WO2003027449A1 - Dispositif de commande d'une section d'ouverture dans un cylindre de combustion d'un moteur a combustion interne - Google Patents

Dispositif de commande d'une section d'ouverture dans un cylindre de combustion d'un moteur a combustion interne Download PDF

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Publication number
WO2003027449A1
WO2003027449A1 PCT/DE2002/002291 DE0202291W WO03027449A1 WO 2003027449 A1 WO2003027449 A1 WO 2003027449A1 DE 0202291 W DE0202291 W DE 0202291W WO 03027449 A1 WO03027449 A1 WO 03027449A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
damping
piston
cylinder
volume displacement
Prior art date
Application number
PCT/DE2002/002291
Other languages
German (de)
English (en)
Inventor
Udo Diehl
Bernd Rosenau
Uwe Hammer
Volker Beuche
Peter Lang
Stefan Reimer
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 WO2003027449A1 publication Critical patent/WO2003027449A1/fr

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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
    • 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

Definitions

  • the invention relates to a device for controlling an opening cross section in a combustion cylinder of an internal combustion engine according to the preamble of claim 1.
  • a known device of this type (DE 198 26 047 AI) has as an actuator or actuator or valve actuator a double-acting, hydraulic working cylinder, in which an actuating piston is axially displaceably guided, which is fixedly connected to the valve stem of the gas exchange valve integrated in the combustion cylinder or its valve-closing body remote End forms itself.
  • the actuating piston delimits a first and a second pressure chamber in the working cylinder with its two end faces facing away from one another. While the first pressure chamber over which one
  • Piston displacement in the direction of valve closing is effected, is constantly pressurized with fluid under pressure, the second pressure chamber, via which a piston displacement in the direction of valve opening is effected, with the aid of control valves, preferably 2/2-way solenoid valves, specifically pressurized with pressurized fluid or - again relieved to approximately ambient pressure ,
  • the pressurized fluid is supplied by a regulated pressure supply.
  • a first control valve connects the second pressure chamber to the pressure supply and a second control valve connects the second pressure chamber to a relief line opening into a fluid reservoir.
  • the second pressure chamber In the closed state of the gas exchange valve, the second pressure chamber is separated from the pressure supply by the closed first control valve and is connected to the relief line by the opened second control valve, so that the actuating piston is transferred into its closed position by the fluid pressure prevailing in the first pressure chamber.
  • the control valves are switched over, thereby shutting off the second pressure chamber from the relief line and to the
  • the gas exchange valve opens because the piston area of the actuating piston in the second pressure chamber is larger than the effective area of the actuating piston in the first pressure chamber.
  • the size of the opening stroke depends on the formation of the electrical control signal applied to the first control valve and the opening speed depends on the fluid pressure controlled by the pressure supply.
  • the control valves switch again to close the gas exchange valve.
  • the second pressure chamber which is shut off in relation to the pressure supply, lies on the relief line and that in the first pressure chamber prevailing fluid pressure leads the control piston back into its valve closed position, so that the gas exchange valve is closed by the control piston.
  • the device according to the invention for controlling an opening cross section in a combustion cylinder
  • valve brake does not influence the stroke movement of the valve member and only comes into engagement with the valve member for the immediate remaining stroke before the valve body hits the valve seat and then brakes it very strongly.
  • Part of the kinetic energy of the valve member is consumed as impact energy at the moment of the intervention and then another part is throttled by pushing out a corresponding volume of fluid from the volume displacement chamber.
  • the stroke of the valve member, after which the damping member comes into direct or indirect engagement with the valve member or the remaining stroke of the valve member, during which the damping member is in engagement with the valve member can be set very easily from the outside without intervention in the actuator become.
  • the damping member has a damping piston which is axially displaceably guided in a damping cylinder and a volume displacement chamber which is delimited by the damping piston and is connected to a throttle opening.
  • the damping member engages in the stroke of the valve member, the valve stem or the actuator strikes the damping piston on its side facing away from the volume displacement chamber.
  • the damping piston is additionally counteracting the displacement of the damping piston in the direction of reducing the volume displacement chamber
  • the damping cylinder is designed as a double-acting working cylinder which additionally has a storage chamber separated from the volume displacement chamber by the damping piston. Like the volume displacement chamber, a fluid flow is fed to the storage chamber via a check valve. The storage chamber is connected to a memory.
  • Actuator even one and is independent of component tolerances and thermal expansion in the gas exchange valve or actuator.
  • FIG. 1 is a circuit diagram of a device for controlling an opening cross section in a combustion cylinder of an internal combustion engine
  • FIG. 2 shows a circuit diagram of a valve brake in the device according to FIG. 1,
  • Fig. 3 is a circuit diagram of two valve brakes in a modified embodiment. Description of the embodiments
  • the device shown in the circuit diagram in FIG. 1 for controlling an opening cross section 11 in a combustion cylinder 10 of an internal combustion engine or an internal combustion engine in vehicles has a gas exchange valve 51 integrated in the combustion cylinder 10 with an axially displaceable valve member 12 which has a valve stem 13 and an end on Valve stem 13 includes formed valve closing body 14.
  • the valve closing body 14 acts with one
  • Valve seat 15 enclosing the opening cross section 11, on which the valve closing body 14 rests with a valve sealing surface 141 in the closed position of the gas exchange valve 10 and thus closes the opening cross section 11 in a gas-tight manner.
  • the device To actuate the stroke of the valve member 12, the device has a hydraulically operated valve actuator, hereinafter referred to as an actuator or actuator 16, which represents and has a double-acting working cylinder
  • Cylinder housing 17 and an actuating piston 18 which is axially displaceably guided in the cylinder housing 17 and which delimits a lower, first pressure chamber 19 and an upper, second pressure chamber 20 in the cylinder housing 17.
  • the first pressure chamber 19 is connected directly and the second pressure chamber 20 is connected via a first control valve 21 to the outlet 221 of an adjustable pressure supply device 22.
  • the second pressure chamber 20 is additionally connected via a second control valve 23 to a return line 25 opening into a fluid reservoir 24, in which a check valve 26 can also be arranged.
  • the Pressure supply device 22 comprises a preferably controllable high-pressure pump 27 which conveys fluid, preferably hydraulic oil, from the fluid reservoir 24, a check valve 28 and a pressure accumulator 29 for pulsation damping and energy storage.
  • the actuating piston 18 is rigidly connected to the valve stem 13 of the gas exchange valve 51 via a piston rod 30 led out of the cylinder housing 17. Alternatively, the adjusting piston 18 can also be formed directly on the valve stem 13.
