EP0255668B1 - Dispositif pour la commande hydraulique de soupapes - Google Patents

Dispositif pour la commande hydraulique de soupapes Download PDF

Info

Publication number
EP0255668B1
EP0255668B1 EP87110729A EP87110729A EP0255668B1 EP 0255668 B1 EP0255668 B1 EP 0255668B1 EP 87110729 A EP87110729 A EP 87110729A EP 87110729 A EP87110729 A EP 87110729A EP 0255668 B1 EP0255668 B1 EP 0255668B1
Authority
EP
European Patent Office
Prior art keywords
working piston
hydraulic chamber
valve
hydraulic
brake element
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 - Lifetime
Application number
EP87110729A
Other languages
German (de)
English (en)
Other versions
EP0255668A3 (en
EP0255668A2 (fr
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 EP0255668A2 publication Critical patent/EP0255668A2/fr
Publication of EP0255668A3 publication Critical patent/EP0255668A3/de
Application granted granted Critical
Publication of EP0255668B1 publication Critical patent/EP0255668B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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

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 when the valve was suddenly placed 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 acts on the valve itself, which, as soon as the volume of the working area 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 area Initiates valve closing movement.
  • the hydraulic fluid thus displaced by the working piston flows towards the end of the closing movement on its way into the working space via a damping gap.
  • This damping gap is formed by an attachment on the working piston and the cylinder wall surrounding the working piston.
  • this arrangement shows a device for hydraulic length compensation. This is particularly the case if the profile of the attachment on the working piston and / or the cylinder wall area interacting with it during gap formation ensures that the gap width changes according to a predetermined function during the valve closing movement, i.e. that the damping does not remain constant, must be ensured be that, despite operational or wear-related dimensional changes in the area of the valve, the association between the described gap function on the one hand and certain movement phases of the valve closing movement on the other hand is maintained.
  • auxiliary piston which is movably mounted in the working piston, which is partially hollow, and which can be displaced in its longitudinal axis acts on the valve stem.
  • a targeted leakage must be provided between the auxiliary piston and the working piston.
  • the resulting pressure loss in the hydraulic system must always be compensated for with a deterioration in efficiency.
  • this arrangement leads to a valve opening movement that can no longer be precisely determined, because depending on the hydraulic pressure in the working space and in the working chamber, the auxiliary piston is moved once, which leads to rapid valve movement because of the small piston cross section, and at other times it becomes - much slower - the other the piston is significantly larger in cross section.
  • the object of the invention is to provide a simple device for the hydraulic control of globe valves, which ensures a precisely definable braking of the valve closing movement, also taking into account operational or wear-related dimensional changes in the area of the valve.
  • a movable connection of the brake 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 develop in such a way that there is a balance of forces between the force storage elements and the hydraulic pressure.
  • the device according to the invention has the advantage that the valve opening movement is transmitted in a precisely definable manner by the rigid coupling between the valve and the working piston. B. by the length compensation element from the above. scripture does not occur here.
  • Claim 3 describes a simple, constructive design of the brake element and working piston.
  • Claim 5 deals with an advantageous embodiment of the counter surface forming the throttle gap together with the braking element. If, for this purpose, a throttle disc movably mounted outside the working piston and supported at at least two stops is provided, an additional damping gap can be formed between the throttle disc and a wall of the device with a corresponding shape, thus creating a second hydraulic working space. As a result, a significantly larger filling cross section is released during the filling phase of the hydraulic space.
  • the braking process is now subdivided into a pre-braking phase, in which the throttle disc - advantageously almost independently of the viscosity of the hydraulic medium - is moved against one of the stops, and a subsequent, reinforced final braking phase.
  • the throttle disc is also provided with breakthroughs outside the damping gap area, the filling of the hydraulic chamber and of the hydraulic space located between the disc and the braking element takes place again during the valve opening movement, so that a desired rapid valve opening movement is made possible.
  • a throttle bore connecting the hydraulic chamber in the interior of the brake element with the partial hydraulic chamber located between the throttle disc and the working piston avoids undesirably strong oscillating movements of the braking element in the working piston. Such oscillating movements are dampened in terms of intensity by partial overflow of hydraulic medium between the two hydraulic spaces mentioned.
  • Claim 8 describes a leakage hole provided in the working piston, via which a subset of the hydraulic medium located in the hydraulic chamber is discharged as a function of the forces acting on the braking element.
  • the discharge takes place in a room which is not pressurized by the pressure of the hydraulic medium in order to avoid the risk of vapor bubbles forming in the hydraulic room - caused by high flow velocities.
  • the inlet mouth of that leakage bore is advantageously disclosed when the forces acting on the brake element from the outside assume very high values, in particular when the brake element is in contact with the walls forming the damping gap.
  • a cam 1 acts on a drive piston 2, which actuates an axially displaceable working piston 43 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 opening 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 or on its upper stop 15 formed by the housing 12.
  • the throttle disc 13 is provided with openings 16 and divides the hydraulic space 3 into two annular 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 disc 13 and braking element 8) or the damping gap 20 (formed of the throttle plate 13 and its upper stop 15) are connected to the hydraulic chamber 3.
  • a connection between the hydraulic chamber 10 and the partial hydraulic chamber 18 is established via a throttle bore 23 in the braking element 8.
  • 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 disc 13 rests on the hollow cylinder 14 forming its lower stop. 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 21 - 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 disc 13 moves in the direction of its upper stop 15.
  • FIG. 5 A modified form of the working piston 4 and of the braking element 10 is shown in FIG. 5.
  • a leakage bore 24 is provided in the sleeve 5, the inlet opening 25 of which is closed by a collar 26 of the brake element 10 in the position of the brake element shown in FIG. 5. If, at the end of the braking process, the rounded upper end of the braking element 10 rests on the throttle disk 13 and this on its upper stop 15, then a further upward movement of the working piston 4 opens the inlet opening 25 of the leakage bore 24, as a result of which part of the one located in the hydraulic chamber 10 Hydraulic fluid is discharged. That leakage bore 24 is absolutely necessary in the embodiment of the brake element 10 shown here, which, in contrast to the brake element shown in FIG.
  • That lacquer bore 24 also offers advantages if, as not shown, the throttle opening 11 shown in FIG. 4 is provided on the brake element 10 in addition to the throttle bore 23. Since that throttle opening 11 must have a very narrow cross-section for functional reasons, sufficient emptying of the hydraulic chamber 10 during the valve closing movement could be called into question in exceptional cases. The result would be a so-called inflation of the braking element 8 or the hydraulic chamber 10; the desired braking function would then no longer be ensured. In those cases, a corresponding subset of hydraulic fluid can be discharged via the leakage hole 24 that then opens.
  • the present invention of the earth is not limited to the exemplary embodiment shown. Rather, what is essential is the general idea of the invention, according to which the working piston is provided with a blind hole, in which a braking element, which is supported by an energy accumulator on the working piston, is formed and forms one of the surfaces of the damping gap in order to brake the valve closing movement in a definable manner, also taking operational or wear-related factors into account To ensure dimensional changes in the area of the valve.

