EP0767295A1 - Commande de soupape hydraulique - Google Patents

Commande de soupape hydraulique Download PDF

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Publication number
EP0767295A1
EP0767295A1 EP95810620A EP95810620A EP0767295A1 EP 0767295 A1 EP0767295 A1 EP 0767295A1 EP 95810620 A EP95810620 A EP 95810620A EP 95810620 A EP95810620 A EP 95810620A EP 0767295 A1 EP0767295 A1 EP 0767295A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
piston
drive
valve
cylinder
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
EP95810620A
Other languages
German (de)
English (en)
Other versions
EP0767295B1 (fr
Inventor
Roland Alder
Patrick Genier
Turhan Yildirim
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.)
Wartsila NSD Schweiz AG
Original Assignee
Winterthur Gas and Diesel 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 Winterthur Gas and Diesel AG filed Critical Winterthur Gas and Diesel AG
Priority to DK95810620T priority Critical patent/DK0767295T3/da
Priority to DE59507966T priority patent/DE59507966D1/de
Priority to EP95810620A priority patent/EP0767295B1/fr
Priority to JP19920596A priority patent/JP3986585B2/ja
Priority to KR1019960038663A priority patent/KR100403693B1/ko
Priority to CN96122831A priority patent/CN1088145C/zh
Priority to NO19964175A priority patent/NO311188B1/no
Priority to FI963945A priority patent/FI107751B/fi
Publication of EP0767295A1 publication Critical patent/EP0767295A1/fr
Application granted granted Critical
Publication of EP0767295B1 publication Critical patent/EP0767295B1/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
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • 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
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
    • F01L2013/0089—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque with means for delaying valve closing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
    • F02F7/00—Casings, e.g. crankcases or frames
    • F02F2007/0097—Casings, e.g. crankcases or frames for large diesel engines

