WO2018059624A1 - Distribution électrohydraulique d'un moteur à combustion interne - Google Patents

Distribution électrohydraulique d'un moteur à combustion interne Download PDF

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Publication number
WO2018059624A1
WO2018059624A1 PCT/DE2017/100820 DE2017100820W WO2018059624A1 WO 2018059624 A1 WO2018059624 A1 WO 2018059624A1 DE 2017100820 W DE2017100820 W DE 2017100820W WO 2018059624 A1 WO2018059624 A1 WO 2018059624A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
pressure
pressure chamber
slave piston
piston
Prior art date
Application number
PCT/DE2017/100820
Other languages
German (de)
English (en)
Inventor
Lothar Von Schimonsky
Oliver Hahn
Andreas Mayer
Original Assignee
Schaeffler Technologies AG & Co. KG
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Schaeffler Technologies AG & Co. KG filed Critical Schaeffler Technologies AG & Co. KG
Publication of WO2018059624A1 publication Critical patent/WO2018059624A1/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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • 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
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • 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
    • F01L13/0005—Deactivating valves
    • 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
    • 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
    • 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

Definitions

  • the invention relates to an electro-hydraulic valve drive for variable opening operation of two gas exchange valves of a cylinder of a combustion engine, comprising:
  • a first slave piston and a second slave piston which delimit the pressure chamber at end faces and in each case actuate one of the gas exchange valves against the force of a valve spring acting in the closing direction of the gas exchange valve
  • the second gas exchange valve operated by the second slave piston can be deactivated when the first gas exchange valve is opened.
  • EP 2 597 276 A1 shows an electro-hydraulic valve drive for fully variable actuation of the gas exchange valves of an internal combustion engine. It is a four-valve engine with two intake and two exhaust valves, the valve train comprises a 3/3-way electrohydraulic switching valve interconnecting the pressure chamber, the pressure relief chamber and the slave pistons of the two intake valves so that in one of the switching valve positions the inlet valves is switched off and consequently only one inlet valve is actuated.
  • a likewise generic electrohydraulic valve train is disclosed in DE 10 2015 207 622 A1 and DE 10 2016 213 976, both of which are not prepublished.
  • the present invention has for its object to provide an electro-hydraulic valve train of the type mentioned in an alternative structural design. This object is achieved in that at least the first slave piston is stepped in diameter and bounded at the diameter stage, the pressure chamber and is hydraulically connected at the end face of smaller diameter with the pressure chamber, wherein the valve drive a second hydraulic valve summarizes, in the closed state, the Interrupt connection between the face of smaller diameter and the pressure chamber, and wherein the opening operation of the second gas exchange valve:
  • Figure 2 is the pressure-valve lift map of the first embodiment
  • Figure 3 shows the second embodiment with different slave piston.
  • FIGS. 1 a and 1 b show the essential components of an electrohydraulic valve train of an internal combustion engine and the hydraulic connection of the components. It is a multi-valve engine with two identical gas exchange valves 1 and 2 per cylinder and present with two variably actuated intake valves 1 and 2.
  • the variable opening operation also includes the complete and sole deactivation of the second intake valve 2.
  • the valve train comprises one of the cam 3 of a camshaft by means of a Rollenschlepphebels 4 driven master piston 5 and two slave pistons 6 and 7, the actuate the inlet valves 1, 2 against the force acting in the closing direction of the valve springs 8.
  • the master piston 5 and the slave piston 6, 7 define a pressure chamber 9, which is hydraulically connected via a first hydraulic valve 10 with a pressure relief chamber 1 1.
