EP1131540B1 - Elektromagnetischer antrieb - Google Patents
Elektromagnetischer antrieb Download PDFInfo
- Publication number
- EP1131540B1 EP1131540B1 EP99958043A EP99958043A EP1131540B1 EP 1131540 B1 EP1131540 B1 EP 1131540B1 EP 99958043 A EP99958043 A EP 99958043A EP 99958043 A EP99958043 A EP 99958043A EP 1131540 B1 EP1131540 B1 EP 1131540B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- electromagnetic drive
- drive according
- armature
- lever
- valve
- 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.)
- Expired - Lifetime
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
- F01L9/20—Valve-gear or valve arrangements actuated non-mechanically by electric 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
- F01L2009/2105—Valve-gear or valve arrangements actuated non-mechanically by electric means actuated by solenoids comprising two or more coils
- F01L2009/2109—The armature being articulated perpendicularly to the coils axes
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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
- F01L2305/00—Valve arrangements comprising rollers
Definitions
- the invention relates to an electromagnetic drive with the features of the preamble of claim 1.
- the invention is based on the object, another Possibility to reduce the electrical losses the drive and the weight of the moving mass create.
- the claim 1 comprises drives according to said State of the art, but also known drives whose anchors performs a linear movement.
- the mentioned in claim 1 at least one electromagnet must have at least one active, i. Lifting work Pol have.
- the armature is driven by two electromagnets,
- the Drive can also be realized by means of a winding, the practically alternately working with different poles.
- the, or the electromagnets formed bipolar, but are also electromagnets conceivable with more than two poles, z. B. also pot magnets.
- the anchor is also an education possible in the only one of the poles is active, d. H. directly an attraction the armature thus does Hubarbeit, while the other pole causes only the inference about the anchor bearing. Combining these possibilities is a solution with an electromagnet and an active pole conceivable.
- the anchor mass is determined by the requirements after maximum driving force.
- the limiting Size here is the power density in the iron circle, in the Saturation occurs.
- the anchor dimensioning is determined through the entire yoke width and the yoke length.
- the entire yoke width is again determined by the Distance between the two thighs, according to the points of view dimensioned by magnetic leakage losses becomes. Overall, the entire yoke width should be as possible kept small.
- the anchor thickness corresponds about the width of the yoke leg. Now is an optimization the anchor weight thereby possible that the yoke width as narrow as possible is chosen as large as possible Jochtiefe. To minimize the weight comes here Ratio of Jochtiefe to the entire yoke width, which is exceptional for magnets.
- conventional Magnets are usually dimensioned so that about a quadratic ratio of width to length arises.
- a ratio chosen which is beyond of the factor 1.5, in particular greater than 2, preferably greater 3 is. It creates a relatively long and thinner Anchor, which must be stored accordingly.
- a long magnet By dimensioning a long magnet can be the magnet in the balance of force oversize, which is special Has advantages, e.g. for the opening magnet of Exhaust valve or the closing magnet of the intake valve, which have to overcome the gas forces.
- known system with anchor lever is the Torsion bar also used as a bearing point for the anchor lever.
- the torsion bar experiences an additional bending load.
- the Torsion bar can be located inside the tube and he is completely relieved of additional bending forces.
- the system In addition to the linear expansion of the valve and the cylinder head the system must be adjustable to a relatively large size Tolerances of the valve, the valve seat, the cylinder head and the housing of the drive.
- the housing about the axis of rotation of the anchor tube or the torsion bar or one more from from the armature axis of rotation is rotatable.
- the housing lies in a storage bed and is over a resilient counter bearing fixed. The adjustment takes place z. B. by two Nuts, where a mother represents the so-called anvil and adjusted for adjustment and the second Mother is used for detection.
- a further optimization consists in a design of the Magnetic circuit in the way that grain-oriented material can be used, which is inexpensive and only at power flux densities of around 1.9 Teslar comes to saturation. Normal magnetic material is included beginning saturation a power density of 1.4 Teslar on. This is a considerable increase in force per unit area possible, what smaller magnets and lower Anchor masses has the consequence.
- a long magnet with a large pole face has disadvantages in the inductance and thus the time behavior; therefore it is proposed to divide the yoke leg and two Use coils.
- the described design of the long Magnet also has the advantage that the width is relatively is low, which in turn is a relatively low Cylinder head allowed.
- a cost-driving factor is the Coil design.
- to insert the coil in the Magnetic circuit shared the yoke causing losses at the joints means.
- the coils are designed so that they are in the window between the two yoke legs can be introduced. Accordingly, the maximum width is measured.
- a special problem make the requirements small time constant for relatively large magnets with corresponding Inductance.
- a small time constant is required to position control, thus achieved is that the valve touches down at low speed.
- the magnetic circuit fast responds to the corresponding control signals. That will achieved in that, as mentioned above by the yoke subdivision several coils used and connected in parallel become. For example, four coils each may be provided be connected by parallel connection are. Since these coils compared to a coil the have the same time constant is less with four coils as a quarter of the time the necessary flow reached.
- the task of the magnets is, once the application the lifting work to cover the mechanical and the gas losses.
- the anchor in its end positions a closed or an open one Valve position can be achieved.
