EP3074614A1 - Arbre à cames réglable - Google Patents

Arbre à cames réglable

Info

Publication number
EP3074614A1
EP3074614A1 EP14809293.5A EP14809293A EP3074614A1 EP 3074614 A1 EP3074614 A1 EP 3074614A1 EP 14809293 A EP14809293 A EP 14809293A EP 3074614 A1 EP3074614 A1 EP 3074614A1
Authority
EP
European Patent Office
Prior art keywords
spherical shape
bearing surface
bearing
shaft
outer shaft
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
EP14809293.5A
Other languages
German (de)
English (en)
Other versions
EP3074614B1 (fr
Inventor
Martin Lehmann
Bernd Mann
Michael Kunz
Uwe Dietel
Jürgen MEUSEL
Manfred Muster
Markus NIEDERLECHNER
Marko CURLIC
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 Presta TecCenter 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 Presta TecCenter AG filed Critical ThyssenKrupp Presta TecCenter AG
Publication of EP3074614A1 publication Critical patent/EP3074614A1/fr
Application granted granted Critical
Publication of EP3074614B1 publication Critical patent/EP3074614B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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
    • F01L1/047—Camshafts
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34413—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using composite camshafts, e.g. with cams being able to move relative to the camshaft
    • 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
    • F01L1/047—Camshafts
    • F01L2001/0471—Assembled camshafts
    • F01L2001/0473—Composite camshafts, e.g. with cams or cam sleeve being able to move relative to the inner camshaft or a cam adjusting rod
    • 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
    • F01L1/047—Camshafts
    • F01L2001/0476—Camshaft bearings

