WO2008071502A1 - Einrichtung zur hydraulischen ansteuerung von gaswechselventilen einer hubkolbenbrennkraftmaschine - Google Patents
Einrichtung zur hydraulischen ansteuerung von gaswechselventilen einer hubkolbenbrennkraftmaschine Download PDFInfo
- Publication number
- WO2008071502A1 WO2008071502A1 PCT/EP2007/061957 EP2007061957W WO2008071502A1 WO 2008071502 A1 WO2008071502 A1 WO 2008071502A1 EP 2007061957 W EP2007061957 W EP 2007061957W WO 2008071502 A1 WO2008071502 A1 WO 2008071502A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- cells
- cam
- gas exchange
- hydraulic
- operative connection
- Prior art date
Links
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
- 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
- Device for the hydraulic control of gas exchange valves of a reciprocating piston internal combustion engine with slave cylinders which communicate with one or more gas exchange valves, with encoder actuators which are in operative connection with at least one cam provided with base and cam profile of a camshaft rotatably driven by the reciprocating internal combustion engine and hydraulically connectable to the slave cylinders, with a control device controlled by an actuator controlling the amounts of hydraulic fluid supplied to the slave cylinders, and at least one supply line through which low pressure fluid from a pressure source can be supplied to the device via at least one check valve.
- each slave cylinder is associated with a trained as Geberaktuator displacement piston, which is in communication with a cam arranged on a cam cam.
- the amount of each slave cylinder supplied hydraulic fluid is controlled by a balance piston, the stop is dominated by an actuator.
- This known device requires a high construction cost, since each gas exchange valve or each group of gas exchange valves is assigned its own unit with actuator, etc.
- each gas exchange valve to assign a slave cylinder and master cylinder associated device for the hydraulic control of the gas exchange valves, wherein the control of the respective slave cylinder supplied hydraulic fluid via a Absteue- tion on the master cylinder and / or slave cylinder.
- EP 1 273 770 A2 Also known is a device for the hydraulic control of gas exchange valves, EP 1 273 770 A2, in which also a slave cylinder and a master cylinder are provided, each unit is associated with a pressure accumulator, in which the not provided for the slave cylinder amount of hydraulic fluid stored is when the control device keeps the Abêtung in the pressure accumulator open.
- the construction cost is even greater because the pressure memory and the control device are separated.
- the object of the invention is therefore to provide a device for the hydraulic control of gas exchange valves, which avoids the disadvantages described and reduces the structural complexity.
- the object of the invention is achieved in that the Geberaktuatoren of movable wings, a wing-bearing member and walls have limited cells and the wings are in operative connection with the base and cam profile of the at least one cam.
- This configuration results in a pump unit having a larger number of cells, which are connected to the respective slave cylinders, so that a plurality of gas exchange valves or groups of gas exchange valves can be actuated by means of only one cam and one component.
- the wing-carrying component is designed as a stator which encloses the at least one cam.
- the stator is preferably annular and has the connections for the slave cylinder.
- the wing-carrying component as a central stator and to arrange the cam as an inner cam on a ring or cylinder.
- the cam may be advantageous to provide two or more units each with a cam and a stator side by side, wherein the cams are arranged side by side on a shaft or on a hollow shaft.
- the number and assignment of the cells to the slave cylinders and the number of cams must be adapted to the number of cylinders and firing order of the reciprocating internal combustion engine.
- the wings are loaded in the direction of the cam profile. This can be done for example by means of springs or by means of hydraulic pressure acting on the wings in the direction of the cam profile.
- the build-up of the hydraulic pressure on the vanes can take place by means of compensating spaces in the stator, wherein the equalizing chambers are connected to a connection for hydraulic fluid and are subjected to a corresponding pressure.
- the hydraulic connection of the encoder actuators with the slave cylinders is preferably carried out by means of hydraulic lines which are connected to the cells and by means of check valves to the supply line for the low-pressure liquid.
- the oil pump of the reciprocating internal combustion engine which is required for lubrication anyway, serve as a pressure source, since the low-pressure fluid currently required only to compensate for leaks and is therefore low.
- Leak lines may be connected to these spaces, which are preferably controlled by at least one outflow or overpressure valve in order to provide a certain amount of liquid and / or pressure in the spaces as a counterweight to the cells.
