EP3519683A1 - Brennkraftmaschine mit hydraulisch variablem gaswechselventiltrieb - Google Patents
Brennkraftmaschine mit hydraulisch variablem gaswechselventiltriebInfo
- Publication number
- EP3519683A1 EP3519683A1 EP17787318.9A EP17787318A EP3519683A1 EP 3519683 A1 EP3519683 A1 EP 3519683A1 EP 17787318 A EP17787318 A EP 17787318A EP 3519683 A1 EP3519683 A1 EP 3519683A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- hydraulic
- housing
- internal combustion
- combustion engine
- 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.)
- Granted
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 24
- 230000005484 gravity Effects 0.000 claims abstract description 15
- 238000013022 venting Methods 0.000 claims description 16
- 239000012530 fluid Substances 0.000 description 14
- 238000001816 cooling Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 230000002035 prolonged effect Effects 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000001934 delay Effects 0.000 description 1
- 238000013461 design Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000007598 dipping method Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000037406 food intake Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000002401 inhibitory effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
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
- 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
-
- 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 invention relates to an internal combustion engine with hydraulically variable gas exchange valve drive, comprising:
- a hydraulic housing having a pressure chamber, a pressure relief chamber and a venting channel, the pressure chamber, the pressure relief chamber and the venting channel being hydraulically connected to one another,
- a master piston guided in the hydraulic housing, which is driven on the outside of the housing by a cam and which delimits the pressure chamber on the housing side,
- 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 which is mounted on the cylinder head of the internal combustion engine and whose hydraulic chambers - in the direction of gravity - vent down into the cylinder head.
- the operational venting of the hydraulic system causes the entrained air bubbles carried by the hydraulic medium in the vicinity of the hydraulic housing and thus prevents air in excessive amount in the pressure chamber and there affects the required for the hydraulic gas exchange valve stiffness keit the hydraulic fluid in an inadmissible height.
- the vent promotes the leakage of hydraulic fluid from the hydraulic housing when the engine is turned off. Because the cooling and shrinking volume of hydraulic fluid creates negative pressure in the hydraulic raulik basic, which is compensated for ingestion of air via vent channel. During this pressure equalization, gravity will cause the hydraulic chambers to deflate through the guide gap between the slave piston and the hydraulic housing in its vicinity.
- EP 2 060 754 A2 proposes a hydraulic unit with an additional low-pressure space which communicates with the interior of the cylinder head via a geodetically highly positioned housing opening and via a geodetically deeply positioned throttle point with the pressure relief space for the purpose of venting.
- the low-pressure chamber is an extended hydraulic reservoir, which supplies the pressure chamber during the starting process of the internal combustion engine with sufficiently air-free hydraulic fluid.
- venting against the direction of gravity on the upper side of the hydraulic housing requires a cylinder head cover, which seals the cylinder head with the hydraulic housing to the environment, and thus an additional component.
- the present invention has the object to further develop an internal combustion engine of the type mentioned in that the hydraulic leakage from the hydraulic housing is reduced to such an extent that the hydraulic fluid in the pressure chamber does not fall below a critical for the start process level even after prolonged downtime of the engine ,
- the venting channel to open in a hydraulic reservoir wherein the channel mouth with respect to the direction of gravity is below the normal level of the hydraulic reservoir.
- the term ' normal level ' is to be understood as meaning the level which, in the steady state, shortly after switching off the fuel adjusting the hydraulic motor in the hydraulic reservoir, wherein the internal combustion engine is not or at most insignificantly inclined with respect to their installation position.
- the channel opening "dipping" in the hydraulic medium prevents air from being sucked back into the pressure relief chamber via the venting channel when the internal combustion engine is at a standstill and due to the cooling down of the hydraulic medium volume This condition extends over a sufficiently long period of time and at least until the level, if applicable of the hydraulic reservoir has dropped due to the cooling volume shrinkage of the hydraulic fluid from the hydraulic housing under the channel mouth.
- the hydraulic reservoir open to the surroundings of the hydraulic housing can be formed either on the hydraulic housing itself or through a local depression 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 with respect to the direction of gravity should run as deep as possible and concretely below the boundary of the pressure chamber from the slave piston.
