EP2511526A1 - Reciprocating piston compressor with transport volume control - Google Patents
Reciprocating piston compressor with transport volume control Download PDFInfo
- Publication number
- EP2511526A1 EP2511526A1 EP12163073A EP12163073A EP2511526A1 EP 2511526 A1 EP2511526 A1 EP 2511526A1 EP 12163073 A EP12163073 A EP 12163073A EP 12163073 A EP12163073 A EP 12163073A EP 2511526 A1 EP2511526 A1 EP 2511526A1
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- EP
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- Prior art keywords
- actuator
- suction valve
- reciprocating compressor
- magnetic actuator
- compressor according
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/08—Actuation of distribution members
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
- F04B39/10—Adaptations or arrangements of distribution members
- F04B39/1053—Adaptations or arrangements of distribution members the members being Hoerbigen valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic means
Definitions
- the invention relates to a reciprocating compressor with flow control, arranged with an at least one of the automatic suction valves, electromagnetically operated in the power stroke Abhebegreifer for periodically controlled keeping open the corresponding suction valve over a certain crank angle range.
- off EP 694 693 A1 a toiletströmregelung for reciprocating compressor known, in which a hydraulic control cylinder which is periodically acted upon by a control member in the stroke with pressure medium and can be relieved, acts in the stroke direction on the closing member of the suction valve to be kept open.
- the hydraulically applied lifting force is thus abruptly reduced at a certain crank angle, whereby a safe and rapid closing of the suction valve is initiated.
- EP 1400692 A1 Similar flow rate controls are also known with pneumatic actuation, which has the advantage that the operating pressure can be derived directly from the reciprocating compressor itself. Because of the relative However, high compressibility of the compressed gas conditions must be met exactly to be defined for the volumes to be vented and ventilation times.
- the magnet should have a high degree of dynamics in order to be able to open and close quickly, which is rather unattainable by large electromagnets, since the stored energy and the effort required to build up or dissipate electricity are significantly greater for large magnets.
- thermal expansions and wear can lead to a displacement of the necessary working stroke range of the magnetic actuator.
- electromagnets have a very limited useful effective range of a few millimeters of lifting height, one would have to in order to apply even with a shift in the working range still correspondingly large actuation forces, also put on correspondingly enlarged magnets, which further reduces the dynamics of actuation. All this was previously contrary to an electromagnetic backflow control of the type mentioned above especially when higher compressor speeds are required and the circumstances of the use do not allow separate cooling in the range of necessarily large magnetic actuators.
- Object of the present invention is to improve an arrangement of the type mentioned so that the mentioned disadvantages of the related art are avoided and that especially with small electromagnets as an actuator of the operating device of the Abhebegreifers the required high actuation dynamics are provided with low heat loss can.
- the electromagnetic actuator has a separate actuator, and that the actuator for shifting as needed the Häshub Schemees of the magnetic actuator used relative to its attack on the suction valve in the optimal for the electromagnet used working area.
- the power losses can be reduced by about 50-70% compared to a simple, larger magnetic actuator, since the shifted amounts of energy are now much lower, which even allows the use of such a flow control without external cooling of the magnetic actuators and thus opens up many new applications of such regulations only where external cooling is not possible or permitted.
- a separate actuator is already off in electromagnetically actuated compressor valves in itself DE 684 110C known, but there is not used to adjust the working stroke range of the solenoid actuator used, but to change the allowable maximum valve lift, which may occur in the electromagnetic control. Depending on the operating conditions of the compressor so only the maximum possible opening of the valve is adjusted according to this document.
- the actuator acts on the magnetic actuator, including actuated Abhebegreifer and adjusted if necessary, their common position relative to the suction valve. So that the entire lifting device is adjusted relative to the sealing element of the corresponding suction valve, which allows a simple adjustment of the working stroke of the magnetic actuator relative to its attack on the suction valve.
