EP1046792A2 - Stellantrieb zur Positionierung eines Stellmittels - Google Patents
Stellantrieb zur Positionierung eines Stellmittels Download PDFInfo
- Publication number
- EP1046792A2 EP1046792A2 EP00107447A EP00107447A EP1046792A2 EP 1046792 A2 EP1046792 A2 EP 1046792A2 EP 00107447 A EP00107447 A EP 00107447A EP 00107447 A EP00107447 A EP 00107447A EP 1046792 A2 EP1046792 A2 EP 1046792A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- gear
- crankshaft
- actuator
- actuator according
- drive
- 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.)
- Withdrawn
Links
Images
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
- F01L1/348—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 by means acting on timing belts or chains
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/04—Engines with variable distances between pistons at top dead-centre positions and cylinder heads
- F02B75/047—Engines with variable distances between pistons at top dead-centre positions and cylinder heads by means of variable crankshaft position
Definitions
- the invention relates to an actuator for positioning of an actuator on a piston internal combustion engine.
- the invention has for its object an actuator to create, with high positioning and low energy consumption Holding forces for positioning an actuator on a Piston engine can be applied.
- the object is achieved according to the invention with an actuator solved, which is provided with a drive means that over switchable means for reversing the direction of rotation and a high gear Gearbox is connected to the actuator.
- a drive means that over switchable means for reversing the direction of rotation and a high gear Gearbox is connected to the actuator.
- a high gear ratio it is possible to apply high positioning forces with low driving force.
- Corresponding to the low actuating forces to be applied it is also possible to use such a gear switchable locking means in the respective position hold, even for the locking means only small holding forces required are.
- gear is designed self-locking. This is particularly advantageous to achieve by a gearbox as worm drive with worm arranged on the drive side is trained.
- the required back and forth movement is expedient effected via a rotary drive.
- an electromotive Rotary drive can do this by electrical means by reversing the direction of rotation.
- the drive means through the Piston engine itself is formed, which has a Intermediate switchable clutch connected to the transmission is.
- the agent for reversing the direction of rotation through a switchable change gear arrangement is formed on the transmission.
- the driving force can here from the crankshaft of the piston internal combustion engine a belt drive expediently from the toothed belt for actuation the camshafts or from the V-belt to the drive the alternator can be tapped. Because the drive means has a constant direction of rotation, the required Float for the actuator by the cause switchable change gear arrangement on the transmission.
- the Switchable coupling through a non-contact electromagnetic Coupling is formed.
- Such an electromagnetic Coupling has the advantage that the adjustment process can be carried out bumpless, so that in particular with small travel ranges depending on the activation of the clutch Adjustment process slow and continuous or alternatively clocked can be done.
- the one for the activation of the electromagnetic Coupling necessary electrical energy is clear less than a direct drive via its own servomotor.
- a particularly useful application is according to the invention provided that the actuating means to be operated as Device for changing the combustion chamber volume of the cylinders the piston internal combustion engine by relocating the crankshaft is trained.
- crankshaft 1 of a four-cylinder piston internal combustion engine with their crankshaft bearings 2 in eccentric rings 3 stored, which in turn can be rotated in corresponding support bearing housings 4 of an indicated engine block are stored.
- crankshaft 1 are each only here through connecting rods 5 schematically indicated piston 6 connected.
- the crankshaft is shown in a position in which the pistons 6.1 and 6.4 are in the top dead center position while pistons 6.2 and 6.3 are in the bottom dead center position.
- At least one of the eccentric rings 3 is with a Gear 7 trained rotating device connected so that synchronous turning of the other eccentric rings via the crankshaft 3 is done.
- the axis of rotation 10 is the Crankshaft 1 eccentric to the pivot axis 11 of the eccentric rings 3 and is arranged via the transmission 7 from an assumed Middle point for changing the altitude a after moved up or down on a circular path.
