EP3519683B1 - Moteur à combustion interne avec soupapes à commande hydraulique variable - Google Patents

Moteur à combustion interne avec soupapes à commande hydraulique variable Download PDF

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Publication number
EP3519683B1
EP3519683B1 EP17787318.9A EP17787318A EP3519683B1 EP 3519683 B1 EP3519683 B1 EP 3519683B1 EP 17787318 A EP17787318 A EP 17787318A EP 3519683 B1 EP3519683 B1 EP 3519683B1
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EP
European Patent Office
Prior art keywords
hydraulic
housing
combustion engine
internal combustion
pressure chamber
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.)
Active
Application number
EP17787318.9A
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German (de)
English (en)
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EP3519683A1 (fr
Inventor
Steffen Pfeiffer
Philipp Galster
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.)
Schaeffler Technologies AG and Co KG
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Schaeffler Technologies AG and Co KG
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Publication of EP3519683A1 publication Critical patent/EP3519683A1/fr
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Publication of EP3519683B1 publication Critical patent/EP3519683B1/fr
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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
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • 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
    • F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
    • F01L3/06—Valve members or valve-seats with means for guiding or deflecting the medium controlled thereby, e.g. producing a rotary motion of the drawn-in cylinder charge
    • 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
    • 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
    • F01L9/11—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column
    • F01L9/12—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem
    • F01L9/14—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic in which the action of a cam is being transmitted to a valve by a liquid column with a liquid chamber between a piston actuated by a cam and a piston acting on a valve stem the volume of the chamber being variable, e.g. for varying the lift or the timing of a valve
    • 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
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the generic DE 10 2013 213 695 A1 shows an internal combustion engine with a fully variable hydraulic valve control. This is formed by a structural unit that is mounted on the cylinder head of the internal combustion engine and the hydraulic chambers of which - in the direction of gravity - vent down into the cylinder head.
  • the operational venting of the hydraulic system causes the air bubbles carried along by the hydraulic fluid to be separated into the vicinity of the hydraulic housing and thus prevents excessive amounts of air from entering the pressure chamber and impairing the hydraulic fluid's stiffness to an impermissible level, which is necessary for the hydraulic gas exchange valve actuation.
  • the venting promotes the leakage of the hydraulic medium from the hydraulic housing when the internal combustion engine is switched off.
  • the hydraulic fluid which cools down and shrinks in volume, creates negative pressure in the hydraulic chambers, which is compensated by sucking in air via the ventilation duct. During this pressure equalization, gravity ensures that the hydraulic chambers are emptied in the vicinity of the leakage through the guide gap between the slave piston and the hydraulic housing.
  • a hydraulic unit with an additional low-pressure chamber which communicates with the interior of the cylinder head via a geodetically high-position housing opening and with the pressure relief chamber via a geodetically low-lying throttle point for the purpose of venting.
  • the low-pressure chamber represents an expanded hydraulic reservoir which supplies the pressure chamber with sufficiently air-free hydraulic medium during the starting process of the internal combustion engine.
  • the vent which is not of the generic type, ie opens against the direction of gravity on the upper side of the hydraulic housing, requires a cylinder head cover that seals the cylinder head with the hydraulic housing from the environment, and therefore an additional component.
  • the present invention is based on the object of developing an internal combustion engine of the type mentioned at the outset in such a way that the hydraulic leakage from the hydraulic housing is reduced to such an extent that the hydraulic medium in the pressure chamber does not fall below a level that is critical for its starting process even after the internal combustion engine has been idle for a long time .
