EP0279265B1 - Valve device with a hydraulic transmission and variable characteristic by means of sliding valve control - Google Patents

Valve device with a hydraulic transmission and variable characteristic by means of sliding valve control Download PDF

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Publication number
EP0279265B1
EP0279265B1 EP88101403A EP88101403A EP0279265B1 EP 0279265 B1 EP0279265 B1 EP 0279265B1 EP 88101403 A EP88101403 A EP 88101403A EP 88101403 A EP88101403 A EP 88101403A EP 0279265 B1 EP0279265 B1 EP 0279265B1
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EP
European Patent Office
Prior art keywords
valve
auxiliary shaft
annular grooves
valve drive
hydraulic fluid
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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EP88101403A
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German (de)
French (fr)
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EP0279265A1 (en
Inventor
Gabriel Tittizer
Ewald Dipl.-Ing. Junghans
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Interatom Internationale Atomreaktorbau GmbH
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Interatom Internationale Atomreaktorbau GmbH
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Priority to AT88101403T priority Critical patent/ATE59212T1/en
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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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • 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
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • 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
    • F01L2301/02—Using ceramic materials

Definitions

  • the present invention relates to a valve train according to the preamble of claim 1.
  • the applicant has described in EP-A-0 191 376 a valve train with hydraulic transmission, by means of which a relatively small control movement can be converted into a relatively large valve lift, which cannot be achieved with the usual camshafts due to the limitation of the steepness of the cams .
  • This enabled the valve characteristics to be changed from the previously more or less sinusoidal shape to an approximate rectangular shape, which appears to be beneficial for improving both the economy and the pollutant behavior of internal combustion engines.
  • a fixed valve characteristic is also possible with this valve train, which is designed with regard to the most frequently occurring operating state of the machine and which is not necessarily optimal in other operating states.
  • a valve train with a housing, links and a displaceable part, the hydraulic connections consisting of radial and axially extending channels and annular grooves, and the links being rotatable in order to set the valve opening time is known from FR-A 2 428 144.
  • this device is dependent on a constant temperature of the hydraulic fluid during operation, for which purpose a particular cooling of the same is provided.
  • their functioning is based on the assumption that the hydraulic fluid has a certain compressibility as a result of an inevitably present content of emulsified air bubbles. Even though this assumption may be correct in principle, the quantifiability and reproducibility of the air content over the operating time seems very questionable.
  • the object of the present invention is a Ven tiltrieb of the type described, in which the valve characteristic can be changed according to the respective operating requirements without the aforementioned disadvantages.
  • the cross-section available for the passage of the hydraulic fluid and thus the valve lift can be regulated by rotating the scenes. If the auxiliary shaft rotates, driven from the crankshaft (usually at half the speed), the supply of hydraulic fluid to the respective valve is interrupted at regular intervals; the duration of the interruption and thus also the valve opening time are determined by the circumferential extent of the fifth or sixth channels. It is expedient not only to apply hydraulic fluid to the valves in one direction of movement (as stated in the last-mentioned publication), but to perform the return movement by means of a spring, but to perform the actuating movement of the valve by the mutual action of a double piston. Accordingly, two hydraulic lines must be provided for each valve.
  • the embodiment of the invention proposed in claim 2 allows the valve opening and closing times of the intake and exhaust valves to be controlled in opposite directions, so that an alternately large overlap of the two valve characteristics can be achieved.
  • a particularly advantageous constructive solution to the mutual rotatability of the scenes is specified in claim 3.
  • the embodiment of the invention specified in claim 4 allows the height of the valve stroke to be changed, since a change in the time during which hydraulic fluid can reach the respective valve also changes the extent of the movement of the piston displacing the valve.
  • the further embodiment according to claim 5 allows said axial displaceability of the auxiliary shaft, without the elements required to drive it having to be displaced at the same time.
  • a plurality of valves 2 are arranged in an engine block 1, only one of which is shown here.