- the coil current clocked To the necessary holding energy to keep small is the coil current clocked. But it can also be a separate holding coil be used. By this holding coil with accordingly large number of turns, the holding energy, d. H. drastically reduce performance. around the heat dissipation
- the coils are relatively thin and by the advantages of the long magnet with relative provided with a large surface.
- filler pieces between yoke and bobbin for better heat dissipation be introduced.
- These patches can be laminated and be made of highly thermally conductive material, but it can also magnetic material to reduce iron losses be used. It's also a combination of both Possibilities given.
- the coils are preferably in The basic body embedded, you can also occasionally be poured there.
- a big problem is the mastery of the different ones Length expansions, the cylinder head and Experienced valve during heating. According to the state The technology often becomes hydraulic elements to the Game compensation used or magnets with large Air gap used. The hydraulic lash adjusters are very complicated and are in the game compensation limited, otherwise there is a risk that the drive is operated outside its middle position. It can, however also a Kochhubfeder after the above-mentioned State of the art can be used.
- a temperature compensation in the housing or in the Valve is the overstroke relatively low, z. B. on a few Tenths limited and affects a relatively small Ratio of the magnet to the valve axis not very strong on the holding power. This overrun spring has the advantage that when putting, d. H.
- the overtravel spring is the remaining Uncoupled mass.
- the over-stroke spring designed so that a majority of the mass fractions on sits small lever arm and thus not directly into the effective Mass arrives.
- the magnet can open smaller residual air gap to be driven.
- the residual air gap must be sized so that it occurs Valve wear and a temperature expansion ver-5 force, without the anchor rests fully. If the anchor Rise before the valve closes, would be no valve tightness given.
- valve it is also possible for the valve to have its own, decouple conventional valve pressure spring. in this connection may be the torsion spring and / or a tension or compression spring provide the necessary counterforce.
- an anchor lever 1 is connected to a pipe piece 2. It transfers the forces to operate the valve over a Matterhubfeder 3 on the bearing housing 1f with a bearing 4 on the valve stem 6.
- the valve stem has a flexible valve stem part 6a.
- the over-travel spring 3 requires a bias voltage; this can be over Setting piece, for example, an eccentric 5, set become.
- a second stop 5a limits the overstroke.
- the Function of the over-travel spring is in the aforementioned State of the art described in more detail.
- the magnet systems consist of a closing magnet 7 and an opening magnet 8.
- the opening magnet 8 is larger than the closing magnet trained, because he at the exhaust valve to open a generate larger lifting work to overcome the gas forces got to.
- the two magnetic yokes are integrally formed and made of grain-oriented material, which low iron losses at high flux densities allows. In zones with a change in direction of the Yoke, the yoke can spread to larger cross sections exhibit. In the yoke legs can with smaller Cross-section and the grain-oriented optimal Flow direction to be worked.
- the magnets each have two double coils 9 and 10. These double coils are per Yoke legs present twice when the yoke is divided is. The double coils are connected in parallel to one another to allow lower inductance and thus a to get faster time behavior. You can, however also operated as single coils or in series connection become.
- Fig. 4 shows two possible Jochnostien with a subdivided 7c and a closed leg 7b.
- the divided leg parts are from two double coils 13 and 13a.
- one or two power amplifiers be used.
- the coils are connected in parallel.
- this whole or partially shorted to decelerate the armature it is also conceivable that this whole or partially shorted to decelerate the armature.
- the magnets 7 and 8 are in Fig. 1 each over a Centering pin 12 fixed. This protrudes on both sides in two Housing plates into it, of which only the rear 13 is visible.
- the magnets are over relatively long bolts 14 braced, with the bolt between the yokes not be magnetic. The tension occurs after the magnetic yoke is adapted to the anchor, so that homogeneous Air gaps arise. Better heat dissipation for the solenoid coils is done by a corresponding Shape design of the plates. So a good on both sides Heat dissipation takes place, the coils of corresponding Elevations 15 of the base plates 13 and 13 a embedded.
- the entire drive is made on both sides in bearing shells stored from webs 20 of the actuator box 21.
- This The bridge is shown in dashed lines behind the magnet 8.
- the counter bearing is made by corresponding recesses formed in the housing 13.
- the resilient abutment 22 is with two screws 23 on Actuator box 21 attached. In this actuator box All drives of a cylinder bank are housed.
- the housing 21 is adjusted and fixed by two nuts.
- This arm is behind the valve stem 6, 6a and the centering of the valve fork 6b shown in dashed lines and shown enlarged in Fig. 1a.
- the extension arm 24 of the housing 13 is clamped by two nuts 25. to Adjustment these are twisted on the screw 26 about the stroke sensor 27, the correct adjustment of valve and Anchor position is ensured. For fixation is the upper nut countered.
- z. B two screws conceivable, in turn, the first screw forming the anvil for the housing and the second screw is used for detection.
- a torsion spring 16 is located in the bore of the anchor tube 2.
- the armature is shown in more detail in FIGS. 2a and 2b.
- FIGS. 2a and 2b show the anchor tube 2 cut shown. It is in Fig. 2a with three the anchor lever representing lever parts 1b to 1d connected. These three Lever parts include the drawn anchor 17.
- This anchor 17 is interrupted by a valve actuating unit 18, which consists essentially of the overstroke spring 3, the Bearing housing 1a and the bearing 4 consists.