Definitions

  • the present invention relates to an adjustable camshaft for the valve train of an internal combustion engine having an outer shaft and extending through the outer shaft inner shaft, wherein on the outer shaft at least one cam element is arranged and which is rotationally fixedly connected to the inner shaft, and wherein the cam member having a shaft passage an inner bearing surface having a bearing surface on the outside of the outer shaft forms a sliding bearing for rotatably mounting the cam member on the outer shaft.
  • DE 10 2012 103 581 A1 shows a generic type adjustable camshaft with an outer shaft and an inner shaft, and the inner shaft extends through the tubular outer shaft and is rotatable in this.
  • a pin on the outer shaft rotatably received cam member is rotatably connected to the inner shaft, so that upon rotation of the inner shaft relative to the outer shaft, a change in the phase position of the cam member is generated on the outer shaft.
  • the rotatable on the outer shaft cam member forms with a shaft passage in the cam member has a sliding bearing on the outside of the outer shaft, and the sliding bearing is supplied via a gap between the inner shaft and the outer shaft with lubricant.
  • the cam member is in contact with a tapping member for the valvetrain, which often results in radially biased forces acting on the cam member. This can lead to tilting of the cam element relative to the longitudinal axis of the camshaft and increased loads in the outer regions of the bearing surfaces, which can lead to so-called edge carriers.
  • edge carriers form when, with a tilting of the cam element on the otherwise cylindrical outer shaft only the edge region of the bearing surface, so for example, the outer longitudinal axis direction locally limited area
  • CONFIRMATION COPY the shaft passage or the edge region of the setting point on the outer shaft, which receives full operating forces on the cam element.
  • a valve actuating element is known, and there is provided a roller bearing outer race, which is in contact with the cam contour of a cam member.
  • the outer ring is roller-mounted via an inner ring, and the bearing unit formed by the outer ring and the inner ring is tiltably received on a bearing pin.
  • the bearing pin is designed crowned.
  • the object of the invention is the development of an adjustable camshaft for the valve train of an internal combustion engine with an improved recording of a cam element on the outer shaft of the camshaft.
  • the invention includes the technical teaching that at least one of the bearing surfaces is at least partially formed with a spherical shape.
  • a spherical shape of at least one of the bearing surfaces is provided for rotational movement of the cam member on the outer shaft about the longitudinal axis, a further degree of freedom for performing a slight tilting movement of the cam member on the outer shaft.
  • bearing air is achieved by the spherical shape that the radial gap increases over the axial length of the bearing surfaces on at least one side to the outside. If the cam element tilts slightly on the outer shaft, a longer axial area of the mutually sliding bearing surfaces comes into play, whereby the formation of edge beams is avoided.
  • the spherical shape according to the invention at least one of the bearing surfaces describes a shape of the bearing surfaces, which is rotationally symmetrical, and generates a variable over the axial length of the bearing surface bearing clearance between the two bearing surfaces.
  • the spherical shape is designed so that the bearing clearance, ie the remaining radial gap between the bearing surfaces, becomes larger towards at least one outer side of the bearing surface.
  • the spherical shape forms according to the invention a deviation from the cylindrical shape in such a way that the surface bulges in the shaft passage or the outside of the outer shaft to the respective opposite bearing surface to form a radial gap narrowing out.
  • the cam element can thus execute a likewise periodic tilting movement following the periodic action of force by a tapping element, as a result of which even a pumping effect of lubricant can be generated in the gap between the bearing surfaces.
  • the lubricant supply can be improved in the bearing gap between the bearing surfaces, in particular it is avoided that in the bearing gap existing lubricant is outdated and not replaced by fresh lubricant.
  • the geometric deviation of the shape of the bearing surface from a cylindrical shape is made so small that the contact of the cam track of the cam element is not adversely affected to the tap element.
  • the cam element maintains a line contact with the pick-up element in an improved manner, without it being possible for edge supports to form in this line contact as well.
  • the crowned shape is made so minimal that it does not come to solid contact between the bearing surface in the shaft passage and the bearing surface on the outside of the outer shaft, and a bearing lubricating film is maintained even with a tilted arrangement of the cam member on the outside of the outer shaft.
  • the bearing surface on the outside of the outer shaft may have a spherical shape, in particular wherein the spherical shape may have a width which corresponds at least to the length of the sliding bearing in the direction of a longitudinal axis in which the camshaft extends.
  • the width of the spherical shape may correspond to the axial length of the sliding bearing, but it can also be provided that the spherical shape has a greater width than the axial length of the plain bearing. This can be achieved in particular that the radius, which results in the bearing surface by the spherical shape, can be made very large, resulting in manufacturing advantages.
