EP2507485B1 - Dispositif de réglage électromagnétique - Google Patents

Dispositif de réglage électromagnétique Download PDF

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Publication number
EP2507485B1
EP2507485B1 EP10781510.2A EP10781510A EP2507485B1 EP 2507485 B1 EP2507485 B1 EP 2507485B1 EP 10781510 A EP10781510 A EP 10781510A EP 2507485 B1 EP2507485 B1 EP 2507485B1
Authority
EP
European Patent Office
Prior art keywords
actuator
pins
pin
actuating device
blocking
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.)
Not-in-force
Application number
EP10781510.2A
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German (de)
English (en)
Other versions
EP2507485A1 (fr
Inventor
Harald Elendt
Andreas Nendel
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.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG 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
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Publication of EP2507485A1 publication Critical patent/EP2507485A1/fr
Application granted granted Critical
Publication of EP2507485B1 publication Critical patent/EP2507485B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/121—Guiding or setting position of armatures, e.g. retaining armatures in their end position
    • H01F7/124—Guiding or setting position of armatures, e.g. retaining armatures in their end position by mechanical latch, e.g. detent
    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01F—MAGNETS; INDUCTANCES; TRANSFORMERS; SELECTION OF MATERIALS FOR THEIR MAGNETIC PROPERTIES
    • H01F7/00—Magnets
    • H01F7/06—Electromagnets; Actuators including electromagnets
    • H01F7/08—Electromagnets; Actuators including electromagnets with armatures
    • H01F7/16—Rectilinearly-movable armatures
    • H01F7/1638—Armatures not entering the winding
    • H01F7/1646—Armatures or stationary parts of magnetic circuit having permanent magnet

