EP2324212A1 - Nockenwellenverstellvorrichtung für eine brennkraftmaschine - Google Patents
Nockenwellenverstellvorrichtung für eine brennkraftmaschineInfo
- Publication number
- EP2324212A1 EP2324212A1 EP09780278A EP09780278A EP2324212A1 EP 2324212 A1 EP2324212 A1 EP 2324212A1 EP 09780278 A EP09780278 A EP 09780278A EP 09780278 A EP09780278 A EP 09780278A EP 2324212 A1 EP2324212 A1 EP 2324212A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure medium
- pressure
- camshaft
- check valve
- opening
- 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
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
- F01L1/34—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
-
- 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
Definitions
- the invention relates to a camshaft adjusting device with a drive wheel and a rotatably arranged relative to this output part, said drive and driven part via at least one pressurizable pressure chamber are in operative connection, and provided to regulate the pressure medium supply to the pressure chamber and the pressure fluid discharge from the pressure chamber at least one regulator is, is formed for the pressure medium supply at least one pressure medium inlet connection between the regulating device and a pressure medium supply means.
- Such a camshaft adjusting device is known from DE 101 03 876 A1 / US Pat. No. 6,553,951 B2 and US 2006/0213471 A1.
- a housing component drivable by the engine of an internal combustion engine and a rotor component rotatably connected to a camshaft of the engine are arranged so as to be rotatable relative to one another.
- these are in operative connection via a plurality of pressure chambers, each of which is connected in a rotationally fixed manner to the rotor component by two pressure chambers which can be acted upon by pressure medium and act against each other.
- the pressure medium is applied to the pressure chambers via a pressure medium connection between the pressure chambers and a pressure medium pump, which promotes pressure medium from a pressure medium reservoir.
- the pressure medium supply to the pressure chambers and the pressure medium discharge from the pressure chambers is regulated via a control valve arranged in the pressure medium connection.
- the control valve is connected via a pressure medium supply line to the pressure medium pump and the pressure medium reservoir.
- an overpressure may occur in the pressure chambers to be filled. If the overpressure exceeds the pressure medium admission pressure prevailing in the pressure medium inlet connection, the overpressure can continue via the pressure medium connection to the control valve and via the internal connections in the control valve into the pressure medium supply line between control valve and pressure medium pump or pressure medium reservoir.
- a check valve is arranged in the pressure medium supply line.
- a check valve which is connected in parallel to a check valve in a bypass is provided in the pressure medium inlet connection and is opened or closed as a function of the temperature of the pressure medium.
- the check valve is opened.
- the pressure medium flows through the open shut-off valve via the bypass with lower flow resistance. If the pressure medium temperature is greater than a predetermined threshold value at which the pressure medium viscosity is small, the Lock valve closed, whereby the bypass is locked and the pressure medium is passed through the check valve.
- the invention is therefore based on the object to provide a Nockenwellenverstellvor- direction of the aforementioned type which avoids the aforementioned disadvantages.
- the object is solved by the features of claim 1.
- opening of a check valve or both depending on the pressure medium prevailing in the pressure medium inlet connection in the direction of passage in front of the non-return valve can be effected in advance (differential pressure)
- Non-return valves the pressure medium supply via a check valve with a small
- the first and second check valves have different opening pressures, wherein the opening pressure is to be understood in each case as the pressure difference between the pressure medium pressure before and after the check valve in the pressure medium inlet connection (differential pressure) required for opening the check valve.
- the first check valve is designed with a low opening pressure and the second check valve with a higher opening pressure, the pressure medium flow is passed through the low opening pressure having a first check valve, while the higher opening pressure having second check valve remains closed at a pressure medium loading in a low pressure medium pre-operating condition. Because the first Opens check valve at low differential pressure, a fast opening of the same is achieved at low pressure medium admission pressure and a high pressure medium flow with high adjustment speed with a small flow resistance.
- the first check valve has a small passage cross-section.
- the passage cross-section for optimization can be reduced in such a way that, in the operating state with low pressure medium admission pressure, throttling of the pressure medium supply by the first check valve which impairs the adjustment speed is barely avoided.
