EP2715078A1 - Dispositif de réglage d'arbre à cames - Google Patents

Dispositif de réglage d'arbre à cames

Info

Publication number
EP2715078A1
EP2715078A1 EP12719612.9A EP12719612A EP2715078A1 EP 2715078 A1 EP2715078 A1 EP 2715078A1 EP 12719612 A EP12719612 A EP 12719612A EP 2715078 A1 EP2715078 A1 EP 2715078A1
Authority
EP
European Patent Office
Prior art keywords
camshaft
units
axis
rotational axis
tappet
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
EP12719612.9A
Other languages
German (de)
English (en)
Other versions
EP2715078B1 (fr
Inventor
Matthias Werner
Thomas Golz
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.)
ETO Magnetic GmbH
Original Assignee
ETO Magnetic 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 ETO Magnetic GmbH filed Critical ETO Magnetic GmbH
Priority to PL12719612T priority Critical patent/PL2715078T3/pl
Publication of EP2715078A1 publication Critical patent/EP2715078A1/fr
Application granted granted Critical
Publication of EP2715078B1 publication Critical patent/EP2715078B1/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
    • F01L1/34—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
    • 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
    • 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
    • F01L2013/10—Auxiliary actuators for variable valve timing
    • F01L2013/101—Electromagnets

Definitions

  • the present invention relates to a camshaft adjusting device according to the preamble of claim 1, comprising a camshaft rotational axis about which the camshaft is rotatable, defined by a camshaft, in particular a carrier shaft of a camshaft.
  • electromagnetic multiple-ram adjustment device comprising a plurality of (typically selectively, ie, independently of each other) controllable plunger units sufficiently compact to realize, so on the one hand a sufficient electromagnetic functionality is ensured (for example, with regard to the necessary stroke of the plunger units and reaction or Switching times), on the other hand no unwanted mutual influence - mechanical or electromagnetic - is present.
  • a camshaft adjusting device is known from DE 10 2007 040 677 A1, in which the tappet units cooperating with a respective drive unit are arranged such that their respective tappet longitudinal center axis intersects the axis of rotation of the camshaft.
  • the drive units are arranged offset in the circumferential direction of the camshaft so that the pushrod longitudinal axis of the pushrod units extend at an angle to one another. This results in a comparatively large necessary installation space. Also disadvantageous are manufacturing difficulties.
  • the object of the present invention is therefore to provide a camshaft adjusting device, comprising an electromagnetic multi-ram adjusting device, which is optimized even further space, while ensuring at the same time that the largest possible overlapping area (contact surface) between the attack side (drive side) end faces of the plunger units and the attack surface of the respectively associated drive unit is given.
  • camshaft adjusting device having the features of the main claim.
  • Advantageous developments of the invention are specified in the subclaims. In the context of Invention, all combinations of at least two of the features disclosed in the description, the claims and / or the figures.
  • the invention is based on the idea, in the case of a camshaft adjusting device comprising an electromagnetic multi-tappet adjusting device, to arrange the tappet units parallel to one another such that the tappet longitudinal axis of at least one of the tappet units, in departure from the teaching of the prior art, defines the axis of rotation, preferably defined by a carrier shaft the camshaft does not intersect, but in an imaginary plane in which the aforementioned axis of rotation is located and perpendicular to all the push rod longitudinal axis extending, is spaced, in particular by a dimension of more than 0.3 mm, preferably by more than 0.5 mm.
  • the invention consciously takes the supposed disadvantage of an off-center force application of the cam piece, preferably axially relative to the aforementioned axis of rotation, in order to advantageously achieve a space-optimized arrangement of the drive units with associated ram units, wherein the inventive proper arrangement of the plunger units advantageously ensures that the largest possible overlap between plunger units and drive units is given.
  • Each drive unit is preferably formed by one, in particular permanent magnet, armature.
  • each armature is associated with its own coil (energizable winding), wherein also a Ausfertigungsform can be realized, in which, for example, according to the principle described in DE 20 2008 015 980 U1, several anchors are driven by a common coil.
  • a Ausfertigungsform can be realized, in which, for example, according to the principle described in DE 20 2008 015 980 U1, several anchors are driven by a common coil.
  • ram units guided longitudinally displaceable
  • the ram units guided longitudinally displaceable
  • a plurality of ram longitudinal center axes are spaced in the aforementioned plane, preferably by the same amount from the axis of rotation of the camshaft, in particular a carrier shaft of the camshaft, and at least one, preferably only one, ram longitudinal axis intersects the axis of rotation.
  • the drive of the elongated (even preferably cylindrical, more preferably realized from a metal material) ram units takes place in known per se, for example in DE 10 2007 028 600 A1. described way in that the plunger units sit on an attack surface of a respective associated drive unit (preferably there by means of magnetic effect adhere) the attack surface typically forms the distal end of an anchor unit of the respective drive unit.
  • the at least one spaced in the aforementioned plane of the axis of rotation of the cam shaft ram longitudinal center axis is spaced by a minimum of 0.5 mm from the axis of rotation.
  • the distance between 0.5 mm and 8.0 mm, preferably between 1, 0 mm and 5.0 mm, even more preferably between 1, 0 mm and 2.0 mm, most preferably the distance is about 1, 5 mm.
  • the at least one ram longitudinal center axis preferably all ram longitudinal axis axes spaced from the axis of rotation of the camshaft, in the plane to the camshaft rotational axis by a dimension, in particular the same amount, which is calculated on the basis of the base circle half diameter of the associated shift groove.
  • a dimension, in particular the same amount which is calculated on the basis of the base circle half diameter of the associated shift groove.
  • the distance measured in the aforementioned plane is between about 3% and about 80%, preferably between about 3% and about 50%, even more preferably between about 3% and about 30%, even more preferably between about 3% and about 20% of this Grundnikcher penmessers the respective ram unit associated, preferably spirally running switching groove , In general, it is preferred if the distance is less than 15% of this base circle half diameter and / or more than 5%.
  • the multi-plunger adjusting device comprises a total of at least three, preferably only three, drive units, each with an associated plunger unit, wherein the at least three plunger units, in particular the exclusively three plunger units will be explained as follows can be arranged.
