WO2010086090A1 - Dispositif de réglage pour arbres à cames de moteurs à combustion interne de véhicules tels que véhicules à moteur, embarcations, bateaux ou similaires - Google Patents

Dispositif de réglage pour arbres à cames de moteurs à combustion interne de véhicules tels que véhicules à moteur, embarcations, bateaux ou similaires Download PDF

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Publication number
WO2010086090A1
WO2010086090A1 PCT/EP2010/000190 EP2010000190W WO2010086090A1 WO 2010086090 A1 WO2010086090 A1 WO 2010086090A1 EP 2010000190 W EP2010000190 W EP 2010000190W WO 2010086090 A1 WO2010086090 A1 WO 2010086090A1
Authority
WO
WIPO (PCT)
Prior art keywords
adjusting device
gear
camshaft
sun gear
connecting element
Prior art date
Application number
PCT/EP2010/000190
Other languages
German (de)
English (en)
Inventor
Andreas Kaiser
Helmut Schön
Original Assignee
Sbs-Feintechnik Gmbh & 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 Sbs-Feintechnik Gmbh & Co. Kg filed Critical Sbs-Feintechnik Gmbh & Co. Kg
Priority to EP10700809.6A priority Critical patent/EP2396521B1/fr
Publication of WO2010086090A1 publication Critical patent/WO2010086090A1/fr

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
    • F01L1/352—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 bevel or epicyclic gear