- the actuator can also have a Gaznverstelltechnik for a switched between the magnetic actuator and Abhebegreifer transmission rod, which does not need to be adjusted relative to the suction valve the entire lift-off and the adjustment of the working stroke of the magnetic actuator only over an elongation or reduction the transmission rod takes place.
- the actuator may have in both variants mentioned an electric motor operated threaded spindle, which, as mentioned, only has to work relatively slowly and thus manages with small driving forces.
- the actuator can according to another embodiment of the invention also indirectly, preferably via levers, oblique ramps or the like, act on the adjustment of the working stroke of the magnetic actuator, which allows simple adaptation to the respective conditions and, for example, further miniaturization or, if necessary, from each other independent adjustments allowed from the start and end point of the stroke.
- the actuating device of the lift-off gripper has additional spring elements and / or fluid dampers, which, with appropriate matching or design, results in additional relief of the magnetic actuator.
- the energization of the magnetic actuator can be regulated in a further preferred embodiment of the invention as a function of the currently acting on the suction return flow.
- the level of remindströmkraft depends on the current piston speed of the compressor, which is known or can be determined, for example, via a crank angle sensor.
- the energization of the magnetic actuator to generate the necessary hold-open force can thus be adjusted accordingly, which further reduces the total power consumption and thus the heat loss.
- Fig. 1 shows a section through the range of a suction valve of a reciprocating compressor according to the invention with flow control
- Fig. 2 an alternative embodiment in the same representation.
- the actuator 3 has for this purpose as a drive to a magnetic actuator 5, the magnetic coil 6 cooperates with an armature plate 7 which is attached to the upper end of a transmission rod 8.
- the transmission rod 8 in turn is connected in its lower region with the Abhebergreifer 2 and guided in the longitudinal direction of a symbolically illustrated guide 9.
- the electromagnetic actuator 3 further has a separate actuator 10, which acts here for example via an electric motor-operated threaded spindle drive 11 and a displaceable oblique ramp 12 to the effective length of the switched between the magnetic actuator 5 and Abhebegreifer 2 transmission rod 8.
- a separate actuator 10 acts here for example via an electric motor-operated threaded spindle drive 11 and a displaceable oblique ramp 12 to the effective length of the switched between the magnetic actuator 5 and Abhebegreifer 2 transmission rod 8.
- an upper stop 13 is shown for example via a spring, not shown here or the like when not activated actuator 3 fixed retracted position of the Abhebegreifers 2, and a spring element 14 and a fluid damper 15, which are also used independently can and with appropriate design and vote allow relief of the electromagnetic actuator 3.
Abstract
Description
Die Erfindung betrifft einen Hubkolbenverdichter mit Fördermengenregelung, mit einem an zumindest einem der selbsttätigen Saugventile angeordneten, elektromagnetisch im Arbeitstakt betätigbaren Abhebegreifer zum periodisch gesteuerten Offenhalten des entsprechenden Saugventils über einen bestimmten Kurbelwinkelbereich.The invention relates to a reciprocating compressor with flow control, arranged with an at least one of the automatic suction valves, electromagnetically operated in the power stroke Abhebegreifer for periodically controlled keeping open the corresponding suction valve over a certain crank angle range.