  • the bearing surface in the shaft passage at least partially have a spherical shape, so that the shaft passage on the inside has a smaller diameter than the edge.
  • the crowned shape can also be provided in both bearing surfaces, whereby the radial gap enlargements in the edge direction of the plain bearing can be added by the two crowned shapes.
  • the spherical shape in at least one of the bearing surfaces can be carried out advantageously in various ways.
  • the spherical shape may be formed symmetrically with respect to the longitudinal axis of the camshaft. This forms a sliding bearing with mutually sliding off bearing surfaces, which has a radial gap narrowing, which results in the axial direction centered over the length of the bearing surfaces.
  • the cam member in two opposite tilting directions tilt in the same way.
  • the area of the minimum radial gap between the bearing surfaces can be arranged centrally below the cam track of the cam element.
  • the cam member may also have a cam collar, resulting in an axially longer configuration of the cam member.
  • the region of the radial gap narrowing can form centrally over the entire length of the bearing surface, which is determined by the axial length of the cam element with the cam collar.
  • the spherical shape in the at least one bearing surface may also be formed asymmetrically.
  • the asymmetrically formed spherical shape can be used, which can be formed both in the bearing surface in the shaft passage and in the outer side of the outer shaft, namely at the setting point for receiving the cam element.
  • the spherical shape may be formed asymmetrically in the at least one bearing surface such that a radial gap narrowing between the bearing surfaces in the portion of the cam collar or preferably adjacent to the portion of the cam collar is formed.
  • the application of force to the cam member is basically created by the cam track of the cam member, whereby the cam member can perform a slight periodic tilting movement on the outer shaft. Due to the symmetrical or asymmetrical crowned shape of at least one of the bearing surfaces roll the bearing surfaces from each other while performing the tilting movement, and in the end point of the tilting arise due to the inventive spherical shape no edge beams.
  • the spherical shape in at least one of the bearing surfaces need not be formed over the entire axial length of the bearing surface.
  • the at least one bearing surface may have at least one cylindrical section which is formed adjacent to a spherical shape. It can also be provided that the cylindrical section axially extends the region of the radial gap narrowing so that on one or both sides of the cylindrical section a spherical shape follows, over which the bearing surface runs out to the edge.
  • Such a Contour profile of the bearing surface with a preferably centrally arranged cylindrical portion and laterally expiring spherical shapes avoids particularly advantageous manner in a tilting of the cam member resulting edge beams, however, results in a mechanically highly resilient, bearing area for receiving the operating forces of the cam member on the outer shaft by the widened formed area of a radial gap narrowing.
  • the spherical shape in at least one edge direction can pass into a peripheral radius, with which the bearing surface of the sliding bearing axially terminates.
  • the spherical shape may have a radial height of for example 1 pm to 15 pm, preferably from 2 pm to 10 pm and more preferably from 4 pm to 6 pm.
  • the deviation of the bearing surface of a cylindrical shape is thus extremely low and may for example be limited to the order of magnitude of the bearing clearance.
  • FIG. 1 shows an embodiment of an adjustable camshaft with a bearing surface, formed by the outside of the outer shaft, which has a spherical shape
  • FIG. 2 shows an exemplary embodiment of an adjustable camshaft with a bearing surface formed by the outer side of the outer shaft, which has a crowned shape, and the spherical shape is wider than the width of the cam element,
  • FIG. 3 shows an exemplary embodiment of an adjustable camshaft with an inner bearing surface in the shaft passage of the cam element, which has a spherical shape
  • FIG. 4 shows an exemplary embodiment of an adjustable camshaft with an inner bearing surface, formed by the shaft passage in the cam element, wherein the bearing surface has an asymmetrical spherical shape
  • Figure 5 shows an embodiment of an adjustable camshaft with a spherical inner bearing surface in the shaft passage of the cam member, wherein the bearing surface has a cylindrical portion and
  • Figure 6 shows an embodiment of an adjustable camshaft with a spherical shape in the bearing surface, formed by the shaft passage in the cam member, wherein the spherical shape is designed asymmetrically.
  • FIGS. 1 to 6 show various exemplary embodiments of adjustable camshafts 1 for the valve drive of an internal combustion engine with an outer shaft 10 and with an inner shaft 11 extending through the outer shaft 10.
  • the inner shaft 11 is rotatable in the outer shaft 10 about the longitudinal axis 15, and extending in the longitudinal axis 15 adjustable camshaft 1 is only partially shown.
  • On the section shown is located on the outside of the outer shaft 10, a camshaft member 12, and the camshaft member 12 is exemplified as a collar cam with a cam collar 16 and connected by a pin 19 rotationally fixed to the inner shaft 11. If the inner shaft 11 is rotated against the outer shaft 10, the cam element 12 likewise rotates on the outer side of the outer shaft 10.
