EP1260680B1 - Dispositif d'actionnement de 2 soupapes simultanément dans un moteur diesel - Google Patents

Dispositif d'actionnement de 2 soupapes simultanément dans un moteur diesel Download PDF

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Publication number
EP1260680B1
EP1260680B1 EP02002524A EP02002524A EP1260680B1 EP 1260680 B1 EP1260680 B1 EP 1260680B1 EP 02002524 A EP02002524 A EP 02002524A EP 02002524 A EP02002524 A EP 02002524A EP 1260680 B1 EP1260680 B1 EP 1260680B1
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EP
European Patent Office
Prior art keywords
control
pressure
piston
valves
stage
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
EP02002524A
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German (de)
English (en)
Other versions
EP1260680A2 (fr
EP1260680A3 (fr
Inventor
Hans-Jürgen Schacht
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.)
Caterpillar Motoren GmbH and Co KG
Original Assignee
Caterpillar Motoren GmbH and Co KG
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Publication date
Application filed by Caterpillar Motoren GmbH and Co KG filed Critical Caterpillar Motoren GmbH and Co KG
Publication of EP1260680A2 publication Critical patent/EP1260680A2/fr
Publication of EP1260680A3 publication Critical patent/EP1260680A3/fr
Application granted granted Critical
Publication of EP1260680B1 publication Critical patent/EP1260680B1/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
    • 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
    • F01L2800/00—Methods of operation using a variable valve timing mechanism

