EP3523512B1 - Unité hydraulique pour moteur à combustion interne comprenant une commande hydraulique variable de soupape - Google Patents

Unité hydraulique pour moteur à combustion interne comprenant une commande hydraulique variable de soupape Download PDF

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Publication number
EP3523512B1
EP3523512B1 EP17784837.1A EP17784837A EP3523512B1 EP 3523512 B1 EP3523512 B1 EP 3523512B1 EP 17784837 A EP17784837 A EP 17784837A EP 3523512 B1 EP3523512 B1 EP 3523512B1
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EP
European Patent Office
Prior art keywords
hydraulic
housing
pressure chamber
pressure
chamber
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Application number
EP17784837.1A
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German (de)
English (en)
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EP3523512A1 (fr
Inventor
Lothar Von Schimonsky
Nicola Morelli
Steffen Pfeiffer
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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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
    • 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
    • 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

Definitions

  • the DE 10 2013 213 695 A1 discloses a hydraulic unit of a fully variable hydraulic valve control.
  • the hydraulic unit is mounted on the cylinder head of an internal combustion engine, and its hydraulic chambers vent - in the direction of gravity - down into the cylinder head.
  • the operational venting of the hydraulic system causes the air bubbles carried along by the hydraulic medium to be separated from the inside into the surroundings of the hydraulic housing and thus prevents excessive amounts of air from entering the pressure chamber and remaining there, whereby the stiffness of the hydraulic medium required for the hydraulic gas exchange valve actuation is inadmissible would be affected.
  • the venting also promotes 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, generates negative pressure in the hydraulic chambers, which is caused by suction of Air is balanced 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 housing opening positioned high in relation to gravity, ie geodetically high, and with the pressure relief chamber via a throttle point positioned geodetically low 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 present invention is based on the object of developing a hydraulic unit of the type mentioned at the outset so 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 solution to this problem results from the features of claim 1.
  • the ventilation duct should have a siphon with a first duct section leading downwards with respect to the direction of gravity and the ventilation direction and a second duct section leading upwards. When the gas exchange valve is closed, the lowest section of the siphon runs below the delimitation of the pressure chamber from the slave piston.
  • the siphon has two functions: On the one hand, it forms a hydraulic reservoir with the second channel section leading upwards, which is filled with hydraulic fluid at the time the internal combustion engine is switched off and which then partially or partially causes the cooling-related shrinkage of the hydraulic fluid in the hydraulic chambers - depending on the volume of the reservoir fully compensated.
  • the falling level in the second channel section causes a corresponding shortening (via the communicating tubes) of the hydraulic or oil column loading on the slave piston, so that the low pressure in the pressure chamber ideally completely prevents its leakage.
  • the ventilation duct should have a third duct section adjoining the second duct section, which (also) leads down to the duct opening on the outside of the housing with regard to the direction of gravity and the venting direction.
  • This structural design with a drilled vent channel leading down into the cylinder head of the internal combustion engine and preferably opening into the underside of the hydraulic housing from a manufacturing point of view enables the top of the cylinder head to be completely closed off from the environment by the hydraulic unit.
  • a vent opening on the upper side of the hydraulic unit on the other hand, a final cylinder head cover and thus a further component is required.