  • the first hydraulic valve 10 is an electrically operated 2/2-way valve in normally open configuration, which accordingly interrupts the connection between the pressure chamber 9 and the pressure relief chamber 1 1 in the illustrated energized state.
  • the printing Lastungsraum 1 1 is connected on the one hand via a check valve 12 to the pressure medium supply of the internal combustion engine and the other to a medium-pressure accumulator 13 with a spring-loaded accumulator piston 14.
  • the first slave piston 6 actuating the first inlet valve 1 and the second slave piston 7 actuating the second inlet valve 2 have the same design with a stepped diameter and are each guided in a slave cylinder 15 and 16 which is correspondingly stepped thereto. Both slave piston 6, 7 limit the pressure chamber 9 at the diameter step 17.
  • the first slave piston 6 is hydraulically connected to the end face 18 of smaller diameter with the pressure chamber 9.
  • a second hydraulic valve 19 is arranged, which interrupts this connection according to Figure 1 a and produces according to Figure 1 b.
  • An overflow line 20 hydraulically connects the two slave pistons 6, 7 to their front surfaces 18 of smaller diameter and is arranged between the slave cylinders 15, 16 such that the mouths of the overflow line 20 reach the slave pistons 6, 7 from their mouths until a predetermined opening stroke Outer jacket are closed.
  • the second hydraulic valve 19 is connected to the three terminals slave cylinder 15 of the first slave piston 6, pressure chamber 9 and overflow 20, a 3/2-way valve, the closed state of Figure 1 a, the connection between the first slave piston 6 and the pressure chamber 9 and a connection 21 between the overflow 20 and the pressure chamber 9 interrupts.
  • the connection 21 is connected to the overflow line 20 between throttle bodies 22, which serve as hydraulic valve brakes in the final closing phase of the inlet valves 1, 2 and the slave piston 6, 7.
  • each have a pressure relief valve 23 is arranged, which is connected on the one hand to the pressure relief chamber 1 1 and on the other hand to a slave cylinder 15 to closing check valve 24 to the pressure chamber 9.
  • the pressure relief valves 23 are opened in the final closing phase of the inlet valves 1, 2 by the end faces 18 of smaller diameter of the slave pistons 6, 7 in order to allow complete closing of the inlet valves 1, 2 in the then already closed orifices of the overflow line 20.
  • the overflow line 20 is further hydraulically connected to a recuperating high pressure accumulator 25 and to compensate for loss of hydraulic fluid in the slave cylinders 15, 16 with the pressure relief chamber 1 1.
  • a check valve 26 which opens to the high-pressure accumulator 25 and prevents the relatively high pressure in the high-pressure accumulator 25 in the pressure relief chamber 1 1 relaxed.
  • the first hydraulic valve 10 ensures that the connection between the pressure chamber 9 and the pressure relief chamber 11 is either established or interrupted. Consequently, a hydraulic fluid flow from the pressure chamber 9 in the pressure relief chamber 1 1 is enabled or prevented, wherein a partial volume of the displaced by the driven master piston 5 hydraulic fluid is continuously displaced adjustable in the pressure relief chamber 1 1 depending on the valve opening time and duration.
  • the variability of the intake valve actuation based on the correspondingly variable hydraulic fluid volume of the pressure chamber 9 extends on the one hand within the limits of maximum opening stroke of the intake valves 1 and 2 when the first hydraulic valve 10 is in the closed position during the entire stroke phase of the master piston 5 and the hydraulic displaced by the master piston 5 - Tel the slave piston 6, 7 applied according to the survey of the cam 3, and on the other hand complete deactivation of both intake valves 1 and 2, when the first hydraulic valve 10 is at least to the maximum elevation of the master piston 5 in the open position and the displaced by the master piston 5 hydraulic fluid completely in the pressure relief chamber 1 1 is pushed out.
  • This basic mode of operation applies both to the two-valve actuation, in which the two inlet valves 1, 2 are opened synchronously, and also to the one-valve actuation, in which the second inlet valve 2 is completely deactivated.
