least one cam package is provided which is fixedly connected to the shaft, so that on the adjusting element and the shaft at least two different cam packages independently are adjustable.
  • a correspondingly wide cam or a sufficiently wide cam contour can serve to enable a cam package to be displaced outside the base circle of a cam.
  • cams or cam packs e.g. be moved axially at the same time, even if a cam is currently operating a valve.
  • the cam package and the adjusting element are axially displaceable along the longitudinal axis of the camshaft, so that a displacement of the adjusting element, a displacement of the cam package causes, whereby the different cams or cam contours of the cam package or possibly the cam packages come into contact with the valves.
  • cam packages Since both the shaft axially displaceable along the longitudinal axis and an axially displaceable adjusting element is provided, at least two different groups of cam packages can be formed, which can be adjusted independently.
  • the cam package, which is firmly connected to the shaft, can also have the same or different widths.
  • the adjusting element is arranged within the shaft.
  • An embodiment of the invention provides that a plurality of cam packages are provided and arranged axially displaceable on the shaft, and that at least two of the cam packages mechanically with the Adjustment are coupled.
  • An embodiment of the invention includes that the adjusting element is designed to be rotatable radially about the longitudinal axis of the camshaft. With this configuration, thus still the angular position and thus the phase of the cams can be adjusted to each other.
  • An embodiment of the invention provides that at least one Axialverstelltechnik is provided, which is connected to the adjusting element, and which at least partially axially displaces the adjusting element.
  • An embodiment of the invention includes that a plurality of adjusting elements are provided which are axially displaceable along the longitudinal axis of the camshaft. By a large number of adjusting elements, a corresponding number of cam packages can be controlled and shifted individually or in groups.
  • An embodiment of the invention provides that the adjusting element is configured as a solid cylinder or as a pipe or as a segment of a cylinder or as a segment of a pipe or as a sheet metal part.
  • a camshaft 1 is shown, which is here to control the valves of four cylinders.
  • the invention can also be applied to engines with a different number of cylinders.
  • Each cylinder - not shown here - two valves are associated with it: the valves of the first cylinder 101, the second cylinder 102, the third cylinder 103 and the fourth cylinder 104.
  • each left shown - valve is a single cam 8 on associated with the camshaft 1, which is axially fixedly mounted on the shaft 3.
  • a cam package 2 is provided, which in particular allows a change in the valve lift.
  • both valves of a cylinder can be controlled differently by changing the cams.
  • Shown here is, for example, the camshaft 1 for the intake valves of the cylinder. Accordingly, such a camshaft 1 can also be used for the exhaust valves.
  • the cam packages 2 each have a slide 20, which is axially displaceable on the shaft 3 along the longitudinal axis - shown here in dash-dotted lines. On the
  • Carriage 20 are in this embodiment, a first cam 21 and a second cam 22.
  • the cams 21, 22 differ in terms their outer profile, for example, at the height of the cam-forming elevation or nose, which determines the valve lift (see Fig. 5 the example of the first cam 21 with nose 21.1).
  • the cams 21, 22 have a different course.
  • at least one cam is a one-piece component of the carriage 20, that is, the carriage 20 may itself also have such a cam contour.
  • the axially displaceable carriage 20 is connected to an adjusting element 4 via a contact element 5, which is, for example, a pin connected in the hollow shaft 3 designed.
  • a contact element 5 which is, for example, a pin connected in the hollow shaft 3 designed.
  • each recesses 30, eg grooves in the shaft 3 are provided.
  • the contact elements 5 extend completely through the adjusting element 4 or the shaft 3. Since the adjusting element 4 itself is designed to be axially displaceable, the cam packs 2 can be displaced axially, ie valve activation with the first cam 21 or with the second cam 22 can be caused.
  • the adjusting element 4 is for example a solid shaft, which optionally consists of a plastic or a composite material.
  • the camshaft 1 is driven, for example, by the crankshaft, not shown here.
  • the torque is - in the example shown here - split and transmitted on the one hand on the outer shaft 3 and the fixed thereto single cam 8 and the other via the adjusting element 4 and the contact elements 5.
  • a corresponding mounting of the adjusting element 4 is provided in the shaft 3 or there is a corresponding pinning instead.
  • the cam packages 2 of the valves of the second 102 and the fourth cylinder 104 are moved.
  • fewer or more cam packages 2 can be grouped accordingly.
  • the cams 21, 22 of the cam packages 2 have different widths.