  • a shaft passage is introduced for the passage of the outer shaft 10, and the shaft passage forms an inner bearing surface 13, which forms a sliding bearing with the bearing surface 14 on the outer side of the outer shaft 10.
  • the cam member 12 is rotatable about a predetermined angle section about the longitudinal axis 15 on the outer shaft 10.
  • the following embodiments show various bearing surfaces 13 and 14 in the shaft passage of the cam member 12 and on the outside of the outer shaft 10, wherein the bearing surfaces 13 and 14 have formed in various ways crowned shapes.
  • Figure 1 shows an embodiment of an adjustable camshaft 1 with a spherical shape of the bearing surface 14 on the outside of the outer shaft 10.
  • the spherical shape is symmetrical and has a width which corresponds approximately to the width of the cam member 12, so that the spherical shape, the width the setting point of the cam member 12 has on the outside of the outer shaft 10. Act through the contact of the cam member 12 with a tap member to the valve train of the engine forces on the cam member 12, this can perform relative to the longitudinal axis 15 a minimal tilting movement, so in the tilting movement, the bearing surface 13 in the shaft passage of the cam member 12 a rolling movement on the crowned bearing surface fourteenth on the outside of the outer shaft 10 performs.
  • the connection of the cam member 12 with the inner shaft 1 1 via the pin 19 need not be assumed to be infinitely stiff, so that slight movements can be performed by the cam member 12 despite a press connection of the cam collar 16 with the pin 19.
  • the spherical shape may be determined by a radius R, which is smaller due to the limited width of the spherical shape than in the embodiment shown below with reference to FIG.
  • the spherical shape of the bearing surface 14 with respect to the longitudinal axis 15 may also be determined by a plurality of consecutively formed radii which are mutually can be different in size.
  • the spherical shape can be formed, for example, in the manner of a polygon of several radii in the direction of the longitudinal axis 15 strung together.
  • a central radius R as shown can be larger than marginal radii, which can run out without edge and step into the cylindrical surface of the outer shaft 10.
  • Figure 2 shows another embodiment of an adjustable camshaft 1 with a spherical shape of the bearing surface 14, which has a width B, which is greater than the width of the cam member 12 according to this embodiment.
  • the radius R defining the spherical shape with a larger value be determined. Consequently, the range of the radial gap narrowing 17, resulting in an increased load capacity of the sliding bearing increases.
  • the convex shape in particular according to this exemplary embodiment, can also be formed in the manner of a polygon consisting of a plurality of radii in the direction of the longitudinal axis 15.
  • Figure 3 shows an embodiment of the adjustable camshaft 1 with a spherical shape of the inner bearing surface 13 in the shaft passage of the cam member 12.
  • the spherical shape is designed approximately symmetrical, so that under a mechanical load of the cam member 12 this can perform a tilting movement relative to the longitudinal axis 15, the starting from the center position shown in two different tilt directions can take place equally.
  • Figure 4 shows an embodiment of the adjustable camshaft 1 with a spherical contour of the bearing surface 13 in the shaft passage of the cam member 12, wherein in a modification of the embodiment of Figure 3, the spherical shape of the bearing surface 13 is asymmetrical, so that the radial gap narrowing 17 in the direction of the cam collar 16th is pronounced.
  • the cam member 12 has a cam collar 16, the crowned shape enlarging to the left with an increasing radial gap in the plane of the illustration.
  • the bearing gap between the bearing surfaces 13 and 14 opens to the left. Act forces on the cam member 12, this can perform a slight tilting movement by the bearing surface 13 rolls on the bearing surface 14.
  • FIG. 5 shows an embodiment of the adjustable camshaft 1 with a bearing surface 13 which has a cylindrical portion 18.
  • a bearing surface 13 which has a cylindrical portion 18.
  • spherical portions of the bearing surface 13 in the shaft passage of the cam member 12 close. Close this the shaft passage in radii from passing, so can be avoided by the spherical shape of the bearing surface 13 shown in a special way edge support, wherein the cylindrical portion 18 between the crowned areas allows high load capacity of the sliding bearing.
  • the crowned sections can pass over into the cylindrical section 18 without edges and edges, so that regions with a mechanical stress increase are avoided.
  • FIG. 6 shows, in a modification of the exemplary embodiment of FIG. 5, an asymmetrical configuration of a crowned shape of the bearing surface 13 in the shaft passage of the cam element 12.
  • the region of a radial gap narrowing 17 falls under the cam contour of the cam element 12 adjacent to the cam collar 16, thus representing a possible embodiment of FIG asymmetrical spherical shape of the bearing surface 13 is shown.
  • the region of the radial gap narrowing 17 can also fall under the cam collar 16 when the bearing surface 13 is configured in the shaft passage of the cam member 12 with an asymmetrical spherical shape.
  • the spherical shape shown in Figure 1 to Figure 6 in the bearing surfaces 13 and 14 is graphically exaggerated graphically, and the non-scale representation of the spherical shapes in the bearing surfaces 13 and 14 serves only to visualize the spherical shape.
  • the spherical shapes are extremely small and move with radial height deviations of the spherical shapes in the range of a few micrometers, for example 1 ⁇ to 15 ⁇

