EP0455761A1 - Dispositif de commande hydraulique de soupapes de moteurs a combustion interne. - Google Patents

Dispositif de commande hydraulique de soupapes de moteurs a combustion interne.

Info

Publication number
EP0455761A1
EP0455761A1 EP19900915296 EP90915296A EP0455761A1 EP 0455761 A1 EP0455761 A1 EP 0455761A1 EP 19900915296 EP19900915296 EP 19900915296 EP 90915296 A EP90915296 A EP 90915296A EP 0455761 A1 EP0455761 A1 EP 0455761A1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
control
piston
storage
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
EP19900915296
Other languages
German (de)
English (en)
Other versions
EP0455761B1 (fr
Inventor
Helmut Rembold
Ernst Linder
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 EP0455761A1 publication Critical patent/EP0455761A1/fr
Application granted granted Critical
Publication of EP0455761B1 publication Critical patent/EP0455761B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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 pressure line is controlled via a 3/2-way valve by, according to a special exemplary embodiment (FIGS. 8 and 9), the directional valve in one switch ⁇ position connects the pressure line with the pressure chamber of a valve tappet and in the other switching position with the pressure chamber of another valve tappet and this using only a single liquid reservoir for both pressure chambers.
  • One control position of the solenoid valve is used for two engine intake valves and only one accumulator is used for both intake valves.
  • valve control device with the characterizing features of the main claim has the advantage that a lower control pressure from the control line is sufficient to lift the accumulator piston from its valve seat. Since the control line is controlled by the solenoid valve, opening the solenoid valve in the delivery line, which is under low preliminary pressure, acts as a pressure surge of the control oil on the accumulator piston.
  • valve control edge of the accumulator valve is preferably the bottom edge of the accumulator piston, which cooperates with a fixed seat, so that in the rest or initial position of the accumulator piston, the pressure channel is delimited radially by the circumferential surface of the accumulator piston, while the accumulator space by Face of the storage piston is limited.
  • a slide control of this storage valve can of course also be provided, according to which the pressure channel is connected to the storage space only after a certain minimum path of the storage piston has been covered.
  • the individual valve control units are each only up to a drive of 180 ° via the electronic control unit Camshaft angle of rotation (° NW) controllable, so that several valve control units are controlled by only one solenoid valve, overlapping control times, that is to say switch-on times of the solenoid valve, above 180 ° NW per valve are prevented.
  • the control line is branched to the individual control units. The control periods of these control units therefore have no overlaps above 180 ° angle of rotation of the crankshaft (° KW) from the start of the control process of the respective control unit.
  • groups of valve control units can be controlled by a first division of the control line downstream of the solenoid valve by at least one pre-selection valve. This can be used particularly advantageously in engines with larger inlet closing angles.
  • the preselection valve is designed as a 3/2-way valve, two pressure chambers being controllable via a 3/2-way valve in connection with the control valve.
  • FIG. 1 shows a longitudinal section through the valve control device of an engine intake valve with the associated hydraulic circuit diagram
  • FIG. 2 shows a detail from FIG. 1 on an enlarged scale
  • Fig. 3 three stacked control diagrams of the opening movement of the valve
  • 4 and 5 show two variants of the hydraulic circuit diagram of FIG. 1
  • 6 shows a variant in the storage piston control with a corresponding and enlarged section from FIG. 1.
  • a hydraulic valve control device is shown in longitudinal section and as a hydraulic circuit diagram. This is arranged between a valve stem 2 carrying a valve plate and a drive cam 4 rotating with a camshaft 3.
  • the valve stem 2 is axially displaceably guided in a valve housing 5 and is loaded in the closing direction of the valve by valve closing springs 6 and 7, as a result of which the valve disk 1 is pressed onto a valve seat 8 in the valve housing 5.
  • the valve disk 1 controls a valve inlet opening 9 formed between it and the valve seat 8 when the valve is open.
  • the delivery line 31 leads to a 2/2 solenoid valve 34 which controls a control line 35 which leads to the storage space 26 via a check valve 36.
  • a supply pressure accumulator 37 is connected to the delivery line 31 shortly before the solenoid valve 34, the storage pressure of which is coordinated with the pressure control valve 33 and which is largely filled with control oil in the closed position of the solenoid valve 34 shown.
  • Additional control lines 38 branch off from the control line 35 and lead to further engine control valve units of the same engine, these units being designed in accordance with the one shown.
  • a filling line 39 branches off from the delivery line 31, which leads to the pressure channel 21 and in which a check valve 41 opening towards the pressure channel 21 is arranged.
  • a spring plate 44 of a weak spring 45 is tensioned by the storage spring 24 within the cup-shaped storage piston 23 onto the storage piston piston bottom, the spring 45 loading the movable valve member of a relief valve 46 which is in a relief line 47 is arranged, which connects the storage space 26 with the storage spring space 48.
  • the relief line 47 is designed here as a throttle line, so that it acts as a throttle for an outflow of control oil from the storage space 26 to the storage spring space 48.
  • the relief valve 46 can also be designed as a pressure control valve in order to maintain a certain admission pressure in the storage space 26.
  • the advantage is that the time at which the solenoid valve 34 opens the closing of the engine valve initiates, the further closing movement of the engine valve being effected by the valve closing springs 6 and 7 - apart from the pressures in the combustion chamber itself which act on the valve plate 1 - being determined by the evasion speed of the storage piston 23.
  • FIG. 3 shows three diagrams of the working stroke profile of the valve for three different speeds, which are shown one above the other.
  • the stroke of the motor valve h (ordinate) is shown as ⁇ KW (abscissa) over the degree of rotation of the crankshaft.
  • the first diagram a is for an engine speed of 1000 rpm; the second diagram b corresponds to a speed of 3000 rpm and the lowest diagram c applies to a speed of 5000 rpm.
  • the outer jacket curve in all three diagrams corresponds to the opening and closing process of the inlet valve without the influence of the interference via the solenoid valve 34.