  • the first cam 21 is narrower than the second cam 22 in the cam packets 2 of the first and third cylinders. Conversely, in the cam packets 2 of the first and third cylinders, the first cam 21 is wider than the second cam 22. Due to the greater width of the first cam Cam 21 can thus be made for example for the valve of the first cylinder 101, the adjustment, even if the valve of the first cylinder 101 just outside the base circle runs, ie when the cam presses the valve, for example via a cam follower against a spring and thus the opening of Valve causes. Only when the adjusting element 4 is moved further, that is, beyond the width of the cam also, the conversion of the cam for the valves of the first 101 and third cylinder 103 takes place.
  • the conversion of a cam package from one cam to the other takes place respectively on the base circle, ie when the cams of the associated cam set do not actuate the associated valve, but during the time in which a cam of another cam set actuates a valve, ie outside the base circle for this other cam-valve combination.
  • the arrangement of the wider or narrower cams here refers only to the illustrated example and can be adapted according to the needs of the engine or the type of control of the cylinder. If the torque is transmitted, for example - in a realization, not shown here - only from the outer shaft 3, so can be done on the adjusting element 4 still twisting, so that a phase change is possible.
  • a Radialverformathü 7 is provided for radial change - relative to the crankshaft and / or relative to the cams to each other - a Radialverformathü 7 is provided.
  • the axial displacement of the adjusting element 4 is accomplished - in this example - by the Axialverstelltechnik 6, in which two actuators 60 engage on matching raceways, so that a linear movement of the actuators 60 perpendicular to the longitudinal axis of the adjusting element 4, an axial displacement of the adjusting element 4 in the direction causes the longitudinal axis.
  • the adjusting element 4 is displaced axially so far that in each case a valve 102, 104 no longer comes into contact with the first cam 21, but with the second cam 22.
  • the - here drawing - left actuator 60 is in the example shown here at the beginning of the axial displacement causing path.
  • the second cam 22 is designed for the illustrated variant such that it causes a shutdown of the associated valve by the valve only runs on the base circle of the - nase- or spy-less - cam 22 and thus is not operated.
  • the illustration Fig. 2 shows the state that a valve of the second 102 and the fourth cylinder 104 is turned off - they are respectively in communication with the second cam 22 - and that also one valve of the first 101 and third cylinder 103 is to be turned off.
  • the shaft 3 and the adjusting element 4 have rotated by 90 °, so that now also the grooves 30 with the contact elements 5 to recognize.
  • the contact elements 5 have no radial clearance in the grooves 30, which would allow rotation about the longitudinal axis of the camshaft 3.
  • Other configurations of the grooves 30 will be discussed below.
  • other angles other than the 90 ° angle are still possible. This is dependent on the control of the valves or the required variant of the adjustment of the camshaft 1.
  • the actuator 60 is located at another area of the track in the Axialverstellmaschine 6.
  • the individual cam 8 fixedly mounted on the shaft 3 actuates the left-hand valve of the fourth cylinder 104, with the right-hand valve of the fourth cylinder 104 running over the second cam 22 of the cam assembly 2 on the base circle and thus, as it were, by a neutral position. Hub is controlled.
  • Fig. 4 there was relative to in the Fig. 3 shown state another 90 ° rotation and the adjusting element 4 is axially displaced so far that the corresponding valves of the first cylinder 101 and the third cylinder 103 come into contact with the narrower second cam 22 of the respective associated cam package 2.
  • valves of the first 101 and third cylinder 103 are shut down due to the outer contour of the second cam 22 of the associated cam packages 2 by running on the base circle, so to say with a zero stroke.
  • the actuator 60 is now at the end of the career arrived and a further axial displacement of the adjusting element 4 no longer takes place.
  • a first cam 21 is shown as applied to a carriage of a cam pack.
  • - not shown - is a hollow cam, which has substantially only an outer contour and a mounting surface for the carriage.
  • the cam is a component of the carriage itself.
  • the base circle and the nose or tip 21.1 are shown.
  • Fig. 6 are three variants a) to c) shown for the configuration of a groove 30 in the shaft 3.
  • the torque can be transmitted via the groove 30 or via the inner shaft.
  • the groove 30 is inclined and the contact element is fixed in the end positions.
  • the S-shaped configuration of Fig. 6c) also allows a fixation of the contact element at the end points of the axial movement.
  • the Fig. 7 illustrates a possible career, over which an actuator shifts the adjustment axially by a distance X1 and in the reverse direction to X2. Shown here is the unwound 360 ° -Außen formation eg a wheel as part of Axialverstelltechnik. Essentially, two shifts take place, which in the above example the FIGS. 1 to 4 Initially cause a shutdown of the valves of the second and fourth cylinders and then the valves of the first and third cylinders (sections a). Between these two shutdowns, a portion (in the figure section b) is provided, which causes no axial displacement of the adjusting element. The two illustrated raceways are here to match the arrangement of the actuators of the figures Fig.
