EP0441100A1 - Device for controlling the exhaust valve of an internal combustion piston engine - Google Patents

Device for controlling the exhaust valve of an internal combustion piston engine Download PDF

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Publication number
EP0441100A1
EP0441100A1 EP90810973A EP90810973A EP0441100A1 EP 0441100 A1 EP0441100 A1 EP 0441100A1 EP 90810973 A EP90810973 A EP 90810973A EP 90810973 A EP90810973 A EP 90810973A EP 0441100 A1 EP0441100 A1 EP 0441100A1
Authority
EP
European Patent Office
Prior art keywords
pressure medium
valve
pilot valve
servo
movable part
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
EP90810973A
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German (de)
French (fr)
Other versions
EP0441100B1 (en
Inventor
Alfred Franz Wunder
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.)
Sulzer AG
Original Assignee
Sulzer AG
Gebrueder Sulzer AG
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Publication date
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Publication of EP0441100A1 publication Critical patent/EP0441100A1/en
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Publication of EP0441100B1 publication Critical patent/EP0441100B1/en
Anticipated expiration legal-status Critical
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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
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • F01L25/04—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means by working-fluid of machine or engine, e.g. free-piston machine
    • F01L25/06—Arrangements with main and auxiliary valves, at least one of them being fluid-driven
    • 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
    • F01L25/00—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means
    • F01L25/02—Drive, or adjustment during the operation, or distribution or expansion valves by non-mechanical means by fluid means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic

Definitions

  • the invention relates to a device for controlling the outlet valve of a reciprocating piston internal combustion engine, which at its end facing away from the closure part is in operative connection with a servo piston guided in a servo cylinder, which is acted upon by a hydraulic pressure medium in the valve opening direction in the work cycle of the machine, which is actuated via a pressure medium line is supplied to the servo cylinder from a pressure medium source.
  • a device of this type is known from GB-OS 2 102 065.
  • the pressure medium line is connected to the pressure side of a piston pump, the piston of which is driven by a camshaft.
  • the camshaft in turn is driven by the crankshaft of the internal combustion engine via interposed elements, for example a pair of gearwheels.
  • the pressure of the pressure medium opening the outlet valve and thus the opening and closing points of this valve are therefore dependent on the shape of the cam driving the pump piston on the camshaft.
  • the cam shape and thus the respective position of the opening and closing points can be varied within relatively narrow limits, which is disadvantageous.
  • the invention has for its object to improve a control device of the type mentioned in such a way that a camshaft drive for generating the opening pressure of the exhaust valve is eliminated.
  • this object is achieved by the features of the characterizing part of claim 1.
  • the actuation of the exhaust valve is effected by electrical signals dependent on the crank angle, which are fed to the electromagnet, which then passes the pressure medium to the servo piston of the exhaust valve by correspondingly influencing the pilot valve and by influencing the 4/2-way valve as a function thereof , whereby this opens, or relieves the pressure of the pressure medium from the servo piston, whereby the outlet valve moves into the closed position.
  • the control device according to the invention is also structurally simpler and cheaper. Furthermore, the new device ensures that the outlet valve also opens when the electromagnet is without current for the sake of malfunction.
  • a working cylinder 1 is formed in the machine housing of a 2-stroke diesel internal combustion engine, and then an exhaust duct 4 is formed in a separate housing 10 at its upper end.
  • an exhaust valve 2 is arranged at the entrance of the exhaust duct 4, which separates the combustion chamber 3 in the working cylinder 1 from the exhaust duct 4 in the closed position shown.
  • a working piston 5 is guided up and down. The air to be compressed in the working cylinder is admitted into the cylinder chamber via slots (not shown) arranged in the lower region of the working cylinder 1 and is compressed in the combustion chamber 3 during the subsequent upward stroke of the working piston 5.
  • the fuel is supplied with the aid of at least one injection nozzle (not shown) which projects into the combustion chamber 3.
  • a piston 6 is arranged, which is guided in a cylinder 7 of the housing 10.
  • a compressed air line 9 is connected via a check valve 8.
  • the air enclosed in the cylinder space 7 'in this way forms an air spring which acts on the exhaust valve 2 in a closing sense.
  • a servo piston 11 actuated by a hydraulic pressure medium acts on a rod 11 ′ and is guided in a servo cylinder 13 to which a hydraulic control device 12 is connected.
  • the control device 12 has a pilot valve 15 designed as a 2/2-way valve and actuated by an electromagnet 14 and a 4/2-way valve 16.
  • the hydraulic pressure medium for example oil, is supplied to the control device 12 via a line 17 from a pressure medium source 18 designed as an accumulator.
  • the accumulator 18 receives the pressure medium from a reservoir 20 by means of a pump 19 which is driven by the crankshaft (not shown) of the internal combustion engine or electrically.
  • the pressure medium in the accumulator 18 is under a pressure of, for example, 200 bar.
  • the line 17 leading from the accumulator 18 to the control device 12 forks upstream of the 4/2-way valve 16 into two line branches 17 'and 17''.
  • the line branch 17 ′′ contains a throttle point 22 and leads on the one hand to the pilot valve 15 and on the other hand to an end face of the 4/2-way valve 16.
  • a relief line 24 which leads to the 4/2-way valve 16 leads and continues as drain line 24 ', which opens into the reservoir 20 via a check valve 25.
  • drain line 24 ' There is also a vent line to the drain line 24 ' 26 connected, which branches off from the servo cylinder 13 above the piston 11 and has a throttle point 57.
  • the servo piston 11 has a blind bore 40 at its end facing away from the rod 11 ', which is connected to an annular space 58 at its lower end in FIG. 1 in the region of the connection point 21 via transverse bores 56. In the area of the connection point 23 there is an annular space 59 between the servo piston 11 and the servo cylinder 13.
  • the current at the electromagnet 14 of the pilot valve 15 is switched on, and the pressure medium supplied via the line branch 17 ′′ acts on the end face of the 4/2-way valve 16; the pressure medium supply via the line branch 17 'and the line 27 to the servo cylinder 13 is shut off.
  • the 4/2-way valve 16 has made the passage from the relief line 24 to the drain line 24 ', so that the servo piston 11 in the servo cylinder 13 is relieved of the pressure of the pressure medium and the outlet valve 2 is influenced in a closing sense by the air spring under the piston 6 becomes.
  • the 4/2-way valve 16 essentially consists of a housing 30 with four connection points 31, 32, 33 and 34 and a slide 35 movable in the housing.
  • the slide 35 has three piston-like thickenings 36, 37 and 38, which are closely guided in five bore sections with a corresponding diameter in the housing 30.
  • the housing 30 has four enlarged chambers 41, 42, 43 and 44 located between these bore sections, each of which via at least one channel 41 ', 42', 43 and 44 'with the associated connection 31 to 34 is connected.
  • the relief line 24 coming from the servo piston 13 opens at the connection point 31, and the drain line 24 ′ leading to the reservoir 20 is connected to the connection point 32.
  • the line 27 leading to the servo piston 13 is connected to the connection point 33 and the line branch 17 ′ coming from the accumulator 18 is connected to the connection point 34.
  • a cover 45 is fastened to it, which is closed at its end not shown in FIG. 2 and has a stop bolt 46 in its center.
  • the bolt 46 limits the upward movement of the slide 35 in FIG. 2.
  • a compression spring 47 is supported on the upper end of the slide 35 in FIG. 2, which is accommodated with its other end, not shown, in the cover 45 and which Slider 35 in Fig. 2 can move in the downward direction.
  • the fork point of the line 17 shown in FIG. 1 outside the 4/2-way valve is in the embodiment 2 integrated into the slide 35.
  • the lowest piston-like thickening 38 in FIG. 2 is provided with a transverse bore 48 which continues downward into an axial blind bore 49.
  • the blind bore 49 At the lower end of the blind bore 49 there follows a narrow transverse bore, which forms the throttle point 22.
  • the throttle bore 22 continues outwards into a bore 50 which opens out into an incision 51 in the lateral surface of the thickened area 38.
  • the thickening 38 leading bore section below the chamber 44 is slightly expanded, so that in the position shown, a pressure medium connection from the chamber 44 via the bores 48, 49, 22 and 50 to a space 52 below the lower end of the Slider 35 is made.
  • the space 52 is delimited at the bottom in FIG. 2 by a connecting piece-like component 54 fastened to the housing 30 and is connected to the pilot valve 15 via a channel 53.
  • the mouth of the channel 53 in the space 52 is opposite a flat surface 55 on the slide 35.
  • the pilot valve 15 consists essentially of a housing 60 with two connection points 61 and 62, a closure part 63 movable in the housing and the electromagnet 14 actuating this closure part.
  • the closure part 63 interacts with a seat part 65 inserted in the housing 60, which at its upper end in FIG. 3 has a valve seat surface, below which a plurality of channels 66 open, which are connected to the connection point 61 via an annular groove 67 and a channel 68.
  • a line not shown, is connected, which is connected to the channel 53 on the 4/2-way valve 16 (FIG. 2).
  • FIG. 2 the pilot valve 15 consists essentially of a housing 60 with two connection points 61 and 62, a closure part 63 movable in the housing and the electromagnet 14 actuating this closure part.
  • the closure part 63 interacts with a seat part 65 inserted in the housing 60, which at its upper end in FIG. 3 has a valve seat surface, below which a plurality of channels 66
  • Outflow chamber 69 is provided, which is connected to the connection point 62 via a narrowed throttle bore 70.
  • the relief line 28 (FIG. 1) is connected to the connection point 62.
  • a spring 71 is provided, which is supported on the closure part 63 and acts on it in the opening sense.
  • the closure part 63 is detachably connected to an armature 73 of the electromagnet 14 via a rod 72.
  • the armature 73 also has a bar 72 ′ corresponding to the bar 72 at its other end.
  • the upper end of the rod 72 'in FIG. 3 interacts with a stop bolt 74 which is adjustably fastened in a cover 75 of the magnet housing 76.
  • the armature 73 is axially movable and is held by two spring spiders 77 and 77 ', which are releasably attached to the center of the rod 72 and 72', respectively.
  • the spring spiders are clamped between a nozzle-like component 64 in the magnet housing 76 and the housing 60 or between the magnet housing 76 and the cover 75.
  • the armature 73 is surrounded by a brass sleeve 78 which is sealed off from the magnet housing 76 and the component 64.
  • the brass sleeve 78 is in turn surrounded by a magnet coil 79, which is provided with a power supply (not shown) via a lateral opening 80 in the magnet housing 76.
  • the armature 73 has a continuous channel 81 which extends in the axial direction and which continues at its lower end into a channel 81 'in the component 64.
  • the two end faces of the armature 63 are connected to the drain chamber 69 in the valve housing 60 via the channels 81 and 81 '.
  • a channel 82 is provided in the magnet housing 76 outside the magnet coil 79, which extends between the upper end face of the armature 73 and the spring spider 77 ', continues downward in the valve housing 60 and via a transverse bore 83 to the connection point 62 ( Fig. 3) leads.
  • the closure part 63 when the closure part 63 is open, different hydraulic pressure prevails on both end faces of the armature 73, so that pressure medium flows through the armature 73 upwards.
  • the space above the armature 73 is vented, specifically via the channel 82 and the bore 83. This significantly increases the repetition accuracy of the actuating movement of the pilot valve.
  • the electromagnet 14 is energized and holds the closure part 63 in the closed position. This prevents the discharge of pressure medium from the space 52 via the channel 53 of the 4/2-way valve, and the slide 35 moves upwards in FIG. 2. This movement is initially relatively rapid and is damped as soon as the lower boundary edge of the incision 51 enters the bore section in the housing 30 that guides the piston-like thickening 38. This damping means that the slider 35 slows down against the stop bolt 46. In this slide position, the connection points 31 and 32 are connected to one another via the chambers 41 and 42, so that the servo piston 11 is relieved and the outlet valve 2 closes.
  • connection point 34 and thus the chamber 44 are separated from the chamber 43 via the piston-like thickening 38, so that no pressure medium can reach the connection point 33.
  • the chamber 44 is through the bores 48, 49, 22 and 50 and the incision 51 during the first phase of movement of the slide 35 in connection with the space 52, so that a pressure builds up in the space 52 due to the closed pilot valve, which moves the slide. Towards the end of this movement, ie during the slowed-down movement due to the damping described above, only a little pressure medium flows into the space 52.
  • the spring 71 presses the closure part 63 into the open position, so that the previously blocked pressure medium from the bores 66 via the outflow space 69, the channels 81 ', 81 and 82 and the bore 83 and Connection point 62 flows into the relief line 28.
  • a smaller amount of pressure medium flows through the throttle bore 70 and the connection point 62 into the relief line 28.
  • This escape of the pressure medium acts via the channel 53 on the 4/2-way valve 16 on the pressure of the pressure medium in the space 52 under the slide 35.
  • the slide 35 consequently moves downward and thereby establishes the connection between the chambers 44 and 43 as soon as the thickening 38 emerges from the bore section between these chambers.
  • Pressure medium can thus pass from the chamber 44 via the connection point 33 into the line 27 and - as described in relation to FIG. 1 - load the servo piston 11.
  • the connection between the chambers 44 and 43 is established, the connection between the chambers 41 and 42 is interrupted because the thickening 36 enters the bore section between these two chambers.
  • the relief line 24 is thus separated from the drain line 24 '.

Abstract

At its end facing away from the closure part, the exhaust valve (2) is in operative connection with a servo piston (11) guided in a servo cylinder (13). During the power stroke of the engine, the servo piston is stressed in the valve opening direction by a hydraulic pressure medium, which is fed to the servo cylinder (13) from a pressure medium source (18) via a pressure medium conduit (17,27). A pilot control valve (15) actuated by an electromagnet (14) and a 4/2-way valve (16) are arranged between the pressure medium source (18) and the servo cylinder (13). The position of the 4/2-way valve (16) is dependent on the position of the pilot control valve (15).

Description

Die Erfindung bezieht sich auf eine Einrichtung zum Steuern des Auslassventils einer Hubkolbenbrennkraftmaschine, das an seinem dem Verschlussteil abgewendeten Ende mit einem in einem Servozylinder geführten Servokolben in Wirkungsverbindung steht, der im Arbeitstakt der Maschine von einem hydraulischen Druckmittel im Ventilöffnungssinn beaufschlagt ist, das über eine Druckmittelleitung von einer Druckmittelquelle dem Servozylinder zugeführt wird.The invention relates to a device for controlling the outlet valve of a reciprocating piston internal combustion engine, which at its end facing away from the closure part is in operative connection with a servo piston guided in a servo cylinder, which is acted upon by a hydraulic pressure medium in the valve opening direction in the work cycle of the machine, which is actuated via a pressure medium line is supplied to the servo cylinder from a pressure medium source.

