EP0254967B1 - Dispositif pour la commande hydraulique de soupapes - Google Patents

Dispositif pour la commande hydraulique de soupapes Download PDF

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Publication number
EP0254967B1
EP0254967B1 EP87110247A EP87110247A EP0254967B1 EP 0254967 B1 EP0254967 B1 EP 0254967B1 EP 87110247 A EP87110247 A EP 87110247A EP 87110247 A EP87110247 A EP 87110247A EP 0254967 B1 EP0254967 B1 EP 0254967B1
Authority
EP
European Patent Office
Prior art keywords
orifice plate
working piston
valve
damping
throttle
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.)
Expired
Application number
EP87110247A
Other languages
German (de)
English (en)
Other versions
EP0254967A2 (fr
EP0254967A3 (en
Inventor
Jurij Gartner
Peter Langen
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.)
Bayerische Motoren Werke AG
Original Assignee
Bayerische Motoren Werke 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 Bayerische Motoren Werke AG filed Critical Bayerische Motoren Werke AG
Publication of EP0254967A2 publication Critical patent/EP0254967A2/fr
Publication of EP0254967A3 publication Critical patent/EP0254967A3/de
Application granted granted Critical
Publication of EP0254967B1 publication Critical patent/EP0254967B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/16—Silencing impact; Reducing wear
    • 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
    • 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 device of the type specified in the preamble of the first claim.
  • Freely controllable hydraulic devices for influencing the course of the valve stroke are sufficiently known in principle. In some cases, only the maximum valve lift can be regulated, or it is possible to additionally influence the rising or falling flank of the valve lift curve. If the falling flank is influenced, the sudden change in the valve speed, which would occur if the valve abruptly touched down on the valve seat ring, must be avoided by interposing a simple hydraulic braking device; the valve speed is continuously throttled until the valve is finally put on.
  • Such a generic arrangement is known for example from DE-OS 35 37 630.
  • a drive piston actuated by a cam acts on a working piston assigned to the valve via a hydraulic working space.
  • a valve spring engages the valve itself, which initiates the valve closing movement as soon as the volume of the working space is increased - be it by the cam-controlled backward movement of the drive piston or by targeted control of the valve lift, i.e. a freely controllable discharge of the hydraulic fluid from the working space .
  • the hydraulic fluid thereby displaced by the working piston flows towards the end of the closing movement on its way into the working space via a throttle gap.
  • This throttle gap is formed by an attachment on the working piston and the cylinder wall surrounding the working piston.
  • a disadvantage of this arrangement is the extremely strong braking towards the end of the valve closing process.
  • the valve closing movement triggered by the valve spring is initially strongly accelerated, and then abruptly braked as soon as the throttle gap opposes a clear resistance to the flowing hydraulic medium. Then the hydraulic fluid passes the throttle gap at high speed for the first time, so that there is a risk of vapor bubble formation and cavitation damage.
  • the system is then subjected to high forces, since large amounts of energy have to be destroyed. As a result, the entire system can be subjected to excessive mechanical loads.
  • the throttle gap in the generic arrangement is designed in such a way that it has a cross section narrowing towards the end of the valve closing movement, the initial braking action of the throttle gap begins too abruptly during the valve closing movement.
  • the object of the invention is therefore to provide a simple device for the hydraulic control of globe valves, in which the valve closing movement is initially slowed down and only decelerated towards the end of the braking phase.
  • Claim 3 describes a simple design of the throttle disc to ensure that the damping gap cross-sections narrow continuously in the course of the valve closing movement.
  • the throttle disk as described in claim 4, is also provided with openings outside of the damping gap area, the filling of the partial hydraulic space between the throttle disk and the working piston takes place significantly accelerated during the valve opening movement, so that a desired rapid valve opening movement is made possible.
  • Claim 5 describes an advantageous embodiment of the working piston.
  • a movable connection of a braking element forming the damping gap to the working piston that transmits the valve movement ensures a constant braking effect regardless of length tolerances, because the damping gap will always be formed in such a way that there is a balance of forces between the force storage elements and the hydraulic pressure.
  • a cam 1 acts on a drive piston 2, which actuates an axially displaceable working piston 4 via a hydraulic chamber 3.
  • This consists of a sleeve 5 and an end plate 6, which rests on the free end of a valve stem 7 of a valve, not shown.
  • An essentially cylindrical brake element 8 is mounted in the interior of the sleeve 5 so as to be longitudinally displaceable and is supported on the end plate 6 by a spring 9.
  • the hydraulic chamber 10 formed in the interior of the braking element 8 is connected to the hydraulic working space 3 via a throttle bore 11 in the braking element 8.
  • a throttle disk 13 movably mounted in the housing 12 of the device is supported either on the hollow cylinder 14 screwed into the housing 12 and forming the raceway for the sleeve 5 (stop 23) or on its upper stop 15 formed by the housing 12.
  • the throttle disc 13 has a central opening 24 and a circumferential collar 25 and is provided with openings 16. It divides the hydraulic space 3 into two ring-shaped partial hydraulic spaces 17 and 18, which are connected to one another via the openings 16 and via the damping gap 19 (formed by throttle disk 13 and braking element 8) or the damping gap 20 (formed by throttle disk 13 and its upper stop) 15) are connected to the hydraulic room 3.
  • a part of the hydraulic volume located in the hydraulic space 3 can be discharged via a control valve 21.
  • a valve spring 22 acts on the valve stem 7 of the lift valve in a known manner.
  • the throttle disk 13 During the valve opening movement, the throttle disk 13, as shown in FIG. 3, rests on its lower stop 23. Due to the pressure applied by the drive piston 2 in the hydraulic chamber 3 and in the hydraulic chamber 10, the working piston 4 moves downward and the lift valve is opened. If the hydraulic chamber 3 is now enlarged - be it by the upward movement of the drive piston 2 or by opening the control valve 16 - the force of the valve spring 22 causes the valve to close, the valve stem 7 presses the working piston 4 upward and the hydraulic fluid flows out of the partial hydraulic chamber 18 via the damping gap 19 and the openings 16 and the damping gap 20. In this pre-braking phase, the throttle disk 13 moves in the direction of its upper stop 15.

