WO2012130487A2 - Dispositif de déphasage discret - Google Patents

Dispositif de déphasage discret Download PDF

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Publication number
WO2012130487A2
WO2012130487A2 PCT/EP2012/050606 EP2012050606W WO2012130487A2 WO 2012130487 A2 WO2012130487 A2 WO 2012130487A2 EP 2012050606 W EP2012050606 W EP 2012050606W WO 2012130487 A2 WO2012130487 A2 WO 2012130487A2
Authority
WO
WIPO (PCT)
Prior art keywords
drive wheel
discrete phase
roller
contours
contour
Prior art date
Application number
PCT/EP2012/050606
Other languages
German (de)
English (en)
Other versions
WO2012130487A3 (fr
Inventor
Michael Breuer
Andres Tönnesmann
Andreas Köster
Costantino Brunetti
Original Assignee
Pierburg 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 Pierburg Gmbh filed Critical Pierburg Gmbh
Publication of WO2012130487A2 publication Critical patent/WO2012130487A2/fr
Publication of WO2012130487A3 publication Critical patent/WO2012130487A3/fr

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
    • 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
    • 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
    • F01L1/356—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 making the angular relationship oscillate, e.g. non-homokinetic drive
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H35/00—Gearings or mechanisms with other special functional features
    • F16H35/008—Gearings or mechanisms with other special functional features for variation of rotational phase relationship, e.g. angular relationship between input and output shaft

