EP2724354B1 - Dispositif de positionnement électromagnétique et dispositif de réglage d'arbre à cames - Google Patents

Dispositif de positionnement électromagnétique et dispositif de réglage d'arbre à cames Download PDF

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Publication number
EP2724354B1
EP2724354B1 EP20120733618 EP12733618A EP2724354B1 EP 2724354 B1 EP2724354 B1 EP 2724354B1 EP 20120733618 EP20120733618 EP 20120733618 EP 12733618 A EP12733618 A EP 12733618A EP 2724354 B1 EP2724354 B1 EP 2724354B1
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EP
European Patent Office
Prior art keywords
core body
contact element
actuating device
contact
core
Prior art date
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Active
Application number
EP20120733618
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German (de)
English (en)
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EP2724354A1 (fr
Inventor
Thomas Golz
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
ETO Magnetic GmbH
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ETO Magnetic GmbH
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Publication date
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Publication of EP2724354A1 publication Critical patent/EP2724354A1/fr
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Classifications

    • H—ELECTRICITY
    • H01—ELECTRIC ELEMENTS
    • H01H—ELECTRIC SWITCHES; RELAYS; SELECTORS; EMERGENCY PROTECTIVE DEVICES
    • H01H50/00—Details of electromagnetic relays
    • H01H50/54—Contact arrangements
    • 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
    • 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
    • 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
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/08—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by electric or magnetic means
    • 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
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric means
    • F01L9/21—Valve-gear or valve arrangements actuated non-mechanically by electric means actuated by solenoids
    • F01L2009/2128—Core and coil construction
    • 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

