WO2008052884A1 - Dispositif de réglage - Google Patents

Dispositif de réglage Download PDF

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Publication number
WO2008052884A1
WO2008052884A1 PCT/EP2007/061089 EP2007061089W WO2008052884A1 WO 2008052884 A1 WO2008052884 A1 WO 2008052884A1 EP 2007061089 W EP2007061089 W EP 2007061089W WO 2008052884 A1 WO2008052884 A1 WO 2008052884A1
Authority
WO
WIPO (PCT)
Prior art keywords
adjusting device
pin
actuator
rest position
locking pin
Prior art date
Application number
PCT/EP2007/061089
Other languages
German (de)
English (en)
Inventor
Andreas Nendel
Harald Elendt
Original Assignee
Schaeffler 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 Schaeffler Kg filed Critical Schaeffler Kg
Publication of WO2008052884A1 publication Critical patent/WO2008052884A1/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
    • 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
    • F01L13/0042—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 being 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
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values

Definitions

  • the invention relates to an adjusting device with at least one mounted in a longitudinal guide of a housing and relative to the housing from a retracted rest position in a working position extendable actuator pin for adjusting a cooperating with the adjusting machine part.
  • This is in particular designed as a support shaft rotatably and longitudinally displaceable cam piece of a variable-stroke valve drive of an internal combustion engine and has a spiral displacement groove into which a first end portion of the actuator pin can be coupled in the working position.
  • the adjusting device has a controllable holding device for holding the force-loaded by a spring means in the direction of the working position Aktuatorchans in the rest position and for releasing the Aktuator reconstructs from the rest position.
  • Such a control device is apparent from the considered as generic type WO 03/021 612 A1.
  • Its holding device for the actuator pin is based on the interaction of an electromagnet with a permanent magnet fixed to the actuator pin, the magnetic attraction of which holds the actuator pin against the force of the spring means in the rest position on the non-energized electromagnet.
  • To release the actuator pin from the rest position Position is merely a pulse-like current application of the electromagnet to overcome the magnetic attraction of the permanent magnet required, the actuator pin is accelerated not only by the force of the spring means but also by the force of a magnetic repulsion effect between the permanent magnet and the energized electromagnet in the direction of the working position.
  • Such, with low power consumption quickly and temporally exactly switching actuator is particularly suitable for adjusting a variable stroke valve train, as is apparent, for example from DE 10 2004 021 376 A1.
  • the stroke variability of the valve drive proposed there is based on a cam piece with cams arranged adjacently thereon, the different opening characteristics of which are selectively transmitted to a gas exchange valve by means of a conventionally rigid cam follower.
  • the cam piece is non-rotatably but longitudinally displaceable on a carrier shaft and has two helical and oppositely extending sliding grooves, in which the end portions of the actuator pins of two adjusting devices of the type mentioned are alternately coupled.
  • the present invention is therefore the object of an adjusting device of the type mentioned in such a way that the disadvantages are avoided. Accordingly, the holding device should have a minimum of additional radial space required compared with the actuator pin, so that the adjusting device can be integrated into existing machine architecture without or at least with reasonable design effort. Ren and in particular in cylinder heads of internal combustion engines can be integrated. In addition, the actuator should be as simple as possible and inexpensive to produce under high volume conditions.
  • the holding device is formed positively acting and has at least the following features:
  • a controllable actuator with a displaceably arranged in the longitudinal bore locking pin which moves in the transverse bore and cooperating with the locking bodies such that the locking pin, the locking body, for holding the Aktuatorchans in the rest position, supported in radially outward direction against the radial recess and that of Locking pin releases the locking body, for releasing the actuator pin from the rest position, in a radially inward direction.
  • the adjusting device has a holding device which does not fix the actuator pin via magnetic attraction forces with correspondingly large effective area according to the cited prior art, but by positive engagement against the force of the spring means in its rest position.
  • the remaining space required for the holding device is now significantly reduced, since the required holding force here as a form-fitting clamping force generated over a magnetic effective area considerably smaller Contact area required.
  • this contact surface is formed by the radial recess, in which the blocking member or members projecting from the transverse bore thereof in the rest position of the actuator pin and supported by the blocking pin are supported to generate the greatest possible clamping forces.