Eine Einrichtung dieser Art ist aus der GB-OS 2 102 065 bekannt. In der bekannten Vorrichtung ist die Druckmittelleitung an die Druckseite einer Kolbenpumpe angeschlossen, deren Kolben von einer Nockenwelle angetrieben ist. Die Nockenwelle ihrerseits wird über zwischengeschaltete Elemente, z.B. ein Zahnradpaar, von der Kurbelwelle der Brennkraftmaschine angetrieben. Der das Auslassventil öffnende Druck des Druckmittels und damit der Oeffnungs- und der Schliesspunkt dieses Ventils sind also von der Form des den Pumpenkolben antreibenden Nockens auf der Nockenwelle abhängig. Die Nockenform und somit die jeweilige Lage des Oeffnungs- und des Schliesspunktes sind in relativ engen Grenzen variierbar, was nachteilig ist.A device of this type is known from GB-OS 2 102 065. In the known device, the pressure medium line is connected to the pressure side of a piston pump, the piston of which is driven by a camshaft. The camshaft in turn is driven by the crankshaft of the internal combustion engine via interposed elements, for example a pair of gearwheels. The pressure of the pressure medium opening the outlet valve and thus the opening and closing points of this valve are therefore dependent on the shape of the cam driving the pump piston on the camshaft. The cam shape and thus the respective position of the opening and closing points can be varied within relatively narrow limits, which is disadvantageous.

Der Erfindung liegt die Aufgabe zugrunde, eine Steuereinrichtung der eingangs genannten Art dahingehend zu verbessern, dass ein Nockenwellenantrieb zum Erzeugen des Oeffnungsdruckes des Auslassventils entfällt.The invention has for its object to improve a control device of the type mentioned in such a way that a camshaft drive for generating the opening pressure of the exhaust valve is eliminated.

Diese Aufgabe wird erfindungsgemäss durch die Merkmale des Kennzeichens des Anspruchs 1 gelöst. Durch diese Ausbildung der Steuereinrichtung wird das Betätigen des Auslassventils durch vom Kurbelwinkel abhängige elektrische Signale bewirkt, die dem Elektromagneten zugeführt werden, der dann durch entsprechende Beeinflussung des Vorsteuerventils und durch von diesem abhängige Beeinflussung des 4/2-Wegeventils das Druckmittel zum Servokolben des Auslassventils weiterleitet, wodurch dieses öffnet, oder den Servokolben vom Druck des Druckmittels entlastet, wodurch das Auslassventil in die Schliessstellung gelangt. Mit Hilfe der elektrischen Signale ist man freier in der Wahl des Oeffnungs- und des Schliesspunktes des Auslassventils, wodurch der Spülvorgang im Arbeitszylinder der Brennkraftmaschine in derem ganzen Arbeitsbereich optimiert werden kann. Daraus resultiert eine Brennstoffersparnis. Durch den Wegfall der Nockenwelle und ihres Antriebes wird die erfindungsgemässe Steuereinrichtung auch konstruktiv einfacher und billiger. Ferner stellt die neue Einrichtung sicher, dass das Auslassventil auch öffnet, wenn der Elektromagnet störungshalber ohne Strom ist.According to the invention, this object is achieved by the features of the characterizing part of claim 1. Through this design of the control device, the actuation of the exhaust valve is effected by electrical signals dependent on the crank angle, which are fed to the electromagnet, which then passes the pressure medium to the servo piston of the exhaust valve by correspondingly influencing the pilot valve and by influencing the 4/2-way valve as a function thereof , whereby this opens, or relieves the pressure of the pressure medium from the servo piston, whereby the outlet valve moves into the closed position. With the help of the electrical signals, one is more free in the choice of the opening and closing point of the exhaust valve, as a result of which the flushing process in the working cylinder of the internal combustion engine can be optimized in its entire working range. This results in fuel savings. By eliminating the camshaft and its drive, the control device according to the invention is also structurally simpler and cheaper. Furthermore, the new device ensures that the outlet valve also opens when the electromagnet is without current for the sake of malfunction.

Ein Ausführungsbeispiel der Erfindung wird in der folgenden Beschreibung anhand der Zeichnung näher erläutert. Es zeigen:

Fig. 1
einen Vertikalschnitt durch den oberen Teil eines Arbeitszylinders mit einem Auslassventil sowie ein Schaltschema der Steuereinrichtung,
Fig. 2
einen Axialschnitt durch ein 4/2-Wegeventil der Steuereinrichtung,
Fig. 3
einen Axialschnitt durch ein Vorsteuerventil der Steuereinrichtung und
Fig. 4
einen gegenüber Fig. 3 um 90o gedrehten Axialschnitt durch den oberen Teil des Vorsteuerventils.
An embodiment of the invention is explained in more detail in the following description with reference to the drawing. Show it:
Fig. 1
a vertical section through the upper part of a working cylinder with a Exhaust valve and a circuit diagram of the control device,
Fig. 2
an axial section through a 4/2-way valve of the control device,
Fig. 3
an axial section through a pilot valve of the control device and
Fig. 4
an compared to Fig. 3 rotated by 90 o axial section through the upper part of the pilot valve.

Gemäss Fig. 1 ist im Maschinengehäuse einer 2-Takt-Dieselbrennkraftmaschine ein Arbeitszylinder 1 und anschliessend an dessen oberen Ende in einem getrennten Gehäuse 10 ein Auspuffkanal 4 ausgebildet. Im Gehäuse 10 ist am Eingang des Auspuffkanals 4 ein Auslassventil 2 angeordnet, das in der gezeichneten geschlossenen Stellung den Brennraum 3 im Arbeitszylinder 1 vom Auspuffkanal 4 trennt. Im Arbeitszylinder 1 ist ein Arbeitskolben 5 auf- und abbeweglich geführt. Die im Arbeitszylinder zu komprimierende Luft wird über nicht dargestellte, im unteren Bereich des Arbeitszylinders 1 angeordnete Schlitze in den Zylinderraum eingelassen und beim anschliessenden Aufwärtshub des Arbeitskolbens 5 im Brennraum 3 verdichtet. Der Brennstoff wird mit Hilfe mindestens einer nicht dargestellten, in den Brennraum 3 ragenden Einspritzdüse zugeführt.1, a working cylinder 1 is formed in the machine housing of a 2-stroke diesel internal combustion engine, and then an exhaust duct 4 is formed in a separate housing 10 at its upper end. In the housing 10, an exhaust valve 2 is arranged at the entrance of the exhaust duct 4, which separates the combustion chamber 3 in the working cylinder 1 from the exhaust duct 4 in the closed position shown. In the working cylinder 1, a working piston 5 is guided up and down. The air to be compressed in the working cylinder is admitted into the cylinder chamber via slots (not shown) arranged in the lower region of the working cylinder 1 and is compressed in the combustion chamber 3 during the subsequent upward stroke of the working piston 5. The fuel is supplied with the aid of at least one injection nozzle (not shown) which projects into the combustion chamber 3.

