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EP0279265A1 - 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
EP0279265A1
EP0279265A1 EP88101403A EP88101403A EP0279265A1 EP 0279265 A1 EP0279265 A1 EP 0279265A1 EP 88101403 A EP88101403 A EP 88101403A EP 88101403 A EP88101403 A EP 88101403A EP 0279265 A1 EP0279265 A1 EP 0279265A1
Authority
EP
European Patent Office
Prior art keywords
auxiliary shaft
valve
annular grooves
valve train
channels
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP88101403A
Other languages
German (de)
French (fr)
Other versions
EP0279265B1 (en
Inventor
Gabriel Tittizer
Ewald Dipl.-Ing. Junghans
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Interatom Internationale Atomreaktorbau GmbH
Original Assignee
Interatom Internationale Atomreaktorbau GmbH
Priority date (The priority date 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 date listed.)
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Publication date
Application filed by Interatom Internationale Atomreaktorbau GmbH filed Critical Interatom Internationale Atomreaktorbau GmbH
Priority to AT88101403T priority Critical patent/ATE59212T1/en
Publication of EP0279265A1 publication Critical patent/EP0279265A1/en
Application granted granted Critical
Publication of EP0279265B1 publication Critical patent/EP0279265B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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.
  • the object of the present invention is a valve train of the type described, in which the valve characteristic can be changed in accordance with 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 with a change in the time during which hydraulic fluid can reach the respective valve, the extent of the movement of the piston displacing the valve is also changed.
  • 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. Is pressed the valve 2 by moving 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 from one side or the other with hydraulic fluid.
  • the respective position of the piston 3 is detected by a contactless displacement transducer 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.
  • Rotatable in the interior of the housing 9, a first or second link 12, 13 is arranged and in this in turn an auxiliary shaft consisting of two parts 14, 15 which can be pushed into one another, the stationary part 15, for. B.
  • 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, which also extend radially through the scenes 12, 13 and open into a third or fourth annular groove 25, 26, from each of which a first and second channel 27, 28 leads to the relevant control cylinder 4.
  • the duration of the action of the associated piston 3 with hydraulic fluid and thus its displacement path are determined by the circumferential dimension of the mouth of the fifth or sixth channel 21, 22 on the surface of the auxiliary shaft 14. 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 rotates about a transverse axis engages in its toothing, so that when it rotates, the linkages 12, 13 rotate against one another. The timing of the valve timing of the intake and exhaust valve can be changed.
  • 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, 15, a larger amount of hydraulic fluid passes through and causes a greater displacement path of the piston 3.
  • the valve curves are both one An inlet and an outlet valve b1 or b3 shown, the valve characteristics overlap over a distance x1, ie both valves are open at the same time. 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 the distance x2. For this purpose, the curve b1 to b2 and the curve b3 to b4 are shifted symmetrically to each other, which is achieved by rotating the adjusting gear 31 and thus the scenes 12, 13 to each other.
  • 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 transducers, 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 them 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, which actuates the setting gear 31.
  • a first stepper motor 46 with which the movable part 14 of the auxiliary shaft is displaced
  • a second stepper motor 47 which actuates the setting gear 31.
  • 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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Mechanically-Actuated Valves (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Non-Deflectable Wheels, Steering Of Trailers, Or Other Steering (AREA)
  • Control Of Fluid Gearings (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 outlet valves are open at the same time, ie 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 operating temperatures of the Machine of different viscosity of the hydraulic fluid, however, cannot achieve exact valve control with a device of this type.