Definitions

  • the invention relates to an electromagnetic actuator according to the preamble of patent claim 1 and a camshaft adjusting device with such an electromagnetic actuator as actuator according to claim 12.
  • Electromagnetic actuating devices which comprise an actuating element, which forms an engagement region at the end and which passes through a recess in permanent magnet means arranged on the shell side.
  • an electromagnetic actuator which comprises an actuator without permanent magnet means, wherein the actuator is equipped with a contact element.
  • the invention is therefore based on the object to provide an improved, adhesion force-optimized electromagnetic actuator, which is characterized by an increased wear resistance and preferably makes do with a comparatively small, ie space-optimized, stationary coil device. Furthermore, the object is to provide a camshaft adjusting device with a correspondingly improved electromagnetic actuator. This object is achieved in terms of the electromagnetic actuator with the features of claim 1 and with respect to the camshaft adjusting device with the features of claim 12. Advantageous developments of the invention are specified in the subclaims.
  • the invention has recognized that the wear resistance can be increased by a suitable choice of material of the core region, initially still has the problem that harder core region material is usually poorly magnetic flux-conducting, resulting in an education of the core body of a cured material to extremely poor efficiencies would lead to the inoperability of the electromagnetic actuator.
  • the inventive design or improvement of an electromagnetic actuator in which the core region is not in one piece as in the prior art, but a plurality of parts and one, preferably good magnetic good conducting, core body and fixed in this core body preferably the core body In the direction of anchor superior contact element, which is characterized with an increased compared to the core body hardness, preferably measured in HRC.
  • the invention initially accepts a disadvantageous multi-part design of the core region at first viewing and can thereby surprisingly achieve a multiplicity of advantages.
  • the contact surface or the lubricant-bearing contact surface between the core region and the actuator can be influenced in a comparatively simple manner by a corresponding adaptation of the contact element geometry, without it being necessary to additionally geometrically adapt the core body.
  • the wear resistance of the core area increases, since the actuator is supported in a switching position on the harder than the core body contact element.
  • the field line course of the magnetic field lines in the contact body partially surrounding the core body is selectively influenced, in particular bundled in a contact element adjacent, preferably annular area, whereby the efficiency of the electromagnetic actuator is increased, which in turn can be used a smaller dimensioned (space-optimized) coil means.
  • the air gap which is preferably formed between the permanent magnet means or an armature pole disk and the core body, preferably as part of a disk package, can be set to a force maximum (vertex) via the core body by means of the preferably pressed-in contact element with defined projection.
  • the air gap can be adjusted or optimized with regard to a maximum repulsive force, whereby minimum switching times can be achieved.
  • the actuator in the aforementioned switching position in addition to the fixed in the core body contact element is supported on the core body, ie that the core area side contact surface is formed only partially or partially by the contact element.
  • the core-area-side contact surface is formed exclusively by the contact element in order to achieve the smallest possible contact surface and thus the lowest possible adhesion forces and on the other hand, is preferred Wear resistance of the electromagnetic actuator, in particular the core region, to optimize overall. It is particularly preferred if the contact surface formed by the contact element is arranged concentrically with respect to a longitudinal center axis of the actuator.
  • the contact element projects beyond the pole face of the core body facing the permanent magnet means.
  • the contact element In principle, it is possible to form the contact element from a material which opposes the magnetic flux with the same or even a lower resistance as the material of the core body. However, it is preferred, as explained above, when the magnetic conductivity of the contact element is worse than that of the surrounding core body to focus the field lines targeted. By means of the preferably pressed-in contact element, therefore, a bundling of the magnetic field lines is achieved which causes the field lines to be "directed" in a more targeted manner to the field lines directed counter to by the permanent magnet means. Thus, an optimization of the repulsive force and thus a minimum switching time can be achieved.
  • the hardness of the material of the contact element is at least twice as high, preferably at least three times as high, even more preferably at least four times as high as the hardness of the core body material.
  • This can be achieved, for example, by forming the core body from the steel alloy 11SMn30 and the preferably pin-shaped contact element from the alloy 16MnCr5.
  • the core body has a hardness of about 10 HRC and the contact element of about 60 HRC.
  • the invention provides that the core region-side contact surface is smaller than a surface extending radially to the longitudinal extent of the actuator (cross-sectional area) of the actuator, in particular as the core area facing end face (end face) of the actuator and / or enclosed by the permanent magnet means cross-sectional area of the actuator. It is very particularly preferred if the core region-side contact surface, which is preferably formed exclusively by the contact element, only max. 70%, preferably max. 60%, more preferably max. 50%, even more preferred max. 40% of this area corresponds.