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

Claims (6)

1. Dispositif de commande hydraulique de soupapes sur des moteurs à pistons, où le mouvement d'ouverture est transmis par une chambre hydraulique et un piston de travail et où le mouvement de fermeture est déclenché par un élément accumulateur d'énergie agissant sur la soupape, où pour le liquide s'écoulant en outre du piston de travail est prévu une fente d'étranglement formée par le piston de travail et une paroi fixe de la chambre hydraulique, caractérisé en ce qu'un disque d'étranglement (13) est prévu dans la chambre hydraulique (3) mobile entre une butée de carter fixe (15) et une butée (23), qui divise la fente d'étranglement en une première fente d'amortissement (19) formée entre le disque d'étranglement (13) et le piston de travail (4) et une seconde fente d'amortissement (20) formée entre le disque d'étranglement (13) et la butée de carter (15).
2. Dispositif selon la revendication 1, caractérisé en ce que les deux fentes d'amortissement (19) et (20) se différenciant par le mouvement du disque d'étranglement (13) et/ou du piston de travail (4) présentent une section transversale particulièrement rétrécie.
3. Dispositif selon la revendication 1 ou 2, caractérisé en ce que le disque d'étranglement (13) comporte autour de son ouverture médiane (24) un collet (25) périphérique disposé angulairement contre le plan du disque qui forme pour l'essentiel les fentes d'amortissement (19) et (20).
4. Dispositif selon l'une des revendications 1 à 3, caractérisé en ce que la surface du disque d'étranglement (13) est munie de trous (16) en dehors de la zone des fentes d'amortissement.
5. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce que le piston de travail (4) comporte un trou borgne dans lequel est supporté, de façon à pouvoir se déplacer axialement, un élément de freinage (8) de forme pratiquement cylindrique appliqué par un accumulateur d'énergie sur le piston de travail (4) dont l'extrémité libre conformée de façon arrondie forme avec le disque d'étranglement (13) la fente d'amortissement (19).
6. Dispositif selon la revendication 5, caractérisé en ce que d'élément de freinage (8) est réalisé creux et réalise une communication par au moins une ouverture d'étranglement (11) entre le trou borgne et la chambre hydraulique (3).
EP87110247A 1986-07-29 1987-07-16 Dispositif pour la commande hydraulique de soupapes Expired EP0254967B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3625627 1986-07-29
DE19863625627 DE3625627A1 (de) 1986-07-29 1986-07-29 Vorrichtung zur hydraulischen steuerung von hubventilen

Publications (3)

Publication Number Publication Date
EP0254967A2 EP0254967A2 (fr) 1988-02-03
EP0254967A3 EP0254967A3 (en) 1988-03-30
EP0254967B1 true EP0254967B1 (fr) 1989-11-08

Family

ID=6306210

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87110247A Expired EP0254967B1 (fr) 1986-07-29 1987-07-16 Dispositif pour la commande hydraulique de soupapes

Country Status (3)

Country Link
EP (1) EP0254967B1 (fr)
DE (2) DE3625627A1 (fr)
ES (1) ES2011471B3 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4027630C1 (fr) * 1990-08-31 1991-12-05 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart, De
US5275136A (en) * 1991-06-24 1994-01-04 Ford Motor Company Variable engine valve control system with hydraulic damper
US5216988A (en) * 1992-10-15 1993-06-08 Siemens Automotive L.P. Dual bucket hydraulic actuator
EP1232336A4 (fr) * 1999-09-17 2009-08-05 Diesel Engine Retarders Inc Accumulateur a volume captif pour systeme a perte de mouvement

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE751538C (de) * 1943-03-03 1952-11-04 Kloeckner Humboldt Deutz Ag Druckfluessigkeitsantrieb, insbesondere fuer Ventile an Brennkraftmaschinen
CH243908A (de) * 1944-11-27 1946-08-15 Schweizerische Lokomotiv Flüssigkeitsbremse mit Rückschlagventil am Passivkolben von hydraulisch gesteuerten Ventilen von Brennkraftmaschinen.
JPS59229011A (ja) * 1983-06-08 1984-12-22 Yanmar Diesel Engine Co Ltd 内燃機関の動弁機構
JPS6193214A (ja) * 1984-10-12 1986-05-12 Sumitomo Heavy Ind Ltd 油圧式排気弁開閉装置
DE3537630A1 (de) * 1984-10-31 1986-04-30 Volkswagen AG, 3180 Wolfsburg Ventilanordnung, insbesondere fuer eine brennkraftmaschine
DE3511819A1 (de) * 1985-03-30 1986-10-09 Robert Bosch Gmbh, 7000 Stuttgart Ventilsteuervorrichtung

Also Published As

Publication number Publication date
DE3760968D1 (en) 1989-12-14
DE3625627C2 (fr) 1988-06-23
ES2011471B3 (es) 1990-01-16
EP0254967A2 (fr) 1988-02-03
EP0254967A3 (en) 1988-03-30
DE3625627A1 (de) 1988-02-04

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