Aufgabe der vorliegenden Erfindung ist ein Ventiltrieb 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 valve train of the type described, in which the valve characteristic can be changed in accordance with 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 with a change in the time during which hydraulic fluid can reach the respective valve, the extent of the movement of the piston displacing the valve is also changed. 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. Is pressed the valve 2 by moving 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 from one side or the other with hydraulic fluid. The respective position of the piston 3 is detected by a contactless displacement transducer 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. Rotatable in the interior of the housing 9, a first or second link 12, 13 is arranged and in this in turn an auxiliary shaft consisting of two parts 14, 15 which can be pushed into one another, the stationary part 15, for. 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, which also extend radially through the scenes 12, 13 and open into a third or fourth annular groove 25, 26, from each of which a first and second channel 27, 28 leads to the relevant control cylinder 4. The duration of the action of the associated piston 3 with hydraulic fluid and thus its displacement path are determined by the circumferential dimension of the mouth of the fifth or sixth channel 21, 22 on the surface of the auxiliary shaft 14. 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 rotates about a transverse axis engages in its toothing, so that when it rotates, the linkages 12, 13 rotate against 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 Überschnei­dung 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 b₁ bzw. b₃ dargestellt, wobei sich die Ventilcharakteristiken über eine Strecke x₁ 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 b₁ nach b₂ und die Kurve b₃ 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, 15, a larger 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 result is then smaller 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 is obtained. 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 and an outlet valve b₁ or b₃ shown, the valve characteristics overlap over a distance x₁, ie both valves are open at the same time. 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 the distance x₂. For this purpose, the curve b₁ to b₂ and the curve b₃ to b₄ are shifted symmetrically to each other, which is achieved by rotating the adjusting gear 31 and thus the scenes 12, 13 to each other.