- Anchor 17 and Valve operating unit 18 are with the lever parts welded.
- the tube 2 is for receiving the relatively large Anchoring forces on both sides of parts 19 and 19a of the housing plates 13 and 13 a according to FIG. 1 stored.
- rolling bearings are used and the bearings designed as an external warehouse. Through these bearings can the torsion bar 16 extending in the tube 2 (torsion spring) be completely relieved of bending loads. He is up one side (left) connected to the tube 2 and on the other side in the part 19a clamped. It occurs no axial play here.
- Fig. 2b shows a simplified embodiment of the anchor attachment.
- the two anchor parts 17 are here with only one Anchor lever 1e and the tube 2 welded.
- the welds are in the usual way by wedge-shaped, marked darkly drawn notches.
- the anchor lever corresponds to Fig. 5a.
- Fig. 3 shows the arrangement in perspective view.
- the anchor tube 2 is connected to the magnetically conductive Anchor levers connected 1b to 1d. Here are also the connection points to see that made by welding become. So that the magnetic flux of the two magnets is not from Anchor tube 2 is affected, this is preferably made non or weakly conductive, or non-magnetic material educated.
- the anchor tube 2 is in the bearings 19 and 19 a stored and receives the torsion bar 16.
- On the left half of the picture shows the long magnet 7, which is cut in the front part to the valve joint 4 to show.
- the magnet 7 shows a recess 20a for the interruption of the yoke for the introduction of each two double coils.
- This recess is also useful for the overstroke spring, which during the lifting movement in the yoke protrudes into it.
- the anchor is also denoted by 17 here.
- a magnetically conductive filler can be used instead of the full recess of both yoke legs.
- the armature is at a distance from the anchor pipe 2 drawn. However, this can also be directly on the anchor tube, as shown in Fig. 2a and 2b, abut.
- Fig.5 shows an alternative valve actuation.
- the valve is, as known from the prior art, via a Compressed spring 30 is pressed in the direction of the closed position.
- the torsion bar 16 acts against the compression spring.
- the spring forces are in balance.
- the power transmission takes place via a with a Roller bearing equipped roller 31, with the anchor lever 1c is connected. This one is easy by his thighs designed resilient to the impact forces when putting on to reduce the valve stem.
- To support the torsion bar 16 may additionally a on a relatively small lever arm hinged compression spring 32 are used.
- Fig. 5a shows instead of the roller a slider 33, which welded into the anchor and on the Gleitstel1e can be surface-coated. This part is also designed to reduce the impact load springy.
- Fig. 5b shows the side view.
- the compression spring pad be stored in a ball bearing 34.
- the upper valve stem portion 35 of low temperature expansion material z. B. Invarstahl and manufactured with the valve stem 36 crimped or welded.
- the hollow valve stem 36/37 filled with sodium is the difference between roller 31, and slider 33 and valve stem 36/37 between cold and warm valve much lower, so that the impact velocity of the roller 31 and thus the bearing load and the holding energy considerably smaller are.
- Fig. 5c includes a slider 39 which is rotatable a shaft 39a is mounted.
- This slider corresponds the conventional cam drive via pivot lever.
- This can also be stored in a spherical cap to fully adapt to the valve stem head.
- This Slider preferably has a slight clamping, so when putting on the valve opening a small Surface pressure arises.
- FIG. 6 differs from FIG. 5 only by one other design of the poles 40 of the opening magnet 41 and a matching design of the armature 42.
- the poles 40 are stepped, - here with two stages - trained.
- Of the Armature 42 points to the opening magnet facing Page a corresponding grading in such a way that the Anchor 42 in the opening of the stepped pole while maintaining small air gap fits in.
- For the good effect of Magnets 41 are the widths and depths 40a and 42a of FIG Pole 40 and anchor 42 essential. This is one Characteristic curve possible with the result that the lifting force the magnet for large air gaps considerably higher is.
- This formation of the magnet 41/42 is in storage of the anchor by means of the rolling bearing of particular Significance, because in the anchor relatively large lateral forces arise through tolerances.
- Fig. 7 shows a corresponding design of the poles the closing magnet 50 and 50a of an intake valve drive and the associated armature 52.
- the yokes and the armature of the opening and closing magnets an actuator, in particular the exhaust valve drive can with the above characteristic curve shaping be designed.
- Fig. 8 are different versions with parallel second rotary tube shown.
- Fig. 8a is the on the valve stem 6 acting lever with 1, the anchor 17, the bearing tube 2 and the torsion bar 16.
- It is a second torsion bar 16a with bearing tube 2a and a lever 1e provided, wherein the spring forces this torsion bar 16e via a connecting member 60 with the Forces of the torsion spring 16 are bundled.
- a valve spring 30 acts according to FIG. 5a on the valve stem and the armature movement is through a slider 33 transmitted to the valve.
- a link 60 transmits the forces of the second Torsion spring 16a to the lever. 1
- valve spring 30 through the torsion bar spring Replaced 16a, which via the connecting member 60 under the Valve stem head 61 engages.
- the torsion spring 16 acts via a slider on the valve stem.
- the connecting member is not rotatable on the lever 1c stored, but rigidly connected.
- the transmission link is a leaf spring 60a, which is also under the valve stem 61 engages.
