WO2007118535A1 - Commande de soupape - Google Patents

Commande de soupape Download PDF

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Publication number
WO2007118535A1
WO2007118535A1 PCT/EP2007/001019 EP2007001019W WO2007118535A1 WO 2007118535 A1 WO2007118535 A1 WO 2007118535A1 EP 2007001019 W EP2007001019 W EP 2007001019W WO 2007118535 A1 WO2007118535 A1 WO 2007118535A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
control
piston
inlet
pressure
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.)
Ceased
Application number
PCT/EP2007/001019
Other languages
German (de)
English (en)
Inventor
Jörg Dantlgraber
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of WO2007118535A1 publication Critical patent/WO2007118535A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/143—Tappets; Push rods for use with overhead camshafts
    • 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
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • 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
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
    • 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
    • F01L1/344—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 changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—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 changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the invention relates to a valve control for reciprocating engines according to the preamble of patent claim 1.
  • variable valve controls In conventional internal combustion engines, the lifting movement of the intake and exhaust valves takes place directly by a camshaft driven by the crankshaft in the speed ratio 2: 1.
  • the lift curve of the valve for the entire range of the map is proportional to the cam profile and thus invariable, so that the opening time and closing time the inlet and outlet valves is not optimally adjustable.
  • variable valve controls have been developed which use an intermediate hydraulic element to adjust the opening and closing times of the valves.
  • Such a variable valve control for intake and exhaust valves of internal combustion engines is known for example from DE 24 48 311 Al.
  • a spring-loaded in its closed position valve can be brought by means of an actuatable via a cam hydraulic piston assembly in an open position.
  • the piston assembly consists in this solution of a cam actuated by the drive piston and a valve engaging with the working piston, via which the valve is adjustable against the force of the valve spring in its opening direction.
  • the drive piston is with one of the Cam facing away end portion guided in a drive cylinder and limited with this a pressure chamber which is connected to the working space of the working piston for actuating the valve via a pressure line.
  • the drive piston also has an annular groove, which is connected via a transverse bore and a longitudinal bore in the drive piston with the pressure chamber of the drive cylinder.
  • annular groove of the drive piston In the region of the annular groove of the drive piston is guided in a likewise provided with an annular groove socket which is axially movable via a drive pinion relative to the drive piston.
  • the annular groove of the socket is connected via a flexible tank line with a tank and the pressure line and cooperates with the annular groove of the drive piston.
  • valve controls A disadvantage of such valve controls is that the opening times and closing times of the intake and exhaust valves are not independently adjustable, so that an optimization of the valve timing is not possible.
  • the performance can be significantly improved if the opening and closing times of the exhaust and intake valves are independently adjustable in dependence on other parameters, in particular of the engine speed.
  • the invention has the object, a valve control for reciprocating engines create, in which the opening and closing times of the valves are independently adjustable.
  • the valve control according to the invention uses a spring-loaded valve, which can be hydraulically brought into an open position by means of a piston arrangement which can be actuated via a cam.
  • the piston arrangement has an inlet control piston and an outlet control piston, each having an independently adjustable control edge, via which a pressure medium connection between a working space assigned to the valve and a pressure medium source and a control space and the pressure medium source or an outlet pressure space bounded by the outlet control piston and the pressure medium source. or is taxable.
  • the opening time of the valve is independent of the closing time adjustable over the prior art according to DE 24 48 311 Al, wherein a change in the valve opening timing by adjusting the control edge of the inlet control piston and a change of the valve closing timing by adjusting the control edge of the Auslenfin Kunststoffbens.
  • control pistons are rotatable about their longitudinal axis independently of each other, wherein the control edges are inclined relative to the longitudinal axis of the control piston. Due to the obliquely employed control edges, the control times are infinitely adjustable by a rotational movement of the control piston.
  • control piston and thus the valve timing adjustment is preferably carried out in each case via a gear wheel connected to the control piston, which rotatably but axially by the cam slidably engages in a rack or a drive gear.
  • the two control pistons are arranged axially one behind the other in a common valve housing.
  • a particularly compact design of the valve control is achieved.
  • control pistons are axially in contact or in engagement.
  • the piston assembly is biased against the cam via at least one spring so that the control pistons are in contact.
  • housing-fixed control edges are formed by pockets or holes.
  • an inlet pressure chamber of the inlet control piston and a working chamber of the valve via a pressure line and the inlet pressure chamber and the outlet pressure chamber via a respective supply line with a common, connected to the pressure medium source supply and return line is connected.
  • the inlet pressure chamber is connected via a longitudinal bore provided in the inlet control piston, which opens into a longitudinal bore of the outlet control piston, and a transverse bore of the outlet control piston is connected to the control chamber of the outlet control piston.