Landscapes

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

Claims (8)

1. Dispositif pour la commande hydraulique de soupapes sur des moteurs à piston dans lequel le mouvement d'ouverture est transmis par un espace hydraulique (3) et un piston de travail (4) directement sur la soupape (7) et le mouvement de fermeture est déclenché par un élément accumulateur d'énergie (22) agissant sur la soupape (7), dans lequel pour le liquide repoussé par le piston de travail (4) est prévue une fente d'amortissement (19), formée par le piston de travail (4) et une paroi fixe (15) de l'espace hydraulique (3), caractérisé en ce que le piston de travail (4) est muni d'un logement à fond plein, dans lequel est guidé un élément de freinage (8) s'appuyant sur le piston de travail (4) par un accumulateur d'énergie (9) coulissant dans le sens de déplacement du piston de travail et constituant une des surfaces de la fente d'amortissement (19).
2. Dispositif selon la revendication 1, caractérisé en ce que l'élément de freinage (8) dans la zone de la fente d'amortissement (19) et/ou la surface opposée (13) concourant à la formation de la fente d'amortissement comportent un profil divergent de la forme cylindrique.
3. Dispositif selon une des revendications 1 ou 2, caractérisé en ce que l'élément de freinage (8) est pour l'essentiel de forme cylindrique.
4. Dispositif selon l'une des revendications précédentes, caractérisé en ce que l'élément de freinage (8) est réalisé creux et forme avec le logement à fond plein une chambre hydraulique (10) qui est en communication avec l'espace hydraulique (3) par au moins une ouverture d'étranglement (11).
5. Dispositif selon l'une des revendications précédentes, caractérisé en ce que l'élément formant la contre-surface opérante est réalisé comme anneau d'étranglement (13) logé mobile à l'extérieur du piston de travail (4) et pouvant s'appuyer sur des butées.
6. Dispositif selon la revendication 5, caractérisé en ce que la surface de l'anneau d'étranglement (13), en dehors de la zone de la fente d'amortissement, est munie de trous perforés (16).
7. Dispositif selon l'une des revendications précédentes, caractérisé en ce que dans l'élément de freinage (8) réalisé creux est prévu un alésage d'étranglement (23) qui met en communication la chambre hydraulique (10) avec l'espace hydraulique partiel (18) formé par le piston de travail (4) et par l'anneau d'étranglement (13).
8. Dispositif selon l'une des revendications précédentes, caractérisé en ce qu'est prévu un alésage de fuite (2) provenant du logement à fond plein dont l'orifice de sortie se trouve sur un côté du piston de travail (4) opposé à l'espace hydraulique (3) et dont l'orifice d'entrée (25) est découvert ou obstrué par l'élément de freinage (8) en fonction des forces agissant sur lui.
EP87110729A 1986-07-29 1987-07-24 Dispositif pour la commande hydraulique de soupapes Expired - Lifetime EP0255668B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3625652 1986-07-29
DE3625652 1986-07-29

Publications (3)

