EP3087575A1 - Dispositif de réglage électromagnétique - Google Patents

Dispositif de réglage électromagnétique

Info

Publication number
EP3087575A1
EP3087575A1 EP14828454.0A EP14828454A EP3087575A1 EP 3087575 A1 EP3087575 A1 EP 3087575A1 EP 14828454 A EP14828454 A EP 14828454A EP 3087575 A1 EP3087575 A1 EP 3087575A1
Authority
EP
European Patent Office
Prior art keywords
armature
plunger
unit
stroke
movement
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP14828454.0A
Other languages
German (de)
English (en)
Other versions
EP3087575B1 (fr
Inventor
Timo Rigling
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
Original Assignee
ETO Magnetic 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 ETO Magnetic GmbH filed Critical ETO Magnetic GmbH
Publication of EP3087575A1 publication Critical patent/EP3087575A1/fr
Application granted granted Critical
Publication of EP3087575B1 publication Critical patent/EP3087575B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • 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
    • H01F7/13—Electromagnets; Actuators including electromagnets with armatures characterised by pulling-force characteristics
    • 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
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/03—Auxiliary actuators
    • F01L2820/031—Electromagnets

Definitions

  • the present invention relates to an electromagnetic actuator according to the preamble of the main claim. Furthermore, the present invention relates to a camshaft adjustment system comprising such an electromagnetic actuator in conjunction with a camshaft adjusting device of an internal combustion engine as a preferred use of the electromagnetic actuator.
  • an electromagnetic actuator which has radially-laterally engaging on the armature plunger locking means.
  • These latching means make it possible to increase the dynamics of the armature and plunger movement, by triggering the latching means only after exceeding a predetermined force and thus the adjustment movement takes place within a shortened positioning time.
  • the actuating force must be generated over the entire effective actuating stroke of the combined armature and tappet unit, as well as the provision must be made opposite the entire stroke.
  • the same increased (and disadvantageous for the reasons discussed above) dimensioning requirements arise in principle as in the generic, gatungslagenden state of the art.
  • the object is achieved by the electromagnetic actuator with the features of the main claim.
  • the armature unit provided movable relative to the plunger means, so that the armature unit (preferably along its armature stroke) drive and can take along the plunger means, but the plunger means movable relative to the armature unit additionally a plunger stroke caused by the spring means according to the invention, can perform, which is inventively larger than the armature stroke itself.
  • the axially coupled arrangement of armature unit and plunger means cooperates with force application means acting on the shell side on the plunger means in the form of the pressure body according to the invention, which has adjacent ramps both with the ramp or cone section on the plunger means and with the plunger sections of larger or smaller diameter - or cone section cooperate can.
  • this arrangement is designed and dimensioned such that the armature unit entrains the plunger means along the direction of movement during its armature movement, whereby the plunger means are advanced as far as the (at least one, preferably radially predominantly distributed) pressure body until the cone or ramp (related to the / the pressure body) is overcome.
  • the further feed then happens by expansion of the spring means according to the invention (which have already already supported the armature movement to the armature stroke).
  • the combined action of both the anchor means and the spring means on the plunger means results in an effective plunger stroke which is greater than the actual armature stroke; in practical embodiments of the invention, at least by a factor of 1.5, more preferably by at least a factor of 2.5.
  • the adjusting device according to the invention can be dimensioned to a much smaller armature stroke (with corresponding advantages of the mechanics and the construction volume), relative to an achievable control stroke.
  • the ramp or cone section according to the invention has an equally advantageous effect on the return of the adjusting device or the plunger means to the starting position.
  • the plunger means are reset from the engagement position (for example, by the engagement in the adjustment groove provided in the preferred use form "camshaft adjustment") only so far against the direction of movement, until, axially, the pressure body (s) follow the ramp.
  • the action of the shell-side force on the ramp or cone section would then lead to a further return or application of force to the ram means in the direction of the starting position lead, without this (in addition to the adjusting partner) postsstellhub further contact with the control partner requires or otherwise driven externally.
  • advantageous effect also for the return movement that the anchor unit itself must have an armature stroke smaller than the ram stroke.
  • the pressure body is preferably a ball or spherical portion of a differently shaped pressure body, other variants are conceivable; It is nevertheless advantageous to arrange the pressure body, more preferably pretensioned by the pretensioning force of a compression spring which is preferably oriented radially to the direction of movement, in a plurality and around a circumference of the plunger means, so that a reliable influencing of the plunger movement by these pressure bodies can take place ,
  • a concrete arrangement of the spring is arbitrary and may depend on the circumstances in the surrounding housing; This also applies to the specific design of a spring.
  • the geometry of the ramp or cone section is important; In the practical realization, it has been found preferable to provide a first recess of the ramp or cone section, which is larger than a (maximum) axial extension of the pressure body, that is to say a ball diameter.
  • a pitch angle of the Rampen- or cone section (as measured in longitudinal section relative to the longitudinal axis of movement) in the range between 20 ° and 60 °, preferably between 30 ° and 50 ° to provide.
  • the spring means more preferably realized as a pressure and / or coil spring, in a (hollow cylindrical) inner region of the radially symmetrical tappet means provided;
  • the plunger means may have approximately a hollow cylindrical interior and / or an inner annular shoulder.