  • the diameter of the preferably cylindrical contact area formed by the contact area of the core area-side contact surface from a value range between 2 mm and 8 mm, preferably between 4 mm and 7 mm, most preferably of about 5.2 mm is selected.
  • a preferably annular ring is formed on the contact element.
  • axial abutment surface is provided with which the fixed in the core body contact element is axially supported on the core body.
  • the air gap can be adjusted for example by setting a (then variable) axial offset of the contact element, in which case it should be ensured that the interference fit between contact element and core body is selected so that even during the Operation an axial migration of the contact element in the Core body into it and an associated air gap reduction during operation is avoided.
  • the contact element can be fixed to the core body via an axial and / or radial deformation of the core body material (caulking).
  • the contact element is received in a frontal bore of the core body and there preferably fixed by means of a press fit.
  • the contact element is introduced in a further development of the invention in a bore of the core body.
  • the hole is not realized as a continuous cylinder bore (which is alternatively possible), but as a stepped bore with at least one annular shoulder, which preferably forms an axial counter-abutment surface for an axial stop surface of the contact element.
  • the press fit is realized in a rear or lower bore section relative to the actuator.
  • an axial pin compression of about 2 mm to 4 mm, preferably realized by 3 mm.
  • the contact surface formed by the contact element is smaller than the maximum bore diameter of the bore, ie in the case of the formation of the bore as a stepped bore is smaller than a front bore diameter or smaller than an outer diameter of an annular axial abutment surface ,
  • the contact surface formed by the contact element corresponds to a cross-sectional area of the contact element in the press-in region. It is particularly preferred if the free end of the contact element is crowned - In other words, a crowning of the contact surface offered by the contact element is advantageous, since the actuating element, as part of the armature assembly, can become less jammed in the retracted state due to the crowning radial preferred position on the edge of the contact element.
  • the contact element supports the core body in the axial direction, i. surmounted in the direction of the actuating element.
  • this axial projection is chosen so that at a given energization of the coil winding results in a maximum force of the repulsive force between the core body and permanent magnet means. If the axial projection is chosen too large, this leads to a loss of power in the acting magnetic forces - the axial projection is too small, this means increased adhesion forces and thus a loss of power in the resulting repulsive force.
  • the axial projection is selected so that the resulting air gap leads to a maximum repulsive force plus / minus 20%, preferably plus / minus 10%, even more preferably plus / minus 5%.
  • the invention also leads to a camshaft adjusting device with an electromagnetic actuating device designed according to the concept of the invention as an actuator for realizing the adjusting movement of the camshaft or its cams.
  • Fig. 1 shows the realization of an electromagnetic actuator for an otherwise not shown camshaft adjusting device.
  • a possible design variant of the combination of core area and anchor is in the FIGS. 2 and 3 shown.
  • the camshaft is actuated directly or indirectly by means of a continuously elongated, bolt-shaped actuator 2, which in addition to be explained later permanent magnet means. 6 Part of the anchor is.
  • the actuator 2 is guided in a sleeve-shaped bearing element 3, which simultaneously performs the function of a magnetic yoke, adjustable in the axial direction.
  • the electromagnetic actuator 1 comprises within a cup-shaped housing 4 a known, in Fig. 1 not shown coil device, which is associated with a magnetic core region 5. With the aid of the coil device, the actuator 2 can be adjusted with the permanent magnet means 6 fixed thereto in the axial direction, wherein on the side remote from the core region 5 end face of the actuator 2, an engagement portion is formed to cooperate with a counterpart, in particular with the camshaft.
  • the engagement region may alternatively be provided on the shell side.
  • the actuator 2 permanent magnet means 6 are assigned, which in the embodiment shown in FIG Fig. 1 have the shape of a cylindrical disc. These sit on the lateral surface 7, ie shell side, a front, cylindrical portion of the actuator 2. The latter passes through a cylindrically contoured, central recess 8 of the permanent magnet means 6. These are, for example, by welding, material fit and / or positively fixed to the actuator 2.
  • the permanent magnet means 6 serve to hold the actuator 2 in the illustrated (left in the plane of the drawing) switching position when not energized coil, in which the actuator 2 with an end face 9, more precisely with a formed on this actuator-side contact surface 10 at a parallel thereto , core-side contact surface 11 is supported. By energizing the coil means the permanent magnet means 6 are repelled and the actuator 2 adjusted together with these in the drawing plane right into a second switching position.
  • the electromagnetic actuator 1 is held in an engine block 12 only partially shown.
  • an inlet and / or outlet channel 13 for liquid lubricant in this case engine oil, is formed in the bearing element 3.
  • Radially offset to the inlet and outlet channel 13 is located within the engine block 12, a further channel 14 for the lubricant.
  • the core region 5 is formed of several parts and comprises a core body 15 of magnetically good conductive material, in the concrete embodiment of a steel alloy 11 SMn 30 with a hardness of 10 HRC.
  • the core body 15 a, the core area-side contact surface 11 forming contact element 16 is determined by compression, wherein the contact element 16 of a material, here the steel alloy 16 MnCr 5, is formed, which has a significantly greater hardness of 60 HRC here than the core body 15th