An dem dem Brennraum 3 abgewendeten Ende des Auslassventils 2 ist ein Kolben 6 angeordnet, der in einem Zylinder 7 des Gehäuses 10 geführt ist. An dem in Fig. 1 unterhalb des Kolbens 6 befindlichen Zylinderraum 7' ist über ein Rückschlagventil 8 eine Druckluftleitung 9 angeschlossen. Die auf diese Weise im Zylinderraum 7' eingeschlossene Luft bildet eine Luftfeder, die auf das Auslassventil 2 in schliessendem Sinne wirkt.At the end of the exhaust valve 2 facing away from the combustion chamber 3, a piston 6 is arranged, which is guided in a cylinder 7 of the housing 10. On the cylinder space 7 'located in FIG. 1 below the piston 6 A compressed air line 9 is connected via a check valve 8. The air enclosed in the cylinder space 7 'in this way forms an air spring which acts on the exhaust valve 2 in a closing sense.

Auf die in Fig. 1 obere Seite des Kolbens 6 wirkt über eine Stange 11' ein von einem hydraulischen Druckmittel betätigter Servokolben 11, der in einem Servozylinder 13 geführt ist, an dem eine hydraulische Steuereinrichtung 12 angeschlossen ist. Die Steuereinrichtung 12 weist ein als 2/2-Wegeventil ausgebildetes, durch einen Elektromagneten 14 betätigtes Vorsteuerventil 15 und ein 4/2-Wegeventil 16 auf. Das hydraulische Druckmittel, z.B. Oel, wird der Steuereinrichtung 12 über eine Leitung 17 von einer als Akkumulator ausgebildeten Druckmittelquelle 18 zugeführt. Der Akkumulator 18 erhält das Druckmittel aus einem Reservoir 20 mittels einer Pumpe 19, die von der nicht dargestellten Kurbelwelle der Brennkraftmaschine oder elektrisch angetrieben ist. Im Akkumulator 18 befindet sich das Druckmittel unter einem Druck von beispielsweise 200 bar. Die vom Akkumulator 18 zur Steuereinrichtung 12 führende Leitung 17 gabelt sich vor dem 4/2-Wegeventil 16 in zwei Leitungszweige 17' und 17''. Der Leitungszweig 17' führt zum 4/2-Wegeventil 16 und setzt sich als Leitung 27 bis zu einer Anschlussstelle 21 am Servozylinder 13 fort. Der Leitungszweig 17'' enthält eine Drosselstelle 22 und führt einerseits zum Vorsteuerventil 15 und andererseits auf eine Stirnseite des 4/2-Wegeventils 16. Am Servozylinder 13 befindet sich eine weitere Anschlussstelle 23 für eine Entlastungsleitung 24, die zum 4/2-Wegeventil 16 führt und sich als Ablaufleitung 24' fortsetzt, die über ein Rückschlagventil 25 in das Reservoir 20 mündet. An die Ablaufleitung 24' ist ausserdem eine Entlüftungsleitung 26 angeschlossen, die vom Servozylinder 13 oberhalb des Kolbens 11 abzweigt und eine Drosselstelle 57 aufweist. Stromoberhalb des Rückschlagventils 25 mündet in die Ablaufleitung 24' eine Entlastungsleitung 28, die vom Vorsteuerventil 15 ausgeht.On the upper side of the piston 6 in FIG. 1, a servo piston 11 actuated by a hydraulic pressure medium acts on a rod 11 ′ and is guided in a servo cylinder 13 to which a hydraulic control device 12 is connected. The control device 12 has a pilot valve 15 designed as a 2/2-way valve and actuated by an electromagnet 14 and a 4/2-way valve 16. The hydraulic pressure medium, for example oil, is supplied to the control device 12 via a line 17 from a pressure medium source 18 designed as an accumulator. The accumulator 18 receives the pressure medium from a reservoir 20 by means of a pump 19 which is driven by the crankshaft (not shown) of the internal combustion engine or electrically. The pressure medium in the accumulator 18 is under a pressure of, for example, 200 bar. The line 17 leading from the accumulator 18 to the control device 12 forks upstream of the 4/2-way valve 16 into two line branches 17 'and 17''. The line branch 17 'leads to the 4/2-way valve 16 and continues as line 27 to a connection point 21 on the servo cylinder 13. The line branch 17 ″ contains a throttle point 22 and leads on the one hand to the pilot valve 15 and on the other hand to an end face of the 4/2-way valve 16. On the servo cylinder 13 there is a further connection point 23 for a relief line 24 which leads to the 4/2-way valve 16 leads and continues as drain line 24 ', which opens into the reservoir 20 via a check valve 25. There is also a vent line to the drain line 24 ' 26 connected, which branches off from the servo cylinder 13 above the piston 11 and has a throttle point 57. A relief line 28, which starts from the pilot valve 15, opens into the outlet line 24 ′ upstream of the check valve 25.

Der Servokolben 11 weist an seinem der Stange 11' abgewendeten Ende eine Sackbohrung 40 auf, die an ihrem in Fig. 1 unteren Ende im Bereich der Anschlussstelle 21 über Querbohrungen 56 mit einem Ringraum 58 in Verbindung steht. Im Bereich der Anschlussstelle 23 besteht zwischen dem Servokolben 11 und dem Servozylinder 13 ein Ringraum 59.The servo piston 11 has a blind bore 40 at its end facing away from the rod 11 ', which is connected to an annular space 58 at its lower end in FIG. 1 in the region of the connection point 21 via transverse bores 56. In the area of the connection point 23 there is an annular space 59 between the servo piston 11 and the servo cylinder 13.

In der in Fig. 1 gezeichneten Stellung ist der Strom am Elektromagneten 14 des Vorsteuerventils 15 eingeschaltet, und das über den Leitungszweig 17'' zugeführte Druckmittel wirkt auf die Stirnfläche des 4/2-Wegeventils 16; die Druckmittelzufuhr über den Leitungszweig 17' und die Leitung 27 zum Servozylinder 13 ist dadurch abgesperrt. Hingegen hat das 4/2-Wegeventil 16 den Durchgang von der Entlastungsleitung 24 zur Ablaufleitung 24' hergestellt, so dass der Servokolben 11 im Servozylinder 13 vom Druck des Druckmittels entlastet wird und das Auslassventil 2 von der Luftfeder unter dem Kolben 6 in schliessendem Sinne beeinflusst wird. Wird der Strom am Elektromagneten 14 ausgeschaltet, so wird im Vorsteuerventil 15 eine Verbindung zwischen dem Leitungszweig 17'' und der Entlastungsleitung 28 hergestellt, so dass die Stirnfläche des 4/2-Wegeventils 16 vom Druck entlastet wird. Das 4/2-Wegeventil 16 unterbricht damit die vorherige Verbindung der Leitungen 24 und 24' und verbindet nunmehr den Leitungszweig 17' mit der Leitung 27, so dass unter Druck stehendes Druckmittel über die Anschlussstelle 21, den Raum 58 und die Querbohrungen 56 in die Sackbohrung 40 gelangt, wodurch der Servokolben 11 abwärts bewegt wird und das Auslassventil 2 öffnet.In the position shown in FIG. 1, the current at the electromagnet 14 of the pilot valve 15 is switched on, and the pressure medium supplied via the line branch 17 ″ acts on the end face of the 4/2-way valve 16; the pressure medium supply via the line branch 17 'and the line 27 to the servo cylinder 13 is shut off. In contrast, the 4/2-way valve 16 has made the passage from the relief line 24 to the drain line 24 ', so that the servo piston 11 in the servo cylinder 13 is relieved of the pressure of the pressure medium and the outlet valve 2 is influenced in a closing sense by the air spring under the piston 6 becomes. If the current at the electromagnet 14 is switched off, a connection is established in the pilot valve 15 between the line branch 17 ″ and the relief line 28, so that the end face of the 4/2-way valve 16 is relieved of pressure. The 4/2-way valve 16 thus interrupts the previous connection of the lines 24 and 24 'and now connects the line branch 17' to the line 27, so that pressurized pressure medium via the connection point 21 Space 58 and the transverse bores 56 enter the blind bore 40, as a result of which the servo piston 11 is moved downward and the outlet valve 2 opens.

