EP3510260B1 - Electromagnetic drive arrangement in particular for setting the position of a camshaft in an internal combustion engine - Google Patents
Electromagnetic drive arrangement in particular for setting the position of a camshaft in an internal combustion engine Download PDFInfo
- Publication number
- EP3510260B1 EP3510260B1 EP17768005.5A EP17768005A EP3510260B1 EP 3510260 B1 EP3510260 B1 EP 3510260B1 EP 17768005 A EP17768005 A EP 17768005A EP 3510260 B1 EP3510260 B1 EP 3510260B1
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- EP
- European Patent Office
- Prior art keywords
- tappet
- armature
- camshaft
- adapter
- adjusting apparatus
- Prior art date
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- 238000002485 combustion reaction Methods 0.000 title claims description 13
- 239000000463 material Substances 0.000 claims description 5
- 229910001220 stainless steel Inorganic materials 0.000 claims description 4
- 239000010935 stainless steel Substances 0.000 claims description 4
- 238000005452 bending Methods 0.000 description 4
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000006835 compression Effects 0.000 description 2
- 238000007906 compression Methods 0.000 description 2
- 239000000446 fuel Substances 0.000 description 2
- 239000010705 motor oil Substances 0.000 description 2
- 230000009849 deactivation Effects 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000007373 indentation Methods 0.000 description 1
- 239000000696 magnetic material Substances 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
Classifications
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- 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
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- 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
- H01F7/1607—Armatures entering the winding
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- 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
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
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- 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
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- 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
- F01L2301/00—Using particular materials
-
- 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
-
- 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
-
- 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
- H01F7/081—Magnetic constructions
- H01F2007/086—Structural details of the armature
-
- 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
- H01F7/081—Magnetic constructions
Definitions
- the present application relates to an electromagnetic adjusting device, in particular for adjusting camshafts of an internal combustion engine.
- Camshafts have a number of cams that represent eccentric sections on the camshaft.
- the cams can either be arranged fixedly on the camshaft or on camshaft sections, which can be attached to a cylindrical shaft in a rotationally fixed but axially displaceable manner. With the cams, axially displaceable components arranged adjacent to one another can be displaced at regular intervals by rotating the camshaft.
- One application of the camshafts that should be emphasized is the opening and closing of valves in an internal combustion engine. In modern internal combustion engines, it is possible, for example, to change the engine characteristics from a comfort-oriented to a sporty one, which is achieved, among other things, by changing the valve lift caused by the Shape of the cam is determined, is implemented.
- camshafts that have cams of different sizes and shapes.
- the camshaft or the camshaft section must be axially displaced in order to allow the respective cams to interact with the valve.
- the camshafts have different grooves in which an actuator engages with a different number of tappets.
- the plungers are movable between a retracted and an extended position, the plungers engaging the grooves in the extended position.
- the grooves represent a guide section and together with the engaging tappets form a link guide for the axial adjustment of the camshaft, which for this purpose must be rotated by a certain amount.
- the camshafts rotate at half the speed of the crankshaft, so that the camshafts can rotate up to 3000 and more rpm. Because of these high speeds of rotation, high radial forces act suddenly on the ram.
- the tappets are only supported in housing sections, also referred to as adapters, with which the adjusting device can be attached to a component, in particular to a cylinder head cover.
- the bending moments acting on the plungers due to the high radial forces can bend the plungers to such an extent that they jam in the adapters. As a result, they are no more movable between the retracted and the extended position, whereby the camshaft or the camshaft section can no longer be moved axially.
- the plunger according to FIG DE 10 2013 102 241 A1 stored not only in the adapter, but also in the pole core which is clearly spaced from the adapter.
- the plunger is not only mounted in the adapter, but also in the armature, which is also arranged at a clear distance from the adapter.
- the tappet In order to keep the wear of the free end of the tappet, with which it engages in the groove of the camshaft, as low as possible, the tappet is rotatably mounted in the adjusting device.
- the anchor In contrast, however, the anchor is in the DE 10 2013 102 241 A1 and the WO 2016/001 254 A1 the anchor is connected to the tappet by means of a clearance fit. As a result, only axial forces, but not torques acting about the longitudinal axis, can be transmitted. The rotation of the tappet when it engages in the groove of the camshaft is therefore not transmitted to the armature.
- the pamphlets DE 10 2015 111 385 A1 , DE 10 2010 045 601 A1 and JP 2014 31745 as U.S. 4,568,021 A represent further state of the art.
- the object of one embodiment of the present invention is to create an electromagnetic adjusting device, in particular for adjusting camshafts or a camshaft section of an internal combustion engine, with which the above-mentioned disadvantages can be eliminated or at least noticeably reduced.
- an adjusting device is to be created in which the high bending moments acting on the plunger during operation can be safely absorbed so that the plunger does not jam.
- the wear between the armature and the tappet should be reduced so that their relative position and in particular their relative axial position to one another do not change during operation.
- One embodiment of the invention relates to an electromagnetic actuating device, in particular for adjusting camshafts of an internal combustion engine, comprising a coil unit that can be energized, with which, in the energized state, an armature mounted movably along a longitudinal axis of the actuating device can be moved relative to a pole core between a retracted position and an extended position cooperating with the armature and movable along the longitudinal axis mounted tappet with a free end with which the tappet interacts with the camshaft in the extended position to adjust the camshaft, and an adapter with which the adjusting device can be attached to a component, in particular to a cylinder head cover, the armature and the tappet non-rotatably are interconnected and the Adjusting device has a first bearing section inside the adapter for rotatably mounting the plunger and a second bearing section outside the adapter for rotatably mounting the plunger and / or the armature.
- the first bearing section is arranged inside the adapter, while the second bearing section is arranged outside the adapter and consequently at a distance from the first bearing section. It is advisable to arrange the second bearing section behind the first bearing section as seen from the free end of the plunger. A small distance is sufficient to prevent the plunger from bending and jamming as a result. Either the plunger or the anchor or both are stored together in the second storage section.
- the second bearing section consists of a non-magnetic or non-magnetizable material. Due to the energization of the coil unit, a magnetic field is generated which acts on the armature and moves it relative to the pole core. If the second bearing section consists of a non-magnetic, non-magnetized or non-magnetizable material, the magnetic field lines are not disturbed or deflected. The second bearing therefore does not need to be taken into account in the design of the coil unit, the armature and the pole core, so that it is possible to fall back on designs that have already been used and tested, so that the additional design effort for implementing the proposed adjusting device in this embodiment can be kept low .
- the second bearing section comprises a plain bearing.
- Plain bearings are widely used and proven machine elements, so that the second bearing section can be designed inexpensively and reliably.
- standardized slide bearings can be used, which further reduces costs.
- slide bearings are largely maintenance-free and able to absorb high forces.
- the plain bearings are lubricated by the engine oil of the combustion engine.
- the sliding bearing can consist of plastic or a non-magnetic or magnetizable stainless steel.
- Many plain bearings are also available in these materials, so that this material restriction does not result in any noticeable increase in costs. It also ensures that the magnetic field lines are not disturbed.
- the plain bearing is arranged in a tubular body.
- the tubular body can, for example, be shrunk onto the sliding bearing so that a secure connection can be created without additional connecting elements, which simplifies production.