  • the longitudinal bores and the transverse bore are designed with a relatively small cross-section, so that the pressure medium flow from the control chamber of the Auslass Kunststoffkolbens back to the pressure medium source and thereby the closing speed of the valve is limited to prevent a hard impact of the valve on the valve seat.
  • the working chamber of the valve is connected via a return line to the outlet pressure chamber of the outlet control piston, wherein a switching valve is arranged in the return line.
  • a switching valve here is preferably a 2/2-way valve use.
  • a throttle In the supply line of the outlet pressure chamber of the Auslass Kunststoffkolbens is preferably arranged in this embodiment, a throttle. This throttle limits the pressure fluid flow from the outlet pressure chamber of the Auslass Kunststoffkolbens to the pressure medium source and thereby delays the closing speed of the valve to prevent a hard impact of the valve on the valve seat.
  • a check valve closing in the direction of the inlet pressure chamber is arranged in the pressure line between the inlet pressure chamber of the inlet control piston and the working chamber of the valve.
  • This check valve prevents a pressure medium flow of the working space of the valve to the inlet pressure space of the inlet control piston during the closing movement of the valve and thereby influencing the valve closing timing by the inlet control piston.
  • the supply line of the inlet pressure chamber is connected via a connecting line to the pressure line, wherein in the connecting line in the direction of inlet pressure chamber opening check valve is provided for sucking pressure medium from the pressure medium source.
  • a pressure medium source is preferably a pressure accumulator, for example, a bubble pressure accumulator use.
  • Figure 1 is a sectional view of a valve control according to the invention according to a first embodiment of the invention
  • Figure 2 is a sectional view of a valve control according to the invention according to a second embodiment of the invention.
  • FIG. 1 shows a first exemplary embodiment of a valve control 1 according to the invention for controlling a valve 2 of a reciprocating piston engine 4, for example an intake or exhaust valve of an internal combustion engine of a motor vehicle.
  • the valve 2 is guided via a valve stem 6 in a valve bore 8 of a cylinder head 10 of the reciprocating engine 4 and biased by a first end to a radial collar 12 of the valve stem 6 and a second end supported on the cylinder head 10 supported conical valve spring 14 in its closed position , In this closed position, a valve disk 16 of the valve 2 is brought into contact with a housing-fixed valve seat 18, so that the connection between the inlet and outlet ports 20 of the cylinder head 10 and a cylinder chamber 22 is closed.
  • the valve 2 can be hydraulically brought into an open position by means of a piston assembly 26 that can be actuated via a cam 24.
  • the piston assembly 26 has an inlet control piston 28 and an outlet control piston 30, each having an independently adjustable control edge 32 and 34, via a pressure medium connection between a valve 2 associated working space 36 and a pressure medium source 38 and a control chamber 40 of the Auslass Kunststoffkolbens 30 and the pressure medium source 38 is up or is zuu Kunststoffbar.
  • the valve control 1 are cooperating with the control edges 32, 34 housing-fixed control edges 42, 44 and 46, 48 formed by a respective pocket 50, 52 in the valve housing 54.
  • the control pistons 28, 30 are rotatable about a common longitudinal axis 56 independently of each other, wherein the control edges 32, 34 are inclined relative to the longitudinal axis 56.
  • control piston 28, 30 The adjustment of the control piston 28, 30 and thereby the valve timing adjustment takes place in each case via an external gear 58, 60 connected to the control piston 28, 30, with respect to the diameter of the control piston 28, 30 enlarged outer diameter, the rotationally fixed, but axially displaceable by the cam 24 engages a rack 62, 64 or a worm wheel.
  • the opening time of the valve 2 is independent of the closing time adjustable, wherein a change in the valve opening timing by adjusting the control edge 34 of the inlet control piston 28 and a change in the valve closing timing by adjusting the control edge 32 of the Auslunuzakolbens 30 so that an adaptation of the valve timing to various operating conditions, for example, depending on the engine speed of the reciprocating piston engine 4 and thereby an operation with optimum efficiency is possible.
  • the two control pistons 28, 30 are arranged axially one behind the other in the common valve housing 54 in the illustrated embodiment and axially, through a through hole 66 of the valve housing 54 through a radially recessed portion of the Auslenfin Kunststoffkolbens 30 or the inlet control piston 28 brought into abutment, wherein the piston assembly 26th via a cone-shaped spring 68, which merges with a first End is supported on a contact shoulder 70 of the valve housing 54 and with its second end to the radially enlarged outer gear 60 of the inlet control piston 28, is biased against the cam 24.
  • the two control pistons 28, 30 are biased against each other and against the cam 24, so that the piston assembly 26 follows the cam movement.
  • the inlet control piston 28 is guided in a lower cylinder bore 72 of the valve housing 54 and limited by a beveled, the control edge 34 forming end face an inlet pressure chamber 74 via a provided in the inlet control piston 28 longitudinal bore 76 which opens into a longitudinal bore 78 of the Auslraw confusekolbens 30 and via a Transverse bore 80 of the Auslraw askkolbens 30 with the control chamber 40 of the Auslass horrkolben 30 is connected.
  • the control chamber 40 is provided on the inlet valve 28 side facing with a control edge 32 forming inclined surface.
  • the outlet control piston 30 is guided in a cylinder bore 88 and defines an outlet pressure chamber 92 via an annular end face 90.
  • the inlet pressure chamber 74 and the working chamber 36 of the valve 2 can be connected to one another via a pressure line 82 and the pocket 52. Furthermore, the inlet pressure chamber 74 can be connected via a supply line 84 which opens into the pocket 52 and the control chamber 40 via a supply line 85 which opens into the pocket 50 to a supply and return line 86 connected to the pressure medium source 38.
  • the outlet pressure chamber 92 is connected via a supply line 94 to the supply and return line 86 connected to the pressure medium source 38.
