EP1662098B1 - Commande de soupape variable de moteur à combustion interne - Google Patents

Commande de soupape variable de moteur à combustion interne Download PDF

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Publication number
EP1662098B1
EP1662098B1 EP05024165A EP05024165A EP1662098B1 EP 1662098 B1 EP1662098 B1 EP 1662098B1 EP 05024165 A EP05024165 A EP 05024165A EP 05024165 A EP05024165 A EP 05024165A EP 1662098 B1 EP1662098 B1 EP 1662098B1
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EP
European Patent Office
Prior art keywords
valve
hydraulic
valve drive
internal combustion
combustion engine
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 - Fee Related
Application number
EP05024165A
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German (de)
English (en)
Other versions
EP1662098A1 (fr
Inventor
Eduard Golovatai-Schmidt
Valeria Prof.- Dr. Vacarescu
Wolfgang Dr. Reik
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.)
IHO Holding GmbH and Co KG
Original Assignee
Schaeffler KG
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 Schaeffler KG filed Critical Schaeffler KG
Publication of EP1662098A1 publication Critical patent/EP1662098A1/fr
Application granted granted Critical
Publication of EP1662098B1 publication Critical patent/EP1662098B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/18—Rocking arms or levers
    • F01L1/185—Overhead end-pivot rocking arms
    • 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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • 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
    • F01L13/0031—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 by modification of tappet or pushrod length
    • 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
    • F01L13/06—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for braking
    • F01L13/065—Compression release engine retarders of the "Jacobs Manufacturing" type
    • 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 variable valve train of an internal combustion engine for actuating a gas exchange valve. Its movement follows a stroke of a cam and a stroke of the cam superimposed on the stroke of the cam and independent of the stroke of the cam.
  • a volume change of a working space of a hydraulic lifting device which is in fluidic communication with a hydraulic fluid conveyor. This limits a pressure chamber with a volume which can be reduced by a displaceable in the pressure chamber wall of the hydraulic fluid delivery device under displacement of hydraulic fluid from the pressure chamber into the working space.
  • the wall is designed as a displacer, which is at least indirectly acted upon by a slide of the hydraulic fluid conveyor at least in the pre-stroke direction.
  • Generic valve trains in which the stroke of the gas exchange valve from a superposition of an output from the cam stroke and a variably adjustable stroke of a hydraulic lifting device, which acts independently of the cam on the movement of the gas exchange valve, are known in the art.
  • a bucket tappet drive with hydraulic lifting device This serves to superimpose a stroke generated by the cam to a stroke independent of the cam on the gas exchange valve.
  • a pressure piston located between the inside of the cup base and the valve stem, a pressure piston whose relative movement is generated to the tappets by volume change of a pressure chamber adjacent to the pressure chamber.
  • the pressure chamber is in turn connected via channels in the interior of the tappet and in the tappet guide of the internal combustion engine to a pressure or volume flow adjustable hydraulic supply.
  • valve drives Although a highly variable valve lift can already be generated with the aforementioned valve drives, these valve drives have some disadvantages.
  • the hydraulic control of the lifting device is carried out by hydraulic systems consisting of various components to fulfill different tasks.
  • the hydraulic fluid usually several hydraulic fluid pumps, one or more pressure accumulator for pressure storage, which are hydraulically interconnected in the case of different pressure levels by means of pressure regulator, and the time to be controlled in and out of the hydraulic fluid into and out of the lifting device Provide hydraulic valve.
  • the object of the invention is therefore to provide a variable valve train of the aforementioned type, in which the cited disadvantages are eliminated by simple means.
  • the variable valve train and in particular its hydraulic supply and control should therefore be as inexpensive to produce as possible and have low system complexity low space requirement with high reliability.
  • the hydraulically generated variability of the valvetrain should only be connected with the lowest possible energy expenditure for pressure generation and delivery of the hydraulic fluid and should be virtually free of losses in the valvetrain rigidity and dynamics.