- the tubular body can be designed in such a way that it only has to be inserted into the adjusting device in a few simple steps and at the same time defines the position of the slide bearing, which also simplifies assembly.
- the sliding bearing is made of a non-magnetic material, no magnetic forces act between the armature and the sliding bearing, which reduces the friction between the armature and the sliding bearing. In this way, on the one hand, wear can be reduced and, on the other hand, the speed at which the armature and consequently the plunger are moved can be increased.
- the plain bearing can be dimensioned in such a way that a gap is formed between the armature and the tubular body. This too is prevents the magnetic forces acting between the armature and the tubular body from creating friction with the disadvantages mentioned above.
- the invention is characterized in that the device comprises a spring element with a first end and a second end, which is supported at the first end by means of a spring plate on the plunger or on the armature and at the second end on the second bearing section. It is entirely possible to move the armature and consequently the plunger in the desired directions along the longitudinal axis exclusively by means of a corresponding energization of the coil unit. However, correspondingly more complex control electronics are necessary for this. In addition, it takes a certain amount of time for the existing magnetic field to dissipate and the new one to build up.
- the plunger can already be moved in the corresponding direction when the magnetic force that is impressed by the magnetic field on the armature and counteracts the pretensioning force of the spring element falls below a certain value. In this respect, the plunger can be moved more quickly.
- the spring plate can be fastened by means of a clearance fit on the plunger or on the armature and axially fixed by means of a shoulder in the effective direction of the pretensioning force. The rotary movement of the plunger is therefore not transmitted to the spring element, so that the spring element does not twist or wear.
- the spring element is supported on the second bearing section and in particular on the sliding bearing, so that no further constructive measures have to be taken in order to fix the axial position of the spring element. This keeps the manufacturing effort low.
- the spring plate can be arranged movably within the tubular body, so that the spring plate is guided by the tubular body. This prevents the spring plate from tilting or tilting or getting stuck on adjacent components.
- the adapter has a stop against which the spring plate strikes in the extended position.
- the wear of the plunger when it engages in the groove is intended to be reduced in that it is rotatably mounted.
- the tappet can roll on the side surfaces of the groove, thereby avoiding or at least reducing sliding that promotes wear.
- the wear of the plunger can be further reduced by the fact that the plunger engages in the groove in the extended state, but does not rest on the bottom surface of the groove or only when the groove depth is reduced at the outlet of the groove. Because the spring plate strikes against the stop of the adapter, which can be designed as a shoulder, for example, the extended position is clearly defined.
- a further developed embodiment is characterized in that the device has a permanent magnet with which the armature is held in the retracted position in the de-energized state of the coil unit. It is true that the armature could be kept in the retracted position by a corresponding constant energization of the coil unit, but for this purpose a corresponding amount of electrical energy is necessary. This electrical energy can be saved by using a permanent magnet, so that the actuating device can be operated economically.
- FIG. 1 an exemplary embodiment of an electromagnetic actuating device 10 according to the invention is shown on the basis of a basic sectional illustration. From the Figure 1 it can be seen that the adjusting device 10 has two identically constructed structural units. For the sake of clarity, essentially only one of the structural units is described below, the description also applying to the other structural unit.
- the adjusting device 10 has a housing 12 which, in the exemplary embodiment shown, is essentially tubular. Regarding the in Figure 1 In the selected representation, the housing 12 is closed at the upper end with a cover 14 and at the lower end with a flange 16.
- the adjusting device 10 has an adapter 18 which is fastened to the flange 16. With this adapter 18, the adjusting device 10 can be attached, for example, to a cylinder head cover of an internal combustion engine (not shown).
- the adapter 18 have recesses 20 in which seals, not shown, can be used to Adjusting device 10 to seal against the cylinder head cover.
- the adapter 18 forms a first bearing section 22 for a plunger 24 which is displaceable along a longitudinal axis L of the adjusting device 10 the inner surface of the adapter 18 coming into contact with the outer surface of the tappet 24.
- the first bearing section 22 is lubricated by the engine oil of the internal combustion engine.
- the adapter 18 is made of hardened stainless steel.
- the tappet 24 is pressed with an armature 26 and is thus connected to it in a rotationally fixed manner.
- the non-rotatable connection can also be implemented in other ways, for example by welding.
- the armature 26 has a recess into which the plunger 24 engages over a longer section.
- the plunger 24 has a free end 28 which protrudes beyond the adapter 18.
- the adjusting device 10 has a second bearing section 30 which, in the exemplary embodiment shown, is arranged, starting from the free end 28, behind the first bearing section 22 and is designed as a slide bearing 32.
- the sliding bearing 32 for example made of a plastic or a non-magnetic stainless steel, is arranged in a tubular body 34 and is connected to the tubular body 34, for example by being shrunk on.
- the plain bearing 32 is arranged in the example shown so that only the armature 26 is supported with the plain bearing 32. Consequently, the second bearing section 30 is located within the housing 12.
- Both the first bearing section 22 and the second bearing section 30 are designed such that the plunger 24 and the armature 26 are mounted both rotatably about the longitudinal axis L and displaceably along the longitudinal axis L. .
- the slide bearing 32 projects radially inward somewhat beyond the tubular body 34, so that a narrow gap is formed between the tubular body 34 and the armature 26. The tubular body 34 and the armature 26 are therefore not
- the adjusting device 10 has a spring plate 36 which encompasses the tappet 24 in a ring shape, which has a clearance fit with respect to the tappet 24 and rests against the tappet 24 in the area of an enlarged diameter 38 of the tappet 24.
- the spring plate 36 is axially fixed by means of the armature 26.
- the spring plate 36 consequently performs the same axial movements along the longitudinal axis L as the armature 26 and the plunger 24.
- the spring plate 36 is radially enclosed by the tubular body 34. During the axial movements of the spring plate 36, the spring plate 36 is guided by the tubular body 34.
- a spring element 40 is provided which has a first end 42 and a second end 44.
- the spring element 40 can provide a prestressing force which acts essentially along the longitudinal axis L. With the first end 42, the spring element 40 is supported on the spring plate 36 and with its second end 44 on the sliding bearing 32. Due to the clearance fit of the spring plate 36 compared to the Tappets 34 are only transmitted rotational movements of the tappet 24 to the spring plate 36 when the pretensioning force with which the spring plate 36 is pressed against the area of an enlarged diameter 38 exceeds a certain value.
- the adjusting device 10 comprises a coil unit 46 which surrounds the armature 26 in an annular manner while forming a gap.
- a pole core 48 is provided which, based on the in Figure 1 selected representation is arranged above the armature 26.
- the adjusting device 10 has a permanent magnet 50 which is fastened to the cover 14 and is arranged above the pole core 48.
- the armature 26 and the tappet 24 are pressed together, they perform the same movements.
- the plunger 24 and the armature 26 consequently do not perform any movements relative to one another, so that there are no points of wear due to relative movements between the armature 26 and the tappet 24.
- the left tappet 24 and the left armature 26 are in a retracted position, whereas the right tappet 24 and the right armature 26 are in an extended position.
- the actuating device 10 is operated in the following way:
- the permanent magnet 50 exerts an attractive force acting along the longitudinal axis L on the armature 26, so that the armature 26 is attracted by the permanent magnet 50 in the retracted state and rests on the pole core 48.
- the spring element 40 is compressed, so that the spring element 40 provides a pretensioning force which, however, is smaller than the attraction force of the Permanent magnet 50.