  • the raceways are designed mirror-symmetrically to each other, wherein a raceway causes the displacement in one and the other career, the shift back.
  • the mirror-symmetrical design results here from the fact that the actuators are arranged side by side.
  • the shape of the raceways is therefore also dependent on how the Axialverstelltechnik is configured or how the actuators are arranged and initiate the shift.
  • the four sections a, b correspond here in each case to an angular extent of 90 °, corresponding to the representation of FIGS. 1 to 4 , However, other angles are also possible, especially with other cylinder numbers.
  • the two angles for the displacement of the cams - in each case sections a - and the two angles during which no displacement takes place - denoted by b -, in each case the same and different from each other.
  • the number of angles and their sizes also depends on the number of shifts, ie on the number of affected cam packages.
  • Fig. 8 a) and b) two variants for the design of the radial twisting unit 7 are shown.
  • the Radialverformattician 7 is connected to the adjusting element 4 and allows its rotation relative to the outer shaft 3 and thereby changing the phase of the cam.
  • the two variants differ with regard to the implementation of a length compensation, which is necessary by the axial displacement of the adjusting element 4.
  • a special element is provided for this compensation, whereas in the variant of Fig. 8b) the compensation takes place via an inner and an outer toothing of two partial elements of the adjusting element 4.
  • balls which run in grooves between the sections of the elements which are located inside one another and function correspondingly, for example, in a length compensation element in drive shafts.
  • Fig. 9 a is a part of a camshaft with two adjacent cam packages 2 shown, both of which a lifting (different Cam contour of the first 21 and the second cam 22) and a phase change (rotation about the longitudinal axis of the shaft 3) allow.
  • Fig. 9b) and Fig. 9c) two sections through the shaft 3 are shown in different positions.
  • the embodiments in the shaft 3 allow for an axial guidance of the contact element 5 and at the same time still a radial mobility and on the other hand only an axial guidance, ie radially fixed.
  • the Fig. 10 shows a part of a camshaft whose shaft 3 has two different grooves 30 for the contact elements 5. In the variant shown on the left, only an axial displacement is possible, and the - here on the representation - right-side groove additionally allows a radial rotation, since the contact element 5 laterally has place in the groove 30.
  • the camshaft 1 of Fig. 11 allows the switching of three different contours by each cam package 2 has three different cams: first cam 21, second cam 22 and third cam 23.
  • three different profiles for the control of the valves can be applied.
  • the different valve strokes can be seen here at the different heights of the cams of the cam package 2 for the valve of the first cylinder 101.
  • the axial adjustment unit 6 here also schematically has two raceways each, so that a displacement from the first 21 to the second 22 and from the second 22 to the third cam 23 is possible.
  • two - here mirror-symmetrically designed - raceways are provided for the pushing back accordingly two - here mirror-symmetrically designed - raceways are provided.
  • Per valve also different numbers of cams or cam contours can be provided.
  • the shaft 3 and the adjusting element 4 form a unit which is axially displaceable configured and arranged and which also serves to transmit the torque.
  • the cam packages 2 'in this representation each come into contact with a roller tappet, wherein two roller tappets are provided for the respective two valves for each cylinder: the roller tappets of the first cylinder 111, the roller tappets of the second cylinder 112, the roller tappets of the third cylinder 113 and the roller tappet of the fourth cylinder 114.
  • the bearings 120 are shown, on which the camshaft 1 rests in the installed state.
  • the shaft 3 and the adjusting element 4 is axially displaced via the Axialverstelltechnik 6 and the actuators 60 (indicated by the double arrow). Since the cam packages 2 'are fixedly mounted on the shaft 3, the roller tappets 111, 112, 113 and 114 thus also come into contact with the different cams 20, 21 or cam contours of the packages 2'.
  • the cam packages 2 'can - as shown here - consist of individual cams 20, 21, but it can also be a unit with correspondingly different cam contours.
  • a radial twisting unit 7 is provided to rotate the shaft 3 radially about its longitudinal axis for adjusting the phase of the cams.
  • a housing 131 is provided, in which, for example via the teeth axially movable plug 130 is arranged.
  • the plug 130 is non-rotatable, eg connected to the shaft 3 via interference fit.