- the second lever 1c is not on a pipe stored.
- a bearing part 63 on the one hand with the Pipe 2 of the torsion spring 16 and on the other hand with a bearing point the torsion bar 16a connected. The lateral forces will be supported at a bearing point 64.
- Fig. 9 shows an arrangement in which a main lever 70th by a secondary lever 71 of the two electromagnets 72 and 73 is pivoted.
- the levers 70 and 71 are with connected to the tube 74, inside which the torsion spring 75 is housed.
- the sub-lever 71 carries the anchor or represents the anchor. It is designed as a long magnet.
- valve stem 76 Similar to Fig. 1 via a at 77 on the main lever 70th fixed overstroke spring 78, which at the front end of Main lever 70 two stops 79 to the deflection limit assigned. Again, a bending zone 76a in Valve stem provided.
- This arrangement has an extremely low height, brings a better utilization of the magnet length, has one low weight and it is a decoupling of the overstroke spring given by the anchor lever.
- Fig. 10a and 10b are two electromagnetic drives shown in which the armature is not pivoted, but by the electromagnets up, or down is moved.
- the magnets 80 and 81 are double as long as in Fig. 10a and it is a corresponding one Anchor 82 is provided.
- the deep according to the invention trained yokes of electromagnets and accordingly the deeply trained anchor according to the invention is not must be integrally formed, but also two or more parts; the magnets can also be composed of several partial magnets be provided with one or more anchors can.
- a torsion bar is respectively provided for generating at least a part of the spring forces.
- the two spring forces, z. B. by coil springs produce.
- Fig. 5a then acts in the Valve axis arranged spring on the lever 1c from above one. As a result, a lower burden of lever storage reached.
- Fig. 11 shows various other possible configurations for the electromagnet (s) than the preceding one Characters.
- Fig. 11a shows two three-pole electromagnets 100 and 101, which face the armature 102.
- Figs. 11b and 11c show top views of the magnetic poles.
- the winding 103 can according to Fig. 11b or as a cup winding accordingly Fig. 11c may be formed.
- Fig. 11d are again shown two three-pole electromagnets, here a pole 104 is not active, so not for lifting contributes. It is also possible the electromagnets form bipolar and then only one active Pole to use.
- Fig. 11f is a combination of Fig. 11e shown using only one active pole.
- the magnetic circuit 110 of FIG. 11g corresponds to an E-core according to FIGS. 11a and 11b.
- the pole distance of the outer legs 111 and 112 is as possible small, to the width 113 a of the armature 113 to small hold.
- the middle leg 114 is made preferably of grain-oriented material and is through Positive locking, z. B. dovetail guide 117 in the yoke used or welded with this.
- the anchor thickness corresponds approximately to the E - magnet the thickness of the outer legs 115 and 116, which in turn is approx. 50% of the width of the middle leg 114 has. This amounts to the thickness of the armature 113 is only about 50% of the anchor thickness a U - magnet. Without special measures is the Pole distance at the E - magnet larger than at the U - magnet. By the measure of Polaufweitung this can Disadvantage be reduced. The effective weight saving is about 40% compared to this magnet shape to the U magnet.
- the E - core also offers four clamping screws 118 compared to three at the U core, what about the symmetry of the clamping forces is very cheap.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Electromagnets (AREA)
- Valve Device For Special Equipments (AREA)
- Magnetically Actuated Valves (AREA)
Description
- Fig. 1:
- eine Seitenansicht eines elektromagnetischen Antriebs;
- Fig. 1a:
- ein Detail der Fig. 1;
- Fig. 2a u. 2b:
- den Aufbau und die Lagerung des Ankers;
- Fig. 3
- den elektromagnetischen Antrieb der Fig.1 in perspektivischer Darstellung;
- Fig. 4:
- die möglichen Ausbildungen der Joche eines Elektromagneten;
- Fig.5, 5a u. 5b und 5c:
- alternative Antriebsmöglichkeiten für den Ventilschaft;
- Fig. 6 und 7:
- besondere Ankerausbildungen
- Fig. 8:
- verschiedene Anordnungen mit zwei Torsionsfedern;
- Fig. 9:
- einen anderen Aufbau eines elektromagnetischen Antriebs;
- Fig. 10a u. 10b:
- die Gegenüberstellung zweier Antriebe mit linearer Ankerbewegung einmal mit kurzen und einmal mit langem (tiefem) Anker und entsprechenden Elektromagneten.
- Fig. 11a bis 11g:
- verschiedene mögliche Ausbildungen des oder der Elektromagnete.
