EP1260680A2 - Hydraulische Steuereinrichtung für gleiche Ventile eines Dieselmotors - Google Patents
Hydraulische Steuereinrichtung für gleiche Ventile eines Dieselmotors Download PDFInfo
- Publication number
- EP1260680A2 EP1260680A2 EP02002524A EP02002524A EP1260680A2 EP 1260680 A2 EP1260680 A2 EP 1260680A2 EP 02002524 A EP02002524 A EP 02002524A EP 02002524 A EP02002524 A EP 02002524A EP 1260680 A2 EP1260680 A2 EP 1260680A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- control
- pressure
- piston
- valves
- control piston
- 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
Links
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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 Diesel engine, each having a valve stem and the spring means for an application in Valve closing direction and hydraulically adjustable Controls for loading valve opening and / or Closing direction are assigned, and the Controls are held in a bridge with one cylinder head is connected and the controls each one operatively connected to the engine valves Hydraulic cylinder with a pressurizing Control spool, depending on Piston positions of the engine via controllable solenoid valves is adjustable in several stages.
- a hydraulic control device for at least one lift valve an internal combustion engine known by one two counteracting spring means movable valve stem comprises, the valve stem in the area of its End position is hydraulically controllable.
- the hydraulic Control device includes a hydraulically controllable Spring means, which is a hydraulically acting auxiliary control member assigned.
- Control pistons are adjustable, which by means of electrical controllable valves with a corresponding control pressure be charged.
- the control pistons are in common a bridge arranged on a cylinder head of the Motor is attached.
- the controllability of the Control pistons can open and open the engine valves be closed as is the acceleration or Allow delays against the valve springs.
- the object of the invention is a hydraulic control device for lift valves of an internal combustion engine and one Create recording for controls of the facility which, on the one hand, enables simple hydraulic control the intake and / or exhaust valves of an internal combustion engine in the opening and closing direction according to the piston position is guaranteed and on the other hand the controls are held in a simple manner on the cylinder head can.
- the main advantages achieved with the invention consist of the fact that hydraulic controls Control device, the inlet and / or outlet valves Internal combustion engine accordingly in an opening and Closing movement can be controlled and the controls for this in a firmly connected to the cylinder head Bridge are arranged and thus the controls directly and directly on the valve stems of the valves can act.
- the control for the Valves are held in at least one common bridge, which is firmly connected to a cylinder head of the engine and the controls each have an engine valve active hydraulic cylinder with a pressurizable Control piston includes. This becomes dependent of electrically controllable valves in several Levels continuously controlled, with the engine valves open or close depending on the spool.
- the bridge is preferred for receiving the controls T-shaped and has a central stand a transverse head bridge, with the stand over at least one screw with the cylinder head of the Motor is firmly connected and cylindrical in the top bridge or corresponding mounts for the hydraulic cylinders or are provided for the controls.
- the effect of the controls on the engine valves is such that those designed as stepped pistons or cylinder pistons Control piston of the controls the engine valves in a preliminary stage in the open and closed position hold when the piston is in TDC and in one another subsequent stage, the intake valves on the Spool a maximum opening or closing position can take.
- the pressure chambers in the control piston of the Control elements for equivalent valves, such as intake valves or exhaust valves are via pressure supply lines connected with each other, opening and Closing the pressure lines by means of, for example, electrical controllable solenoid valves.
- the control piston is successively connected via two pressure lines pressurized, the control piston of the hydraulic cylinder in the pressure chamber above the control piston has merging control channels, and in a first Control process of the pressure chamber via the pressure line and the subsequent control channels in the control piston with a control pressure be added and subsequently in a second Control process the pressure lines and the subsequent ones Control channels with a quasi-superimposed control pressure for further pressure chamber can be acted upon until an outflow bore released from the control piston in the hydraulic cylinder becomes.
- the pressure chamber above the control piston is in the first control process of the pressure from the one pressure line pressurized, the further pressure line being depressurized is open and with both released by the control piston Mouth openings of the pressure lines is via the second Pressure line pressurizing the control piston up to to release the discharge opening.
- the piston is expediently designed as a stepped piston.
- the effective areas of the stepped piston are calculated the spring force.
- the stepped piston preferably has one inner transverse control channel with a Ring channel is connected, the transverse control channel in an axial inner control channel in the Control piston opens and this an upper pressure chamber is prepared.