  • the axial adjustment between plug 130 and housing 131 takes place as a result of the axial displacement of the shaft 3 by a corresponding internal toothing.
  • the housing 131 is mounted axially.
  • the camshaft 1 of Fig. 13 differs thereby from the variant of Fig. 12 in that the shaft 3 is coupled directly to the housing 131, for example via a corresponding toothing, which allows the axial displacement.
  • An axial adjustment is also possible here by means of balls, which are located in raceways between the shaft 3 and the housing 131.
  • the variants of the camshaft 1 of the figures Fig. 12 and Fig. 13 allow only the displacement of all cam packages 2 'at the same time, since all cam packages 2' are fixedly connected to the shaft 3 and with the adjusting element 4 identical to the shaft 3.
  • the displacement while a cam actuates a valve, ie outside the base circle, is due to the different width cam 21, 22 possible.
  • the variants of Fig. 1 to 4 and Fig. 11 allow it further by the adjusting element 4 in conjunction with the shaft 3, that not all cam packages are moved because the cam packages are firmly connected to the different in these embodiments of the shaft 3 adjustment 4. This possibility that individual cams are not moved allows, for example, in the variant of Fig. 1 the use of a single cam 8, which is not changed.
  • Fig. 14 makes it possible to control both valves of each cylinder with different combinations of cam contours.
  • a cam package 2 'for a valve with the shaft 3 and a cam package 2 via the contact element 5 through the groove 30 with the adjusting element 4 is connected.
  • the adjusting element 4 is axially displaced by the Axialverstelltechnik 6 and the actuators 60 and the tube 3 of the Rajaxialverstelltechnik 9 with its associated actuators 90.
  • the Rajaxialverstelltechnik 9 is mounted laterally in this example shown here.
  • crankshaft not shown here - drive the camshaft 1, for example via a - also not shown here - chain.
  • the cam packages 2, which are displaced with the adjusting element 4, are each a unit in this embodiment, which correspondingly has two different cam contours. The adjustment of a cam during actuation of the associated valve by the cam is also made possible by the appropriately wide cam contour.
  • a section of a further variant of the camshaft 1 is shown. It is possible to form four, for example, different sized groups of cam packages 2, which are each adjusted simultaneously.
  • the shaft 3 are for this purpose four adjusting elements 4, which are each connected via contact elements 5 with the individual cam packages 2.
  • the individual adjusting elements 4 are configured, for example, in the form of superimposed carrier strips, such as in the Fig. 15b ).
  • the shaft 3 has, for example, a rectangular free area in its interior, at the longitudinal sides in each case at least one slot or generally a recess for the contact elements 5, which are also configured here as pins, for example.
  • different fixing elements which have the described inner contour or otherwise provide a guide.
  • the adjusting elements 4 For the displacement of the cam packages 2, which are arranged here axially displaceable on the shaft 3, the adjusting elements 4 have grooves 40.
  • the individual adjusting elements 4 For the excerpt of Fig. 15 a) are in the Fig. 15c) the individual adjusting elements 4 arranged side by side.
  • two contact elements 5 - here on the uppermost and the lowest displacement element 4 - are provided which lie at different axial positions. Since the contact elements 5 project completely through the shaft 3 and thus through all adjusting elements 4, the two other adjusting elements 4 at the height of the contact elements 5 each have grooves 40 which allow the axial displacement of the other elements.
  • the individual adjusting elements 4 can be individually offset axially.
  • the axial movements of the individual adjusting elements 4 can be coupled to one another via the grooves of the adjusting elements 40, ie via their configuration and arrangement. Since it is possible in this variant to move individual cam packages 2 targeted, it is not necessary, for example, that the individual cams have different widths, since the shift is preferably on the base circle can be made. However, a combination is also possible to meet any special requirements for the adjustment of the camshaft 1. With the variant shown here, four groups of cam packages can be formed or only individual cam packages can be controlled separately. A different number of groups is also possible, where appropriate, the number of individual here designed flat adjusting elements 4 is to be increased or increased. The variant of the adjusting 4 of the Fig.
  • adjusting element 4 of Fig. 16 Within the shaft 3, an adjusting element 4 is provided here, which consists of - in this example - four segments, which are individually axially displaceable.
  • a possible radial rotation of the individual segments and thus the respectively associated cam packages show the pictures Fig. 17 a) and b).
  • each two opposing segments can be adjusted radially to each other by a space between the adjacent segments, in which - in this embodiment - a fixing element 10 is introduced.
  • the number of segments can be adjusted according to the needs or the number of cylinders.