Definitions

  • Hydraulic control device for the same valves of a diesel engine, each having a valve stem and are associated with the spring means for acting in the valve closing direction and hydraulically controllable controls for acting in Ventilötechnischs- and / or closing direction, and the controls are held in a bridge, which with a Cylinder head is connected and the controls each comprise a functionally connected to the engine valves hydraulic cylinder with a pressurizing control piston which is adjustable in response to piston positions of the engine via controllable solenoid valves in several stages.
  • DE 197 16 042 C1 discloses a hydraulic control device for at least one lifting valve of an internal combustion engine, which comprises a valve stem movable by two spring means acting against each other, wherein the valve stem can be hydraulically actuated in the region of its end position.
  • the hydraulic control device includes a hydraulically controllable spring means, which is assigned a hydraulically acting auxiliary control member.
  • the object of the invention is to provide a hydraulic control device for globe valves of an internal combustion engine and a receptacle for controls of the device, whereby on the one hand a simple hydraulic control of the intake and / or exhaust valves of an internal combustion engine in the opening and closing direction is ensured according to the piston position and on the other the controls can be easily held on the cylinder head.
  • the inlet and / or exhaust valves of an internal combustion engine can be controlled accordingly in an opening and closing movement and for this purpose the controls are arranged in a fixedly connected to the cylinder head bridge and thus the controls can act directly and directly on the valve stems of the valves.
  • the control for the valves are held in at least one common bridge which is fixedly connected to a cylinder head of the engine and the controls each operatively connected to an engine valve hydraulic cylinder with a pressurizable Spool includes. This is driven in response to electrically controllable valves in several stages continuously, the engine valves open or close depending on the control piston.
  • the bridge is for receiving the controls preferably T-shaped and has a central stator with a transverse head land, the stand is firmly connected via at least one screw with the cylinder head of the engine and cylindrical head or corresponding receptacles for the hydraulic cylinder or are provided for the controls.
  • the effect of the controls on the engine valves is such that the control pistons of the controls designed as stepped pistons or cylinder pistons hold the engine valves in a preliminary stage in the open and closed positions when the piston is in TDC and in a further subsequent stage the intake valves over the Control piston can take a maximum opening or closing position.
  • the pressure chambers in the control piston of the controls for the same effect valves, such as inlet valves or exhaust valves are connected to each other via pressure supply lines, wherein an opening and closing of the pressure lines by means of, for example, electrically controllable solenoid valves.
  • the control piston is acted upon in succession via two pressure lines with pressure, wherein the control piston of the hydraulic cylinder in the pressure chamber above the control piston has opening control channels, and in a first control process, the pressure chamber via the pressure line and the subsequent control channels in the control piston are baufschlagt with a control pressure and subsequently in a second control process, the pressure lines and the subsequent control channels are acted upon with a quasi overlapping control pressure to the other pressure chamber until a discharge hole in the hydraulic cylinder is released from the control piston.
  • the pressure chamber above the control piston is acted upon in the first control process by the pressure from the one pressure line, wherein the other pressure line is opened pressure-free and released from the control piston two mouth openings of the pressure lines via the second pressure line pressurization of the control piston until release of the discharge opening.
  • the piston is expediently designed as a stepped piston.
  • the effective areas of the stepped piston are calculated according to the spring force.
  • the stepped piston preferably has an inner transverse control channel which is connected to an annular channel, wherein the transverse control channel opens into an axial further inner control channel in the control piston and this is an upper pressure chamber trimmed.
  • the pressure supply lines to the control piston are arranged one above the other with their junctions in the pressure chamber and with respect to the precursor of the control piston, the one pressurized pressure supply line will open into the annular space, wherein the further pressure supply line opens into a lower pressure chamber of the control piston.
  • the stepped piston according to the invention is hydraulically controlled by a preliminary stage via a first and a subsequent second stage via the solenoid valves in the pressure supply lines, wherein the control piston is pressurized from the precursor to a first stage adjustable, open at both pressure lines in the annular channel and the control piston is controlled such that in response to the direction of the TDC position of the engine piston, the second pressure line is acted upon by a control pressure from the solenoid valve and the control piston in the further second stage to achieve a maximum setting stroke is movable.
  • the annular space of the stepped piston is arranged in this second stage such that a discharge opening or bore is released.
  • An opening of the control piston can be made gentle by adapted bevels on the piston, as well as at the end of the opening process, a bevel on the piston finish the opening process gently.
  • the control piston may have a circumferentially bevelled head area.
  • Fig. 1 is a basic design and arrangement of controls 1, 2 with control piston 8; 8a for engine valves 4, 5 of an internal combustion engine in a bridge 3, in particular for two equal-acting inlet or outlet engine valves 4, 5 with pressure supply lines 6, 7 shown.
  • These lines 6, 7 are connected, for example, with control channels 11, 12 and 11a, 12a in the bridge 16, which open into control channels 11b, 11c, 11d, for example in the control piston 8.
  • the pressure lines 6, 7 are the input side connected to electrically controllable solenoid valves 9, 10 for pressure control.
  • a control piston 1, 2 is in each case operatively connected to a valve stem 4a, 5a of the valves 4, 5, the valves 1, 2 being held in the closed position via valve springs 13, 14.
  • the control pistons 1, 2 are held in the bridge 3, wherein this is designed approximately T-shaped and comprises a central post 15 and a transverse head bar 16 by on both sides of the stator 15th the control piston 1, 2 are held.
  • the stand 15 itself is firmly connected to the cylinder head 17 via at least one screw 18.
  • the control channels 11, 12 and 11a, 12a are preferably recessed, which are connected to the pressure lines 6, 7 in the cylinder head 17.
  • the controls 1, 2 are held in corresponding cylindrical receptacles 20 in the headpiece 16 of the bridge 3.
  • the controls 1, 2 gem. Fig. 1 are in several successive stages V, I and II axially adjustable by hydraulic pressure control, each control 1, 2 via its control piston 8, 8a an adjusting pressure on the valve stem 4a, 5a of the valve 4, 5 exerts, causing them in a .Opening or closing position can move according to the engine piston position, as shown in more detail with reference to the diagram Fig. 3.
  • a precursor V valves 4 and 5 are closed
  • a subsequent stage II engine piston 21 is in TDC position
  • a stage II valves 4 and 5 are open
  • control 1, 2 are approximately above the control piston 8; 8a transverse control channels 11a, 12a, which are connected to vertically extending further control channels 11, 12, which open into the pressure lines 6, 7, which can be pressure-controlled by the solenoid valves or two / two-way valves 9, 10.
  • the control channels 11a and 12a are with control channels 11b, c and d in the control piston 8; 8a connected.
  • An upper pressure chamber D in the hydraulic cylinder of the control elements 1, 2 is acted upon in a first control process by the hydraulic pressure from the first pressure line 6 via the control channels 11, 11a and then via the channels 11b and 11c, the second pressure line 7 initially remains open.
  • the engine valves 4, 5 are opened until the control piston 8; 8a, the drainage holes 25; 26 releases. This measure should be such that the engine valves 4, 5 can not touch the piston 21 in TDC position.
  • the pressure line 7 is acted upon by oil pressure, whereby the valves 4, 5 now open further and after exposing the drain holes 25; 26 of the maximum stroke H is reached and in this position now the oil can flow.
  • the diameter of the control piston 8; 8a should be so dimensioned that the valves 4, 5 can be opened against the force of the valve springs 13, 14.
  • control piston can preferably also be designed as a stepped piston 8a, as shown in more detail in FIGS. 2, 4, and 6 is.
  • the mode of operation whether a stepped piston or a differently designed control piston is used, is basically the same, as far as a sequence according to the diagram acc. Fig. 3 takes place.
  • the engine valve 4.5 closes in reverse order by first the solenoid valve 9, the pressure line 7 switches to passage and the oil drains and in stage II, the other solenoid valve 10 switches the pressure line 6 to passage.
  • the opening of the control piston 8, 8a can be effected gently by a bevelled edge 27 (FIG. 8) on the piston head 28, wherein also at the end of the opening process the bevel 27 on the piston head can end the opening process accordingly.
  • the closing takes place in the same way at the beginning gently over the inclined edge 27 and the closing operation of the engine valve is braked again by the beveled edge.
  • control piston 8a is advantageously used, as is shown in FIGS. 4, 5 and 6 and the like. is shown. Via the upper control channel 11a of the control piston 8a in Fig. 4, the control piston 8a is initially acted upon from above in 0Druckraum D and moves a maximum until the release of the lower control channel 12a of stage 1, which is still open at this time and leak oil freely leaves. In this phase, the control piston 8a and the valve remains 4.5 until the control channel 12a stage II is either closed or even 01 promotes into the cylinder of the control piston 8a. Since the spring force increases with increasing stroke, the control piston 8a in stage II should have about twice the area or the prevailing spring force must be adapted in diameter for a constant oil pressure.
  • control piston 8 can also gem.
  • Fig. 2 are formed.
  • the oil penetrates into the hydraulic cylinder through the control channel 11 via a ring channel 11d in a transverse bore 11b and then into an axial bore 11c and opens the control piston 8 to the stage 1.
  • the control channel 11a Upon reaching the stage 1, the control channel 11a is closed and the control channel 12a opens. The oil loss is thereby minimized.
  • Oil pressure is supplied to the hydraulic cylinder via the control line 12a. This oil flow is also completed when reaching the maximum stroke H, at the same time opens the drain hole 26, from which then the remaining oil can escape freely.
  • Fig. 11 is provided, which may consist of inserted screws 30,31 or lugs.