Definitions

  • the invention relates to a device for discrete phase shift of a rotational angle between a drive wheel and an output shaft with a drive wheel, a coupling gear, an output shaft which is driven via the coupling gear and an actuator, in the actuation of the rotational angle of the drive wheel to the output shaft via the coupling gear is displaceable ,
  • Phase shifting devices are used, for example, to shift the angle of rotation between a crankshaft and a camshaft of an internal combustion engine. Also, such devices can be used in internal combustion engines for cycle accurate control of an exhaust gas recirculation system. The phase shift is used for variable valve timing to improve the combustion process in the engine.
  • phase shift of the camshaft for example, vane-cam phaser, camshaft chains are verstellor or axially displaceable
  • US 5,680,836 discloses a device for phase shifting between a camshaft and a crankshaft with a planetary gear.
  • a planet carrier is fixedly mounted on a camshaft, wherein the planetary gears with the sun gear and an internal toothing of a drive wheel are engaged.
  • the drive wheel is driven via a chain drive in a fixed transmission ratio via the crankshaft, for example.
  • a Angle adjustment takes place in this embodiment by rotating the sun gear by means of an actuator.
  • a disadvantage of such a design is that for holding the sun gear, an electric actuator must be supplied with voltage, since there is no self-locking of the drive. Accordingly, there is a high permanent energy requirement.
  • Another device for angular adjustment of a shaft relative to a drive wheel is known from DE 197 06 855 AI.
  • the actuator consists of a two pivot axes connecting rocker, wherein the pivot axes are formed by pins which are guided in slots.
  • the rotary angular adjustment of the first pin is moved on a radial straight line while the second pin is moved along a EUipsenUnie, whereby a relative rotation between the drive wheel and the output shaft is formed.
  • this arrangement is very limited in terms of the maximum adjustment angle by a necessary window in a flange which is arranged on the output shaft.
  • a synchronization between the gears for adjustment is required.
  • the adjustment of the actuating element takes place hydraulically due to the eccentric arrangement. This hydraulic pressure must be provided over the entire adjustment period.
  • the actuator to be used must be designed to be large enough to apply the necessary restoring forces. It is therefore an object to provide a device for discrete phase shift of the angle of rotation between a drive wheel and an output shaft, in which the mechanical load of the actuator and at the same time the energy requirement of the actuator are minimized.
  • the device should be robust while requiring only a small amount of space.
  • a first of the at least two contours is a circular contour. While the roller or the gear runs in this circular contour, there is no adjustment of the angle of rotation, since the eccentric is not rotated by the circular contour to the drive wheel. Accordingly, the Corresponding diameter of the circle of the envelope of the roller or the gear in a movement in which the position of the eccentric remains unchanged relative to the drive wheel.
  • a second and third contour have rotational angle ranges whose diameter is greater or smaller than that of the circle of the first contour and rotational angle ranges which have the same diameter as the circle of the first contour.
  • the area of the same diameter serves as a synchronization area, in which the pass can be changed from one contour to the other.
  • the other rotation angle ranges produce in a four-bar linkage rotation of the Exzenterabtriebsachse relative to the drive wheel.
  • the output shaft is also rotated by a corresponding angle. This means that during one revolution of the roller on the contour the
  • the first stationary axis of the four-bar link is formed by a first shaft, which is rotatably mounted in the drive wheel and auf0 of the eccentric is arranged.
  • a first connecting rod is rotatably mounted, at the opposite end a second shaft is rotatably mounted, on which the roller or the gear and a second connecting rod are rotatably mounted and which serves as a second movable axis.
  • a third shaft is rotatably supported, the opposite end of which is secured to the drive wheel and serves as the second stationary axle to the driving wheel.
  • the first shaft is centrally rotatably mounted in the drive wheel. This facilitates the storage of the eccentric shaft, whereby the life of the device is increased.
  • a gear is rotatably fixed to the first time, which is coupled via a reduction gear to the output shaft.
  • a particularly simple form of adjustment results when the contours are arranged one behind the other and are axially displaceable by the actuator.
  • the device has a second four-bar link, whose two stationary axes and whose first movable axis correspond to the axes of the first four-bar linkage and on the second movable axis of a second roller or a second gear is rotatably mounted, the or in to orbits corresponding to the first contours.
  • This second four-bar joint reduces the degrees of freedom of the movement of the roller, so that a necessary for correct function rolling of the roller on the contour is largely ensured.
  • the other contours are axially adjustable together with the first contours on the actuator.
  • a synchronization is ensured during the movement.
  • the means for pressing the roller or the gear against the contour are formed by a spring element.
  • a spring element biases the connecting rods mounted on the second stationary shaft to the outside.
  • the spring element is arranged particularly simple and easy to install. It is particularly advantageous if a helical spring is arranged as a spring element about the second stationary axis, whose spring limbs are prestressed against abutments which are arranged on the connecting rods rotatably mounted on the second stationary axis. This type of arrangement of the spring element is simple and therefore inexpensive to carry out.
  • FIG. 1 shows a side view of a device according to the invention for the discrete phase shift in a schematic representation.