Zur Fördermengenregelung von bevorzugt mit konstanter Drehzahl laufenden Hubkolbenverdichtern wird oft auf die sogenannte Rückströmregelung zurückgegriffen, bei der zumindest ein Saugventil je Zylinder über einen bestimmten Bereich des Verdichtungshubes offengehalten wird. Die Druckkräfte bzw. Strömungskräfte des über das offengehaltene Saugventil rückgeschobenen Gases können das Schließorgan des jeweiligen Saugventils erst nach Überwindung eines gewissen Teiles des Kolbenhubes schließen, da dieses Schließorgan von der anderen Seite her mit einer entsprechend der gewünschten Fördermengenreduzierung eingestellten Gegenkraft beaufschlagt wird. Je größer diese Gegenkraft ist, desto später schließt das jeweilige Saugventil im Verdichtungshub, womit die Fördermenge sinkt. Da bei zu groß eingestellter konstanter Gegenkraft das Saugventil irgendwann überhaupt nicht mehrschließt, muss der Regelbereich bei dieser Art der Verdichterregelung nach unten hin begrenzt werden, um einen zwischenzeitlichen Leerlauf des Verdichters mit allen damit verbundenen Problemen zu vermeiden. Bei diesen Fördermengenregelungen sind Ausführungen bekannt, bei denen die Belastungseinrichtung für das offenzuhaltende Saugventil einfach hydraulisch oder pneumatisch vorgespannt ist, wobei durch Variation des entsprechenden Vorspanndruckes Einfluss auf die Fördermenge genommen werden kann.For flow control of preferably running at constant speed reciprocating compressors is often resorted to the so-called backflow control in which at least one suction valve per cylinder is kept open over a certain range of Verdichtungshubes. The pressure forces or flow forces of the gas pushed back through the open suction valve can close the closing member of the respective suction valve only after overcoming a certain part of the piston stroke, since this closing member is acted upon from the other side with a counter-force set according to the desired flow reduction. The greater this counterforce, the later closes the respective suction valve in the compression stroke, whereby the flow rate decreases. Since the suction valve at some point does not close at all if the constant counteracting force is set too high, the control range in this type of compressor control must be limited downwards in order to avoid an intermediate idling of the compressor with all the associated problems. In these flow rate control arrangements are known in which the loading device for the suction valve to be kept open is simply biased hydraulically or pneumatically, which can be made by varying the corresponding biasing pressure influence on the flow rate.
Weiters ist beispielsweise aus
Bereits sehr lange sind weiters auch Hubkolbenverdichter mit einer elektromagnetisch betriebenen Rückströmregelung der eingangs genannten Art bekannt. So beispielsweise aus der
Aufgabe der vorliegenden Erfindung ist es, eine Anordnung der eingangs genannten Art so zu verbessern, dass die erwähnten Nachteile des diesbezüglichen Standes der Technik vermieden werden und dass insbesonders auch mit kleinen Elektromagneten als Aktor der Betätigungseinrichtung des Abhebegreifers die erforderliche hohe Betätigungsdynamik bei geringer Verlustwärme bereitgestellt werden kann.Object of the present invention is to improve an arrangement of the type mentioned so that the mentioned disadvantages of the related art are avoided and that especially with small electromagnets as an actuator of the operating device of the Abhebegreifers the required high actuation dynamics are provided with low heat loss can.
Diese Aufgabe wird gemäß der vorliegenden Erfindung dadurch gelöst, dass die elektromagnetische Betätigungseinrichtung einen separaten Stellantrieb aufweist, und dass der Stellantrieb zur bedarfsweisen Verschiebung des Arbeitshubbereiches des verwendeten Magnetaktors relativ zu seinem Angriff am Saugventil in den für den verwendeten Elektromagneten optimalen Arbeitsbereich dient.This object is achieved according to the present invention in that the electromagnetic actuator has a separate actuator, and that the actuator for shifting as needed the Arbeitsshubbereiches of the magnetic actuator used relative to its attack on the suction valve in the optimal for the electromagnet used working area.