Definitions

  • the invention relates to an electromagnetic actuator, comprising a housing, two actuator pins, which are mounted independently movable between a retracted in the housing rest position and a retracted from the housing working position in the housing, and an electrically energizable solenoid device for actuating the actuator pins and two with the Aktuatorstatten in the operating sense cooperating permanent magnets, the two-pole magnetized and polarized in the opposite direction polarity aligned with each other and a stationary core region of the magnetic coil means are assigned together.
  • the magnetic coil device is designed to generate depending on their energization in the direction of action reversing magnetic field at the core region, which attracts the first permanent magnet and repels the second permanent magnet and vice versa.
  • Such a control device is particularly suitable for adjusting hubvariabler valve drives of internal combustion engines, whose basic operation, for example, from DE 10 2004 021 376 A1 evident.
  • the stroke variability of this valve train is based on a cam piece with two cams arranged directly adjacent thereto, the different opening characteristics of which are selectively transferred to a gas exchange valve by means of a conventionally rigid cam follower.
  • the cam piece is non-rotatable, however arranged longitudinally displaceable on a support shaft and has two spiral and oppositely extending sliding grooves, in which the end portions of the actuator pins of two actuating devices (with only one Aktuatorux) are alternately coupled.
  • WO 03/021612 A1 is proposed an actuating device whose operation is based on the interaction of a magnetic coil with a permanent magnet attached to the actuator pin. Due to its magnetic attraction of the spring-loaded in the extension direction actuator pin adheres to the non-energized magnetic coil. For solving the actuator pin from this rest position, only a pulse-shaped current loading of the magnetic coil to overcome the magnetic attraction of the permanent magnet is required, the Aktuatorrob 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 magnetic coil in the direction the working position is accelerated.
  • An adjusting device of the type mentioned is from the unpublished DE 10 2009 010 949 A1 out.
  • the actuating device proposed there has a magnetic coil which is reversible for the purpose of reversing the magnetic field effect, ie is energized with opposite current flow directions. Depending on the magnetic field direction, one of the two actuator pins is actuated in the extension direction, while the other actuator pin remains in its retracted rest position.
  • the required for the electrical control of the actuator power supply device - in the preferred application of said variable stroke valve engine of an internal combustion engine is expediently to the engine control unit - must be provided with a corresponding current reversing circuit, for example in the form of a so-called H-bridge.
  • such a circuit is usually not provided in engine control units and requires a complex adaptation of the control unit.
  • the present invention has the object, a control device of the type mentioned in such a way that the aforementioned disadvantages are eliminated by simple means.
  • the actuator should be compatible with conventional control devices without reversing the direction of current or require a slight modification of the control device if necessary in order to be operational in terms of the reversible magnetic field effect.
  • the magnet coil device has two magnet coils which can be energized independently of each other, such that when the first magnet coil is energized, the magnetic field is generated with the first effective direction and when the second magnet coil is energized, the magnetic field is reversed with the second effective direction.
  • the solenoids are preferably sequential in the travel direction, i. arranged in axial series connection around the core area.
  • the actuator pins each a Aktuatorux in the extension direction kraftbeauf sodes spring means, a detent and a cooperating with the actuator pin by means of detent locking pin to be assigned, which holds the associated actuator pin with locked detent in the rest position and in the direction of travel relative to this is relocatable.
  • the actuator pins facing away from the head portions of the locking pins are each provided with one of the permanent magnets. The magnetic field generated when energizing one of the magnetic coils displaces one of the locking pins in the retraction direction to release the associated detent, and force the other of the locking pins in the extension direction to lock the associated detent.
  • the lock pin connected to the first permanent magnet shifts toward the core portion, that is, the core pin. in the retraction of the associated actuator pin, which shifts in now released detent by the force of the spring means in its working position.
  • the locking pin connected to the second permanent magnet and the associated actuator pin remain locked when the detent is locked.
  • the permanent magnets should be spaced apart when the head portions of the locking pins on the core area. This is done constructively expediently in that the head portions of the locking pins are raised relative to the permanent magnets.
  • the force effect of the permanent magnets which increases exponentially in the vicinity of the core region, can be limited to such a degree that a sufficient force effect resetting the blocking pins remains with currentless solenoid coils. This force effect should expediently proceed from further spring means, which force the locking pins in the extension direction.
  • the one or more locking bodies are preferably formed as balls, as they are removable as an extremely cost-effective mass product of a rolling element.
  • three balls and three evenly distributed over the circumference of the actuator pin transverse bores may be provided.
  • This arrangement is advantageous over only one ball insofar as either larger holding forces can be generated with identical dimensioning of the balls or with smaller dimensions of the balls - according to a further reduced space requirements of the detent - the possibly already sufficient holding force only one ball can be generated.
  • the arrangement of circumferentially distributed by 120 ° balls leads to a mechanically favorable, centered support of the locking pin in the longitudinal bore of the actuator pin. Nevertheless, of course, arrangements with only one, two, four or more balls are possible.
  • the balls may be self-locking clamped between the support surfaces, wherein the support surfaces have a constant or a decreasing in the retraction distance from each other.
  • the second support surface may be parallel to the direction of travel of the actuator pin and be part of a production-wise continuous cylindrical guide for the Aktuatorux.
  • both the forces of the spring means and the friction conditions on the ball-support surface contacts are taken into account, so that the required for proper functioning of the detent region of self-locking is not left at these contacts.