Fig. 10a | Fig. 10b | |
Mitteljochbreite | b | b/2 |
Schenkelbreite | b/2 | b/4 |
Wicklungsdicke | K | K |
Ankerhöhe | h = b/2 | b/4 |
Magnetbreite | L | 2L |
Ankerfläche | (2b + 2K)L | (b + 2K)2L |
Ankervolumen | (2b + 2K)L x b/2 | (b + 2K)2L x b/4= |
(b+2K)L x b/2 |
Claims (42)
- Elektromagnetischer Antrieb mit einem beweglich gelagerten, elektromagnetisch hin- und herbewegbaren Anker (17) der von wenigstens einem Elektromagneten (7, 8) in Endstellungen bewegt wird, wobei durch die Bewegung des Ankers (17) ein Element (6), insbesondere ein Ventil eines Verbrennungsmotors, angetrieben wird, wobei der wenigstens eine Elektromagnet Joche und wenigstens eine Wicklung aufweist und die Pole der Joche dem Anker gegenüberstehen,
dadurch gekennzeichnet, daß
das Verhältnis der Tiefe zur Breite der Joche der Elektromagnete (7, 8) und das entsprechende Verhältnis der Tiefe zur Breite des Ankers (17) größer als 1,5 insbesondere größer 2 und gegebenenfalls größer 3 ist, wobei die Tiefe und die Breite die senkrecht zur Flußrichtung im Luftspalt und senk-recht zueinander verlaufenden Ausdehnungen sind und die Breite durch die Schenkelbreiten der Joche und die Wickelfensterbreite bestimmt ist. - Elektromagnetischer Antrieb nach Anspruch 1, dadurch gekennzeichnet, daß auf den Anker (17) zwei entgegengesetzt gerichtete Federkräfte (16) einwirken, die ohne Wirkung von Erregerströmen den Anker (17) in eine Zwischenstellung stellen.
- Elektromagnetischer Antrieb nach Anspruch 2, dadurch gekennzeichnet, daß bei schwenkbar gelagertem Anker die beiden Federkräfte wenigstens teilweise durch eine Torsionsfeder (16) gebildet sind.
- Elektromagnetischer Antrieb nach Anspruch 2, dadurch gekennzeichnet, daß die beiden Federkräfte wenigstens teilweise durch Zug- und/oder Druckfedern gebildet sind.
- Elektromagnetischer Antrieb nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, daß eine Ventilfeder (30) vorgesehen ist, deren Federkraft auf den Ventilschaft (36) in Richtung Schließstellung des Ventils einwirkt.
- Elektromagnetischer Antrieb nach Anspruch 3, dadurch gekennzeichnet, daß bei schwenkbar gelagertem oder von einem schwenkbar gelagerten Hebel (1) getragenen Anker (17) der Anker (17) oder Hebel (1) mit einem schwenkbar gelagerten Rohr (2) oder rohrähnlichen Teil verbunden ist, daß dieses Rohr (2) oder Teil mit der wenigstens teilweise in dem Rohr oder Teil verlaufenden Torsionsfeder (16) verbunden ist und daß das Rohr (2) oder Teil außen gelagert ist.
- Elektromagnetischer Antrieb nach Anspruch 6 dadurch gekennzeichnet, daß der Anker (17) über wenigstens einen, vorzugsweise drei, parallel im Abstand zueinander angeordnete Teilhebel (1b bis 1d) mit dem Rohr verbunden ist.
- Elektromagnetischer Antrieb nach Anspruch 6 oder 7
dadurch gekennzeichnet, daß in den Hebel (1) eine Überhubfeder (3) integriert ist, über die die Ankerbewegung auf das bewegbare Element (6) übertragen wird und die für diese zu übertragende Bewegung steif ist und nur bei stärkerer Beanspruchung (Überhub) als Feder wirksam ist. - Elektromagnetischer Antrieb nach Anspruch 8, dadurch gekennzeichnet, daß der Teil des Hebels (1a), der das bewegbare Teil (6) antreibt, ein Gelenk (4) aufweist mit dem das bewegbare Element (6) verbunden ist.
- Elektromagnetischer Antrieb nach Anspruch 9, dadurch gekennzeichnet, daß das anzutreibende Element der Schaft (6) eines Ventils ist und daß der Schaft (6) des Ventils biegsam ausgebildet ist.
- Elektromagnetischer Antrieb nach Anspruch 5, dadurch gekennzeichnet, daß der Hebel (1, 1a) auf dem Schaft (36, 37) des Ventils lose aufliegt.
- Elektromagnetischer Antrieb nach Anspruch 11, dadurch gekennzeichnet, daß der Hebel (1, 1a) über eine Rolle (31) oder dergleichen auf den Ventilschaft einwirkt.
- Elektromagnetischer Antrieb nach Anspruch 11, dadurch gekennzeichnet, daß der Hebel (1, 1a) über ein Gleitstück (33) auf den Ventilschaft (36, 37) einwirkt.
- Elektromagnetischer Antrieb nach einem der Ansprüche 11 bis 13, dadurch gekennzeichnet, daß- der Hebel exzentrisch auf den Ventilschaft einwirkt.
- Elektromagnetischer Antrieb nach einem der Ansprüche 1 bis 14, dadurch gekennzeichnet, daß das Material des Magnetkerns( 7, 8) und/oder des Ankers (17) kornorientiert ist.
- Elektromagnetischer Antrieb nach Anspruch 15, dadurch gekennzeichnet, daß die Magnetkerne der Elektromagnete (7, 8) in Zonen (7a, 8a) mit Richtungsänderung der Joche einen größeren Querschnitt aufweisen.
- Elektromagnetischer Antrieb nach einem der Ansprüche 1 bis 16, dadurch gekennzeichnet, daß der Magnetkern der Magnete einstückig ausgebildet ist (Fig1).