  • the dimensioning of the ventilation channel which determines the volume of the hydraulic reservoir, can also be relevant for the state in which the level in the lowest section of the siphon drops so far that air can be sucked back through the first channel section. Only from a minimum size of the channel cross-section can air bubbles rise in it without pushing the oil column above it and displacing it into the pressure relief space. Since the back-sucked air bubbles rise through the oil column in the first duct section and this quasi closes again, the leakage-inhibiting vacuum is maintained in the hydraulic housing.
  • its inner diameter should be at least 6 mm. Particularly good and robust results were achieved with an inner diameter of approx. 8 mm.
  • FIG. 1 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.
  • an electromagnetic hydraulic valve 9 in this case a normally open 2-2-way valve, interrupts the connection between the pressure relief chamber 6 and the pressure chamber 5 in the closed state.
  • a piston pressure accumulator 10 for receiving the displaced hydraulic medium is connected to each pressure relief chamber 6.
  • the pressure relief spaces 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 separates the air bubbles which are operationally conveyed from the hydraulic circuit into the hydraulic housing 4 from the hydraulic chambers into the cylinder head.
  • the ventilation duct 11 is hydraulically connected to the respective pressure relief chamber 6 on the inside of the housing via throttles 12 and opens out on the outside of the housing into the interior of the cylinder head 1.
  • the ventilation duct 11 runs geodetically, i.e. with respect to the direction of gravity g symbolized by the arrow above the throttle points 12, the pressure relief chambers 6 and the pressure chambers 5, which are limited by the slave piston 8 at the level of the limitation 13 when these are completely retracted into the hydraulic housing 4 with the gas exchange valves 2 closed.
  • the ventilation duct 11 has a siphon with a first duct section 14 and a first duct section 14 leading downwards in the ventilation direction in each case geodetically upward leading second channel section 15, which terminates at the channel opening 16 on the outside of the housing with the upper side of the hydraulic housing 4.
  • the hydraulic housing 4 is in the vented state shortly after the internal combustion engine has been switched off, in which the vent channel 11 is completely filled with hydraulic medium up to the channel opening 16.
  • Figure 1 shows the fill level at a significantly later point in time when the hydraulic fluid has cooled down completely to ambient temperature and its volume has accordingly shrunk.
  • the volume compensation takes place by lowering the hydraulic medium in the second channel section 15 to the level shown at the lowest section 17 of the siphon. This lowermost section 17 runs geodetically below the delimitation 13, so that the oil column in the first channel section 14 generates a negative pressure in the pressure chambers 5 that inhibits leakage.
  • first and second channel sections can be drilled at an angle to one another, in which case the lowermost section of the siphon would be formed by the intersection of the two channel sections.
  • the illustrated embodiment differs from the previously explained embodiment only in the geodetically deep positioning of the channel mouth 16 'on the hydraulic housing 4.
  • the ventilation duct 11' has a third duct section 19, which adjoins the second duct section 15 and which - also with regard to the direction of gravity and the venting direction - leads geodetically downwards like the first duct section 14 and to its duct opening 16 'on the outside of the housing the underside of the hydraulic housing 4 lies and in the present case terminates with its underside.
  • the duct opening on the outside of the housing of the ventilation duct can open below the level of a hydraulic reservoir which is formed, for example, in the cylinder head outside the hydraulic housing. In this way - without impairing the ventilation of the hydraulic spaces in the hydraulic housing - when the internal combustion engine is not running, air is sucked back into the hydraulic spaces via the ventilation duct.