Landscapes

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

Abstract

Un dispositif de commande hydraulique de soupapes utile pour moteurs à combustion interne à cylindres multiples comprend une chambre d'accumulation (26) reliée à la chambre de pression (19) du poussoir de soupape et pourvue d'un piston d'accumulation (23) qui sert en même temps de soupape et qui permet de séparer la chambre d'accumulation (26) de la chambre de pression (19). Le piston d'accumulation (23) est déplacé de sa position de repos pour assurer sa fonction d'accumulation au moyen d'une poussée hydraulique réglée par une électrovanne (34) et transmise à travers un conduit de commande (35), dans lequel est agencé un clapet de non-retour (36), jusqu'à la chambre d'accumulation (26). Le déplacement du piston d'accumulation (23) ne se produit que lorsque la soupape est actionnée par une came d'entraînement (4), assurant une pression de travail suffisante dans la chambre de pression (19) pour que le piston d'accumulation (23) puisse se déplacer.
EP90915296A 1989-11-25 1990-10-26 Dispositif de commande hydraulique de soupapes de moteurs a combustion interne Expired - Lifetime EP0455761B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3939065 1989-11-25
DE3939065A DE3939065A1 (de) 1989-11-25 1989-11-25 Hydraulische ventilsteuervorrichtung fuer brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0455761A1 true EP0455761A1 (fr) 1991-11-13
EP0455761B1 EP0455761B1 (fr) 1993-12-29

Family

ID=6394204

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90915296A Expired - Lifetime EP0455761B1 (fr) 1989-11-25 1990-10-26 Dispositif de commande hydraulique de soupapes de moteurs a combustion interne

Country Status (5)

Country Link
US (1) US5263441A (fr)
EP (1) EP0455761B1 (fr)
JP (1) JPH04502660A (fr)
DE (2) DE3939065A1 (fr)
WO (1) WO1991008385A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001027467A1 (fr) 1999-10-14 2001-04-19 Robert Bosch Gmbh Dispositif pour une montee en pression rapide dans un dispositif de vehicule automobile alimente en fluide sous pression par une pompe refoulante
WO2003018966A1 (fr) 2001-08-21 2003-03-06 Robert Bosch Gmbh Mecanisme de soupape comportant une section d'ouverture de soupape variable