Landscapes

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

Claims (6)

  1. Arbre à cames réglable (1),
    avec au moins un arbre (3),
    et
    avec au moins un ensemble de cames (2) qui présente au moins deux cames (21, 22) et/ou contours de cames différents,
    les cames (21, 22) et/ou les contours de cames de l'ensemble de cames (2) présentant des largeurs différentes,
    l'ensemble de cames (2) étant configuré mobile axialement le long d'un axe longitudinal de l'arbre à cames (1),
    un élément de réglage (4) au moins, qui est configuré mobile axialement le long de l'axe longitudinal, étant prévu,
    et
    l'élément de réglage (4) étant accouplé mécaniquement à l'ensemble de cames (2) par l'intermédiaire d'au moins un élément de contact (5),
    caractérisé en ce
    que l'arbre (3) est configuré mobile axialement le long de l'axe longitudinal de l'arbre à cames (1),
    et
    qu'au moins un ensemble de cames (2'), qui est relié de façon fixe à l'arbre (3), est prévu,
    de sorte que, par l'intermédiaire de l'élément de réglage (4) et de l'arbre (3), au moins deux ensembles de cames (2, 2') différents sont réglables indépendamment l'un de l'autre.
  2. Arbre à cames selon revendication 1,
    caractérisé en ce
    que plusieurs ensembles de cames (2) sont prévus et placés mobiles axialement sur l'arbre (3),
    et
    qu'au moins deux des ensembles de cames (2) sont accouplés mécaniquement à l'élément de réglage (4).
  3. Arbre à cames (1) selon revendication 1 ou 2,
    caractérisé en ce
    que l'élément de réglage (4) est configuré radialement rotatif autour de l'axe longitudinal de l'arbre à cames (1).
  4. Arbre à cames selon l'une des revendications 1 à 3,
    caractérisé en ce
    qu'au moins qu'une unité de réglage axiale (6), qui est reliée à l'élément de réglage (4) et qui déplace l'élément de réglage (4) axialement par sections au moins,
    est prévue
  5. Arbre à cames selon l'une des revendications 1 à 4,
    caractérisé en ce
    que plusieurs éléments de réglage (4), qui sont configurés mobiles axialement le long de l'axe longitudinal de l'arbre à cames (1), sont prévus.
  6. Arbre à cames (1) selon l'une des revendications 1 à 5,
    caractérisé en ce
    que l'élément de réglage (4) est configuré en tant que cylindre massif ou en tant que tube ou en tant que segment d'un cylindre ou en tant que segment d'un tube ou en tant qu'élément en tôle.
EP11758091.0A 2010-06-25 2011-06-11 Arbres à cames pouvant être déphasé Active EP2585687B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010025100A DE102010025100A1 (de) 2010-06-25 2010-06-25 Verstellbare Nockenwelle
PCT/DE2011/001205 WO2012006992A1 (fr) 2010-06-25 2011-06-11 Arbres à cames pouvant être déphasé

Publications (2)

Publication Number Publication Date
EP2585687A1 EP2585687A1 (fr) 2013-05-01
EP2585687B1 true EP2585687B1 (fr) 2014-09-03

