EP2603675A1 - Dispositif de réglage d'un arbre à cames - Google Patents

Dispositif de réglage d'un arbre à cames

Info

Publication number
EP2603675A1
EP2603675A1 EP11735792.1A EP11735792A EP2603675A1 EP 2603675 A1 EP2603675 A1 EP 2603675A1 EP 11735792 A EP11735792 A EP 11735792A EP 2603675 A1 EP2603675 A1 EP 2603675A1
Authority
EP
European Patent Office
Prior art keywords
eccentric
gear
central axis
camshaft
adjusting device
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
EP11735792.1A
Other languages
German (de)
English (en)
Other versions
EP2603675B1 (fr
Inventor
Michael Schober
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.)
Magna Powertrain GmbH and Co KG
Original Assignee
Magna Powertrain GmbH and Co KG
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 Magna Powertrain GmbH and Co KG filed Critical Magna Powertrain GmbH and Co KG
Publication of EP2603675A1 publication Critical patent/EP2603675A1/fr
Application granted granted Critical
Publication of EP2603675B1 publication Critical patent/EP2603675B1/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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • 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
    • F01L1/352—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 bevel or epicyclic gear

Definitions

  • the invention relates to an adjustment for elatiwer too a camshaft with respect to a camshaft coaxial driving drive wheel, wherein the drive wheel and the camshaft are arranged coaxially with respect to a central axis of the adjusting device.
  • the crankshaft is coupled via a chain drive, a toothed belt drive or a toothed drive with a drive wheel which drives the camshaft substantially synchronously with the crankshaft.
  • the valve opening times of the internal combustion engine are controlled via the camshaft.
  • the phase position of the camshaft relative to the drive wheel (and thus relative to the crankshaft) can be selectively changed to influence the combustion processes taking place in the internal combustion engine.
  • a control gear can be effective between the drive wheel and the camshaft, which can be driven by means of an electric motor to adjust the camshaft relative to the drive wheel.
  • the use of an electric motor allows a particularly accurate control.
  • the actuating mechanism in such an arrangement forms a summation gear, in which the drive wheel is assigned to a first input, an output element of the electric motor (eg a motor pinion) is assigned to a second input and the camshaft or a camshaft section (eg a camshaft flange) corresponds to an output of the Summing gear is assigned.
  • the drive wheel, the Output member of the electric motor and the camshaft are rotatable coaxially with each other, so that the entire unit of drive wheel, electric motor, control gear and camshaft about a common axis, the so-called central axis, can rotate.
  • the actuating mechanism In order to adjust the camshaft relative to the drive wheel, comparatively high torques must be applied. For this puncture can be met by a small-sized, fast-running electric motor, the actuating mechanism must cause a high ratio of the speed of the electric motor to slow (based on a fixed drive wheel).
  • the actuating gear having an internally toothed gear and an externally toothed gear meshing therewith, wherein the internally toothed gear is rotatable about said central axis and the externally toothed gear is eccentric with respect to the central axis and driven in this eccentric arrangement to a circular movement about the central axis is.
  • the said circular motion is here - as the externally toothed gear rolls on the internally toothed gear - a relatively slow rotation of the externally toothed gear (relative to the innenverz zahnten gear) superimposed. If, in such an arrangement, the externally toothed gear has only slightly fewer teeth than the internally toothed gear meshing therewith (e.g., 1 to 5 tooth difference), this advantageously translates to high ratios (e.g., 60 to 300).
  • An object of the invention is to provide a camshaft adjusting device of the type mentioned, in which the actuating mechanism causes a high gear ratio with a compact design and high efficiency in the slow.
  • This object is achieved by an adjusting device with the features of claim 1, and in particular in that the externally toothed gear is eccentrically mounted on at least two eccentric shafts, each eccentric shaft is drivable for rotational movement about a respective eccentric axis, wherein the eccentric axes eccentric with respect to the central axis arranged and rotatable about the central axis.
  • At least two eccentric axes are provided, which are arranged eccentrically with respect to the genanten central axis of the adjusting device and in particular are arranged parallel to each other.
  • the arrangement of the fixed relative to each other eccentric axes can be rotated about the central axis, i. the arrangement of at least two eccentric axes is rotatable coaxially to the drive wheel, the electric motor and the camshaft, wherein the respective position of the eccentric axes is defined for example by a common carrier device.
  • Each eccentric axis is assigned a respective eccentric shaft.
  • Each eccentric shaft includes an eccentric portion (ie, a cam) and is drivable for rotational movement about the respective eccentric axis.
  • the said externally toothed gear which is connected to said inner Tooth gear is engaged, is mounted on the at least two eccentric shafts, so that by the rotational movement of the eccentric shafts about the respective eccentric axis, the externally toothed gear can be driven to said (eccentric) circular motion about the central axis.
  • the required eccentricity of the externally toothed gear can be represented by the respective eccentric portion of the eccentric shafts, wherein the eccentric axes associated with the eccentric shafts can jointly perform a rotational movement coaxial with the central axis.
  • the eccentric shafts which are rotatable about the eccentrically arranged eccentric axes, thus make it possible for the eccentric circular movement (with superimposed rotation) of the externally toothed toothed wheel to be guided back to a rotational movement about the central axis of the verse device, namely in the form of a rotation of the aforementioned Eccentric axes around the central axis. Therefore, the two inputs and the output of the adjusting gear can all be arranged coaxially to the central axis.
  • the externally toothed gear is mounted by means of a respective rolling bearing on the eccentric shafts.
  • the eccentric circular movement of the externally toothed gear and the resulting torque transmission can be represented with a particularly good efficiency.
  • the externally toothed gear can be supported by means of a respective sliding bearing on the eccentric shafts.
  • each eccentric shaft is rotatably mounted on a respective bearing pin - the so-called eccentric pin -, wherein the eccentric pins define said eccentric axes and are fastened to a common carrier device.
  • the eccentric shafts are designed in particular as hollow shafts, which are mounted on the inside of the eccentric pin.
  • the eccentric shafts for example, can engage directly in the manner of a peg in a common carrier device and be rotatably mounted on this outer side.
  • the eccentric shafts are in turn mounted on the eccentric pin by means of a respective further rolling bearing. As a result, the efficiency of the adjusting gear is further increased, since thus for the movement of the externally toothed gear a rolling bearing can be provided.
  • the internally toothed gear is rotatably connected to the drive wheel and the arrangement of the plurality of eccentric axes (in particular the arrangement of the plurality of eccentric pins) is rotatably connected to the camshaft.