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4101117A1 (de) * 1991-01-16 1992-07-23 Rexroth Mannesmann Gmbh Fremdkraftbetaetigtes, insbesondere elektrisch- bzw. magnetbetaetigtes wege-sitzventil
DE4206696C2 (de) * 1992-03-04 2000-12-14 Bosch Gmbh Robert Hydraulische Ventilsteuervorrichtung für Motorventile
US5373817A (en) * 1993-12-17 1994-12-20 Ford Motor Company Valve deactivation and adjustment system for electrohydraulic camless valvetrain
US5829397A (en) * 1995-08-08 1998-11-03 Diesel Engine Retarders, Inc. System and method for controlling the amount of lost motion between an engine valve and a valve actuation means
AUPN678395A0 (en) * 1995-11-23 1995-12-14 Mitchell, William Richard Hydraulically or pneumatically actuated electronically controlled automotive valve system
ITTO980060A1 (it) * 1998-01-23 1999-07-23 Fiat Ricerche Perfezionamenti ai motori a combustione intenra con valvole ad azionam ento variabile.
GB9906504D0 (en) * 1999-03-23 1999-05-12 Csa Performance Ltd Valve actuation means
US6135073A (en) * 1999-04-23 2000-10-24 Caterpillar Inc. Hydraulic check valve recuperation
ITTO20010270A1 (it) * 2001-03-23 2002-09-23 Fiat Ricerche Motore a combustione interna con sistema idraulico di azionamento variabile delle valvole e punteria a doppio stantuffo.
ITTO20010269A1 (it) * 2001-03-23 2002-09-23 Fiat Ricerche Motore a combustione interna, con sistema idraulico di azionamento variabile delle valvole, e mezzi di compensazione delle variazioni di vol
DE10140941A1 (de) 2001-08-21 2003-03-20 Bosch Gmbh Robert Ventilmechanismus mit einem variablen Ventilöffnungsquerschnitt
DE10140919A1 (de) 2001-08-21 2003-03-20 Bosch Gmbh Robert Ventilmechanismus mit einem variablen Ventilöffnungsquerschnitt
LU90889B1 (en) * 2002-02-04 2003-08-05 Delphi Tech Inc Hydraulicv control system for a gas exchange valve of an internal combustion engine
DE10231143B4 (de) * 2002-07-10 2004-08-12 Siemens Ag Verfahren zum Steuern des Ventilhubes von diskret verstellbaren Einlassventilen einer Mehrzylinder-Brennkraftmaschine
JP2004197588A (ja) * 2002-12-17 2004-07-15 Mitsubishi Motors Corp 内燃機関の動弁装置
FI117348B (fi) * 2004-02-24 2006-09-15 Taimo Tapio Stenman Hydraulinen laitejärjestely polttomoottorin venttiilien toiminnan ohjaamiseksi
DE102010018209A1 (de) * 2010-04-26 2011-10-27 Schaeffler Technologies Gmbh & Co. Kg Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb
KR20120017982A (ko) * 2010-08-20 2012-02-29 현대자동차주식회사 전기-유압 가변 밸브 리프트 장치
JP6003439B2 (ja) * 2012-09-18 2016-10-05 アイシン精機株式会社 弁開閉時期制御装置
SE540359C2 (sv) * 2013-10-16 2018-08-07 Freevalve Ab Förbränningsmotor

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3135650A1 (de) * 1981-09-09 1983-03-17 Robert Bosch Gmbh, 7000 Stuttgart "ventilsteuerung fuer hubkolben-brennkraftmaschinen mit mechanisch-hydraulischen bewegungsuebertragungsmitteln"
JPH0612058B2 (ja) * 1984-12-27 1994-02-16 トヨタ自動車株式会社 可変バルブタイミング・リフト装置
DE3511819A1 (de) * 1985-03-30 1986-10-09 Robert Bosch Gmbh, 7000 Stuttgart Ventilsteuervorrichtung
DE3511820A1 (de) * 1985-03-30 1986-10-02 Robert Bosch Gmbh, 7000 Stuttgart Ventilsteuervorrichtung fuer eine hubkolben-brennkraftmaschine
DE3532549A1 (de) * 1985-09-12 1987-03-19 Bosch Gmbh Robert Ventilsteuervorrichtung
DE3815668A1 (de) * 1988-05-07 1989-11-16 Bosch Gmbh Robert Ventilsteuervorrichtung mit magnetventil fuer brennkraftmaschinen
US4930465A (en) * 1989-10-03 1990-06-05 Siemens-Bendix Automotive Electronics L.P. Solenoid control of engine valves with accumulator pressure recovery

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9108385A1 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001027467A1 (fr) 1999-10-14 2001-04-19 Robert Bosch Gmbh Dispositif pour une montee en pression rapide dans un dispositif de vehicule automobile alimente en fluide sous pression par une pompe refoulante
WO2003018966A1 (fr) 2001-08-21 2003-03-06 Robert Bosch Gmbh Mecanisme de soupape comportant une section d'ouverture de soupape variable

Also Published As

Publication number Publication date
JPH04502660A (ja) 1992-05-14
EP0455761B1 (fr) 1993-12-29
WO1991008385A1 (fr) 1991-06-13
DE3939065A1 (de) 1991-05-29
US5263441A (en) 1993-11-23
DE59004044D1 (de) 1994-02-10

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