Definitions

  • the invention relates to a hydraulic valve drive according to the preamble of independent claim 1.
  • valve drives replace the mechanical drives with lever systems e.g. Bumpers for intake and / or exhaust valves of engines.
  • Mechanical drives are subject to wear and tear on the mechanical parts of the drive and must be reset relatively frequently.
  • hydraulic drives allow the control times to be changed with relatively simple means. This setting is particularly critical and delicate for engines with more than one intake and / or exhaust valve.
  • valve piston usually pushes against the shaft of the Valve that is pressed against the valve piston by spring force.
  • the object of the invention is to provide a hydraulic valve drive, which ensures the reliable, synchronous opening and closing of intake or exhaust valves under the given conditions.
  • such a hydraulic valve drive is characterized by the features in the characterizing part of independent claim 1.
  • the dependent claims relate to advantageous developments of the invention.
  • the valve drive can advantageously be operated with a hydraulic piston pump and with the hydraulic line system of claim 6 or 7.
  • Claims 8 and 9 relate to advantageous embodiments of the piston pump with the line system.
  • two or more valves can be actuated synchronously.
  • the drives for the individual valves are independent of one another in the sense that differences in the frictional resistance of the individual valves have no influence on the synchronization. Differences in the protrusion of the valve stems are compensated and changes in the protrusion of the valve stems during operation are continuously compensated for.
  • the damper device ensures that the synchronization piston of the hydraulic drive and thus also the valves in the valve seats come into contact with damping. The high alternating loads of the undamped impact are avoided. This increases the service life of valve seats and valves. The so-called pitting, i.e. prevents the formation of dimples in the sealing surfaces of the valves.
  • the hydraulic drive also allows the valve closing process to be delayed within certain limits.
  • hydraulic pressure sources other than the hydraulic piston pump according to claims 6 to 9 can also be suitable as a drive for the hydraulic valve drive.
  • hydraulic high-pressure systems known under the name “common rail system” are also suitable, in which high-pressure fluid, from a high-pressure fluid system, is fed to the hydraulic drive via electromagnetically controlled valves and the hydraulic fluid flowing back from the hydraulic drive is returned to the reservoir of the high-pressure fluid system.
  • a damper device on the front, ie on the side of the steps of the synchronization piston, in order to dampen the impact on the cylinder cover.
  • damper devices may be provided for the valve pistons in the opening direction of the valves.
  • valve 1 shows a hydraulic drive according to the invention for, for example, the two intake valves 11 and 11 'of a diesel engine, the valve seats 111 and 111' are incorporated in the cylinder cover 10 (only partially shown).
  • the two shafts 112, 112 'each have a collar 113 or 113', on each of which a valve spring 115 or 115 'is supported.
  • the other end of the valve springs 115, 115 ' is supported on the cylinder cover 10.
  • the hydraulic drive for the valves 11, 11 ' also has a synchronization piston 12, which is designed here as a stepped piston.
  • Each of the stages 121 and 122 moves in a chamber 1210 and 1220, respectively.
  • the synchronization piston 12 is designed in such a way that the same volume changes occur in each of the chambers 1210 and 1220 during a displacement.
  • the end of the cylinder for the synchronization piston 12 and the end of the synchronization piston 12 are shaped such that they together form a damper 124.
  • the damper 124 hinders the backflow of hydraulic oil into the line 1200 and thus reduces the backflow quantity per unit of time.
  • the damping of the impact of the synchronization piston 12 on the cylinder base 123 means that the valves 11 and 11 'also hit the valve seats 111, 111' in a damped manner.
  • valve pistons 13 and 13 ' are each of the same size and the corresponding active surfaces 125, 125' of the synchronization piston 12 are of the same size, then the two valve pistons 13, 13 'move by a certain distance when moving the same Path.
  • synchronous is meant to mean equilateral and synchronous for the same distance.
  • Hydraulic fluid is supplied to the hydraulic circuits via the two feed lines 114, 114 'in order to compensate for any losses caused by leakage currents.
  • the return flow of hydraulic oil is prevented with the one-way valves 1141 and 1141 '.
  • the supply of hydraulic oil to the system also means that the valve pistons are in contact with the ends of the valve stems 112, 112 'at all times, regardless of any different projections (distance from the valve stem end to the cylinder cover) H or H' of the valve stems 112 , 112 '.
  • Fig. 2 shows an example of the course of opening and closing a valve in a four-stroke diesel engine depending on the crankshaft angle.
  • the valve is opened via a crankshaft angle that is approximately between 180 ° and 250 °.
  • the closing time is between 470 ° and 540 ° crankshaft angle. Hydraulic oil is fed into the system via the feed lines when the valves 11, 11 'are in the rest position R.
  • the hydraulic piston pump shown schematically in Fig. 3 with the line system 3 is used to drive the synchronization piston of the hydraulic drive of e.g. Fig. 1.
  • the arrangement consists essentially of a piston pump 31 for pumping the hydraulic oil. From this piston pump, the main line 32 leads with the one-way valve 321 to a drive, as it is e.g. is shown in Fig. 1.
  • the bypass line 33 bridges the one-way valve 321 and opens into the cylinder space 310 of the piston pump 31.
  • the bypass line 34 also bridges the one-way valve 321, but ends with both ends in the main line 32.
  • the switchable valve 341 is installed in the bypass 34, for example via the Compressed air connection 342 is switched.
  • the switchable valve 341 could also be a hydraulic, electromagnetic or other switchable valve.
  • the bypass line 34 can be omitted if, for example, the one-way valve 321 in the main line can be blocked in the open state.
  • the feed line 35 serves to supply hydraulic fluid in the hydraulic system as a result of leakage losses is missing. It contains a one-way valve 351. Excess hydraulic oil can be returned to the feed line through the bypass 352.
  • the piston of the piston pump 31 is actuated, for example, with a cam (not shown).
  • control pressure in control line 342 is switched on. The following occurs during the delivery stroke of the pump piston 311: after 3512 has been completed by the piston 311, the hydraulic fluid is conveyed via the paths 33, 32 34 to the hydraulic drive, the valve actuation. The connection 332 of the bypass 33 is later closed, and the hydraulic oil continues to flow via 32 and 34.
  • control pressure in the control line 342 is switched off, which means that the bypass 34 is closed.
  • the hydraulic fluid is conveyed via the paths 33, 32 to the hydraulic drive, the valve actuation.
  • the connection 332 of the bypass 33 is later closed, and the hydraulic oil continues to flow via 32.
  • the increase in system volume is compensated for by the supply of hydraulic fluid via the feed line 35.
  • a pressure of a few, e.g. 3 to 10 bar in the feed line 35 As soon as the piston 311 begins to open the bore 332, a reverse flow begins via the bypass 33.
  • the valve closing movement now begins and is controlled by the downward movement of the piston 311. Hole 3512 is opened near the lower reversal point of piston 311. The closing movement is now "uncontrolled”. In order to avoid a hard seating of the valves, the damper 124 now comes into action on the synchronization piston (FIG. 1).
  • the closing course 42 of the valve is shown in dashed lines in FIG. 4.
  • the curve 40 in the lower diagram of FIG. 4 shows the course of the stroke of the piston 311 in an arrangement according to FIG. 3.
  • the point 44 on the lower curve 40 which represents the course of the movement of the piston 311 over the crank shaft angle, corresponds to that Position of the piston 311, where on the return the piston 311 opens the bore 332, so that hydraulic oil can flow back. If the closing process of the valves 11, 11 'is to begin before this position 44 of the piston has been reached, this can be achieved by opening the valve 341.
  • the hydraulic drive 1 is suitable for two or more valves 11, 11 'of an engine cylinder, in particular the intake valves 11, 11' or exhaust valves of a large diesel engine.
  • a hydraulic synchronization piston 12, 121 has a drive chamber 1210, 1220 for each valve to be driven, which drives one valve piston 13, 13 'for each valve 11, 11' to be driven such that the valve pistons 13, 13 'are synchronous and with the same stroke move.
  • a damping device 124 dampens the return of the synchronization piston 12 to its initial position. Differences in the projection H, H 'of the stems 112, 112' of the valves 11, 11 'are compensated for by a hydraulic device 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP95810620A 1995-10-03 1995-10-03 Commande de soupape hydraulique Expired - Lifetime EP0767295B1 (fr)

