WO1998042961A1 - Ventilantrieb für gaswechselventile von brennkraftmaschinen - Google Patents
Ventilantrieb für gaswechselventile von brennkraftmaschinen Download PDFInfo
- Publication number
- WO1998042961A1 WO1998042961A1 PCT/EP1998/001531 EP9801531W WO9842961A1 WO 1998042961 A1 WO1998042961 A1 WO 1998042961A1 EP 9801531 W EP9801531 W EP 9801531W WO 9842961 A1 WO9842961 A1 WO 9842961A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- tappet
- valve
- gas exchange
- drive according
- valve drive
- 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
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/12—Transmitting gear between valve drive and valve
- F01L1/14—Tappets; Push rods
- F01L1/143—Tappets; Push rods for use with overhead camshafts
-
- 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
- F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L13/0036—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque the valves being driven by two or more cams with different shape, size or timing or a single cam profiled in axial and radial direction
-
- 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
- F01L13/0015—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque
- F01L2013/0089—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque with means for delaying valve closing
- F01L2013/0094—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations for optimising engine performances by modifying valve lift according to various working parameters, e.g. rotational speed, load, torque with means for delaying valve closing with switchable clamp for keeping valve open
Definitions
- Vfinf -i 1 antri eb for ffa ⁇ wech ⁇ el v n le by Brp ⁇ n ra f t-.ms sr i npn
- the invention relates to a valve drive for gas exchange valves of internal combustion engines with the features according to the preamble of claim 1.
- the generic valve drives are used on the one hand to switch off individual or several valves or on the other hand to switch from one stroke characteristic to another in the same valve.
- Valves of individual cylinders are switched off in gasoline engines in order to avoid the gas exchange losses on the switched-off cylinders — and to work with a higher medium pressure in the remaining fired cylinders, which increases the thermal efficiency. Consumption and exhaust gas in the partial load range are reduced accordingly.
- the charge change causes significantly lower losses.
- the intake swirl in the combustion chamber can be influenced as a function of the speed and thus the combustion can be improved.
- valve's stroke characteristics can be changed in several ways by the valve switchover, both with regard to the opening stroke and with regard to the control times. With two different stroke characteristics, the control times for two speed ranges can be optimized. be lubricated, which results in consumption and exhaust gas advantages.
- valve actuators for gas exchange valves which have a device for switching off or switching over a gas exchange valve, e.g. DE 42 13 147 AI, DE 43 33 927 AI, DE 44 05 189 C2 and DE 44 43 101 AI. There are basically two different systems.
- a first, DE 44 43 101 AI, has a pressure medium chamber within a tappet, which is filled or emptied with oil in order to switch the gas exchange valve on or off.
- a high oil pressure is required to transmit the actuation forces, which makes simple sealing difficult and requires a complex pressure medium supply. Both the seal than the Pressure also k food supplies take up much space.
- the gas exchange valves are switched by form-fit, switchable coupling elements, e.g. Pins, bolts or washers, switched on or off, which are arranged between a tappet and the gas exchange valve.
- the arrangement and actuation of the form-fit coupling elements also take up considerable space.
- an impermissibly high surface pressure and associated wear can occur in the coupling point if a complete positive fit is not achieved when engaging. Annoying coupling noise can also occur.
- the object of the invention is to reduce the construction costs of generic valve actuators and to improve their efficiency with a small construction volume. It is solved according to the invention by the features of claim 1.
- a switchable clamping device is provided as the coupling element, no hydraulic pressure needs to be built up to transmit the actuating forces from the cam to the gas exchange valve.
- the forces for switching the clamping device device are small and can be applied electrically or by a low oil pressure that is easy to seal and can be generated by a lubricating oil pump.
- the clamping device works silently and continuously. It is able to automatically compensate for manufacturing tolerances, wear and play due to different operating temperatures. If gas exchange valves are only to be switched on and off, an additional device to compensate for valve clearance can be dispensed with.
- a simple, space-saving clamping device is achieved with a clamping ring which, with its conical surface, interacts with a corresponding counter surface on the tappet.
- the conical surfaces can also be on the side towards the inner plunger or on both sides, but it is usually sufficient if the clamping ring has a conical surface on only one side.
- the cone angle is dimensioned so small that self-locking occurs in an S position of the clamping ring that transmits the actuating force.
- large actuation forces can be transmitted to the gas exchange valve in a force-locking manner without the need to apply energy for additional holding forces.
- the clamping ring is only held by one or more compression springs in a position in which the conical surfaces touch slightly, so that the frictional forces required for self-locking take effect.
- the clamping ring is expediently divided in the axial direction in a sector-like manner.
- Oil pressure is applied to the clamp ring to release the clamp connection.