  • a pressure medium source 38th In the embodiment shown, a low-pressure bubble storage is used.
  • valve control 1 the function of the valve control 1 will be explained by way of example with reference to FIG.
  • the piston assembly 26 is displaced downwardly by cam movement against the force of the spring 68 in FIG. 1, with the pocket 52 associated with the inlet control piston 28 being covered by the inlet control piston 28, ie the control edge 34 of the inlet control piston 28 is below the control edge 48 fixed to the housing.
  • Characterized the pressure medium in the inlet pressure chamber 74 is displaced via the pressure line 82 into the working chamber 36 of the valve 2 and this brought against the force of the valve spring 14 from its closed position shown in Figure 1 in its open position, so that the connection of the inlet and outlet channels 20th is turned on to the cylinder chamber 22.
  • FIG. 2 shows a second exemplary embodiment of a valve controller 1 according to the invention, in which both flank sides of the cam 24 are used for the movement of the piston assembly 26.
  • the piston arrangement 26 has an outlet control piston 100, which is embodied without longitudinal bore 78 in contrast to the outlet control piston 30 of the first embodiment, in a cylinder bore 110 the valve housing 54 is guided and limited with this via an obliquely attached, a control edge 104 forming end face an outlet pressure chamber 108.
  • the piston arrangement 26 furthermore has an inlet control piston 102 guided in the valve bore 72 and an inlet pressure chamber 114 bounded by an obliquely set end face forming a control edge 106, so that the control pistons 100, 102 each have a control edge 104 independently adjustable by means of the racks 62, 64 , 106, via which a pressure medium connection between the working space 36 of the valve 2 and the pressure medium memory 38 on the one hand and the limited by the Auslass whykolben 100 outlet pressure chamber 108 and the pressure medium accumulator 38 or is alsu mortbar.
  • the working space 36 of the valve 2 via a return line 98 and the pocket 50 with the outlet pressure chamber 108 is connectable, wherein in the Return line 98 is a magnetically actuated 2/2-way valve 99 is arranged with a blocking and a passage position.
  • the outlet pressure chamber 108 is connected via the supply line 94 to the supply and return line 86 connected to the pressure medium accumulator 38.
  • a throttle 112 is arranged, this limits the pressure fluid flow from the Auslrawdruckraum 108 to the pressure medium reservoir 38 and thereby reduces the closing speed of the valve 2, to prevent a hard impact of the valve 2 on the valve seat 18 ,
  • a check valve 116 closing in the direction of the inlet pressure chamber 114 is arranged. This prevents fluid flow from the working space 36 of the valve 2 to the inlet pressure chamber 114 of the inlet control piston 102 during the closing movement of the valve 2 and thereby the inlet control piston 102 becoming effective.
  • the supply line 84 of the inlet pressure chamber 114 connected to the supply and return line 86 is via a connection line 118 connected to the pressure line 82, wherein in the connecting line 118 in the direction of inlet pressure chamber 114 opening check valve 120 is provided for sucking pressure fluid from the accumulator 38.
  • the cam movement of the valve control 1 from FIG. 2 is represented by a curve 122 indicated by dashed lines and the valve movement by a curve 124 as a function of time as a function of the crank angle.
  • the function of the valve controller 1 according to the second exemplary embodiment is explained below by way of example with reference to FIGS. 2 and 3. Due to the cam movement, the piston assembly 26 is displaced downward against the force of the spring 68, wherein the connection from the inlet pressure chamber 114 to the pocket 52 is initially controlled by the control edge 106 of the inlet control piston 102, so that pressure medium from the inlet pressure chamber 114 to the pressure medium reservoir 38th is displaced and the valve 2 remains in its illustrated closed position (distance AB in Figure 3).
  • the switching valve 99 is closed, so that the pressure medium connection is shut off from the working space 36 of the valve 2 via the return line 98 and the pocket 50 to the outlet control valve 100.
  • the connection to the pocket 52 is controlled by the inlet control piston 102 (point B in FIG. 3) and displaces pressure medium from the inlet pressure chamber 114 via the pressure line 82 and the opening nonreturn valve 116 into the working chamber 36 of the valve 2 moved by the pressure building up against the force of the valve spring 14 from its illustrated closed position in the direction of its open position.
  • the pocket 50 is covered by the outlet control piston 100 with the control edge 104 of the outlet control piston 100 below the pocket 50 and the valve 2 is moved further towards its open position until the vertex of the cam is reached (point C in Figure 3).
  • the switching valve 99 is brought into its open position. Since the pressure medium connection to the pocket 50 is interrupted by the outlet control piston 100, a cost-effective switching valve be used with relatively slow switching time for the 2/2-way valve 99.
  • the check valve 120 arranged in the connecting line 118 acts as a suction valve via the pressure medium from the pressure medium accumulator 38 and the supply line 122 is sucked into the inlet pressure chamber 114 during the upward movement of the inlet control piston 102.
  • the 2/2-way valve is moved back to its closed position (distance ET in Figure 3) and the valve control cycle is completed.
  • valve control device 1 is not limited to the described drive of the control piston 28, 30, 100, 102 by means of racks 58, 60, but rather any known from the prior art drive means, in particular a worm or friction drive for driving the control piston 28, 30th , 100, 102 find use.
  • the piston arrangement 26 has an inlet control piston 28, 102 and an outlet control piston 30, 100 which each have an independently adjustable control edge 32, 34, 104, 106, via which a pressure medium connection between a working space 36 associated with the valve 2 and a pressure medium source 38 and a Control chamber 40 and the pressure medium source 38 or one of the Auslass capitakolben 100 limited outlet pressure chamber 108 and the pressure medium source 38 is up or is zuu mortbar.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