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 transducers, 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 them 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 to the desired 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, which actuates the setting gear 31. Corresponding Depending on the 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. Ventiltrieb für eine Verbrennungskraftmaschine (1) mit einer von der Kurbelwelle angetriebenen Hilfswelle (14, 15), einer Hydraulikpumpe (6) und Ventilen (2), die je für sich durch die Einwirkung des Hydraulikfluids auf einen Kolben (3) bewegbar sind, wobei die Hilfswelle mit drehbaren Kulissen (12, 13) versehen ist, mit deren Hilfe die Zufuhr von Hydraulikfluid zu den Ventilen in regelmäßigen Abständen abgesperrt und wieder freigegeben wird, gekennzeichnet durch folgende Merkmale: a) ein Gehäuse (9), in dem die Hilfswelle (14, 15) gelagert ist und das mit einer ersten und zweiten Zufuhrleitung (7, 8) für Hydraulikfluid zur Betätigung der Ein- bzw. Auslaßventile (2) verbunden ist, die sich bis auf die Innenseite des Gehäuses fortsetzen und in einer ersten und zweiten Ringnut enden (10, 11), sowie mit einer dritten bzw. vierten Ringnut (25, 26), von denen aus sich ein erster und zweiter (27, 28) bzw. siebenter und achter (23, 24) Kanal zu jedem Ein- bzw. Auslaßventil erstreckt, b) einer oder zwei Kulissen (12, 13), die zwischen Gehäuse (9) und Hilfswelle (14, 15) angeordnet sind und mit einer der Ventilzahl entsprechenden Zahl von radialen, an ihrer Außenseite in den ersten bis vierten Ringnuten (10, 11, 25, 26) endenden dritten und vierten (17, 18) Kanälen versehen sind, c) fünften und sechsten Ringnuten (19, 20) in der Hilfswelle (14, 15), in die die ersten bzw. dritten Kanäle (27, 17) an ihrer Innenseite münden, und mit hiervon ausgehenden fünften und sechsten Kanälen (21, 22), die sich axial erstrecken und in der Querschnittsebene der zweiten bzw. vierten Kanäle (28, 18) nach außen münden, wobei die Ringnuten durch Stege 29 in eine der Ventilzahl entsprechende Zahl von Sektoren geteilt sind. 1. Valve train for an internal combustion engine (1) with an auxiliary shaft driven by the crankshaft (14, 15), a hydraulic pump (6) and valves (2), each of which can be moved by 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 at regular intervals, characterized by the following features: a) a housing (9) in which the auxiliary shaft (14, 15) is mounted and which is connected to a first and second supply line (7, 8) for hydraulic fluid for actuating the inlet and outlet valves (2), which are Continue to the inside of the housing and end in a first and second ring groove (10, 11), and with a third and fourth ring groove (25, 26), of which a first and second (27, 28) or seventh and eighth (23, 24) channel extends to each intake and exhaust valve, b) one or two links (12, 13) which are arranged between the housing (9) and the auxiliary shaft (14, 15) and which have a number of radial numbers corresponding to the number of valves, on the outside thereof in the first to fourth annular grooves (10, 11 , 25, 26) ending third and fourth (17, 18) channels are provided, c) fifth and sixth annular grooves (19, 20) in the auxiliary shaft (14, 15) into which the first and third channels (27, 17) open on the inside thereof, and with fifth and sixth channels (21, 22 ), which extend axially and open outward in the cross-sectional plane of the second and fourth channels (28, 18), the annular grooves being divided by webs 29 into a number of sectors corresponding to the number of valves. 2. Ventiltrieb nach Anspruch 1 mit zwei Kulissen (12, 13), dadurch gekennzeichnet, daß diese in einander entgegengesetztem Drehsinn gegenüber dem Gehäuse (9) verdrehbar sind.2. Valve train according to claim 1 with two scenes (12, 13), characterized in that they rotate in opposite directions with respect to the housing (9) are rotatable. 3. Ventiltrieb nach Anspruch 2, dadurch gekennzeichnet, daß die Kulissen (12, 13) mittels eines quer zu ihrer Achse drehbaren, zwischen ihnen angeordneten und in an ihnen angebrachte Zahnkränze (30) eingreifenden Stellzahnrades (31) verdrehbar sind.3. Valve train according to claim 2, characterized in that the scenes (12, 13) are rotatable by means of a rotatable transversely to their axis, arranged between them and engaging in them on sprockets (30) engaging adjusting gear (31). 4. Ventiltrieb nach Anspruch 1, dadurch gekennzeichnet, daß die Hilfswelle (14, 15) axial verschieblich ist und die Mündungen der fünften und sechsten Kanäle (21, 22) auf ihrer Oberfläche in verschiedenen Querschnittsebenen verschieden große Teile des Wellenumfanges einnehmen.4. Valve train according to claim 1, characterized in that the auxiliary shaft (14, 15) is axially displaceable and the mouths of the fifth and sixth channels (21, 22) occupy different parts of the shaft circumference on their surface in different cross-sectional planes. 5. Ventiltrieb nach Anspruch 4, dadurch gekennzeichnet, daß die Hilfswelle aus zwei ineinander verschiebbaren Teilen (14, 15) besteht, von denen der eine (14) mit den fünften und sechsten Ringnuten (19, 20) bzw. Kanälen (21, 22) versehen ist und der andere mit den Antriebselementen (16).5. Valve train according to claim 4, characterized in that the auxiliary shaft consists of two mutually displaceable parts (14, 15), one of which (14) with the fifth and sixth annular grooves (19, 20) or channels (21, 22nd ) is provided and the other with the drive elements (16). 6. Ventiltrieb nach Anspruch 1, dadurch gekennzeichnet, daß das axiale Verschieben der Hilfswelle (14) und/oder das Verdrehen der Kulissen (12, 13) zueinander durch Stellorgane (46, 47) erfolgt, die in dem Sinne gesteuert werden, daß Ventilhub und -öffnungszeit Sollwerten nachgefahren werden, die in Abhängigkeit von gemessenen Betriebsparametern (41-43) der Verbrennungskraftmaschine (1) bestimmt werden.6. Valve train according to claim 1, characterized in that the axial displacement of the auxiliary shaft (14) and / or the rotation of the scenes (12, 13) to each other by actuators (46, 47) which are controlled in the sense that valve lift Setpoint values and opening time are traced, which are determined as a function of measured operating parameters (41-43) of the internal combustion engine (1). 7. Ventiltrieb nach Anspruch 6, dadurch gekennzeichnet, daß jedes Ventil (2) mit einem Wegaufnehmer (32) versehen ist, dessen Meßsignal als Istwert in einen Komparator (45) eingeht, der ihn mit einem Sollwert vergleicht, der durch einen Prozeßrechner (44) aus den aktuellen Betriebsparametern (41-43) der Verbrennungskraftmaschine ermittelt wird, wobei der Komparator bei Abweichungen des Ist­vom Sollwert Steuersignale an die Stellorgane (46, 47) sendet.7. Valve train according to claim 6, characterized in that each valve (2) is provided with a displacement sensor (32), the measurement signal of which is received as an actual value in a comparator (45) which compares it with a setpoint value which is determined by a process computer (44 ) from the current operating parameters (41-43) of the internal combustion engine is determined, the comparator sending control signals to the actuators (46, 47) if the actual value deviates from the target value. 8. Ventiltrieb nach Anspruch 7, dadurch gekennzeichnet, daß als aktuelle Betriebs­parameter Drehzahl (41), Drehmoment (42) und/oder Temperatur (43) eingehen.8. Valve train according to claim 7, characterized in that the current operating parameters include speed (41), torque (42) and / or temperature (43).
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)