  • armature 17 with elongated actuator 2 and core region 5 according to a preferred embodiment is shown.
  • the core region 5 which comprises the core body 15 with therein fixed contact element 16 which forms the core-area side contact surface 11, which cooperates with a correspondingly large actuator-side contact surface 10 in the illustrated switching position, that is applied to this.
  • Fig. 2 results in the structure of the armature 17.
  • permanent magnet means 6 are set in the form of two permanent magnet discs.
  • the permanent magnet means 6 is associated with a pole disc 18, which is also penetrated by the actuator 2.
  • the pole plate 18 is parallel oriented to a corresponding opposite pole face 19 of the core body 15.
  • Between Polin 18 and pole face 19 is a partially or completely filled with oil working air gap 20 is formed.
  • the width of this working air gap 20 is essentially defined by the extent to which the contact element 16 projects beyond the pole face 19 of the core body 15 in the direction of the actuator 2.
  • the working air gap 20 is determined by the axial distance between the pole face 19 facing Ringpolisation the pole plate 18 and the end face 9 of the actuator second
  • FIG. 2 shows, in front of the core body 15 formed as a stepped bore bore 21 is introduced, which is divided into a rear, cylindrical, reduced diameter portion 22 (press-fit) and a front, enlarged diameter portion 23, the bottom of a counter-abutment surface 24 for an annular axial stop surface 25th of the contact element 16 forms.
  • the actual interference fit between the contact element 16 and the bore 21 is realized (exclusively) in the reduced-diameter portion 22, whereas the diameter-expanded portion 23 has substantially only the formation of the counter-abutment surface 24 to function (ie a radial play is possible there).
  • the contact element 16 For positive reception of the contact element 16 in the bore 21 as a stepped bore, the contact element 16 according to the illustrated preferred embodiment, a lower diameter reduced cylinder portion 26 and an axially adjacent, diameter-expanded cylinder portion 27, which projects beyond the diameter-reduced cylinder portion 26 by means of a circumferential collar on which on the side facing away from the actuator 2 side, the axial stop surface 25 is formed.
  • a cylindrical contact surface portion 28 adjoining the diameter-extended cylinder portion 27 is a cylindrical contact surface portion 28 which in the embodiment shown has a diameter which corresponds to the diameter of the reduced diameter portion 26, however, may also differ if necessary. It is also an embodiment variant conceivable in which the contact surface portion 28 is formed by an axially elongated, diameter-expanded cylinder portion 27.
  • the contact element pin-shaped for example in the form of a circular cylinder form, then preferably the bore 21 is not designed as a stepped bore, but as a continuous cylindrical bore.
  • the core area-side contact surface 11 is substantially smaller than the end face 9 of the actuator.
  • the surface extension of the end face 9 corresponds, at least approximately, to the surface extension of the cross-sectional area of the actuator 2, which is surrounded by the permanent magnet means 6.
  • Fig. 3 is an alternative representation of a section of an example in Fig. 1 shown electromagnetic actuator.
  • the core body 15 in which the contact element 16 is fixed, as in the embodiment according to Fig. 2 in a cylinder bore 21 which provides a counter-abutment surface 24 for the contact element.
  • the cross-sectional area of the cylindrical contact surface portion 28 is less than that of the reduced-diameter cylinder portion 26, which in turn is smaller than that of the diameter-extended cylinder portion 27, to which the axial abutment surface 25 to Cooperation of the counter-abutment surface 24 of the core body 15 is formed.
  • the core body 15 is enclosed by a coil device 29, which is shown only schematically, for generating the magnetic field 30, which is shown in the form of field lines. It can be seen that the bore 21 with the contact element 16 received therein displaces the field lines radially outwards and thus bundles them in a radially adjacent to the contact element 16 region 31 of the core body 15, so as to increase the magnetic force between the core body 15 and pole plate 18 in this area.
  • Fig. 4 is a diagram shown that the relationship between the force acting on the armature assembly repulsion force and the width of the in Fig. 2 shown air gap 20 between the core body 15 and the pole plate 18 (alternatively directly to the permanent magnet means).
  • the repulsive force is given in Newton on the vertical axis and the width of the air gap in millimeters on the transverse axis.
  • the repulsive force is the difference between the magnetic repulsion force and the adhesion force. It will be appreciated that in the example, a repulsive force maximum exists at an air gap width of about 0.4mm. If the air gap is chosen smaller, the adhesion forces increase extremely, so that despite increasing magnetic forces, the repulsion force decreases.
  • the magnetic repulsive force and thus the resulting repulsive force with increasing air gap width also decreases.
  • the axial projection of the contact element 16 via the core body 15 is therefore preferably selected in the embodiment shown so that the resulting air gap has a width of at least approximately 0.4 mm in that switching position in which the actuating element 2 bears against the contact element.
  • Fig. 5 shows an embodiment of a preferably used core area 5. It can be seen, provided in the core body 15 contact element 16, which projects beyond the core body 15 in the axial direction. It can also be seen that the core area-side contact surface 11 is made slightly spherical, wherein the crowning radius corresponding to a multiple of the diameter of the front contact surface portion 28, which is preferred.
  • a radial preferred position of the adjusting element 2 can be set on the contact element, as a result of which jamming against a contact element edge is reliably prevented.