- the control device has outlet openings which are in communication with the cells and whose cross-section is adjustable.
- corresponding outflow windows can be provided in at least one wall of the number of cells.
- the wall is designed to be rotatable according to the proposal, wherein the outflow windows between the cells and the adjacent spaces are pivotable.
- the control device has compensating pistons which are connected to the hydraulic lines and which are spring-loaded and communicate with adjustable end stops.
- the end stops are preferably designed as a stop ram and preferably cup-shaped, so that they can accommodate a part of the spring.
- the stop plunger or the compensating piston have on the mutually facing surfaces annular grooves, which can cause a cushioning of the compensating piston against the stopper plunger.
- the stop ram or the compensating piston has a flange which fits to a shoulder in the second component, so that a central annular groove is formed.
- the stopper rams are supported on rotatably mounted eccentric discs, wherein the eccentric discs can be fastened on an associated common shaft, which is connected to the actuator, which is designed for Drehverstellen.
- the stopper plunger may be in communication with a control ring which has matching control surfaces to the stopper plungers whose depth changes along the circumference.
- the control surfaces move along the stop ram so that the position of the stop ram changes in the radial direction and the compensating pistons can perform a greater or smaller compensation movement.
- the control ring can be mounted directly on the stator.
- control ring has a transmission element, preferably a worm thread, which is in communication with a second transmission element, preferably a worm.
- the second transmission element is connected to the actuator, so that a rotational movement of the second transmission element causes an adjustment of the amount of reaching to the slave cylinders hydraulic fluid.
- At least one cam, a plurality of cells with associated components, a plurality of balance pistons and stop ram and a control ring can be added to a rad- / disc-shaped unit, so that the Geberaktua- factors can be combined with the associated control unit to a space-saving and cost-effective unit to which the hydraulic lines are connected to the slave cylinders.
- wheel / disc-shaped units can also be provided side by side.
- FIG. 1 shows a sketched device for the hydraulic actuation of gas exchange valves, in which the stator carrying the blades and the cam contour are unwound
- 2 shows a section of a stator with two wings and a circumferential extent of the cam profile and the associated lift curve of the gas exchange valve
- FIG. 3 shows an illustration similar to FIG. 2, but in which the cam profile is extended in the circumferential direction, so that a broader elevation curve results
- FIG. 4 shows an exemplary embodiment similar to FIG. 1, in which leak lines are connected to the spaces between the cells;
- FIG. 5 shows an embodiment similar to FIG. 4, in which compensating pistons are provided for changing the flow rate
- FIG. 6 shows an embodiment in which a cell, a slave cylinder with gas exchange valve and a detail of a control device are shown on an enlarged scale
- FIGS. 7 and 8 sections through one encoder actuator unit with outflow windows
- FIG. 10 shows a section through an encoder actuator unit according to FIGS. 7 and 8 with a changed position of the outflow windows;
- Figures 11 u. 12 shows a section through a Geberaktuator - unit according to Figures 7 and 8 with further changed position of the Abströmdon and
- FIG. 13 is a side view of a unit with cams, cells, control device and their individual parts. Detailed description of the drawings
- FIG. 1 gas exchange valves, which are connected to slave cylinders 2 such that they can open the gas exchange valves when pressurized.
- a hydraulic line 3 is connected to each slave cylinder 2 and controlled by a control device 4 shown as a "black box.”
- the hydraulic lines 3 lead after a branch to check valves 5 connected to a supply line 6 for the low-pressure fluid, the supply line being connected to an oil pump 7.
- the hydraulic lines 3 after their branching lead on the other hand to cells 8 which are delimited by a stator 9, vanes 10 and a cam 11.
- the cam 11 is mounted in a position shown in FIG 13.
- the lateral boundary is effected via a wall in each case
- the unit cell, stator, vanes and cam is also referred to as a brake actuator 12.
- a pressure relief valve 19 is connected to the leakage lines 17 and furthermore an accumulator designated 20, so that the leak oil does not flow out of the chambers 14 but is kept at a certain pressure level.
- the control device generally designated 4
- the compensating piston 21 are loaded by means of compression springs 22 which are supported on stop tappets 23.