- Elektromagnetischer Antrieb nach einem der Ansprüche 1 bis 17 dadurch gekennzeichnet, daß wenigstens an einem Joch eines Magneten zur Polfläche hin eine Unterteilung des Jochs in wenigstens zwei Jochteile (7b) vorgesehen ist (Fig.4) und daß auf diesen Jochteilen jeweils wenigstens eine Spule, vorzugsweise jedoch zwei Spulen (13, 13a) aufgebracht sind und daß diese Spulen (13, 13a) parallel geschaltet sind (Fig. 4).
- Elektromagnetischer Antrieb nach einem der Ansprüche 1 bis 18, dadurch gekennzeichnet, daß wenigstens auf dem Joch des Schließmagneten (7) zusätzlich eine Spule (13c) aufgebracht ist, die zum Halten des Ventils in der entsprechenden Stellung dient.
- Elektromagnetischer Antrieb nach einem der Ansprüche 1 bis 19, dadurch gekennzeichnet, daß die Magnetkerne der Elektromagnete (7, 8) zwischen zwei Platten (13) des Gehäuses eingespannt und ausgerichtet sind.
- Elektromagnetischer Antrieb nach Anspruch 20, dadurch gekennzeichnet, daß zur Ausrichtung der Joche zum Anker (17) die Magnete verdrehbar gelagert sind.
- Elektromagnetischer Antrieb nach Anspruch 20 oder 21, dadurch gekennzeichnet, daß die Spulen (9, 10, 11) mit den Platten (13) des Gehäuses über die Joche in wärmeleitender Verbindung stehen.
- Elektromagnetischer Antrieb nach Anspruch 22, dadurch gekennzeichnet, daß zur Wärmeabfuhr Füllstükke (15) zwischen den Spulen (9, 11, 12) und den Jochen vorgesehen sind.
- Elektromagnetischer Antrieb nach einem der Ansprüche 20 bis 23, dadurch gekennzeichnet, daß zur Wärmegabe Verrippungen vorgesehen sind.
- Elektromagnetischer Antrieb nach einem der Ansprüche 6 bis 24, dadurch gekennzeichnet, daß zur Justage der gesamte Antrieb um die Rohrachse oder um eine weiter ab vom Anker liegende Achse verdrehbar ist.
- Elektromagnetischer Antrieb nach einem der Ansprüche 3 oder 5 bis 25, dadurch gekennzeichnet, daß die Torsionsfeder (16) als Stab mit rechteckigem Querschnitt ausgebildet ist.
- Elektromagnetischer Antrieb nach einem der Ansprüche 1 bis 26, dadurch gekennzeichnet, daß im Querschnitt gesehen die Pole (40) wenigstens eines der Elektromagnete (7, 8) gestuft (40a) ausgebildet sind und daß der Anker (42) eine im Querschnitt in diese Stufung passende Gegenstufung (42a) aufweist.
- Elektromagnetischer Antrieb nach Anspruch 27, dadurch gekennzeichnet, daß der Öffnungsmagnet des Auslaßventils eine derartige Stufung aufweist.
- Elektromagnetischer Antrieb nach Anspruch 27, dadurch gekennzeichnet, daß der Schließmagnet des Einlaßventils eine derartige Stufung aufweist.
- Elektromagnetischer Antrieb nach Anspruch 13 oder 14, dadurch gekennzeichnet, daß das Gleitstück (39) am Hebel (1c) verdrehbar gelagert ist (Welle 39a) (Fig. 5c).
- Elektromagnetischer Antrieb nach Anspruch 30, dadurch gekennzeichnet, daß das Gleitstück mittels einer Kugel und einer Kugelkalotte am Hebel gelagert ist.
- Elektromagnetischer Antrieb nach einem der Ansprüche 6 bis 31, dadurch gekennzeichnet, daß ein Haupthebel (70) zur Betätigung des Elements (z. B. des Ventilschafts 76) und ein den Anker darstellender oder ihn tragender, um einen Winkel gegenüber dem Haupthebel (70) verdreht angeordneter und mit dem Haupthebel verbundenen Nebenhebel (71) vorgesehen ist.
- Elektromagnetischer Antrieb nach einem der Ansprüche 3 bis 32, dadurch gekennzeichnet, daß zur wenigstens teilweisen Erzeugung der Federkräfte zwei parallel geschaltete Torsionsfeder (16, 16a) vorgesehen sind
- Elektromagnetischer Antrieb nach Anspruch 33, dadurch gekennzeichnet, daß beide Torsionsfedern (16, 16a) über ein Lagerrohr (2,2a) mit einem Hebel (1, 1e) verbunden sind, wobei die über die beiden Hebel (1, 1e) übertragenen Kräfte auf den Ventilschaft einwirken.
- Elektromagnetischer Antrieb nach Anspruch 33, dadurch gekennzeichnet, daß der eine Hebel (1) über ein Lagerrohr (2) mit der Torsionsfeder (16) verbunden ist, und der andere Hebel (1c) direkt mit der Torsionsfeder (16a) verbunden ist.
- Elektromagnetischer Antrieb nach einem der Ansprüche 1 bis 35, dadurch gekennzeichnet, daß die Joche der Elektromagnete (7,8) und/oder der Anker (17) aus zwei oder mehreren Teilen zusammengesetzt sind.
- Elektromagnetischer Antrieb nach Anspruch 36, dadurch gekennzeichnet, daß mehrere Magnete hintereinander angeordnet sind, denen ein einteiliger oder mehrteiliger Anker gegenübersteht.