Um den Magnetaktor für die kontrollierte Bewegung des Abhebegreifers über den für die Fördermengenregelung erforderlichen Hubbereich optimal nutzen zu können, wird dieser also mit einem separaten Stellantrieb kombiniert, der vergleichsweise langsam arbeiten kann, da er lediglich dazu dient, den eigentlichen Regelungs-Aktor immer in dem für den Elektromagneten optimalen Arbeitsbereich zu betreiben. Damit wird es nun einfach möglich, allen Anforderungen im Hinblick auf Kraft, Dynamik und Energieaufwand gerecht zu werden und den eigentlichen Magnetaktor der elektromagnetischen Betätigungseinrichtung des Abhebegreifers um zumindest einen Faktor 2 kleiner auszuführen. Dies führt zu einer nahezu doppelt hohen Dynamik der Regelung bei relativ geringer Verlustleistung. Die hohe Dynamik erlaubt in äußerst vorteilhafter Weise eine aktive Kontrolle der Öffnungs- und Schließbewegung der Abhebeeinrichtung während des Hubes des Magnetaktors. Die Verlustleistungen können um etwa 50 - 70 % gegenüber einem einfachen, größer ausgeführten Magnetaktor reduziert werden, da die verschobenen Energiemengen nun deutlich geringer sind, was sogar die Verwendung einer derartigen Fördermengenregelung ohne externe Kühlung der Magnetaktoren erlaubt und somit viele neue Anwendungen derartiger Regelungen erst erschließt, bei denen externe Kühlungen nicht möglich oder nicht zulässig sind.In order to use the magnetic actuator for the controlled movement of Abhebegreifers on the necessary for the flow control stroke range optimally, this is thus combined with a separate actuator that can work comparatively slowly because it only serves to the actual control actuator always in the to operate for the electromagnet optimal working range. Thus, it is now possible to meet all requirements in terms of power, dynamics and energy consumption and to make the actual magnetic actuator of the electromagnetic actuator of the lift-off gripper smaller by at least a factor of 2. This leads to a nearly twice the dynamics of the control with relatively low power loss. The high dynamics allows in an extremely advantageous manner an active control of the opening and closing movement of the lifting device during the stroke of the magnetic actuator. The power losses can be reduced by about 50-70% compared to a simple, larger magnetic actuator, since the shifted amounts of energy are now much lower, which even allows the use of such a flow control without external cooling of the magnetic actuators and thus opens up many new applications of such regulations only where external cooling is not possible or permitted.
Ein separater Stellantrieb ist bei elektromagnetisch betätigten Kompressorventilen an sich bereits aus
In vorteilhafter Ausgestaltung der Erfindung wirkt der Stellantrieb auf den Magnetaktor samt davon betätigtem Abhebegreifer ein und verstellt bedarfsweise deren gemeinsame Position relativ zum Saugventil. Damit wird also die gesamte Abhebeeinrichtung relativ zum Dichtelement des entsprechenden Saugventils verstellt, was eine einfache Justierung des Arbeitshubbereiches des Magnetaktors relativ zu seinem Angriff am Saugventil ermöglicht. Nach einer anderen bevorzugten Ausgestaltung der Erfindung kann der Stellantrieb aber auch eine Längenverstelleinheit für eine zwischen Magnetaktor und Abhebegreifer eingeschaltete Übertragungsstange aufweisen, womit nicht die gesamte Abhebeeinrichtung relativ zum Saugventil verstellt zu werden braucht und die Justierung des Arbeitshubbereiches des Magnetaktors lediglich über eine Längung bzw. Kürzung der Übertragungsstange erfolgt.In an advantageous embodiment of the invention, the actuator acts on the magnetic actuator, including actuated Abhebegreifer and adjusted if necessary, their common position relative to the suction valve. So that the entire lifting device is adjusted relative to the sealing element of the corresponding suction valve, which allows a simple adjustment of the working stroke of the magnetic actuator relative to its attack on the suction valve. According to another preferred embodiment of the invention, the actuator can also have a Längenverstelleinheit for a switched between the magnetic actuator and Abhebegreifer transmission rod, which does not need to be adjusted relative to the suction valve the entire lift-off and the adjustment of the working stroke of the magnetic actuator only over an elongation or reduction the transmission rod takes place.
Der Stellantrieb kann bei beiden genannten Varianten einen elektromotorisch betätigbaren Gewindespindel aufweisen, wobei dieser wie erwähnt nur relativ langsam arbeiten muss und damit auch mit kleinen Antriebskräften auskommt.The actuator may have in both variants mentioned an electric motor operated threaded spindle, which, as mentioned, only has to work relatively slowly and thus manages with small driving forces.