  • the spring means would then be supported on a portion of a housing guiding the plunger means, so that according to the invention the spring means can make their contribution to the acceleration of the plunger unit, wherein the armature unit can continue to comprise permanent magnet means as before and in an otherwise known manner Alternatively, however, it can also be actuated electromagnetically in a different manner relative to the stationary core unit.
  • the armature unit (or caused in the actuator electromagnetic drive of the armature unit) monostable design, ie only provide an anchor initial position as the only stable end position, in which case while energizing the coil means though the armature unit is moved around the armature, however, after completion of the energization, the armature unit is moved into the armature's starting position. back falls.
  • This configuration is advantageous in cooperation with the plunger means in that the armature unit after the initial driving of the plunger means makes no contribution to further advancement of the plunger means (this is rather taken over by the spring means) while then returning, in particular by the interaction between the pressure body and Rampen- or cone section, no additional return or take along the anchor unit is necessary in the starting position.
  • an apparatus is provided by the present invention which significantly prolongs effective stroke length of existing generic actuators without requiring equally larger or bulkier magnet assemblies.
  • the present invention is not limited to this application context, but rather is also suitable for any other actuating applications in which there are limited electromagnetic means long strokes are to be realized.
  • FIG. 1 is a schematic longitudinal sectional view of the electromagnetic actuator according to a first preferred embodiment of the invention, symbolically divided along the vertical axis of symmetry and movement in a withdrawn initial position (right) and an engaging condition (left) relative to a camshaft shift gate as engagement partner.
  • the reference numeral 10 symbolically shows an armature unit with an elongated armature tappet 12 and an armature body 14 which is widened relative to it.
  • the armature unit 10 is wound relative to the armature coil (not shown in the drawing) in an otherwise known manner a stationary core unit (not shown) movable between an armature initial position (Fig. 1, right) and an armature feed position (Fig. 1, left half).
  • a typical armature stroke is in the range between 1 and 1, 5 mm with an effective stroke of the plunger means of about 4 mm.
  • FIG. 1 further schematically illustrates, the armature tappet section 12 engages on the inside on a tappet unit (tappet means) 16, which is guided in a surrounding tappet housing 18.
  • the tappet unit 16 is open on the bottom side for receiving the armature tappet section 12; this is dimensioned so that it maintains a - small - distance from the plunger in the armature initial position (Fig.1, right half) and then along the direction of movement (in the plane of FIG. 1 down) only on feed the plunger 16 ,
  • a coil spring 22 is shown, which is supported at the other end of a ring bottom 24 of the plunger housing 18.
  • the coil spring 22 is correspondingly compressed and exerts a maximum preload on the plunger unit 16 in the downward direction of movement.
  • the ram unit 16 has, in the direction of the armature unit 10, a tappet portion 26 larger outside diameter; Via a conical section 28, this (larger) outer diameter tapers in a front-tappet section 30, which has a reduced external diameter, on an engagement-side front tappet section.
  • the cone section 28 extends over an axial length of approximately 1.2 mm at an angle with respect to the vertical movement axis of approximately 25 °.
  • the axial extension (axial length) of the cone section 28 corresponds to the armature stroke, plus the (gap-laden) distance between an engagement end 34 of the tappet unit and the control partner in the disengaged state.
  • pressure bodies 32 grip the lateral surface of the tappet unit in the form of balls distributed around the circumference of the tappet unit 16; These balls 32 are biased by their own, horizontally (and thus radially to the longitudinal movement axis) extending compression springs 33.
  • Engaging side i. Opposite the armature unit 10, the plunger unit 16 forms the engagement portion (engagement end) 34, which is dimensioned to cooperate with a shift groove 36 of a switching gate 38 of a camshaft adjustment system shown by way of example as a control partner;
  • the double arrow 40 illustrates the groove depth in the example shown of approximately 3.7 mm, which is covered by the ram stroke (here approx. 4 mm).
  • energization of the coil means is first followed by movement of the armature unit (consisting of the armature body 14 and the armature directly and firmly ansitzenden, alternatively (permanently) magnetically adhering anchoring anchor plunger 12) along the direction of movement, ie in Fig. 1 downwards; the armature stroke is in the range between about 1 and 1, 5 mm.
  • the armature stroke is in the range between about 1 and 1, 5 mm.
  • the cone section 28 slides in the downward direction along the horizontally fixed spherical pressure body 32, until they lie on the (upper) cylindrical shell portion 26 of the plunger unit.
  • Fig. 1 shows the fully ejected state of the armature plunger 16 from the housing 18.
  • the plunger unit 16 has a total stroke of about 4 mm performs and engages in this state in the groove 36 of the adjusting partner 38 a.
  • the camshaft adjustment takes place in an otherwise known manner.
  • the adjusting groove 36 also causes the return of the plunger 16 along a first return stroke section; Concretely, a decreasing groove depth (upon rotation of the gate 38) causes the plunger unit 16 to be pushed in the return direction (ie, upwards in the plane of the figure).
  • the device shown here is dimensioned such that this provision takes place axially as far along the first return stroke until the balls 32 engaging on the cylindrical lateral surface 26 reach the beginning of the cone section 28 (acting as a ramp). To this Time then leads the radial application of force to the balls 32 as a pressure body to that along the conical surface, the return movement is continued in the direction of the starting position, the cone so far a subsequent to the first return stroke of the groove second return stroke, to the in FIG.
  • the plunger unit 16 in this return operation does not additionally reset the anchor unit 10 with (about by entrainment of the section 12), but took place immediately after the Bestromungsende already when taking out the plunger 16 is a falling back the anchor unit 10 in its monostable end position (Fig. 1, right).
  • a bistable design for example by means of a permanently magnetically realized anchor body 14, may be useful, in particular also with regard to a (magnetic field detected) position, motion and / or reset detection.