L'invention concerne une commande de soupape mécano-hydraulique pour machines à piston alternatif, notamment pour soupapes d'admission ou d'échappement de moteurs à combustion interne, comprenant une soupape à ressort qui peut être amenée hydrauliquement dans une position d'ouverture au moyen d'un arrangement à piston pouvant être actionné par le biais d'une came. Conformément à l'invention, l'arrangement de piston comprend un piston de commande d'admission et un piston de commande d'échappement qui présentent chacun un bord de commande pouvant être positionné indépendamment de l'autre, par le biais desquels peut être ouverte ou fermée une liaison de fluide sous pression entre un espace de travail associé à la soupape et une source de fluide sous pression ainsi qu'un espace de commande et la source de fluide sous pression ou un espace de pression d'échappement délimité par le piston de commande d'échappement et la source de fluide sous pression.
PCT/EP2007/001019 2006-04-04 2007-02-07 Commande de soupape Ceased WO2007118535A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006015720.6 2006-04-04
DE102006015720A DE102006015720A1 (de) 2006-04-04 2006-04-04 Ventilsteuerung

Publications (1)

Publication Number Publication Date
WO2007118535A1 true WO2007118535A1 (fr) 2007-10-25

Family

ID=38050279

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2007/001019 Ceased WO2007118535A1 (fr) 2006-04-04 2007-02-07 Commande de soupape

Country Status (2)

Country Link
DE (1) DE102006015720A1 (fr)
WO (1) WO2007118535A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107313828B (zh) * 2017-08-31 2023-05-23 吉林大学 一种电机控制式液压驱动可变气门机构
DK181628B1 (en) * 2022-01-31 2024-08-13 Troels Vollertsen Hydraulic valve lifter system and engine with it and method of operation thereof