Der Stellantrieb kann gemäß einer anderen Ausgestaltung der Erfindung auch indirekt, vorzugsweise über Hebel, schiefe Rampen oder dergleichen, auf die Verstellung des Arbeitshubbereiches des Magnetaktors einwirken, was auf einfache Weise konstruktive Anpassungen an die jeweiligen Gegebenheiten ermöglicht und beispielsweise auch weitere Miniaturisierungen oder bedarfsweise auch voneinander unabhängige Verstellungen vom Anfangs- und Endpunkt des Hubes erlaubt.The actuator can according to another embodiment of the invention also indirectly, preferably via levers, oblique ramps or the like, act on the adjustment of the working stroke of the magnetic actuator, which allows simple adaptation to the respective conditions and, for example, further miniaturization or, if necessary, from each other independent adjustments allowed from the start and end point of the stroke.
In besonders bevorzugterweitererAusgestaltung ist vorgesehen, dass die Betätigungseinrichtung des Abhebegreifers zusätzliche Federelemente und-/oder Fluiddämpfer aufweist, was bei entsprechender Abstimmung bzw. Auslegung eine zusätzliche Entlastung des Magnetaktors ergibt.In a particularly preferred further embodiment, it is provided that the actuating device of the lift-off gripper has additional spring elements and / or fluid dampers, which, with appropriate matching or design, results in additional relief of the magnetic actuator.
Die Bestromung des Magnetaktors kann in weiters bevorzugter Ausgestaltung der Erfindung in Abhängigkeit von der aktuell am Saugventil angreifenden Rückströmkraft geregelt sein. Während des Offenhaltens des Saugventils hängt das Niveau der Rückströmkraft von der aktuellen Kolbengeschwindigkeit des Verdichters ab, die beispielsweise über einen Kurbelwinkelsensor bekannt oder ermittelbar ist. Die Bestromung des Magnetaktors zur Erzeugung der notwendigen Offenhaltekraft kann damit entsprechend angepasst werden, was die gesamte Leistungsaufnahme und damit auch die Verlustwärme weiter reduziert.The energization of the magnetic actuator can be regulated in a further preferred embodiment of the invention as a function of the currently acting on the suction return flow. During the keeping open of the suction valve, the level of Rückströmkraft depends on the current piston speed of the compressor, which is known or can be determined, for example, via a crank angle sensor. The energization of the magnetic actuator to generate the necessary hold-open force can thus be adjusted accordingly, which further reduces the total power consumption and thus the heat loss.
Die Erfindung wird im Folgenden noch anhand der in der Zeichnung schematisch dargestellten Ausführungsbeispiele näher erläutert.
Gemäß
Die elektromagnetische Betätigungseinrichtung 3 weist weiters einen separaten Stellantrieb 10 auf, der hier beispielsweise über einen elektromotorisch betätigbaren Gewindespindelantrieb 11 und eine verschiebbare schiefe Rampe 12 auf die effektive Länge der zwischen Magnetaktor 5 und Abhebegreifer 2 eingeschalteten Übertragungsstange 8 einwirkt. Auf diese Weise ist also die periodische elektromagnetische Betätigung des Abhebegreifers 2 im Arbeitstakt des Hubkolbenverdichters entkoppelt von der über den Stellantrieb 10 erfolgenden Einstellung des Arbeitshubbereiches des Magnetaktors 5.The
An der Oberseite der Ankerplatte 7 ist ein oberer Anschlag 13 für die beispielsweise über eine hier nicht dargestellte Feder oder dergleichen bei nicht aktivierter Betätigungseinrichtung 3 festgelegte eingefahrene Stellung des Abhebegreifers 2 dargestellt, sowie ein Federelement 14 und ein Fluiddämpfer 15, die auch unabhängig voneinander verwendet werden können und bei entsprechender Auslegung und Abstimmung eine Entlastung der elektromagnetischen Betätigungseinrichtung 3 ermöglichen.At the top of the anchor plate 7, an