  • a single one of the plurality of ram longitudinal axis axes it is possible for only a single one of the plurality of ram longitudinal axis axes to arrange the camshaft rotational axis, the further ram longitudinal center axes, preferably the two further ram longitudinal axis in the previously explained plane of the camshaft of the axis of rotation, preferably spaced by the same amount. It is particularly expedient in the case of providing a total of three tappet units with respect to the longitudinal extent of the axis of rotation medium ram unit to arrange the axis of rotation cutting.
  • At least two, preferably only two of the at least three, in particular the only three push rod longitudinal central axes intersect the camshaft rotational axis.
  • these are two adjacent to one another in the direction of the longitudinal extent of the axis of rotation of the camshaft, that is to say adjacent ram longitudinal center axes.
  • all of the at least three, preferably the only three ram longitudinal center axes in the aforementioned plane are spaced apart from the camshaft rotational axis, in each case by the same amount.
  • each plunger longitudinal center axis defines a plunger plane that receives the respective plunger longitudinal center axis, the plunger planes arranged side by side in the direction of the longitudinal extension of the rotational axis being spaced apart by the same amount.
  • the arrangement of the plunger units becomes particularly compact in that at least one of the plunger units is seated eccentrically and / or with only a partial surface of the attack-side end face on the associated engagement surface with its attack-side end face.
  • the drive units a common housing is assigned, which particularly preferably frontally cooperates with a housing guide portion which - typically in the form of mutually parallel through holes, in particular through holes - guides for the offers several ram units, which are then to be arranged so relative to each other and to the camshaft rotation axis, that at least one ram longitudinal center axis does not intersect the aforementioned axis of rotation.
  • FIG. 3 is a view of an actuator of a Nockenwellenverstell- device in a view from below with a total of three plunger units, wherein a push rod longitudinal axis of a central plunger unit is spaced from a rotational axis of the camshaft,
  • Camshaft adjusting device wherein two of three ram longitudinal center axes are spaced on different sides of the camshaft rotation axis, and
  • FIG. 5 shows a further alternative exemplary embodiment of a multi-tappet adjusting device of a camshaft adjusting device, in which the tappet longitudinal center axis of an outer tappet unit is laterally offset from the axis of rotation of the camshaft and the other two ram longitudinal axis axes intersect the camshaft axis of rotation.
  • the figures of the same element and elements with the same functions are denoted by the same reference numerals.
  • FIGS. 1 and 2 exemplary embodiments of variable gas exchange valve drives for an internal combustion engine 2 indicated in FIG. 1 are shown.
  • 1 and 2 show possible embodiments of camshaft lenverstellvortechniken 3 with an electromagnetic Mehrst Congressel- adjusting 4.
  • the Nockenwellenverstellvortechniken 3 according to FIGS. 1 and 2 each comprise a camshaft 5, comprising a support shaft 6 on the rotationally fixed and axially displaceable Cam piece 7 is arranged with a plurality of cam lobes of different geometry.
  • the carrier shaft 6 is rotatably driven about a camshaft rotational axis D by means of the internal combustion engine 2.
  • Each of the cylindrical, elongate plunger units 9, 10, 11 defines a plunger longitudinal center axis A1, A2, A3, wherein the plunger longitudinal center axes A1, A2, A3 are arranged parallel to one another and perpendicular to the camshaft rotational axis D.
  • the tappet units 9, 10, 11 each interact with a front side (not shown) on the cam piece 7, in the manner described in detail in DE 10 2007 028 600 A1, each with a drive unit, not shown (on the attack side or on the actuator side), more precisely with a plane attack surface of the respective drive unit.
  • the drive units which are not shown separately, are accommodated in a common, cylindrical housing 14, which cooperates with a housing guide section 15 on the front side, in which the tappet units 9, 10, 11 are guided longitudinally displaceable.
  • the ram longitudinal center axis A2 of a middle (second) ram unit 10 is laterally spaced or offset from one another in a plane E to the camshaft rotational axis D (rotational axis), so it does not intersect.
  • the aforesaid plane E receives the camshaft rotational axis D and extends perpendicular to all the longitudinal axis of the push rods A1, A2, A3.
  • the other two (outer) and first and second plunger units 9, 1 1 are arranged such that they intersect the axis of rotation D in the plane E.
  • an embodiment of an electromagnetic multi-ram adjusting device 4 of a camshaft adjusting device 3 not shown otherwise in Fig.
  • camshaft rotational axis D which is arranged in a plane perpendicular to the longitudinal axis of the push rod A1 to A3 plane E.
  • the tappet units 9, 10, 11 are guided in the guide section 15 of the housing so as to be longitudinally displaceable such that the two outer longitudinal axis of the push rods A1 and A3, viewed in the direction of the longitudinal extent of the camshaft rotational axis D, intersect the camshaft rotational axis D in the plane E, whereas the longitudinal axis of the pushrod A2 the central tappet unit 10 is arranged laterally spaced from the camshaft rotational axis D and that by the dimension a, of about 1.5 mm in the exemplary embodiment shown.
  • the two outer ram longitudinal center axes A1, A3 are equidistant from the central ram longitudinal center axis A2 in the direction of the axial extent of the camshaft rotational axis D, specifically by the dimension b of about 7 mm in the exemplary embodiment shown.
  • the diameter of the circular cylindrical ram units 9, 10, 1 1 in the exemplary embodiment is about 4.5 mm.
  • the diameter of the hollow cylindrical housing 14 is about 20 mm.
  • FIG. 4 shows an alternative embodiment of a multi-poppet adjusting device 4 of a camshaft adjusting device 3. Recognizable again is the camshaft rotational axis D, which is arranged in the plane E, to which the ram longitudinal center axes A1 to A3 run vertically.
  • the plunger units 9, 10, 1 1 are arranged such that viewed in the direction of the longitudinal extent of the camshaft rotation axis D average (second) ram unit 10 and the ram longitudinal center axis A2 intersects the camshaft rotational axis D in the plane E, whereas in the middle ram longitudinal center axis A2 parallel ram longitudinal center axes A1, A3 of the outer ram units 9, 10 are spaced in the plane E of the camshaft about the same absolute dimension a, of about 1, 5 mm in the embodiment shown. It can be seen that the outer ram longitudinal center axes A1, A3 are arranged on different sides of the camshaft rotational axis D.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