Landscapes

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

Abstract

L'invention concerne un arbre à cames réglable (1) destiné au mécanisme de distribution d'un moteur à combustion interne, comportant un arbre extérieur (10) et un arbre intérieur (11) traversant l'arbre extérieur (10), au moins un élément came (12) étant agencé sur l'arbre extérieur (10) et étant relié de manière solidaire en rotation à l'arbre intérieur (11), et l'élément came (12) comportant un passage d'arbre muni d'une surface de palier intérieure (13) qui forme avec une surface de palier (14) sur le côté extérieur de l'arbre extérieur (10) un palier lisse permettant l'agencement rotatif de l'élément came (12) sur l'arbre extérieur (10). Selon l'invention, au moins une des surfaces de palier (13, 14) présente au moins par endroits une forme bombée.
EP14809293.5A 2013-11-29 2014-11-27 Arbre a cames ajustable Active EP3074614B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013113255.3A DE102013113255A1 (de) 2013-11-29 2013-11-29 Verstellbare Nockenwelle
PCT/EP2014/003177 WO2015078588A1 (fr) 2013-11-29 2014-11-27 Arbre à cames réglable

Publications (2)

Publication Number Publication Date
EP3074614A1 true EP3074614A1 (fr) 2016-10-05
EP3074614B1 EP3074614B1 (fr) 2017-10-18

Family

ID=52016024

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14809293.5A Active EP3074614B1 (fr) 2013-11-29 2014-11-27 Arbre a cames ajustable

Country Status (7)

Country Link
US (1) US9926815B2 (fr)
EP (1) EP3074614B1 (fr)
KR (1) KR20160093005A (fr)
CN (1) CN105940191A (fr)
DE (1) DE102013113255A1 (fr)
HU (1) HUE036093T2 (fr)
WO (1) WO2015078588A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013208609A1 (de) * 2013-05-10 2014-11-13 Mahle International Gmbh Nockenwelle
DE102015224015A1 (de) * 2015-12-02 2017-06-08 Mahle International Gmbh Verstellbare Nockenwelle

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD115523A1 (fr) * 1974-10-28 1975-10-05
DE3144720A1 (de) * 1981-11-11 1983-05-19 Friedrich Prof. Dr.-Ing. 4300 Essen Jarchow Radialgleitlager mit lastverformungsangepasster mantelgeometrie von bohrung oder welle oder achse
DE3624827A1 (de) * 1986-07-23 1988-02-04 Sueddeutsche Kolbenbolzenfabri Verstelleinrichtung fuer eine nockenwelle zum steuern der gasein- und auslassventile von verbrennungsmotoren
JP3314600B2 (ja) * 1995-11-27 2002-08-12 日本精工株式会社 拡管組立式中空カム軸
DE10054622A1 (de) 2000-11-03 2002-05-08 Audi Ag Ventilbetätigungselement
DE102005014680A1 (de) * 2005-02-03 2006-08-10 Mahle International Gmbh Nockenwelle mit gegeneinander verdrehbaren Nocken für insbesondere Kraftfahrzeuge
US7374257B2 (en) 2005-02-11 2008-05-20 Caterpillar Inc. Machine track roller assembly
GB2424257A (en) * 2005-03-18 2006-09-20 Mechadyne Plc Single cam phaser camshaft with adjustable connections between the inner shaft and associated cam lobes
GB2431977A (en) * 2005-11-02 2007-05-09 Mechadyne Plc Camshaft assembly
DE102006051332A1 (de) * 2006-10-31 2008-05-08 Robert Bosch Gmbh Förderpumpe, insbesondere zur Förderung von Dieselkraftstoff mit einer verbesserten Lagerung der Antriebswelle
JP4980031B2 (ja) * 2006-11-10 2012-07-18 Ｎｔｎ株式会社 ころ軸受のクラウニングの設計方法
DE102007026824A1 (de) * 2007-06-06 2008-12-11 Muhr Und Bender Kg Verfahren zur Herstellung von Nocken für gebaute Nockenwellen
BR112012004592A2 (pt) * 2009-12-07 2016-04-05 Mitsubishi Motors Corp dispositivo de atuação de válvula variável para um motor de combustão interna
DE102010032254A1 (de) * 2010-07-26 2012-01-26 Schaeffler Technologies Gmbh & Co. Kg Tassenstößel und Verfahren zu dessen Herstellung
CN102686911B (zh) * 2010-12-28 2015-03-11 丰田自动车株式会社 双重凸轮轴结构及双重凸轮轴结构的组装方法
DE102011106395A1 (de) * 2011-07-02 2013-01-03 Man Truck & Bus Ag Ventilsteuerung für mindestens ein Ventil einer Brennkraftmaschine
DE102012103581A1 (de) 2012-04-24 2013-10-24 Thyssenkrupp Presta Teccenter Ag Nockenwelle mit durch Drucköl beölbare, verstellbare Nocken
DE102013208609A1 (de) * 2013-05-10 2014-11-13 Mahle International Gmbh Nockenwelle

Also Published As

Publication number Publication date
HUE036093T2 (hu) 2018-06-28
KR20160093005A (ko) 2016-08-05
WO2015078588A1 (fr) 2015-06-04
DE102013113255A1 (de) 2015-06-03
US20170030229A1 (en) 2017-02-02
EP3074614B1 (fr) 2017-10-18
CN105940191A (zh) 2016-09-14
US9926815B2 (en) 2018-03-27