- the blocking body of the first check valve is executable with the lowest possible passage cross-section with the lowest possible mass and lowest possible inertia, whereby particularly short reaction times of the first check valve during opening and locking of the pressure medium inlet connection can be achieved.
- the opening pressure of the second check valve can be adjusted such that when the pressure medium admission pressure in the pressure medium inlet connection rises, an opening is produced by opening the second check valve the adjustment speed is barely avoided by a throttle effect of the first check valve.
- An optimal setting is achieved when the opening pressure of the second check valve corresponds to the pressure medium pressure (differential pressure) in the pressure medium inlet connection, in which a swinging back of the wings in the pressure chambers is reduced so far that the first check valve is permanently open.
- too early opening of the second check valve at low pressure medium admission pressure with the consequence of slower reaction times when opening and blocking the Druckschzulauf für is prevented and on the other hand, a timely opening of the second check valve to avoid throttle effect in individual operation guaranteed.
- an optimized pressure medium flow in parallel operation can be achieved at high pressure medium pre-pressure for rapid adjustment. In this way, for example, in high-speed operation in hot or cold condition of the engine optimum adjustment dynamics possible.
- FIG. 1 shows a perspective partial side view of the camshaft adjusting device
- FIG. 2 shows a simplified schematic representation of the structure of the pressure medium system of the camshaft adjusting device.
- FIG. 1 shows a perspective view of a hydraulic camshaft adjusting device 1 without a front cover from the side 1 a facing away from the engine.
- the camshaft adjusting device 1 has a driving wheel 2 mounted rotatably on a driven part 3 for this purpose.
- the drive wheel can be driven via an engagement point 2a, an exemplarily illustrated, non-rotatably connected to the drive wheel 2 sprocket, on whose teeth can attack a driven by a crankshaft, not shown, chain. It is also conceivable that the drive wheel 2 is driven by a belt or wheel drive.
- the driven part 3 is designed as an impeller and rotatably connected via a central receptacle 3a with a camshaft, not shown, for example by means of a screw or welded connection.
- a central receptacle 3a with a camshaft, not shown, for example by means of a screw or welded connection.
- the driven part 3 has radial recesses forming, axially extending vane grooves 3c, in which the vanes 10 are arranged rotatably connected to the driven part 3.
- a side cover (not shown) is arranged on each of the side surfaces of the drive wheel 2 and rotationally fixed via five fastening screws 11 fixed thereto.
- the drive wheel 2 five symmetrically arranged pressure chambers 4 are provided in the circumferential direction.
- the pressure chambers are bounded in each case at two substantially radially extending, opposite boundary walls 2b, 2c adjacent projections 2d of the drive wheel 2 in the circumferential direction.
- the pressure chambers 4 are each bounded radially outwardly by a peripheral wall 2e of the drive wheel 2 and radially inward by the outer circumference 3b of the driven part 3.
- each of the pressure chambers 4 projects one of the wings 10, wherein the wings 10 are formed such that they both abut against the peripheral wall 2e as well as on the boundary walls 2b, 2c of the projections 2d can be applied.
- Each of the vanes 10 divides the respective pressure chamber 4 into two counteracting pressure chambers 4a, 4b.
- the drive wheel 2 is arranged rotatable in a defined angular range to the output part 3.
- the angular range is limited in a direction of rotation in that the wings 10 come to rest on a formed on the boundary wall 2 b of the pressure chamber 4 late stop 12.
- the angle range in the other direction of rotation is limited by the fact that the wings 10 come to rest on the formed on the opposite boundary wall 2c of the pressure chamber early stop 13.
- the camshaft adjusting device 1 shows the camshaft adjusting device 1 in the maximum retarded position, in which the wings 10 are placed on the late stop 12.
- the two adjacent to the axial bore 3d arranged wings 10 are released when reaching the maximum early or late position and beat on the respective boundary walls 2b , 2c not on.
- a pressure medium system For the supply of pressure medium to or pressure medium removal from the pressure chambers 4a, 4b, a pressure medium system is provided which comprises a pressure medium pump 14, a tank 15, a control valve designed as a hydraulic control device 5 and the pressure medium connections 16, 17.
