EP0767295B1 - Commande de soupape hydraulique - Google Patents

Commande de soupape hydraulique Download PDF

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Publication number
EP0767295B1
EP0767295B1 EP95810620A EP95810620A EP0767295B1 EP 0767295 B1 EP0767295 B1 EP 0767295B1 EP 95810620 A EP95810620 A EP 95810620A EP 95810620 A EP95810620 A EP 95810620A EP 0767295 B1 EP0767295 B1 EP 0767295B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
piston
cylinder
drive
valve
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
EP95810620A
Other languages
German (de)
English (en)
Other versions
EP0767295A1 (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
Wartsila NSD Schweiz 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 Wartsila NSD Schweiz AG filed Critical Wartsila NSD Schweiz AG
Priority to EP95810620A priority Critical patent/EP0767295B1/fr
Priority to DE59507966T priority patent/DE59507966D1/de
Priority to DK95810620T priority patent/DK0767295T3/da
Priority to JP19920596A priority patent/JP3986585B2/ja
Priority to KR1019960038663A priority patent/KR100403693B1/ko
Priority to CN96122831A priority patent/CN1088145C/zh
Priority to FI963945A priority patent/FI107751B/fi
Priority to NO19964175A priority patent/NO311188B1/no
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 generic term of the 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 often.
  • hydraulic drives allow a change tax times with relatively simple means. Especially This setting is critical and delicate for engines with more than one inlet and / or outlet valve.
  • the Manufacture of the valve seats in the cylinder cover and especially when grinding in the valve and valve seat slight differences arise, which are different protruding valve stems.
  • the Differences can be in the range of plus / minus millimeters, lie. As a rule, these differences are almost always in the range of 1 / + 3 mm. These deviations lie in the Magnitude of the immersion depth of the damper, what to big deviations and differences when closing the Can lead valves. Increasing the Manufacturing accuracy and reduce the Manufacturing tolerances could be a certain one Bring improvement, but is not for cost reasons justifiable. Even then, there would still be some disturbing differences when closing the valves count.
  • DE A 38 07 699 describes an adjustable one hydraulic drive for a valve one Engine cylinder.
  • the only drive piston has only one only drive chamber on.
  • US 4,887,562 a hydraulic valve actuator for Internal combustion engines with a single piston Drive chamber for two valves.
  • the two chambers over The actuating pistons for the valves are with a channel connected.
  • the object of the invention is a hydraulic Valve actuator to create the given among the Conditions for reliable, synchronous opening and Guaranteed closing of intake or exhaust valves.
  • the hydraulic drive With the hydraulic drive according to the invention two or more valves are operated synchronously.
  • the Actuators for the individual valves are in this sense independently, as differences in Frictional resistance of the individual valves has no influence to have synchronization. Differences in the supernatant
  • the valve stems are balanced and changes the overhangs of the valve stems in operation become ongoing compensated.
  • the damper device ensures that the Synchronization piston of the hydraulic drive and thus also place the valves in the valve seats damped. The high alternating loads of the undamped impact are avoided. So that the lifespan of Valve seats and valves increased. Further is through the Muted placement also called pitting, i.e. making prevented by dimples in the sealing surfaces of the valves.
  • the hydraulic drive also allows that Closing process of the valve within certain limits to delay time.
  • valve 1 shows a hydraulic drive according to the invention for example for the two inlet valves 11 and 11 ' of a diesel engine.
  • the two shafts 112, 112 'each have one Collar 113, or 113 ', on each of which a valve spring 115, or 115 'is supported.
  • the hydraulic drive for the valves 11, 11 ' has next a synchronization piston 12 on the here as Step piston is formed.
  • Each of stages 121 and 122 moves in a chamber 1210 or 1220.
  • the Synchronization piston 12 is designed so that at a shift in each of the chambers 1210 and 1220 equal volume changes take place.