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

Claims (10)

  1. Dispositif de commande hydraulique pour des soupapes identiques d'un moteur diesel, comportant chacune une tige de soupape avec associés à celle-ci un système de ressort qui sollicitent la soupape dans la direction de fermeture et des éléments de commande réglables hydrauliquement qui sollicitent la soupape dans la direction de l'ouverture et/ou de la fermeture, les éléments de commande étant logés dans un pontet qui est lié à une culasse de moteur et les éléments de commande comprenant chacun un vérin hydraulique avec un piston de commande sollicité par une pression, qui est lié activement aux soupapes du moteur et qui, en fonction de positions de piston du moteur, peut être déplacé en plusieurs étapes par l'intermédiaire d'électrovannes, caractérisé par le fait qu'il est prévu dans le piston de commande (8, 8a) pour les soupapes identiques (4, 5) des chambres de pression (D, D1) qui sont reliées à des conduites de pression (6, 7) par l'intermédiaire de canaux de commande (11, 12, 11a, 12, que lesdites conduites (6, 7) sont ouvertes et fermées au moyen d'électrovannes (9, 10), par le fait que les pistons de commande (8, 8a) des éléments de commande (1, 2) maintiennent les soupapes de moteur (4, 5) dans la position ferméc dans une pré-phase (V) et avec une levée partielle (VH) dans une phase (1) consécutive, au voisinage du point mort supérieur du piston de moteur (21), et que dans une phase supplémentaire (Il) les soupapes de moteur (4, 5) sont amenées dans une position d'ouverture maximale par les pistons de commande (8, 8a).
  2. Dispositif selon la revendication 1, caractérisé par le fait que les canaux de commande (11, 12, 11a, 12a) débouchent au-dessus de la chambre de pression (D) du piston de commande (8, 8a) et que dans une première action de commande une pression de commande est appliquée à la chambre de pression (D) par l'intermédiaire de la conduite de pression (6) et des canaux de commande (11, 11a; 11b, 11c), puis dans une deuxième action de commande, une pression de commande combinée est appliquée à la chambre de pression (DI) inférieure supplémentaire jusqu'à cc qu'un trou de décharge (25, 26) dans le corps de cylindre soit découvert par le piston (8, 8a).
  3. Dispositif selon la revendication 1 ou 2, caractérisé par le fait que la chambre de pression (D) dans la première action de commande est sollicitée par la pression de la conduite de pression (6), l'autre conduite de pression (7) étant ouverte sans pression, et que lorsque le piston de commande (8a, 8) a découvert les deux orifices des conduites de pression (6, 7) le piston de commande (8a, 8) est sollicité en pression par l'intermédiaire de la deuxième conduite de pression (7) jusqu'à ce que les orifices de décharge (25, 26) soient découverts.
  4. Dispositif selon une des revendications 1 à 3, caractérisé par le fait que le piston de commande est conformé en piston étagé (8) et présente un canal annulaire (11d) qui communique avec le canal de commande (11b) transversal et que le canal de commande (11b) transversal communique avec le canal de commande (11c) transversal supplémentaire menant à une chambre de pression (D).
  5. Dispositif selon une des revendications 1 à 4, caractérisé par le fait que les arrivées des conduites de pression (6, 7) dans la chambre de pression (D) sont disposées l'une au-dessus de l'autre - par rapport à la pré-phase (V) - et qu'une conduite de pression alimentée en pression débouche dans la chambre annulaire (11d), l'autre conduite de pression débouchant dans la chambre de pression (D1) inférieure du piston de commande (8).
  6. Dispositif selon une des revendications 1 à 5, caractérisé par le fait que le piston de commande (8), par une pression appliquée via la conduite de pression (6), peut être déplacé de la pré-phase (V) dans la phase (I), dans laquelle les deux conduites de pression (6, 7) débouchent dans le canal annulaire (11d) et le piston de commande (8) peut être piloté de telle sorte qu'en fonction de la position du piston de moteur en direction du point mort supérieur, la conduite de pression (7) peut être alimentée avec une pression de commande par l'électrovanne (9) et le piston de commande (8) déplacé dans la phase (II) aux fins d'obtenir une levée maximale.
  7. Dispositif selon une des revendications 1 à 6, caractérisé par le fait que le canal annulaire (11d) du piston de commande (8) dans la phase (II) est positionné de manière à découvrir un orifice de décharge (26).
  8. Dispositif selon une des revendications 1 à 7, caractérisé par le fait que dans la phase (11) l'électrovannc (9) de la conduite de pression (7) est commutée en premier en mode passant, puis l'autre électrovanne (10) de la conduite de pression (6) est fermée, l'huile hydraulique s'écoulant dans la chambre de pression.
  9. Dispositif selon une des revendications 1 à 8, caractérisé par le fait qu'un piston étagé du piston de commande (8, 8a) présente une tête dont le pourtour est chanfreiné.
  10. Dispositif selon une des revendications 1 à 9, caractérisé par le fait que le pontet (3) est conformé en T et comporte un élément support (15) avec une traverse frontale (16) et que l'élément support (15) est lié à la culasse (17) par au moins deux vis (18) et que les éléments de commande (1, 2) sont disposés dans la traverse frontale (16), dans des logements (20).
EP02002524A 2001-05-22 2002-02-04 Dispositif d'actionnement de 2 soupapes simultanément dans un moteur diesel Expired - Lifetime EP1260680B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10124869A DE10124869C2 (de) 2001-05-22 2001-05-22 Hydraulische Steuereinrichtung für gleichwirkende Motorventile eines Dieselmotors
DE10124869 2001-05-22