Sobald der Magnetaktor 5 der Betätigungseinrichtung 3 über die elektrische Ansteuereinrichtung 16 bestromt und damit die Ankerplatte 7 (entgegen einer nicht dargestellten Befederung) angezogen wird, bewegt sich der Abhebegreifer 2 in der Darstellung nach unten und wirkt damit auf die ansonsten freie Beweglichkeit der Dichtelemente 4 ein. Diese können damit entgegen der sonst rein über die Druckverhältnisse vor und hinter dem Saugventil 1 erfolgende automatische Betätigung über einen steuerbaren Teil des Verdichtungshubes des Hubkolbenverdichters offengehalten werden, was in bekannter Weise eine Regelung der Fördermenge eines mit konstanter Drehzahl laufenden Verdichters über die sogenannte Rückströmregelung erlaubt. Über ein in
Bei der Ausführung nach
Claims (7)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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ATA531/2011A AT511238B1 (en) | 2011-04-14 | 2011-04-14 | PISTON COMPRESSORS WITH CONVEYOR RANGE CONTROL |
Publications (2)
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EP2511526A1 true EP2511526A1 (en) | 2012-10-17 |
EP2511526B1 EP2511526B1 (en) | 2019-08-21 |
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EP12163073.5A Active EP2511526B1 (en) | 2011-04-14 | 2012-04-04 | Reciprocating piston compressor with transport volume control |
Country Status (5)
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US (1) | US9027459B2 (en) |
EP (1) | EP2511526B1 (en) |
JP (1) | JP6112772B2 (en) |
CN (1) | CN102734134B (en) |
AT (1) | AT511238B1 (en) |
Families Citing this family (5)
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ITCO20110072A1 (en) * | 2011-12-22 | 2013-06-23 | Nuovo Pignone Spa | VALVES WITH VALVE VALVE END CONNECTED TO THE ACTUAL COUNTERS AND RELATIVE METHODS |
AT514580B1 (en) * | 2013-11-21 | 2015-02-15 | Hoerbiger Kompressortech Hold | Lifting gripper for a valve element of a compressor valve |
ITUB20150797A1 (en) | 2015-05-22 | 2016-11-22 | Nuovo Pignone Tecnologie Srl | VALVE FOR AN ALTERNATIVE COMPRESSOR |
AT525119B1 (en) * | 2021-05-10 | 2023-04-15 | Hoerbiger Wien Gmbh | Reciprocating compressor with variable capacity control |
CN114135475B (en) * | 2021-11-30 | 2024-01-30 | 中船动力研究院有限公司 | Position control device and diesel engine fuel pump speed regulation system |
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DE849739C (en) | 1942-03-17 | 1952-09-18 | Linde Eismasch Ag | Electromagnetically controlled plate valve |
US4515343A (en) * | 1983-03-28 | 1985-05-07 | Fev Forschungsgesellschaft fur Energietechnik und ver Brennungsmotoren mbH | Arrangement for electromagnetically operated actuators |
EP0694693A1 (en) | 1994-07-29 | 1996-01-31 | Hoerbiger Ventilwerke Aktiengesellschaft | Method and device for valve control |
EP1400692A1 (en) | 2002-09-19 | 2004-03-24 | HOERBIGER KOMPRESSORTECHNIK SERVICES GmbH | Volumetric piston compressor and method to continuously adjust its displacement |
US20070272890A1 (en) * | 2006-05-26 | 2007-11-29 | Herbert Kopecek | Electromagnetic actuators |
Also Published As
Publication number | Publication date |
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AT511238A1 (en) | 2012-10-15 |
AT511238B1 (en) | 2013-03-15 |
CN102734134A (en) | 2012-10-17 |
EP2511526B1 (en) | 2019-08-21 |
US20120260796A1 (en) | 2012-10-18 |
JP2012225345A (en) | 2012-11-15 |
US9027459B2 (en) | 2015-05-12 |
CN102734134B (en) | 2015-12-16 |
JP6112772B2 (en) | 2017-04-12 |
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