EP2724354A1 - Elektromagnetische stellvorrichtung sowie nockenwellenverstellvorrichtung - Google Patents
Elektromagnetische stellvorrichtung sowie nockenwellenverstellvorrichtungInfo
- Publication number
- EP2724354A1 EP2724354A1 EP12733618.8A EP12733618A EP2724354A1 EP 2724354 A1 EP2724354 A1 EP 2724354A1 EP 12733618 A EP12733618 A EP 12733618A EP 2724354 A1 EP2724354 A1 EP 2724354A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- core body
- contact element
- core
- adjusting device
- contact surface
- 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
Links
- 239000000463 material Substances 0.000 claims abstract description 19
- 238000002485 combustion reaction Methods 0.000 claims abstract 3
- 230000004907 flux Effects 0.000 claims description 3
- 239000012141 concentrate Substances 0.000 claims 1
- 238000011161 development Methods 0.000 description 4
- 230000018109 developmental process Effects 0.000 description 4
- 229910000851 Alloy steel Inorganic materials 0.000 description 3
- 239000000314 lubricant Substances 0.000 description 3
- 230000009467 reduction Effects 0.000 description 3
- 239000000853 adhesive Substances 0.000 description 2
- 230000001070 adhesive effect Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000003921 oil Substances 0.000 description 2
- 229910000760 Hardened steel Inorganic materials 0.000 description 1
- 230000006978 adaptation Effects 0.000 description 1
- 229910045601 alloy Inorganic materials 0.000 description 1
- 239000000956 alloy Substances 0.000 description 1
- 239000004020 conductor Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 230000005012 migration Effects 0.000 description 1
- 238000013508 migration Methods 0.000 description 1
- 239000010705 motor oil Substances 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
- 238000004804 winding Methods 0.000 description 1
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
- Electromagnetic actuator as well
- 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 10.
- the Applicant has developed an improved electromagnetic actuator described in WO 2008/014996 A1 for adjusting a camshaft in a motor vehicle. From the document it is known to reduce the lubricant-related adhesive force between the actuator and the core area in that in the end face of the actuator, a slot-shaped recess and / or notch, ie recess, is provided. With the proposed by the applicant reduction of the contact surfaces between the actuator and the core area is accompanied by a significantly increased surface pressure and thus an increased material load of the core body of the core area. There are efforts to improve the wear resistance of the adjusting device while reducing the adhesion force. Preferably, the efficiency of the adjusting device should be improved at the same time.
- 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 in terms of the camshaft adjusting device with the features of claim 10.
- Advantageous developments of the invention are specified in the subclaims. All combinations of at least two features disclosed in the description, the claims and / or the figures fall within the scope of the invention.
- 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 magnetically well-conductive, 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 core body is selectively influenced, in particular bundled in a contact element adjacent, preferably annular region, whereby the efficiency of the electromagnetic actuator is increased, which in turn can be used a smaller dimensioned (space-optimized) coil device.
- the air gap which is preferably formed between the permanent magnet means or an armature-side pole disk and the core body, preferably as part of a disk package, can be adjusted via the core body to a force maximum (vertex), ie the air gap, by means of the preferably pressed-in contact element with defined projection can be adjusted or optimized with regard to a maximum repulsive force, whereby minimum switching times can be achieved.
- a force maximum verex
- 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 for example be achieved in that the core body of the steel alloy 1 1 SMn30 and the, preferably pin-shaped, contact element of the alloy 16MnCr5 is formed.
- 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-area-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 is a partially cutaway view of a possible embodiment of an electromagnetic actuator according to the concept of the invention, in which the core area-side contact area is formed by a contact element defined in a core body,
- FIG. 2 a detailed representation of a possible embodiment of a combination of core region and armature
- FIG. 3 a representation of the optimized field line course through the use of a magnetically poorly conducting contact element
- Fig. 4 is a diagram which can be used to design the air gap and thus the axial projection of the contact element on the core body to a maximum
- Fig. 5 shows the representation of an embodiment with spherical, contact element-side contact surface.
- Fig. 1 shows the realization of an electromagnetic actuator for an otherwise not shown camshaft adjusting device.
- a possible embodiment variant of the combination of core region and armature is shown in FIGS. 2 and 3.
- 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 actuating device 1 comprises, within a cup-shaped housing 4, a coil device, which is known per se and not shown in FIG. 1, to which a magnetic core region 5 is assigned.
- 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 have the shape of a cylindrical disc in the embodiment shown in FIG. 1. 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 1 1 supports.