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

Claims (12)

  1. Dispositif de commande électromagnétique (1), en particulier pour un dispositif de réglage d'arbre à cames d'un moteur à combustion interne d'un véhicule automobile, comprenant un élément de commande (2) allongé, constituant une zone d'engagement au niveau d'une extrémité, déplaçable par la force d'un dispositif de bobine stationnaire (29), et présentant de préférence par sections un contour d'enveloppe cylindrique, lequel élément de commande traverse un évidement (8) dans des moyens d'aimants permanents (6) du dispositif de commande électromagnétique (1) disposés du côté de l'enveloppe, lesquels sont réalisés en vue de coopérer avec une zone de noyau stationnaire (5) du dispositif de commande électromagnétique (1) comprenant un corps de noyau (15), et lequel élément de commande s'applique dans une position de commutation par une surface de contact frontale du côté de l'élément de commande (10) contre une surface de contact (11) du côté de la zone de noyau,
    caractérisé en ce que
    la surface de contact du côté de la zone de noyau (11) du dispositif de commande électromagnétique (1) est formée au moins en partie par un élément de contact (16) du dispositif de commande électromagnétique fixé dans le corps de noyau (15), lequel élément de contact est réalisé en un matériau qui présente une dureté supérieure à celle du matériau du corps de noyau (15).
  2. Dispositif de commande selon la revendication 1,
    caractérisé en ce que
    la surface de contact du côté de la zone de noyau (11) est formée entièrement par l'élément de contact (16).
  3. Dispositif de commande selon l'une quelconque des revendications 1 ou 2,
    caractérisé en ce que
    l'élément de contact (16) présente une résistance au flux magnétique supérieure à celle du corps de noyau (15) afin de concentrer le flux magnétique dans une région (31) notamment de section transversale annulaire, adjacente à l'élément de contact (16).
  4. Dispositif de commande selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    la dureté du matériau de l'élément de contact (16), de préférence indiquée en HRC, est au moins deux fois plus élevée, de préférence au moins trois fois plus élevée, de préférence au moins quatre fois plus élevée que la dureté du matériau du corps de noyau (15).
  5. Dispositif de commande selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    la surface de contact du côté de la zone de noyau (11) est inférieure à une surface en section transversale de l'élément de commande (2), en particulier au côté frontal de l'élément de commande (2) tourné vers la zone de noyau (5) et/ou la surface en section transversale de l'élément de commande (2) entourée par les moyens d'aimants permanents (6), de préférence la surface de contact du côté de la zone de noyau (11) correspondant seulement au maximum à 70 %, de préférence au maximum à 60 %, en particulier de préférence au maximum à 50 %, et plus préférablement au maximum à 40 % de cette surface en section transversale.
  6. Dispositif de commande selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    l'élément de contact (16) s'appuie axialement contre le corps de noyau (15) avec une surface de butée de préférence annulaire.
  7. Dispositif de commande selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    l'élément de contact (16) est reçu dans un alésage frontal (21) du corps de noyau (15), de préférence est maintenu dans cet alésage (21) au moyen d'un ajustement serré et/ou est fixé contre le corps de noyau (15) par matage de préférence axial et/ou radial du corps de noyau.
  8. Dispositif de commande selon la revendication 7,
    caractérisé en ce que
    l'alésage (21) est réalisé sous forme d'alésage étagé et forme un étage de l'alésage (21) en tant que surface de butée conjuguée axiale (24) pour l'élément de contact (16).
  9. Dispositif de commande selon l'une quelconque des revendications 7 ou 8,
    caractérisé en ce que
    la surface de contact formée par l'élément de contact (16) est inférieure au diamètre d'alésage maximal de l'alésage.
  10. Dispositif de commande selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    l'élément de contact (16) présente un côté frontal (9) de contour bombé, constituant une surface de contact (10) du côté de l'élément de commande.
  11. Dispositif de commande selon l'une quelconque des revendications précédentes,
    caractérisé en ce que
    l'élément de contact (16) dépasse axialement au-delà du corps de noyau (15) dans une mesure telle qu'un entrefer résultant (20) entre les moyens d'aimants permanents (6) et le corps de noyau (15) soit si large que lors d'une alimentation donnée en courant du dispositif de bobine (29), une force de repoussement entre les moyens d'aimants permanents (6) et le corps de noyau (15) soit maximale.
  12. Dispositif de réglage d'arbre à cames pour régler un arbre à cames dans un moteur à combustion interne comprenant un dispositif de commande électromagnétique selon l'une quelconque des revendications précédentes.
EP20120733618 2011-06-22 2012-06-15 Dispositif de positionnement électromagnétique et dispositif de réglage d'arbre à cames Active EP2724354B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110051268 DE102011051268B4 (de) 2011-06-22 2011-06-22 Elektromagnetische Stellvorrichtung sowie Nockenwellenverstellvorrichtung
PCT/EP2012/061437 WO2012175421A1 (fr) 2011-06-22 2012-06-15 Dispositif de réglage électromagnétique et dispositif de réglage d'arbre à cames