Gemäss Fig. 2 besteht das 4/2-Wegeventil 16 im wesentlichen aus einem Gehäuse 30 mit vier Anschlussstellen 31,32,33 und 34 und einem im Gehäuse beweglichen Schieber 35. Der Schieber 35 weist drei kolbenartige Verdickungen 36,37 und 38 auf, die in fünf Bohrungsabschnitten mit entsprechendem Durchmesser im Gehäuse 30 eng geführt sind. Den vier Anschlüssen 31 bis 34 entsprechend weist das Gehäuse 30 vier erweiterte, zwischen diesen Bohrungsabschnitten befindliche Kammern 41,42,43 und 44 auf, von denen jede über mindestens einen Kanal 41',42',43 bzw. 44'mit dem zugehörigen Anschluss 31 bis 34 verbunden ist. An der Anschlussstelle 31 mündet die vom Servokolben 13 kommende Entlastungsleitung 24, und an der Anschlussstelle 32 ist die zum Reservoir 20 führende Ablaufleitung 24' angeschlossen. An der Anschlussstelle 33 ist die zum Servokolben 13 führende Leitung 27 und an der Anschlussstelle 34 der vom Akkumulator 18 kommende Leitungszweig 17' angeschlossen. Am in Fig. 2 oberen Ende des Gehäuses 30 ist an diesem ein Deckel 45 befestigt, der an seinem in Fig. 2 nicht gezeigten Ende verschlossen ist und in seinem Zentrum einen Anschlagbolzen 46 aufweist. Der Bolzen 46 begrenzt die in Fig. 2 nach oben gerichtete Bewegung des Schiebers 35. Auf dem in Fig. 2 oberen Ende des Schiebers 35 stützt sich eine Druckfeder 47 ab, die mit ihrem anderen nicht gezeigten Ende im Deckel 45 untergebracht ist und die den Schieber 35 in Fig. 2 in Abwärtsrichtung bewegen kann.2, the 4/2-way valve 16 essentially consists of a housing 30 with four connection points 31, 32, 33 and 34 and a slide 35 movable in the housing. The slide 35 has three piston-like thickenings 36, 37 and 38, which are closely guided in five bore sections with a corresponding diameter in the housing 30. Corresponding to the four connections 31 to 34, the housing 30 has four enlarged chambers 41, 42, 43 and 44 located between these bore sections, each of which via at least one channel 41 ', 42', 43 and 44 'with the associated connection 31 to 34 is connected. The relief line 24 coming from the servo piston 13 opens at the connection point 31, and the drain line 24 ′ leading to the reservoir 20 is connected to the connection point 32. The line 27 leading to the servo piston 13 is connected to the connection point 33 and the line branch 17 ′ coming from the accumulator 18 is connected to the connection point 34. At the upper end of the housing 30 in FIG. 2, a cover 45 is fastened to it, which is closed at its end not shown in FIG. 2 and has a stop bolt 46 in its center. The bolt 46 limits the upward movement of the slide 35 in FIG. 2. A compression spring 47 is supported on the upper end of the slide 35 in FIG. 2, which is accommodated with its other end, not shown, in the cover 45 and which Slider 35 in Fig. 2 can move in the downward direction.

Die in Fig. 1 ausserhalb des 4/2-Wegeventils gezeigte Gabelstelle der Leitung 17 ist bei der Ausführungsform nach Fig. 2 in den Schieber 35 integriert. Zu diesem Zweck ist die in Fig. 2 unterste kolbenartige Verdickung 38 mit einer Querbohrung 48 versehen, die sich nach unten in eine axiale Sackbohrung 49 fortsetzt. Am unteren Ende der Sackbohrung 49 schliesst sich an diese eine enge Querbohrung an, die die Drosselstelle 22 bildet. Die Drosselbohrung 22 setzt sich nach aussen in eine Bohrung 50 fort, die aussen in einen Einschnitt 51 in der Mantelfläche der Verdickung 38 mündet. Im Bereich dieses Einschnitts 51 ist der die Verdickung 38 führende Bohrungsabschnitt unterhalb der Kammer 44 etwas erweitert, so dass in der gezeichneten Stellung eine Druckmittelverbindung von der Kammer 44 über die Bohrungen 48,49,22 und 50 zu einem Raum 52 unterhalb des unteren Endes des Schiebers 35 besteht. Der Raum 52 ist in Fig. 2 nach unten von einem stutzenartigen, am Gehäuse 30 befestigten Bauteil 54 begrenzt und steht über einen Kanal 53 mit dem Vorsteuerventil 15 in Verbindung. Der Mündung des Kanals 53 in den Raum 52 steht eine ebene Fläche 55 am Schieber 35 gegenüber.The fork point of the line 17 shown in FIG. 1 outside the 4/2-way valve is in the embodiment 2 integrated into the slide 35. For this purpose, the lowest piston-like thickening 38 in FIG. 2 is provided with a transverse bore 48 which continues downward into an axial blind bore 49. At the lower end of the blind bore 49 there follows a narrow transverse bore, which forms the throttle point 22. The throttle bore 22 continues outwards into a bore 50 which opens out into an incision 51 in the lateral surface of the thickened area 38. In the area of this incision 51, the thickening 38 leading bore section below the chamber 44 is slightly expanded, so that in the position shown, a pressure medium connection from the chamber 44 via the bores 48, 49, 22 and 50 to a space 52 below the lower end of the Slider 35 is made. The space 52 is delimited at the bottom in FIG. 2 by a connecting piece-like component 54 fastened to the housing 30 and is connected to the pilot valve 15 via a channel 53. The mouth of the channel 53 in the space 52 is opposite a flat surface 55 on the slide 35.

Gemäss Fig. 3 besteht das Vorsteuerventil 15 im wesentlichen aus einem Gehäuse 60 mit zwei Anschlussstellen 61 und 62, einem im Gehäuse beweglichen Verschlussteil 63 und dem diesen Verschlussteil betätigenden Elektromagnet 14. Der Verschlussteil 63 wirkt mit einem im Gehäuse 60 eingesetzten Sitzteil 65 zusammen, der an seinem in Fig. 3 oberen Ende eine Ventilsitzfläche aufweist, unterhalb der mehrere Kanäle 66 münden, die über eine Ringnut 67 und einen Kanal 68 mit der Anschlussstelle 61 in Verbindung stehen. An der Anschlussstelle 61 ist eine nicht dargestellte Leitung angeschlossen, die mit dem Kanal 53 am 4/2-Wegeventil 16 (Fig. 2) in Verbindung steht. In Fig. 3 oberhalb des Sitzteils 65 ist im Gehäuse 60 eine Abströmkammer 69 vorgesehen, die über eine verengte Drosselbohrung 70 mit der Anschlussstelle 62 in Verbindung steht. An der Anschlussstelle 62 ist die Entlastungsleitung 28 (Fig. 1) angeschlossen. In Fig. 3 unterhalb des Verschlussteils 63 ist eine Feder 71 vorgesehen, die sich am Verschlussteil 63 abstützt und auf diesen im öffnenden Sinne wirkt.According to FIG. 3, the pilot valve 15 consists essentially of a housing 60 with two connection points 61 and 62, a closure part 63 movable in the housing and the electromagnet 14 actuating this closure part. The closure part 63 interacts with a seat part 65 inserted in the housing 60, which at its upper end in FIG. 3 has a valve seat surface, below which a plurality of channels 66 open, which are connected to the connection point 61 via an annular groove 67 and a channel 68. At the connection point 61, a line, not shown, is connected, which is connected to the channel 53 on the 4/2-way valve 16 (FIG. 2). In Fig. 3 above the seat part 65 is in the housing 60 Outflow chamber 69 is provided, which is connected to the connection point 62 via a narrowed throttle bore 70. The relief line 28 (FIG. 1) is connected to the connection point 62. In Fig. 3 below the closure part 63, a spring 71 is provided, which is supported on the closure part 63 and acts on it in the opening sense.