- the lubricating oil pressure of the internal combustion engine is expediently used. This is sufficient since only a small pressure is required to loosen as long as the cam does not actuate the tappet. Does it work Cam on the tappet after the clamp connection is released, this is moved against the force of a first compression spring in the direction of the gas exchange valve without the gas exchange valve opens.
- the clamping body having a second conical surface which forms an obtuse angle with the first and is brought into effect by the oil pressure against the force of the second compression spring.
- the cone angle is chosen so large that no self-locking occurs.
- the second clamp connection keeps the tappet in a bottom dead center position as long as the oil pressure is active. Friction losses between the bucket tappet and the cam and the cylinder head are thus avoided.
- the second compression spring can overcome the clamping effect, which is supported by the first compression spring, and release the clamping connection.
- the first compression spring presses the bucket tappet against the base circle of the camshaft. This compensates for any valve play that may be present.
- An additional device for compensating the valve clearance is not necessary.
- a limited residual pressure is expediently maintained via a throttle valve and a pressure-maintaining valve in order to improve the response behavior of the switch-off or switching device.
- the spring chambers are connected to an unpressurized space in the cylinder head.
- FIG. 1 is a partial cross section through a valve drive with a schematic representation of a pressure supply
- FIG. 3 shows a detail III in FIG. 1,
- Fig. 4 shows a detail corresponding to Fig. 3, but in a different switching position
- Fig. 5 shows a valve drive with a valve switch.
- a camshaft 1 rotates in the direction of the arrow and describes a dashed circle with its cam 2.
- the distance between the dashed circle and the base circle of the camshaft 1 corresponds to the stroke of the cam 2, which actuates a tappet 6 guided in a cylinder head 5 and shifts it to a bottom dead center position.
- a first compression spring 14 presses the bucket tappet 6 against the camshaft 1 or the cam 2. It is supported on an inner tappet 7 which is guided in the bucket tappet 6 and bears against a valve stem 8 of a gas exchange valve.
- This has a valve plate 9 with a valve seat 11, which is held by a valve spring 12 sealingly against a valve seat ring 10 and thus closes a gas exchange duct 13 to a combustion chamber, not shown, of an internal combustion engine.
- the clamping ring 15 has a first conical surface 17 which, due to the force F C2 of a second compression spring 16, bears against a first conical counter surface 18 in the tappet 6.
- the second compression spring 16 can consist of several individual springs.
- the first conical surface 17 or the first conical counter surface 18 has a cone angle ⁇ ⁇ ; which is dimensioned so that self-locking occurs through friction. It must therefore be ⁇ 2 smaller than the arc tangent of the minimal, to be expected friction coefficient ⁇ min between the tappet 6 and the clamping ring 15.
- a force is generated by the force F N of the cam 2 and the force F v of the valve spring 12 via the normal forces N x and N 2 without additional holding forces having to be applied.
- the forces F C1 of the first compression spring 14 are negligibly small.
- the frictional forces R x and R 2 act in the direction of the contact surfaces between the cup tappet 6 or the inner tappet 7 on the one hand 'and the clamping ring 15 on the other hand.
- the clamp connection can be released with a relatively low pressure P, which is applied by a pressure oil pump 25, for example a lubricating oil pump of the internal combustion engine, via a solenoid valve 24 and a pressure channel 23.
- a pressure oil pump 25 for example a lubricating oil pump of the internal combustion engine
- the clamping ring 15 has a second conical surface 19 which interacts with a second conical counter surface 20.
- the cone angle ⁇ 2 is designed so that it under which oil pressure produces a sufficient clamping connection to hold the tappet 6 against the force F C1 of the first compression spring 14 in the bottom dead center position. There is no self-locking, so that the clamp connection is automatically released under the influence of the second compression spring 16 as soon as the oil pressure P has dropped accordingly.
- a pressure control valve 26 in conjunction with a throttle 31 ensures that there is always a certain upstream pressure in the pressure chamber 22 and in the pressure channel 23, as a result of which the response behavior of the clamping device is improved.
- the clamping ring 15 is divided into four sectors in the axial direction. A simple assembly and a good contact of the conical surfaces 17 and 19 on the corresponding counter surfaces 18 and 20 is thereby achieved.
- the oil control f lu ß by gaps 21, which are formed by the sectors of the clamping ring 15 is kept small, it is expedient to seal the gaps 21 on the pressure side or on the side of the second compression spring 16 with a cylindrical sealing ring 30 or elastic.
- the seal on the compression spring side has the advantage that the pressure oil reliably releases the first clamping connection by penetrating between the first conical surface 17 and the corresponding first counter surface 18.
- ventilation openings in the form of a ventilation groove 28 and a ventilation bore 29 are provided.