  • the applied to release the actuator pin from this locked rest position of the actuator actuation forces only need to overcome the frictional forces occurring between the locking pin and the locking bodies. Since these frictional forces are many times lower than the producible clamping forces, the actuating device can also be designed to be very small, regardless of its physical operating principle, as far as possible.
  • the transverse bore should be formed as a through hole and two locking bodies arranged on both sides of the locking pin should be provided.
  • this arrangement is advantageous over only one blocking body, since larger clamping forces can be generated either with identical dimensioning of the blocking body or with smaller dimensioning of the blocking body - corresponding to a further reduced space requirement of the holding device - the possibly already sufficient clamping force of only one clamping body can be generated.
  • this arrangement has the advantage of fewer components and the restriction to only one transverse bore in Aktuatorchan compared to three or more sprags.
  • the blocking body should be formed as balls. These can be removed as extremely low-cost mass product of a WälzSystemfertigung, it may be appropriate that a cooperating with the balls end portion of the locking pin tapers in the direction of its ball-side end conically. This embodiment allows a particularly low-wear sliding or rolling contact between the balls and the locking pin, just before the actuator pin returns to its rest position. Because in this phase of movement they must first completely in the transverse bore aufhaltenden balls are displaced by the then running in the transverse bore locking pin as free of edge pressures radially outward in the direction of the radial recess.
  • the radial recess is formed as an annular groove with a radially inwardly conically tapering and serving in the rest position of Aktua- torx as a support surface for the balls axial shoulder.
  • the annular groove represents an advantageous alternative to locally formed radial recesses which, in accordance with the number of balls used, can be designed, for example, as bores aligned with the transverse bore in the longitudinal guide of the housing.
  • a bushing arranged in a stationary manner in the housing is provided as part of the longitudinal guide, which bushing axially delimits the annular groove with its annular end face facing the axial shoulder.
  • the housing makes sense to provide the housing with a diameter-stepped bore, so that, based on the first end portion of the Aktuatorrobs, this side of the transverse bore extending part of the longitudinal guide directly in the housing and beyond the transverse bore extending part of the longitudinal guide formed by the nenmantel
  • the actuating device should be designed as a Elektrohubmagnet with a locking pin actuated anchor.
  • the actuator can also be based on other known, for example, hydraulic or pneumatic action principles, the electromagnetically controlled locking pin can be actuated particularly quickly and with high precision.
  • the locking pin and the armature can also be combined to form a one-piece component. In this case, the different mechanical and electromagnetic requirements for the component properties, for example, by adapted material selection with an optionally required, wear-resistant surface coating can be taken into account.
  • the adjusting device should be designed as a structural unit comprising at least the housing, a housing arranged in the group of actuator pins, the actuator pins kraftbeaufier waveden spring means and the mutually independently controllable holding devices.
  • a structural unit is particularly suitable in the case of the variable-stroke valve drive as a separately manufactured from the cylinder head of the engine and ready-to-install supplier part, which can also be inexpensively constructed modular depending on the number of actuator pins.
  • it can nevertheless be provided to arrange the actuator pins in a housing common to the machine part and the adjusting device, so that the actuator pins are mounted as housings in the cylinder head of the internal combustion engine directly or by means of bushes in the case of the variable-displacement valve drive.
  • the actuator pin and designed as a helical compression spring spring means are to be rotatably decoupled by means of a sliding disk arranged between them.
  • the locking pin should be subjected to force in the direction of the transverse bore by the force of a spring formed as a helical compression spring further Feeder, wherein the further spring means is supported on a fixedly connected to the locking pin Axialbund.
  • a Federkraftbeetzschlagung the locking pin for the function of the adjusting device is not absolutely necessary, since this would be kraftbeaufschlagbar in a particularly low-friction trained adjusting device only by gravity action in the direction of the transverse bore, supports the other spring means the predetermined for the function of the actuator movement sequence of locking pin. This sequence of movements is explained in more detail in the context of the description of an embodiment.
  • the spring means and the further spring means are concentric and abut with their the sliding disk or the Axialbund facing away from the spring ends to a stationary in the housing support disk.