Landscapes

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

Claims (4)

  1. Unité hydraulique pour un moteur à combustion interne dotée d'une commande hydraulique variable de soupape, comprenant :
    - un boîtier hydraulique (4) comportant une chambre de pression (5), une chambre de décompression (6) et un canal d'aération (11, 11'), la chambre de pression (5), la chambre de décompression (6) et le canal d'aération (11, 11') étant raccordés de manière hydraulique les uns aux autres,
    - un piston émetteur (7) guidé dans le boîtier hydraulique (4), lequel est entraîné, côté extérieur du boîtier, par une came (3) et délimite, côté intérieur du boîtier, la chambre de pression (5),
    - un piston récepteur (8) guidé dans le boîtier hydraulique (4), lequel entraîne, côté extérieur du boîtier, la soupape d'échange des gaz (2) et délimite, côté intérieur du boîtier, la chambre de pression (5),
    - et une soupape hydraulique (9), laquelle, à l'état fermé, interrompt la liaison entre la chambre de décompression (6) et la chambre de pression (5),
    dans laquelle le canal d'aération (11, 11'), côté intérieur du boîtier, est raccordé par l'intermédiaire d'un point d'étranglement (12) à la chambre de décompression (6) et s'ouvre, côté extérieur du boîtier, caractérisée en ce que le canal d'aération (11, 11') comprend un siphon comportant respectivement, par rapport à une direction de gravité et à une direction d'aération, une première section de canal (14) dirigée vers le bas et une seconde section de canal (15) dirigée vers le haut, dans laquelle une section inférieure (17) du siphon, lorsque la soupape d'échange des gaz (2) est fermée, s'étend en dessous d'une limite (13) de la chambre de pression (5) du piston récepteur (8).
  2. Unité hydraulique selon la revendication 1, caractérisée en ce que le canal d'aération (11') comprend une troisième section de canal (19), laquelle jouxte la deuxième section de canal (15) et laquelle est dirigée vers le bas, par rapport à la direction de gravité et à la direction d'aération, jusqu'à une embouchure de canal (16') côté extérieur du boîtier.
  3. Unité hydraulique selon la revendication 2, caractérisée en ce que l'embouchure de canal (16') se trouve, par rapport à la direction de gravité, sur une face inférieure du boîtier hydraulique (4).
  4. Unité hydraulique selon l'une quelconque des revendications précédentes, caractérisée en ce que la première section de canal (14) comprend une section transversale circulaire dont le diamètre intérieur est d'au moins 6 mm.
EP17784837.1A 2016-10-05 2017-09-29 Unité hydraulique pour moteur à combustion interne comprenant une commande hydraulique variable de soupape Active EP3523512B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016219297.3A DE102016219297B4 (de) 2016-10-05 2016-10-05 Hydraulikeinheit für eine Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb
PCT/DE2017/100833 WO2018065010A1 (fr) 2016-10-05 2017-09-29 Unité hydraulique pour un moteur à combustion interne à commande hydraulique variable des soupapes d'échange des gaz

Publications (2)

Publication Number Publication Date
EP3523512A1 EP3523512A1 (fr) 2019-08-14
EP3523512B1 true EP3523512B1 (fr) 2020-11-11

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Application Number Title Priority Date Filing Date
EP17784837.1A Active EP3523512B1 (fr) 2016-10-05 2017-09-29 Unité hydraulique pour moteur à combustion interne comprenant une commande hydraulique variable de soupape

Country Status (5)

Country Link
US (1) US11187117B2 (fr)
EP (1) EP3523512B1 (fr)
CN (1) CN109790766B (fr)
DE (1) DE102016219297B4 (fr)
WO (1) WO2018065010A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111546119A (zh) * 2020-04-28 2020-08-18 东莞市固达机械制造有限公司 数控双换台精密平面铣床

Family Cites Families (19)

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GB501738A (en) * 1936-09-02 1939-02-28 Schweizerische Lokomotiv Improvements in or relating to hydraulic telemotor systems
FR1459833A (fr) * 1965-07-19 1966-06-17 Hispano Suiza Sa Perfectionnements apportés aux moteurs à combustion interne à soupapes, notammentaux moteurs diesel de ce type
DE2840445C2 (de) * 1978-09-16 1984-10-04 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg Hydraulische Vorrichtung zum Betätigen eines Gaswechselventils für Brennkraftmaschinen
DE3939066A1 (de) * 1989-11-25 1991-05-29 Bosch Gmbh Robert Elektrohydraulische ventilsteuervorrichtung fuer brennkraftmaschinen
US5537976A (en) * 1995-08-08 1996-07-23 Diesel Engine Retarders, Inc. Four-cycle internal combustion engines with two-cycle compression release braking
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EP2653703B1 (fr) * 2012-04-19 2014-04-30 C.R.F. Società Consortile per Azioni Moteur à combustion interne avec cylindres qui peuvent être désactivés, les cylindres désactivés sont utilisés comme pompes pour récirculer le gas d'échappement dans les cylindres actives et un procédé pour contrôler ce moteur
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Also Published As

Publication number Publication date
DE102016219297A1 (de) 2018-04-05
US20210293162A1 (en) 2021-09-23
US11187117B2 (en) 2021-11-30
CN109790766B (zh) 2021-01-26
EP3523512A1 (fr) 2019-08-14
WO2018065010A1 (fr) 2018-04-12
DE102016219297B4 (de) 2021-12-30
CN109790766A (zh) 2019-05-21

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