An seinem in Fig. 3 oberen Ende ist der Verschlussteil 63 lösbar über eine Stange 72 mit einem Anker 73 des Elektromagneten 14 verbunden. Eine der Stange 72 entsprechende Stange 72' weist der Anker 73 auch an seinem anderen Ende auf. Das in Fig. 3 obere Ende der Stange 72' wirkt mit einem Anschlagbolzen 74 zusammen, der in einem Deckel 75 des Magnetgehäuses 76 verstellbar befestigt ist. Der Anker 73 ist axial beweglich und wird von zwei Federspinnen 77 und 77' gehalten, die in ihrem Zentrum an der Stange 72 bzw. 72' lösbar befestigt sind. An ihrem äusseren Umfang sind die Federspinnen zwischen einem stutzenartigen Bauteil 64 im Magnetgehäuse 76 und dem Gehäuse 60 bzw. zwischen dem Magnetgehäuse 76 und dem Deckel 75 eingeklemmt. Der Anker 73 ist von einer Messinghülse 78 umgeben, die gegenüber dem Magnetgehäuse 76 und dem Bauteil 64 abgedichtet ist. Die Messinghülse 78 ist ihrerseits von einer Magnetspule 79 umgeben, die über eine seitliche Oeffnung 80 im Magnetgehäuse 76 mit einer nicht dargestellten Stromzufuhr versehen ist. Der Anker 73 weist einen sich in axialer Richtung erstreckenden, durchgehenden Kanal 81 auf, der sich an seinem unteren Ende in einen Kanal 81' im Bauteil 64 fortsetzt. Ueber die Kanäle 81 und 81' stehen die beiden Stirnseiten des Ankers 63 mit dem Abflussraum 69 im Ventilgehäuse 60 in Verbindung.At its upper end in FIG. 3, the closure part 63 is detachably connected to an armature 73 of the electromagnet 14 via a rod 72. The armature 73 also has a bar 72 ′ corresponding to the bar 72 at its other end. The upper end of the rod 72 'in FIG. 3 interacts with a stop bolt 74 which is adjustably fastened in a cover 75 of the magnet housing 76. The armature 73 is axially movable and is held by two spring spiders 77 and 77 ', which are releasably attached to the center of the rod 72 and 72', respectively. On their outer circumference, the spring spiders are clamped between a nozzle-like component 64 in the magnet housing 76 and the housing 60 or between the magnet housing 76 and the cover 75. The armature 73 is surrounded by a brass sleeve 78 which is sealed off from the magnet housing 76 and the component 64. The brass sleeve 78 is in turn surrounded by a magnet coil 79, which is provided with a power supply (not shown) via a lateral opening 80 in the magnet housing 76. The armature 73 has a continuous channel 81 which extends in the axial direction and which continues at its lower end into a channel 81 'in the component 64. The two end faces of the armature 63 are connected to the drain chamber 69 in the valve housing 60 via the channels 81 and 81 '.

Wie Fig. 4 zeigt, ist im Magnetgehäuse 76 ausserhalb der Magnetspule 79 ein Kanal 82 vorgesehen, der zwischen der oberen Stirnfläche des Ankers 73 und der Federspinne 77' ausgeht, sich nach unten im Ventilgehäuse 60 fortsetzt und über eine Querbohrung 83 zur Anschlussstelle 62 (Fig. 3) führt. Auf diese Weise herrscht bei geöffnetem Verschlussteil 63 auf beiden Stirnseiten des Ankers 73 unterschiedlicher hydraulischer Druck, so dass der Anker 73 von Druckmittel aufwärts durchströmt wird. Gleichzeitig findet eine Entlüftung des Raumes oberhalb des Ankers 73 statt, und zwar über den Kanal 82 und die Bohrung 83. Hierdurch wird die Repetiergenauigkeit der Stellbewegung des Vorsteuerventils wesentlich erhöht.As shown in FIG. 4, a channel 82 is provided in the magnet housing 76 outside the magnet coil 79, which extends between the upper end face of the armature 73 and the spring spider 77 ', continues downward in the valve housing 60 and via a transverse bore 83 to the connection point 62 ( Fig. 3) leads. In this way, when the closure part 63 is open, different hydraulic pressure prevails on both end faces of the armature 73, so that pressure medium flows through the armature 73 upwards. At the same time, the space above the armature 73 is vented, specifically via the channel 82 and the bore 83. This significantly increases the repetition accuracy of the actuating movement of the pilot valve.

In der in Fig. 3 und 4 gezeichneten Stellung ist der Elektromagnet 14 unter Strom und hält den Verschlussteil 63 in geschlossener Stellung. Dadurch wird der Ablauf von Druckmedium aus dem Raum 52 über den Kanal 53 des 4/2-Wegeventils verhindert, und der Schieber 35 bewegt sich in Fig. 2 nach oben. Diese Bewegung ist anfänglich verhältnismässig schnell und wird gedämpft, sobald der Einschnitt 51 mit seiner unteren Begrenzungskante in den die kolbenartige Verdickung 38 führenden Bohrungsabschnitt im Gehäuse 30 eintritt. Durch diese Dämpfung wird erreicht, dass der Schieber 35 sich verlangsamt gegen den Anschlagbolzen 46 bewegt. In dieser Schieberstellung sind also die Anschlussstellen 31 und 32 über die Kammern 41 und 42 miteinander verbunden, so dass der Servokolben 11 entlastet ist und das Auslassventil 2 schliesst. Zugleich ist über die kolbenartige Verdickung 38 die Anschlussstelle 34 und damit die Kammer 44 von der Kammer 43 getrennt, so dass kein Druckmittel zur Anschlussstelle 33 gelangen kann. Die Kammer 44 ist jedoch über die Bohrungen 48, 49, 22 und 50 und den Einschnitt 51 während der ersten Bewegungsphase des Schiebers 35 mit dem Raum 52 in Verbindung, so dass sich wegen des geschlossenen Vorsteuerventils ein Druck im Raum 52 aufbaut, der den Schieber bewegt. Gegen Ende dieser Bewegung, d.h. während der oben beschriebenen verlangsamten Bewegung infolge der Dämpfung strömt nur noch wenig Druckmittel in den Raum 52 nach.In the position shown in FIGS. 3 and 4, the electromagnet 14 is energized and holds the closure part 63 in the closed position. This prevents the discharge of pressure medium from the space 52 via the channel 53 of the 4/2-way valve, and the slide 35 moves upwards in FIG. 2. This movement is initially relatively rapid and is damped as soon as the lower boundary edge of the incision 51 enters the bore section in the housing 30 that guides the piston-like thickening 38. This damping means that the slider 35 slows down against the stop bolt 46. In this slide position, the connection points 31 and 32 are connected to one another via the chambers 41 and 42, so that the servo piston 11 is relieved and the outlet valve 2 closes. At the same time, the connection point 34 and thus the chamber 44 are separated from the chamber 43 via the piston-like thickening 38, so that no pressure medium can reach the connection point 33. However, the chamber 44 is through the bores 48, 49, 22 and 50 and the incision 51 during the first phase of movement of the slide 35 in connection with the space 52, so that a pressure builds up in the space 52 due to the closed pilot valve, which moves the slide. Towards the end of this movement, ie during the slowed-down movement due to the damping described above, only a little pressure medium flows into the space 52.