- This will make the Axis of rotation 10 of the crankshaft with respect to the horizontal engine fixed Reference plane B also with respect to the fixed swivel axis 11 of the eccentric rings 3 raised or lowered.
- Limitation, d. H the lateral distance of the axis of rotation 10 to the cylinder axes is changed.
- the gear 7 can now directly with a corresponding Extension shaft not shown here in extension the axis of rotation 11 connected to the eccentric ring 3 to be rotated his.
- a corresponding pinion 14 to a with the interlocking eccentric ring 3 connected tooth segment 15 acts, as shown here.
- 3 and 4 are still different embodiments for the transmission 7 explained in more detail.
- the gear 7 is a preferably electromagnetically actuated Actuator 16 which can be controlled via a controller 13 is assigned, with a change gear arrangement provided in the transmission 17 can be actuated for a reversal of the direction of rotation.
- the Swivel path or the respective change in altitude "a" can be detected by a sensor 12 assigned to the controller 13 become.
- the change gear assembly 17 is with a drive pinion 18 in connection, which via a shaft 19.2 and a switchable coupling 19, here a contactless one electromagnetic clutch, through a timing chain or to drive a V-belt 20 using the crankshaft is.
- FIG. 2 is a schematic front view of a piston internal combustion engine the timing chain 20 shown with the via a drive pinion connected to the crankshaft 21 the camshafts 22 of the piston internal combustion engine are driven.
- the timing chain stands with the switchable clutch 19 in constant engagement.
- the driving part 19.1 the electromagnetic described in more detail with reference to FIG. 5 acting clutch 19 with the timing chain 20 in constant Intervention. If the electromagnetic clutch 19 is activated, so is connected to the shaft 19.2 via the magnetic force Output part, to which the drive pinion 18 is connected, taken in the specified unchanged direction of rotation. With the help of the actuator 16 can by a corresponding Circuit of the change gear 17 despite constant direction of rotation the clutch 19, the direction of rotation of the transmission 7th changed and so the desired back and forth movement (arrow 9) can be effected.
- FIG. 3 an embodiment for that in Fig. 1 is schematic shown transmission 7 shown in perspective.
- this is connected to the shaft 19.2 Drive pinion 18 formed as a bevel gear, the as Change gear arrangement 17 two bevel gears 17.1 and 17.2 in constant Intervention are assigned.
- the bevel gears 17.1 and 17.2 are freely rotatable on a shaft shoulder of a drive worm 23, which is connected to a worm wheel 24 stands, as shown in Fig. 1 and above also described, acts on the eccentric ring 3.
- Between the two bevel gears 17.1 and 17.2 is a turning test longitudinally connected to the drive worm 23 Shift sleeve 17.3 arranged alternately via the actuator 16 engaged with the bevel gear 17.1 or 17.2 can be.
- the change gear assembly 17 stands with Actuator 16 (Fig. 1) in connection and can in this Direction of arrow 17.3 shifted within the switching distance and so either the bevel gear 17.1 or the bevel gear 17.2 are brought into engagement with the drive pinion 18.
- This embodiment is based on the design as a drive screw 23 of the gear 7 self-locking. Depending on the position the change gear assembly 17 can then the worm wheel 24 in Direction of the double arrow 8 are rotated back and forth.
- the clutch 19 is in a change gear arrangement 25 Connection that a first change gear 25.1 and a second Change gear 25.2, which as a block on the example designed as a spline shaft 19.2 of the coupling 19 in a bearing bracket not shown here axially displaceable are stored so that either the change gear 25.1 or the change gear 25.2 with the gear 25 in engagement can be brought.
- the second change gear 25.2 protrudes an intermediate gear firmly connected to the first change gear 25.1 25.3 in engagement, so that the second gear 25.2 despite constant direction of rotation of the clutch 19 rotates in the opposite direction.