  • the support disk also has a surface on which the ends of the two helical compression springs can rotate simultaneously. This is useful if the rotation of the actuator pin is transmitted by friction in the longitudinal bore on the locking pin and consequently its the axial compression coil supporting the helical compression spring. Also in this case would be without further measures the risk that the rotation of the Axialbunds is transmitted to the helical compression spring of the locking pin and leads to excessive friction force on the opposite spring support to an unacceptable twist this helical compression spring. To avoid a resulting damage to the helical compression spring, it can Nevertheless, it may also be expedient to additionally or alternatively provide the spring support of the axial collar with favorable sliding properties.
  • the support plate can also serve for defined stroke limitation of the locking pin by the locking pin has a fixedly connected to this further Axialbund, which abuts in the direction of the transverse bore on the side facing away from the spring ends of the support disk.
  • Figure 1 is designed as a structural unit actuating device with three Aktua- torloche in perspective longitudinal section and
  • FIG. 2 shows the adjusting device according to Figure 1 in uncut perspective view.
  • an actuating device 1 which is used to control a known variable stroke drive of an internal combustion engine, not shown here.
  • the basic operating principle of such a valvetrain is derived, for example, from the publications DE 196 11 641 C1 and DE 10 2004 021 376 A1 cited at the beginning, and can be summarized to the effect that instead of a conventional one rigidly formed camshaft, a carrier shaft is provided with a rotatably and longitudinally displaceable cam piece arranged thereon.
  • the cam piece has one or more groups of axially adjacent cams with a different opening profile, which serve for operating point-dependent actuation of gas exchange valves.
  • each of the longitudinal guides 5 is formed, on the one hand, by the diameter-reduced section of a stepped bore 6 in the housing 4 and, on the other hand, by the inner lateral surface 7 of a bush 8 drawn into the diameter-enlarged section of the stepped bore 6.
  • radial recesses 9 in the form of an annular groove 10 which is limited in the axial direction by a housing-side axial shoulder 1 1 on the one hand and by a sleeve-side annular end face 12 on the other.
  • the actuator pins 3 are shown in different axial positions.
  • the left in Figure 1 actuator pin 3 is in its retracted rest position, ie, the first end portion 2 is out of engagement with the sliding groove.
  • the right actuator pin 3 is in its extended working position, ie, the first end portion 2 is in engagement with the sliding groove.
  • the middle actuator pin 3 is in the state of movement shortly after leaving its rest position. Due to the modular construction of the actuator 1 with three identical kits, each containing one of the actuator pins 3 and the components involved in its operation, only one of the kits is explained below for linguistic simplification.
  • a spring means 13 which clamped in the form of a helical compression spring 14 between a stationary housing 4 resting on the support disk 15 on the one hand and a front side of a second end portion 16 of the actuator pin 3 adjacent sliding disk 17 on the other are.
  • the object of the sliding disk 17 is to decouple the actuator pin 3 rotationally from the helical compression spring 14 so that a rotation of the first end portion 2 of the actuator pin 3 located in the engaged state with the sliding groove does not lead to a twisting of the helical compression spring 14.
  • the adjusting device 1 has a controllable holding device 18, which holds the actuator pin 3 in the rest position and, if necessary, releases from the rest position (the three holding devices 18 are, of course, independently controllable).
  • the holding device 18 is of positive-locking design and comprises the following features or components: a longitudinal bore 19 extending in the second end section 16 of the actuator pin 3;
  • a further axial collar 32 which is firmly connected to the latter and serves as a simple diameter widening in the transition region to the armature 25, is used in this exemplary embodiment the spring ends 33 of the helical compression springs 14 and 30 facing away from the support plate 15 abuts.
  • the actuator pin 3 safely reaches the locked rest position, taking into account component tolerances, and at the same time to prevent a sliding, wear ß regimennden contact between the end face 35 of the first end portion 2 and the cam piece outside the sliding groove, it is further provided, the sliding groove in her Outlet area to be provided with at least one acting in the radial direction acceleration ramp. Upon rotation of the cam piece, this acceleration ramp causes the actuator pin 3 to lift due to its inertia against the bottom of the sliding groove and to safely return to the locked rest position after a free-flying phase of the order of 1 mm or less.
  • annular end face 12 of the bushing 8 is formed with an inner bevel 36 substantially mirror-symmetrical to the axial shoulder 1 1 of the annular groove 10 to the occurring at a dynamically induced abutment of the balls 21 on the annular end face 12 contact pressures on a low To keep level.
  • FIG. 1 An uncut general view of the adjusting device 1 is finally shown in FIG.
  • the representation required for the control of the Elektrohubmagneten 24 power cables or connectors has been omitted.
  • the flange-like housing 4 with screwing points 37 for fastening the adjusting device 1 on the cylinder head and a closure cover 38 bolted to the housing 4 are clearly recognizable.