  • the synchronization piston 121 by the valve springs 115, 115 'via the valve pistons 13, 13' and their hydraulic connection line in the direction of Starting position pushed.
  • fluid loss Cold
  • Damper 124 hinders hydraulic oil from flowing back into line 1200 and thus reduces the amount of reflux per unit of time.
  • the damping of the impact of the synchronization piston 12 on the cylinder bottom 123 also causes the valves 11 and 11 'damped on the valve seats 111, 111' hit.
  • valve pistons 13 and 13 ' are each the same are large, and the corresponding active areas 125, 125 'of the synchronization piston 12 are of the same size, then the two valve pistons 13, 13 'move at the Movement along a certain path around the same Path.
  • the valve stems 112 and 112 'thus become synchronous emotional. Synchronous in the sense of the present document at the same time and in the same direction over the same distance mean.
  • Fig. 2 shows an example of the course of the opening and Closing a valve on a four-stroke diesel engine in Dependence on crankshaft angle.
  • the valve is over opened a crankshaft angle of approximately between 180 ° and is 250 °.
  • Lingers after closing the valve the valve 11, 11 'in its rest position or in Closed position R until it is opened again.
  • the closing time is between 470 ° and 540 ° Crankshaft angle.
  • the replenishment of hydraulic oil in the System takes place via the feed lines when the Valves 11, 11 'are in the rest position R.
  • Piston pump with the line system 3 is used for the drive of the synchronization piston of the hydraulic drive from e.g. Fig. 1.
  • the arrangement consists essentially of a piston pump 31 for conveying the hydraulic oil.
  • the main line 32 With the One-way valve 321 for a drive, e.g. in Fig. 1 is shown.
  • the bypass line 33 bridges the one-way valve 321 and opens into the cylinder chamber 310 of the piston pump 31.
  • Die Bypass line 34 also bridges the one-way valve 321, but ends with both ends in the main line 32. Im Bypass 34, the switchable valve 341 is installed, which switched for example via the compressed air connection 342 becomes.
  • the switchable valve 341 could also be a hydraulic, be an electromagnetic or other switchable valve.
  • the bypass line 34 can be omitted if, for example the one-way valve 321 in the main line in the open state can be blocked.
  • the feed line 35 is used to supply hydraulic Fluid that in the hydraulic system due to leakage is missing. It contains a one-way valve 351. Excess Hydraulic oil can flow back into the bypass 352 Feed line can be returned.
  • the piston of the Piston pump 31 is e.g. with a cam (not shown) operated.
  • control pressure in control line 342 is switched on. The following happens during the delivery stroke of the pump piston 311: After completion of 3512 by the piston 311, the Hydraulic fluid via paths 33, 32 34 to hydraulic drive, the valve actuation promoted. The connection 332 of the bypass 33 is later closed, the flow of hydraulic oil continues through 32 and 34.
  • control pressure in control line 342 is switched off, which means that the bypass 34 is closed.
  • the delivery stroke of the pump piston 311 is as follows. To Completion of 3512 by the piston 311, the Hydraulic fluid via paths 33, 32 to hydraulic drive, the valve actuation promoted. The connection 332 of the bypass 33 is later closed, the flow of hydraulic oil continues through 32.
  • the closing course 42 of the valve is in FIG. 4 shown in dashed lines.
  • Curve 40 in the lower diagram 4 shows the course of the stroke of piston 311 in an arrangement according to Fig. 3.
  • the point 44 on the lower Curve 40 which shows the course of the movement of the piston 311 over the crank shaft angle corresponds to Position of the piston 311, where the piston 311 opens the hole 332 so that hydraulic oil flows back can.
  • the hydraulic actuator 1 is for two or more valves 11, 11 'of an engine cylinder, in particular the Intake valves 11, 11 'or exhaust valves one Large diesel engine suitable.
  • a hydraulic one Synchronization pistons 12, 121 have for each valve to be driven has a drive chamber 1210, 1220, which each have a valve piston 13, 13 'to be driven Valve 11, 11 'drives so that the valve piston 13, 13' move synchronously and with the same stroke.
  • a Damping device 124 dampens the return of the Synchronization piston 12 in its starting position. With a hydraulic device 1 differences in Overhang H, H 'of the stems 112, 112' of the valves 11, 11 ' balanced.