Family

ID=44653920

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11758091.0A Active EP2585687B1 (fr) 2010-06-25 2011-06-11 Arbres à cames pouvant être déphasé

Country Status (4)

Country Link
US (1) US8695547B2 (fr)
EP (1) EP2585687B1 (fr)
DE (1) DE102010025100A1 (fr)
WO (1) WO2012006992A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US12031460B2 (en) 2020-08-12 2024-07-09 Thyssenkrupp Dynamic Components Gmbh Sliding cam system

Families Citing this family (28)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009034990A1 (de) * 2009-07-28 2011-02-03 Daimler Ag Ventiltriebvorrichtung
DE102011012614A1 (de) 2011-02-28 2012-08-30 Neumayer Tekfor Holding Gmbh Nockenfolger und Ventiltrieb
DE102011002136B4 (de) 2011-04-18 2022-05-05 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Schaltbare Nockenwelle
WO2012175070A1 (fr) 2011-06-20 2012-12-27 Neumayer Tekfor Holding Gmbh Levier basculant et moteur à combustion interne pourvu d'un tel levier
DE102011121104A1 (de) 2011-12-14 2013-06-20 Neumayer Tekfor Holding Gmbh Motorkomponente
DE102012206683B4 (de) 2012-04-24 2019-05-09 Bayerische Motoren Werke Aktiengesellschaft Ventiltrieb für einen Zylinderkopf einer Brennkraftmaschine
JP5874520B2 (ja) * 2012-05-08 2016-03-02 トヨタ自動車株式会社 可変動弁装置
DE102012009621B4 (de) 2012-05-15 2023-06-29 Neumayer Tekfor Engineering Gmbh Ventilbetätigungsvorrichtung für einen Verbrennungsmotor
DE102012209310A1 (de) * 2012-06-01 2013-12-05 Schaeffler Technologies AG & Co. KG Grundwelle für einen Schiebenockenventiltrieb
CN102788700A (zh) * 2012-07-23 2012-11-21 中国兵器工业集团第七0研究所 一种多功能配气机构试验台的凸轮轴布置结构
DE102012016356A1 (de) 2012-08-16 2014-02-20 Neumayer Tekfor Holding Gmbh Verstellbare Nockenwelle und Verbrennungsmotor
DE102012112482A1 (de) * 2012-12-18 2014-06-18 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Verfahren zum Betreiben einer Brennkraftmaschine
DE102012112795A1 (de) * 2012-12-20 2014-06-26 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Ventiltrieb für eine Brennkraftmaschine
KR101448778B1 (ko) * 2013-03-08 2014-10-13 현대자동차 주식회사 다단 가변 밸브 리프트 장치
DE102013207355A1 (de) * 2013-04-23 2014-10-23 Mahle International Gmbh Verstellbarer Mehrprofilnocken
DE102013007741A1 (de) * 2013-05-07 2014-11-13 Thyssenkrupp Presta Teccenter Ag Nockenwelle
JP6145567B2 (ja) * 2014-03-20 2017-06-14 ヤマハ発動機株式会社 多気筒エンジンの動弁装置
DE102014007287A1 (de) * 2014-05-20 2015-11-26 Thyssenkrupp Presta Teccenter Ag Nockenwelle
DE102014116479B4 (de) * 2014-11-12 2022-02-17 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Anordnung einer Schaltnockenwelle und einer antreibbaren Aufnahme für diese
DE102014116480B4 (de) * 2014-11-12 2022-01-05 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Lagerung einer Schaltnockenwelle
JP6233387B2 (ja) * 2015-10-30 2017-11-22 トヨタ自動車株式会社 可変動弁機構
WO2017079383A1 (fr) * 2015-11-06 2017-05-11 Borgwarner Inc. Système d'actionnement de soupape offrant une levée de soupape variable et/ou un réglage de soupape variable
DE102016225050A1 (de) * 2016-12-14 2018-06-14 Volkswagen Aktiengesellschaft Brennkraftmaschine und Verfahren zum Betreiben einer Brennkraftmaschine
WO2018195370A1 (fr) * 2017-04-20 2018-10-25 Borgwarner Inc. Système d'actionnement de soupape de levée de soupape variable ayant un ou plusieurs anneaux de commande de mouvement
DE102017116987A1 (de) 2017-07-27 2019-01-31 Man Truck & Bus Ag Schiebenockensystem und Verfahren zum Betreiben eines Verbrennungsmotors
DE102017130977A1 (de) 2017-12-21 2019-06-27 Volkswagen Aktiengesellschaft Brennkraftmaschine mit vier Zylindern und Verfahren zum Betreiben einer solchen Brennkraftmaschine
DE102017011855A1 (de) * 2017-12-21 2019-06-27 Daimler Ag Ventiltrieb für eine Verbrennungskraftmaschine, insbesondere eines Kraftfahrzeugs
CN110566303A (zh) * 2019-09-24 2019-12-13 深圳臻宇新能源动力科技有限公司 发动机凸轮轴和发动机