- the geodätician height difference between the (retracted in the hydraulic housing) slave piston and the channel mouth directly affects the negative pressure, which forms when the engine and shrinking hydraulic fluid against the environment of the hydraulic housing and counteracts the gravitational leakage of hydraulic fluid from the hydraulic housing.
- the channel mouth is inclined with respect to the direction of gravity, i. geodetic always below the level of the hydraulic reservoir. This condition assumes that the hydraulic reservoir can be made sufficiently voluminous in view of the temperature and leakage-reducing hydraulic volume in the hydraulic housing.
- the volume of the hydraulic reservoir is constructively limited such that a drop in the reservoir level below the channel mouth and consequently the suck back of air are unavoidable.
- the downtime of the internal combustion engine can be significantly extended until it reaches the critical level in the pressure chamber that the vent channel at least locally has a dimensioned so large that air bubbles can ascend therein without pushing the overlying hydraulic or oil column in front of him and to displace into the pressure relief chamber.
- the cross-section is to be dimensioned so that the air sucked back rises in the stationary oil column, so that the remaining oil column virtually closes the channel mouth again and maintains the leakage-inhibiting negative pressure in the hydraulic housing.
- the venting channel in the case of an oil having the viscosity index 0W20 and in the case of a circular first pipe section, the venting channel must have a pipe inside diameter of at least 6 mm. Particularly good and robust results were achieved with the tube inner diameter of about 8 mm.
- the circular shape of the vent channel can have manufacturing advantages. Nevertheless, other cross-sectional shapes are possible, as long as the rising of the air without displacing the overlying oil column is possible.
- the channel mouth should be formed by a circular second pipe section, which is followed by (abrupt or gradual) reduction of the tube outer diameter of the first pipe section. This structural design of the vent channel with the diameter-stepped pipe sections may be required if the surface of the hydraulic reservoir is too small to accommodate the relatively large diameter of the first pipe section.
- the venting channel is expediently formed by a venting tube fastened in the hydraulic housing and preferably screwed in, the first and possibly the second tubular section being parts of the venting tube.
- Figure 1 a the first embodiment with a stepped in diameter vent passage
- Figure 1 b in an enlarged detail of the channel mouth and the hydraulic reservoir of the first embodiment
- Figure 2 shows the second embodiment with a comparatively low-lying
- Figure 3 shows the third embodiment with a permanently immersed in the hydraulic reservoir channel mouth.
- FIG 1 a shows schematically the essential for understanding the invention section of an internal combustion engine with hydraulically variable Gas
- Gas Shown is a cylinder head 1 with two similar and spring-loaded in the closing direction gas exchange valves 2 per cylinder and associated cam 3 of a camshaft.
- the variability of the gas exchange valve drive is generated in a known manner by means of a arranged between the cam 3 and the gas exchange valves 2 hydraulic unit.
- This comprises a mounted in the cylinder head 1 hydraulic housing 4, in which each cylinder a pressure chamber 5 and a pressure relief chamber 6 formed and a master piston 7 are guided outside the housing is driven by the cam 3 and the housing side limited the pressure chamber 5.
- two slave pistons 8 are guided per cylinder, which drive the gas exchange valves 2 on the outside of the housing and bound the common pressure chamber 5 on the housing side.
- An electromagnetic hydraulic valve 9, in this case a normally open 2-2-way valve interrupts in the closed state, the hydraulic connection between the pressure relief chamber 6 and the pressure chamber 5.
- a portion of the displaced by the master piston 7 hydraulic fluid can flow into the pressure relief chamber 6, without participating in the operation of the slave piston 8 and the associated gas exchange valve 2.
- a piston pressure accumulator 10 for receiving the displaced hydraulic fluid is connected.
- the pressure relief chambers 6 are connected via a hydraulic connection, not shown, on the hydraulic housing 4 to the hydraulic circuit, ie the oil circuit of the internal combustion engine.