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AT88101403T ATE59212T1 (en) 1987-02-10 1988-02-01 VALVE GEAR WITH HYDRAULIC TRANSMISSION AND VARIABLE CHARACTERISTICS BY LINK CONTROL.

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DE3704071 1987-02-10
DE3704071 1987-02-10

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EP (1) EP0279265B1 (en)
JP (1) JPS63198710A (en)
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AT (1) ATE59212T1 (en)
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EP0390422A1 (en) * 1989-03-30 1990-10-03 Isuzu Ceramics Research Institute Co., Ltd. Valve stepping drive apparatus
WO1991001435A1 (en) * 1989-07-20 1991-02-07 Siemens Aktiengesellschaft Modular position controller for variable valve timing
WO1991002897A1 (en) * 1989-08-23 1991-03-07 Robert Bosch Gmbh Fuel injection pump for internal combustion engines
FR2702003A1 (en) * 1993-02-25 1994-09-02 Arlaud Roger Electrohydraulic control device for an internally opening valve for an internal combustion engine
EP0721056A1 (en) * 1995-01-06 1996-07-10 Ford Motor Company Limited Rotary hydraulic valve control of an electrohydraulic camless valvetrain
US5985237A (en) * 1996-10-29 1999-11-16 Honjo Chemical Corporation Process for producing lithium manganese oxide suitable for use as cathode material of lithium ion secondary batteries
FR2758857A1 (en) * 1997-01-27 1998-07-31 Aisin Seiki IC engine valve actuating mechanism
US6752116B2 (en) 2000-07-28 2004-06-22 Robert Bosch Gmbh Connection between two shaft ends, positioned coaxially one behind the other, of a gas shuttle valve in an internal combustion engine and a valve actuator
DE10315594A1 (en) * 2003-04-05 2004-10-14 Daimlerchrysler Ag Camshaft adjustment device to change rotational position of camshaft in relation to crankshaft has driving power of camshaft directed from crankshaft via hydraulic transmission formed by pump unit and hydromotor unit
EP1734233A2 (en) * 2005-06-17 2006-12-20 Eaton Corporation Hydraulic cam for variable timing/displacement valve train
EP1734233A3 (en) * 2005-06-17 2009-10-21 Eaton Corporation Hydraulic cam for variable timing/displacement valve train
EP2525066A2 (en) 2011-05-19 2012-11-21 MAN Truck & Bus AG Method and device for desulfation of a exhaust gas cleaning device in a diesel combustion engine
EP2525060A2 (en) 2011-05-19 2012-11-21 MAN Truck & Bus AG Method and device for testing the functionality, in particular the oxidation capacity of an NO oxidation catalytic converter installed in the waste gas line of a combustion engine operated with excess air
DE102011102047A1 (en) 2011-05-19 2012-11-22 Man Truck & Bus Ag Method and apparatus for desulfating a arranged in a diesel engine exhaust purification device
DE102011102008A1 (en) 2011-05-19 2012-11-22 Man Truck & Bus Ag Method and device for checking the operability, in particular the oxidation capability, of a NO oxidation catalytic converter installed in the exhaust gas line of an internal combustion engine operated with excess air

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BR8800533A (en) 1988-09-27
ATE59212T1 (en) 1991-01-15
ES2019411B3 (en) 1991-06-16
DE3861290D1 (en) 1991-01-31
US4821689A (en) 1989-04-18
MX160235A (en) 1990-01-10
EP0279265B1 (en) 1990-12-19
CN88100461A (en) 1988-08-24
KR880010219A (en) 1988-10-07
JPS63198710A (en) 1988-08-17
SU1621816A3 (en) 1991-01-15

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