  • the valve 2 is actuated by displacing a piston 3 made of a ferritic material, which slides in a control cylinder 4 attached to the engine block 1 and is alternately acted upon by hydraulic fluid from one side or the other.
  • the respective position of the piston 3 is detected by a contactless displacement sensor 32, which consists of a housing 34 inserted into the top of the control cylinder 4 and made of a non-magnetic, for example austenitic material, in which an electromagnet composed of a magnetic core 35 and a coil 37 passes through Insulation 38 is housed separately, the coil 37 being supplied by supply lines 36.
  • a first or second supply line 7, 8 emanate from an only indicated oil pump 6 with a variable mass flow for the separate actuation of the inlet and outlet valves and open inside a housing 9 in a first and second circumferential annular groove 10, 11.
  • a first or second link 12, 13 is rotatably arranged in the interior of the housing 9 and in this in turn an auxiliary shaft consisting of two parts 14, 15 which can be pushed into one another.
  • the first or second link 12, 13 are provided with radially extending third or fourth channels 17, 18, through which the hydraulic fluid which has reached the first or second annular groove 10, 11 can pass. From here, the hydraulic fluid flows into a fifth or sixth annular groove 19, 20 in the auxiliary shaft 14.
  • a fifth or sixth channel 21, 22 extend axially to the cross-sectional plane of a seventh or eighth channel 23, 24 also extend radially through the scenes 12, 13 and open into a third or fourth annular groove 25, 26, from which a first and a second channel 27, 28 leads to the respective control cylinder 4 from each valve.
  • the circumference of the mouth of the fifth or sixth channel 21, 22 on the surface of the auxiliary shaft 14 determines the duration of the action of the associated piston 3 with hydraulic fluid and thus its displacement path. This in turn is equal to the valve lift achieved.
  • the fifth and sixth annular grooves 19, 20 are divided into the same number of chambers by webs 29 extending in the axial direction as valves are to be actuated.
  • the scenes 12, 13 are provided on their opposite sides with sprockets 30.
  • a toothing gear 31, which can be rotated about a transverse axis, engages in its toothing, so that when it rotates, the links 12, 13 rotate relative to one another. The timing of the valve timing of the intake and exhaust valve can be
  • FIG. 1 This property is illustrated by Figures 2 and 3.
  • curve a represents the previously customary, approximately sinusoidal control characteristic of the valves, as can be achieved with the conventional cam control.
  • b represents a more rectangular control curve that can be achieved with the device proposed here.
  • the large valve lift shown in this way results when the displaceable part 14 of the auxiliary shaft is displaced (to the right in FIG. 1) in such a way that a part of the mouths of the fifth and sixth channels 21, 22, which extends over a larger part of the circumference, is opposite the seventh and eighth channels 23, 24 come to rest. Due to the longer period of overlap of these openings per revolution of the auxiliary shaft 14, a greater amount of hydraulic fluid passes through and causes a greater displacement path of the piston 3.
  • the valve curves are both one An inlet valve and an outlet valve bi or b 3 are shown, the valve characteristics overlapping over a distance xi, ie both valves are open simultaneously for the corresponding period.
  • it may be more convenient to extend the simultaneous opening period which means that the area of overlap is extended to distance x 2 .
  • the curve b i to b 2 and the curve bs to b 4 are shifted symmetrically to one another, which is achieved by rotating the adjusting gear 31 and thus the links 12, 13 relative to one another.
  • the rotary slide valve shown in FIG. 1 is designated 40 in the schematic illustration in FIG.
  • the operation of the internal combustion engine is e.g. B. monitored by three sensors and - converter, namely by a tachometer 41, a torque meter 42 and a thermometer 43.
  • the measured values are fed to a process computer and pulse generator 44, which calculates a setpoint value for the respective valve position and inputs it into a comparator 45 .
  • the setpoint is compared with an actual value of the current valve position, amplified in an amplifier 49, as supplied by the contactless displacement sensor 32, with the aid of which the position of the associated piston 3 is determined on each control cylinder 4.
  • the comparator 45 sends control signals to a first stepper motor 46 with which the movable part 14 of the auxiliary shaft is displaced and to a second stepper motor 47 that the actuating gear 31 is actuated.
  • a first stepper motor 46 with which the movable part 14 of the auxiliary shaft is displaced
  • a second stepper motor 47 that the actuating gear 31 is actuated.
  • one or the other of the stepper motors 46, 47 or both can be actuated simultaneously, in the latter case there being a superimposition of the changes in the valve characteristics shown in FIGS. 2 and 3.
  • the hydraulic fluid displaced from the cylinder 4 flows via a return line 33 into a reservoir 48 from which the pump 6 draws in.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Control Of Fluid Gearings (AREA)
  • Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)
  • Mechanically-Actuated Valves (AREA)