  • the first control valve 21 is closed and the second control valve 23 is open.
  • the high pressure prevailing in the first pressure chamber 19 ensures that the actuating piston 18 is in the top dead center position and the valve closing body 14 with its valve closing surface 141 is thereby pressed gas-tight onto the valve seat 15 and the opening cross section 11 is thus closed gas-tight.
  • the control valves 21, 23 are switched over, the second pressure chamber 20 is shut off from the return line 25 and the high pressure at the outlet 221 of the pressure supply device 22 is applied to the second pressure chamber 20. Since the area of the actuating piston 18 delimiting the second pressure chamber 20 is larger than the area of the actuating piston 18 delimiting the first pressure chamber 19, the actuating piston 18 moves downward, and the
  • Valve closing body 14 of valve member 12 is lifted off valve seat 15, so that opening cross section 11 is released.
  • the control valves 21, 23 are returned to the switching position shown in FIG. 1. This is the second
  • the adjusting piston 18 moves upward in FIG. 1 and places the valve body 14 of the valve member 12 on the valve seat 15, sealing the opening cross section 11.
  • a valve brake 50 which has a hydraulic damping element 31 which is designed such that it is decoupled from the lifting movement of the valve element 12 and only comes into indirect engagement with the valve element 12 after a predetermined closing stroke.
  • the damping member 31 has a damping cylinder 32 and a damping piston 33 which is axially displaceably guided in the damping cylinder 32 and which delimits a volume displacement chamber 34 in the damping cylinder 32.
  • Volume displacement chamber 34 is a return spring 35 designed as a compression spring, which is supported on the one hand on the piston surface of the damping piston 33 delimiting the volume displacement chamber 34 and on the other hand on an end face 321 of the damping cylinder 32 opposite the damping piston 33 and the damping piston 33 with one of the displacement movements of the damping piston 33 Counteracting spring force acts in the direction of reducing the volume displacement chamber 34.
  • a return spring 35 designed as a compression spring
  • Volume displacement chamber 34 two fluid connections 341 and 342, of which the fluid connection 341 is connected to an inlet line 36 and the fluid connection 342 is connected to an outlet line 37.
  • a check valve 38 with a flow direction directed towards the fluid connection 341 is arranged in the inlet line 36 and a throttle valve 39 with a preferably adjustable throttle opening 391 is arranged in the outlet line 37.
  • a fluid flow is fed to the volume displacement chamber 34 via the inlet line 36 and flows off via the outlet line 37 to a collecting container 40.
  • inlet and outlet lines 36, 37 are preferably connected to the engine oil circuit of the internal combustion engine.
  • the damping piston 33 is rigidly connected to a piston rod 41 which is led out of the damping cylinder 32 and whose axis is aligned with the axis of the valve stem 13 and the actuating piston 18 of the actuator 16.
  • the damping piston 33 and the piston rod 41 can be made in one piece, so that the damping piston 35 is a stepped or - with the piston diameter corresponding rod diameter - stepless piston.
  • the actuating piston 18 carries a further piston rod 42, the outer diameter of which is significantly smaller than the outer diameter of the other piston rod 30 on the actuating piston 18.
  • Piston rod 42 is rigidly connected to the actuating piston 18, is guided out of the damping cylinder 32 through the second pressure chamber 20, and has an end collar 421 with an enlarged diameter at the end.
  • the piston rod 42 with an impact collar 421 is aligned so that its axis is aligned with the axis of the piston rod 41 at the Damping cylinder 32 is aligned.
  • the piston rods 41 and 42 of the damping piston 33 and the actuating piston 18 are arranged with respect to one another such that with the engagement of the damping member 31 in the stroke of the valve member 12, the piston rod 42 of the adjusting piston 18 with the impact collar 421 strikes the end face of the piston rod 41 of the damping piston 33 ,
  • valve brake 50 when the gas exchange valve 51 closes is as follows:
  • the actuating piston 18 in FIG. 1 is at or more or less close to its bottom dead center position.
  • the damping piston 33 assumes a bottom dead center position under the action of the return spring 35. In this position, the piston rods 41, 42 are spaced apart from one another and, depending on the opening stroke of the valve member 12, the impact collar 421 is at a greater or lesser distance from the front end of the piston rod 41.
  • the control piston 21, 22 is actuated accordingly by the fluid pressure by the control valves 21, 22 Moved upwards in the first pressure chamber 19, after a defined and externally adjustable closing stroke of the valve member 12, the impact collar 421 strikes the end face of the piston rod 41 and begins by compressing the return spring 35 and pushing out fluid volume from the volume displacement chamber 34, the damping piston 33 to move up in Fig. 1.
  • the kinetic energy of the valve member 12 and the actuating piston 18 is due to the impact of the actuating piston 18 on the Damping piston 33, by compressing the return spring 35 and by throttling the fluid flowing through the throttle valve 39 so far that the impact speed with which the valve closing body 14 finally sits on the valve seat 15 is reduced to a desired level.
  • valve brake 50 shown schematically in FIG. 2 and in the block diagram is modified to the extent that the damping cylinder 32 is designed as a double-acting working cylinder 32 ', which is in addition to the
  • Volume displacement chamber 34 has a storage chamber 43 separated from it by the damping piston 33.
  • the storage chamber 43 is connected via a check valve 44 with a flow direction pointing to the storage chamber 43 at the inlet of the check valve 38 upstream of the volume displacement chamber 34, so that fluid can also flow into the storage chamber 43.
  • the storage chamber 43 is connected to a storage 45 having a specific storage volume.
  • the damping piston 33 can still be coupled to the actuator 16 in the manner described above via the piston rod 41 which now extends through the storage chamber 43.
  • the damping piston 33 can no longer move.
  • the damping piston thus remains below its top dead center position by an amount dependent on the volume of the storage chamber 43 and the storage 45. This position defines that stroke of the valve member 12 at which the actuating piston 18 during the closing process
  • valve brake 50 Each of the two valve brakes shown schematically in FIG. 3 for one valve member 12 of two gas exchange valves correspond almost completely to the valve brake 50 described for FIG. 2.
  • a modification has been made to the extent that the throttle valve 39 with a controllable throttle opening 391 is used in common for both damping members 31 and for this purpose the discharge line 37 opening into the collecting container 40, in which the throttle valve 39 is arranged, is connected to both volume displacement chambers 34 in the two damping cylinders 32 ' is.
  • the invention is not limited to the exemplary embodiment described.
  • the intervention of the valve brake 50 in the lifting movement of the valve member 12 can be carried out not only indirectly via the actuator 16, but also directly via the valve stem 13.
  • the piston rod 41 of the damping piston 33 strikes the end face of the valve stem 13, which is guided, for example, through the actuator 16 and whose axis is aligned in the same way with the axis of the piston rod 41 on the damping piston 33.