- the armature 26 and the plunger 24 consequently assume the retracted position.
- the groove has a helical course with respect to the axis of rotation of the camshaft, so that the engagement of the tappet 24 in the groove in combination with the rotation of the camshaft about its own axis of rotation causes a longitudinal adjustment along the axis of rotation of the camshaft.
- the tappet 24 rests against one of the side walls of the groove and rolls on it, so that the tappet 24 is rotated at a very high rotational speed when it engages in the groove. Due to the compression of the armature 26 with the tappet 24, the rotary movement of the tappet 24 is also transmitted to the armature 26.
- the stop 52 of the adapter 18 and the depth of the groove are selected so that the plunger 24 does not touch the bottom surface of the groove with its free end 28 in the extended position.
- the depth of the groove decreases towards the end, so that from a At a certain angle of rotation of the camshaft, the free end 28 of the tappet 24 comes into contact with the bottom surface of the groove, whereby the tappet 24 is shifted again in the direction of the permanent magnet 50.
- the energization of the coil unit 46 is interrupted, so that the force of attraction exerted by the permanent magnet 50 on the armature 26 is again greater than the sum of the prestressing force provided by the spring element 40 and the magnetic force that no longer acts due to the lack of energization of the coil unit 46. Consequently, the plunger 24 and the armature 26 again assume the retracted position until the coil unit 46 is again energized.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Power Engineering (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
- Electromagnets (AREA)
Description
Die vorliegende Anmeldung betrifft eine elektromagnetische Stellvorrichtung insbesondere zum Verstellen von Nockenwellen eines Verbrennungsmotors.The present application relates to an electromagnetic adjusting device, in particular for adjusting camshafts of an internal combustion engine.
Nockenwellen weisen eine Anzahl von Nocken auf, die exzentrische Abschnitte auf der Nockenwelle darstellen. Die Nocken können entweder fest auf der Nockenwelle oder auf Nockenwellenabschnitten angeordnet sein, die drehfest aber axial verschiebbar auf eine zylindrische Welle aufbracht werden können. Mit den Nocken können angrenzend angeordnete, axial verschiebbare Bauteile durch Drehen der Nockenwelle in regelmäßigen Abständen verschoben werden. Eine hervorzuheben Anwendung der Nockenwellen stellt dabei das Öffnen und Schließen von Ventilen in einem Verbrennungsmotor dar. In modernen Verbrennungsmotoren ist es möglich, die Motorcharakteristik beispielsweise von einer komfortbetonten zu einer sportlichen Charakteristik zu verändern, was unter anderem durch die Veränderung des Ventilhubs, der durch die Form der Nocken bestimmt wird, umgesetzt wird. Zudem erfordern unterschiedliche Motordrehzahlen variable Ventilhübe, um das Drehmoment und den Kraftstoffverbrauch zu optimieren. Andere Verbrennungsmotoren weisen eine Zylinderabschaltung auf, bei denen einige der Zylinder zum Einsparen von Kraftstoff abgeschaltet werden können. In diesem Fall müssen die Ventile der abgeschalteten Zylinder gar nicht mehr geöffnet werden. Auch in diesem Fall ist es vorteilhaft, nicht nur einzelne Zylinder abzuschalten, sondern auch variable Ventilhübe aus den oben genannten Gründen zu ermöglichen.Camshafts have a number of cams that represent eccentric sections on the camshaft. The cams can either be arranged fixedly on the camshaft or on camshaft sections, which can be attached to a cylindrical shaft in a rotationally fixed but axially displaceable manner. With the cams, axially displaceable components arranged adjacent to one another can be displaced at regular intervals by rotating the camshaft. One application of the camshafts that should be emphasized is the opening and closing of valves in an internal combustion engine. In modern internal combustion engines, it is possible, for example, to change the engine characteristics from a comfort-oriented to a sporty one, which is achieved, among other things, by changing the valve lift caused by the Shape of the cam is determined, is implemented. In addition, different engine speeds require variable valve lifts in order to optimize torque and fuel consumption. Other internal combustion engines have cylinder deactivation, in which some of the cylinders can be deactivated to save fuel. In this case, the valves of the deactivated cylinders no longer have to be opened. In this case, too, it is advantageous not only to switch off individual cylinders, but also to enable variable valve lifts for the reasons mentioned above.
Derartige Verbrennungsmotoren erfordern Nockenwellen, die Nocken mit unterschiedlicher Größe und Form aufweisen. Um jedoch das Ventil mit den unterschiedlichen Hubkurven öffnen und schließen zu können, muss die Nockenwelle oder der Nockenwellenabschnitt axial verschoben werden, um die jeweils die entsprechenden Nocken mit dem Ventil zusammenwirken zu lassen. Bei bekannten Stellvorrichtungen, die beispielsweise in der der
Bei den meisten Viertakt-Verbrennungsmotoren in Standardbauweise drehen die Nockenwellen mit der halben Drehzahl der Kurbelwelle, so dass die Nockenwellen durchaus bis zu 3000 und mehr U/min drehen können. Aufgrund dieser hohen Umdrehungsgeschwindigkeiten wirken stoßartig hohe radiale Kräfte auf die Stößel. Bei den oben beschriebenen Stellvorrichtungen zum Verstellen von Nockenwellen oder eines Nockenwellenabschnitts sind die Stößel nur in auch als Adapter bezeichneten Gehäuseabschnitten gelagert, mit welchen die Stellvorrichtung an einem Bauteil, insbesondere an einer Zylinderkopfhaube, befestigt werden kann. Die aufgrund der hohen radialen Kräfte auf die Stößel wirkenden Biegemomente können sich die Stößel so weit verbiegen, dass sie sich in den Adaptern verklemmen. Infolgedessen sind sie nicht mehr zwischen der eingefahrenen und der ausgefahrenen Stellung bewegbar, wodurch die Nockenwelle oder der Nockenwellenabschnitt auch nicht mehr axial verschoben werden kann.In most standard four-stroke internal combustion engines, the camshafts rotate at half the speed of the crankshaft, so that the camshafts can rotate up to 3000 and more rpm. Because of these high speeds of rotation, high radial forces act suddenly on the ram. In the case of the adjusting devices described above for adjusting camshafts or a camshaft section, the tappets are only supported in housing sections, also referred to as adapters, with which the adjusting device can be attached to a component, in particular to a cylinder head cover. The bending moments acting on the plungers due to the high radial forces can bend the plungers to such an extent that they jam in the adapters. As a result, they are no more movable between the retracted and the extended position, whereby the camshaft or the camshaft section can no longer be moved axially.