Priority Applications (8)

Application Number Priority Date Filing Date Title
DK95810620T DK0767295T3 (da) 1995-10-03 1995-10-03 Hydraulisk ventildrev
DE59507966T DE59507966D1 (de) 1995-10-03 1995-10-03 Hydraulischer Ventilantrieb
EP95810620A EP0767295B1 (fr) 1995-10-03 1995-10-03 Commande de soupape hydraulique
JP19920596A JP3986585B2 (ja) 1995-10-03 1996-07-29 油圧式弁駆動装置
KR1019960038663A KR100403693B1 (ko) 1995-10-03 1996-09-06 유압밸브드라이브
CN96122831A CN1088145C (zh) 1995-10-03 1996-09-28 液压阀门驱动装置
NO19964175A NO311188B1 (no) 1995-10-03 1996-10-02 Hydraulisk ventilstyring
FI963945A FI107751B (fi) 1995-10-03 1996-10-02 Hydraulinen käyttölaite

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP95810620A EP0767295B1 (fr) 1995-10-03 1995-10-03 Commande de soupape hydraulique

Publications (2)

Publication Number Publication Date
EP0767295A1 true EP0767295A1 (fr) 1997-04-09
EP0767295B1 EP0767295B1 (fr) 2000-03-08

Family

ID=8221802

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95810620A Expired - Lifetime EP0767295B1 (fr) 1995-10-03 1995-10-03 Commande de soupape hydraulique

Country Status (8)

Country Link
EP (1) EP0767295B1 (fr)
JP (1) JP3986585B2 (fr)
KR (1) KR100403693B1 (fr)
CN (1) CN1088145C (fr)
DE (1) DE59507966D1 (fr)
DK (1) DK0767295T3 (fr)
FI (1) FI107751B (fr)
NO (1) NO311188B1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2758857A1 (fr) * 1997-01-27 1998-07-31 Aisin Seiki Dispositif de commande de soupape pour un moteur a combustion interne
WO2003018968A1 (fr) * 2001-08-17 2003-03-06 Robert Bosch Gmbh Dispositif pour commander des soupapes de changement des gaz
EP1260680A3 (fr) * 2001-05-22 2003-05-02 Caterpillar Motoren GmbH & Co. KG Dispositif d'actionnement de 2 soupapes simultanément dans un moteur diesel
WO2004022929A1 (fr) * 2002-08-29 2004-03-18 Robert Bosch Gmbh Actionneur hydraulique de soupape servant a actionner une soupape d'echange de gaz
WO2008004020A1 (fr) * 2006-07-04 2008-01-10 Renault Trucks Système de commande de soupape actionné hydrauliquement et moteur à combustion interne comprenant un tel système
WO2018019457A1 (fr) * 2016-07-26 2018-02-01 Jaguar Land Rover Limited Appareil pour commander les soupapes d'un moteur à combustion interne