Abstract

A valve drive assembly for an internal combustion engine includes a given number of pistons, the given number of inlet or outlet valves each being connected to a piston and independently movable by hydraulic fluid acting upon the pistons, at least one rotatable link disposed in a housing for aiding in shutting off and releasing a supply of hydraulic fluid to the pistons at regular intervals, and an auxiliary shaft supported in the rotatable link and driven by a crankshaft. First and second supply lines for hydraulic fluid lead from a hydraulic pump to first and second annular grooves formed in the housing. The rotatable link has the given number of radial third and fourth conduits formed therein communicating with the first and second annular grooves. The auxiliary shaft has fifth and sixth annular grooves formed therein communicating with the third and fourth conduits. Fifth and sixth conduits communicate with the fifth and sixth annular grooves. Seventh and eighth conduits communicate with the fifth and sixth conduits. Third and fourth annular grooves lead from the seventh and eighth conduits to first and second conduits which lead to the pistons. Ribs divide the fifth and sixth annular grooves into the given number of sectors.

Description

Die vorliegende Erfindung betrifft einen Ventiltrieb nach dem Oberbegriff des 1. Anspruchs. Die Anmelderin hat in der EP-A-0 191 376 einen Ventiltrieb mit hydraulischer Übersetzung beschrieben, mittels dessen eine verhältnismäßig kleine Steuerbewegung in einen verhältnismäßig großen Ventilhub umgesetzt werden kann, wie er mit den üblichen Nockenwellen wegen der Begrenzung der Flankensteilheit der Nocken nicht realisierbar ist. Damit gelang eine Änderung der Ventilcharakteristik von der bislang üblichen, mehr oder weniger sinusähnlichen Form hin zu einer angenäherten Rechteckform, wie sie für die Verbesserung sowohl der Wirtschaftlichkeit als auch des Schadstoffverhaltens von Verbrennungskraftmaschinen günstig erscheint. Immerhin ist auch bei diesem Ventiltrieb nur eine feste Ventilcharakteristik möglich, die im Hinblick auf den am häufigsten vorkommenden Betriebszustand der Maschine ausgelegt wird und bei anderen Betriebszuständen notwendigerweise nicht optimal ist. Dazu wäre es erforderlich, Ausmaß und Dauer des Ventilhubs der einzelnen Ventile und unter Umständen auch die Länge des Zeitraumes zu variieren, in dem sowohl das Ein- als auch das Auslaßventil gleichzeitig geöffnet sind, d. h. das Maß der Überschneidung der beiden Ventilcharakteristiken zu ändern. Zu diesem Zweck ist in der FR-A-2 480 853 eine hydraulische Ventilsteuerung vorgeschlagen worden, bei der aus einer zentralen Druckquelle beaufschlagte, hydraulisch betätigte Ventile dadurch in ihrer Charakteristik verändert werden, daß durch zwei gegeneinander verdrehbare Kulissen ein in Abhängigkeit von verschiedenen Betriebsparametern der Maschine variierbarer Durchgang für das Hydraulikfluid geschaffen wird. Wegen der bei den verschiedenen Betriebstemperaturen der Maschine unterschiedlichen Viskosität des Hydraulikfluids läßt sich mit einer Einrichtung dieser Art jedoch keine exakte Ventilsteuerung erreichen.The present invention relates to a valve train according to the preamble of claim 1. The applicant has described in EP-A-0 191 376 a valve train with hydraulic transmission, by means of which a relatively small control movement can be converted into a relatively large valve lift, which cannot be achieved with the usual camshafts due to the limitation of the steepness of the cams . This enabled the valve characteristics to be changed from the previously more or less sinusoidal shape to an approximate rectangular shape, which appears to be beneficial for improving both the economy and the pollutant behavior of internal combustion engines. After all, only a fixed valve characteristic is also possible with this valve train, which is designed with regard to the most frequently occurring operating state of the machine and which is not necessarily optimal in other operating states. To do this, it would be necessary to vary the extent and duration of the valve lift of the individual valves and, under certain circumstances, also the length of the period in which both the inlet and the outlet valve are open at the same time, i. H. to change the degree of overlap of the two valve characteristics. For this purpose, a hydraulic valve control has been proposed in FR-A-2 480 853, in which the characteristics of hydraulically actuated valves which are acted upon from a central pressure source are changed in such a way that, depending on different operating parameters, the two are rotated against one another Machine variable passage for the hydraulic fluid is created. Because of the different viscosity of the hydraulic fluid at the different operating temperatures of the machine, an exact valve control cannot be achieved with a device of this type.

Ein Ventiltrieb mit Gehäuse, Kulissen und einem verschieblichen Teil, wobei die hydraulischen Verbindungen aus radialen und sich axial erstreckenden Kanälen und Ringnuten bestehen, und die Kulissen drehbar sind um die Ventilöffnungszeit einzustellen, ist aus der FR-A 2 428 144 bekannt. Diese Vorrichtung ist jedoch auf eine während des Betriebes gleichbleibende Temperatur des Hydraulikfluides angewiesen, wofür eine besondere Kühlung desselben vorgesehen wird. Ferner beruht ihr Funktionieren auf der Annahme, daß das Hydraulikfluid in Folge eines unvermeidlicherweise vorhandenen Gehaltes an emulgierten Luftbläschen eine gewisse Kompressibilität aufweist. Auch wenn diese Annahme im Prinzip zutreffend sein mag, so erscheint doch eine Quantifizierbarkeit und Reproduzierbarkeit des Luftgehaltes über die Betriebszeit hinweg sehr fraglich.A valve train with a housing, links and a displaceable part, the hydraulic connections consisting of radial and axially extending channels and annular grooves, and the links being rotatable in order to set the valve opening time, is known from FR-A 2 428 144. However, this device is dependent on a constant temperature of the hydraulic fluid during operation, for which purpose a particular cooling of the same is provided. Furthermore, their functioning is based on the assumption that the hydraulic fluid has a certain compressibility as a result of an inevitably present content of emulsified air bubbles. Even though this assumption may be correct in principle, the quantifiability and reproducibility of the air content over the operating time seems very questionable.