  • the first support surface on the locking pin in the extension direction radially tapers and that the support surfaces are parallel to each other.
  • the support surfaces are formed Vietnameseflgelstumpfförmig. This embodiment allows a particularly low-wear sliding or rolling contact between the balls and the support surfaces when the actuator pin leaves the rest position and reached again.
  • FIG. 1 discloses an embodiment of an adjusting device 1 according to the invention, which serves to control a basically known variable stroke valve train of an internal combustion engine.
  • the basic operating principle of such a valve train is in FIG. 2 and can be summarized to the effect that instead of a conventional rigidly trained Camshaft, a support shaft 2 with a rotatably and longitudinally displaceably arranged cam piece 3 is provided.
  • the cam piece 3 has two groups of axially adjacent cams 4 and 5 with different opening curves, which serve for operating point-dependent actuation of gas exchange valves 6.
  • the adjusting device 1 is an assembly which can be mounted in the cylinder head of the internal combustion engine with a housing 10 and two hollow cylindrical actuator pins 8 and 9.
  • the actuator pins 8, 9 designed as identical parts are mounted in longitudinal guides 11 of the housing 10 and can be mounted move independently between a retracted in the housing 10 rest position (as shown) and a retracted from the housing 10 working position back and forth. As explained above, in the working position (not shown), the actuator pins 8, 9 are engaged with an associated cam groove of a cam piece to displace the cam piece.
  • the mutually identical detents are formed in each case by a longitudinal bore 15 running in the actuator pin 8, and by cross-bores 16, a first support surface 17 formed on the locking pin 13, 14, and a second support surface 18 formed in the housing 10, and three detent bodies in the form of balls 19 ,
  • the in the evenly on the circumference of the Aktuatorcks 8, 9 distributed transverse bores 16 movably arranged balls 19 are clamped in the rest position of the actuator pin 8, 9 between the support surfaces 17 and 18.
  • the extending in the longitudinal bore 15 end portion 20 of the locking pin 13, 14 tapers conically in the extension direction of the Aktuatorlixs 8, 9, so that the first support surface 17 forms the outer circumferential surface of a circular truncated cone.
  • the second support surface 18 in the housing 10 extends at a constant distance thereto and thus forms the inner circumferential surface of a circular truncated cone.
  • the locking pins 13, 14 are each acted upon by a further spring means - here a helical compression spring 21 - also in the extension direction.
  • the angle of inclination of the support surfaces 17, 18 with respect to the direction of travel of the actuator pin 8, 9 is chosen taking into account the force acting on the locking pin 13, 14 and the actuator pin 8, 9 spring forces and the friction conditions on the ball-support surface contacts that the balls 19th self-locking between the support surfaces 17, 18 are clamped and so fix the actuator pin 8, 9 securely in the rest position.
  • the inclination angle is presently about 5 °.
  • the concentric helical compression springs 12, 21 are based, on the one hand, on bushes 22 pressed in in the housing 10 and, on the other hand, on annular end faces 23 and 24 of the actuator pins 8, 9 and the locking pins 13, 14, respectively. These are electromagnetically kraftbeaufschlagt for releasing the detents in the retraction of the actuator pins 8, 9 shifted and are provided for this purpose at their the actuator pins 8, 9 facing away from the head portions 25 with attached permanent magnets 26 and 27. These are axially magnetized bipolar, in the direction of movement of the actuator pins 8, 9 with respect to their designated N and S north and south poles aligned opposite to each other and exposed to the magnetic field of a solenoid device.
  • the magnetic coil device comprises, as essential components, a stationary core region 28 and two magnet coils which can be energized independently of one another 29 and 30, which are arranged in the direction of travel of the actuator pins 8, 9 successively, ie in axial series connection to the core region 28 and generate a reversible magnetic field, the effective direction of the instantaneous energization state of the magnetic coils 29, 30 depends.
  • the selective power supply of the magnetic coils 29, 30 via a connector 31.
  • the coaxial with the magnetic coils 29, 30 extending core portion 28 has on the part of the permanent magnets 26, 27 has a shoulder which forms a flat contact surface 31 for the locking pins 13, 14.
  • a strongly adhering contact of the permanent magnets 26, 27 on the abutment surface 31 is avoided in that the head portions 25 of the locking pins 13, 14 are raised relative to the permanent magnets 26, 27 and they always have a corresponding minimum distance to the abutment surface 31.
  • the operation of the actuator 1 is as follows: the energization of the first solenoid 29 (the second solenoid 30 is energized) generates a magnetic field first direction of action with south pole on the contact surface 31 of the core portion 28, so that the first permanent magnet 26 with its NS pole alignment tightened and the second permanent magnet 27 is repelled with its SN pole alignment. While the ejected second permanent magnet 27, the associated locking pin 14 and consequently also the associated actuator pin 9 remain at rest with locked detent, attracted with the first permanent magnet 26 locking pin 13 is displaced to the contact surface 31 in the retraction direction. In this case, the associated detent releases by the clamping action of the balls 19 relative to the support surfaces 17, 18 is repealed.
  • the actuator pin 8 is driven by the force of the helical compression spring 12 in its working position.
  • the first solenoid 29 is then de-energized, so that the attracted locking pin 13 by the force of the helical compression spring 21 returns to its original position.
  • the actuator pin 8 located in engagement with the cam piece is moved through the radially rising outlet region of the sliding groove pushed back into its rest position and locked there again. This is done by the balls 19 follow the inclined course of the first support surface 17 on the locking pin 13, move radially outward in the transverse bores 16 and are clamped under self-locking between the support surfaces 17, 18.
  • the actuation of the other actuator pin 9 is initiated by the fact that now the second solenoid 30 is energized, while the first solenoid coil 29 remains energized.
  • the reverse direction of action of the magnetic field with a north pole at the abutment surface 31 of the core region 28 abuts the first permanent magnet 26 with its NS pole orientation and attracts the second permanent magnet 27 with its SN pole orientation.
  • the further control curve of the other actuator pin 9 takes place in an identical manner as explained above for the actuator pin 8.