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB186369A (en) * 1921-04-27 1922-09-27 Charles Frederic Heywood Improvements in or relating to means for starting and altering conditions of operating internal combustion engines
DE2737601C2 (de) 1977-08-20 1983-01-27 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg Einrichtung zum Anlassen einer luftverdichtenden Viertakt-Brennkraftmaschine
JPS6341610A (ja) * 1986-08-08 1988-02-22 Mazda Motor Corp エンジンのバルブ駆動装置
US5129407A (en) * 1991-06-10 1992-07-14 J. D. Phillips Corporation Variable camshaft
DE19549572C2 (de) * 1994-08-08 2003-01-23 Unisia Jecs Corp Ventilsteuereinrichtung und Verfahren zur Steuerung einer Ventilsteuereinrichtung
DE19519048A1 (de) * 1995-05-24 1996-11-28 Hermann Prof Dr Ing Krueger Variabler Ventiltrieb mit mehreren Nocken
DE19520117C2 (de) * 1995-06-01 2002-04-11 Porsche Ag Ventiltrieb einer Brennkraftmaschine
US7036465B2 (en) * 2004-03-17 2006-05-02 Ricardo, Inc. Two-stroke and four-stroke switching mechanism
DE102004055852A1 (de) * 2004-09-30 2006-04-13 Bayerische Motoren Werke Ag Ventiltrieb für eine Brennkraftmaschine, insbesondere zur selektiven Zylinderzuschaltung
DE102007016977A1 (de) * 2007-04-10 2008-10-16 Bayerische Motoren Werke Aktiengesellschaft Vorrichtung zum Verstellen der Hubfunktion eines nockenbetätigten Ventils
DE102008050776A1 (de) 2008-10-08 2010-04-15 Daimler Ag Ventiltriebvorrichtung

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US12031460B2 (en) 2020-08-12 2024-07-09 Thyssenkrupp Dynamic Components Gmbh Sliding cam system

Also Published As

Publication number Publication date
DE102010025100A1 (de) 2011-12-29
US20130104824A1 (en) 2013-05-02
US8695547B2 (en) 2014-04-15
WO2012006992A1 (fr) 2012-01-19
EP2585687A1 (fr) 2013-05-01