  • Figure 2 shows a top view of the device of Figure 1 without contours in a schematic representation.
  • FIG. 3 shows schematically a comparison of the different contours.
  • the illustrated in the figures embodiment of a discrete phase shift device according to the invention consists of a drive wheel 2, which may for example be designed as a chain nritzel and coupled via a chain with a crankshaft of an internal combustion engine.
  • This drive wheel 2 is mounted on an output shaft 4, which according to the invention can be rotated in discrete steps to the drive wheel 2 in order to realize a phase shift of the opening times of the intake valves to the rotational angle of the crankshaft and which serves as an axis during the rotation of the drive wheel 2.
  • a first time 8 is mounted, which serves as the first stationary to drive wheel 2 axis of a coupling mechanism serving as four-bar linkage 10.
  • This fixed to the drive wheel 2 axis is simultaneously the axis of rotation of an eccentric 12 which is mounted on the first shaft 8 and whose Exzenterabtriebsachse 14 is thus rotated about the first stationary axis of rotation.
  • This Exzenterabretesachse 14 serves as the first to the drive wheel 2 movable axis of the four-bar 10th
  • a first connecting rod 16 is arranged, the opposite end is rotatably mounted on a second shaft 18 which serves as the second drive wheel 2 movable axis of the four-bar linkage 10 and on the additionally rotatably mounted a roller 20 is.
  • a first end of a second connecting rod 22 is further arranged, whose opposite end encloses a third shaft 24, which serves as a second stationary axis of the four-bar 10 and which is also secured in the drive wheel 2.
  • this third shaft 24 is arranged substantially on the side of the drive wheel 2 opposite the first shaft 8.
  • a third connecting rod 26 is additionally supported, the opposite end is in turn mounted on a fourth shaft 28 on which a second roller 30 is additionally mounted and which serves as a second movable axis to the drive wheel of a second four-bar link 32, the first movable axis in turn is the Exzenterabtriebsachse 14, with which the fourth shaft 28 is rotatably connected by means of a fourth connecting rod 34.
  • a spring element 36 is arranged in the form of a helical spring, the two spring legs 38, 40 bear against stops 42, 44. These stops 42, 44 are arranged in the form of bolts on the two attached to the third shaft 24 connecting rods 22, 26.
  • the spring element is arranged such that the two connecting rods 22, 26 spread apart from each other and thus the two rollers 20, 30 are pressed outwardly against a respective contour 46, 48, 50, 52, 54, 56, thereby ensuring that this both rollers 20, 30 on the contours 46, 48, 50, 52, 54, 56 unroll and not stand out from these.
  • each roller 20, 30 each include three different contours 46, 48, 50, 52, 54, 56, which are arranged axially one behind the other and can be moved together via an actuator 58 in the axial direction.
  • one of these contours 46, 48 is circular.
  • the axial spacing of these contours 46, 48 corresponds to the axial spacing of the rollers 20, 30, so that the rollers 20, 30 always run simultaneously in the associated circular contour 46, 48.
  • the further contours 50, 52 in the present exemplary embodiment, as can be seen in FIG. 3, have a shape modified relative to the circular contour 46, 48, in which the distance to the center in a rotation angle range 60 is slightly larger. In addition are in a further rotation angle range 62 of approximately 90 °, the circular contours 46, 48 modeled.
  • the contour 50 of the roller 20 is offset from the contour 52 of the second roller 30, so that a completely guided rotational movement of the eccentric 12 follows.
  • the same applies to the contours 5 54, 56 wherein the circular rotation angle range of the first roller 20 belonging to contours 46, 50, 54 is arranged in the same area, so they are arranged axially one behind the other.
  • the extended rotation angle range 60 of the contours 54, 56 is arranged in a different angle of rotation range than that of the contours 50, 52, so that a different movement of the eccentric output axis 14 it follows, as will be described in more detail below.
  • a gear 64 is rotatably disposed, which meshes with a gear 66 which is rotatably mounted on the output shaft 4, respectively. Accordingly, the rotational movement of the gear 64, which is held relative to the drive wheel 2, transmitted to the gear 66.
  • Any other translation can of course also be made by appropriate choice of gears.
  • large ratios in the range of, for example, 80: 1 are required to provide a reasonable discrete angular range.
  • Such translations can be realized for example by downstream differential planetary gear 5.
  • the device shown when used as a camshaft divider to modify accordingly.
  • the contours 46, 48, 50, 52, 54, lo 56 are axially displaced via the actuator 58.
  • the control for shifting takes place in such a way that the axial movement takes place in the phase in which the two rollers 20, 30 are located in the circular contoured angular regions 60 of the contours 50, 52, as a result of which the rollers 20, 30 continue to unroll. If the contours 50, 52 reached, takes place in the rotation angle range 62 a
  • the device described for the discrete rotational angle adjustment of a drive wheel to an output shaft thus allows adjustment without having to bring in the adjustment of external energy. Only the short-term adjustment of the contours in the axial direction is required, in which no torque is applied. This is completely taken from the movement of the crankshaft itself. Correspondingly small drives with low energy consumption can be used.
  • the second lever can be dispensed with at sufficient angular speeds.
  • a pressing of the roller and a rotational movement of the eccentric in a constant direction during the adjustment can be already sufficiently ensured by the centrifugal forces occurring if necessary.
  • the eccentric shaft as a central shaft in the drive wheel to arrange and to translate their rotation translated in the further power flow to the camshaft.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Retarders (AREA)
  • Arrangement And Driving Of Transmission Devices (AREA)
  • Transmission Devices (AREA)