Landscapes

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

Claims (10)

  1. Commande hydraulique (1) pour deux soupapes ou plus (11, 11') d'un cylindre de moteur, notamment des soupapes d'admission d'un grand moteur Diesel, caractérisée par un piston de synchronisation hydraulique (12, 121) qui présente pour chaque soupape à commander (11, 11') une chambre de commande (1210, 1220), qui commande respectivement un piston de soupape (13, 13') pour chaque soupape à commander (11, 11') de façon que les pistons de soupape (13, 13') se déplacent d'une manière synchronisée, et par un dispositif d'amortissement (124) pour amortir le retour du piston de synchronisation (12) et des soupapes (11, 11') dans leur position de départ, ainsi que par une installation hydraulique (1) pour égaliser des différences de dépassement (H, H') des tiges (112, 112') des deux soupapes (11, 11') ou plus commandées par la commande hydraulique (1).
  2. Commande hydraulique (1) selon la revendication 1, où l'installation d'amortissement pour amortir le retour di piston de synchronisation (12) présente une installation pour diminuer (124) la section transversale d'écoulement du moyen de commande hydraulique qui reflue.
  3. Commande hydraulique (1) selon la revendication 2, où l'installation (124) pour diminuer la section transversale d'écoulement est formée par la forme du côté d'entraínement du piston de synchronisation (121) et la paroi du cylindre de piston.
  4. Commande hydraulique (1) selon l'une des revendications 1 à 3, où l'installation hydraulique pour égaliser le dépassement (H, H') présente un dispositif d'alimentation (114, 114') pour le fluide hydraulique.
  5. Commande hydraulique (1) avec un piston de commande pour la course avant et arrière du piston de sychronisation d'une commande hydraulique selon l'une des revendications 1 à 4, avec un agencement de commutation hydraulique (3) pour retarder le retour du piston de synchronisation (12) dans sa position de départ, en comparaison avec le retour du piston de commande (311) dans sa position de départ et par conséquent du reflux du fluide hydraulique dans l'enceinte (310) dans le cylindre du piston de commande (311).
  6. Commande hydraulique selon l'une des revendications 1 à 5, avec une pompe à piston hydraulique pour l'entraínement du piston de synchronisation (12 ;121) et avec un système de conduits hydrauliques (32, 33, 34, 35, 352) pour amener et ramener le fluide hydraulique de la pompe à piston (31) au piston de synchronisation (12 ;121) dans le sens aller et retour,
    avec un conduit principal (32) comportant une soupape à une voie (321) qui empêche le reflux du fluide au cylindre de pompe (310) et
    avec un conduit de dérivation (34), avec une soupape (341) apte à être commutée qui passe sur la soupape à une voie (321) dans le conduit principal (32) et
    avec un conduit secondaire, d'amenée et de retour (33) qui passe également sur la soupape à une voie (321) dans le conduit principal (32) et qui débouche à travers la paroi de cylindre (332) de la pompe à piston hydraulique (31) dans l'enceinte de cylindre (310) de la pompe à piston (31).
  7. Commande hydraulique selon l'une des revendications 1 à 5, avec une pompe à piston hydraulique pour l'entraínement du piston de synchronisation (12, 121) selon l'une des revendications 1 à 5, avec un système de conduits hydrauliques (32, 33, 35, 352) pour amener et ramener le fluide hydraulique de la pompe à piston (32) au piston de synchronisation (12 ; 121) dans le sens aller et retour,
    avec un conduit principal (32) avec une soupape à une voie (321) qui peut être maintenue sélectivement dans la position d'ouverture et qui empêche le reflux du fluide vers le cylindre de pompe (310) à l'état non bloqué et
    avec un conduit secondaire, d'amenée et de retour (33) qui passe sur la soupape à une voie (321) dans le conduit principal (32) et qui débouche à travers la paroi de cylindre (332) de la pompe à piston hydraulique (31) dans l'enceinte de cylindre (310) de la pompe à piston (31).
  8. Commande hydraulique selon la revendication 6 ou 7, avec un agencement d'amenée (35, 352) pour du fluide hydraulique depuis et vers un réservoir, avec un conduit d'amenée (35), avec une soupape à une voie (351) qui empêche le reflux du fluide hydraulique dans le réservoir et
       avec un conduit d'amenée et de retour (352) qui passe sur la soupape à une voie (351) du conduit d'amenée (35) et qui débouche au voisinage du point d'inversion inférieur dans l'enceinte de cylindre (310, 3512) de la pompe à piston (311).
  9. Commande hydraulique selon la revendication 8, où le conduit d'amenée (35) débouche au voisinage du point d'inversion supérieur dans l'enceinte de cylindre (310),
    où le conduit d'amenée et de retour (352, 3512) débouche au voisinage du point d'inversion inférieur dans l'enceinte de cylindre (310) et
    où le conduit secondaire, d'amenée et de reflux (33) de la commande hydraulique débouche à une hauteur qui se situe entre (332), dans l'enceinte de cylindre (310).
  10. Grand moteur Diesel avec une commande hydraulique (1) pour des soupapes d'admission (11, 11') ou d'échappement de cylindre selon l'une des revendications 1 à 9.
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
EP95810620A EP0767295B1 (fr) 1995-10-03 1995-10-03 Commande de soupape hydraulique
DE59507966T DE59507966D1 (de) 1995-10-03 1995-10-03 Hydraulischer Ventilantrieb
DK95810620T DK0767295T3 (da) 1995-10-03 1995-10-03 Hydraulisk ventildrev
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
FI963945A FI107751B (fi) 1995-10-03 1996-10-02 Hydraulinen käyttölaite
NO19964175A NO311188B1 (no) 1995-10-03 1996-10-02 Hydraulisk ventilstyring