Wenn der Strom des Elektromagneten 14 abgeschaltet wird, drückt die Feder 71 den Verschlussteil 63 in die offene Stellung, so dass das vorher abgesperrte Druckmittel aus den Bohrungen 66 über den Abströmraum 69, die Kanäle 81', 81 und 82 sowie die Bohrung 83 und die Anschlussstelle 62 in die Entlastungsleitung 28 abströmt. Zugleich strömt auch eine kleinere Menge Druckmittel über die Drosselbohrung 70 und die Anschlussstelle 62 in die Entlastungsleitung 28 ab. Dieses Entweichen des Druckmittels wirkt über den Kanal 53 am 4/2-Wegeventil 16 auf den Druck des Druckmittels im Raum 52 unter dem Schieber 35. Der Schieber 35 bewegt sich infolgedessen abwärts und stellt dabei die Verbindung zwischen den Kammern 44 und 43 her, sobald die Verdickung 38 aus dem Bohrungsabschnitt zwischen diesen Kammern austritt. Damit kann Druckmedium aus der Kammer 44 über die Anschlussstelle 33 in die Leitung 27 gelangen und - wie zu Fig. 1 beschrieben - den Servokolben 11 belasten. Mit dem Herstellen der Verbindung zwischen den Kammern 44 und 43 wird die Verbindung zwischen den Kammern 41 und 42 unterbrochen, weil die Verdickung 36 in den Bohrungsabschnitt zwischen diesen beiden Kammern eintritt. Damit ist die Entlastungsleitung 24 von der Ablaufleitung 24' getrennt. Wenn der Schieber 35 mit seiner ebenen Fläche 55 in die Nähe der Mündung des Kanals 53 kommt, tritt auch eine Dämpfung der Bewegung des Schiebers 35 ein.When the current of the electromagnet 14 is switched off, the spring 71 presses the closure part 63 into the open position, so that the previously blocked pressure medium from the bores 66 via the outflow space 69, the channels 81 ', 81 and 82 and the bore 83 and Connection point 62 flows into the relief line 28. At the same time, a smaller amount of pressure medium flows through the throttle bore 70 and the connection point 62 into the relief line 28. This escape of the pressure medium acts via the channel 53 on the 4/2-way valve 16 on the pressure of the pressure medium in the space 52 under the slide 35. The slide 35 consequently moves downward and thereby establishes the connection between the chambers 44 and 43 as soon as the thickening 38 emerges from the bore section between these chambers. Pressure medium can thus pass from the chamber 44 via the connection point 33 into the line 27 and - as described in relation to FIG. 1 - load the servo piston 11. When the connection between the chambers 44 and 43 is established, the connection between the chambers 41 and 42 is interrupted because the thickening 36 enters the bore section between these two chambers. The relief line 24 is thus separated from the drain line 24 '. When the slide 35 comes with its flat surface 55 near the mouth of the channel 53, there is also a damping of the movement of the slide 35.

Abweichend von dem beschriebenen Ausführungsbeispiel ist es auch möglich - statt den Kanal 82 im Magnetgehäuse 76 anzuordnen - den Kanal 82 durch den Deckel 75 nach aussen zu führen und ihn dann über eine besondere Leitung mit der Entlastungsleitung 28 zu verbinden. Ausserdem ist es aus Symmetriegründen vorteilhaft, im Anker 73 statt einem Kanal 81 mehrere solcher Kanäle anzuordnen. Entsprechend sind auch im Bauteil 64 mehrere Kanäle vorgesehen.In a departure from the exemplary embodiment described, it is also possible - instead of arranging the channel 82 in the magnet housing 76 - to lead the channel 82 outward through the cover 75 and then to connect it to the relief line 28 via a special line. In addition, for reasons of symmetry, it is advantageous to arrange several such channels in the armature 73 instead of one channel 81. Correspondingly, several channels are also provided in component 64.

Claims (9)