- Elektromagnetischer Antrieb nach einem der Ansprüche 3 bis 37, dadurch gekennzeichnet, daß der Krafteinwirkbereich des Ankers oder des den Anker tragenden Hebels (3) auf den Ventilschaft (6) außerhalb des Wirkbereichs des wenigsten einen Elektromagneten liegt.
- Elektromagnetischer Antrieb nach einem der Ansprüche 1 bis 38, dadurch gekennzeichnet, daß wenigstens einer der Magnete einen E - Kern (110) aufweist, wobei die Enden (111, 112) der äußeren Schenkel zum Mittelschenkel (114) hin verlaufen.
- Elektromagnetischer Antrieb nach Anspruch 39, dadurch gekennzeichnet, daß der Mittelschenkel (114) Träger der Wicklung (119) (vorzugsweise eine Bandspule) ist.
- Elektromagnetischer Antrieb nach Anspruch 39 oder 40, dadurch gekennzeichnet, daß der Mittelschenkel (114) durch Verschweißung und/oder durch eine schwalbenschwanzförmige Verbindung (117) mit dem Kern (115/116) verbunden ist.
- Elektromagnetischer Antrieb nach einem der Ansprüche 39 bis 41, dadurch gekennzeichnet, daß der Mittelschenkel (114) aus kornorientiertem Material besteht.
Applications Claiming Priority (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19854020 | 1998-11-16 | ||
DE19854020 | 1998-11-16 | ||
DE19900933 | 1999-01-13 | ||
DE19900933 | 1999-01-13 | ||
PCT/EP1999/008785 WO2000029723A1 (de) | 1998-11-16 | 1999-11-15 | Elektromagnetischer antrieb |
Publications (2)
Publication Number | Publication Date |
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EP1131540A1 EP1131540A1 (de) | 2001-09-12 |
EP1131540B1 true EP1131540B1 (de) | 2003-03-19 |
Family
ID=26050323
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99958043A Expired - Lifetime EP1131540B1 (de) | 1998-11-16 | 1999-11-15 | Elektromagnetischer antrieb |
Country Status (4)
Country | Link |
---|---|
US (1) | US6516758B1 (de) |
EP (1) | EP1131540B1 (de) |
DE (2) | DE19955079A1 (de) |
WO (1) | WO2000029723A1 (de) |
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DE10134708A1 (de) * | 2001-07-21 | 2003-02-06 | Heinz Leiber | Elektromagnet |
DE10140706A1 (de) * | 2001-08-18 | 2003-02-27 | Mahle Filtersysteme Gmbh | Hochgeschwindigkeitsstelleinrichtung |
JP2003077722A (ja) | 2001-08-31 | 2003-03-14 | Mitsubishi Electric Corp | 積層コアの形成方法および電磁式バルブ駆動装置 |
US6681731B2 (en) * | 2001-12-11 | 2004-01-27 | Visteon Global Technologies, Inc. | Variable valve mechanism for an engine |
DE10220788A1 (de) * | 2002-05-10 | 2003-11-20 | Daimler Chrysler Ag | Elektromagnetischer Aktuator mit einem Schwenkanker |
DE10224866A1 (de) * | 2002-06-05 | 2003-12-24 | Daimler Chrysler Ag | Elektromagnetischer Aktuator |
DE10251988A1 (de) * | 2002-11-08 | 2004-05-19 | Mahle Filtersysteme Gmbh | Stelleinrichtung und zugehöriges Montageverfahren |
DE20305920U1 (de) | 2003-04-11 | 2003-08-14 | TRW Deutschland GmbH, 30890 Barsinghausen | Vorrichtung zur nockenwellenlosen Betätigung eines Gaswechselventils |
DE10317644A1 (de) * | 2003-04-17 | 2004-11-04 | Fev Motorentechnik Gmbh | Elektromagnetischer Aktuator mit unsymmetrischer Magnetkreisauslegung zur Betätigung eines Gaswechselventils |
US6889636B2 (en) * | 2003-09-03 | 2005-05-10 | David S. W. Yang | Two-cycle engine |
DE102004050013B4 (de) * | 2003-10-14 | 2009-03-19 | Visteon Global Technologies Inc., Van Buren | Elektromechanischer Ventilauslöser |
US20050076866A1 (en) * | 2003-10-14 | 2005-04-14 | Hopper Mark L. | Electromechanical valve actuator |
US7152558B2 (en) * | 2003-10-14 | 2006-12-26 | Visteon Global Technologies, Inc. | Electromechanical valve actuator assembly |
US7089894B2 (en) | 2003-10-14 | 2006-08-15 | Visteon Global Technologies, Inc. | Electromechanical valve actuator assembly |
US7255073B2 (en) * | 2003-10-14 | 2007-08-14 | Visteon Global Technologies, Inc. | Electromechanical valve actuator beginning of stroke damper |
JP2006022776A (ja) * | 2004-07-09 | 2006-01-26 | Toyota Motor Corp | 電磁駆動弁 |