Similar Documents

Publication Publication Date Title
DE602005003991T2 (de) Gleichlauftripodegelenk
EP1838972A1 (fr) Corps de serrage
DE102010034254A1 (de) Käfig für ein Rollenlager
DE102010038185A1 (de) Düseneinrichtung eines Turboladers variabler Geometrie
DE4300793B4 (de) Zentrierfeder für Triplan-Kugelgleichlaufgelenke
WO2015149790A1 (fr) Ensemble pendule centrifuge
EP1357255A1 (fr) Turbocompresseur avec distributeur à géométrie variable
EP3074614B1 (fr) Arbre a cames ajustable
DE60302638T2 (de) Durch einen Bolzen verbundener Gestängemechanismus
DE102007016209B4 (de) Ventiltrieb für Gaswechselventile mit Axialkraftreduktion in Nockenwelle
WO2017041797A1 (fr) Douille et chaîne à douilles correspondante
DE102004060540B4 (de) Fluiddynamisches Lager mit druckerzeugenden Oberflächenstrukturen
DE102015201937A1 (de) Doppelgelenk
DE102016120453B4 (de) Variabler ventilmechanismus
DE202007013685U1 (de) Taumelgetriebe
DE102017118204A1 (de) Wälzlager und Drehverhinderungsmechanismus für einen Turbolader
EP3014079B1 (fr) Arbre à cames réglable
DE102010011462A1 (de) Kegelrollenlager mit profilierter Laufbahn
WO2015155115A1 (fr) Arbre à cames réglable
EP3161338A1 (fr) Joint coulissant à billes à chemins de roulement croisés ayant des angles d'inclinaison différents et des distances radiales minimales différentes
DE112014000436B4 (de) Taumelscheibenverdichter mit variabler Verdrängung und verbessertem Drehverhinderungsmechanismus
WO2018162601A1 (fr) Arbre à cames comprenant une pièce coulissante lubrifiée
DE102017202330A1 (de) Radiallageranordnung, insbesondere für eine Ausgleichswelle
DE60103787T2 (de) Stufenlos regelbares Getriebe der toroidalen Bauart
DE102016105329A1 (de) Variabler Ventilmechanismus einer 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: 20160519

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

AX Request for extension of the european patent

Extension state: BA ME

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: 502014005899

Country of ref document: DE

Free format text: PREVIOUS MAIN CLASS: F01L0001047000

Ipc: F01L0001340000

RIC1 Information provided on ipc code assigned before grant

Ipc: F01L 1/047 20060101ALI20170410BHEP

Ipc: F01L 1/34 20060101AFI20170410BHEP

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20170621

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

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 938143

Country of ref document: AT

Kind code of ref document: T

Effective date: 20171115

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: 502014005899

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 4

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20171018

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: 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: 20171018

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

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: 20171018

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: 20180118

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: 20171018

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: 20171018

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: 20180119

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: 20180218

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: 20171018

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: 20171018

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: 20180118

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: 20171018

REG Reference to a national code

Ref country code: HU

Ref legal event code: AG4A

Ref document number: E036093

Country of ref document: HU

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502014005899

Country of ref document: DE

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: 20171018

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: 20171018

Ref country code: LI

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

Effective date: 20171130

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: 20171018

Ref country code: CH

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

Effective date: 20171130

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: 20171018

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: LU

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

Effective date: 20171127

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: 20171018

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: 20171018

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: 20171018

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20171130

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

26N No opposition filed

Effective date: 20180719

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: 20171018

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 NON-PAYMENT OF DUE FEES

Effective date: 20171127

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: 20171018

Ref country code: BE

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

Effective date: 20171130

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

Ref country code: PL

Payment date: 20181030

Year of fee payment: 5

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: 20171018

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: 20171018

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

Ref country code: CZ

Payment date: 20191126

Year of fee payment: 6

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: 20171018

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: 20171018

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: 20171018

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 NON-PAYMENT OF DUE FEES

Effective date: 20191128

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 938143

Country of ref document: AT

Kind code of ref document: T

Effective date: 20191127

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: 20191127

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

Ref country code: CZ

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

Effective date: 20201127

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230530

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

Ref country code: GB

Payment date: 20231123

Year of fee payment: 10

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

Ref country code: SE

Payment date: 20231120

Year of fee payment: 10

Ref country code: IT

Payment date: 20231124

Year of fee payment: 10

Ref country code: FR

Payment date: 20231120

Year of fee payment: 10

Ref country code: DE

Payment date: 20231121

Year of fee payment: 10