L'invention concerne un dispositif de réglage d'arbre à cames (3), comprenant un axe de rotation d'arbre à cames (D) et un dispositif de réglage électromagnétique à multipoussoir de cames (4) présentant au moins deux unités d'entraînement électromagnétiques qui sont commandées, en vue d'exercer une force de réglage sur une pluralité correspondante d'unités de poussoirs (9, 10, 11) allongés, montées suivant des axes parallèles entre eux, définissant chacune un axe médian longitudinal (A1) de poussoir, disposé perpendiculairement à l'axe de rotation d'arbre à cames (D), de manière à venir en prise avec les unités de poussoirs dans des rainures de commande (8) d'une pièce de came réglable (7), les unités d'entraînement formant chacune, à une extrémité d'attaque tournée vers l'une, associée, des unités de poussoirs, une surface d'attaque, mobile dans une direction de réglage des unités d'entraînement, et une surface frontale, côté attaque, d'une, respective, des unités de poussoirs (9, 10, 11), opposée à la rainure de commande (8) respectivement associée, coopérant avec la surface d'attaque. L'invention est caractérisée en ce qu'au moins l'une des unités de poussoirs (9, 10, 11) est disposée, par rapport à l'axe de rotation d'arbre à cames (D), de façon que son axe médian longitudinal de poussoirs, s'étendant parallèlement aux axes médians longitudinaux de poussoirs (A1, A2, A3) d'au moins une autre unité de poussoirs, soit dans un plan (E) contenant l'axe de rotation (D) d'arbre de came, et s'étendant perpendiculairement aux axes médians longitudinaux de poussoirs (9, 10, 11), à distance de l'axe de rotation (D) de l'arbre à cames.
EP12719612.9A 2011-05-30 2012-04-18 Dispositif de réglage d'arbre à cames Active EP2715078B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL12719612T PL2715078T3 (pl) 2011-05-30 2012-04-18 Układ przestawiania wału krzywkowego