  • the object is achieved in that the slider is displaceable by an electromagnetic biasing means of the hydraulic fluid conveyor at least in the pre-stroke direction.
  • the subject of the present invention is therefore a valve gear which can be produced cost-effectively and which, with low system complexity, makes it possible to superimpose the stroke of a cam and a stroke of a hydraulic lifting device independent of the stroke of the cam on the gas exchange valve.
  • the low complexity of the system is essentially achieved by integrating the functions hydraulic fluid delivery and pressure generation and the time-adjustable supply and removal of hydraulic fluid into and out of the hydraulic lifting device all in the simply constructed hydraulic fluid delivery device.
  • the control of the hydraulic fluid delivery device is purely on demand with correspondingly low energy consumption, resulting in a favorable efficiency of the internal combustion engine.
  • the displacement piston is at least in the pre-stroke direction of the slide of the hydraulic fluid conveyor, d. H. in the sense of a volume decrease of the pressure chamber, acted upon.
  • An attachment of the displacer piston on the slide, which also acts in the return stroke direction, is not absolutely necessary insofar as the displacer piston is acted upon in the return stroke direction by hydraulic fluid pressure, which is applied in particular by the valve spring acting on the gas exchange valve in its closing direction.
  • An attachment of the displacer piston on the slide both in Vorhub- and in remindhubides to a one-piece component with a simultaneously acting as a displacer slide may still be appropriate depending on the characteristic of the application of force by the hydraulic fluid delivery device.
  • the displaceable by the electromagnetic urging means at least in Vorhubraum slider can be in operative connection with an armature stand or anchor itself, which moves by the electromagnetic force effect of the biasing means between a basic position and a stroke position.
  • the valve train should also allow a secondary stroke of the gas exchange valve during a stroke-free base circle phase of the cam according to claim 2. This results in advantageous ways to suck back exhaust gas in high and precisely adjustable amounts internally.
  • This form of exhaust gas recirculation is in particular the basis for operation of the internal combustion engine with homogeneous and self-igniting charge.
  • HCCI Homogeneous Charge Compression Ignition
  • combustion method is used both in self-ignited diesel internal combustion engines as well as externally ignited gasoline internal combustion engines, at least in part-load operation of the internal combustion engine mainly for the purpose of emission reduction.
  • the combustion process in the HCCI process is essentially determined by controlling the charge composition and the charge temperature history.
  • a very effective means for increasing the charge temperature is to increase the residual gas content, ie to increase the content of untrushed or purged exhaust gas returned to the cylinder of the previous combustion cycle in the cylinder charge for the next combustion cycle.
  • the residual gas content on the operating point of the internal combustion engine must be fully variable, with residual gas quantities of 60% of the cylinder charge and more may be required. Residual gas components can no longer be provided at this altitude via internal exhaust gas recirculation through conventional valve overlap or via an arrangement for external exhaust gas recirculation.
  • the HCCI process reacts with unacceptable combustion processes extremely sensitive to changes in charge characteristics, so that in addition to the provision of residual gas in the required amount also a combustion cycle-faithful, high-precision and cylinder-specific dosing of the residual gas content is required.
  • the secondary stroke is carried out according to claim 3 preferably at an outlet valve.
  • exhaust gas which has already been ejected into the exhaust passage is sucked back into the combustion chamber via the then opened exhaust valve during the intake stroke of the internal combustion engine.
  • valve gear according to the invention in particular in air-compressing internal combustion engines for safety-relevant supplementation of the service brake.
  • engine brakes are usually used as a continuous brake in commercial vehicles and are based on the principle that the drag torque of the combustion engine located in overrun and not fueled by increasing the charge exchange work can be significantly increased and the vehicle is slowed down.