  • the vent channel should open into a hydraulic reservoir, the channel mouth being below the normal level of the hydraulic reservoir with respect to the direction of gravity.
  • the term “normal level” is to be understood as the level that is in the steady state shortly after the internal combustion engine has been switched off sets in the hydraulic reservoir, the internal combustion engine not being inclined or at most inclined to an insignificant extent with respect to its installation position.
  • the duct opening "immersed" in the hydraulic medium prevents air from being sucked back into the pressure relief chamber via the ventilation duct when the internal combustion engine is at a standstill and the hydraulic medium volume shrinks due to cooling. This state extends over a sufficiently long period of time and at least until the level of the hydraulic reservoir has dropped below the channel opening as a result of the cooling-related volume shrinkage of the hydraulic medium from the hydraulic housing.
  • the hydraulic reservoir open to the surroundings of the hydraulic housing can be formed either on the hydraulic housing itself or by a local trough or trough shape of a component or section of the cylinder head or of the engine block of the internal combustion engine.
  • the channel mouth should run as deep as possible with respect to the direction of gravity and specifically below the delimitation of the pressure chamber from the slave piston.
  • the geodetic height difference between the slave piston (retracted in the hydraulic housing) and the duct opening directly influences the negative pressure that is created in relation to the surroundings of the hydraulic housing when the internal combustion engine is switched off and the hydraulic fluid is shrinking and which counteracts the gravity-induced leakage of the hydraulic fluid from the hydraulic housing.
  • the channel mouth with respect to the direction of gravity i.e. geodetically always below the level of the hydraulic reservoir. This state presupposes that the hydraulic reservoir can be made sufficiently voluminous in view of the hydraulic volume in the hydraulic housing, which decreases due to temperature and leakage.
  • the volume of the hydraulic reservoir is structurally limited in such a way that a drop in the reservoir level below the channel mouth and consequently the sucking back of air cannot be avoided.
  • the downtime of the internal combustion engine until the critical level in the pressure chamber is reached can be significantly extended by the fact that the ventilation duct has, at least locally, a cross-section dimensioned in such a way that air bubbles can rise in it without pushing the hydraulic or oil column above it in front of it and to be displaced into the pressure relief space.
  • the cross-section is to be dimensioned so that the back-sucked air rises in the standing oil column, so that the remaining oil column more or less closes the channel mouth again and maintains the leakage-inhibiting vacuum in the hydraulic housing.
  • the ventilation duct in the case of an oil with the viscosity index 0W20, and in the case of a circular first pipe section, the ventilation duct must have an inside diameter of at least 6 mm. Particularly good and robust results have been achieved with the pipe inside diameter of approx. 8 mm.
  • the circular shape of the ventilation channel can have manufacturing advantages. However, other cross-sectional shapes are possible as long as the air can rise without displacing the oil column above.
  • the channel mouth should be formed by a circular second pipe section, which adjoins the first pipe section with (abrupt or gradual) reduction in the outer diameter of the pipe.
  • This structural design of the ventilation channel with the tube sections stepped in diameter may be necessary if the surface of the hydraulic reservoir is too small to accommodate the relatively large diameter of the first tube section.
  • the ventilation channel is expediently formed by a ventilation pipe fastened and preferably screwed in in the hydraulic housing, the first and optionally the second pipe section being parts of the ventilation pipe.
  • FIG. 1a shows schematically the section of an internal combustion engine with a hydraulically variable gas exchange valve drive which is essential for understanding the invention.
  • a cylinder head 1 is shown with two similar gas exchange valves 2 per cylinder, which are spring-loaded in the closing direction, and associated cams 3 of a camshaft.
  • the variability of the gas exchange valve drive is generated in a known manner by means of a hydraulic unit arranged between the cams 3 and the gas exchange valves 2.
  • This comprises a hydraulic housing 4 fastened in the cylinder head 1, in which a pressure chamber 5 and a pressure relief chamber 6 are formed for each cylinder and a master piston 7 is guided, which is driven by the cam 3 on the outside of the housing and delimits the pressure chamber 5 on the inside of the housing.