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 EP0767295A1 (fr) 1997-04-09
EP0767295B1 true 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)

Families Citing this family (15)

* 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
EP1114918B1 (fr) * 2000-01-06 2004-08-11 Wärtsilä Schweiz AG Commande de soupape pour moteur à combustion interne et mode d'opération
DK176119B1 (da) * 2000-02-16 2006-09-04 Man B & W Diesel As System til hydraulisk aktivering af en udstödsventil i en forbrændingsmotor
DE10124869C2 (de) * 2001-05-22 2003-06-26 Caterpillar Motoren Gmbh & Co Hydraulische Steuereinrichtung für gleichwirkende Motorventile eines Dieselmotors
DE10140528A1 (de) * 2001-08-17 2003-02-27 Bosch Gmbh Robert Vorrichtung zur Steuerung von Gaswechselventilen
JP2004084670A (ja) * 2002-08-28 2004-03-18 Man B & W Diesel As 水圧で作動されるバルブ
DE10239747A1 (de) 2002-08-29 2004-03-11 Robert Bosch Gmbh Hydraulischer Ventilsteller zum Betätigen eines GAswechselventils
CN1289796C (zh) * 2003-10-13 2006-12-13 方戟 内燃式发动机的液压配气机构
JP5143833B2 (ja) * 2006-07-04 2013-02-13 ルノー・トラックス 油圧作動式弁制御システムおよびそのようなシステムを備える内燃機関
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
GB2552499B (en) * 2016-07-26 2019-11-27 Jaguar Land Rover Ltd Apparatus for controlling valves using a hydraulic control system
GB2553120B (en) * 2016-08-24 2019-12-25 Jaguar Land Rover Ltd Variable valve lift system with a diffusing system

Family Cites Families (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
EP0520633B1 (fr) * 1991-06-24 1996-08-14 Ford Motor Company Limited Dispositif de commande hydraulique de soupapes pour moteurs à combustion interne
AU9017291A (en) * 1991-07-12 1993-02-11 Caterpillar Inc. Recuperative engine valve system and method of operation

Also Published As

Publication number Publication date
NO964175D0 (no) 1996-10-02
FI963945A (fi) 1997-04-04
KR970021645A (ko) 1997-05-28
CN1160120A (zh) 1997-09-24
KR100403693B1 (ko) 2004-01-28
NO311188B1 (no) 2001-10-22
CN1088145C (zh) 2002-07-24
NO964175L (no) 1997-04-04
EP0767295A1 (fr) 1997-04-09
JPH09100706A (ja) 1997-04-15
DE59507966D1 (de) 2000-04-13
DK0767295T3 (da) 2000-06-05
JP3986585B2 (ja) 2007-10-03
FI963945A0 (fi) 1996-10-02
FI107751B (fi) 2001-09-28

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