  • the exhaust valve is opened again during the compression phase, so that the cylinder charge is not compressed gas-spring-like, but is pushed into the outlet channel by applying Ausschiebearbeit.
  • exhaust gas recirculation it may also be expedient, according to claim 4, for the secondary stroke to take place at an inlet valve.
  • exhaust gas is expelled in Ausschiebetakt the internal combustion engine with the intake valve again open in the inlet channel and sucked back into the combustion chamber during the intake stroke.
  • a group of similar valve trains ie a group of intake valves or a group of exhaust valves of a cylinder of the internal combustion engine in each case exactly one hydraulic fluid delivery device is assigned.
  • a group of similar valve trains ie a group of intake valves or a group of exhaust valves of a cylinder of the internal combustion engine in each case exactly one hydraulic fluid delivery device is assigned.
  • the valve train should have according to claim 6 via a hydraulic valve clearance compensation device. It may be advantageous according to claim 7, that the working space of the hydraulic lifting device is identical to a compensation chamber of the valve play compensation device.
  • valve train as a drag lever drive and the hydraulic lifting device are designed as a rocker arm bearing pivot bearing.
  • the lubricating oil of the internal combustion engine is used according to claim 9 for the sake of simplicity.
  • any other suitable fluids in a hydraulic fluid circuit which would then be separated from the lubricating oil circuit of the internal combustion engine.
  • FIG. 1 shows the valve drive 1 according to the invention of an internal combustion engine using the example of a drag lever drive 2.
  • a gas exchange valve 3 which is actuated via a drag lever 4 by a cam 5 in the opening direction.
  • the drag lever 4 is mounted on a pivot bearing 6, which is received by a hollow cylindrical recess 7 of the internal combustion engine, in the direction of actuation of the gas exchange valve 3 and has a rotatably mounted roller 8 as low-friction contact surface 9 to the cam 5.
  • This has a cam lobe phase 10, the one Hub generated at the gas exchange valve 3, and a lift-free base circle phase eleventh
  • the pivot bearing 6 has a hollow-cylindrical housing 12 in which a plunger 13 which supports the drag lever 4 and a compensating piston 14 of a hydraulic valve play compensation device 15 are longitudinally movably guided.
  • the plunger 13 can be formed integrally with the compensating piston 14 or as a separate component to the balance piston 14.
  • a side facing away from the drag lever 4 end 16 of the compensating piston 14 defines a compensation chamber 17 of the valve play compensation device 15, whose basic operation is familiar to those skilled in the art.
  • the compensation chamber 17 is in the embodiment shown in the figures at the same time a working space 18 integrated in the pivot bearing 6 hydraulic lifting device 19.
  • the working chamber 18 is connected via a passage 20 in the housing 12 of the pivot bearing 6 and a supply line 21 with a pressure chamber 22 in hydraulic Connection.
  • the pressure chamber 22 is bounded by a hollow cylindrical recess 23 of the internal combustion engine and an end face 24 of a hydraulic fluid conveyor 25, which is screwed in the illustrated embodiment with a hollow cylindrical guide pin 26 in the recess 23.
  • a wall 27 is arranged, which is for the displacement of hydraulic fluid from the pressure chamber 22 in the working space 18 is displaced.
  • the wall 27 is designed as a displacer 28, which is acted upon by a slide 29 and in an inner circumferential surface 30 of the guide pin 26 is longitudinally movable and sealing gap-like manner in Vorhub- and remindhubides "P" or "R” out.
  • a shoulder 31 originating from the inner circumferential surface 30 serves as a stop for the displacer piston 28 which acts in the return stroke direction "R" and forms the basic position.
  • the slide 29 is in turn displaced by a loading means 32 which is designed electromagnetically in the form of a lifting magnet 33.
  • the slider 29 is in operative connection with an armature which moves by an electromagnetic force effect of the solenoid 33 between the basic position and a stroke position.
  • the solenoid 33 may be formed as a so-calledStrathubmagnet whose electromagnetic force acts only in Vorhubides “P” and its resetting by external, in the return direction "R” acting forces.
  • the solenoid 33 may be formed as a so-called Um Spotifyhubmagnet whose electromagnetic force acts depending on the excitation current both in the pre-stroke direction "P" and in the return stroke direction "R".
  • Both the single-stroke magnet and the reverse-stroke magnet can be designed as a proportional or quasi-proportional magnet.