Landscapes

  • 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)

Abstract

L'invention concerne un dispositif de réglage électromagnétique pourvu d'une unité d'induit (10) pouvant être entraînée avec une course d'induit le long d'une direction de déplacement axial à la suite de l'alimentation en courant de moyens fixes formant bobine. Le dispositif de réglage électromagnétique est également pourvu de moyens formant poussoir (16) associés à l'unité d'induit, conçus côté extrémité pour coopérer avec un partenaire de réglage externe, et pouvant se déplacer le long de la direction de déplacement, avec une course de poussoir, d'une position de départ à une position d'entrée en contact, et de moyens élastiques (22) précontraignant les moyens formant poussoir dans la direction de déplacement. Les moyens formant poussoir guidés mobiles par rapport à l'unité d'induit comportent côté enveloppe une section en forme de rampe et/ou de cône (28) entre une section de poussoir côté induit de plus grand diamètre (26) et une section de poussoir (30) présentant un plus petit diamètre. Un corps de pression (32) contenu sous l'effet d'une précontrainte dans une section de boîtier (18) guidant les moyens formant poussoir coopère côté enveloppe avec la section en forme de rampe ou de cône et la section en forme de rampe ou de cône est présente sur les moyens formant poussoir de sorte que le corps de pression, lorsque l'unité bobine n'est pas alimentée en courant et/ou lorsque l'unité d'induit n'est pas entraînée, et du fait d'une force exercée côté enveloppe sur la section en forme de rampe et/ou de cône, ramène les moyens formant poussoir à l'encontre de la précontrainte des moyens élastiques en direction de la position de départ, en particulier dans la position de départ, la course de l'induit étant moins importante que la course du poussoir.
EP14828454.0A 2013-12-23 2014-12-18 Dispositif de réglage électromagnétique Active EP3087575B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013114830.1A DE102013114830A1 (de) 2013-12-23 2013-12-23 Elektromagnetische Stellvorrichtung
PCT/EP2014/078547 WO2015097068A1 (fr) 2013-12-23 2014-12-18 Dispositif de réglage électromagnétique

Publications (2)

Publication Number Publication Date
EP3087575A1 true EP3087575A1 (fr) 2016-11-02
EP3087575B1 EP3087575B1 (fr) 2017-07-12

Family

ID=52394215

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14828454.0A Active EP3087575B1 (fr) 2013-12-23 2014-12-18 Dispositif de réglage électromagnétique

Country Status (5)

Country Link
US (1) US9741481B2 (fr)
EP (1) EP3087575B1 (fr)
CN (1) CN105830179B (fr)
DE (1) DE102013114830A1 (fr)
WO (1) WO2015097068A1 (fr)

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DE102017117402A1 (de) * 2017-08-01 2019-02-07 Eto Magnetic Gmbh Vorrichtung und Verfahren zum Aktivieren eines Motorbremsbetriebs eines Verbrennungsmotors
DE102017213539A1 (de) * 2017-08-03 2019-02-07 Mahle International Gmbh Ventiltrieb
DE102017124485A1 (de) 2017-10-19 2019-04-25 Eto Magnetic Gmbh Elektromagnetische Aktuatorvorrichtung und Verwendung einer solchen
CN108251977A (zh) * 2018-04-08 2018-07-06 苏州胜璟电磁科技有限公司 一种距离可调电磁铁
CN117123981B (zh) * 2023-10-26 2024-03-15 江苏快克芯装备科技有限公司 芯片吸取机构微压力装置及芯片焊接机

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Also Published As

Publication number Publication date
EP3087575B1 (fr) 2017-07-12
CN105830179A (zh) 2016-08-03
WO2015097068A1 (fr) 2015-07-02
US20160322146A1 (en) 2016-11-03
DE102013114830A1 (de) 2015-06-25
US9741481B2 (en) 2017-08-22
CN105830179B (zh) 2018-01-23

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