- the pressure relief chambers 6 are connected to a common vent channel 1 1 in the hydraulic housing 4, which is hydraulically connected inside the housing via throttle points 12 with the respective pressure relief chamber 6 and outside the housing in a hydraulic reservoir 13 in the interior of the cylinder head 1 opens.
- the throttle points 12 are geodetic, ie with respect to the symbolized by the arrow of gravity g above the pressure relief chambers 6, and the hydraulic reservoir 13 is located geodetically below the pressure relief chambers 6.
- the channel mouth 14 of the vent passage 1 1 is not only geodetically below the level 15 of the hydraulic reservoir 13 but also below the boundary 16 of the pressure chamber 5 by the slave piston 8, when they are fully retracted in the hydraulic housing 4 with closed gas exchange valves 2.
- the pressureless hydraulic reservoir 13, which is pressureless with respect to the internal pressure of the cylinder head 1, is closed by a depression closed in the direction of gravity 17 formed in the cylinder head 1 (see Figure 1 b), in which hydraulic fluid accumulates during operation of the internal combustion engine.
- the vent channel 1 1 is outside the housing formed by a solid and sealingly screwed in the hydraulic housing 4 vent pipe 18.
- This has a circular first pipe section 19, whose tube inner diameter 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 a pipe inside diameter of approximately 4 mm.
- the tube outer diameter of the second tube section 21 is correspondingly small and dimensioned such that the second tube section 21 can be introduced into the cavity 17 without collision during assembly of the hydraulic unit into the cylinder head 1.
- Figure 1 a shows the vented filling state of the hydraulic system shortly after switching off the internal combustion engine.
- the level 15 of the hydraulic reservoir 13 of the initially defined normal level shows the filling state of the hydraulic system at a much later time at which the hydraulic fluid is completely cooled and its volume is shrunk accordingly.
- the forming with the reduction in volume in the hydraulic chambers negative pressure causes the suction of hydraulic fluid from the hydraulic reservoir 13 in the pressure relief chambers 6. This air bubbles free after-expiration ends when the level 15 of the hydraulic reservoir 13 geodetically below the channel opening 14 drops. Thereafter, the pressure equalization between the pressure relief chambers 6 and the environment of the hydraulic housing 4 takes place by sucking back of air bubbles 22.
- the higher oil column between the boundary 16 and the level 15 of the Hydraulikre- reservoir 13 ' causes an increased negative pressure in the hydraulic system in favor of further reduced leakage of the pressure chambers 5 through the guide gap to the slave piston 8.
- the vent passage 1 1 is in this embodiment by a vent pipe 18 'formed with a uniform diameter, wherein the pipe inner diameter is dimensioned so large in this case that the therein rising air bubbles 22, the standing in the vent pipe 18 ' oil column can happen.
- the third exemplary embodiment according to FIG. 3 has a hydraulic reservoir 13 " whose volume is so great that the channel mouth 14 is always geodetically below the level 15 of the hydraulic reservoir 13 " .
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Claims
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 (de) | 2016-09-29 | 2017-09-28 | Brennkraftmaschine mit hydraulisch variablem gaswechselventiltrieb |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3519683A1 true EP3519683A1 (de) | 2019-08-07 |
EP3519683B1 EP3519683B1 (de) | 2020-09-02 |
Family
ID=60153020