  • Proportional magnets are Gleichstromhubmagnete that represent approximately proportional to the input of an excitation current depending on the application, a reproducible output in the form of a certain path of the armature or a certain force of the armature.
  • Quasiproportionalmagneten are also Gleichstromhubmagnete with an input variable dependent output variable, but their ratio is not proportional to each other in the rule, but follows a non-linear characteristic.
  • the design of the hydraulic fluid delivery device 25 and its connection to the pressure chamber 22 comprehensive hollow cylindrical recess 23 is to be designed by suitable, but not further illustrated measures that the pressure chamber 22 and the hydraulic lifting device 19 in terms of a fast and reproducible pressure build-up ideally always complete filled with hydraulic fluid and are free of gas bubbles.
  • suitable sealing measures in particular a leakage of hydraulic fluid from the pressure chamber 22 and from the hydraulic fluid delivery device 25 in the environment of the internal combustion engine to prevent permanently.
  • a leakage current possibly forming between the displacer piston 28 and the inner circumferential surface 30 of the guide journal 26 and leaving the pressure chamber 22 is attributable to a hydraulic fluid circuit of the internal combustion engine.
  • the operation of the hydraulic lifting device 19 results from the following described interaction with the hydraulic fluid delivery device 25.
  • the valve drive 1 is in Figure 1 in a position in which the cam lobe phase 10 according to cam rotation direction just ended and the gas exchange valve 3 is just closed, so that the roller 8 of the finger lever 4 picks up the base circle phase 11 of the cam 5.
  • the displacer piston 28 of the hydraulic fluid delivery device 25 is in the basic position, in which the displacer piston 28 is in contact with the shoulder 31 of the guide pin 26.
  • mechanical valve clearance which possibly arises during the cam elevation phase 10 due to sinking of the compensating piston 14 and the plunger 13 in a direction facing away from the cam 5, can be compensated.
  • the valve play compensation device 15 is assigned a hydraulic fluid supply 35 in a manner known per se.
  • the rocker arm 4 acted upon by the plunger 13 actuates the gas exchange valve 3 in the opening direction, by pivoting about the roller 8 supported on the cam 5.
  • a limitation of the movement of the displacer piston 28 in the pre-stroke direction "P" can be achieved, for example, by the displacer piston 28 abutting against a bottom 37 of the hollow-cylindrical recess 23.
  • An abort of the hydraulically generated stroke of the gas exchange valve 3 begins with a retraction of the displacer 28 in the return direction "R".
  • the volume 36 of the pressure chamber 22 increases with simultaneous decrease in volume of the working space 18 and return flow of the pressurized by the valve train 1 hydraulic fluid from the working space 18 into the pressure chamber 22. Due to the decrease in volume of the working chamber 18, the plunger 13 and the compensating piston 14 are moved back from the drag lever 4 in a cam-distant direction.
  • the retraction of the displacer piston 28 in the return stroke direction "R” can be effected depending on the above-described embodiment of the solenoid 33 in that the slide 29 in the return direction "R” only force-free and thus reset by the pressurized displacer 28.
  • the course of movement of the slide 29 can be weg- or force-controlled in the return direction "R” from the solenoid 33.
  • the latter possibility is the embodiment of the lifting magnet 33, which is more advantageous with regard to opening course shaping and in particular the closing process of the gas exchange valve 3, since the gas exchange valve 3 follows both the movement of the cam 5 and the movement of the displacer 28 in accordance with the mechanical and hydraulic gear ratios.
  • valve train 1 has been described using the example of a drag lever drive 2 with a pivot bearing 6 having a hydraulic valve clearance compensation device 15.
  • the idea of the invention can equally be implemented in other types of valve train without hydraulic valve lash adjuster, such as cup drives, tilting or rocker arm drives or pushrod drives.
  • Figures 1 and 2 relate to a hydraulically generated stroke of the gas exchange valve 3 during the base circle phase 11 of the cam 5, the hydraulically generated stroke can of course take place at any desired position of the cam within the mechanical limits of the valve train 1.
  • valve trains which are formed switchable by coupling means to strokes of multiple cams depending on the coupling state selectively to the gas exchange valve. 3 transferred to. This applies equally to valve trains that continuously vary the stroke of the gas exchange valve 3 by means of a cam and other adjusting elements.