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011050730A DE102011050730A1 (de) 2011-05-30 2011-05-30 Nockenwellenverstellvorrichtung
PCT/EP2012/057039 WO2012163591A1 (fr) 2011-05-30 2012-04-18 Dispositif de réglage d'arbre à cames

Publications (2)

Publication Number Publication Date
EP2715078A1 true EP2715078A1 (fr) 2014-04-09
EP2715078B1 EP2715078B1 (fr) 2015-01-07

Family

ID=46046130

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12719612.9A Active EP2715078B1 (fr) 2011-05-30 2012-04-18 Dispositif de réglage d'arbre à cames

Country Status (6)

Country Link
US (1) US8939119B2 (fr)
EP (1) EP2715078B1 (fr)
CN (1) CN103597175B (fr)
DE (1) DE102011050730A1 (fr)
PL (1) PL2715078T3 (fr)
WO (1) WO2012163591A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013108027A1 (de) * 2013-07-26 2015-01-29 Eto Magnetic Gmbh Elektromagnetische Stellvorrichtung und System zur Verstellung einer Funktionalität eines Kraftfahrzeugaggregats
DE102014008156B4 (de) * 2014-05-30 2022-04-14 Daimler Ag Ventiltrieb für eine Brennkraftmaschine
US9583249B2 (en) 2014-10-31 2017-02-28 Husco Automotive Holdings Llc Methods and systems for push pin actuator
CN105863765A (zh) * 2016-05-18 2016-08-17 宁波圣龙汽车动力系统股份有限公司 气门升程可变的滑动式凸轮轴
CN106121764A (zh) * 2016-07-18 2016-11-16 杰锋汽车动力系统股份有限公司 一种用于可变气门升程系统的凸轮轴调节装置
JP7153586B2 (ja) * 2019-02-27 2022-10-14 株式会社オティックス 内燃機関の可変動弁機構

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10360287A1 (de) * 2003-02-05 2004-10-14 Ina-Schaeffler Kg Stößel in einem Ventiltrieb einer Brennkraftmaschine
DE102004037198A1 (de) * 2004-07-30 2006-03-23 Ina-Schaeffler Kg Ventiltrieb einer Brennkraftmaschine
DE102006051809A1 (de) 2006-11-03 2008-05-08 Schaeffler Kg Stellvorrichtung
DE102007028600B4 (de) 2007-06-19 2011-06-22 ETO MAGNETIC GmbH, 78333 Elektromagnetische Stellvorrichtung
DE102007040677A1 (de) 2007-08-29 2009-03-05 Schaeffler Kg Brennkraftmaschine mit variablem Gaswechselventiltrieb
DE102007057811B4 (de) * 2007-11-30 2015-04-30 Volkswagen Ag Ventiltrieb für Gaswechselventile einer Brennkraftmaschine
JP5444345B2 (ja) * 2008-08-01 2014-03-19 エト・マグネティック・ゲー・エム・ベー・ハー 電磁駆動装置
DE202008015980U1 (de) 2008-12-03 2010-04-29 Eto Magnetic Gmbh Elektromagnetische Aktuatorvorrichtung
DE102009015486A1 (de) * 2009-03-28 2010-09-30 Schaeffler Technologies Gmbh & Co. Kg Elektromagnetischer Aktuator
DE102009030375A1 (de) 2009-06-25 2010-12-30 Schaeffler Technologies Gmbh & Co. Kg Elektromagnetische Stellvorrichtung

Non-Patent Citations (1)

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Title
See references of WO2012163591A1 *

Also Published As

Publication number Publication date
EP2715078B1 (fr) 2015-01-07
CN103597175B (zh) 2016-09-07
PL2715078T3 (pl) 2015-04-30
US8939119B2 (en) 2015-01-27
US20140190430A1 (en) 2014-07-10
WO2012163591A1 (fr) 2012-12-06
DE102011050730A1 (de) 2012-12-06
CN103597175A (zh) 2014-02-19

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