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  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Electromagnets (AREA)

Claims (10)

  1. Dispositif de réglage électromagnétique (1), comprenant un boîtier (10), deux goupilles d'actionneur (8, 9) qui sont montées dans le boîtier (10) de manière déplaçable indépendamment l'une de l'autre entre une position de repos rentrée dans le boîtier (10) et une position de travail sortie hors du boîtier (10), et un dispositif de bobine magnétique pouvant être parcouru par un courant électrique pour l'actionnement des goupilles d'actionneur (8, 9) ainsi que deux aimants permanents (26, 27) coopérant dans le sens de l'actionnement avec les goupilles d'actionneur (8, 9), lesquels aimants permanents sont aimantés selon deux pôles et sont orientés l'un par rapport à l'autre avec leurs pôles opposés dans la direction de déplacement, et sont associés en commun à une région de noyau stationnaire (28) du dispositif de bobine magnétique, le dispositif de bobine magnétique étant réalisé de manière à produire au niveau de la région de noyau (28) un champ magnétique inversant son sens d'action en fonction de son alimentation en courant, lequel champ magnétique attire le premier aimant permanent (26) et repousse le deuxième aimant permanent (27) et inversement, caractérisé en ce que le dispositif de bobine magnétique présente deux bobines magnétiques (29, 30) pouvant être alimentées en courant indépendamment l'une de l'autre, de telle sorte que lors de l'alimentation en courant de la première bobine magnétique (29), le champ magnétique soit produit avec un premier sens d'action et que lors de l'alimentation en courant de la deuxième bobine magnétique (30), le champ magnétique soit produit avec un deuxième sens d'action inverse.
  2. Dispositif de réglage (1) selon la revendication 1, caractérisé en ce que les bobines magnétiques (29, 30) sont disposées l'une derrière l'autre dans le sens de déplacement.
  3. Dispositif de réglage (1) selon la revendication 1, caractérisé en ce qu'aux goupilles d'actionneur (8, 9) sont à chaque fois associés un moyen de ressort (12) sollicitant par force dans la direction de sortie la goupille d'actionneur (8, 9), un crantage et une goupille d'arrêt (13, 14) coopérant au moyen du crantage avec la goupille d'actionneur (8, 9), laquelle goupille d'arrêt retient la goupille d'actionneur associée (8, 9) dans la position de repos lorsque le crantage est bloqué et peut être déplacée dans le sens de déplacement par rapport à ladite goupille d'actionneur, les portions de tête (25) des goupilles d'arrêt (13, 14) opposées aux goupilles d'actionneur (8, 9) étant à chaque fois pourvues de l'un des aimants permanents (26, 27) et le champ magnétique produit lors de l'alimentation en courant de l'une des bobines magnétiques (29, 30) déplaçant l'une des goupilles d'arrêt (13, 14) dans le sens de rétraction, afin de libérer le crantage associé et sollicitant par une force l'autre des goupilles d'arrêt (13, 14) dans le sens de la sortie, afin de bloquer le crantage associé.
  4. Dispositif de réglage (1) selon la revendication 3, caractérisé en ce que les aimants permanents (26, 27), lors de l'application des portions de tête (25) des goupilles d'arrêt (13, 14), s'étendent au niveau de la région de noyau (28) à distance de cette dernière.
  5. Dispositif de réglage (1) selon la revendication 4, caractérisé en ce que les portions de tête (25) des goupilles d'arrêt (13, 14) s'étendent de manière rehaussée par rapport aux aimants permanents (26, 27).
  6. Dispositif de réglage (1) selon la revendication 3, caractérisé en ce que les crantages sont à chaque fois formés par les caractéristiques suivantes .
    - un alésage longitudinal (15) s'étendant dans la goupille d'actionneur (8, 9) pour recevoir la goupille d'arrêt (13, 14) et un ou plusieurs alésages transversaux (16) coupant les alésages longitudinaux (15),
    - une première surface d'appui (17) réalisée sur la goupille d'arrêt (13, 14) et une deuxième surface d'appui (18) réalisée dans le boîtier (10), au moins l'une des surfaces d'appui (17, 18) s'étendant de manière inclinée par rapport au sens de déplacement,
    - et des corps d'encliquetage (19), qui sont disposés de manière mobile dans les alésages transversaux (16) et qui sont serrés dans la position de repos entre les surfaces d'appui (17, 18).
  7. Dispositif de réglage (1) selon la revendication 6, caractérisé en ce que trois corps d'encliquetage (19) réalisés sous forme de billes et trois alésages transversaux (16) répartis uniformément sur la périphérie de la goupille d'actionneur (8, 9) sont prévus.
  8. Dispositif de réglage (1) selon la revendication 7, caractérisé en ce que les billes (19) sont serrées de manière autobloquante entre les surfaces d'appui (17, 18), les surfaces d'appui (17, 18) présentant une distance mutuelle constante ou diminuant dans le sens de rétraction.
  9. Dispositif de réglage (1) selon la revendication 8, caractérisé en ce que la première surface d'appui (17) se rétrécit radialement dans le sens de la sortie et en ce que les surfaces d'appui (17, 18) s'étendent parallèlement l'une à l'autre.
  10. Dispositif de réglage (1) selon la revendication 9, caractérisé en ce que les surfaces d'appui (17, 18) sont réalisées sous forme tronconique circulaire.
EP10781510.2A 2009-12-02 2010-11-24 Dispositif de réglage électromagnétique Not-in-force EP2507485B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009056609A DE102009056609A1 (de) 2009-12-02 2009-12-02 Elektromagnetische Stellvorrichtung
PCT/EP2010/068071 WO2011067142A1 (fr) 2009-12-02 2010-11-24 Dispositif de réglage électromagnétique