Aufgabe der vorliegenden Erfindung ist ein Ven tiltrieb der beschriebenen Art, bei dem die Ventilcharakteristik entsprechend den jeweiligen Betriebserfordernissen geändert werden kann, ohne daß sich die vorerwähnten Nachteile ergeben.The object of the present invention is a Ven tiltrieb of the type described, in which the valve characteristic can be changed according to the respective operating requirements without the aforementioned disadvantages.

Die Lösung dieser Aufgabe erfolgt durch die im kennzeichnenden Teil des 1. Anspruchs angegebenen Mittel. Durch die Drehung der Kulissen kann der für den Durchtritt des Hydraulikfluids zur Verfügung stehende Querschnitt reguliert werden und damit der Ventilhub. Dreht sich, von der Kurbelwelle aus (üblicherweise mit der halben Drehzahl) angetrieben die Hilfswelle, so wird in regelmäßigen Abständen die Zufuhr von Hydraulikfluid zu dem jeweiligen Ventil unterbrochen; die Dauer der Unterbrechung und damit auch die der Ventilöffnungszeit werden durch die Umfangsausdehnung der fünften bzw. sechsten Kanäle bestimmt. Dabei ist es zweckmäßig, die Ventile nicht nur (wie in der zuletzt genannten Druckschrift angegeben) in ihrer einen Bewegungsrichtung mit Hydraulikfluid zu beaufschlagen, die Rückstellbewegung jedoch durch eine Feder vorzunehmen, sondern die Stellbewegung des Ventils durch die wechselseitige Beaufschlagung eines Doppelkolbens vorzunehmen. Entsprechend sind für jedes Ventil zwei Hydraulikleitungen vorzusehen.This object is achieved by the means specified in the characterizing part of claim 1. The cross-section available for the passage of the hydraulic fluid and thus the valve lift can be regulated by rotating the scenes. If the auxiliary shaft rotates, driven from the crankshaft (usually at half the speed), the supply of hydraulic fluid to the respective valve is interrupted at regular intervals; the duration of the interruption and thus also the valve opening time are determined by the circumferential extent of the fifth or sixth channels. It is expedient not only to apply hydraulic fluid to the valves in one direction of movement (as stated in the last-mentioned publication), but to perform the return movement by means of a spring, but to perform the actuating movement of the valve by the mutual action of a double piston. Accordingly, two hydraulic lines must be provided for each valve.

Die im 2. Anspruch vorgeschlagene Ausgestaltung der Erfindung gestattet es, die Ventilöffnungs-und -schließzeiten der Ein- und Auslaßventile entgegengesetzt zu steuern, so daß eine wechselnd große Überlappung der beiden Ventilcharakteristiken erreicht werden kann. Eine konstruktiv besonders günstige Lösung der gegenseitigen Verdrehbarkeit der Kulissen wird im 3. Anspruch angegeben.The embodiment of the invention proposed in claim 2 allows the valve opening and closing times of the intake and exhaust valves to be controlled in opposite directions, so that an alternately large overlap of the two valve characteristics can be achieved. A particularly advantageous constructive solution to the mutual rotatability of the scenes is specified in claim 3.

Die im 4. Anspruch angegebene Ausgestaltung der Erfindung gestattet es, die Höhe des Ventilhubes zu verändern, da bei einer Änderung in der Zeit, während derer Hydraulikfluid zu dem jeweiligen Ventil gelangen kann, auch das Ausmaß der Bewegung des das Ventil verschiebenden Kolbens verändert wird. Die weitere Ausgestaltung nach dem 5. Anspruch gestattet die besagte axiale Verschiebbarkeit der Hilfswelle, ohne daß gleichzeitig die zu deren Antrieb erforderlichen Elemente auch verschoben werden müßten.The embodiment of the invention specified in claim 4 allows the height of the valve stroke to be changed, since a change in the time during which hydraulic fluid can reach the respective valve also changes the extent of the movement of the piston displacing the valve. The further embodiment according to claim 5 allows said axial displaceability of the auxiliary shaft, without the elements required to drive it having to be displaced at the same time.

Besonders beim Betrieb in Kraftfahrzeugen ändern sich die Betriebsparameter von Verbrennungsmaschinen ständig, so daß eine selbsttätige Anpassung der Ventilcharakteristik an diese Änderungen wünschenswert erscheint. Diese erfolgt bei dem erfindungsgemäßen Ventiltrieb durch die im 6. Anspruch vorgeschlagenen Maßnahmen. Da die Maschine ständig mit optimaler Ventileinstellung betrieben wird, werden sowohl günstige Verbrauchswerte erreicht als auch das Auftreten schädlicher Verbrennungsrückstände minimiert. Der 7. Anspruch gibt die konstruktiven Mittel an, mittels derer eine derartige selbsttätige Anpassung am günstigsten erfolgen kann.Particularly when operating in motor vehicles, the operating parameters of internal combustion engines are constantly changing, so that an automatic adaptation of the valve characteristics to these changes seems desirable. This takes place in the valve train according to the invention by the measures proposed in claim 6. Since the machine is constantly operated with optimal valve setting, both favorable consumption values are achieved and the occurrence of harmful combustion residues is minimized. The 7th claim specifies the constructive means by means of which such an automatic adjustment can take place at the cheapest.