Publication Number Publication Date
EP0255668A2 EP0255668A2 (fr) 1988-02-10
EP0255668A3 EP0255668A3 (en) 1988-03-23
EP0255668B1 true EP0255668B1 (fr) 1990-01-03

Family

ID=6306228

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87110729A Expired - Lifetime EP0255668B1 (fr) 1986-07-29 1987-07-24 Dispositif pour la commande hydraulique de soupapes

Country Status (3)

Country Link
EP (1) EP0255668B1 (fr)
DE (1) DE3761320D1 (fr)
ES (1) ES2012474B3 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH01134018A (ja) * 1987-11-19 1989-05-26 Honda Motor Co Ltd 内燃機関の動弁装置
DE3833459A1 (de) * 1988-10-01 1990-04-05 Audi Ag Hydraulischer ventiltrieb fuer eine brennkraftmaschine
AT410696B (de) * 1999-09-22 2003-06-25 Jenbacher Ag Ventilantrieb für ein ventil eines verbrennungsmotors
DE102006012067B4 (de) * 2006-03-16 2016-03-24 Volkswagen Ag Hydraulische Ventilbetätigungsvorrichtung für ein Gaswechselventil
DE102016219227A1 (de) * 2016-10-05 2018-04-05 Schaeffler Technologies AG & Co. KG Gaswechselventiltrieb mit einem an einem Druckraum über eine Drossel angeschlossenen Dämpferraum
DE102017113783A1 (de) 2017-06-21 2018-12-27 Man Truck & Bus Ag Kraftübertragungsvorrichtung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH243908A (de) * 1944-11-27 1946-08-15 Schweizerische Lokomotiv Flüssigkeitsbremse mit Rückschlagventil am Passivkolben von hydraulisch gesteuerten Ventilen von Brennkraftmaschinen.
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
ES2012474B3 (es) 1990-04-01
EP0255668A3 (en) 1988-03-23
EP0255668A2 (fr) 1988-02-10
DE3761320D1 (de) 1990-02-08

Similar Documents

Publication Publication Date Title
EP0400395B1 (fr) Amortisseur de choc
EP0484648B1 (fr) Butée avec dispositif d'amortissement
DE4409252C2 (de) Luftfederungsanlage
EP3314145B1 (fr) Agencement de soupape d'amortissement dépendant de la fréquence
EP0565982B1 (fr) Agencement de soupape
EP1180599A1 (fr) Dispositif de sécurité pour une pompe pouvant être utilisée dans une transmission à fluide
DE2121775C3 (fr)
DE10203886B4 (de) Vorsteuerventil
EP0325958A1 (fr) Clapet à commande hydraulique
DE4190781C2 (de) Hydraulischer Schwingungsdämpfer für ein Kraftfahrzeug
LU88558A1 (de) Vorgesteuertes Servoventil
EP0667459A1 (fr) Unité de soupape à électro-aimant proportionnel
EP0255668B1 (fr) Dispositif pour la commande hydraulique de soupapes
AT410696B (de) Ventilantrieb für ein ventil eines verbrennungsmotors
WO1994004829A1 (fr) Dispositif de commande hydraulique
DE4032078C2 (de) Steuervorrichtung für einen hydraulischen Arbeitszylinder
EP0976948B1 (fr) Dispositif d'amortissement de masses déplacées, en particulier pour systèmes moteurs électromagnétiques
EP0254967B1 (fr) Dispositif pour la commande hydraulique de soupapes
DE3234520A1 (de) Spindelpresse
DE3207995C2 (de) Ventil für das Umsteuern der Kolbenbewegung einer hydraulischen Zylinder-Kolbeneinheit
DE19622948A1 (de) Manuell betätigbares hydraulisches Vorsteuergerät
EP1182374B1 (fr) Amortisseur réglable pour véhicules automobiles, et méthode de réglage d'un amortisseur
EP1105651A1 (fr) Verin hydraulique
DE2508268C3 (de) Steuerkolben fur hydraulische Druckmittelfolgesteuerungen, insbesondere für ein Lenkventil einer Servolenkeinrichtung von Fahrzeugen
DE1290778B (de) Elektromagnetisch betaetigtes Hydraulikventil

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE ES FR GB IT SE

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE ES FR GB IT SE

17P Request for examination filed

Effective date: 19880415

17Q First examination report despatched

Effective date: 19890215

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT SE

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
REF Corresponds to:

Ref document number: 3761320

Country of ref document: DE

Date of ref document: 19900208

ET Fr: translation filed
ITF It: translation for a ep patent filed

Owner name: STUDIO JAUMANN

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19910704

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: ES

Payment date: 19910717

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 19910724

Year of fee payment: 5

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19910730

Year of fee payment: 5

ITTA It: last paid annual fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19920724

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19920725

Ref country code: ES

Free format text: LAPSE BECAUSE OF THE APPLICANT RENOUNCES

Effective date: 19920725

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 19920724

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19930331

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 19930703

Year of fee payment: 7

EUG Se: european patent has lapsed

Ref document number: 87110729.8

Effective date: 19930204

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Effective date: 19950401

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 19991007

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20050724