EP0441100A1 - Dispositif pour commander la soupape d'échappement d'un moteur à combustion interne à piston - Google Patents

Dispositif pour commander la soupape d'échappement d'un moteur à combustion interne à piston 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
Other languages
German (de)
English (en)
Other versions
EP0441100B1 (fr
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
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.)
Filing date
Publication date
Application filed by Sulzer AG, Gebrueder Sulzer AG filed Critical Sulzer AG
Publication of EP0441100A1 publication Critical patent/EP0441100A1/fr
Application granted granted Critical
Publication of EP0441100B1 publication Critical patent/EP0441100B1/fr
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
    • 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 '.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP90810973A 1990-02-08 1990-12-12 Dispositif pour commander la soupape d'échappement d'un moteur à combustion interne à piston Expired - Lifetime EP0441100B1 (fr)

Applications Claiming Priority (2)

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

Publications (2)

Publication Number Publication Date
EP0441100A1 true EP0441100A1 (fr) 1991-08-14
EP0441100B1 EP0441100B1 (fr) 1993-04-28

Family

ID=4186209

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90810973A Expired - Lifetime EP0441100B1 (fr) 1990-02-08 1990-12-12 Dispositif pour commander la soupape d'échappement d'un moteur à combustion interne à piston

Country Status (5)

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

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0539320A1 (fr) * 1991-10-23 1993-04-28 New Sulzer Diesel Ag Dispositif de commande hydraulique d'une soupape d'échappement d'un moteur à combustion interne à piston
DE10154339A1 (de) * 2001-11-06 2003-05-15 Volkswagen Ag Aktuator für ein Gaswechsel-Hubventil
WO2004022929A1 (fr) * 2002-08-29 2004-03-18 Robert Bosch Gmbh Actionneur hydraulique de soupape servant a actionner une soupape d'echange de gaz
DE102013220555A1 (de) * 2013-10-11 2015-04-16 Schaeffler Technologies Gmbh & Co. Kg Hydraulische Ventilsteuerung einer Brennkraftmaschine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
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 (de) 2003-12-24 2006-03-09 Man B&W Diesel A/S Vorrichtung zur Steuerung der zeitlich versetzten Verbindung von zwei mit einem Druckmittel beaufschlagbaren Aggregaten mit einer Druckmittelquelle

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0139566A1 (fr) * 1983-09-23 1985-05-02 Societe Alsacienne De Constructions Mecaniques De Mulhouse Bloc électro-hydraulique de commande des soupapes pour moteur à combustion interne
DE3806969A1 (de) * 1988-03-03 1989-09-14 Rexroth Mannesmann Gmbh Elektrohydraulische stelleinrichtung zur betaetigung von gaswechselventilen bei brennkraftmaschinen

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK225982A (da) * 1981-07-07 1983-01-08 Sulzer Ag Indstroemnings-eller udstoedningsventil til en forbraendingsmotors cylindertopstykke

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0139566A1 (fr) * 1983-09-23 1985-05-02 Societe Alsacienne De Constructions Mecaniques De Mulhouse Bloc électro-hydraulique de commande des soupapes pour moteur à combustion interne
DE3806969A1 (de) * 1988-03-03 1989-09-14 Rexroth Mannesmann Gmbh Elektrohydraulische stelleinrichtung zur betaetigung von gaswechselventilen bei brennkraftmaschinen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 9, no. 25 (M-355)(1748) 02 Februar 1985, & JP-A-59 170414 (NISSAN) 26 September 1984, *

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0539320A1 (fr) * 1991-10-23 1993-04-28 New Sulzer Diesel Ag Dispositif de commande hydraulique d'une soupape d'échappement d'un moteur à combustion interne à piston
DE10154339A1 (de) * 2001-11-06 2003-05-15 Volkswagen Ag Aktuator für ein Gaswechsel-Hubventil
WO2004022929A1 (fr) * 2002-08-29 2004-03-18 Robert Bosch Gmbh Actionneur hydraulique de soupape servant a actionner une soupape d'echange de gaz
US7007642B2 (en) 2002-08-29 2006-03-07 Robert Bosch Gmbh Hydraulic valve actuator for actuating a gas-exchange valve
DE102013220555A1 (de) * 2013-10-11 2015-04-16 Schaeffler Technologies Gmbh & Co. Kg Hydraulische Ventilsteuerung einer Brennkraftmaschine
DE102013220555B4 (de) * 2013-10-11 2015-05-13 Schaeffler Technologies AG & Co. KG Hydraulische Ventilsteuerung einer Brennkraftmaschine

Also Published As

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

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