Im 8. Anspruch sind die Parameter aufgeführt, in deren Abhängigkeit ein Ventiltrieb nach der vorliegenden Erfindung am vorteilhaftesten betrieben wird.In the 8th claim, the parameters are listed, depending on which a valve train according to the present invention is most advantageously operated.

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt, und zwar zeigt

  • Figur 1 einen Längsaxialschnitt,
  • Figur 2 und Figur 3 typischerweise erreichbare Ventilcharakteristiken und
  • Figur 4 schematisch die zur Steuerung des Ventiltriebes vorgeschlagene Schaltung.
An embodiment of the invention is shown in the drawing, namely shows
  • FIG. 1 shows a longitudinal axial section,
  • Figure 2 and Figure 3 typically achievable valve characteristics and
  • Figure 4 schematically shows the circuit proposed for controlling the valve train.

In einem Motorblock 1 sind eine Vielzahl von Ventilen 2 angeordnet, von denen hier nur eines gezeigt ist. Betätigt wird das Ventil 2 durch das Verschieben eines aus einem ferritischen Material hergestellten Kolbens 3, der in einem am Motorblock 1 befestigten Steuerzylinder 4 gleitet und wechselseitig von der einen oder anderen Seite mit Hydraulikfluid beaufschlagt wird. Die jeweilige Lage des Kolbens 3 wird durch einen kontaktlosen Wegaufnehmer 32 erfaßt, der aus einem oben in den Steuerzylinder 4 eingesetzten, aus einem unmagnetischen, beispielsweise austenitischen Material gefertigten Gehäuse 34 besteht, in dem ein aus einem Magnetkern 35 und einer Spule 37 zusammengesetzter Elektromagnet durch Isolierung 38 getrennt untergebracht ist, wobei die Spule 37 durch Zuleitungen 36 versorgt wird. Das sich bei Obenlage des Kolbens 3 über die Wandung des Steuerzylinders 4 schließende Magnetfeld bricht zusammen, wenn sich der Kolben 3 abwärts bewegt. Eine Feder 5 dient anders als bei herkömmlichen Ventilen nicht der Rückstellung derselben sondern lediglich dem Spielausgleich. Von einer nur angedeuteten Ölpumpe 6 mit variablem Massenstrom gehen für die getrennte Betätigung der Einlaß- bzw. Auslaßventile eine erste bzw. zweite Zufuhrleitung 7, 8 aus und münden im Inneren eines Gehäuses 9 in einer ersten bzw. zweiten umlaufenden Ringnut 10,11. Drehbar im Inneren des Gehäuses 9 sind eine erste bzw. zweite Kulisse 12, 13 angeordnet und in diesen wiederum eine aus zwei ineinander schiebbaren Teilen 14, 15 bestehende Hilfswelle, wobei das ortsfeste Teil 15 z. B. mit einem Antriebszahnrad 16 versehen ist, mittels derer die Hilfswelle 14, 15 von der hier nicht gezeigten Kurbelwelle der Verbrennungskraftmaschine in bekannter Weise mittels eines hier ebenfalls nicht gezeigten Zahnriemens mit halber Kurbelwellenumdrehungszahl angetrieben wird. Die erste bzw. zweite Kulisse 12, 13 sind mit sich radial erstreckenden dritten bzw. vierten Kanälen 17, 18 versehen, durch die das bis in die erste bzw. zweite Ringnut 10, 11 gelangte Hydraulikfluid hindurchtreten kann. Von hier aus fließt das Hydraulikfluid in eine fünfte bzw. sechste Ringnut 19, 20 in der Hilfswelle 14. Von hier aus erstrecken sich axial ein fünfter bzw. sechster Kanal 21, 22 bis zur Querschnittsebene eines siebten bzw. achten Kanals 23, 24, die sich ebenfalls radial durch die Kulissen 12, 13 erstrecken und in einer dritten bzw. vierten Ringnut 25, 26 münden, von denen aus je Ventil ein erster und zweiter Kanal 27, 28 zu dem betreffenden Steuerzylinder 4 führt. Durch das Umfangsmaß der Mündung des fünften bzw. sechsten Kanals 21, 22 auf der Oberfläche der Hilfswelle 14 wird die Dauer der Beaufschlagung des zugehörigen Kolbens 3 mit Hydraulikfluid bestimmt und damit dessen Verschiebeweg. Dieser wiederum ist gleich dem erzielten Ventilhub. Die fünfte und sechste Ringnut 19, 20 sind durch in axialer Richtung verlaufende Stege 29 in ebensoviele Kammern geteilt, wie Ventile zu betätigen sind. Die Kulissen 12, 13 sind an ihren einander gegenüberliegenden Seiten mit Zahnkränzen 30 versehen. In ihre Verzahnung greift ein um eine Querachse drehbares Stellzahnrad 31 ein, so daß sich bei dessen Drehung die Kulissen 12, 13 gegeneinander verdrehen. Es läßt sich so die zeitliche Zuordnung der Ventilsteuerzeiten von Ein- und Auslaßventil verändern.A plurality of valves 2 are arranged in an engine block 1, only one of which is shown here. The valve 2 is actuated by displacing a piston 3 made of a ferritic material, which slides in a control cylinder 4 attached to the engine block 1 and is alternately acted upon by hydraulic fluid from one side or the other. The respective position of the piston 3 is detected by a contactless displacement sensor 32, which consists of a housing 34 inserted into the top of the control cylinder 4 and made of a non-magnetic, for example austenitic material, in which an electromagnet composed of a magnetic core 35 and a coil 37 passes through Insulation 38 is housed separately, the coil 37 being supplied by supply lines 36. The magnetic field that closes when the piston 3 is on top of the wall of the control cylinder 4 collapses when the piston 3 moves downward. In contrast to conventional valves, a spring 5 is not used to reset them but only to compensate for play. A first or second supply line 7, 8 emanate from an only indicated oil pump 6 with a variable mass flow for the separate actuation of the inlet and outlet valves and open inside a housing 9 in a first and second circumferential annular groove 10, 11. A first or second link 12, 13 is rotatably arranged in the interior of the housing 9 and in this in turn an auxiliary shaft consisting of two parts 14, 15 which can be pushed into one another. B. is provided with a drive gear 16, by means of which the auxiliary shaft 14, 15 is driven by the crankshaft, not shown here, of the internal combustion engine in a known manner by means of a toothed belt, also not shown here, at half the number of crankshaft revolutions. The first or second link 12, 13 are provided with radially extending third or fourth channels 17, 18, through which the hydraulic fluid which has reached the first or second annular groove 10, 11 can pass. From here, the hydraulic fluid flows into a fifth or sixth annular groove 19, 20 in the auxiliary shaft 14. From here, a fifth or sixth channel 21, 22 extend axially to the cross-sectional plane of a seventh or eighth channel 23, 24 also extend radially through the scenes 12, 13 and open into a third or fourth annular groove 25, 26, from which a first and a second channel 27, 28 leads to the respective control cylinder 4 from each valve. The circumference of the mouth of the fifth or sixth channel 21, 22 on the surface of the auxiliary shaft 14 determines the duration of the action of the associated piston 3 with hydraulic fluid and thus its displacement path. This in turn is equal to the valve lift achieved. The fifth and sixth annular grooves 19, 20 are divided into the same number of chambers by webs 29 extending in the axial direction as valves are to be actuated. The scenes 12, 13 are provided on their opposite sides with sprockets 30. A toothing gear 31, which can be rotated about a transverse axis, engages in its toothing, so that when it rotates, the links 12, 13 rotate relative to one another. The timing of the valve timing of the intake and exhaust valve can be changed.