Um diesem Nachteil zu begegnen, ist der Stößel gemäß der
Um den Verschleiß des freien Endes des Stößels, mit welchem dieser in die Nut der Nockenwelle eingreift, so gering wie möglich zu halten, ist der Stößel drehbar in der Stellvorrichtung gelagert. Im Gegensatz dazu ist jedoch der Anker bei der
Die Druckschriften
Aufgabe einer Ausführungsform der vorliegenden Erfindung ist es, eine elektromagnetische Stellvorrichtung insbesondere zum Verstellen von Nockenwellen oder eines Nockenwellenabschnitts eines Verbrennungsmotors zu schaffen, mit welcher die oben genannten Nachteile beseitigt oder zumindest spürbar reduziert werden können. Insbesondere soll eine Stellvorrichtung geschaffen werden, bei welcher die im Betrieb auf den Stößel wirkenden hohen Biegemomente sicher aufgenommen werden können, so dass es nicht zu einem Verklemmen des Stößels kommt. Gleichzeitig soll der Verschleiß zwischen Anker und Stößel reduziert werden, so dass sich ihre relative Position und insbesondere ihre relative axiale Position zueinander im Betrieb nicht verändert.The object of one embodiment of the present invention is to create an electromagnetic adjusting device, in particular for adjusting camshafts or a camshaft section of an internal combustion engine, with which the above-mentioned disadvantages can be eliminated or at least noticeably reduced. In particular, an adjusting device is to be created in which the high bending moments acting on the plunger during operation can be safely absorbed so that the plunger does not jam. At the same time, the wear between the armature and the tappet should be reduced so that their relative position and in particular their relative axial position to one another do not change during operation.
Diese Aufgabe wird mit den in Anspruch 1 angegebenen Merkmalen gelöst. Vorteilhafte Ausführungsformen sind Gegenstand der Unteransprüche.This object is achieved with the features specified in claim 1. Advantageous embodiments are the subject of the subclaims.
Eine Ausführungsform der Erfindung betrifft eine elektromagnetische Stellvorrichtung insbesondere zum Verstellen von Nockenwellen eines Verbrennungsmotors, umfassend eine bestrombare Spuleneinheit, mit welcher im bestromten Zustand ein entlang einer Längsachse der Stellvorrichtung bewegbar gelagerter Anker relativ zu einem Polkern zwischen einer eingefahrenen Stellung und einer ausgefahrenen bewegbar ist, einen mit dem Anker zusammenwirkenden und entlang der Längsachse bewegbar gelagerten Stößel mit einem freien Ende, mit welchem der Stößel in der ausgefahrenen Stellung zum Verstellen der Nockenwelle mit dieser zusammenwirkt, und einen Adapter, mit welchem die Stellvorrichtung an einem Bauteil, insbesondere an einer Zylinderkopfhaube, befestigbar ist, wobei der Anker und der Stößel drehfest miteinander verbunden sind und die Stellvorrichtung einen ersten Lagerabschnitt innerhalb des Adapters zum drehbaren Lagern des Stößels und einen zweiten Lagerabschnitt außerhalb des Adapters zum drehbaren Lagern des Stößels und/oder des Ankers aufweist.One embodiment of the invention relates to an electromagnetic actuating device, in particular for adjusting camshafts of an internal combustion engine, comprising a coil unit that can be energized, with which, in the energized state, an armature mounted movably along a longitudinal axis of the actuating device can be moved relative to a pole core between a retracted position and an extended position cooperating with the armature and movable along the longitudinal axis mounted tappet with a free end with which the tappet interacts with the camshaft in the extended position to adjust the camshaft, and an adapter with which the adjusting device can be attached to a component, in particular to a cylinder head cover, the armature and the tappet non-rotatably are interconnected and the Adjusting device has a first bearing section inside the adapter for rotatably mounting the plunger and a second bearing section outside the adapter for rotatably mounting the plunger and / or the armature.
Dadurch, dass der Anker und der Stößel drehfest miteinander verbunden sind, wird die Drehung des Stößels beim Eingreifen in die Nut der Nockenwelle oder des Nockenwellenabschnitts auf den Anker übertragen. Folglich findet keine relative Drehbewegung zwischen dem Anker und dem Stößel statt, so dass hier keine Verschleißstellen mehr vorhanden sind, welche zu einer Veränderung insbesondere der relativen axialen Position des Stößels und des Ankers zueinander führen könnte. Eine begrenzte relative axiale Bewegbarkeit zwischen dem Anker und dem Stößel kann vorgesehen werden, da diese nicht oder zu einem im Vergleich zur Drehbewegung deutlich verminderten Verschleiß führt. Aus fertigungstechnischer Sicht bietet es sich an, den Anker mit dem Stößel zu verpressen, so dass sich der Anker und der Stößel sowohl translatorisch als auch rotatorisch synchron bewegen.Because the armature and the tappet are connected to one another in a rotationally fixed manner, the rotation of the tappet is transmitted to the armature when it engages in the groove of the camshaft or the camshaft section. As a result, there is no relative rotational movement between the armature and the tappet, so that there are no longer any wear points which could lead to a change in particular in the relative axial position of the tappet and the armature to one another. A limited relative axial mobility between the armature and the tappet can be provided, since this does not lead to wear or to a significantly reduced wear compared to the rotary motion. From a manufacturing point of view, it is advisable to press the armature with the ram, so that the armature and the ram move synchronously both translationally and rotationally.
Ein Verklemmen des Stößels aufgrund der im Betrieb auf ihn wirkenden Biegemomente wird dadurch verhindert, dass der Stößel nicht nur im ersten Lagerabschnitt, sondern auch im zweiten Lagerabschnitt gelagert ist. Der erste Lagerabschnitt ist innerhalb des Adapters angeordnet, während der zweite Lagerabschnitt außerhalb des Adapters und folglich beabstandet vom ersten Lagerabschnitt angeordnet ist. Es bietet sich dabei an, den zweiten Lagerabschnitt vom freien Ende des Stößels aus gesehen hinter dem ersten Lagerabschnitt anzuordnen. Dabei genügt bereits ein geringer Abstand, um ein Verbiegen und ein hieraus resultierendes Verklemmen des Stößels zu verhindern. Dabei kann entweder der Stößel oder der Anker oder beide zusammen im zweiten Lagerabschnitt gelagert werden. Bei einer entsprechenden drehfesten Verbindung des Stößels mit dem Anker bewirkt eine Lagerung des Ankers im zweiten Lagerabschnitt eine indirekte Lagerung des Stößels im zweiten Lagerabschnitt. Dies gilt umso mehr, wenn der Anker mit dem Stößel verpresst ist.Jamming of the plunger due to the bending moments acting on it during operation is prevented by the fact that the plunger is not only supported in the first bearing section but also in the second bearing section. The first bearing section is arranged inside the adapter, while the second bearing section is arranged outside the adapter and consequently at a distance from the first bearing section. It is advisable to arrange the second bearing section behind the first bearing section as seen from the free end of the plunger. A small distance is sufficient to prevent the plunger from bending and jamming as a result. Either the plunger or the anchor or both are stored together in the second storage section. With a corresponding non-rotatable connection of the plunger to the armature, a bearing of the armature in the second bearing section causes an indirect bearing of the tappet in the second bearing section. This is all the more true when the armature is pressed with the ram.