  • two slave pistons 8 per cylinder are guided in the hydraulic housing 4, which drive the gas exchange valves 2 on the outside of the housing and delimit the common pressure chamber 5 on the inside of the housing.
  • a piston pressure accumulator 10 for receiving the displaced hydraulic medium is connected to each pressure relief chamber 6.
  • the pressure relief chambers 6 are connected to the hydraulic circuit, ie the oil circuit of the internal combustion engine, via a hydraulic connection (not shown) on the hydraulic housing 4.
  • the functionality of the hydraulic gas exchange valve drive which is known per se, can be summarized in that the pressure chamber 5 between the master piston 7 and the slave piston 8 acts as a hydraulic linkage.
  • the hydraulic medium displaced by the master piston 7 - if leaks are neglected - proportionally to the stroke of the cam 3, depending on the opening time and the opening duration of the hydraulic valve 9, is transferred into a first partial volume that acts on the slave piston 8 and into a second partial volume, into the pressure relief chamber 6 including the piston pressure accumulator 10 outflowing partial volumes divided.
  • the transfer of the stroke of the master piston 7 to the slave piston 8 and consequently not only the control times but also the stroke height of the gas exchange valves 2 can be set in a fully variable manner.
  • the pressure relief chambers 6 are connected to a common ventilation duct 11 in the hydraulic housing 4, which is hydraulically connected to the respective pressure relief chamber 6 on the inside of the housing via throttling points 12 and opens on the outside of the housing in a hydraulic reservoir 13 inside the cylinder head 1.
  • the throttling points 12 are geodetically, ie above the pressure relief spaces 6 with respect to the direction of gravity g symbolized by the arrow, and the hydraulic reservoir 13 is geodetically below the pressure relief spaces 6 but also below the delimitation 16 of the pressure chamber 5 by the slave piston 8 when these are completely retracted into the hydraulic housing 4 with the gas exchange valves 2 closed.
  • the hydraulic reservoir 13, which is pressureless with respect to the internal pressure of the cylinder head 1, is formed by a trough which is closed in the direction of gravity 17 formed in cylinder head 1 (s. Figure 1b ), in which hydraulic fluid accumulates during operation of the internal combustion engine.
  • the ventilation duct 11 is formed on the outside of the housing by a ventilation tube 18 screwed tightly and sealingly into the hydraulic housing 4.
  • This has a circular first pipe section 19, the pipe inside diameter of which is between 8 mm and 9 mm.
  • the first pipe section 19 merges at a diameter step 20 into a circular second pipe section 21 with an inside diameter of approximately 4 mm.
  • the outer pipe diameter of the second pipe section 21 is correspondingly small and dimensioned in such a way that the second pipe section 21 can be inserted into the recess 17 without collision when the hydraulic unit is installed in the cylinder head 1.
  • Figure 1a shows the vented fill level of the hydraulic system shortly after the internal combustion engine has been switched off.
  • the level 15 of the hydraulic reservoir 13 is the normal level defined at the outset.
  • the particular according to Figure 1b shows the filling level of the hydraulic system at a significantly later point in time when the hydraulic medium has cooled down completely and its volume has accordingly shrunk.
  • the negative pressure that forms in the hydraulic chambers with the volume reduction causes hydraulic medium to be sucked in from the hydraulic reservoir 13 into the pressure relief chambers 6.
  • This air bubble-free sucking ends when the level 15 of the hydraulic reservoir 13 sinks geodetically below the channel mouth 14.
  • the pressure is then equalized between the pressure relief chambers 6 and the surroundings of the hydraulic housing 4 by sucking back air bubbles 22.
  • the in Figure 2 The second exemplary embodiment shown, the hydraulic reservoir 13 'is geodetically significantly lower than in the first exemplary embodiment.
  • the higher oil column between the delimitation 16 and the level 15 of the hydraulic reservoir 13 ' causes an increased negative pressure in the hydraulic system in favor of the further reduced leakage of the pressure chambers 5 through the guide gap around the slave piston 8.
  • the ventilation duct 11 is in this embodiment through a ventilation pipe 18' formed with a uniform diameter, wherein the pipe inner diameter is dimensioned so large in this case too that the air bubbles 22 rising therein can pass the oil column in the vent pipe 18 '.
  • the third embodiment according to Figure 3 has a hydraulic reservoir 13 ′′, the volume of which is so large that the channel mouth 14 is always geodetically below the level 15 of the hydraulic reservoir 13 ′′.