Publications (2)

Publication Number Publication Date
EP2507485A1 EP2507485A1 (fr) 2012-10-10
EP2507485B1 true EP2507485B1 (fr) 2013-11-06

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP10781510.2A Not-in-force EP2507485B1 (fr) 2009-12-02 2010-11-24 Dispositif de réglage électromagnétique

Country Status (6)

Country Link
US (1) US20120235777A1 (fr)
EP (1) EP2507485B1 (fr)
JP (1) JP5746204B2 (fr)
CN (1) CN102639824B (fr)
DE (1) DE102009056609A1 (fr)
WO (1) WO2011067142A1 (fr)

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DE102007037232A1 (de) * 2007-08-07 2009-02-12 Eto Magnetic Gmbh Vorrichtung zur Nockenwellenverstellung einer Brennkraftmaschine
DE102007037333A1 (de) 2007-08-08 2009-02-26 Daimler Ag Betätigungsvorrichtung
DE102007052254B4 (de) * 2007-11-02 2021-02-04 Daimler Ag Ventiltriebvorrichtung
DE102007052253B4 (de) * 2007-11-02 2023-07-06 Mercedes-Benz Group AG Ventiltriebvorrichtung
US20090140188A1 (en) * 2007-12-03 2009-06-04 Stonel Corporation Energy efficient solenoid for mechanically actuating a movable member
DE102008020892A1 (de) * 2008-04-25 2009-10-29 Schaeffler Kg Stellvorrichtung
DE102008020893A1 (de) * 2008-04-25 2009-10-29 Schaeffler Kg Elektromagnetische Stellvorrichtung
DE102008024086A1 (de) * 2008-05-17 2009-11-19 Daimler Ag Ventiltriebvorrichtung
DE102008060166A1 (de) * 2008-11-27 2010-06-02 Dr.Ing.H.C.F.Porsche Aktiengesellschaft Ventiltrieb für Gaswechselventile einer Brennkraftmaschine
DE202008015980U1 (de) * 2008-12-03 2010-04-29 Eto Magnetic Gmbh Elektromagnetische Aktuatorvorrichtung
DE202009015466U1 (de) * 2009-02-27 2010-03-18 Schaeffler Kg Elektromagnetische Stellvorrichtung
DE102009053121A1 (de) * 2009-11-13 2011-05-19 Schaeffler Technologies Gmbh & Co. Kg Elektromagnetische Stellvorrichtung

Also Published As

Publication number Publication date
CN102639824B (zh) 2014-12-17
EP2507485A1 (fr) 2012-10-10
CN102639824A (zh) 2012-08-15
WO2011067142A1 (fr) 2011-06-09
JP5746204B2 (ja) 2015-07-08
US20120235777A1 (en) 2012-09-20
JP2013513054A (ja) 2013-04-18
DE102009056609A1 (de) 2011-06-09

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