- the bearing bracket can now be operated using an appropriate actuator with the two change gears 25.1 and 25.2 in axial Direction on the drive shaft 19.2 are shifted and so either for one or the other direction of rotation with the Gear 24 can be engaged to the desired To effect pivoting movement. Via one connected to the shaft 24.1 small gear and a meshing with it Another large gear wheel, which is then via a pinion 14 (Fig. 1) acts on the eccentric ring 3, the desired strong reduction can be effected.
- Fig. 5 is an embodiment schematically in a vertical section shown for the clutch 19.
- the outer rotor 19.1 is with a Coil winding 30 provided, via a slip ring transformer 31 can be energized.
- the inner rotor 19.3 is over the drive shaft 19.2 with the drive pinion 18 (Fig. 1) or 25.1 (Fig. 4) connected.
- the outer drive rotor 19.1 stands accordingly Fig. 2 with the timing chain 20 in connection, such as this is indicated here.
- the inner rotor 19.3 with a chargeable winding can be provided, which then also over corresponding Slip ring transmitter or via a non-contact Energy coupling generates a magnetic field.
- the height of the Coil winding 30 current supplied the strength of the electromagnetic field and with that also on the inner rotor 19.3 acting torque, but also the slip between the outer and the inner rotor is determined.
- Energizing the coil winding 30 can thus be a "gentle” and slow adjustment of the actuator.
- the amount of energization of the coil winding 30 can over the Engine control, for example, specified depending on the speed be so that adapting to the respective engine speed the amount of current for the coil 30 is predetermined and so despite changing engine speeds over the entire operating range the piston internal combustion engine a constant adjustment speed is achieved.
- the actuator of the invention can not only on the Piston engine even with intermediate electromagnetic clutch can be operated as a drive means. It is also possible to use one in its drive Direction of rotation non-switchable stepper motor, electric motor low power or use a hydraulic motor. Depending on the design of the drive means and possibly an intermediate one Parking brake, the actuator between two predetermined end positions can be adjusted or intermediate positions if appropriate sensors are used between the given end positions.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transmission Devices (AREA)
- Gear Transmission (AREA)
- Valve Device For Special Equipments (AREA)
- Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Description
- Fig. 1
- als Anwendungsbeispiel eine perspektivische Schemadarstellung einer Vierzylinder-Kolbenbrennkraftmaschine mit variabel einstellbarem Brennraum,
- Fig. 2
- eine Stirnansicht der Antriebsmittel,
- Fig. 3
- eine perspektivische Ansicht eines Stellentriebes mit Schneckengetriebe,
- Fig. 4
- eine perspektivische Ansicht einer anderen Ausführungsform für einen Stellantrieb,
- Fig. 5
- eine Ausführungsform einer elektromagnetischen Kupplung im Schnitt.
Claims (8)
- Stellantrieb zur Positionierung eines Stellmittels an einer Kolbenbrennkraftmaschine, der mit einem Antriebsmittel versehen ist, das über schaltbare Mittel (17) zur Drehrichtungsumkehr und ein hoch untersetztes Getriebe (7) mit dem Stellmittel in Verbindung steht.
- Stellantrieb nach Anspruch 1, dadurch gekennzeichnet, daß das Getriebe mit schaltbaren Sperrmitteln (27, 28) in Verbindung steht.
- Stellantrieb nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß das Getriebe selbstsperrend ausgebildet ist.
- Stellantrieb nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß das Getriebe (7) als Schneckentrieb mit antriebsseitig angeordneter Schnecke (23) ausgebildet ist.
- Stellantrieb nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß das Mittel zur Drehrichtungsumkehr durch eine schaltbare Wechselradanordnung (17, 25) an Getriebe (7) gebildet wird.
- Stellantrieb nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß das Antriebsmittel durch die Kolbenbrennkraftmaschine selbst gebildet wird, die über eine zwischengeschaltete schaltbare Kupplung (19) mit dem Getriebe (7) verbunden ist.
- Stellantrieb nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß das Getriebe (7) über eine berührungslos wirkende elektromagnetische Kupplung (19) antriebsseitig mit der Kolbenbrennkraftmaschine verbunden ist.