- the position of the stopper plunger 23 is dominated by eccentric discs 24 which are arranged on a shaft, wherein the position of the shaft and thus of the eccentric discs 24 is fixed by an actuator 25.
- vanes 10 in the stator 9 are in operative connection with equalization spaces 26, which are connected via branch lines to the respective hydraulic lines 3, so that when the pressure builds up in the cells, a pressure increase takes place in the equalization spaces 26, whereby the wings 10 are pressed against the cam profile 13 for better sealing.
- a pressure chamber 27 is connected, which is bounded by the balance piston 21.
- the stop plunger 23 has a flange 28 which engages around a shoulder on the balance piston.
- the flange 28 of the stopper plunger 23 forms with the compensating piston 21 an annular groove 29 which serves to cushion the end of the balancing piston 21 on the stopper plunger 23.
- FIGS. 7 to 12 u. a. a wall of the cells 8 is shown, which is designated 34.
- the number of cells according to outflow window 30 are provided. Since the wall 34 is rotatable, the outflow windows 30 can be adjusted so that they lie entirely in the spaces 14 or entirely in the cells 8.
- outflow windows 30 are located in the area of the spaces 14, a regular pressure build-up in the cells takes place with full delivery of hydraulic fluid as the cam profile moves into the cell. If the outflow windows 30 are partially in the spaces 14 and partly in the cells 8 in such a position, which leads the movement of the cam profile, there is a delayed pressure build-up with reduced delivery volume, as shown in Figures 9 and 10, because volume can escape into the spaces 14, which are of course depressurized or loaded only by low pressure.
- the outflow windows 30 have such a radial height as the cam profile 13, so that when the outflow windows 30 are located in the region of the cells 8, no appreciable pressure build-up takes place in the cells 8 the volume lying radially outside the outflow window 30 is not compressed.
- the stopper rams 23 protrude radially out of the stator 9 and are in operative connection with control surfaces 31, which are arranged on a control ring 32 which is arranged around the stator 9.
- the control ring 32 has a screw thread, which is operatively connected to a designated 33 screw, so that upon rotation of the axially fixed screw of the control ring 32 is rotated about the stator 9 so that the stopper plungers 23 are moved radially over the control surfaces 31 and thereby the quantity control takes place.
- the unit is integrated so far that the check valves 5 are mounted on the stator 9.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2009540684A JP2010513767A (ja) | 2006-12-13 | 2007-11-07 | 往復動ピストン内燃機関のガス交換弁をハイドロリック的に制御するための装置 |
CN2007800462329A CN101627186B (zh) | 2006-12-13 | 2007-11-07 | 用于液压控制往复式内燃机的换气阀的装置 |
US12/518,966 US7987824B2 (en) | 2006-12-13 | 2007-11-07 | Device for the hydraulic control of gas exchange valves of a reciprocating internal combustion engine |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006058691A DE102006058691A1 (de) | 2006-12-13 | 2006-12-13 | Einrichtung zur hydraulischen Ansteuerung von Gaswechselventilen einer Hubkolbenbrennkraftmaschine |
DE102006058691.3 | 2006-12-13 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2008071502A1 true WO2008071502A1 (de) | 2008-06-19 |
Family
ID=39079334
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2007/061957 WO2008071502A1 (de) | 2006-12-13 | 2007-11-07 | Einrichtung zur hydraulischen ansteuerung von gaswechselventilen einer hubkolbenbrennkraftmaschine |
Country Status (5)
Country | Link |
---|---|
US (1) | US7987824B2 (de) |
JP (1) | JP2010513767A (de) |
CN (1) | CN101627186B (de) |
DE (1) | DE102006058691A1 (de) |