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2011864A (en) * 1932-02-19 1935-08-20 Gen Motors Corp Pump
US2602434A (en) * 1947-03-29 1952-07-08 Worthington Pump & Mach Corp Hydraulic valve operating mechanism operable to vary valve lift and valve timing
US3683874A (en) * 1970-09-08 1972-08-15 Martin John Berlyn Valve actuating means
DE2448311A1 (de) * 1974-10-10 1976-04-22 Maschf Augsburg Nuernberg Ag Regelbare, hydraulische ventilsteuerung fuer hubkolbenmaschinen
US4112884A (en) * 1976-03-12 1978-09-12 Toyota Jidosha Kogyo Kabushiki Kaisha Valve lifter for internal combustion engine
DE2825316A1 (de) * 1978-06-09 1979-12-20 Maschf Augsburg Nuernberg Ag Regelbare hydraulische ventilsteuerung fuer hubkolbenkraft- oder arbeitsmaschinen
DE3048887A1 (de) * 1980-12-23 1982-07-22 Audi Nsu Auto Union Ag, 7107 Neckarsulm Steuerbarer ventiltrieb, insbesondere fuer die gaswechselventile einer hubkolben-brennkraftmaschine
DE3611476A1 (de) * 1986-04-05 1987-10-08 Irm Antriebstech Gmbh Verfahren zur betaetigung von ventilen zum ladungswechsel bei brennkraftmaschinen mit direkter hydraulischer uebertragung
JPH01100306A (ja) * 1987-10-13 1989-04-18 Ishikawajima Harima Heavy Ind Co Ltd 内燃機関の動弁装置
US5002022A (en) * 1989-08-30 1991-03-26 Cummins Engine Company, Inc. Valve control system with a variable timing hydraulic link
DE4221097A1 (de) * 1992-06-26 1994-01-05 Rexroth Mannesmann Gmbh Ventilsteuerung für ein Ventil einer Brennkraftmaschine
JPH0726926A (ja) * 1993-07-07 1995-01-27 Zexel Corp 内燃機関のバルブ制御装置
DE10155669A1 (de) * 2001-11-13 2003-05-22 Bosch Gmbh Robert Vorrichtung zur Steuerung mindestens eines Gaswechselventils

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2011864A (en) * 1932-02-19 1935-08-20 Gen Motors Corp Pump
US2602434A (en) * 1947-03-29 1952-07-08 Worthington Pump & Mach Corp Hydraulic valve operating mechanism operable to vary valve lift and valve timing
US3683874A (en) * 1970-09-08 1972-08-15 Martin John Berlyn Valve actuating means
DE2448311A1 (de) * 1974-10-10 1976-04-22 Maschf Augsburg Nuernberg Ag Regelbare, hydraulische ventilsteuerung fuer hubkolbenmaschinen
US4112884A (en) * 1976-03-12 1978-09-12 Toyota Jidosha Kogyo Kabushiki Kaisha Valve lifter for internal combustion engine
DE2825316A1 (de) * 1978-06-09 1979-12-20 Maschf Augsburg Nuernberg Ag Regelbare hydraulische ventilsteuerung fuer hubkolbenkraft- oder arbeitsmaschinen
DE3048887A1 (de) * 1980-12-23 1982-07-22 Audi Nsu Auto Union Ag, 7107 Neckarsulm Steuerbarer ventiltrieb, insbesondere fuer die gaswechselventile einer hubkolben-brennkraftmaschine
DE3611476A1 (de) * 1986-04-05 1987-10-08 Irm Antriebstech Gmbh Verfahren zur betaetigung von ventilen zum ladungswechsel bei brennkraftmaschinen mit direkter hydraulischer uebertragung
JPH01100306A (ja) * 1987-10-13 1989-04-18 Ishikawajima Harima Heavy Ind Co Ltd 内燃機関の動弁装置
US5002022A (en) * 1989-08-30 1991-03-26 Cummins Engine Company, Inc. Valve control system with a variable timing hydraulic link
DE4221097A1 (de) * 1992-06-26 1994-01-05 Rexroth Mannesmann Gmbh Ventilsteuerung für ein Ventil einer Brennkraftmaschine
JPH0726926A (ja) * 1993-07-07 1995-01-27 Zexel Corp 内燃機関のバルブ制御装置
DE10155669A1 (de) * 2001-11-13 2003-05-22 Bosch Gmbh Robert Vorrichtung zur Steuerung mindestens eines Gaswechselventils

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