- the pressure supply lines to the control piston are on top of each other with their junctions in the pressure chamber arranged and in relation to the preliminary stage of the control piston becomes the one pressurized pressure supply line open into the annulus, the further pressure supply line in a lower pressure chamber of the control piston opens.
- the step piston according to the invention is a preliminary step hydraulically via a first and a subsequent second stage via the solenoid valves in the pressure supply lines controlled, the control piston being pressurized adjustable from the preliminary stage to a first stage is formed, in which both pressure lines in the ring channel open out and the control piston can be controlled in this way is that depending on the towards the TDC position of the engine piston, the second pressure line with a control pressure is acted upon by the solenoid valve and the control piston in the further second stage to achieve a maximum stroke is movable.
- the annulus of the Step piston is arranged in this second stage in such a way that an outflow opening or bore is released is.
- An opening of the control piston can be done by using bevelled edges be gently designed on the piston, as can on At the end of the opening process, an oblique edge on the piston End the opening process gently. Furthermore, the control piston have a circumferentially beveled head area.
- Fig. 1 is a basic training and arrangement of control elements 1, 2 with control piston 8; 8a for engine valves 4, 5 of an internal combustion engine in a bridge 3, especially for two identical intake or exhaust engine valves 4, 5 with pressure supply lines 6, 7 shown.
- These lines 6, 7 are, for example, with control channels 11, 12 and 11a, 12a connected in the bridge 16, that in control channels 11b, 11c, 11d, for example in the Control piston 8, open out.
- the pressure lines 6, 7 are on the input side with electrically controllable solenoid valves 9, 10 connected for pressure control.
- a control piston 1, 2 is each with a valve stem 4a, 5a of the valves 4, 5 operatively connected, the valves 1, 2 held in the closed position via valve springs 13, 14 are.
- the Control piston 1, 2 held in the bridge 3 this is approximately T-shaped and has a central stand 15 as well as a transverse head web 16 comprises by the control pistons 1, 2 are held on both sides of the stand 15 are.
- the stand 15 itself is fixed to the cylinder head 17 connected via at least one screw 18.
- in the Top bridge 16 of bridge 3 is preferably the control channels 11, 12 and 11a, 12a, which are connected to the pressure lines 6, 7 are connected in the cylinder head 17.
- the controls 1, 2 are in corresponding cylindrical receptacles 20 held in the top bridge 16 of the bridge 3.
- the controls 1, 2 acc. Fig. 1 are in several consecutive Levels V, I and II through hydraulic Pressure control axially adjustable, with each control 1, 2 via its control piston 8; 8a an adjustment pressure exerts on the valve stem 4a, 5a of the valve 4, 5, which causes them to open or close can move according to the engine piston position, such as is shown in more detail with the aid of the diagram in FIG. 3.
- a preliminary stage V. (Valves 4 and 5 are closed), a subsequent stage II (engine piston 21 is in TDC position) and then one Stage II (valves 4 and 5 are open) activated.
- control element 1, 2 are approximately above the Control piston 8; 8a transverse control channels 11a, 12a assigned that with vertically running further control channels 11, 12 are connected, which in the pressure lines 6, 7 open out by the solenoid valves or Two / two-way valves 9, 10 can be controlled by pressure.
- 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 in a first control process from hydraulic pressure from the first pressure line 6 via the Control channels 11, 11a and then via 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 drain holes 25; 26 releases. This measure should be such that the Engine valves 4, 5 do not move the piston 21 in the TDC position can touch. If the engine piston 21 is far enough has moved away from the TDC position, so does the pressure line 7 pressurized with oil pressure, causing the valves 4, 5 now open further and after exposing the Drain holes 25; 26 the maximum stroke H is reached and in this position, the oil can now drain off.
- the opening and the pressure lines 6, 7 are closed via the valves 9, 10.
- the diameter of the control piston 8; 8a should be dimensioned so that the valves 4, 5 against the force of Valve springs 13, 14 can be opened.
- control piston is preferably also designed as a stepped piston 8a be, as shown in Figs. 2, 4, and 6 in more detail is.
- stepped piston 8a. 4 is in the upper pressure chamber D via the control channel 11a in the Bridge 16, which is connected to the pressure line 6, Given oil pressure, so that the control piston 8a from the preliminary stage V moves into the subsequent stage I and in this Stage I remains stable until the engine piston 21 again goes down and the solenoid valve 9 pressure on the line 7 and thus on the control channel 12a.
