EP2381075B1 - Unité hydraulique pour une tête de cylindre d'un moteur à combustion interne dotée d'une commande de soupape hydraulique variable à échange de gaz - Google Patents

Unité hydraulique pour une tête de cylindre d'un moteur à combustion interne dotée d'une commande de soupape hydraulique variable à échange de gaz Download PDF

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Publication number
EP2381075B1
EP2381075B1 EP20110160128 EP11160128A EP2381075B1 EP 2381075 B1 EP2381075 B1 EP 2381075B1 EP 20110160128 EP20110160128 EP 20110160128 EP 11160128 A EP11160128 A EP 11160128A EP 2381075 B1 EP2381075 B1 EP 2381075B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
pressure chamber
valve
medium
low
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.)
Not-in-force
Application number
EP20110160128
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German (de)
English (en)
Other versions
EP2381075A2 (fr
EP2381075A3 (fr
Inventor
Andreas Rinnert
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 EP2381075A2 publication Critical patent/EP2381075A2/fr
Publication of EP2381075A3 publication Critical patent/EP2381075A3/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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit

Definitions

  • Such a hydraulic unit is from the unpublished DE 10 2009 011 983 A1 out.
  • all essential, required for the hydraulically variable transmission of cam lobes on the gas exchange valves components and the pressure chambers are combined in a common hydraulic housing.
  • the throttling point connecting the medium-pressure space with the low-pressure space serving as the hydraulic medium reservoir is configured in such a way that that from the medium-pressure space In the low pressure chamber flowing hydraulic fluid must pass through a throttle cross-section and vice versa the hydraulic fluid flow from the low-pressure space in the medium-pressure space is a low-throttle flow area available.
  • the low throttling in this flow direction is intended to ensure that the medium-pressure chamber is provided with a sufficiently rapidly available hydraulic fluid reservoir when the engine is cold-starting.
  • the present invention has the object to further develop a hydraulic unit of the type mentioned in that the hydraulic medium leakage is minimized from the hydraulic unit, so that even after a long downtime of the internal combustion engine required for their successful start operation opening operation of the gas exchange valves is ensured to a sufficient extent.
  • the first flow cross-section which is available to the hydraulic fluid flow from the medium-pressure space in the low-pressure chamber, is greater than the second flow cross-section, which is the hydraulic fluid flow from the low-pressure space in the medium-pressure space available.
  • the throttle body should be configured so that it presents a lower resistance to the hydraulic fluid flow from the medium-pressure chamber into the low-pressure chamber than the reverse hydraulic fluid flow from the low-pressure chamber into the medium-pressure chamber. Consequently, it is also not the primary purpose of the invention that the medium-pressure space and the high-pressure chamber at the start of the engine, a sufficiently quickly available hydraulic fluid reservoir in the form of low pressure space is available, but rather that during the downtime before starting the hydraulic medium leakage from the hydraulic unit minimized as far as possible becomes.
  • the second flow cross-section allows a defined within predetermined limits, compared to the known systems, however, relatively small and leakage-inhibiting flow from the low-pressure chamber in the medium-pressure space.
  • This small volume flow causes a constant pressure equalization of the pressure chambers with each other, which in terms of cyclic changes in ambient temperature such as day-night change or changing sunlight during the downtime of the internal combustion engine can have a significant impact on the leakage behavior of the hydraulic unit. Because a lack of pressure equalization would lead due to thermally induced pressure differences to a successive emptying of the pressure chambers with a corresponding intake of ambient air within a few idle days of the internal combustion engine.
  • the valve body is intended to be the ball which lifts off from the valve seat of a ball valve in the direction of the low-pressure space, the second flow area being determined by a non-circular cross-section of the valve seat when the ball is seated against the valve seat.
  • the cross section of the valve seat may have the shape of a regular polygon with, for example, three or five rounded corners.
  • the valve seat is expediently shaped similar to a truncated cone, wherein the contact surface to the ball - viewed as a longitudinal section through the ball valve - convex, concave or straight.
  • the first flow area may be defined by a throttle bore that is hydraulically connected in series with the ball valve.
  • the valve seat of the ball valve is to be integrally formed on a cylindrical valve carrier (preferably by cold forming such as embossing), which is pressed by the low-pressure chamber into a stepped bore of the hydraulic housing and presses a throttle disk penetrated by the throttle bore against a bore step of the stepped bore.
  • a check valve opening between the low-pressure space and the medium-pressure space can also be provided for the medium-pressure space, during the downtime of the internal combustion engine is closed and in the subsequent start operation due to the then forming in the medium pressure space negative pressure hydraulic fluid flow from the low pressure chamber in the medium pressure space allows low resistance.
  • the low pressure chamber 16 is provided with an opening into the cylinder head 2 overflow 20. This serves not only the venting of the low-pressure chamber 16, but also the cooling of the hydraulic unit 5 by heated heated hydraulic fluid via low-pressure chamber 16 in the cylinder head 2 and thus can be returned to the cooled hydraulic fluid circuit of the engine.