- hydraulic pressure medium usually the lubricating oil of the internal combustion engine is used.
- a locking unit 18 Abthebsteil 3 and drive wheel 2 are mechanically coupled.
- the locking unit 18 has an axially displaceable in an axial bore 3d in the driven part 3 arranged locking bolt 18a, which can engage in the locked state on the driven part 3 facing the inside of the side cover, not shown in a complementarily shaped recess.
- Figure 2 shows in a hydraulic diagram very schematically and by way of example the structure of the pressure medium system of the camshaft adjusting device 1.
- the pressure medium supply and the pressure medium discharge to and from the groups of the pressure chambers 4a, 4b takes place via separate pressure medium connections 16, 17 between these and the control valve designed as a control device 5. It is provided that the control valve, the pressure medium flows to and from the first and second Pressure chambers 4a, 4b regulated.
- Two ports A, B connect the control valve to the pressure chambers 4a, 4b.
- a first working port A communicates with the pressure medium connection 16, via which the group of the first pressure chamber 4a is supplied with pressure medium.
- the second working port B communicates with the pressure medium connection 17, via which the group of the second pressure chambers 4b is supplied with pressure medium.
- the control valve is connected to a pressure medium supply device 7 via an inlet connection P.
- a pressure medium inlet connection 6 is provided, which connects the control valve with the pressure medium supply device 7.
- the pressure medium supply device 7 consists of a pressure medium pump 14, the camshaft adjuster 1 perma- Nent a pressure medium flow is available, and designed as a tank 15 pressure fluid reservoir. Via a discharge port T, which communicates directly with a pressure medium drain connection 19, the pressure medium can flow into the tank 15.
- the ports P and T may be connected to the engine oil circuit of the engine, for example, the cylinder head gallery, the oil pressure of which depends on engine speed and oil temperature.
- the port P then allows the supply of pressure medium in the camshaft adjusting device 1 from the oil circuit of the engine, while via the port T, the displaced in the camshaft adjusting device 1 oil can flow back into the oil circuit of the engine.
- the control valve which may be designed as a plug-in valve or as a central valve, consists of an electric actuator 5a and a hydraulic section 5b.
- the hydraulic section 5b has a valve housing 5c and an axially displaceable control piston 5d.
- the control piston 5d in the valve housing 5c can be displaced axially.
- the force acting in the opposite direction spring force of a valve spring 5e allows a provision of the control piston 5d.
- the working ports A, B can be selectively connected to the inlet connection P, the outlet connection T or neither.
- the internal connections of the connections of the control valve are shown symbolically for three switching positions 5f, 5g, 5h.
- the vibration angle in the direction of late is smaller than in the direction of early.
- the wings 10 are moved in periodic swinging movements in the direction of the early stop 13, whereby a rotary movement of the driven part 3 is achieved relative to the drive wheel 2 in the early direction.
- an adjustment in the direction of later control times in the trailing position 5h is achieved.
- the second working port B is connected to the inlet port P and the first working port A to the drain port T.
- the adjustment in the direction of the spring takes place counter to the forces acting on the camshaft friction moments, while assisting in an adjustment in the late direction the forces acting on the camshaft friction moments support the adjustment.
- the pressure medium supply to all pressure chambers 4a, 4b is suppressed (switching position 5g).
- the wings 10 are hydraulically clamped within the respective pressure chambers 4 and prevents a rotational movement of the driven part 3 relative to the drive wheel 2.
- the pressure-medium inlet connection 6 is in pressure medium connection via the inlet connection P and via the working connection A of the control valve to the group of the first pressure chambers 4a.
- Analog are in the Nacheil thoroughly 5h the Druckmittezulauf für 6 and the group of second pressure chambers 4b connected to each other via the inlet port P and the working port B of the control valve.
- a first check valve 8 and a second check valve 9 connected in parallel thereto are arranged, via which the pressure medium inlet connection 6 can be blocked in the direction of the pressure medium supply device 7.