- control piston 8a opens up to the maximum stroke H (diagram Fig. 3).
- the stroke limitation serves on the one hand Spring force of the valve springs 13, 14 to which the oil pressure can be coordinated and on the other hand the drain hole 26, now released from the top edge of the spool 8a is so that the oil can escape freely.
- the motor valve 4,5 closes in the reverse order, by first solenoid valve 9 opening pressure line 7 Passage switches and drains the oil and in stage II the further solenoid valve 10 also switches the pressure line 6 on passage.
- the opening of the control piston 8; 8a can be done by means of a bevel edge 27 (Fig. 8) on the piston head 28 take place gently, whereby likewise at the end of the opening process, the inclined edge 27 on the piston head, end the opening process accordingly can.
- the closing takes place in the same way at the beginning gently over the bevel 27 and the closing process of the Motor valve is braked again by the sloping edge.
- control piston 8a used, as in Figs. 4, 5 and 6 and others. is shown. Via the upper control channel 11a of the control piston 8a in Fig. 4 is the control piston 8a from above in Opressure chamber D acts and moves up to Release of the lower control channel 12a of stage 1, which too is still open at this point and oil can escape freely. In this phase, the control piston 8a and the valve remain 4,5 until the control channel 12a of stage II is either closed will or even 01 in the cylinder of the Control piston 8a promotes. Because the spring force increases with the stroke should grow for a constant oil pressure Control piston 8a in stage II approximately twice the area have or the prevailing spring force in diameter be adjusted.
- control piston 8 can also acc. Fig. 2 are formed.
- the oil penetrates the hydraulic cylinder through the control channel 11 via an annular channel 11d into a transverse bore 11b and then in an axial bore 11c and opens the control piston 8 to level 1.
- the control channel 11a is closed and the control channel 12a opens. This minimizes oil loss.
- Oil pressure is supplied to the hydraulic cylinder via the control line 12a given. This oil flow is when the Maximum stroke H also completed, opens at the same time the drain hole 26, from which the remaining oil is then released can leak.
- Stroke limiter acc. Fig. 11 provided the inserted from Screws 30.31 or approaches can exist.
Abstract
Description
- Fig. 1
- eine Ansicht teilweise im Schnitt auf eine ortsfeste Brücke am Zylinderkopf mit aufgenommenen Steuerelementen der Einrichtung, die über Druckversorgungsleitungen mit Magnetventilen verbunden sind,
- Fig. 2
- eine Darstellung eines Steuerelements mit einem Stufenkolben in drei Stellungen,
- Fig. 3
- ein Ablaufdiagramm der Öffnungs- und Schließbewegungen der Motorventile mit Bezug auf die Kolbenstellung und der Stellungen der Steuerelemente,
- Fig. 4, 5 und 6
- Darstellungen eines Steuerelements in einer Vorstufe , einer Stufe 1 bei OT-Stellung des Motorkolbens und einer Stufe II bei voll geöffnetem Motoreinlaßventil,
- Fig. 7
- eine Darstellung des Gesamthubes und eines Vorhubes eines Motorventils anhand der Stellung des Steuerkolbens im Hydraulikzylinder,
- Fig. 8
- eine Einzelheit eines mit zwei Schrägflächen aufweisenden Steuerkolbens,
- Fig. 9
- eine Darstellung des gesamten Steuerzylinders mit beiden Schrägflächen,
- Fig. 10
- eine Darstellung des Steuerzylinders mit einem oberen und unteren Anschlag und
- Fig. 11
- eine Darstellung einer Brücke am Zylinderkopf gem. Fig. 1 zur Aufnahme der Hydraulikzylinder.