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  • 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 (1) avec au moins un ergot d'actionneur (3) pouvant être sorti d'une position de repos dans une position de travail, notamment pour régler un élément de came, disposé en solidarité de rotation et à translation longitudinale sur un arbre porteur, d'un mécanisme de distribution à course variable d'un moteur à combustion interne. Le dispositif de réglage présente un dispositif de maintien asservissable (18) pour maintenir l'ergot d'actionneur dans la position de repos et pour libérer l'ergot d'actionneur de la position de repos. Le dispositif de maintien doit ici être conçu à action par engagement positif, par le fait qu'un ergot de blocage (26) coopère avec des corps de blocage (22) de telle sorte que l'ergot de blocage, afin de maintenir l'ergot d'actionneur dans la position de repos, appuie les corps de blocage en direction radialement extérieure contre un évidement radial (9), et que l'ergot de blocage, afin de libérer l'ergot d'actionneur de la position de repos, relâche les corps de blocage en direction radialement intérieure.
PCT/EP2007/061089 2006-11-03 2007-10-17 Dispositif de réglage WO2008052884A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006051809A DE102006051809A1 (de) 2006-11-03 2006-11-03 Stellvorrichtung
DE102006051809.8 2006-11-03

Publications (1)

Publication Number Publication Date
WO2008052884A1 true WO2008052884A1 (fr) 2008-05-08

Family

ID=38983217

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/061089 WO2008052884A1 (fr) 2006-11-03 2007-10-17 Dispositif de réglage

Country Status (2)

Country Link
DE (1) DE102006051809A1 (fr)
WO (1) WO2008052884A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102333936A (zh) * 2009-02-27 2012-01-25 谢夫勒科技有限两合公司 电磁调整装置
JP2013513054A (ja) * 2009-12-02 2013-04-18 シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト 電磁式作動装置