- the inner tappet 7 is guided through the bottom of the tappet 6 and is actuated by a central cam 3. Flanking cams 4, which have a different stroke characteristic than the central cam 3, actuate the cup tappet 6.
- the cup tappet 6 can be coupled to the inner tappet 7 via the clamping ring 15. In the coupled state, the stroke characteristic of the flanking cams 4 acts on the valve. valve stem 8 of the gas exchange valve. If the first clamp connection is released by the oil pressure P and the tappet 6 is held in its bottom dead center position by the second clamp connection, only the stroke characteristic of the middle cam 3 acts on the gas exchange valve. In this way, optimal control times for the gas exchange valve can be achieved for two speed ranges.
- valve clearance between the flanking cams 4 and the valve stem 8 is compensated for by the clamping ring 15.
- a special device 27 for compensating for a valve clearance is expediently provided.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Claims
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP10544837A JP2000510546A (ja) | 1997-03-26 | 1998-03-17 | 内燃機関のガス交換弁用弁駆動装置 |
EP98916971A EP0970300A1 (de) | 1997-03-26 | 1998-03-17 | Ventilantrieb für gaswechselventile von brennkraftmaschinen |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19712668.5 | 1997-03-26 | ||
DE19712668A DE19712668C1 (de) | 1997-03-26 | 1997-03-26 | Ventilantrieb für Gaswechselventile von Brennkraftmaschinen |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1998042961A1 true WO1998042961A1 (de) | 1998-10-01 |
Family
ID=7824665
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1998/001531 WO1998042961A1 (de) | 1997-03-26 | 1998-03-17 | Ventilantrieb für gaswechselventile von brennkraftmaschinen |
Country Status (5)
Country | Link |
---|---|
US (1) | US6293239B1 (de) |
EP (1) | EP0970300A1 (de) |
JP (1) | JP2000510546A (de) |
DE (1) | DE19712668C1 (de) |
WO (1) | WO1998042961A1 (de) |
Families Citing this family (19)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19837098A1 (de) * | 1998-08-17 | 2000-02-24 | Porsche Ag | Verfahren zum Betrieb einer mehrzylindrigen Brennkraftmaschine und Ventiltrieb einer mehrzylindrigen Brennkraftmaschine |
DE19903455B4 (de) * | 1999-01-28 | 2008-06-05 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Schaltbarer Tassenstößel, insbesondere für Gaswechselventile |
DE19919245B4 (de) * | 1999-04-28 | 2015-05-13 | Schaeffler Technologies AG & Co. KG | Ventiltrieb einer Brennkraftmaschine |
WO2001090538A1 (fr) * | 2000-05-23 | 2001-11-29 | Mitsubishi Denki Kabushiki Kaisha | Dispositif d'ajustement de levee de soupape |
JP3814462B2 (ja) * | 2000-05-30 | 2006-08-30 | 株式会社日立製作所 | 内燃機関のバルブリフタ |
AT4872U1 (de) * | 2000-11-20 | 2001-12-27 | Avl List Gmbh | Variabler ventiltrieb für ein nockenbetätigtes hubventil einer brennkraftmaschine |
JP2002317613A (ja) | 2001-04-20 | 2002-10-31 | Mitsubishi Electric Corp | バルブリフト調整装置 |
DE10140952A1 (de) * | 2001-08-21 | 2003-03-20 | Bosch Gmbh Robert | Ventilmechanismus mit einem variablen Ventilöffnungsquerschnitt |
US6477997B1 (en) * | 2002-01-14 | 2002-11-12 | Ricardo, Inc. | Apparatus for controlling the operation of a valve in an internal combustion engine |
EP1380728B1 (de) * | 2002-07-12 | 2005-04-06 | AVL List GmbH | Ventiltriebseinrichtung |
DE102004039705A1 (de) * | 2004-08-17 | 2006-03-23 | Ina-Schaeffler Kg | Schaltbarer Stößel |
DE102006018588A1 (de) * | 2006-04-21 | 2007-10-25 | Schaeffler Kg | Ventilbetätigungseinrichtung, insbesondere für Gaswechselventile von Hubkolbenbrennkraftmaschinen |
DE102007014248A1 (de) * | 2007-03-24 | 2008-09-25 | Schaeffler Kg | Hubkolbenbrennkraftmaschine mit Motorbremseinrichtung |
DE102007014250A1 (de) * | 2007-03-24 | 2008-09-25 | Schaeffler Kg | Brennkraftmaschine mit Motorbremse |