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

Claims (7)

  1. Moteur à combustion interne avec soupape d'échange de gaz à commande hydraulique variable, comprenant :
    - un boîtier hydraulique (4) avec une chambre de pression (5), une chambre de détente (6) et un conduit de purge (11), la chambre de pression (5), la chambre de détente (6) et le conduit de purge (11) étant reliés hydrauliquement les uns aux autres,
    - un piston émetteur (7) guidé dans le boîtier hydraulique (4), qui est entraîné par une came (3) à l'extérieur du boîtier et qui délimite la chambre de pression (5) à l'intérieur du boîtier,
    - un piston récepteur (8) guidé dans le boîtier hydraulique (4), qui entraîne la soupape d'échange de gaz (2) à l'extérieur du boîtier et délimite la chambre de pression (5) à l'intérieur du boîtier,
    - et une soupape hydraulique (9) qui à l'état fermé interrompt la connexion entre la chambre de détente (6) et la chambre de pression (5),
    dans lequel le conduit de purge (11) est relié hydrauliquement à l'intérieur du boîtier à la chambre de détente (6) par l'intermédiaire d'un point d'étranglement (12) et s'ouvre à l'extérieur du boîtier par rapport au sens de la gravité en dessous de la chambre de détente (6), caractérisé en ce que le conduit de purge (11) se trouve dans un réservoir hydraulique (13, 13', 13"), l'embouchure du conduit (14) étant en dessous du niveau normal du réservoir hydraulique (13, 13', 13") par rapport au sens de la gravité.
  2. Moteur à combustion interne selon la revendication 1, caractérisé en ce que lorsque la soupape d'échange de gaz (2) est fermée, l'embouchure du conduit (14) s'étend depuis le piston récepteur (8) par rapport au sens de la gravité en dessous de la limite (16) de la chambre de pression (5).
  3. Moteur à combustion interne selon la revendication 1 ou 2, caractérisé en ce que l'embouchure du conduit (14) est toujours en dessous du niveau (15) du réservoir hydraulique (13") par rapport au sens de la gravité.
  4. Moteur à combustion interne selon l'une quelconque des revendications précédentes, caractérisé en ce que le conduit de purge (11) présente une première section de tuyau circulaire (19) dont le diamètre intérieur de tuyau est d'au moins 6 mm.
  5. Moteur à combustion interne selon la revendication 4, caractérisé en ce que l'embouchure du conduit (14) est formée par une seconde section de tuyau circulaire (21) qui jouxte la première section de tuyau (19) tout en réduisant le diamètre extérieur de tuyau.
  6. Moteur à combustion interne selon la revendication 4 ou 5, caractérisé en ce que la première section de tuyau (19) fait partie d'un tuyau de ventilation (18) fixé dans le boîtier hydraulique (4).
  7. Moteur à combustion interne selon la revendication 6, caractérisé en ce que le tuyau de ventilation (18) est vissé dans le boîtier hydraulique (4).
EP17787318.9A 2016-09-29 2017-09-28 Moteur à combustion interne avec soupapes à commande hydraulique variable Active EP3519683B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016218918.2A DE102016218918B4 (de) 2016-09-29 2016-09-29 Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb
PCT/DE2017/100828 WO2018059627A1 (fr) 2016-09-29 2017-09-28 Moteur à combustion interne à mécanisme de distribution hydrauliquement variable de soupape d'échange des gaz

Publications (2)

Publication Number Publication Date
EP3519683A1 EP3519683A1 (fr) 2019-08-07
EP3519683B1 true EP3519683B1 (fr) 2020-09-02

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP17787318.9A Active EP3519683B1 (fr) 2016-09-29 2017-09-28 Moteur à combustion interne avec soupapes à commande hydraulique variable

Country Status (5)

Country Link
US (1) US10900389B2 (fr)
EP (1) EP3519683B1 (fr)
CN (1) CN109715911B (fr)
DE (1) DE102016218918B4 (fr)
WO (1) WO2018059627A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102021117501A1 (de) 2021-07-07 2023-01-12 Schaeffler Technologies AG & Co. KG Hydraulikeinheit mit selektiv wirkendem Dichtring, interne Abdichtung für UniAir-Komponenten und Verteilerblock mit Hydraulikeinheit

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Also Published As

Publication number Publication date
US20190211718A1 (en) 2019-07-11
US10900389B2 (en) 2021-01-26
CN109715911A (zh) 2019-05-03
WO2018059627A1 (fr) 2018-04-05
DE102016218918B4 (de) 2018-09-13
DE102016218918A1 (de) 2018-03-29
EP3519683A1 (fr) 2019-08-07
CN109715911B (zh) 2021-10-12

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