JP4155243B2 (ja) * | 2004-08-04 | 2008-09-24 | トヨタ自動車株式会社 | 電磁駆動弁 |
JP4196940B2 (ja) * | 2004-11-29 | 2008-12-17 | トヨタ自動車株式会社 | 電磁駆動弁 |
US7305942B2 (en) * | 2005-02-23 | 2007-12-11 | Visteon Global Technologies, Inc. | Electromechanical valve actuator |
US7305943B2 (en) | 2005-02-23 | 2007-12-11 | Visteon Global Technologies, Inc. | Electromagnet assembly for electromechanical valve actuators |
JP2006336737A (ja) * | 2005-06-01 | 2006-12-14 | Toyota Motor Corp | 電磁駆動弁 |
JP2006336525A (ja) * | 2005-06-01 | 2006-12-14 | Toyota Motor Corp | 電磁駆動弁 |
JP4475198B2 (ja) | 2005-07-27 | 2010-06-09 | トヨタ自動車株式会社 | 電磁駆動弁 |
CN1908386A (zh) | 2005-08-02 | 2007-02-07 | 丰田自动车株式会社 | 电磁驱动阀 |
JP2007040162A (ja) | 2005-08-02 | 2007-02-15 | Toyota Motor Corp | 電磁駆動弁 |
JP2007040238A (ja) * | 2005-08-04 | 2007-02-15 | Toyota Motor Corp | 電磁駆動弁 |
JP2007046497A (ja) * | 2005-08-08 | 2007-02-22 | Toyota Motor Corp | 電磁駆動弁 |
JP2007046503A (ja) * | 2005-08-08 | 2007-02-22 | Toyota Motor Corp | 電磁駆動弁 |
US7374147B2 (en) * | 2005-10-14 | 2008-05-20 | Et Us Holdings Llc | Valve assembly with overstroke device and associated method |
JP2008180140A (ja) * | 2007-01-24 | 2008-08-07 | Toyota Motor Corp | 電磁駆動弁 |
JP2008202427A (ja) * | 2007-02-16 | 2008-09-04 | Toyota Motor Corp | 電磁駆動弁 |
JP2008303783A (ja) * | 2007-06-07 | 2008-12-18 | Toyota Motor Corp | 電磁駆動弁 |
JP2008303782A (ja) * | 2007-06-07 | 2008-12-18 | Toyota Motor Corp | 電磁駆動弁 |
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CH651739A5 (de) * | 1981-09-09 | 1985-10-15 | Hans Fickler | Vorrichtung zum verstellen der winkellage einer schwenkbeweglichen stuetzflaeche. |
DE3437106A1 (de) * | 1983-10-14 | 1985-05-02 | Equipements Automobiles Marchal S.A., Issy-les-Moulineaux | Elektromagnetische stelleinrichtung |
DE3616540A1 (de) * | 1986-05-16 | 1987-11-19 | Porsche Ag | Vorrichtung zum betaetigen eines gaswechsel-tellerventils einer hubkolben-brennkraftmaschine |
US4900965A (en) * | 1988-09-28 | 1990-02-13 | Fisher Technology, Inc. | Lightweight high power electromotive device |
AT390763B (de) * | 1988-11-11 | 1990-06-25 | Steyr Daimler Puch Ag | Radaufhaengung fuer fahrzeuge |
US5161494A (en) * | 1992-01-15 | 1992-11-10 | Brown Jr John N | Electromagnetic valve actuator |
US5791442A (en) * | 1994-05-25 | 1998-08-11 | Orscheln Management Co. | Magnetic latch mechanism and method particularly for linear and rotatable brakes |
DE29604946U1 (de) * | 1996-03-16 | 1997-07-17 | FEV Motorentechnik GmbH & Co. KG, 52078 Aachen | Elektromagnetischer Aktuator für ein Gaswechselventil mit Ventilspielausgleich |
WO1998042953A1 (de) * | 1997-03-24 | 1998-10-01 | Lsp Innovative Automotive Systems Gmbh | Ventil für einen verbrennungsmotor |
WO1998042957A1 (de) * | 1997-03-24 | 1998-10-01 | Lsp Innovative Automotive Systems Gmbh | Elektromagnetischer antrieb |
DE29706491U1 (de) * | 1997-04-11 | 1998-08-06 | FEV Motorentechnik GmbH & Co. KG, 52078 Aachen | Elektromagnetischer Aktuator mit wirbelstromarmem Anker |
DE59806749D1 (de) * | 1997-07-22 | 2003-01-30 | Lsp Innovative Automotive Sys | Elektromagnetische stelleinrichtung |
-
1999
- 1999-11-15 DE DE19955079A patent/DE19955079A1/de not_active Withdrawn
- 1999-11-15 DE DE59904667T patent/DE59904667D1/de not_active Expired - Lifetime
- 1999-11-15 EP EP99958043A patent/EP1131540B1/de not_active Expired - Lifetime
- 1999-11-15 US US09/856,010 patent/US6516758B1/en not_active Expired - Lifetime
- 1999-11-15 WO PCT/EP1999/008785 patent/WO2000029723A1/de active IP Right Grant
Also Published As
Publication number | Publication date |
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EP1131540A1 (de) | 2001-09-12 |
DE59904667D1 (de) | 2003-04-24 |
US6516758B1 (en) | 2003-02-11 |
WO2000029723A1 (de) | 2000-05-25 |
DE19955079A1 (de) | 2000-05-25 |
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