Claims (10)
- Hydraulische Steuereinrichtung für gleiche Ventile eines Dieselmotors, die jeweils einen Ventilschaft aufweisen und dem Federmittel für eine Beaufschlagung in Ventilschließrichtung und hydraulisch regelbare Steuerelemente für eine Beaufschlagung in Ventilöffnungs- und/oder Schließrichtung zugeordnet sind, und die Steuerelemente in einer Brücke gehalten sind, die mit einem Zylinderkopf verbunden ist und die Steuerelemente jeweils einen mit den Motorventilen wirkverbundenen Hydraulikzylinder mit einem druckbeaufschlagenden Steuerkolben umfassen, der in Abhängigkeit von Kolbenstellungen des Motors über ansteuerbare Magnetventile in mehrere Stufen verstellbar ist, dadurch gekennzeichnet, daß im Steuerkolben (8, 8a) für die gleichen Ventile (4, 5) Druckräume (D, D1) vorgesehen sind, welche über Steuerkanäle (11, 12, 11a, 12a) mit Druckversorgungsleitungen (6, 7) verbunden sind und ein Öffnen und Schließen dieser Leitungen (6, 7) mittels der Magnetventile (9, 10) erfolgt und daß die Steuerkolben (8, 8a) der Steuerelemente (1, 2) die Motorventile · (4, 5) in einer Vorstufe (V) in Schließstellung (S) und in einer nachfolgenden Stufe (I) bei OT-Stellung des Motorkolbens (21) mit einem Vorhub (VH) halten und in einer weiteren Stufe (II) die Motorventile (4, 5) über die Steuerkolben (8, 8a) in eine maximale Öffnungsstellung verstellbar sind.
- Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Steuerkanäle (11, 12, 11a, 12a) oberhalb des Druckraumes (D) des Steuerkolbens (8, 8a) einmünden und in einem ersten Steuervorgang der Druckraum (D) über die Druckleitung (6) und die Steuerkanäle (11, 11a; 11b, 11c) mit einem Steuerdruck beaufschlagbar ist und nachfolgend in einem zweiten Steuervorgang die Druckleitung (7) und die Steuerkanäle (12, 12a; 11b, 11c) mit einem überlagernden Steuerdruck zum weiteren unteren Druckraum (Dl) beaufschlagbar sind, bis eine Abströmbohrung (25; 26) im Hydraulikzylinder vom Steuerkolben (8a; 8) freigebbar ist.
- Einrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Druckraum (D) im ersten Steuervorgang vom Druck an der Druckleitung (6) beaufschlagbar ist, wobei die weitere Druckleitung (7) druckfrei geöffnet ist und bei vom Steuerkolben (8a; 8) freigegebenen beiden Mündungsöffnungen der Druckleitungen (6, 7) über die zweite Druckleitung (7) eine Druckbeaufschlagung des Steuerkolbens (8a;8) bis zur Freigabe der Abströmöffnungen (26:25) erfolgt.
- Einrichtung nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Steuerkolben als Stufenkolben (8) ausgebildet ist und einen mit dem querverlaufenden Steuerkanal (11b) verbundenen Ringkanal (11d) aufweist und der Steuerkanal (11b) mit dem weiteren axialen Steuerkanal (11c) verbunden ist, der einem Druckraum (D) zugerichtet ist.
- Einrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß die Druckversorgungsleitungen (6, 7) mit ihren Einmündungen in den Druckraum (D) übereinander angeordnet sind und - in Bezug auf die Vorstufe (V) - die eine mit Druck beaufschlagte Versorgungsleitung in den Ringraum (11d) einmündet, wobei die weitere Druckversorgungsleitung in den unteren Druckraum (Dl) des Steuerkolbens (8) einmündet.
- Einrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß der Steuerkolben (8) druckbeaufschlagt über die Druckleitung (6) von der Vorstufe (V) in die Stufe (I) verstellbar ausgebildet ist, bei der beide Druckleitungen (6,7) in den Ringkanal (11d) einmünden und der Steuerkolben (8) derart ansteuerbar ist, daß in Abhängigkeit von der in Richtung OT-Stellung des Motorkolbens (21) die Druckleitung (7) mit einem Steuerdruck vom Magnetventil (9) beaufschlagbar ist und der Steuerkolben (8) in der Stufe II zur Erzielung eines maximalen Stellhubes verfahrbar ist.
- Einrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß der Ringkanal (11d) des Steuerkolbens (8) in der Stufe (II) eine Abströmöffnung (26) freigebend angeordnet ist.
- Einrichtung nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß in der Stufe (II) zuerst das Magnetventil (9) der Druckleitung (7) auf Durchgang schaltbar ist und nachfolgend das weitere Magnetventil (10) der Druckleitung (6) abschaltbar ist, wobei das 01 im Druckraum abfließt.