  • the known operation of the hydraulic gas exchange valve drive 1 can be summarized to the effect that the high-pressure chamber 11 between the transmitter unit 6 and the slave unit 8 acts as a hydraulic linkage, which - neglecting leaks - proportional to the stroke of the cam 3 displaced by the pump plunger 7 hydraulic volume depending on the opening time and the opening duration of the hydraulic valve 10 in a first, the slave piston 9 acting sub-volume and in a second, in the medium pressure chamber 12 including pressure accumulator 13 effluent partial volume is divided.
  • the stroke transmission of the pump tappet 7 to the slave piston 9 and therefore not only the timing, but also the lifting height of the gas exchange valve 4 are fully variable adjustable.
  • FIG. 2 shows the throttle point 17 as a hydraulic symbol.
  • Essential for the invention is the existence of a displaceable in the direction of the hydraulic fluid flow between the medium pressure chamber 12 and low-pressure chamber 16 valve body 19 to form the throttle body 17 such that it has two different flow cross-sections for the hydraulic fluid flow depending on the position of the valve body 19.
  • the throttle body 17 is formed as a series connection of a constriction 21 on the one hand and a ball valve 22 with ball 19 and valve seat 23 on the other. Starting from its contact with the valve seat 23, the ball 19 lifts in the direction of the low-pressure chamber 16 and allows a low-throttle flow through the ball valve 22.
  • the first flow cross-section relevant for the hydraulic fluid flow from the medium-pressure chamber 12 into the low-pressure chamber 16 is determined by the size of the constriction 21 ,
  • the valve seat 23 is geometrically shaped so that this with the adjacent ball 19 not completely seals.
  • a predetermined leakage of the ball valve 22 with a second flow cross-section is established, as symbolized by the bottleneck without a reference number running parallel to the ball valve 22. Since the first flow cross-section - significantly the constriction 21 - is significantly greater than the second flow cross-section - is decisive the closed ball valve 22 - is the hydraulic fluid flow from the low-pressure chamber 16 in the medium-pressure chamber 12 much more throttled than in the opposite direction.
  • the significantly smaller second flow cross-section prevents leakage-induced rapid emptying of the pressure chambers 11, 12 and 16 and at the same time allows pressure equalization between the pressure chambers, which counteracts a successive emptying of the pressure chambers and the simultaneous suction of air.
  • FIG. 3 shows an executed hydraulic unit 5, in which all the aforementioned components are accommodated in a one-piece hydraulic housing 24.
  • the hydraulic unit 5 is mounted as a preassembled and filled with hydraulic fluid assembly in the cylinder head of a 2-cylinder inline engine.
  • the two encoder units 6 each include a support member 25, a pivotally mounted thereon rocker arm 26 mounted therein roller 27 for a low-friction cam and the here actuated by rocker arm 26 and spring loaded in remindhubraum pump tappet 7.
  • Brackets 28 serve as captive for the rocker arm 26 at not in the cylinder head mounted hydraulic unit 5. This is further designed so that each of the transmitter units 6 cooperates with two slave units 8.
  • FIG. 4 is a sectional view through the hydraulic unit 5, which in FIG. 3 corresponding to the dash-dotted section plane.
  • the medium-pressure chamber 12 is connected on the one hand via the check valve 15 to the hydraulic medium supply of the internal combustion engine and on the other hand with the spring-loaded compensating piston 14 of the pressure accumulator 13 in connection.
  • the opening in the medium pressure chamber 12 inner end of the hydraulic valve 10 can be seen.
  • the connection of serving as a hydraulic fluid reservoir low-pressure chamber 16 to the medium-pressure chamber 12 is made via a stepped bore 30, the entry is closed in the hydraulic housing 24 with an interspersed by the overflow plug 20 31 (see FIG. 3 ). Both air bubbles, which pass through the throttling point 17 from the medium-pressure chamber 12 into the low-pressure chamber 16 during operation of the internal combustion engine, as well as excess hydraulic fluid can be deposited via the overflow 20 into the interior of the cylinder head.
  • FIG. 5 shows the fixed in the stepped bore 30 throttle body 17 in magnification.
  • the valve seat 23 of the ball valve 22 is integrally formed on a cylindrical valve carrier 32 which is pressed by the low-pressure chamber 16 into the stepped bore 30 and presses a throttle disk 33 against a bore step 34.
  • the decisive for the hydraulic fluid flow from the medium-pressure chamber 12 in the low-pressure chamber 16 first flow cross-section is determined by the constriction 21 in the form of a throttling disc 33 passing through the throttle bore, which is hydraulically connected in series with the ball valve 22 and here has a diameter of 0.4mm.
  • the decisive for the reverse flow of hydraulic fluid from the low-pressure chamber 16 in the medium-pressure chamber 12 second flow cross-section is determined by the shape of the valve seat 23 in abutting ball 19.
  • the real dimensional deviations of the polygon 35, 36 from the circular shape can be taken from the dimensioning shown in each case.
  • FIG. 8 An alternative throttle point 17 'goes out FIG. 8 in a schematic representation.
  • a ball valve 22 ' is also provided, the ball 19 between two valve seats 21' and 23 'is displaced.
  • the lower valve seat 23 ' which runs from the middle pressure chamber 12, determines the second flow cross section when the ball 19 abuts against it and corresponds geometrically to the one in FIG FIG. 6 or 7
  • the part of the low-pressure chamber 16 extending upper valve seat 21 ' replaces the throttle plate 33 and the valve cap 37 in FIG. 5
  • the larger first flow cross-section is also determined here by a predetermined leak between the upper valve seat 21 'and the adjacent thereto (dashed lines) ball 19. This leakage is also generated by a deviating from the circular cross-section of the upper valve seat 21 ', but the deviations are dimensionally significantly greater than in FIG. 6 or 7 shown.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Claims (5)