JP6030058B2 (ja) | 2010-07-27 | 2016-11-24 | ジェイコブス ビークル システムズ、インコーポレイテッド | エンジン・ブレーキと正出力エンジン併用の空動きバルブ作動システム |
US9790824B2 (en) | 2010-07-27 | 2017-10-17 | Jacobs Vehicle Systems, Inc. | Lost motion valve actuation systems with locking elements including wedge locking elements |
EP2975230B1 (de) * | 2014-07-15 | 2018-02-21 | Jacobs Vehicle Systems, Inc. | Leerlaufventilbetätigungssysteme mit sicherungselementen einschliesslich keilsicherungselementen |
DE102018125978A1 (de) * | 2018-10-19 | 2020-04-23 | Schaeffler Technologies AG & Co. KG | Variabler Ventiltrieb eines Verbrennungskolbenmotors |
CN109854326A (zh) * | 2019-03-27 | 2019-06-07 | 大连理工大学 | 一种高效移动式制动支点 |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4213147A1 (de) | 1991-05-03 | 1992-11-05 | Volkswagen Ag | Variabler ventiltrieb fuer ein hubventil mit zwei durch unterschiedliche nocken betaetigbaren stoesseln |
DE9403422U1 (de) * | 1994-03-01 | 1994-04-28 | INA Wälzlager Schaeffler KG, 91074 Herzogenaurach | Schaltbarer Ventiltriebstößel |
DE9403420U1 (de) * | 1994-03-01 | 1994-04-28 | INA Wälzlager Schaeffler KG, 91074 Herzogenaurach | Abschaltbarer Ventiltriebstößel |
DE4333927A1 (de) | 1993-10-05 | 1995-04-06 | Schaeffler Waelzlager Kg | Schaltstößel |
DE4443101A1 (de) | 1994-12-03 | 1996-06-05 | Schaeffler Waelzlager Kg | Schaltstößel |
DE4405189C2 (de) | 1994-02-18 | 1996-07-11 | Porsche Ag | Stößel für ein abschaltbares Ventil einer Brennkraftmaschine |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4711207A (en) * | 1987-04-07 | 1987-12-08 | General Motors Corporation | Valve deactivator mechanism |
WO1993022543A1 (de) * | 1992-04-27 | 1993-11-11 | Iav - Motor Gmbh | Ventiltrieb für ladungswechselventile, vorzugsweise einlassventile von hubkolbenbrennkraftmaschinen |
US5694894A (en) * | 1993-03-25 | 1997-12-09 | Lotus Cars Limited | Valve control means |
DE4314619A1 (de) * | 1993-05-04 | 1994-11-10 | Schaeffler Waelzlager Kg | Stößel |
DE4404145A1 (de) * | 1994-02-09 | 1995-08-10 | Schaeffler Waelzlager Kg | Schalteinrichtung in einem Ventiltrieb |
US6076491A (en) * | 1994-05-03 | 2000-06-20 | Lotus Cars Limited | Valve control mechanism |
US5709180A (en) * | 1997-02-06 | 1998-01-20 | General Motors Corporation | Narrow cam two-step lifter |
-
1997
- 1997-03-26 DE DE19712668A patent/DE19712668C1/de not_active Expired - Fee Related
-
1998
- 1998-03-17 WO PCT/EP1998/001531 patent/WO1998042961A1/de not_active Application Discontinuation
- 1998-03-17 JP JP10544837A patent/JP2000510546A/ja active Pending
- 1998-03-17 EP EP98916971A patent/EP0970300A1/de not_active Withdrawn
-
1999
- 1999-12-13 US US09/402,004 patent/US6293239B1/en not_active Expired - Fee Related
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4213147A1 (de) | 1991-05-03 | 1992-11-05 | Volkswagen Ag | Variabler ventiltrieb fuer ein hubventil mit zwei durch unterschiedliche nocken betaetigbaren stoesseln |
DE4333927A1 (de) | 1993-10-05 | 1995-04-06 | Schaeffler Waelzlager Kg | Schaltstößel |
DE4405189C2 (de) | 1994-02-18 | 1996-07-11 | Porsche Ag | Stößel für ein abschaltbares Ventil einer Brennkraftmaschine |
DE9403422U1 (de) * | 1994-03-01 | 1994-04-28 | INA Wälzlager Schaeffler KG, 91074 Herzogenaurach | Schaltbarer Ventiltriebstößel |
DE9403420U1 (de) * | 1994-03-01 | 1994-04-28 | INA Wälzlager Schaeffler KG, 91074 Herzogenaurach | Abschaltbarer Ventiltriebstößel |
DE4443101A1 (de) | 1994-12-03 | 1996-06-05 | Schaeffler Waelzlager Kg | Schaltstößel |
Also Published As
Publication number | Publication date |
---|---|
DE19712668C1 (de) | 1998-05-07 |
US6293239B1 (en) | 2001-09-25 |
EP0970300A1 (de) | 2000-01-12 |
JP2000510546A (ja) | 2000-08-15 |
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