- the electromagnetic actuating device 1 is held in an engine block 12 which is 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 in several parts and comprises a core body 15 of magnetically good conductive material, in the concrete embodiment of a steel alloy 1 1 SMn 30 with a Hardness of 10 HRC.
- a, the core area-side contact surface 1 1 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 that Core body 15.
- armature 17 is shown with elongated actuator 2 and core portion 5 according to a preferred embodiment.
- FIG. 2 shows 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 Polpol nature 19 facing Ringpol constitution the Polefficiency 18 and the end face 9 of the actuator 2.
- frontally formed in the core body 15 is formed as a stepped bore bore 21, the is divided into a rear, cylindrical, reduced diameter portion 22 (press-fit) and a front, diameter-expanded portion 23, the bottom of which forms a counter-abutment surface 24 for an annular axial stop surface 25 of the contact element 16.
- 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 the positive reception of the contact element 16 in the stepped bore 21, the contact element 16 according to the illustrated preferred embodiment, a lower diameter-reduced cylinder portion 26 and an axially adjacent, diameter-enlarged cylinder portion 27, which projects beyond the diameter-reduced cylinder portion 26 by means of a circumferential covenant, on the side facing away from the actuator 2 side, the axial stop surface 25 is formed.
- 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 1 1 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 shows an alternative representation of a detail of an electromagnetic setting device shown by way of example in FIG. 1.
- the core body 15 in which the contact element 16 is fixed, and indeed as in the embodiment of 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 for 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 contact element 16 received therein follows the field lines displaced radially outward and thus bundles in a radially adjacent to the contact element 16 region 31 of the core body 15, thus increasing the magnetic force between the core body 15 and pole piece 18 in this area.
- Fig. 4 is a diagram showing the relationship between the force acting on the armature assembly repulsion force and the width of the air gap 20 shown in Fig. 2 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 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.
- 5 shows an exemplary embodiment of a core region 5 which is preferably used. It can be seen that the contact element 16 provided in the core body 15 projects beyond the core body 15 in the axial direction. It can also be seen that the contact area 11 on the core area is slightly convex, with the radius defining the crowning corresponding to a multiple of the diameter of the front contact area section 28, which is preferred. As a result of this crowning, 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.
Landscapes
- 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)
Abstract
Description
Claims
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 (de) | 2011-06-22 | 2012-06-15 | Elektromagnetische stellvorrichtung sowie nockenwellenverstellvorrichtung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2724354A1 true EP2724354A1 (de) | 2014-04-30 |
EP2724354B1 EP2724354B1 (de) | 2014-09-24 |
Family
ID=46506312
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20120733618 Active EP2724354B1 (de) | 2011-06-22 | 2012-06-15 | Elektromagnetische stellvorrichtung sowie nockenwellenverstellvorrichtung |
Country Status (5)
Country | Link |
---|---|
US (1) | US9021995B2 (de) |
EP (1) | EP2724354B1 (de) |
CN (1) | CN103620708B (de) |
DE (1) | DE102011051268B4 (de) |
WO (1) | WO2012175421A1 (de) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0277376U (de) * | 1988-12-01 | 1990-06-13 | ||
US5986530A (en) * | 1998-01-13 | 1999-11-16 | Caterpillar Inc. | Solenoid and method for manufacturing |
WO2008014996A1 (de) | 2006-08-03 | 2008-02-07 | Eto Magnetic Gmbh | 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 |
DE202011001412U1 (de) | 2011-01-12 | 2012-04-17 | Eto Magnetic Gmbh | Elektromagnetische Stellvorrichtung sowie Nockenwellenverstellvorrichtung |
-
2011
- 2011-06-22 DE DE201110051268 patent/DE102011051268B4/de active Active
-
2012
- 2012-06-15 US US14/127,993 patent/US9021995B2/en active Active
- 2012-06-15 CN CN201280030734.3A patent/CN103620708B/zh active Active
- 2012-06-15 EP EP20120733618 patent/EP2724354B1/de active Active
- 2012-06-15 WO PCT/EP2012/061437 patent/WO2012175421A1/de active Application Filing
Non-Patent Citations (1)
Title |
---|
See references of WO2012175421A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN103620708B (zh) | 2016-09-21 |
EP2724354B1 (de) | 2014-09-24 |
DE102011051268A1 (de) | 2012-12-27 |
DE102011051268B4 (de) | 2014-03-06 |
WO2012175421A1 (de) | 2012-12-27 |
US20140137820A1 (en) | 2014-05-22 |
CN103620708A (zh) | 2014-03-05 |
US9021995B2 (en) | 2015-05-05 |
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