Nach Maßgabe einer weiteren Ausführungsform besteht der zweite Lagerabschnitt aus einem nicht magnetischen oder nicht magnetisierbaren Material. Aufgrund der Bestromung der Spuleneinheit wird ein Magnetfeld erzeugt, welches auf den Anker wirkt und diesen relativ zum Polkern bewegt. Wenn der zweite Lagerabschnitt aus einem nicht magnetischen, nicht magnetisierten oder nicht magnetisierbaren Material besteht, werden die Magnetfeldlinien nicht gestört oder umgelenkt. Die zweite Lagerstelle braucht daher bei der Auslegung der Spuleneinheit, des Ankers und des Polkerns nicht weiter berücksichtigt zu werden, so dass auf bereits verwendete und erprobte Auslegungen zurückgegriffen werden kann, wodurch der konstruktive Mehraufwand zum Umsetzen der vorschlagsgemäßen Stellvorrichtung in dieser Ausführungsform gering gehalten werden kann.According to a further embodiment, the second bearing section consists of a non-magnetic or non-magnetizable material. Due to the energization of the coil unit, a magnetic field is generated which acts on the armature and moves it relative to the pole core. If the second bearing section consists of a non-magnetic, non-magnetized or non-magnetizable material, the magnetic field lines are not disturbed or deflected. The second bearing therefore does not need to be taken into account in the design of the coil unit, the armature and the pole core, so that it is possible to fall back on designs that have already been used and tested, so that the additional design effort for implementing the proposed adjusting device in this embodiment can be kept low .
Erfindungsgemäß umfasst der zweite Lagerabschnitt ein Gleitlager. Gleitlager stellen weit verbreitete und bewährte Maschinenelemente dar, so dass der zweite Lagerabschnitt kostengünstig und zuverlässig ausgestaltet werden kann. Insbesondere können standardisierte und genormte Gleitlager verwendet werden, was die Kosten nochmals verringert. Zudem sind Gleitlager weitgehend wartungsfrei und in der Lage, hohe Kräfte aufzunehmen. Die Schmierung der Gleitlager erfolgt über das Motoröl des Verbrennungsmotors.According to the invention, the second bearing section comprises a plain bearing. Plain bearings are widely used and proven machine elements, so that the second bearing section can be designed inexpensively and reliably. In particular, standardized slide bearings can be used, which further reduces costs. In addition, slide bearings are largely maintenance-free and able to absorb high forces. The plain bearings are lubricated by the engine oil of the combustion engine.
Bei einer weitergebildeten Ausführungsform kann das Gleitlager aus Kunststoff oder aus einem nicht magnetischen oder magnetisierbaren Edelstahl bestehen. Auch in diesen Materialien sind viele Gleitlager erhältlich, so dass durch diese Materialeinschränkung keine nennenswerte Kostensteigerung hervorgerufen wird. Zudem wird sichergestellt, dass die Magnetfeldlinien nicht gestört werden.In a further developed embodiment, the sliding bearing can consist of plastic or a non-magnetic or magnetizable stainless steel. Many plain bearings are also available in these materials, so that this material restriction does not result in any noticeable increase in costs. It also ensures that the magnetic field lines are not disturbed.
Das Gleitlager ist in einem rohrförmigen Körper angeordnet. Der rohrförmige Körper kann beispielsweise auf das Gleitlager aufgeschrumpft werden, so dass eine sichere Verbindung ohne zusätzliche Verbindungselemente geschaffen werden kann, wodurch die Fertigung vereinfacht wird. Zudem kann der rohrförmige Körper so ausgestaltet sein, dass er nur noch mit wenigen Handgriffen in die Stellvorrichtung eingesetzt werden muss und zugleich die Position des Gleitlagers festlegt, wodurch ebenfalls die Montage vereinfacht wird. Insbesondere dann, wenn das Gleitlager aus einem nicht magnetischen Material aufgebaut ist, wirken keine Magnetkräfte zwischen dem Anker und dem Gleitlager, was die Reibung zwischen dem Anker und dem Gleitlager reduziert. Hierdurch können einerseits der Verschleiß reduziert und andererseits die Geschwindigkeit, mit welcher der Anker und folglich der Stößel bewegt werden, erhöht werden. Darüber hinaus kann das Gleitlager so dimensioniert werden, dass ein Spalt zwischen dem Anker und dem rohrförmigen Körper gebildet wird. Auch hierdurch wird verhindert, dass die zwischen dem Anker und dem rohrförmigen Körper wirkenden Magnetkräfte Reibung mit den oben genannten Nachteilen entsteht.The plain bearing is arranged in a tubular body. The tubular body can, for example, be shrunk onto the sliding bearing so that a secure connection can be created without additional connecting elements, which simplifies production. In addition, the tubular body can be designed in such a way that it only has to be inserted into the adjusting device in a few simple steps and at the same time defines the position of the slide bearing, which also simplifies assembly. In particular when the sliding bearing is made of a non-magnetic material, no magnetic forces act between the armature and the sliding bearing, which reduces the friction between the armature and the sliding bearing. In this way, on the one hand, wear can be reduced and, on the other hand, the speed at which the armature and consequently the plunger are moved can be increased. In addition, the plain bearing can be dimensioned in such a way that a gap is formed between the armature and the tubular body. This too is prevents the magnetic forces acting between the armature and the tubular body from creating friction with the disadvantages mentioned above.
Die Erfindung zeichnet sich dadurch aus, dass die Vorrichtung ein Federelement mit einem ersten Ende und einem zweiten Ende umfasst, welches sich am ersten Ende mittels eines Federtellers am Stößel oder am Anker und am zweiten Ende am zweiten Lagerabschnitt abstützt. Es ist durchaus möglich, den Anker und folglich den Stößel ausschließlich mittels einer entsprechenden Bestromung der Spuleneinheit in die gewünschten Richtungen entlang der Längsachse zu bewegen. Allerdings ist hierfür eine entsprechend aufwendigere Steuerelektronik notwendig. Zudem vergeht eine gewisse Zeit, bis dass sich das vorhandene Magnetfeld abgebaut und das neue aufgebaut hat. Mithilfe des Federelements kann der Stößel bereits in die entsprechende Richtung bewegt werden, wenn die vom Magnetfeld auf den Anker aufgeprägte und der Vorspannkraft des Federelements entgegenwirkende Magnetkraft einen bestimmten Wert unterschreitet. Insofern kann der Stößel schneller bewegt werden. Der Federteller kann mittels einer Spielpassung am Stößel oder am Anker befestigt und axial mittels eines Absatzes in die Wirkrichtung der Vorspannkraft festgelegt sein. Die Drehbewegung des Stößels wird daher nicht auf das Federelement übertragen, so dass es nicht zu einem Verdrehen oder einem Verschleiß des Federelements kommt. Am zweiten Ende stützt sich das Federelement am zweiten Lagerabschnitt und insbesondere am Gleitlager ab, so dass keine weitergehenden konstruktiven Maßnahmen ergriffen werden müssen, um die axiale Position des Federelements festzulegen. Der Fertigungsaufwand wird hierdurch gering gehalten. Zudem kann der Federteller innerhalb des rohrförmigen Körpers bewegbar angeordnet sein, so dass der Federteller vom rohrförmigen Körper geführt wird. Ein Verkippen oder Verkanten oder ein Hängenbleiben des Federtellers an benachbarten Bauteilen wird hierdurch vermieden.The invention is characterized in that the device comprises a spring element with a first end and a second end, which is supported at the first end by means of a spring plate on the plunger or on the armature and at the second end on the second bearing section. It is entirely possible to move the armature and consequently the plunger in the desired directions along the longitudinal axis exclusively by means of a corresponding energization of the coil unit. However, correspondingly more complex control electronics are necessary for this. In addition, it takes a certain amount of time for the existing magnetic field to dissipate and the new one to build up. With the aid of the spring element, the plunger can already be moved in the corresponding direction when the magnetic force that is impressed by the magnetic field on the armature and counteracts the pretensioning force of the spring element falls below a certain value. In this respect, the plunger can be moved more quickly. The spring plate can be fastened by means of a clearance fit on the plunger or on the armature and axially fixed by means of a shoulder in the effective direction of the pretensioning force. The rotary movement of the plunger is therefore not transmitted to the spring element, so that the spring element does not twist or wear. At the second end, the spring element is supported on the second bearing section and in particular on the sliding bearing, so that no further constructive measures have to be taken in order to fix the axial position of the spring element. This keeps the manufacturing effort low. In addition, the spring plate can be arranged movably within the tubular body, so that the spring plate is guided by the tubular body. This prevents the spring plate from tilting or tilting or getting stuck on adjacent components.