- the non-return valves 8, 9 in the forward direction at a pressure medium beaufschlung the passage of the pressure medium only when the respective opening pressure, ie. allow the opening respectively required differential pressure in front of and behind the check valve 8, 9, during a adjustment both in the advanced position and in the Nacheilwolf of the control valve in the pressure medium supply connection 6 pressure medium lent only in the direction of the group of the first pressure chambers 4a and flow in the direction of the group of second pressure chambers 4b. If the respective differential pressure required for opening is not reached, the check valves 8, 9 close automatically and block the passage of the pressure medium in the direction of the pressure medium supply device 7 directly in the pressure medium inlet connection 6. As a result, a return flow of the pressure medium from the pressure medium inlet connection 6 in FIG the pressure medium supply means 7 securely prevented.
- the first check valve 8 is designed with a blocking body 8b low mass and low inertia, whereby particularly short reaction times for opening and locking the pressure medium inlet connection 6 are achieved.
- the opening pressure of the second check valve 9 is set according to a pressure medium upstream pressure (differential pressure) in the pressure medium inlet connection 6, in which the first check valve 8 is permanently open when the engine speed increases. A generated by the swinging back of the wings 10 in the pressure chambers 4 overpressure in the pressure medium inlet connection 6 acts then not more.
- the second check valve 9 opens at a prevailing in the pressure medium inlet connection 6 pressure medium upstream pressure (differential pressure), in which a Verstell Ausing throttling of the pressure medium supply through the small passage cross section at the first check valve 8 is reliably prevented. In this way, an optimally high pressure medium flow is ensured in the pressure medium inlet connection 6 with an optimal adjustment dynamics with increasing engine speed in parallel operation with both open check valves 8, 9.
- the second check valve 9 opens in a warm state of the engine, for example, at a pressure medium temperature of about 140 0 C at an engine speed of about 1700 U / min.
- the first and the second check valve 8, 9 are each carried out with a by the spring force of a valve spring 8a, 9a in the reverse direction loaded locking body 8b, 9b hermetically seals the pressure medium inlet connection in the locked direction to the pressure medium supply means 7.
- the valve spring 8a of the first check valve 8 has a low spring force. This opens at low opening pressure.
- the valve spring 9a of the second check valve 9 is formed with a larger spring force, whereby a larger differential pressure for opening the same in the pressure medium inlet connection 6 is required.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008036876A DE102008036876A1 (de) | 2008-08-07 | 2008-08-07 | Nockenwellenverstellvorrichtung für eine Brennkraftmaschine |
PCT/EP2009/058626 WO2010015474A1 (de) | 2008-08-07 | 2009-07-07 | Nockenwellenverstellvorrichtung für eine brennkraftmaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2324212A1 true EP2324212A1 (de) | 2011-05-25 |
EP2324212B1 EP2324212B1 (de) | 2012-01-04 |
Family
ID=41082595
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP09780278A Not-in-force EP2324212B1 (de) | 2008-08-07 | 2009-07-07 | Nockenwellenverstellvorrichtung für eine brennkraftmaschine |
Country Status (6)
Country | Link |
---|---|
US (1) | US8590498B2 (de) |
EP (1) | EP2324212B1 (de) |
CN (1) | CN102119263B (de) |
AT (1) | ATE540198T1 (de) |
DE (1) | DE102008036876A1 (de) |