WO (1) | WO2008071502A1 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013100632A1 (de) * | 2013-01-22 | 2014-07-24 | Lsp Innovative Automotive Systems Gmbh | Variable elektrohydraulische Ventilsteuerung |
JP6190997B1 (ja) * | 2017-04-07 | 2017-09-06 | 正裕 井尻 | 内燃機関の弁駆動機構 |
US10704431B2 (en) * | 2017-10-03 | 2020-07-07 | Vianney Rabhi | Regenerative valve hydraulic actuator |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1231820A (de) * | 1968-12-18 | 1971-05-12 | ||
US4047859A (en) * | 1976-08-16 | 1977-09-13 | Chandler Evans Inc | Axial vane pump with non-rotating vanes |
DE3109045A1 (de) * | 1981-03-10 | 1982-09-16 | Alfred Teves Gmbh, 6000 Frankfurt | Regelbare hydraulikpumpe |
EP0571472B1 (de) * | 1991-02-20 | 1995-05-03 | ITT Automotive Europe GmbH | Hydraulikanlage |
US20020148421A1 (en) * | 1999-12-09 | 2002-10-17 | Prometheus Engineering B.V. | Hydraulic valve-operating machanism |
WO2005068838A1 (en) * | 2004-01-09 | 2005-07-28 | Pierburg S.P.A. | Pumping system |
EP1485621B1 (de) * | 2002-03-06 | 2005-10-12 | ZF Lenksysteme GmbH | System zur steuerung einer hydraulischen verstellpumpe |
US20060102117A1 (en) * | 2002-07-23 | 2006-05-18 | Vianney Rabhi | Hydraulic valve actuator for reciprocating engine |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE395464C (de) * | 1923-02-21 | 1924-05-13 | Gustav Fries | Vorrichtung zum geraeuschlosen Steuern von Ventilen an Verbrennungsmotoren |
DE2813132A1 (de) * | 1978-03-25 | 1979-09-27 | Kloeckner Humboldt Deutz Ag | Einrichtung zur veraenderung der steuerzeiten von gaswechselventilen einer hubkolbenbrennkraftmaschine |
FI101165B (fi) * | 1994-07-01 | 1998-04-30 | Waertsilae Nsd Oy Ab | Järjestely polttomoottorin venttiilin ajoituksen säätämiseksi |
ITTO20010660A1 (it) * | 2001-07-06 | 2003-01-06 | Fiat Ricerche | Motore diesel pluricilindrico con azionamento variabile delle valvole. |
US6886511B1 (en) * | 2004-04-07 | 2005-05-03 | General Motors Corporation | Lost motion assembly for a poppet valve of an internal combustion engine |
US20070221149A1 (en) * | 2006-03-22 | 2007-09-27 | Victoriano Ruiz | Auxiliary cam phaser hydraulic circuit and method of operation |
-
2006
- 2006-12-13 DE DE102006058691A patent/DE102006058691A1/de not_active Withdrawn
-
2007
- 2007-11-07 CN CN2007800462329A patent/CN101627186B/zh not_active Expired - Fee Related
- 2007-11-07 US US12/518,966 patent/US7987824B2/en not_active Expired - Fee Related
- 2007-11-07 JP JP2009540684A patent/JP2010513767A/ja active Pending
- 2007-11-07 WO PCT/EP2007/061957 patent/WO2008071502A1/de active Application Filing
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1231820A (de) * | 1968-12-18 | 1971-05-12 | ||
US4047859A (en) * | 1976-08-16 | 1977-09-13 | Chandler Evans Inc | Axial vane pump with non-rotating vanes |
DE3109045A1 (de) * | 1981-03-10 | 1982-09-16 | Alfred Teves Gmbh, 6000 Frankfurt | Regelbare hydraulikpumpe |
EP0571472B1 (de) * | 1991-02-20 | 1995-05-03 | ITT Automotive Europe GmbH | Hydraulikanlage |
US20020148421A1 (en) * | 1999-12-09 | 2002-10-17 | Prometheus Engineering B.V. | Hydraulic valve-operating machanism |
EP1485621B1 (de) * | 2002-03-06 | 2005-10-12 | ZF Lenksysteme GmbH | System zur steuerung einer hydraulischen verstellpumpe |
US20060102117A1 (en) * | 2002-07-23 | 2006-05-18 | Vianney Rabhi | Hydraulic valve actuator for reciprocating engine |
WO2005068838A1 (en) * | 2004-01-09 | 2005-07-28 | Pierburg S.P.A. | Pumping system |
Also Published As
Publication number | Publication date |
---|---|
US20100024752A1 (en) | 2010-02-04 |
DE102006058691A1 (de) | 2008-06-19 |
CN101627186A (zh) | 2010-01-13 |
US7987824B2 (en) | 2011-08-02 |
JP2010513767A (ja) | 2010-04-30 |
CN101627186B (zh) | 2012-07-04 |
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