Nach Maßgabe einer weiteren Ausführungsform weist der Adapter einen Anschlag auf, gegen den der Federteller in der ausgefahrenen Stellung anschlägt. Wie eingangs erwähnt, soll der Verschleiß des Stößels beim Eingreifen in die Nut dadurch verringert werden, dass er drehbar gelagert ist. Hierdurch kann sich der Stößel an den Seitenflächen der Nut abrollen, wodurch ein verschleißförderndes Gleiten vermieden oder zumindest reduziert wird. Der Verschleiß des Stößels kann dadurch weiter reduziert werden, dass der Stößel im ausgefahrenen Zustand zwar in die Nut eingreift, nicht aber auf der Bodenfläche der Nut aufliegt oder nur dann, wenn sich die Nuttiefe am Auslauf der Nut reduziert. Dadurch, dass der Federteller gegen den Anschlag des Adapters anschlägt, der beispielsweise als ein Absatz ausgeführt sein kann, wird die ausgefahrene Stellung klar definiert. Zudem ist bei einer entsprechenden Anordnung des Stößels relativ zur Nut gewährleistet, dass der Stößel an seinem freien Ende außerhalb des Auslaufs der Nut nicht mit der Bodenfläche der Nut in Kontakt tritt, wodurch der Verschleiß des Stößels am freien Ende reduziert wird.According to a further embodiment, the adapter has a stop against which the spring plate strikes in the extended position. As mentioned at the beginning, the wear of the plunger when it engages in the groove is intended to be reduced in that it is rotatably mounted. As a result, the tappet can roll on the side surfaces of the groove, thereby avoiding or at least reducing sliding that promotes wear. The wear of the plunger can be further reduced by the fact that the plunger engages in the groove in the extended state, but does not rest on the bottom surface of the groove or only when the groove depth is reduced at the outlet of the groove. Because the spring plate strikes against the stop of the adapter, which can be designed as a shoulder, for example, the extended position is clearly defined. In addition, with a corresponding arrangement of the tappet relative to the groove, it is ensured that the tappet does not come into contact with the bottom surface of the groove at its free end outside the outlet of the groove, whereby the wear of the tappet at the free end is reduced.
Eine weitergebildete Ausführungsform ist dadurch gekennzeichnet, dass die Vorrichtung einen Permanentmagnet aufweist, mit welchem der Anker im unbestromten Zustand der Spuleneinheit in der eingefahrenen Stellung gehalten wird. Zwar könnte der Anker durch eine entsprechende ständige Bestromung der Spuleneinheit in der eingefahrenen Stellung gehalten werden, wozu aber eine entsprechende Menge an elektrischer Energie notwendig ist. Diese elektrische Energie kann durch die Verwendung eines Permanentmagnets eingespart werden, so dass die Stellvorrichtung wirtschaftlich betrieben werden kann.A further developed embodiment is characterized in that the device has a permanent magnet with which the armature is held in the retracted position in the de-energized state of the coil unit. It is true that the armature could be kept in the retracted position by a corresponding constant energization of the coil unit, but for this purpose a corresponding amount of electrical energy is necessary. This electrical energy can be saved by using a permanent magnet, so that the actuating device can be operated economically.
Beispielhafte Ausführungsformen der Erfindung werden im Folgenden unter Bezugnahme auf die beigefügten Zeichnungen näher erläutert. Es zeigt
- Figur 1
- eine prinzipielle Schnittdarstellung durch ein Ausführungsbeispiel einer vorschlagsgemäßen elektromagnetischen Stellvorrichtung.
- Figure 1
- a basic sectional view through an embodiment of a proposed electromagnetic adjusting device.
In
Die Stellvorrichtung 10 weist ein Gehäuse 12 auf, welches im dargestellten Ausführungsbeispiel im Wesentlichen rohrförmig ausgestaltet ist. In Bezug auf die in
Der Adapter 18 bildet einen ersten Lagerabschnitt 22 für einen entlang einer Längsachse L der Stellvorrichtung 10 verschiebbaren Stößel 24. Der erste Lagerabschnitt 22 kann beispielsweise dadurch bereitgestellt werden, dass die äußere Oberfläche des Stößels 24 mit einer entsprechenden Oberflächengüte versehen ist, ebenso, wie die mit der äußeren Oberfläche des Stößels 24 in Kontakt tretende innere Oberfläche des Adapters 18. Eine Schmierung des ersten Lagerabschnitts 22 erfolgt über das Motoröl des Verbrennungsmotors. Um die hohen axialen Kräfte, die im Betrieb auf den Stößel 24 wirken, sicher aufnehmen zu können, ist der Adapter 18 aus einem gehärteten Edelstahl gefertigt.The
Der Stößel 24 ist im dargestellten Ausführungsbeispiel mit einem Anker 26 verpresst und damit drehfest mit ihm verbunden. Die drehfeste Verbindung kann auch auf andere Weise realisiert sein, beispielsweise durch Verschweißen. Um eine gute Verpressung zu erreichen, weist der Anker 26 eine Vertiefung auf, in welche der Stößel 24 über einen längeren Abschnitt eingreift. Der Stößel 24 weist ein freies Ende 28 auf, welches über den Adapter 18 hervorragt.In the exemplary embodiment shown, the
Die Stellvorrichtung 10 weist einen zweiten Lagerabschnitt 30 auf, der im dargestellten Ausführungsbeispiel ausgehend vom freien Ende 28 hinter dem ersten Lagerabschnitt 22 angeordnet und als ein Gleitlager 32 ausgeführt ist. Das Gleitlager 32, beispielsweise aus einem Kunststoff oder aus einem nicht magnetischen Edelstahl gefertigt, ist in einem rohrförmigen Körper 34 angeordnet und beispielsweise durch Aufschrumpfen mit dem rohrförmigen Körper 34 verbunden. Das Gleitlager 32 ist im dargestellten Beispiel so angeordnet, dass nur der Anker 26 mit dem Gleitlager 32 gelagert wird. Folglich befindet sich der zweite Lagerabschnitt 30 innerhalb des Gehäuses 12. Sowohl der erste Lagerabschnitt 22 als auch der zweite Lagerabschnitt 30 sind so ausgeführt, dass der Stößel 24 und der Anker 26 sowohl um die Längsachse L drehbar als auch entlang der Längsachse L verschiebbar gelagert sind. Das Gleitlager 32 steht radial nach innen etwas über den rohrförmigen Körper 34 vor, so dass ein schmaler Spalt zwischen dem rohrförmigen Körper 34 und dem Anker 26 gebildet wird. Der rohrförmige Körper 34 und der Anker 26 liegen daher nicht aneinander an.The adjusting