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

Claims (9)

  1. Commande de soupape variable (1) d'un moteur à combustion interne pour actionner une soupape de gaz à deux voies (3), dont le mouvement suit une course d'une came (5) ainsi qu'une course d'un poussoir (13) superposée à la course de la came (5) et indépendante de la course de la came (5), sur lequel un changement de volume d'une chambre de travail (18) d'un dispositif de levée hydraulique (19) agit dans le sens de la course de levée, laquelle est en relation de travail fluidique avec un dispositif de refoulement d'un moyen hydraulique (25), lequel délimite une chambre de pression (22) présentant un volume (36), lequel peut être réduit par refoulement du moyen hydraulique hors de la chambre de pression (22) dans la chambre de travail (18) par une paroi (27) du dispositif de refoulement du moyen hydraulique (25) capable d'être déplacée dans la chambre de pression (22), la paroi (27) étant conformée en tant que piston de refoulement (28), lequel peut être actionné au moins dans le sens de course avant (P) au moins directement par un coulisseau (29) du dispositif de refoulement du moyen hydraulique (25), caractérisée en ce que le coulisseau (29) peut être déplacé au moins dans le sens de course avant (P) par un moyen d'excitation électromagnétique (32) du dispositif de refoulement du moyen hydraulique 25).
  2. Commande de soupape selon la revendication 1, caractérisée en ce que la soupape de gaz à deux voies (3) effectue au moins une course secondaire pendant une phase de rotation de la came (5) suivant le cercle de base (11).
  3. Commande de soupape selon la revendication 2, caractérisée en ce que la soupape de gaz à deux voies (3) est une soupape d'échappement du moteur à combustion interne.
  4. Commande de soupape selon la revendication 2, caractérisée en ce que la soupape de gaz à deux voies (3) est une soupape d'admission du moteur à combustion interne.
  5. Commande de soupape selon la revendication 3 ou 4, caractérisée en ce qu'un dispositif de refoulement d'un moyen hydraulique (25) est précisément prévu de façon commune pour plusieurs commandes de soupapes (1) similaires d'un cylindre du moteur à combustion interne.
  6. Commande de soupape selon la revendication 1, caractérisée en ce que la commande de soupape (1) comporte un dispositif de compensation hydraulique (15) du jeu de la soupape.
  7. Commande de soupape selon la revendication 6, caractérisée en ce que la chambre de travail (18) du dispositif de levée hydraulique (19) est identique à une chambre de compensation (17) du dispositif de compensation hydraulique (15) du jeu de la soupape.
  8. Commande de soupape selon la revendication 1, caractérisée en ce que la commande de soupape (1) est conformée en tant que commande de culbuteur (2) et le dispositif de levée hydraulique (19) en tant que palier de pivotement (6).
  9. Commande de soupape selon la revendication 1, caractérisée en ce que le moyen hydraulique est de l'huile de lubrification du moteur à combustion interne.
EP05024165A 2004-11-30 2005-11-05 Commande de soupape variable de moteur à combustion interne Expired - Fee Related EP1662098B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102004057574A DE102004057574A1 (de) 2004-11-30 2004-11-30 Variabler Ventiltrieb einer Brennkraftmaschine

Publications (2)

Publication Number Publication Date
EP1662098A1 EP1662098A1 (fr) 2006-05-31
EP1662098B1 true EP1662098B1 (fr) 2008-01-23

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DE (2) DE102004057574A1 (fr)

Cited By (1)

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US9157340B2 (en) 2013-03-25 2015-10-13 GT Technologies Dual feed hydraulic lash adjuster for valve actuating mechanism

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DE102011101239A1 (de) * 2011-05-11 2012-11-15 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Hydrostößel mit einer zweiten Ölzuführung zur
CN109661508A (zh) * 2016-07-20 2019-04-19 伊顿公司 使用空转和复位的ii型阀系的可变阀致动系统

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9157340B2 (en) 2013-03-25 2015-10-13 GT Technologies Dual feed hydraulic lash adjuster for valve actuating mechanism

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DE502005002644D1 (de) 2008-03-13
DE102004057574A1 (de) 2006-06-08
EP1662098A1 (fr) 2006-05-31

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