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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 un dispositif de commande de la section d'ouverture (11) dans un cylindre de combustion (10) d'un moteur à combustion interne, comprenant une soupape à deux voies à gaz (51) présentant un organe de soupape déplaçable (12) comprenant une tige de soupape (13) et un organe de soupape proprement dit (12) formé sur la tige de soupape (13), coopérant avec un siège de soupape entourant la section d'ouverture (11), et comportant un actionneur (16) en prise avec l'organe de soupape (12), à sa commande de course. En vue de réduire la vitesse au choc du corps de fermeture de soupape (14) sur le siège de soupape (15) lors de la course de fermeture dudit organe de soupape, l'invention est caractérisée en ce qu'il est prévu un frein de soupape (50) présentant un organe d'amortissement hydraulique (31) réalisé de façon qu'il soit désaccouplé par le mouvement de la course de l'organe de soupape (12) et qu'il ne vienne en prise directement ou indirectement avec l'organe de soupape (12) qu'après une cours de fermeture prédéterminée de celui-ci.
PCT/DE2002/002291 2001-09-26 2002-06-21 Dispositif de commande d'une section d'ouverture dans un cylindre de combustion d'un moteur a combustion interne WO2003027449A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10147299A DE10147299A1 (de) 2001-09-26 2001-09-26 Vorrichtung zur Steuerung eines Öffnungsquerschnitts in einem Verbrennungszylinder einer Brennkraftmaschine
DE10147299.4 2001-09-26