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DK1114918T3 (da) * 2000-01-06 2004-09-06 Waertsilae Nsd Schweiz Ag Gasskiftesystem til en forbrændingsmotor og fremgangsmåde til drift af et sådant
DK176119B1 (da) * 2000-02-16 2006-09-04 Man B & W Diesel As System til hydraulisk aktivering af en udstödsventil i en forbrændingsmotor
JP2004084670A (ja) * 2002-08-28 2004-03-18 Man B & W Diesel As 水圧で作動されるバルブ
CN1289796C (zh) * 2003-10-13 2006-12-13 方戟 内燃式发动机的液压配气机构
US8069828B2 (en) * 2009-08-13 2011-12-06 International Engine Intellectual Property Company, Llc Intake valve closing hydraulic adjuster
CN101660435B (zh) * 2009-09-14 2012-10-24 奇瑞汽车股份有限公司 一种液压凸轮轴及其液压控制系统
CN101936199B (zh) * 2010-09-20 2012-10-03 武央 摩托车发动机液压传动配气系统
SE537454C2 (sv) * 2013-10-16 2015-05-05 Freevalve Ab Förbränningsmotor samt gashanteringssystem för pneumatisk drivning av en ventilaktuator
GB2553120B (en) * 2016-08-24 2019-12-25 Jaguar Land Rover Ltd Variable valve lift system with a diffusing system

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3807699A1 (de) * 1988-03-09 1989-09-21 Audi Ag Regelbare hydraulische ventilsteuerung
US4887562A (en) * 1988-09-28 1989-12-19 Siemens-Bendix Automotive Electronics L.P. Modular, self-contained hydraulic valve timing systems for internal combustion engines
EP0520633A2 (fr) * 1991-06-24 1992-12-30 Ford Motor Company Limited Dispositif de commande hydraulique de soupapes pour moteurs à combustion interne
WO1993001399A1 (fr) * 1991-07-12 1993-01-21 Caterpillar Inc. Systeme de soupape de moteur a recuperation et son procede de fonctionnement

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3807699A1 (de) * 1988-03-09 1989-09-21 Audi Ag Regelbare hydraulische ventilsteuerung
US4887562A (en) * 1988-09-28 1989-12-19 Siemens-Bendix Automotive Electronics L.P. Modular, self-contained hydraulic valve timing systems for internal combustion engines
EP0520633A2 (fr) * 1991-06-24 1992-12-30 Ford Motor Company Limited Dispositif de commande hydraulique de soupapes pour moteurs à combustion interne
WO1993001399A1 (fr) * 1991-07-12 1993-01-21 Caterpillar Inc. Systeme de soupape de moteur a recuperation et son procede de fonctionnement

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2758857A1 (fr) * 1997-01-27 1998-07-31 Aisin Seiki Dispositif de commande de soupape pour un moteur a combustion interne
EP1260680A3 (fr) * 2001-05-22 2003-05-02 Caterpillar Motoren GmbH & Co. KG Dispositif d'actionnement de 2 soupapes simultanément dans un moteur diesel
WO2003018968A1 (fr) * 2001-08-17 2003-03-06 Robert Bosch Gmbh Dispositif pour commander des soupapes de changement des gaz
WO2004022929A1 (fr) * 2002-08-29 2004-03-18 Robert Bosch Gmbh Actionneur hydraulique de soupape servant a actionner une soupape d'echange de gaz
US7007642B2 (en) 2002-08-29 2006-03-07 Robert Bosch Gmbh Hydraulic valve actuator for actuating a gas-exchange valve
WO2008004020A1 (fr) * 2006-07-04 2008-01-10 Renault Trucks Système de commande de soupape actionné hydrauliquement et moteur à combustion interne comprenant un tel système
US8365690B2 (en) 2006-07-04 2013-02-05 Renault Trucks Hydraulically operated valve control system and internal combustion engine comprising such a system
WO2018019457A1 (fr) * 2016-07-26 2018-02-01 Jaguar Land Rover Limited Appareil pour commander les soupapes d'un moteur à combustion interne

Also Published As

Publication number Publication date
CN1160120A (zh) 1997-09-24
DK0767295T3 (da) 2000-06-05
KR970021645A (ko) 1997-05-28
NO964175D0 (no) 1996-10-02
NO311188B1 (no) 2001-10-22
JP3986585B2 (ja) 2007-10-03
FI107751B (fi) 2001-09-28
KR100403693B1 (ko) 2004-01-28
EP0767295B1 (fr) 2000-03-08
FI963945A0 (fi) 1996-10-02
FI963945A (fi) 1997-04-04
DE59507966D1 (de) 2000-04-13
JPH09100706A (ja) 1997-04-15
CN1088145C (zh) 2002-07-24
NO964175L (no) 1997-04-04

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