Diese Eigenschaft wird durch die Figuren 2 und 3 veranschaulicht. In der Figur 1 stellt die Kurve a die bislang übliche, angenähert sinusförmige Steuercharakteristik der Ventile dar, wie sie mit der herkömmlichen Nockensteuerung zu erreichen ist. Mit b ist dagegen eine mit der hier vorgeschlagenen Vorrichtung zu erzielende, mehr rechteckförmige Steuerkurve dargestellt. Der so dargestellte große Ventilhub ergibt sich, wenn das verschiebliche Teil 14 der Hilfswelle so verschoben ist (in der Figur 1 nach rechts), daß ein sich über einen größeren Teil des Umfanges erstreckender Teil der Mündungen des fünften bzw. sechsten Kanals 21, 22 gegenüber dem siebenten bzw. achten Kanal 23, 24 zu liegen kommt. Durch die je Umdrehung der Hilfswelle 14, 15 längere Zeit der Uberschneidung dieser Öffnungen tritt eine größere Menge Hydraulikfluid hindurch und bewirkt einen größeren Verschiebeweg des Kolbens 3. Wird umgekehrt das verschiebliche Teil 14 der Hilfswelle in die andere Richtung verschoben, ergibt sich infolge des dann kleineren wirksamen Querschnittes der Öffnungen des fünften bzw. sechsten Kanals 21, 22 eine kürzere Überschneidungszeit. Weniger Hydraulikfluid tritt durch, der Kolben 3 wird nur um eine kleinere Strecke verschoben und es ergibt sich die Ventilcharakteristik c in der Figur 2. In dem Diagramm der Figur 3, in dem gleichfalls h den Ventilhub und t die Zeit bedeutet sind die Ventilkurven sowohl eines Ein- als auch eines Auslaßventils bi bzw. b3 dargestellt, wobei sich die Ventilcharakteristiken über eine Strecke xi überlappen, d. h. für den entsprechenden Zeitraum beide Ventile gleichzeitig geöffnet sind. Bei anderen Betriebsverhältnissen kann es günstiger sein, die Zeitdauer des gleichzeitigen Öffnens zu verlängern, was bedeutet, daß der Bereich der Überlappung auf die Strecke x2 ausgedehnt wird. Hierzu werden die Kurve bi nach b2 und die Kurve bs nach b4 symmetrisch zueinander verschoben, was durch ein Verdrehen des Stellzahnrades 31 und damit der Kulissen 12, 13 zueinander erreicht wird.This property is illustrated by Figures 2 and 3. In FIG. 1, curve a represents the previously customary, approximately sinusoidal control characteristic of the valves, as can be achieved with the conventional cam control. In contrast, b represents a more rectangular control curve that can be achieved with the device proposed here. The large valve lift shown in this way results when the displaceable part 14 of the auxiliary shaft is displaced (to the right in FIG. 1) in such a way that a part of the mouths of the fifth and sixth channels 21, 22, which extends over a larger part of the circumference, is opposite the seventh and eighth channels 23, 24 come to rest. Due to the longer period of overlap of these openings per revolution of the auxiliary shaft 14, a greater amount of hydraulic fluid passes through and causes a greater displacement path of the piston 3. Conversely, if the displaceable part 14 of the auxiliary shaft is displaced in the other direction, the smaller part results effective cross section of the openings of the fifth and sixth channels 21, 22 a shorter overlap time. Less hydraulic fluid passes through, the piston 3 is only displaced by a smaller distance and the valve characteristic c in FIG. 2 results. In the diagram in FIG. 3, in which h also means the valve lift and t time, the valve curves are both one An inlet valve and an outlet valve bi or b 3 are shown, the valve characteristics overlapping over a distance xi, ie both valves are open simultaneously for the corresponding period. In other operating conditions, it may be more convenient to extend the simultaneous opening period, which means that the area of overlap is extended to distance x 2 . For this purpose, the curve b i to b 2 and the curve bs to b 4 are shifted symmetrically to one another, which is achieved by rotating the adjusting gear 31 and thus the links 12, 13 relative to one another.