  • the internal gear forms a Input and the arrangement of the multiple eccentric axes forms the output of the actuating gear.
  • said eccentric shafts are drivable by means of the electric motor to a rotational movement about the respective eccentric axis.
  • the eccentric shafts carrying the externally toothed gear are assigned to an input of the adjusting gear.
  • the eccentric shafts are drivable to a mutually synchronous rotational movement about the respective eccentric axis in order to effect the desired circular movement of the externally toothed gear.
  • each eccentric shaft with a respective coupling gear rotatably connected (in particular integrally formed).
  • the electric motor can drive a motor pinion, which is arranged coaxially with the central axis of the adjusting device and meshes with the coupling gears directly or via at least one common intermediate gear.
  • the coupling gears and the intermediate gear (if present) in each position of the adjusting gear are arranged radially completely within the toothing of the externally toothed gear.
  • the coupling gears and possibly the intermediate gear are arranged completely within an imaginary to the central axis concentric cylinder jacket, wherein the cylinder shell is in each gear position completely within the teeth of the external gear, so that the tooth width of the external gear and also the tooth width of the internally toothed Gear can continue axially via the coupling gears and the intermediate gear.
  • the coupling gears or the intermediate gear can thus be arranged axially completely or partially within the externally toothed gearwheel and the internally toothed gearwheel. This shortens the axial length of the adjusting gear.
  • two, three or four eccentric shafts are provided, which are rotatably driven about a respective eccentric axis in order to drive the externally toothed gear, wherein the
  • Eccentric axes are preferably arranged distributed in a uniform angular pitch about the central axis.
  • Fig. 1 shows a side view of an adjusting device according to the invention.
  • Fig. 2 shows a cross section along the plane II-II according to
  • Fig. 3 shows a cross section along the plane III-III according to
  • Fig. 1. 4 shows a longitudinal section along the plane IV-IV according to FIG. 2.
  • Fig. 5 shows a longitudinal section along the plane V-V according to
  • Fig. 1 which is rotated relative to the sectional plane of FIG. 4 by 90 °.
  • the adjustment device shown in FIGS. 1 to 5 is used to Relatiwer ein a camshaft 1 1 of a Verbrennungskraftmaschi- ne not shown with respect to a camshaft 11 coaxially driving drive wheel 13, which is coupled to drive, for example via a chain drive, not shown, with a crankshaft of the internal combustion engine.
  • the drive wheel 13 and the camshaft 1 1 are arranged coaxially with respect to a central axis A of the adjusting device.
  • the drive wheel 13 is coupled to the camshaft 11 via a control gear 15 which can be driven by means of an electric motor 17 in order to adjust the phase position of the camshaft 1 1 relative to the drive wheel 13.
  • the adjusting gear 15 comprises an internally toothed gear 19, which is rotatably supported via a rolling bearing 21 on a carrier device 23 of the adjusting gear 15 coaxially with the central axis A.
  • the internal gear 19 is in engagement with an externally toothed gear 25.
  • the externally toothed gear 25 is arranged slightly eccentric with respect to the central axis A, and it is in this slightly eccentric arrangement to a circular motion about the central axis A drivable.
  • the number of teeth difference between the internal gear 19 and the external gear 25 is very small.
  • the externally toothed gearwheel 25 has only one, two, three, four or five teeth less than the internally toothed gear 25. Tooth gear 19. Accordingly, as is apparent in particular from FIG. 3, the eccentricity of the externally toothed gear 25 with respect to the central axis A is very small. In the upper part of Fig. 3, the externally toothed gear 25 is in engagement with the internal gear 19, while in the lower portion of Fig. 3, the externally toothed gear 25 is just out of engagement with the internal gear 19.
  • FIG. 3 shows that the externally toothed gearwheel 25 is mounted on two eccentric shafts 29 via a respective rolling bearing 27.
  • Each of the two eccentric shafts 29 is in turn supported by a rolling bearing 31 on a respective eccentric pin 33 and rotatable about a respective eccentric axis B.
  • the two eccentric pins 33 and thus the two eccentric axes B are arranged eccentrically with respect to the central axis A.
  • the two eccentric pins 33 extend parallel to each other, and they are attached to the support means 23, so that the two eccentric pins 33 and thus the two eccentric axes B are rotatable about the central axis A in a fixed relative position. It can be seen from FIG.
  • the eccentricity of the respective outer circumference of the eccentric shafts 29 with respect to the respective eccentric axis B corresponds to the eccentricity of the externally toothed gearwheel 25 with respect to the central axis A.
  • the eccentricity of the eccentric axes B with respect to the central axis A is significantly greater than the eccentricity of the externally toothed gear 25 with respect to the central axis A.
  • the central axis A and the eccentric axes B are within the pitch circle of the externally toothed
  • each eccentric shaft 29 rotatably connected to a respective coupling gear 34, namely formed in one piece.
  • Fig. 2 it is shown that the two coupling gears 34 via a common intermediate gear 35 with a motor pinion 37 are engaged.
  • the intermediate gear 35 is rotatably mounted on a bearing pin 36 which is aligned parallel to the eccentric 33 and also secured to the support means 23 (Fig. 5).
  • Fig. 2 3 and 5 screws 39 are shown, through which the actuating gear 15, by means of the support means 23, fixed to a flange 24 of the camshaft 11 is connected.
  • One of the screws 39 passes coaxially through the bearing pin 36 and screwed this bearing pin 36 via the support means 23 with the cam shaft flange 24th
  • the motor pinion 37 is driven by the electric motor 17 via a motor shaft 41 (FIGS. 4 and 5).
  • the intermediate gear 35 is not mandatory; instead, the motor pinion 37 may also drive the two coupling gears 34 directly. In both cases, a synchronous drive of the two eccentric shafts 29 takes place through the motor pinion 37.
  • the actuating mechanism 15 forms a summing gear to vary by means of the electric motor 17, the phase angle of the camshaft 1 1 relative to the drive wheel 13 can.
  • the internal gearwheel 19 assigned to the drive wheel 13 forms a first input.
  • the motor gear 17 associated with the electric motor 17 forms a second input.
  • the eccentric 33 carrying and with the cam shaft flange 24 fixedly connected support means 23 forms an output of the actuating gear 15th
  • the two inputs (drive wheel 13 with internal gear 19 and motor shaft 41 with motor pinion 37) and the output (eccentric cam 33 with camshaft 1 1) of the actuating gear 15 coaxial with the central axis A and nevertheless for all rotatable elements of the adjusting gear 15 to allow a rolling bearing.
  • the adjusting device shown is therefore characterized despite high reduction effect of the actuating gear 15 with a small size by a high efficiency.
  • the coupling gears 34 and the intermediate gear 35 may be formed so smaller that they are arranged radially completely within the toothing of the external gear 25. In this way, a shortened axial length of the adjusting gear 15 can be achieved, namely when the externally toothed gear 25 and accordingly the internally toothed gear 19, the coupling gears 34 and the intermediate gear 35 axially partially or completely overlap.