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP17787318.9A Active EP3519683B1 (de) | 2016-09-29 | 2017-09-28 | Brennkraftmaschine mit hydraulisch variablem gaswechselventiltrieb |
Country Status (5)
Country | Link |
---|---|
US (1) | US10900389B2 (de) |
EP (1) | EP3519683B1 (de) |
CN (1) | CN109715911B (de) |
DE (1) | DE102016218918B4 (de) |
WO (1) | WO2018059627A1 (de) |
Families Citing this family (1)
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 |
Family Cites Families (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5447022A (en) * | 1977-09-21 | 1979-04-13 | Nissan Motor Co Ltd | Valve lifter for internal combustion engine |
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 |
JPH04111505U (ja) * | 1991-03-15 | 1992-09-28 | 本田技研工業株式会社 | 内燃機関における給油装置 |
EP1031706A1 (de) * | 1995-08-08 | 2000-08-30 | Diesel Engine Retarders, Inc. | Verfahren zum Betreiben einer Brennkraftmaschine |
RU2151305C1 (ru) | 1998-09-07 | 2000-06-20 | Военный автомобильный институт | Гидравлический привод клапанов двигателя внутреннего сгорания |
US20020179029A1 (en) | 1998-09-09 | 2002-12-05 | Watson John P. | Hydraulically actuated, electrically controlled linear motor |
DE102007054376A1 (de) | 2007-11-14 | 2009-05-20 | Schaeffler Kg | Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Ventiltrieb |
DE102008049181A1 (de) * | 2008-09-26 | 2010-04-01 | Schaeffler Kg | Elektrohydraulische Ventilsteuerung |
US9194261B2 (en) * | 2011-03-18 | 2015-11-24 | Eaton Corporation | Custom VVA rocker arms for left hand and right hand orientations |
DE102009034512A1 (de) | 2009-07-25 | 2011-01-27 | Schaeffler Technologies Gmbh & Co. Kg | Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine |
DE102010018209A1 (de) | 2010-04-26 | 2011-10-27 | Schaeffler Technologies Gmbh & Co. Kg | Hydraulikeinheit für einen Zylinderkopf einer Brennkraftmaschine mit hydraulisch variablem Gaswechselventiltrieb |
DE102010053685B4 (de) * | 2010-12-08 | 2014-10-30 | Schwäbische Hüttenwerke Automotive GmbH | Vorrichtung zur Verstellung der Drehwinkelposition einer Nockenwelle |
DE102013100632A1 (de) * | 2013-01-22 | 2014-07-24 | Lsp Innovative Automotive Systems Gmbh | Variable elektrohydraulische Ventilsteuerung |
DE102013213695A1 (de) | 2013-07-12 | 2015-01-15 | Schaeffler Technologies Gmbh & Co. Kg | Vorrichtung zum Entlüften von Hohlräumen |
DE102013223926B4 (de) | 2013-11-22 | 2018-02-08 | Schaeffler Technologies AG & Co. KG | Hydraulische Ventilbremse für einen hydraulisch variablen Ventiltrieb und Verfahren zur Einstellung der hydraulischen Ventilbremse |
CN104481625A (zh) | 2014-11-13 | 2015-04-01 | 浙江师范大学 | 一种可变配气相位系统 |
EP3032054B1 (de) | 2014-12-10 | 2017-03-29 | C.R.F. Società Consortile per Azioni | Brennkraftmaschine mit elektronisch gesteuertem hydrauliksystem zur variablen betätigung von einlassventilen, mit einer vorrichtung zum auffüllen des systems mit fluid |
CN204402605U (zh) | 2015-01-23 | 2015-06-17 | 吉林大学 | 凸轮驱动式内燃机液压全可变气门机构 |
CN205477806U (zh) | 2016-01-25 | 2016-08-17 | 李月贵 | 一种发动机全可变液压气门机构 |
CN205578058U (zh) | 2016-04-23 | 2016-09-14 | 吉林大学 | 一种液压驱动式全可变气门的机械调节装置 |
-
2016
- 2016-09-29 DE DE102016218918.2A patent/DE102016218918B4/de not_active Expired - Fee Related
-
2017
- 2017-09-28 EP EP17787318.9A patent/EP3519683B1/de active Active
- 2017-09-28 US US16/326,944 patent/US10900389B2/en active Active
- 2017-09-28 WO PCT/DE2017/100828 patent/WO2018059627A1/de unknown
- 2017-09-28 CN CN201780058183.4A patent/CN109715911B/zh active Active
Also Published As
Publication number | Publication date |
---|---|
DE102016218918B4 (de) | 2018-09-13 |
US10900389B2 (en) | 2021-01-26 |
DE102016218918A1 (de) | 2018-03-29 |
CN109715911B (zh) | 2021-10-12 |
CN109715911A (zh) | 2019-05-03 |
US20190211718A1 (en) | 2019-07-11 |
WO2018059627A1 (de) | 2018-04-05 |
EP3519683B1 (de) | 2020-09-02 |
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