  • the second hydraulic valve 19 according to FIG. 1 a is in the closed state. Accordingly, the pressurization of the two slave pistons 6, 7 relevant for the synchronous opening actuation of the intake valves 1, 2 takes place mainly at the respective end face 28 of the diameter stage 17.
  • the high-pressure accumulator 25, for the purpose of recuperation during each closing operation of the intake valves 1, 2 is biased by the displaced from the slave cylinders 15, 16 in the overflow 20 hydraulic fluid, supports the opening operation by the two end faces 18 of smaller diameter pressurized.
  • connection between the overflow line 20 and the pressure chamber 9 is also made via the second hydraulic valve 19, so that when closing the inlet valve 1, the displaced from the slave cylinder 15 in the overflow 20 hydraulic fluid only in the pressure chamber 9 and in the pressure relief space 1 first relaxed. Consequently, the high-pressure accumulator 25 remains inactive during Einventilbetrucist.
  • FIG. 2 illustrates the principle underlying the invention of the different pressures in the pressure chamber 9 designated therein as HPC, with which the slave piston or pistons 6, 7 in the single-valve or two-valve actuation depending on the opening stroke of the intake valves 1 , 2 be charged.
  • HPC pressure chamber 9 designated therein as HPC
  • the map is greatly simplified in that it is based on quasi-static consideration and thus does not take into account the dynamics of the valve train.
  • the numerical values given refer to that in the figures 1 illustrated embodiment with the same size end faces AR and ⁇
  • the valve spring 8 is biased at 260 N with the intake valves 1, 2 closed, and its maximum force is 360 N at the maximum lift of the intake valve 1, 2 of 10 mm. This corresponds to a pressure chamber pressure between 45 bar and 62 bar in the two-valve operation and between 22.5 bar and 31 bar in the Einventilbetuschist.
  • the working pressure range of the high-pressure accumulator 25 is above the maximum pressure chamber pressure in the one-valve actuation so that the pressure chamber pressure present in the slave cylinder 15 can not relax into the high-pressure accumulator 25 with a corresponding stroke loss of the first inlet valve 1.
  • the working pressure range is below the minimum pressure chamber pressure in the two-valve actuation so as not to hydraulically block the complete closing of the inlet valves 1, 2 due to excessive pressure in the slave cylinders 15, 16 then separated from the pressure chamber 9.
  • the (optional) connection 21 between the overflow line 20 and the pressure chamber 9 can be omitted, in which case the second hydraulic valve 19 is designed as a 2/2 way valve.
  • the illustrated in Figure 3 second embodiment of an electro-hydraulic valve train differs from the previously described valve train for a fact that a recuperating high-pressure accumulator is missing.
  • the two slave pistons 6 and 7 ' are different in that only the first slave piston 6 is provided with the diameter step 17.
  • the second slave piston 7 ' is guided with a uniform diameter in a correspondingly ungestuften slave cylinder 16 ' .
  • the following relationship applies to the faces of the slave pistons:
  • the first slave piston 6 is hydraulically connected to the end face 28 of the diameter stage 17 via a branching line 30 to the pressure chamber 9.
  • the second slave piston 7 ' is hydraulically connected to the end surface 29 via the line 30 to the pressure chamber 9.
  • the two line branches each contain a conventional hydraulic valve brake, which is symbolized by a non-return valve 31 and the throttling points 22 opening towards the slave cylinder 15 and 16 and which decelerates the closing inlet valve 1, 2 to an acoustically and mechanically acceptable valve seating speed.
  • the first slave piston 6 is hydraulically connected to its end face 18 of smaller diameter with the pressure chamber 9.
  • the connection comprises two lines 32 and 33, of which one line 32, the 2/2 way valve and the other line 33 includes a to the line 30 and thus to the pressure chamber 9 out opening check valve 34.
  • the first slave piston 6 is hydraulically connected to its end face 18 of smaller diameter via a pressure equalization line 35 with the pressure relief space 1 1.
  • a check valve 36 is arranged, which opens to the first slave piston 6 out.
  • recuperating high-pressure accumulator can be dispensed with in the first exemplary embodiment or supplemented in the second exemplary embodiment.