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 pour le réglage relatif d'un arbre à cames par rapport à une roue d'entraînement entraînant l'arbre à cames coaxialement, ledit dispositif comprenant un mécanisme de réglage fonctionnant entre la roue d'entraînement et l'arbre à cames, et qui peut être entraîné au moyen d'un moteur électrique pour le réglage de l'arbre à cames. Le mécanisme de réglage présente une roue dentée à denture intérieure et une roue dentée à denture extérieure en prise avec cette dernière, la roue dentée à denture intérieure pouvant tourner autour d'un axe central du dispositif de réglage et la roue dentée à denture extérieure étant disposée de manière excentrique par rapport à l'axe central et pouvant être entraînée dans un mouvement circulaire autour de ce dernier. La roue dentée à denture extérieure est montée de manière excentrique sur au moins deux arbres excentriques, chaque arbre excentrique pouvant être entraîné dans un mouvement de rotation autour d'un axe excentrique respectif, les axes excentriques étant disposés de manière excentrique par rapport à l'axe central et pouvant tourner autour de ce dernier.
EP11735792.1A 2010-08-10 2011-07-06 Dispositif de réglage d'un arbre à cames Active EP2603675B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010033897.4A DE102010033897B4 (de) 2010-08-10 2010-08-10 Nockenwellen-Verstellvorrichtung
PCT/EP2011/003363 WO2012019680A1 (fr) 2010-08-10 2011-07-06 Dispositif de réglage d'un arbre à cames