Ferner weist die Stellvorrichtung 10 einen den Stößel 24 ringförmig umgreifenden Federteller 36 auf, der eine Spielpassung gegenüber dem Stößel 24 aufweist und im Bereich einer Durchmesservergrößerung 38 des Stößels 24 an diesem anliegt. Darüber hinaus wird der Federteller 36 mittels des Ankers 26 axial fixiert. Der Federteller 36 führt folglich dieselben axialen Bewegungen entlang der Längsachse L aus wie der Anker 26 und der Stößel 24. Wie aus der
Darüber hinaus ist ein Federelement 40 vorgesehen, welches ein erstes Ende 42 und ein zweites Ende 44 aufweist. Das Federelement 40 kann eine im Wesentlichen entlang der Längsachse L wirkende Vorspannkraft bereitstellen. Mit dem ersten Ende 42 stützt sich das Federelement 40 am Federteller 36 und mit seinem zweiten Ende 44 am Gleitlager 32 ab. Aufgrund der Spielpassung des Federtellers 36 gegenüber dem Stößel 34 werden Drehbewegungen des Stößels 24 nur dann auf den Federteller 36 übertragen, wenn die Vorspannkraft, mit welcher der Federteller 36 gegen den Bereich einer Durchmesservergrößerung 38 gedrückt wird, einen bestimmten Wert übersteigt.In addition, a spring element 40 is provided which has a first end 42 and a second end 44. The spring element 40 can provide a prestressing force which acts essentially along the longitudinal axis L. With the first end 42, the spring element 40 is supported on the
Zum Bewegen des Ankers 26 umfasst die Stellvorrichtung 10 eine Spuleneinheit 46, welche den Anker 26 unter Ausbildung eines Spalts ringförmig umschließt. Darüber hinaus ist ein Polkern 48 vorgesehen, der bezogen auf die in
Dadurch, dass der Anker 26 und der Stößel 24 miteinander verpresst sind, führen sie dieselben Bewegungen aus. Der Stößel 24 und der Anker 26 führen folglich keine Relativbewegungen zueinander aus, so dass keine Verschleißstellen aufgrund von Relativbewegungen zwischen dem Anker 26 und dem Stößel 24 vorhanden sind. Der linke Stößel 24 und der linke Anker 26 befinden sich in einer eingefahrenen Stellung, wohingegen sich der rechte Stößel 24 und der rechte Anker 26 in einer ausgefahrenen Stellung befinden.Because the
Die Stellvorrichtung 10 wird auf folgende Weise betrieben: Der Permanentmagnet 50 übt eine entlang der Längsachse L wirkende Anziehungskraft auf den Anker 26 aus, so dass der Anker 26 im eingefahrenen Zustand vom Permanentmagnet 50 angezogen wird und am Polkern 48 anliegt. Hierdurch wird das Federelement 40 gestaucht, so dass das Federelement 40 eine Vorspannkraft bereitstellt, die aber kleiner ist als die Anziehungskraft des Permanentmagnets 50. Der Anker 26 und der Stößel 24 nehmen folglich die eingefahrene Stellung ein.The
Wird nun die Spuleneinheit 46 bestromt, wird ein Magnetfeld aufgebaut, welches eine Magnetkraft auf den Anker 26 induziert, welche in dieselbe Richtung wie die vom Federelement 40 bereitgestellte Vorspannkraft und folglich gegen die Anziehungskraft des Permanentmagnets 50 wirkt. Die Summe aus der Magnetkraft und der Vorspannkraft ist größer als die Anziehungskraft des Permanentmagnets 50, so dass der Anker 26 und folglich der Stößel 24 weg vom Permanentmagnet 50 entlang der Längsachse L bewegt werden, bis dass der Federteller 36 gegen einen Anschlag 52 des Adapters 18 anschlägt, wodurch der Stößel 24 und der Anker 26 die ausgefahrene Stellung erreicht haben. In dieser ausgefahrenen Stellung greift der Stößel 24 mit seinem freien Ende 28 in eine Nut einer nicht dargestellten Nockenwelle oder eines nicht dargestellten Nockenwellenabschnitts ein. Die Nut weist einen bezogen auf die Drehachse der Nockenwelle schraubenförmigen Verlauf auf, so dass das Eingreifen des Stößels 24 in die Nut in Kombination mit der Drehung der Nockenwelle um die eigene Drehachse eine Längsverstellung entlang der Drehachse der Nockenwelle bewirkt. Um die entsprechenden Axialkräfte zu übertragen, liegt der Stößel 24 an einer der Seitenwände der Nut an und rollt auf dieser ab, so dass der Stößel 24 beim Eingriff in die Nut mit einer sehr hohen Umdrehungsgeschwindigkeit gedreht wird. Aufgrund der Verpressung des Ankers 26 mit dem Stößel 24 wird die Drehbewegung des Stößels 24 auch auf den Anker 26 übertragen. Der Anschlag 52 des Adapters 18 und die Tiefe der Nut sind so gewählt, dass der Stößel 24 in der ausgefahrenen Stellung mit seinem freien Ende 28 die Bodenfläche der Nut nicht berührt. Die Tiefe der Nut nimmt aber zum Ende hin ab, so dass ab einem gewissen Drehwinkel der Nockenwelle eine Berührung des freien Endes 28 des Stößels 24 mit der Bodenfläche der Nut erfolgt, wodurch der Stößel 24 wieder in Richtung des Permanentmagnets 50 verschoben wird. Spätestens dann wird die Bestromung der Spuleneinheit 46 unterbrochen, so dass die vom Permanentmagnet 50 ausgeübte Anziehungskraft auf den Anker 26 wieder größer ist als die Summe aus der vom Federelement 40 bereitgestellten Vorspannkraft und der aufgrund der fehlenden Bestromung der Spuleneinheit 46 nicht mehr wirkenden Magnetkraft. Folglich nehmen der Stößel 24 und der Anker 26 wieder die eingefahrene Stellung ein, bis dass die Spuleneinheit 46 erneut bestromt wird.If the
- 1010
- StellvorrichtungAdjusting device
- 1212th
- Gehäusecasing
- 1414th
- Deckellid
- 1616
- Flanschflange
- 1818th
- Adapteradapter
- 2020th
- VertiefungenIndentations
- 2222nd
- erster Lagerabschnittfirst storage section
- 2424
- StößelPlunger
- 2626th
- Ankeranchor
- 2828
- freies Endefree end
- 3030th
- zweiter Lagerabschnittsecond storage section
- 3232
- Gleitlagerbearings
- 3434
- rohrförmiger Körpertubular body
- 3636
- FedertellerSpring plate
- 3838
- Bereich der DurchmesservergrößerungArea of increase in diameter
- 4040
- FederelementSpring element
- 4242
- erstes Endefirst end
- 4444
- zweites Endesecond end
- 4646
- SpuleneinheitCoil unit
- 4848
- PolkernPole core
- 5050
- PermanentmagnetPermanent magnet
- 5252
- Anschlagattack
- LL.
