EP2060754B1 - Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Ventiltrieb - Google Patents

Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Ventiltrieb Download PDF

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Publication number
EP2060754B1
EP2060754B1 EP08167285A EP08167285A EP2060754B1 EP 2060754 B1 EP2060754 B1 EP 2060754B1 EP 08167285 A EP08167285 A EP 08167285A EP 08167285 A EP08167285 A EP 08167285A EP 2060754 B1 EP2060754 B1 EP 2060754B1
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EP
European Patent Office
Prior art keywords
hydraulic
pressure space
housing
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.)
Active
Application number
EP08167285A
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German (de)
English (en)
French (fr)
Other versions
EP2060754A2 (de
EP2060754A3 (de
Inventor
Martin Rauch
Markus Proschko
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
Original Assignee
Schaeffler Technologies AG and Co KG
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Publication of EP2060754A3 publication Critical patent/EP2060754A3/de
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Publication of EP2060754B1 publication Critical patent/EP2060754B1/de
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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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • 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
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/02—Formulas

Definitions

  • a small-volume medium-pressure space can be problematic during the starting process of the internal combustion engine, especially if it is a starting operation at low outside temperatures and after a long stoppage of the internal combustion engine. This is due to the fact that the hydraulic fluid supply to the internal combustion engine does not yet deliver sufficient hydraulic fluid flow into the medium-pressure space during the starting process and only the hydraulic fluid volume remaining in the medium-pressure space and shrunk at low temperatures is insufficiently large for a complete refilling of a then-expanding high-pressure space. This problem applies to a greater extent in a short time repetitive starting operations, since in this case the hydraulic fluid consumption from the medium-pressure space can be greater than the nachge deviste volume of the hydraulic fluid supply of the internal combustion engine. Such multi-start operations are typical, for example, for taxi cabs at taxi stands.
  • the present invention is therefore the object of a hydraulic unit of the type mentioned in such a way that the disadvantages mentioned are eliminated by simple means. Accordingly, even with a compact hydraulic housing with a corresponding volume-limited medium-pressure space always safe and complete refilling of the expanding during the starting process of the engine high-pressure chamber to be ensured with hydraulic fluid.
  • the partition wall is formed as a housing intermediate part of the assembled in sandwich construction of the housing parts hydraulic housing.
  • the throttle opening extends at a geodetically deep point of the partition. This ensures even with possibly only slightly filled low pressure space, for example due to very low ambient temperatures and correspondingly strong shrinking hydraulic fluid, a bubble-free suction of hydraulic fluid from the low-pressure chamber in the medium-pressure space.
  • the upper housing part to be provided with at least one opening into the cylinder head vent opening for the low-pressure chamber.
  • the safety of a complete refilling operation of the high-pressure chamber can be increased in particular with regard to multiple starts within a short time by a volume ratio of the pressure chambers with (V L + V M ) / V H ⁇ 2, if V L is the volume of the low-pressure space, V M the volume of Medium pressure space and V H is the volume of the high-pressure chamber.
  • the hydraulic fluid reservoir available for refilling the high-pressure chamber should be at least twice as large as the high-pressure chamber, which of course is also important for such valve trains, in which two slave units for the simultaneous actuation of two gas exchange valves communicate with a single transmitter unit.
  • the partition should be designed as a housing intermediate part of the assembled in sandwich construction of the housing parts hydraulic housing. Alternatively, however, it may also be provided an integrally formed on the upper housing part partition, in which case such a housing upper part may be prepared for example by hydroforming.
  • the housing upper part should be coated with a sealing material made of elastomer material, at least in the area of contact with the housing intermediate part.
  • the sealing means which prevent an emptying of the low-pressure space can be either an elastomer seal which is printed or sprayed locally on the sealing surface of the housing upper part or an elastomer coating applied over the entire surface of the housing upper part.
  • a separate seal between the upper housing part and the intermediate housing part for example in the form of a paper seal possible.
  • the upper housing part can be made either in a thermoforming process of aluminum or steel material or in an injection molding of plastic.