  1. Unité hydraulique (5) pour une culasse (2) d'un moteur à combustion interne comprenant une commande de soupape à échange de gaz variable hydrauliquement (1), comprenant :
    - un boîtier hydraulique (24) comprenant au moins une unité émettrice (6) du côté de l'entraînement, au moins une unité réceptrice (8) du côté de la sortie et au moins une soupape hydraulique commandable (10),
    - au moins un espace moyenne pression (12) s'étendant dans le boîtier hydraulique (24),
    - au moins un espace haute pression (11) s'étendant dans le boîtier hydraulique (24), lequel espace haute pression est disposé, dans le sens du transfert, entre l'unité émettrice associée (6) et l'unité réceptrice associée (8) et peut être connecté par le biais de la soupape hydraulique associée (10) à l'espace moyenne pression associé (12),
    - au moins un espace basse pression (16) s'étendant dans le boîtier hydraulique (24), lequel espace basse pression sert de réservoir de fluide hydraulique et est connecté par le biais d'un étranglement (17) à l'espace moyenne pression associé (12),
    - et un corps de soupape (19), qui est reçu de manière déplaçable dans la direction d'un flux de fluide hydraulique entre l'espace moyenne pression (12) et l'espace basse pression (16) dans le boîtier hydraulique (24) et qui sert à former l'étranglement (17), lequel étranglement présente deux sections transversales d'écoulement pour le flux de fluide hydraulique de tailles différentes en fonction de la position du corps de soupape (19),
    caractérisée en ce que la première section transversale d'écoulement qui est disponible pour le flux de fluide hydraulique depuis l'espace moyenne pression (12) jusque dans l'espace basse pression (16) est supérieure à la deuxième section transversale d'écoulement qui est disponible pour le flux de fluide hydraulique depuis l'espace basse pression (16) jusque dans l'espace moyenne pression (12).
  2. Unité hydraulique (5) selon la revendication 1, caractérisée en ce que le corps de soupape (19) est la bille se soulevant du siège de soupape (23) d'une soupape à bille (22) dans la direction de l'espace basse pression (16), la deuxième section transversale d'écoulement étant déterminée par une section transversale non circulaire du siège de soupape (23) lorsque la bille (19) s'applique contre le siège de soupape (23).
  3. Unité hydraulique (5) selon la revendication 2, caractérisée en ce que la section transversale du siège de soupape (23) présente la forme d'un polygone régulier (35, 36) avec des coins arrondis.
  4. Unité hydraulique (5) selon la revendication 2, caractérisée en ce que la première section transversale d'écoulement est déterminée par un alésage d'étranglement (21) qui est monté en série hydrauliquement avec la soupape à bille (22).
  5. Unité hydraulique (5) selon la revendication 4, caractérisée en ce que le siège de soupape (23) de la soupape à bille (22) est façonné sur un support de soupape cylindrique (32), qui est pressé dans un alésage étagé (30) du boîtier hydraulique (24) depuis l'espace basse pression (16) et presse un disque d'étranglement (33) traversé par l'alésage d'étranglement (21) contre un étage d'alésage (34) de l'alésage étagé (30).
EP20110160128 2010-04-26 2011-03-29 Unité hydraulique pour une tête de cylindre d'un moteur à combustion interne dotée d'une commande de soupape hydraulique variable à échange de gaz Not-in-force EP2381075B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE201010018209 DE102010018209A1 (de) 2010-04-26 2010-04-26 Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb

Publications (3)

Publication Number Publication Date
EP2381075A2 EP2381075A2 (fr) 2011-10-26
EP2381075A3 EP2381075A3 (fr) 2013-01-23
EP2381075B1 true EP2381075B1 (fr) 2013-10-16

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EP20110160128 Not-in-force EP2381075B1 (fr) 2010-04-26 2011-03-29 Unité hydraulique pour une tête de cylindre d'un moteur à combustion interne dotée d'une commande de soupape hydraulique variable à échange de gaz

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US (1) US8413621B2 (fr)
EP (1) EP2381075B1 (fr)
DE (1) DE102010018209A1 (fr)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012200366A1 (de) * 2012-01-12 2013-07-18 Schaeffler Technologies AG & Co. KG Vollvariable hydraulische Ventilsteuereinheit für Gaswechselventile von Hubkolbenbrennkraftmaschinen, insbesondere mehrzylindrischen Maschinen
DE102014211193A1 (de) 2014-06-12 2015-12-17 Schaeffler Technologies AG & Co. KG Hydraulikeinheit für eine Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb
GB2553120B (en) * 2016-08-24 2019-12-25 Jaguar Land Rover Ltd Variable valve lift system with a diffusing system
DE102016218918B4 (de) 2016-09-29 2018-09-13 Schaeffler Technologies AG & Co. KG Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb
DE102016219227A1 (de) * 2016-10-05 2018-04-05 Schaeffler Technologies AG & Co. KG Gaswechselventiltrieb mit einem an einem Druckraum über eine Drossel angeschlossenen Dämpferraum
DE102016219297B4 (de) * 2016-10-05 2021-12-30 Schaeffler Technologies AG & Co. KG Hydraulikeinheit für eine Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb

Family Cites Families (9)

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DE3604233A1 (de) * 1986-02-11 1987-08-13 Bosch Gmbh Robert Ventilsteuervorrichtung fuer eine hubkolben-brennkraftmaschine
DE3939065A1 (de) * 1989-11-25 1991-05-29 Bosch Gmbh Robert Hydraulische ventilsteuervorrichtung fuer brennkraftmaschinen
DE4206696C2 (de) * 1992-03-04 2000-12-14 Bosch Gmbh Robert Hydraulische Ventilsteuervorrichtung für Motorventile
WO2001020150A1 (fr) * 1999-09-17 2001-03-22 Diesel Engine Retarders, Inc. Accumulateur a volume captif pour systeme a perte de mouvement
AU2001243313A1 (en) * 2000-02-29 2001-09-12 Bombardier Inc. Four stroke engine with cooling system
ITTO20010269A1 (it) * 2001-03-23 2002-09-23 Fiat Ricerche Motore a combustione interna, con sistema idraulico di azionamento variabile delle valvole, e mezzi di compensazione delle variazioni di vol
US7509933B2 (en) * 2006-03-06 2009-03-31 Delphi Technologies, Inc. Valve lash adjuster having electro-hydraulic lost-motion capability
DE102007054376A1 (de) 2007-11-14 2009-05-20 Schaeffler Kg Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Ventiltrieb
DE102009011983A1 (de) 2009-03-05 2010-09-09 Schaeffler Technologies Gmbh & Co. Kg Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb

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Publication number Publication date
US20110259288A1 (en) 2011-10-27
US8413621B2 (en) 2013-04-09
EP2381075A2 (fr) 2011-10-26
EP2381075A3 (fr) 2013-01-23
DE102010018209A1 (de) 2011-10-27

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