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008029325A1 (de) * 2008-06-20 2009-12-24 Daimler Ag Ventiltriebvorrichtung
DE102008029349A1 (de) * 2008-06-20 2009-12-24 Daimler Ag Ventiltriebvorrichtung
DE102008060166A1 (de) * 2008-11-27 2010-06-02 Dr.Ing.H.C.F.Porsche Aktiengesellschaft Ventiltrieb für Gaswechselventile einer Brennkraftmaschine
DE102008060169B4 (de) * 2008-11-27 2023-02-09 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Ventiltrieb für Gaswechselventile einer Brennkraftmaschine
DE102009008422A1 (de) * 2009-02-11 2010-08-12 Daimler Ag Ventiltriebumschaltvorrichtung
DE102009030375A1 (de) 2009-06-25 2010-12-30 Schaeffler Technologies Gmbh & Co. Kg Elektromagnetische Stellvorrichtung
DE102011003760B4 (de) * 2010-11-29 2022-03-24 Schaeffler Technologies AG & Co. KG Elektromagnetische Stellvorrichtung
DE102011050730A1 (de) 2011-05-30 2012-12-06 Eto Magnetic Gmbh Nockenwellenverstellvorrichtung
DE102011086233B4 (de) 2011-11-14 2015-11-26 Schaeffler Technologies AG & Co. KG Aktorvorrichtung zur Verstellung eines Schiebenockensystems mit Schaltscheibe
DE102012101619A1 (de) 2012-02-28 2013-08-29 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Elektromagnetische Stellvorrichtung
JP5505744B2 (ja) * 2012-03-23 2014-05-28 株式会社デンソー アクチュエータ
DE102012213660A1 (de) * 2012-08-02 2014-02-06 Schaeffler Technologies AG & Co. KG Magnetaktor eines Schiebenockensystems
DE102015115684A1 (de) 2015-09-17 2017-03-23 Eto Magnetic Gmbh Elektromagnetische Aktuatorvorrichtung sowie System
DE102016116776A1 (de) * 2016-09-07 2018-03-08 Kendrion (Villingen) Gmbh Elektromagnetische Stellvorrichtung insbesondere zum Verstellen von Nockenwellen eines Verbrennungsmotors
DE102017121723B4 (de) * 2017-09-19 2021-07-01 Kendrion (Villingen) Gmbh Elektromagnetische Stellvorrichtung insbesondere zum Verstellen von Nockenwellen eines Verbrennungsmotors
DE102017121947A1 (de) 2017-09-21 2019-03-21 Kendrion (Villingen) Gmbh Stellvorrichtung mit einem abgedichteten Führungszylinder

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB603865A (en) * 1945-11-01 1948-06-24 Electrol Inc Improvements relating to hydraulic or pneumatic jacks
US3180234A (en) * 1963-07-25 1965-04-27 Jarry Hydraulics Ltd Dual-position lockable actuator
GB2128680A (en) * 1982-10-08 1984-05-02 Johnston Brothers Hydraulic cylinder and piston
US4635536A (en) * 1983-09-19 1987-01-13 Miller Fluid Power Corporation Cylinder locking apparatus
WO2003021612A1 (fr) * 2001-09-01 2003-03-13 Ina-Schaeffler Kg Dispositif de reglage electromagnetique
WO2003042550A1 (fr) * 2001-10-10 2003-05-22 Hydrotech Construction Company Ab Cylindre de blocage automatique et dispositif renseignant sur l'etat dudit cylindre

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB603865A (en) * 1945-11-01 1948-06-24 Electrol Inc Improvements relating to hydraulic or pneumatic jacks
US3180234A (en) * 1963-07-25 1965-04-27 Jarry Hydraulics Ltd Dual-position lockable actuator
GB2128680A (en) * 1982-10-08 1984-05-02 Johnston Brothers Hydraulic cylinder and piston
US4635536A (en) * 1983-09-19 1987-01-13 Miller Fluid Power Corporation Cylinder locking apparatus
WO2003021612A1 (fr) * 2001-09-01 2003-03-13 Ina-Schaeffler Kg Dispositif de reglage electromagnetique
WO2003042550A1 (fr) * 2001-10-10 2003-05-22 Hydrotech Construction Company Ab Cylindre de blocage automatique et dispositif renseignant sur l'etat dudit cylindre

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102333936A (zh) * 2009-02-27 2012-01-25 谢夫勒科技有限两合公司 电磁调整装置
JP2013513054A (ja) * 2009-12-02 2013-04-18 シェフラー テクノロジーズ アクチエンゲゼルシャフト ウント コンパニー コマンディートゲゼルシャフト 電磁式作動装置

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