  • the known operation of the hydraulic valve train 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 as a function of 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 split.
  • the timing, but also the lifting height of the gas exchange valve 4 can be set fully variable.
  • the hydraulic unit 5 as a further essential part of a common hydraulic housing 19, so that the hydraulic unit 5 can be mounted as a preassembled and optionally already filled with hydraulic fluid assembly in the cylinder head 2 of the internal combustion engine.
  • the executed for a 4-cylinder inline hydraulic unit 5 is in general view FIG. 2 out.
  • the composite in sandwich construction hydraulic housing 19 consists of a lower housing part 20, formed as intermediate housing part 21 partition wall 18 and a housing upper part 22. While the housing parts 20, 21, 22 are screwed together at various Verschraubungsddlingen 23 hydraulically sealing, the lower housing part 20 separate Verschraubungsus 24 to Attaching the entire hydraulic unit 5 in the cylinder head 2 of the internal combustion engine.
  • the four transmitter units 6 each comprise a support element 25 accommodated in the housing lower part 20, a rocker arm 26 pivotally mounted thereon and having a rotatably mounted roller 27 for a low-friction cam tapping From the intermediate housing part 21 outgoing bracket 28 serve as captive for the drag lever 26 mounted in the cylinder head 2 hydraulic unit 5.
  • This is also designed so that each of the transmitter units 6 with two slave units 8 interacts.
  • only one cam 3 and one transmitter unit 6 are required for each pair of identical gas exchange valves 4, ie intake valves or exhaust valves of a cylinder of the internal combustion engine, wherein the hydraulic volume displaced by the pump tappet 7 simultaneously acts on both slave units 8.
  • the respective one encoder unit 6 and the two slave units 8 associated hydraulic valves 10 can be seen with electrical connectors 29, wherein the normally open hydraulic valves 10 in a known per se and not shown here in valve receptacles are fixed in the housing base 20.
  • FIG. 3 shows cross section through the hydraulic unit 5 before.
  • the pressure accumulator 13 connected to the medium-pressure chamber 12 is also shown with the compensating piston 14, which is acted on by spring force.
  • the throttle opening 17 connecting the low-pressure chamber 16 with the medium-pressure chamber 12 is arranged such that it extends at a geodetically low point of the housing intermediate part 21 of the hydraulic unit 5 inclined to gravity g in and / or with the internal combustion engine. As explained above, this ensures that only bubble-free hydraulic fluid from the low-pressure chamber 16 is sucked into the medium-pressure space 12.
  • each of the medium-pressure spaces 12 can also communicate with the associated low-pressure space 16 via two or more throttle openings 17. Conversely, it would also be conceivable to associate each of two medium-pressure chambers 12 with two or more low-pressure chambers 16 separated from one another.
  • Gas bubbles which pass through the throttle opening 17 from the medium-pressure chamber 12 into the low-pressure chamber 16 during operation of the internal combustion engine, can be deposited in the interior of the cylinder head 2 via a vent opening 30 extending in the upper housing part 22 and opening into the cylinder head 2.
  • the upper housing part 22 is coated with a sealing material made of elastomer material, not shown here.
  • this coating is not limited only to the contact region to the intermediate housing part 21, but is located on the entire surface of the upper housing part 22 produced here in a deep-drawing of sheet steel.
  • the volume designated by V L of the low-pressure chamber 16 on the one hand taking into account the space available in the cylinder head 2 and on the other hand, to be sized as large as possible with an always sufficient hydraulic fluid reservoir.
  • V M the volume ratio
  • V H the volume ratio (V L + V M ) to V H has a value of at least 2
  • the pressure accumulator 13 the partition 18 and the check valve 15 limited volume of the medium-pressure space 12 and with V H the volume of the high-pressure chamber 11 delimited by the transmitter unit 6, by the slave unit or units 8 and by the hydraulic valve 10 is designated.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
EP08167285A 2007-11-14 2008-10-22 Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Ventiltrieb Active EP2060754B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007054376A DE102007054376A1 (de) 2007-11-14 2007-11-14 Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Ventiltrieb

Publications (3)

Publication Number Publication Date
EP2060754A2 EP2060754A2 (de) 2009-05-20
EP2060754A3 EP2060754A3 (de) 2010-05-05
EP2060754B1 true EP2060754B1 (de) 2011-12-14

Family

ID=40345032

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08167285A Active EP2060754B1 (de) 2007-11-14 2008-10-22 Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Ventiltrieb

Country Status (6)

Country Link
US (1) US8020526B2 (ko)
EP (1) EP2060754B1 (ko)
JP (1) JP5354260B2 (ko)
KR (1) KR101515636B1 (ko)
CN (1) CN101435353B (ko)
DE (1) DE102007054376A1 (ko)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
DE102018129287A1 (de) 2018-11-21 2020-05-28 Schaeffler Technologies AG & Co. KG Verbrennungsmotor mit hydraulisch variablem Gaswechselventiltrieb