Publications (2)

Publication Number Publication Date
EP2724354A1 EP2724354A1 (fr) 2014-04-30
EP2724354B1 true EP2724354B1 (fr) 2014-09-24

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Application Number Title Priority Date Filing Date
EP20120733618 Active EP2724354B1 (fr) 2011-06-22 2012-06-15 Dispositif de positionnement électromagnétique et dispositif de réglage d'arbre à cames

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Country Link
US (1) US9021995B2 (fr)
EP (1) EP2724354B1 (fr)
CN (1) CN103620708B (fr)
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US9583249B2 (en) 2014-10-31 2017-02-28 Husco Automotive Holdings Llc Methods and systems for push pin actuator
JP6311617B2 (ja) * 2015-01-19 2018-04-18 株式会社デンソー 電磁アクチュエータ
DE102015109077A1 (de) * 2015-06-09 2016-12-15 Kendrion (Villingen) Gmbh Volumenstromgeregeltes Sitzventil
KR101634546B1 (ko) 2015-10-05 2016-06-29 주식회사 현대케피코 전자식 연속 가변 밸브 타이밍 조정 장치 및 방법
CN105546195A (zh) * 2016-02-29 2016-05-04 成都富临精工汽车零部件有限公司 一种自润滑电磁驱动器
DE102020109117A1 (de) 2020-04-01 2021-10-07 Eto Magnetic Gmbh Haftoptimierte Ankerbaugruppe sowie elektromagnetische Stellvorrichtung

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US5986530A (en) * 1998-01-13 1999-11-16 Caterpillar Inc. Solenoid and method for manufacturing
ATE531054T1 (de) 2006-08-03 2011-11-15 Eto Magnetic Kg Elektromagnetische stellvorrichtung
DE202007010814U1 (de) * 2006-08-03 2007-11-29 Eto Magnetic Kg Elektromagnetische Stellvorrichtung
DE202006011905U1 (de) * 2006-08-03 2007-12-06 Eto Magnetic Kg Elektromagnetische Stellvorrichtung
DE202007005133U1 (de) * 2007-04-04 2008-08-14 Eto Magnetic Gmbh Elektromagnetische Stellvorrichtung
DE202009001187U1 (de) * 2009-01-30 2010-06-24 Eto Magnetic Gmbh Elektromagnetische Stellvorrichtung
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CN103620708A (zh) 2014-03-05
US9021995B2 (en) 2015-05-05
EP2724354A1 (fr) 2014-04-30
DE102011051268B4 (de) 2014-03-06
CN103620708B (zh) 2016-09-21
US20140137820A1 (en) 2014-05-22
DE102011051268A1 (de) 2012-12-27
WO2012175421A1 (fr) 2012-12-27

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