- Einrichtung nach einem der Ansprüche 1 bis 8, dadurch gekennzeichnet, daß ein abgestufter Kolben des Steuerkolbens (8; 8a) einen umfangsseitig abgeschrägten Kopfbereich (27) aufweist.
- Einrichtung nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß die Brücke (3) T-förmig ausgebildet ist und einen zentralen Ständer (15) mit einem querverlaufenden Kopfsteg (16) umfaßt und der Ständer (15) über mindestens ein Schraubmittel (18) mit dem Zylinderkopf (17) verbunden ist und im Kopfsteg (16) in Aufnahmen (20) die Steuerelemente (1, 2) gehalten sind.
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 true EP1260680A2 (de) | 2002-11-27 |
EP1260680A3 EP1260680A3 (de) | 2003-05-02 |
EP1260680B1 EP1260680B1 (de) | 2006-04-05 |
Family
ID=7685687
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP02002524A Expired - Lifetime EP1260680B1 (de) | 2001-05-22 | 2002-02-04 | Hydraulische Steuereinrichtung für gleiche Ventile eines Dieselmotors |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1260680B1 (de) |
AT (1) | ATE322610T1 (de) |
DE (2) | DE10124869C2 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2878559A1 (fr) * | 2004-11-30 | 2006-06-02 | Renault Sas | Dispositif d'actionnement des soupapes d'un moteur thermique sans arbre a cames et piston de soupape en deux parties |
EP1607593A3 (de) * | 2004-06-17 | 2007-01-03 | Isuzu Motors Limited | Ausslassventilantrieb Steuerungsverfahren und Vorrichtung |
WO2008004020A1 (en) * | 2006-07-04 | 2008-01-10 | Renault Trucks | Hydraulically operated valve control system and internal combustion engine comprising such a system |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1993001399A1 (en) | 1991-07-12 | 1993-01-21 | Caterpillar Inc. | Recuperative engine valve system and method of operation |
DE19716042C1 (de) | 1997-04-17 | 1998-05-07 | Daimler Benz Ag | Hydraulische Steuervorrichtung für wenigstens ein Hubventil |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
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 |
-
2001
- 2001-05-22 DE DE10124869A patent/DE10124869C2/de not_active Expired - Fee Related
-
2002
- 2002-02-04 AT AT02002524T patent/ATE322610T1/de not_active IP Right Cessation
- 2002-02-04 DE DE50206283T patent/DE50206283D1/de not_active Expired - Fee Related
- 2002-02-04 EP EP02002524A patent/EP1260680B1/de not_active Expired - Lifetime
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO1993001399A1 (en) | 1991-07-12 | 1993-01-21 | Caterpillar Inc. | Recuperative engine valve system and method of operation |
DE19716042C1 (de) | 1997-04-17 | 1998-05-07 | Daimler Benz Ag | Hydraulische Steuervorrichtung für wenigstens ein Hubventil |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1607593A3 (de) * | 2004-06-17 | 2007-01-03 | Isuzu Motors Limited | Ausslassventilantrieb Steuerungsverfahren und Vorrichtung |
US7191744B2 (en) | 2004-06-17 | 2007-03-20 | Isuzu Motors Limited | Exhaust valve drive control method and device |
CN100510328C (zh) * | 2004-06-17 | 2009-07-08 | 五十铃自动车株式会社 | 排气阀驱动控制方法和装置 |
FR2878559A1 (fr) * | 2004-11-30 | 2006-06-02 | Renault Sas | Dispositif d'actionnement des soupapes d'un moteur thermique sans arbre a cames et piston de soupape en deux parties |
WO2008004020A1 (en) * | 2006-07-04 | 2008-01-10 | Renault Trucks | Hydraulically operated valve control system and internal combustion engine comprising such a system |
US8365690B2 (en) | 2006-07-04 | 2013-02-05 | Renault Trucks | Hydraulically operated valve control system and internal combustion engine comprising such a system |
Also Published As
Publication number | Publication date |
---|---|
EP1260680A3 (de) | 2003-05-02 |
ATE322610T1 (de) | 2006-04-15 |
DE10124869A1 (de) | 2002-12-12 |
DE50206283D1 (de) | 2006-05-18 |
DE10124869C2 (de) | 2003-06-26 |
EP1260680B1 (de) | 2006-04-05 |
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