Abstract

Les dispositifs servant à créer un déphasage entre un pignon d'entraînement et un arbre mené, dans lesquels un couple à introduire dans le système est exercé sur l'arbre mené pour assurer le déphasage, sont connus. L'invention concerne un dispositif comprenant un pignon d'entraînement (2), un mécanisme articulé (10), un arbre mené (4) entraîné par l'intermédiaire du mécanisme articulé (10) et un actionneur (58) dont l'actionnement permet de réaliser un décalage de l'angle de rotation du pignon d'entraînement par rapport à l'arbre mené par l'intermédiaire du mécanisme articulé. Selon l'invention, un quadrilatère articulé (10), comprenant deux axes (8, 24) fixes par rapport au pignon d'entraînement (2) et deux axes (14, 18) mobiles par rapport à ce dernier, sert de mécanisme articulé; ce quadrilatère articulé (10) présente un excentrique (12) dont l'axe de rotation est le premier (8) des axes fixes et dont l'axe mené (14) est le premier des axes mobiles et une poulie (20) ou une roue dentée, qui tourne de manière sélective dans l'un d'au moins deux contours (46, 50, 54) pouvant être déplacés par rapport à la poulie (20) ou à la roue dentée, est agencée sur le deuxième axe mobile (18), la poulie (20) ou la roue dentée étant sollicitée par des moyens (36; 32) servant à la plaquer contre le contour (46, 50, 54). La consommation d'énergie dans ce type de réalisation est considérablement réduite.
PCT/EP2012/050606 2011-03-29 2012-01-17 Dispositif de déphasage discret WO2012130487A2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011001612.0 2011-03-29
DE201110001612 DE102011001612B4 (de) 2011-03-29 2011-03-29 Vorrichtung zur diskreten Phasenverschiebung

Publications (2)

Publication Number Publication Date
WO2012130487A2 true WO2012130487A2 (fr) 2012-10-04
WO2012130487A3 WO2012130487A3 (fr) 2012-11-22

Family

ID=45833317

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2012/050606 WO2012130487A2 (fr) 2011-03-29 2012-01-17 Dispositif de déphasage discret

Country Status (2)

Country Link
DE (1) DE102011001612B4 (fr)
WO (1) WO2012130487A2 (fr)

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5680836A (en) 1996-09-17 1997-10-28 General Motors Corporation Planetary cam phaser with lash compensation
DE19706855A1 (de) 1997-02-21 1998-08-27 Bauss Hans Werner Vorrichtung zur Winkelverstellung einer Welle gegenüber ihrem Antriebsrad

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2079009A (en) * 1936-06-03 1937-05-04 S H Mcevoy Automatically variable camshaft
FR2518677A1 (fr) * 1981-12-23 1983-06-24 Citroen Sa Dispositif d'entrainement non homocinetique, notamment pour arbre a cames de moteur a combustion interne
GB8511680D0 (en) * 1985-05-09 1985-06-19 Stidworthy F M Variable phase & oscillatory drives
DE3920895A1 (de) * 1989-06-26 1991-01-03 Bayerische Motoren Werke Ag Betaetigungsvorrichtung fuer ein gaswechselventil einer brennkraftmaschine
IT1259099B (it) * 1992-05-19 1996-03-11 Carraro Spa Variatore di fase
DE59307123D1 (de) * 1992-12-13 1997-09-18 Bayerische Motoren Werke Ag Ventilsteuerung für eine brennkraftmaschine
DE102004027636A1 (de) * 2004-06-05 2006-01-05 Robert Bosch Gmbh Steuereinrichtung zum Verstellen des Drehwinkels einer Nockenwelle
DE102005053119A1 (de) * 2005-11-08 2007-05-10 Robert Bosch Gmbh Vorrichtung zur Verstellung der relativen Drehwinkellage zwischen Nockenwelle und Antriebsrad
JP4463211B2 (ja) * 2006-01-16 2010-05-19 株式会社デンソー バルブタイミング調整装置
DE102008022932B4 (de) * 2008-05-09 2021-08-05 Schaeffler Technologies AG & Co. KG Montageanordnung eines Phasenstellers und Phasensteller
DE102009054687A1 (de) * 2009-12-15 2011-06-16 Robert Bosch Gmbh Viergelenk-Koppelgetriebe sowie Abgasturbolader

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5680836A (en) 1996-09-17 1997-10-28 General Motors Corporation Planetary cam phaser with lash compensation
DE19706855A1 (de) 1997-02-21 1998-08-27 Bauss Hans Werner Vorrichtung zur Winkelverstellung einer Welle gegenüber ihrem Antriebsrad

Also Published As

Publication number Publication date
DE102011001612A1 (de) 2012-10-04
WO2012130487A3 (fr) 2012-11-22
DE102011001612B4 (de) 2013-02-28

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