- Stellantrieb nach einem der Ansprüche 1 bis 7, dadurch gekennzeichnet, daß das zu betätigende Stellmittel als Einrichtung zur Veränderung des Brennraumvolumens der Zylinder der Kolbenbrennkraftmaschine durch Verlagerung der Kurbelwelle (2) ausgebildet ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19918592 | 1999-04-23 | ||
DE19918592A DE19918592B4 (de) | 1999-04-23 | 1999-04-23 | Stellantrieb zur Positionierung eines Stellmittels |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1046792A2 true EP1046792A2 (de) | 2000-10-25 |
EP1046792A3 EP1046792A3 (de) | 2001-11-21 |
Family
ID=7905695
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00107447A Withdrawn EP1046792A3 (de) | 1999-04-23 | 2000-04-06 | Stellantrieb zur Positionierung eines Stellmittels |
Country Status (4)
Country | Link |
---|---|
US (1) | US6276314B1 (de) |
EP (1) | EP1046792A3 (de) |
JP (1) | JP2000337181A (de) |
DE (1) | DE19918592B4 (de) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1286029A1 (de) * | 2001-08-23 | 2003-02-26 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Steuertrieb einer Kolbenbrennkraftmaschine mit variablem Brennraum |
DE10207760A1 (de) * | 2002-02-23 | 2003-09-04 | Ina Schaeffler Kg | Vorrichtung zum lösbaren Verbinden und Verstellen zweier zueinander drehwinkelverstellbarer Wellen |
DE10211998A1 (de) * | 2002-03-18 | 2003-10-02 | Ina Schaeffler Kg | Vorrichtung zum Steuern der Zylinderladung eines fremdgezündeten Verbrennungsmotors |
DE10248351A1 (de) * | 2002-10-17 | 2004-04-29 | Ina-Schaeffler Kg | Elektrisch angetriebener Nockenwellenversteller |
Families Citing this family (11)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1247958A1 (de) * | 2001-04-07 | 2002-10-09 | Ford Global Technologies, Inc., A subsidiary of Ford Motor Company | Verbrennungskraftmaschine mit veränderlichem Verdichtungsverhältnis |
DE10352255B4 (de) * | 2003-11-08 | 2017-03-09 | Schaeffler Technologies AG & Co. KG | Verstellvorrichtung zum Verstellen der relativen Drehwinkellage einer Nockenwelle gegenüber einer Kurbelwelle einer Brennkraftmaschine |
DE102005047203A1 (de) * | 2005-10-01 | 2007-04-19 | Daimlerchrysler Ag | Brennkraftmaschine mit variablem Verdichtungsverhältnis |
DE102008003108A1 (de) | 2008-01-01 | 2009-10-15 | Fev Motorentechnik Gmbh | VCR - Antrieb Nebentrieb ohne PKG |
DE102008005467A1 (de) * | 2008-01-21 | 2009-07-23 | Fev Motorentechnik Gmbh | Hubkolbenmaschine |
DE102008040459A1 (de) * | 2008-07-16 | 2010-01-21 | Zf Friedrichshafen Ag | Verstellvorrichtung eines Verbrennungsmotors |
DE102008050827A1 (de) * | 2008-10-08 | 2010-04-15 | Schaeffler Kg | Verstellvorrichtung für eine Kurbelwelle eines Verbrennungsmotors sowie Verfahren zu deren Ansteuerung |
DE102008050826A1 (de) * | 2008-10-08 | 2010-04-15 | Schaeffler Kg | Verstellvorrichtung zur Lageveränderung einer in Exzenterbuchsen gelagerten Kurbelwelle eines Verbrennungsmotors |
DE102010026472A1 (de) | 2010-07-07 | 2012-01-12 | Fev Motorentechnik Gmbh | Abtriebseinheit für den Steuertrieb eines VCR-Motors mit exzentrisch gelagerter Kurbelwelle |