Der in der Figur 1 dargestellte Drehschieber ist in der schematischen Darstellung der Figur 4 mit 40 bezeichnet. Der Betrieb der Verbrennungskraftmaschine wird z. B. durch drei Meßaufnehmer und - umformer überwacht, und zwar durch einen Drehzahlmesser 41, einen Drehmomentmesser 42 und ein Thermometer 43. Die Meßwerte werden einem Prozeßrechner und Impulsgenerator 44 zugeführt, der daraus einen Sollwert für die jeweilige Ventilstellung errechnet und in einen Komparator 45 eingibt. Hier wird der Sollwert mit einem in einem Verstärker 49 verstärkten Istwert der momentanen Ventilstellung verglichen, wie er von dem kontaktlosen Wegaufnehmer 32 geliefert wird, mit dessen Hilfe an jedem Steuerzylinder 4 die Lage des dazugehörigen Kolbens 3 ermittelt wird. Um den Ist- an den Sollwert anzugleichen, gibt der Komparator 45 Steuersignale an einen ersten Schrittmotor 46, mit dem der bewegliche Teil 14 der Hilfswelle verschoben wird und an einen zweiten Schrittmotor 47, daß das Stellzahnrad 31 betätigt. Entsprechend den jeweiligen Gegebenheiten kann der eine oder andere der Schrittmotoren 46, 47 oder auch beide gleichzeitig betätigt werden, wobei im letzteren Falle sich eine Überlagerung der in den Figuren 2 und 3 dargestellten Änderungen der Ventilcharakteristik ergibt. Das aus dem Zylinder 4 verdrängte Hydraulikfluid fließt über eine Rücklaufleitung 33 in ein Reservoir 48, aus dem die Pumpe 6 ansaugt.The rotary slide valve shown in FIG. 1 is designated 40 in the schematic illustration in FIG. The operation of the internal combustion engine is e.g. B. monitored by three sensors and - converter, namely by a tachometer 41, a torque meter 42 and a thermometer 43. The measured values are fed to a process computer and pulse generator 44, which calculates a setpoint value for the respective valve position and inputs it into a comparator 45 . Here, the setpoint is compared with an actual value of the current valve position, amplified in an amplifier 49, as supplied by the contactless displacement sensor 32, with the aid of which the position of the associated piston 3 is determined on each control cylinder 4. In order to adjust the actual value to the target value, the comparator 45 sends control signals to a first stepper motor 46 with which the movable part 14 of the auxiliary shaft is displaced and to a second stepper motor 47 that the actuating gear 31 is actuated. Depending on the particular circumstances, one or the other of the stepper motors 46, 47 or both can be actuated simultaneously, in the latter case there being a superimposition of the changes in the valve characteristics shown in FIGS. 2 and 3. The hydraulic fluid displaced from the cylinder 4 flows via a return line 33 into a reservoir 48 from which the pump 6 draws in.