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WO2003027449A1 true WO2003027449A1 (fr) 2003-04-03

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PCT/DE2002/002291 WO2003027449A1 (fr) 2001-09-26 2002-06-21 Dispositif de commande d'une section d'ouverture dans un cylindre de combustion d'un moteur a combustion interne

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DE (1) DE10147299A1 (fr)
WO (1) WO2003027449A1 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1491732A1 (fr) * 2003-06-23 2004-12-29 Magneti Marelli Powertrain S.p.A. Méthode et dispositif pour contrôler la vitesse des soupapes dans un moteur à combustion
WO2007094732A1 (fr) * 2006-02-14 2007-08-23 Cargine Engineering Ab Procede de freinage d'un piston d'actionneur, et actionneur pneumatique
WO2013121100A1 (fr) * 2012-02-16 2013-08-22 Wärtsilä Finland Oy Agencement de soupape hydraulique pour actionner de façon commandée une soupape d'échange de gaz d'un moteur à combustion interne à piston
SE2250884A1 (en) * 2022-07-11 2024-01-12 Freevalve Ab An apparatus comprising a plurality of tools, wherein each tool comprises at least one hydraulic chamber

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008002202A1 (de) 2008-06-04 2009-12-10 Robert Bosch Gmbh Vorrichtung zur Steuerung eines Öffnungsquerschnitts in einem Verbrennungszylinder einer Brennkraftmaschine
DE102014111618A1 (de) 2014-08-14 2016-02-18 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Luftdämpfer für eine Stauraumabdeckung eines Kraftfahrzeugs und Verfahren zum Betreiben einer Stauraumabdeckung eines Kraftfahrzeugs