Publications (3)

Publication Number Publication Date
EP1260680A2 EP1260680A2 (fr) 2002-11-27
EP1260680A3 EP1260680A3 (fr) 2003-05-02
EP1260680B1 true EP1260680B1 (fr) 2006-04-05

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EP02002524A Expired - Lifetime EP1260680B1 (fr) 2001-05-22 2002-02-04 Dispositif d'actionnement de 2 soupapes simultanément dans un moteur diesel

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EP (1) EP1260680B1 (fr)
AT (1) ATE322610T1 (fr)
DE (2) DE10124869C2 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4182922B2 (ja) * 2004-06-17 2008-11-19 いすゞ自動車株式会社 排気弁駆動制御方法及び装置
FR2878559B1 (fr) * 2004-11-30 2009-07-03 Renault Sas Dispositif d'actionnement des soupapes d'un moteur thermique sans arbre a cames et piston de soupape en deux parties
US8365690B2 (en) 2006-07-04 2013-02-05 Renault Trucks Hydraulically operated valve control system and internal combustion engine comprising such a system

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1993001399A1 (fr) * 1991-07-12 1993-01-21 Caterpillar Inc. Systeme de soupape de moteur a recuperation et son procede de fonctionnement
US6148778A (en) * 1995-05-17 2000-11-21 Sturman Industries, Inc. Air-fuel module adapted for an internal combustion engine
DK0767295T3 (da) * 1995-10-03 2000-06-05 Wortsilo Nsd Schweiz Ag Hydraulisk ventildrev
DE19716042C1 (de) * 1997-04-17 1998-05-07 Daimler Benz Ag Hydraulische Steuervorrichtung für wenigstens ein Hubventil
JPH1130135A (ja) * 1997-07-11 1999-02-02 Nippon Soken Inc ディーゼルエンジンの制御装置

Also Published As

Publication number Publication date
DE10124869C2 (de) 2003-06-26
DE10124869A1 (de) 2002-12-12
EP1260680A2 (fr) 2002-11-27
DE50206283D1 (de) 2006-05-18
ATE322610T1 (de) 2006-04-15
EP1260680A3 (fr) 2003-05-02

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