Publications (2)

Publication Number Publication Date
EP2603675A1 true EP2603675A1 (fr) 2013-06-19
EP2603675B1 EP2603675B1 (fr) 2014-11-26

Family

ID=44628961

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11735792.1A Active EP2603675B1 (fr) 2010-08-10 2011-07-06 Dispositif de réglage d'un arbre à cames

Country Status (7)

Country Link
US (1) US8881701B2 (fr)
EP (1) EP2603675B1 (fr)
JP (1) JP5646058B2 (fr)
KR (1) KR101510971B1 (fr)
CN (1) CN103080486B (fr)
DE (1) DE102010033897B4 (fr)
WO (1) WO2012019680A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016210710A1 (de) 2015-08-14 2017-02-16 Magna Powertrain Bad Homburg GmbH Verstellvorrichtung zur Verstellung einer Nockenwelle

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04105906U (ja) * 1991-02-27 1992-09-11 株式会社アツギユニシア 内燃機関のバルブタイミング制御装置
US7086309B2 (en) * 2002-09-19 2006-08-08 The Johns Hopkins University Planetary-harmonic motor
DE102004007052A1 (de) * 2004-02-13 2005-09-08 Daimlerchrysler Ag Verstelleinrichtung für eine Welle
JP2007198376A (ja) * 2006-01-26 2007-08-09 Delphi Technologies Inc 可変カム位相装置
JP4438768B2 (ja) * 2006-04-27 2010-03-24 株式会社デンソー バルブタイミング調整装置
JP4360426B2 (ja) * 2007-07-09 2009-11-11 株式会社デンソー バルブタイミング調整装置
US8418665B2 (en) * 2008-04-23 2013-04-16 Nittan Valve Co., Ltd. Variable phase controller for automotive engine
WO2010046974A1 (fr) * 2008-10-22 2010-04-29 日鍛バルブ株式会社 Dispositif de phase variable d’arbre à cames dans un moteur pour automobile
US8245679B2 (en) * 2008-10-22 2012-08-21 Denso Corporation Variable valve timing apparatus
JP4605292B2 (ja) * 2008-10-22 2011-01-05 株式会社デンソー バルブタイミング調整装置

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2012019680A1 *

Also Published As

Publication number Publication date
EP2603675B1 (fr) 2014-11-26
US20130291815A1 (en) 2013-11-07
JP2013533431A (ja) 2013-08-22
KR20130038365A (ko) 2013-04-17
CN103080486B (zh) 2015-05-06
DE102010033897B4 (de) 2017-03-16
JP5646058B2 (ja) 2014-12-24
WO2012019680A1 (fr) 2012-02-16
US8881701B2 (en) 2014-11-11
DE102010033897A1 (de) 2012-02-16
KR101510971B1 (ko) 2015-04-10
CN103080486A (zh) 2013-05-01

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