Similar Documents

Publication Publication Date Title
EP2585687B1 (fr) Arbres à cames pouvant être déphasé
EP3332100B1 (fr) Système de distribution pour un moteur à combustion interne
EP2291578B1 (fr) Distribution pour les soupapes d'echange de gaz d'un moteur a combustion interne avec des supports de came doublement soutenus
EP1608849B1 (fr) Commande de soupape d'un moteur a combustion interne presentant une culasse
EP2464835B1 (fr) Commande variable pour actionner des soupapes de changement des gaz sur des moteurs à combustion interne
DE102006000026B4 (de) Variable Ventilzeitsteuereinrichtung
AT408127B (de) Brennkraftmaschine mit mindestens einer durch eine verstellvorrichtung axial verschiebbaren nockenwelle
EP2464833B1 (fr) Commande pour actionner des soupapes de changement des gaz sur des moteurs à combustion interne
DE102010025099A1 (de) Nockenwelle
EP2464834B1 (fr) Commande pour actionner des soupapes de changement des gaz sur des moteurs à combustion interne
WO2010115399A1 (fr) Mécanisme de distribution pour moteurs à combustion interne pour l'actionnement de soupapes d'échange des gaz
EP3947927A1 (fr) Système de cames coulissantes et moteur
WO2014019684A1 (fr) Unité d'actionnement pour composants de mécanisme moteur variables
DE102014111411A1 (de) Nockenwellenbaugruppe
EP2126292A1 (fr) Mécanisme de distribution pour des soupapes d'échange des gaz d'un moteur à combustion interne, doté d'un palier à mouvement axial
WO2011026562A1 (fr) Mécanisme de distribution pour soupapes d'échange de gaz d'un moteur à combustion interne comportant des ensembles came axialement déplaçables
EP2504115A2 (fr) Arbre à cames en segments
DE102012008555B4 (de) Vorrichtung für einen Ventiltrieb zum Umschalten des Hubs von Gaswechselventilen einer Brennkraftmaschine
EP3332099B1 (fr) Distribution pour un moteur à combustion interne
WO2013149737A9 (fr) Système de distribution à commande mécanique, moteur à combustion interne et procédé pour faire fonctionner un moteur à combustion interne
DE102009056224B4 (de) Ventiltrieb einer Brennkraftmaschine sowie Brennkraftmaschine
WO2012175070A1 (fr) Levier basculant et moteur à combustion interne pourvu d'un tel levier
DE102007057811A1 (de) Ventiltrieb für Gaswechselventile einer Brennkraftmaschine
DE102012001303B4 (de) Verstellwellenbetätigung eines Ventiltriebs für Brennkraftmaschinen zur Betätigung von Gaswechselventilen
DE102017210661A1 (de) Ventiltriebvorrichtung für eine mehrzylindrige Brennkraftmaschine

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: 20121221

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
REG Reference to a national code

Ref country code: DE

Ref legal event code: R079

Ref document number: 502011004284

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F01L0001040000

Ipc: F01L0001340000

RIC1 Information provided on ipc code assigned before grant

Ipc: F01L 1/04 20060101ALI20140310BHEP

Ipc: F01L 1/34 20060101AFI20140310BHEP

Ipc: F01L 13/00 20060101ALI20140310BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20140430

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): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM 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

Ref country code: AT

Ref legal event code: REF

Ref document number: 685753

Country of ref document: AT

Kind code of ref document: T

Effective date: 20140915

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502011004284

Country of ref document: DE

Effective date: 20141016

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: 20140903

Ref country code: NO

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: 20141203

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: 20140903

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: 20141204

Ref country code: LT

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: 20140903

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: 20140903

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20140903

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

Ref country code: LV

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: 20140903

Ref country code: RS

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: 20140903

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: 20140903

Ref country code: HR

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: 20140903

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: 20140903

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

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: 20150105

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: 20140903

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: 20140903

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: 20140903

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: 20140903

Ref country code: IS

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: 20150103

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

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: 20140903

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011004284

Country of ref document: DE

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: 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: 20140903

26N No opposition filed

Effective date: 20150604

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

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: 20140903

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: 20140903

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140903

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: LU

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: 20150611

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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: 20150630

Ref country code: LI

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

Effective date: 20150630

Ref country code: IE

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

Effective date: 20150611

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

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

Ref country code: MT

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: 20140903

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502011004284

Country of ref document: DE

Owner name: NEUMAYER TEKFOR ENGINEERING GMBH, DE

Free format text: FORMER OWNER: NEUMAYER TEKFOR HOLDING GMBH, 77756 HAUSACH, DE

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

Ref country code: SM

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: 20140903

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; INVALID AB INITIO

Effective date: 20110611

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: 20140903

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 7

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: 20150630

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 685753

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160611

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: 20140903

REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

Free format text: REGISTERED BETWEEN 20170914 AND 20170920

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: 20160611

REG Reference to a national code

Ref country code: FR

Ref legal event code: TP

Owner name: NEUMAYER TEKFOR ENGINEERING GMBH, DE

Effective date: 20180314

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

Ref country code: MK

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: 20140903

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 8

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

Ref country code: AL

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: 20140903

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

Ref country code: GB

Payment date: 20190627

Year of fee payment: 9

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

Effective date: 20200611

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: 20200611

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

Ref country code: FR

Payment date: 20230622

Year of fee payment: 13

Ref country code: DE

Payment date: 20230627

Year of fee payment: 13