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DE102009011983A1 (de) 2009-03-05 2010-09-09 Schaeffler Technologies Gmbh & Co. Kg Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb
DE102009011982A1 (de) 2009-03-05 2010-09-09 Schaeffler Technologies Gmbh & Co. Kg Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb
EP2261471B1 (en) * 2009-05-25 2014-09-17 C.R.F. Società Consortile per Azioni Internal combustion engine with two hydraulically actuated intake valves with different return springs for each cylinder
EP2282022B1 (en) 2009-06-30 2011-11-23 C.R.F. Società Consortile per Azioni Electronically controlled hydraulic system for variable actuation of the valves of an internal combustion engine, with fast filling of the high pressure side of the system
BR112012013125B1 (pt) * 2009-12-08 2021-01-12 Schaeffler Technologies AG & Co. KG motor de combustão com comando de válvula eletro-hidráulico, e processo para operar o motor de combustão com comando de válvula eletro-hidráulico
DE102010013927B4 (de) 2010-04-06 2019-03-21 Schaeffler Technologies AG & Co. KG Verbrennungskraftmaschine mit zwei fluiddicht voneinander getrennten Schmierräumen
DE102010018209A1 (de) 2010-04-26 2011-10-27 Schaeffler Technologies Gmbh & Co. Kg Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb
DE102010024028A1 (de) 2010-06-16 2011-12-22 Schaeffler Technologies Gmbh & Co. Kg Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb
DE102010052550A1 (de) * 2010-11-25 2012-05-31 Schaeffler Technologies Gmbh & Co. Kg Druckspeicher eines hydraulischen Betätigungssystems
CN102278161B (zh) * 2011-07-19 2013-07-24 天津大学 可变气门用缓冲液压缸
DE102012200469A1 (de) * 2012-01-13 2013-07-18 Schaeffler Technologies AG & Co. KG Aktuator für vollvariable Ventiltriebsysteme
DE102012212860B3 (de) * 2012-07-23 2013-12-12 Schaeffler Technologies AG & Co. KG Verfahren zur Ermittlung der Füllung der Zylinder von Hubkolbenbrennkraftmaschinen
DE102012221354A1 (de) 2012-11-22 2013-01-24 Schaeffler Technologies AG & Co. KG Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb
DE102013213695A1 (de) * 2013-07-12 2015-01-15 Schaeffler Technologies Gmbh & Co. Kg Vorrichtung zum Entlüften von Hohlräumen
SE540359C2 (sv) * 2013-10-16 2018-08-07 Freevalve Ab Förbränningsmotor
US9217339B2 (en) 2014-04-24 2015-12-22 Ford Global Technologies, Llc Hydraulic rolling cylinder deactivation systems and methods
US9631526B2 (en) * 2014-09-17 2017-04-25 Fca Us Llc Engine variable valve lift system having integrated hydraulic fluid retention
DE102014219736A1 (de) 2014-09-30 2016-03-31 Schaeffler Technologies AG & Co. KG Ventiltrieb einer Brennkraftmaschine
DE102016218784A1 (de) * 2015-10-26 2017-04-27 Schaeffler Technologies AG & Co. KG Ventilsteueraktor mit Eisenspansammelmagnet in Ölleitung
WO2017170708A1 (ja) 2016-03-31 2017-10-05 マツダ株式会社 多気筒エンジンの制御装置
JP6350975B2 (ja) * 2016-03-31 2018-07-04 マツダ株式会社 エンジンの制御装置
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
DE102016219297B4 (de) 2016-10-05 2021-12-30 Schaeffler Technologies AG & Co. KG Hydraulikeinheit für eine Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb
FR3071869B1 (fr) * 2017-10-02 2019-10-11 Vianney Rabhi Actionneur hydraulique de soupape a regeneration
US11168592B2 (en) * 2019-02-27 2021-11-09 Ford Global Technologies, Llc Variable valve actuation system

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Publication number Priority date Publication date Assignee Title
DE102018129287A1 (de) 2018-11-21 2020-05-28 Schaeffler Technologies AG & Co. KG Verbrennungsmotor mit hydraulisch variablem Gaswechselventiltrieb

Also Published As

Publication number Publication date
JP5354260B2 (ja) 2013-11-27
CN101435353B (zh) 2013-03-27
KR101515636B1 (ko) 2015-04-27
EP2060754A2 (de) 2009-05-20
CN101435353A (zh) 2009-05-20
JP2009121481A (ja) 2009-06-04
US20090120389A1 (en) 2009-05-14
KR20090049999A (ko) 2009-05-19
US8020526B2 (en) 2011-09-20
DE102007054376A1 (de) 2009-05-20
EP2060754A3 (de) 2010-05-05

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