Einrichtung zum Steuern des Auslassventils einer Hubkolbenbrennkraftmaschine, das an seinem dem Verschlussteil abgewendeten Ende mit einem in einem Servozylinder geführten Servokolben in Wirkungsverbindung steht, der im Arbeitstakt der Maschine von einem hydraulischen Druckmittel im Ventilöffnungssinn beaufschlagt ist, das über eine Druckmittelleitung von einer Druckmittelquelle dem Servozylinder zugeführt wird, dadurch gekennzeichnet, dass zwischen der Druckmittelquelle und dem Servozylinder ein von einem Elektromagneten betätigtes Vorsteuerventil und ein 4/2-Wegeventil angeordnet sind, dass bei eingeschaltetem Strom des Elektromagneten das Vorsteuerventil in geschlossener Stellung ist, wobei der bewegliche Teil des 4/2-Wegeventils eine Stellung innehat, in der der Servokolben des Auslassventils vom Druckmittel entlastet wird, und dass bei ausgeschaltetem Strom des Elektromagneten das Vorsteuerventil in offener Stellung ist, wobei der bewegliche Teil des 4/2-Wegeventils in einer Stellung ist, in der der Servokolben des Auslassventils vom Druckmittel belastet wird.Device for controlling the outlet valve of a reciprocating piston internal combustion engine, which at its end facing away from the closure part is operatively connected to a servo piston guided in a servo cylinder, which is acted upon by a hydraulic pressure medium in the valve opening direction during the work cycle of the machine, which hydraulic fluid is supplied to the servo cylinder via a pressure medium line from a pressure medium source is characterized in that between the pressure medium source and the servo cylinder, a pilot valve actuated by an electromagnet and a 4/2-way valve are arranged, that when the electromagnet is switched on, the pilot valve is in the closed position, the movable part of the 4/2 Directional valve is in a position in which the servo piston of the outlet valve is relieved of pressure medium, and that when the electromagnet is switched off, the pilot valve is in the open position, the movable part of the 4/2-way valve in one Position in which the servo piston of the exhaust valve is loaded by the pressure medium. Einrichtung nach Anspruch 1, dadurch gekennzeichnet, dass als Druckmittelquelle ein das Druckmittel unter Druck speichernder Akkumulator vorgesehen ist.Device according to Claim 1, characterized in that an accumulator which stores the pressure medium under pressure is provided as the pressure medium source. Einrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Anker des Elektromagneten mindestens einen seine beiden Stirnseiten verbindenden Durchgang aufweist, der an seinem dem Vorsteuerventil zugewendeten Ende mit dem Abflussraum des Vorsteuerventils in Verbindung steht,und dass der Durchgang an seinem dem Vorsteuerventil abgewendeten Ende über einen Kanal mit der Abflussseite des Vorsteuerventils in Verbindung steht.Device according to claim 1 or 2, characterized in that the armature of the electromagnet has at least one passage connecting its two end faces, which at its end facing the pilot valve is connected to the discharge space of the pilot valve, and that the passage at its end facing away from the pilot valve is connected to the discharge side of the pilot valve via a duct. Einrichtung nach Anspruch 3, dadurch gekennzeichnet, dass der Kanal im Gehäuse des Elektromagneten verläuft.Device according to claim 3, characterized in that the channel runs in the housing of the electromagnet. Einrichtung nach Anspruch 3, dadurch gekennzeichnet, dass eine Drosselverbindung zwischen dem Abflussraum und der Abflusseite des Vorsteuerventils besteht.Device according to claim 3, characterized in that there is a throttle connection between the discharge space and the discharge side of the pilot valve. Einrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, dass die Druckmittelzufuhr zum Vorsteuerventil über den beweglichen Teil des 4/2-Wegeventils geführt ist.Device according to one of claims 1 to 5, characterized in that the pressure medium supply to the pilot valve is guided via the movable part of the 4/2-way valve. Einrichtung nach Anspruch 6, dadurch gekennzeichnet, dass der bewegliche Teil des 4/2-Wegeventils mit einer Dämpfungsvorrichtung versehen ist, die wirksam wird, nachdem der bewegliche Teil die Verbindung zwischen der Druckmittelquelle und dem Servozylinder hergestellt und die Verbindung zwischen dem Servozylinder und einer Ablaufleitung unterbrochen hat.Device according to claim 6, characterized in that the movable part of the 4/2-way valve is provided with a damping device which is effective after the movable part has established the connection between the pressure medium source and the servo cylinder and the connection between the servo cylinder and a drain line interrupted. Einrichtung nach Anspruch 6, dadurch gekennzeichnet, dass der bewegliche Teil des 4/2-Wegeventils mit einer Dämpfungsvorrichtung versehen ist, die wirksam wird, nachdem der bewegliche Teil die Verbindung zwischen dem Servozylinder und einer Ablaufleitung hergestellt und die Verbindung zwischen der Druckmittelquelle und dem Zylinder unterbrochen hat.Device according to claim 6, characterized in that the movable part of the 4/2-way valve is provided with a damping device which is effective is established after the movable part has established the connection between the servo cylinder and a drain line and has broken the connection between the pressure medium source and the cylinder. Einrichtung nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, dass das Auslassventil mit einer Luftfeder verbunden ist, die auf das Auslassventil in schliessendem Sinne wirkt.Device according to one of claims 1 to 8, characterized in that the outlet valve is connected to an air spring which acts on the outlet valve in a closing sense.
EP90810973A 1990-02-08 1990-12-12 Device for controlling the exhaust valve of an internal combustion piston engine Expired - Lifetime EP0441100B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH402/90 1990-02-08
CH40290 1990-02-08

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EP0441100A1 true EP0441100A1 (en) 1991-08-14
EP0441100B1 EP0441100B1 (en) 1993-04-28

Family

ID=4186209

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Application Number Title Priority Date Filing Date
EP90810973A Expired - Lifetime EP0441100B1 (en) 1990-02-08 1990-12-12 Device for controlling the exhaust valve of an internal combustion piston engine

Country Status (5)

Country Link
EP (1) EP0441100B1 (en)
JP (1) JP3126741B2 (en)
KR (1) KR100192602B1 (en)
DE (1) DE59001316D1 (en)
DK (1) DK0441100T3 (en)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0539320A1 (en) * 1991-10-23 1993-04-28 New Sulzer Diesel Ag Device for hydraulically operating an exhaust valve of an internal combustion piston engine
DE10154339A1 (en) * 2001-11-06 2003-05-15 Volkswagen Ag Actuator for a gas exchange lifting valve of an internal combustion engine comprises a control chamber having a first chamber connected to a hydraulic system and a second chamber
WO2004022929A1 (en) * 2002-08-29 2004-03-18 Robert Bosch Gmbh Hydraulic valve actuator for actuating a gas exchange valve
DE102013220555A1 (en) * 2013-10-11 2015-04-16 Schaeffler Technologies Gmbh & Co. Kg Hydraulic valve control of an internal combustion engine

Families Citing this family (3)

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Publication number Priority date Publication date Assignee Title
US5647318A (en) 1994-07-29 1997-07-15 Caterpillar Inc. Engine compression braking apparatus and method
US5526784A (en) 1994-08-04 1996-06-18 Caterpillar Inc. Simultaneous exhaust valve opening braking system
DE10361221B4 (en) 2003-12-24 2006-03-09 Man B&W Diesel A/S Device for controlling the time-shifted connection of two acted upon by a pressure medium units with a pressure medium source

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EP0139566A1 (en) * 1983-09-23 1985-05-02 Societe Alsacienne De Constructions Mecaniques De Mulhouse Electro-hydraulic unit for the control of the valves of an internal-combustion engine
DE3806969A1 (en) * 1988-03-03 1989-09-14 Rexroth Mannesmann Gmbh Electrohydraulic adjusting mechanism for actuation of the inlet and exhaust valves in internal combustion engines

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DK225982A (en) * 1981-07-07 1983-01-08 Sulzer Ag INHIBIT OR EXHAUST VALVE TO A CYLINDER TOP OF A COMBUSTION ENGINE

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EP0139566A1 (en) * 1983-09-23 1985-05-02 Societe Alsacienne De Constructions Mecaniques De Mulhouse Electro-hydraulic unit for the control of the valves of an internal-combustion engine
DE3806969A1 (en) * 1988-03-03 1989-09-14 Rexroth Mannesmann Gmbh Electrohydraulic adjusting mechanism for actuation of the inlet and exhaust valves in internal combustion engines

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0539320A1 (en) * 1991-10-23 1993-04-28 New Sulzer Diesel Ag Device for hydraulically operating an exhaust valve of an internal combustion piston engine
DE10154339A1 (en) * 2001-11-06 2003-05-15 Volkswagen Ag Actuator for a gas exchange lifting valve of an internal combustion engine comprises a control chamber having a first chamber connected to a hydraulic system and a second chamber
WO2004022929A1 (en) * 2002-08-29 2004-03-18 Robert Bosch Gmbh Hydraulic valve actuator for actuating a gas exchange valve
US7007642B2 (en) 2002-08-29 2006-03-07 Robert Bosch Gmbh Hydraulic valve actuator for actuating a gas-exchange valve
DE102013220555A1 (en) * 2013-10-11 2015-04-16 Schaeffler Technologies Gmbh & Co. Kg Hydraulic valve control of an internal combustion engine
DE102013220555B4 (en) * 2013-10-11 2015-05-13 Schaeffler Technologies AG & Co. KG Hydraulic valve control of an internal combustion engine

Also Published As

Publication number Publication date
KR910015774A (en) 1991-09-30
KR100192602B1 (en) 1999-06-15
JPH04214914A (en) 1992-08-05
EP0441100B1 (en) 1993-04-28
DE59001316D1 (en) 1993-06-03
JP3126741B2 (en) 2001-01-22
DK0441100T3 (en) 1993-06-01

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