WO (1) | WO2010015474A1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP5447543B2 (ja) | 2012-01-26 | 2014-03-19 | 株式会社デンソー | バルブタイミング調整装置、およびその組付方法 |
DE102014102617A1 (de) * | 2014-02-27 | 2015-08-27 | Hilite Germany Gmbh | Hydraulikventil für einen Schwenkmotorversteller einer Nockenwelle |
Family Cites Families (22)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4210580C2 (de) * | 1992-03-31 | 2001-06-28 | Bosch Gmbh Robert | Vorrichtung zur Winkelverstellung der Nockenwelle einer Brennkraftmaschine |
US5615648A (en) | 1992-07-25 | 1997-04-01 | Robert Bosch Gmbh | Electro-hydraulic adjusting device |
DE19511522C1 (de) * | 1995-03-29 | 1996-07-18 | Fluidtech Gmbh | Rastschaltvorrichtung |
JPH1113430A (ja) * | 1997-06-24 | 1999-01-19 | Toyota Motor Corp | 内燃機関のバルブタイミング制御装置 |
DE19756016A1 (de) * | 1997-12-17 | 1999-06-24 | Porsche Ag | Vorrichtung zur hydraulischen Drehwinkelverstellung einer Welle zu einem Antriebsrad |
DE10103876B4 (de) | 2000-01-31 | 2005-12-01 | Aisin Seiki K.K., Kariya | Ventilsteuerzeitverstellvorrichtung für Verbrennungsmotoren |
US6453859B1 (en) * | 2001-01-08 | 2002-09-24 | Borgwarner Inc. | Multi-mode control system for variable camshaft timing devices |
US6779501B2 (en) | 2002-06-14 | 2004-08-24 | Borgwarner Inc. | Method to reduce rotational oscillation of a vane style phaser with a center mounted spool valve |
US7137371B2 (en) * | 2003-02-07 | 2006-11-21 | Borgwarner Inc. | Phaser with a single recirculation check valve and inlet valve |
DE102004035035B4 (de) * | 2003-07-24 | 2022-04-14 | Daimler Ag | Nockenwellenversteller für Brennkraftmaschinen |
JP4175987B2 (ja) * | 2003-09-30 | 2008-11-05 | 株式会社日本自動車部品総合研究所 | バルブタイミング調整装置 |
US6997150B2 (en) * | 2003-11-17 | 2006-02-14 | Borgwarner Inc. | CTA phaser with proportional oil pressure for actuation at engine condition with low cam torsionals |
JP4202297B2 (ja) | 2004-05-20 | 2008-12-24 | 株式会社日立製作所 | 内燃機関のバルブタイミング制御装置 |
JP4534147B2 (ja) | 2005-03-22 | 2010-09-01 | アイシン精機株式会社 | オイル供給装置 |
JP2007138725A (ja) | 2005-11-15 | 2007-06-07 | Denso Corp | バルブタイミング調整装置 |
WO2007125842A1 (ja) * | 2006-04-26 | 2007-11-08 | Denso Corporation | ベーン式の可変バルブタイミング調整機構の制御装置 |
US7434554B2 (en) * | 2006-05-19 | 2008-10-14 | Denso Corporation | Controller for vane-type variable valve timing adjusting mechanism |
JP2008069651A (ja) * | 2006-09-12 | 2008-03-27 | Denso Corp | バルブタイミング調整装置 |
JP4545127B2 (ja) * | 2006-09-15 | 2010-09-15 | 株式会社デンソー | バルブタイミング調整装置 |
GB2448737B (en) * | 2007-04-26 | 2011-08-10 | Ford Global Tech Llc | A variable camshaft timing (VCT) system |
DE102007056683A1 (de) * | 2007-11-24 | 2009-05-28 | Schaeffler Kg | Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine |
DE102007056685A1 (de) * | 2007-11-24 | 2009-05-28 | Schaeffler Kg | Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine |
-
2008
- 2008-08-07 DE DE102008036876A patent/DE102008036876A1/de not_active Withdrawn
-
2009
- 2009-07-07 US US13/057,636 patent/US8590498B2/en not_active Expired - Fee Related
- 2009-07-07 CN CN200980131050.0A patent/CN102119263B/zh not_active Expired - Fee Related
- 2009-07-07 WO PCT/EP2009/058626 patent/WO2010015474A1/de active Application Filing
- 2009-07-07 AT AT09780278T patent/ATE540198T1/de active
- 2009-07-07 EP EP09780278A patent/EP2324212B1/de not_active Not-in-force
Non-Patent Citations (1)
Title |
---|
See references of WO2010015474A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN102119263A (zh) | 2011-07-06 |
EP2324212B1 (de) | 2012-01-04 |
WO2010015474A1 (de) | 2010-02-11 |
US20110168113A1 (en) | 2011-07-14 |
US8590498B2 (en) | 2013-11-26 |
DE102008036876A1 (de) | 2010-04-15 |
ATE540198T1 (de) | 2012-01-15 |
CN102119263B (zh) | 2014-03-05 |
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