EP0255668A2 - Dispositif pour la commande hydraulique de soupapes - Google Patents

Dispositif pour la commande hydraulique de soupapes Download PDF

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Publication number
EP0255668A2
EP0255668A2 EP87110729A EP87110729A EP0255668A2 EP 0255668 A2 EP0255668 A2 EP 0255668A2 EP 87110729 A EP87110729 A EP 87110729A EP 87110729 A EP87110729 A EP 87110729A EP 0255668 A2 EP0255668 A2 EP 0255668A2
Authority
EP
European Patent Office
Prior art keywords
working piston
hydraulic chamber
valve
hydraulic
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.)
Granted
Application number
EP87110729A
Other languages
German (de)
English (en)
Other versions
EP0255668B1 (fr
EP0255668A3 (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 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

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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

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 acts on the valve itself, which initiates the valve closing movement as soon as the volume of the work 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 work space .
  • the thereby from Hydraulic fluid 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 important 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 partly hollow, and which can be displaced in its longitudinal axis acts on the valve stem.
  • this arrangement has several disadvantages: On the one hand, 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. Furthermore, 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, because of the small piston cross section, leads to rapid valve actuation movement leads, another time - much slower - the working piston, which is significantly larger in cross-section, is advanced.
  • 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 document does not occur.
  • 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 disk - advantageously almost independent of the viscosity of the hydraulic medium - is moved against one of the stops, and into a subsequent, intensified final braking phase.
  • the throttle disc is also provided with breakthroughs outside the damping gap area, the hydraulic chamber and the one located between the disc and the braking element are filled during the valve opening movement Lichen hydraulic space accelerated again, so that a desired quick 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 Lec kagbohrung provided in the working piston, via which a subset of the hydraulic medium located in the hydraulic chamber is discharged depending on 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, that is to say in particular when the brake element bears against 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 disc 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 the throttle disc 13 and braking element 8) or the damping gap 20 (formed of the throttle disc 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 via a throttle bore 23 in the braking element 8 produced.
  • 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 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, in exceptional cases sufficient emptying of the hydraulic chamber 10 during the valve closing movement could be called into question. 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 and which forms one of the surfaces of the damping gap by a definable one is guided To ensure braking of the valve closing movement taking into account operational or wear-related 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)
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 true EP0255668A2 (fr) 1988-02-10
EP0255668A3 EP0255668A3 (en) 1988-03-23
EP0255668B1 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)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0317371A1 (fr) * 1987-11-19 1989-05-24 Honda Giken Kogyo Kabushiki Kaisha Dispositif de commande de soupape pour moteur à combustion interne
DE3833459A1 (de) * 1988-10-01 1990-04-05 Audi Ag Hydraulischer ventiltrieb fuer eine brennkraftmaschine
US6382147B1 (en) 1999-09-22 2002-05-07 Jenbacher Aktiengesellschaft Valve drive for a valve of an internal combustion engine
DE102006012067A1 (de) * 2006-03-16 2007-09-20 Volkswagen Ag Hydraulische Ventilbetätigungsvorrichtung für ein Gaswechselventil
WO2018065011A1 (fr) * 2016-10-05 2018-04-12 Schaeffler Technologies AG & Co. KG Soupape d'échange des gaz hydraulique dotée d'un compartiment d'amortissement raccordé à un compartiment de compression par un étranglement
DE102017113783A1 (de) 2017-06-21 2018-12-27 Man Truck & Bus Ag Kraftübertragungsvorrichtung

Citations (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.
DE3537630A1 (de) * 1984-10-31 1986-04-30 Volkswagen AG, 3180 Wolfsburg Ventilanordnung, insbesondere fuer eine brennkraftmaschine
JPS6193214A (ja) * 1984-10-12 1986-05-12 Sumitomo Heavy Ind Ltd 油圧式排気弁開閉装置
EP0196441A1 (fr) * 1985-03-30 1986-10-08 Robert Bosch Gmbh Système de commande de soupape

Patent Citations (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
EP0196441A1 (fr) * 1985-03-30 1986-10-08 Robert Bosch Gmbh Système de commande de soupape

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, Band 10, Nr. 270 (M-517)[2326], 13. September 1986; & JP-A-61 93 214 (SUMITOMO HEAVY IND. LTD) 12-05-1986 *
PATENT ABSTRACTS OF JAPAN, Band 9, Nr. 103 (M-377)[1826], 8. Mai 1985; & JP-A-39 229 011 (YANMAR DIESEL K.K.) 22-12-1984 *

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0317371A1 (fr) * 1987-11-19 1989-05-24 Honda Giken Kogyo Kabushiki Kaisha Dispositif de commande de soupape pour moteur à combustion interne
DE3833459A1 (de) * 1988-10-01 1990-04-05 Audi Ag Hydraulischer ventiltrieb fuer eine brennkraftmaschine
US6382147B1 (en) 1999-09-22 2002-05-07 Jenbacher Aktiengesellschaft Valve drive for a valve of an internal combustion engine
AT410696B (de) * 1999-09-22 2003-06-25 Jenbacher Ag Ventilantrieb für ein ventil eines verbrennungsmotors
DE102006012067A1 (de) * 2006-03-16 2007-09-20 Volkswagen Ag Hydraulische Ventilbetätigungsvorrichtung für ein Gaswechselventil
DE102006012067B4 (de) * 2006-03-16 2016-03-24 Volkswagen Ag Hydraulische Ventilbetätigungsvorrichtung für ein Gaswechselventil
WO2018065011A1 (fr) * 2016-10-05 2018-04-12 Schaeffler Technologies AG & Co. KG Soupape d'échange des gaz hydraulique dotée d'un compartiment d'amortissement raccordé à un compartiment de compression par un étranglement
DE102017113783A1 (de) 2017-06-21 2018-12-27 Man Truck & Bus Ag Kraftübertragungsvorrichtung
US10718237B2 (en) 2017-06-21 2020-07-21 Man Truck & Bus Ag Force transmission device

Also Published As

Publication number Publication date
EP0255668B1 (fr) 1990-01-03
DE3761320D1 (de) 1990-02-08
EP0255668A3 (en) 1988-03-23
ES2012474B3 (es) 1990-04-01

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