DE102011116952B4 (de) * | 2011-10-26 | 2015-09-03 | Audi Ag | Mehrgelenkskurbeltrieb einer Brennkraftmaschine sowie Verfahren zum Betreiben eines Mehrgelenkskurbeltriebs |
DE102013220399A1 (de) * | 2012-11-08 | 2014-05-08 | Schaeffler Technologies Gmbh & Co. Kg | Verfahren zur Steuerung eines hybridischen Antriebsstrangs |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR636527A (de) * | 1928-04-11 | |||
DE2232591A1 (de) * | 1972-07-03 | 1974-01-31 | Heinz Rudolf Gunkel | Gemischverdichtende, ladepumpengespuelte, zweitakt-brennkraftmaschine mit veraenderlicher kompression und selbstzuendung |
US4152955A (en) * | 1975-01-02 | 1979-05-08 | Mcwhorter Edward M | Engine compound crankshaft |
US4535730A (en) * | 1980-12-08 | 1985-08-20 | Allen Dillis V | Rocker engine |
US4485768A (en) * | 1983-09-09 | 1984-12-04 | Heniges William B | Scotch yoke engine with variable stroke and compression ratio |
DE3601528A1 (de) * | 1986-01-20 | 1987-07-23 | Wolfgang Schwarz | Brennkraft-kolbenmaschine, reihenmotor mit variablem verdichtungsverhaeltnis |
US4860702A (en) * | 1988-03-21 | 1989-08-29 | Doundoulakis George J | Compression ratio control in reciprocating piston engines |
US5680840A (en) * | 1996-11-08 | 1997-10-28 | Mandella; Michael J. | Multi-crankshaft variable stroke engine |
DE29719343U1 (de) * | 1997-10-31 | 1998-01-08 | FEV Motorentechnik GmbH & Co. KG, 52078 Aachen | Kolbenbrennkraftmaschine mit einstellbarem Verdichtungsverhältnis |
-
1999
- 1999-04-23 DE DE19918592A patent/DE19918592B4/de not_active Expired - Fee Related
-
2000
- 2000-04-06 EP EP00107447A patent/EP1046792A3/de not_active Withdrawn
- 2000-04-20 JP JP2000119315A patent/JP2000337181A/ja not_active Withdrawn
- 2000-09-06 US US09/655,884 patent/US6276314B1/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
None |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1286029A1 (de) * | 2001-08-23 | 2003-02-26 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Steuertrieb einer Kolbenbrennkraftmaschine mit variablem Brennraum |
DE10207760A1 (de) * | 2002-02-23 | 2003-09-04 | Ina Schaeffler Kg | Vorrichtung zum lösbaren Verbinden und Verstellen zweier zueinander drehwinkelverstellbarer Wellen |
DE10207760B4 (de) * | 2002-02-23 | 2019-10-31 | Schaeffler Technologies AG & Co. KG | Vorrichtung zum lösbaren Verbinden und Verstellen zweier zueinander drehwinkelverstellbarer Wellen |
DE10211998A1 (de) * | 2002-03-18 | 2003-10-02 | Ina Schaeffler Kg | Vorrichtung zum Steuern der Zylinderladung eines fremdgezündeten Verbrennungsmotors |
DE10248351A1 (de) * | 2002-10-17 | 2004-04-29 | Ina-Schaeffler Kg | Elektrisch angetriebener Nockenwellenversteller |
US7308876B2 (en) | 2002-10-17 | 2007-12-18 | Schaeffler Kg | Electrically driven camshaft adjuster |
Also Published As
Publication number | Publication date |
---|---|
EP1046792A3 (de) | 2001-11-21 |
US6276314B1 (en) | 2001-08-21 |
JP2000337181A (ja) | 2000-12-05 |
DE19918592B4 (de) | 2013-05-23 |
DE19918592A1 (de) | 2000-10-26 |
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