Citations (7)

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Publication number Priority date Publication date Assignee Title
JPS6241907A (ja) * 1985-08-16 1987-02-23 Yanmar Diesel Engine Co Ltd 弁着座時の衝撃緩衝装置
DE3841997A1 (de) * 1987-12-19 1989-06-29 Lucas Ind Plc Ventilantriebssystem
DE3833459A1 (de) * 1988-10-01 1990-04-05 Audi Ag Hydraulischer ventiltrieb fuer eine brennkraftmaschine
US5275136A (en) * 1991-06-24 1994-01-04 Ford Motor Company Variable engine valve control system with hydraulic damper
DE19826047A1 (de) * 1998-06-12 1999-12-16 Bosch Gmbh Robert Vorrichtung zur Steuerung eines Gaswechselventils für Brennkraftmaschinen
EP1087109A2 (fr) * 1999-09-22 2001-03-28 Jenbacher Aktiengesellschaft Actionneur de soupape de moteur à combustion interne
US6223846B1 (en) * 1998-06-15 2001-05-01 Michael M. Schechter Vehicle operating method and system

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6241907A (ja) * 1985-08-16 1987-02-23 Yanmar Diesel Engine Co Ltd 弁着座時の衝撃緩衝装置
DE3841997A1 (de) * 1987-12-19 1989-06-29 Lucas Ind Plc Ventilantriebssystem
DE3833459A1 (de) * 1988-10-01 1990-04-05 Audi Ag Hydraulischer ventiltrieb fuer eine brennkraftmaschine
US5275136A (en) * 1991-06-24 1994-01-04 Ford Motor Company Variable engine valve control system with hydraulic damper
DE19826047A1 (de) * 1998-06-12 1999-12-16 Bosch Gmbh Robert Vorrichtung zur Steuerung eines Gaswechselventils für Brennkraftmaschinen
US6223846B1 (en) * 1998-06-15 2001-05-01 Michael M. Schechter Vehicle operating method and system
EP1087109A2 (fr) * 1999-09-22 2001-03-28 Jenbacher Aktiengesellschaft Actionneur de soupape de moteur à combustion interne

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 011, no. 228 (M - 610) 24 July 1987 (1987-07-24) *

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1491732A1 (fr) * 2003-06-23 2004-12-29 Magneti Marelli Powertrain S.p.A. Méthode et dispositif pour contrôler la vitesse des soupapes dans un moteur à combustion
US7086358B2 (en) 2003-06-23 2006-08-08 Magneti Marelli Powertrain S.P.A. Method and device for controlling the speed of the valves of an internal combustion engine
WO2007094732A1 (fr) * 2006-02-14 2007-08-23 Cargine Engineering Ab Procede de freinage d'un piston d'actionneur, et actionneur pneumatique
WO2013121100A1 (fr) * 2012-02-16 2013-08-22 Wärtsilä Finland Oy Agencement de soupape hydraulique pour actionner de façon commandée une soupape d'échange de gaz d'un moteur à combustion interne à piston
CN104169532A (zh) * 2012-02-16 2014-11-26 瓦锡兰芬兰有限公司 用于可控地操作内燃活塞式发动机的气体交换阀的液压阀装置
EP3045689A3 (fr) * 2012-02-16 2016-11-16 Wärtsilä Finland Oy Agencement de soupape hydraulique pour faire fonctionner de manière commandée une soupape d'échange gazeux d'un moteur à combustion interne à piston
SE2250884A1 (en) * 2022-07-11 2024-01-12 Freevalve Ab An apparatus comprising a plurality of tools, wherein each tool comprises at least one hydraulic chamber
WO2024015002A1 (fr) * 2022-07-11 2024-01-18 Freevalve Ab Appareil comprenant une pluralité d'outils ayant chacun au moins une chambre hydraulique pour liquide hydraulique
SE546024C2 (en) * 2022-07-11 2024-04-16 Freevalve Ab An apparatus comprising a plurality of tools, wherein each tool comprises at least one hydraulic chamber

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