- LängsachseLongitudinal axis
Claims (5)
- Electromagnetic adjusting apparatus for adjusting camshafts or a section of a camshaft of a combustion motor, comprising- an energizable coil unit (46) with which, when supplied with a current, an anchor (26), which is moveably mounted along a longitudinal axis (L) of the adjusting apparatus (10), can be moved relative to a pole core (48) between a retracted position and a deployed position,- a tappet (24), which interacts with the anchor (26), is moveably mounted along the longitudinal axis (L), and which has a free end (28) with which the tappet (24), when in a deployed position, interacts with the camshaft to adjust the latter, and- an adapter (18) with which the adjusting apparatus (10) can be attached to a component, in particular to a cylinder head cover, wherein- the anchor (26) and the tappet (24) are non-rotatably connected to each other, and the adjusting apparatus (10) comprises- a first mounting segment (22) within the adapter (18) for the rotatable mounting of the tappet (24) and- a second mounting segment (30) outside of the adapter (18) for the rotatable mounting of the tappet (24) or of the anchor (26) which is non-rotatably connected to the tapped (24),characterized in that,the second mounting segment (30) includes a plain bearing (32), wherein the plain bearing (32) is arranged in a tube-shaped body (34), andin that the apparatus includes a spring element (40) with a first end (42) and with a second end (44) and which is supported at the first end (42) on the tappet (24) or on the anchor (26) by means of a spring seat (36) and at the second end (28) on the second mounting segment (30), andin that the plain bearing (32), the spring seat (36) and the spring element (40) are radially enclosed by the tube-shaped body (34).
- Adjusting apparatus in accordance with claim 1,
characterized in that the second mounting segment (30) is comprised of a non-magnetic or of a non-magnetizable material. - Adjusting apparatus in accordance with claim 1,
characterized in that the plain bearing (32) is comprised of plastic or of a non-magnetic or magnetizable stainless steel. - Adjusting apparatus in accordance with claim 1,
characterized in that the adapter (18) comprises an end stop (52) against which the spring seat (36) comes to rest in the deployed position. - Adjusting apparatus in accordance with any of the preceding claims,
characterized in that the apparatus comprises a permanent magnet (50) with which the anchor (26) is held in the retracted position when the coil unit (46) is not energized.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102016116776.2A DE102016116776A1 (en) | 2016-09-07 | 2016-09-07 | Electromagnetic actuator, in particular for adjusting camshafts of an internal combustion engine |
PCT/EP2017/071412 WO2018046314A1 (en) | 2016-09-07 | 2017-08-25 | Electromagnetic control device, in particular for adjusting camshafts of an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3510260A1 EP3510260A1 (en) | 2019-07-17 |
EP3510260B1 true EP3510260B1 (en) | 2021-09-29 |
Family
ID=59887192
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17768005.5A Active EP3510260B1 (en) | 2016-09-07 | 2017-08-25 | Electromagnetic drive arrangement in particular for setting the position of a camshaft in an internal combustion engine |
Country Status (6)
Country | Link |
---|---|
US (1) | US20210003047A1 (en) |
EP (1) | EP3510260B1 (en) |
JP (1) | JP6731542B2 (en) |
CN (1) | CN109690035B (en) |
DE (1) | DE102016116776A1 (en) |
WO (1) | WO2018046314A1 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017121949A1 (en) * | 2017-09-21 | 2019-03-21 | Kendrion (Villingen) Gmbh | Actuating device, as well as motor vehicle with an adjusting device |
CN108869056B (en) * | 2018-07-31 | 2023-12-22 | 辽宁工业大学 | Cylinder deactivation device of variable cylinder engine and control method thereof |
AT16974U1 (en) * | 2019-01-28 | 2021-01-15 | Msg Mechatronic Systems Gmbh | |
EP4259946A1 (en) * | 2020-12-11 | 2023-10-18 | Saint-Gobain Performance Plastics Corporation | Solenoid low friction bearing liner |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS61258976A (en) * | 1985-05-13 | 1986-11-17 | Nitsukisou Eiko Kk | Solenoid-driven reciprocating pump |
DE20114466U1 (en) * | 2001-09-01 | 2002-01-03 | Eto Magnetic Kg | Electromagnetic actuator |
JP2006097727A (en) * | 2004-09-28 | 2006-04-13 | Keihin Corp | Linear solenoid valve |
DE102006027349A1 (en) * | 2006-06-13 | 2007-12-20 | Schaeffler Kg | Camshaft adjuster with an electromagnetic actuator |
DE202006011904U1 (en) | 2006-08-03 | 2007-12-06 | Eto Magnetic Kg | Electromagnetic actuator |
WO2008014996A1 (en) | 2006-08-03 | 2008-02-07 | Eto Magnetic Gmbh | Electromagnetic actuating apparatus |
DE102006051809A1 (en) * | 2006-11-03 | 2008-05-08 | Schaeffler Kg | locking device |
DE102007028600B4 (en) | 2007-06-19 | 2011-06-22 | ETO MAGNETIC GmbH, 78333 | Electromagnetic actuator |
JP5442980B2 (en) * | 2008-11-06 | 2014-03-19 | カヤバ工業株式会社 | solenoid |
DE102010045601B4 (en) * | 2010-09-16 | 2013-04-18 | Hydac Electronic Gmbh | Electromagnetic actuator |
DE102011003760B4 (en) * | 2010-11-29 | 2022-03-24 | Schaeffler Technologies AG & Co. KG | Electromagnetic actuator |
JP6035965B2 (en) * | 2012-08-02 | 2016-11-30 | 株式会社デンソー | Electromagnetic actuator |
DE102012213660A1 (en) * | 2012-08-02 | 2014-02-06 | Schaeffler Technologies AG & Co. KG | Magnetic actuator of a sliding cam system |
DE102013102241A1 (en) | 2013-03-06 | 2014-09-11 | Kendrion (Villingen) Gmbh | Electromagnetic actuator, in particular for the camshaft adjustment of an internal combustion engine |
JP2015169183A (en) * | 2014-03-11 | 2015-09-28 | スズキ株式会社 | Variable valve device of internal combustion engine |
DE102014109124B4 (en) | 2014-06-30 | 2016-05-19 | Kendrion (Villingen) Gmbh | Electromagnetic camshaft adjusting device |
JP6248871B2 (en) * | 2014-09-05 | 2017-12-20 | 株式会社デンソー | Electromagnetic actuator |
JP2016149416A (en) * | 2015-02-10 | 2016-08-18 | 株式会社デンソー | Linear solenoid |
-
2016
- 2016-09-07 DE DE102016116776.2A patent/DE102016116776A1/en not_active Withdrawn
-
2017
- 2017-08-25 WO PCT/EP2017/071412 patent/WO2018046314A1/en unknown
- 2017-08-25 US US16/330,711 patent/US20210003047A1/en not_active Abandoned
- 2017-08-25 CN CN201780054466.1A patent/CN109690035B/en not_active Expired - Fee Related
- 2017-08-25 EP EP17768005.5A patent/EP3510260B1/en active Active
- 2017-08-25 JP JP2019511539A patent/JP6731542B2/en not_active Expired - Fee Related
Also Published As
Publication number | Publication date |
---|---|
US20210003047A1 (en) | 2021-01-07 |
JP2019528399A (en) | 2019-10-10 |
CN109690035A (en) | 2019-04-26 |
DE102016116776A1 (en) | 2018-03-08 |
JP6731542B2 (en) | 2020-07-29 |
WO2018046314A1 (en) | 2018-03-15 |
CN109690035B (en) | 2021-06-29 |
EP3510260A1 (en) | 2019-07-17 |
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