Claims (8)

1. Valve drive for an internal combustion engine (1) having an auxiliary shaft (14, 15) which is driven by the crankshaft, a hydraulic pump (6) and valves (2), each of which is moveable independently by means of the action of the hydraulic fluid on a piston (3), the auxiliary shaft being provided with rotatable links (12, 13) with the aid of which the supply of hydraulic fluid to the valves is shut off and released again at regular intervals, characterised by the following features:
a) a housing (9) in which the auxiliary shaft (14, 15) is supported and which is connected to a first and second supply line (7, 8), for hydraulic fluid for the actuation of the inlet or outlet valves (2), continuing as far as the inside of the housing and ending in a first and second annular groove (10, 11), and having a third and fourth annular groove (25, 26) from which a first and second (27, 28) port extends to each inlet and outlet valve respectively;
b) one or two links (12, 13) which are arranged between housing (9) and auxiliary shaft (14, 15) and are provided with a number, corresponding to the number of valves, of radial third, fourth, seventh and eighth (17, 18, 23, 24) ports which end on the outside thereof in the first to fourth annular grooves (10, 11, 25, 26);
c) fifth and sixth annular grooves (19, 20) in the auxiliary shaft (14, 15) into which run the third and fourth ports (17, 18) respectively on their inner side, and having fifth and sixth ports (21, 22) which proceed from this point, extend axially and issue to the outside in the cross-sectional plane of the seventh or eighth port (23, 24), the annular grooves being divided by webs 29 into a number of sectors corresponding to the number of valves.
2. Valve drive according to claim 1 having two links (12, 13), characterised in that the latter are rotatable relative to the housing (9) in mutually opposite directions of rotation.
3. Valve drive according to claim 2, characterised in that the links (12, 13) are rotatable by means of an adjusting gear wheel (31) which is rotatable transversely to their axis, is arranged between them and acts on crown gears (30) attached to them.
4. Valve drive according to claim 1, characterised in that the auxiliary shaft (14, 15) is axially displaceable and the mouths of the fifth and sixth ports (21, 22) on its surface, in various crosssectional planes, occupy varyingly large portions of the shaft periphery.
5. Valve drive according to claim 4, characterised in that the auxiliary shaft consists of two portions (14, 15) which can be displaced into one another, one (14) of which is provided with the fifth and sixth annular grooves (19, 20) or ports (21, 22) respectively and the other is provided with the drive elements (16).
6. Valve drive according to claim 1, characterised in that the axial displacement of the auxiliary shaft (14) and/or the rotation of the links (12, 13) in relation to each other takes place by means of adjusting units (46, 47) which are controlled in the sense that valve stroke and opening time are adjusted to desired values which are determined as a function of measured operating parameters (41-43) of the internal combustion engine (1).
7. Valve drive according to claim 6, characterised in that each valve (2) is provided with a displacement pick-up (32), the measurement signal of which as actual value enters a comparator (45) which compares it with a desired value which is established by a process computer (44) from the current operating parameters (41-43) of the internal combustion engine, the comparator transmitting control signals to the adjusting units (46, 47) in the case of deviations of the actual value from the desired value.
8. Valve drive according to claim 7, characterised in that speed (41), torque (42) and/or temperature (43) are entered as current operating parameters.
EP88101403A 1987-02-10 1988-02-01 Valve device with a hydraulic transmission and variable characteristic by means of sliding valve control Expired - Lifetime EP0279265B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88101403T ATE59212T1 (en) 1987-02-10 1988-02-01 VALVE GEAR WITH HYDRAULIC TRANSMISSION AND VARIABLE CHARACTERISTICS BY LINK CONTROL.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3704071 1987-02-10
DE3704071 1987-02-10

Publications (2)

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EP0279265A1 EP0279265A1 (en) 1988-08-24
EP0279265B1 true EP0279265B1 (en) 1990-12-19

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EP88101403A Expired - Lifetime EP0279265B1 (en) 1987-02-10 1988-02-01 Valve device with a hydraulic transmission and variable characteristic by means of sliding valve control

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US (1) US4821689A (en)
EP (1) EP0279265B1 (en)
JP (1) JPS63198710A (en)
KR (1) KR880010219A (en)
CN (1) CN88100461A (en)
AT (1) ATE59212T1 (en)
BR (1) BR8800533A (en)
DE (1) DE3861290D1 (en)
ES (1) ES2019411B3 (en)
MX (1) MX160235A (en)
SU (1) SU1621816A3 (en)

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Also Published As

Publication number Publication date
EP0279265A1 (en) 1988-08-24
KR880010219A (en) 1988-10-07
ES2019411B3 (en) 1991-06-16
DE3861290D1 (en) 1991-01-31
ATE59212T1 (en) 1991-01-15
CN88100461A (en) 1988-08-24
BR8800533A (en) 1988-09-27
SU1621816A3 (en) 1991-01-15
MX160235A (en) 1990-01-10
US4821689A (en) 1989-04-18
JPS63198710A (en) 1988-08-17

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