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

Abstract

L'invention concerne une distribution électrohydraulique destinée à l'actionnement en ouverture variable de deux soupapes d'échange des gaz (1, 2) d'un cylindre d'un moteur à combustion interne, comprenant : un piston transmetteur (5) et une chambre de compression (9) délimitée par le piston transmetteur, un premier piston récepteur (6) et un deuxième piston récepteur (7, 7'), lesquels délimitent la chambre de compression et actionnent respectivement l'une des soupapes d'échange des gaz, une chambre de réduction de pression (11) reliée à la chambre de compression, et une première vanne hydraulique (10) qui, en position fermée, interrompt la liaison entre la chambre de réduction de pression et la chambre de compression. La deuxième soupape d'échange des gaz (2) actionnée par le deuxième piston récepteur peut être désactivée lorsque la soupape d'échange des gaz (1) est ouverte. Au moins le premier piston récepteur présente ici un diamètre étagé et délimite la chambre de compression au niveau de son gradin de diamètre (17) et il est relié hydrauliquement à la chambre de compression par sa face frontale (18) ayant le diamètre le plus petit. Une deuxième vanne hydraulique (19), lorsqu'elle est fermée, interrompt le liaison entre la face frontale de plus petit diamètre et la chambre de compression. L'actionnement en ouverture de la deuxième soupape d'échange des gaz : est désactivé lorsque la deuxième vanne hydraulique se trouve à l'état ouvert et est activé lorsque la deuxième vanne hydraulique se trouve à l'état fermé.
PCT/DE2017/100820 2016-09-27 2017-09-26 Distribution électrohydraulique d'un moteur à combustion interne WO2018059624A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016218562.4A DE102016218562B4 (de) 2016-09-27 2016-09-27 Elektrohydraulischer Ventiltrieb zur variablen Öffnungsbetätigung von zwei Gaswechselventilen eines Zylinders eines Verbrennungsmotors
DE102016218562.4 2016-09-27

Publications (1)

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WO2018059624A1 true WO2018059624A1 (fr) 2018-04-05

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WO (1) WO2018059624A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019106464A1 (de) 2018-05-08 2019-11-14 Schaeffler Technologies AG & Co. KG Bremsvorrichtung für ein variables Ventiltriebsystem
CN116044538B (zh) * 2023-03-08 2023-06-23 龙口中宇热管理系统科技有限公司 一种液压可变气门控制机构

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2597276A1 (fr) 2011-11-24 2013-05-29 C.R.F. Società Consortile per Azioni Moteur avec un mécanisme de distibution variable avec une électrovanne a troi voies
WO2015051794A1 (fr) * 2013-10-11 2015-04-16 Schaeffler Technologies AG & Co. KG Commande hydraulique des soupapes pour moteur à combustion interne
DE102015207622A1 (de) 2015-04-27 2016-10-27 Schaeffler Technologies AG & Co. KG Elektrohydraulischer Ventiltrieb für eine Brennkraftmaschine
DE102016216976A1 (de) 2015-09-25 2017-03-30 Schaeffler Technologies AG & Co. KG Kupplungsgeber mit Hochdruckraum im Kolben, (Doppel-)Kupplung mit Kupplungsgeber und Antriebstrang

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19531870C2 (de) 1995-08-30 2002-07-18 Bosch Gmbh Robert Kraftstoffeinspritzsystem
DE102016213976B4 (de) 2016-07-29 2018-07-05 Schaeffler Technologies AG & Co. KG Elektrohydraulischer Ventiltrieb eines Verbrennungsmotors

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2597276A1 (fr) 2011-11-24 2013-05-29 C.R.F. Società Consortile per Azioni Moteur avec un mécanisme de distibution variable avec une électrovanne a troi voies
WO2015051794A1 (fr) * 2013-10-11 2015-04-16 Schaeffler Technologies AG & Co. KG Commande hydraulique des soupapes pour moteur à combustion interne
DE102015207622A1 (de) 2015-04-27 2016-10-27 Schaeffler Technologies AG & Co. KG Elektrohydraulischer Ventiltrieb für eine Brennkraftmaschine
DE102016216976A1 (de) 2015-09-25 2017-03-30 Schaeffler Technologies AG & Co. KG Kupplungsgeber mit Hochdruckraum im Kolben, (Doppel-)Kupplung mit Kupplungsgeber und Antriebstrang

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DE102016218562B4 (de) 2018-08-23
DE102016218562A1 (de) 2018-03-29

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