Definitions

  • Adjustment device for camshafts of internal combustion engines of vehicles such as motor vehicles, boats, ships or the like
  • the invention relates to an adjusting device for camshafts of internal combustion engines of vehicles, such as motor vehicles, boats, ships and the like, according to the preamble of claim 1.
  • the invention has for its object to provide the generic adjustment so that it allows for simple and cost-effective production and assembly accurate adjustment of the relative angular position of the camshaft to the crankshaft.
  • the sun gear of the planetary gear surrounds the connecting element with which the phase adjuster of the adjusting device is connected to the camshaft.
  • the connecting element can also be part of the camshaft.
  • the camshaft consists of a tube to which the cams are applied as separate elements.
  • the tube may be the connecting element of the adjusting device according to the invention.
  • the connecting element is formed at least by a part of a planet carrier.
  • the connecting element is operatively connected to the camshaft via a screw.
  • the connecting element may be connected directly to the camshaft in a force-locking manner, preferably by means of a press connection, in particular a cylindrical press connection.
  • the sun gear is provided with a planetary gear projecting sun gear, which can be coupled to the actuator.
  • the sun gear is advantageously arranged within the planetary gear so that it surrounds the planet carrier.
  • a reliable and yet simple sealing of the planetary gear is achieved when the planet carrier extends so far in the direction of the sun gear, that the sealing of the planetary gear between the sun gear and the planet carrier is possible to the outside.
  • the planet carrier consists of the connecting element, which is essentially a prismatic tube, and a flange in which the axes of the planet wheels are fastened.
  • the prismatic tube can be made for example by centerless grinding.
  • the ring gear of the planetary gear part of a housing in which the planet gears and the sun gear are housed.
  • the sun gear protrudes from the housing. This makes it easily possible to connect the planetary gear containing phaser with the actuator.
  • the positive locking profiling is located advantageously on the outside of the sun gear shaft. This has the advantage that the sun gear can be easily pushed onto the closure element.
  • the phase divider In order to simply connect the phase divider with the actuator, it is provided with at least one coupling element, with which the actuator can be coupled to the phase divider. Since the actuator and the phase adjuster are two separate structural units, it is not necessary, for example, to replace the entire adjusting device if the actuator is damaged.
  • the coupling element of the actuator is advantageously formed sleeve-shaped and provided with a form-locking profiling. It is preferably located on the inside of the coupling element.
  • the coupling element is advantageously connected via a reduction gear to a motor, preferably an electric motor.
  • the high speed of this engine can thus be reduced via the reduction gear to the low speed of the coupling element.
  • the motor may be a brushless DC motor or a stepper motor.
  • the rotation of the motor shaft is advantageously detected by sensors.
  • the reduction gear is advantageous a worm gear, with which not only a high reduction is possible, but which is also self-locking in an advantageous manner.
  • the motor shaft is advantageously in a plane which is perpendicular to the camshaft or to the axis of the connecting element.
  • the adjusting device has only a small length in the axial direction of the camshaft.
  • the motor shaft can also lie in a plane which is rotated about the pitch angle of a worm gear from the perpendicular to the camshaft or to the axis of the connecting element.
  • the sun gear is preferably mounted on the connecting element.
  • the ring gear on a smaller diameter approach on which a deflection wheel is mounted for an endlessly rotating drive element.
  • the guide wheel can be designed with the drive element so that the guide wheel and the larger diameter portion of the ring gear have approximately the same diameter. Since the deflection wheel is mounted on the smaller diameter approach of the ring gear, the ring gear with guide wheel can have a relatively small diameter, which has an advantageous effect on the size of the phaser.
  • the deflection wheel is advantageously provided with radially inwardly projecting teeth which engage in apertures of the neck of the ring gear. In this way, a reliable positive connection in the direction of rotation between the guide wheel and the ring gear is achieved.
  • the deflection wheel is preferably arranged in half the length of the projection of the ring gear. This ensures optimum introduction of force from the deflection wheel to the ring gear.
  • the ring gear is advantageously rotatably mounted on the connecting element by means of at least one bearing, preferably a roller bearing.
  • at least one bearing preferably a roller bearing.
  • the bearing is advantageously arranged substantially in the plane of action of the deflection wheel.
  • the bearing is preferably housed in the approach of the ring gear.
  • the bearing is located near the camshaft-side end of the phaser and thereby supports the connection region between the connecting element and the camshaft, so that in this critical area no or at most only a very small deflection of the camshaft occurs.
  • the deflection wheel is advantageously made of metallic material.
  • the teeth of such a metallic deflecting on the outer ring of the bearing Due to this metal-metal contact results in a good heat dissipation and in particular a very high rigidity of the phaser in the region of the deflection wheel.
  • the guide wheel is expediently directly operatively connected to an outer ring of the bearing. This ensures optimal heat dissipation.
  • the gear parts of the planetary gear can be made of a plastic, which has a high strength and wear resistance.
  • at least one gear part, preferably the sun gear, made of a metallic material is about him then a good heat dissipation from the planetary gear is possible.
  • the ring gear is advantageously closed on one side by a lid, so that a lubricant which is located in the ring gear, can not escape to the outside.
  • lid and the ring gear are advantageously made of plastic, these two parts can be very easily welded together.
  • the weld formed thereby increases the strength of the phaser.
  • the motor shaft of the actuator rotates only if the phase is to be adjusted.
  • FIG. 1 is a schematic representation of a camshaft drive with an adjusting device according to the invention
  • FIG. 2 is a perspective and partially in section an adjusting device according to the invention
  • 3 is a phase divider of the adjusting device according to the invention in a perspective view
  • 4 shows in perspective and partially in section an actuator of the adjusting device according to the invention
  • FIG. 5 is a perspective and partially sectional view of the phaser of the adjusting device according to the invention.
  • Fig. 6 in perspective view of the actuator of the adjusting device according to the invention.
  • Phase dividers are used for camshaft adjustments that change the angular position between a crankshaft and a camshaft during engine operation. Turning the camshaft shifts the opening and closing times of valves, which changes the filling processes in the cylinder of internal combustion engines.
  • Fig. 1 shows schematically a camshaft drive with two camshafts 1 and a crankshaft 2. Sitting on the camshaft and the crankshaft wheels 1 ', 2', preferably sprockets, over which an endlessly rotating drive element 3, preferably a chain, is guided.
  • the chain 3 is held by chain tensioner 4 in a known manner under tension.
  • the left in Fig. 1 chain tensioner 4 can be adjusted by means of a clamping device 5 in order to achieve the required chain tension.
  • This chain tensioner 4 is pivotable about an axis 6 lying parallel to the camshaft 1 or crankshaft 2.
  • the phaser has a cylindrical housing 7 (FIG. 5), which is provided at one end with a reduced diameter, axial approach 8 in diameter. It is advantageously integrally formed with the housing 7. At the other end, the housing 7 is covered by a lid 9 closed, which is mounted in the housing 7 after assembly of the transmission to be described later.
  • a drive wheel 10 in the embodiment, a sprocket, rotatably secured, over which the chain 3 is guided.
  • the sprocket 10 is spaced from a flat end face 11 of the housing 7 and from the free end 12 of the neck. 8
  • the outer ring 14 of a rolling bearing 13 On the inner wall of the projection 8, the outer ring 14 of a rolling bearing 13 is attached.
  • the outer ring 14 engages in an annular groove 15 in the inner wall of the neck 8 and is thereby secured axially.
  • the inner ring 16 of the rolling bearing 13 is non-rotatably mounted on a planet carrier 17 of a planetary gear 18th
  • the planet carrier 17 has a centrally projecting into the neck 8 sleeve 19, which extends to the free end 12 of the neck 8.
  • the sleeve 19 is advantageously formed by a centerless ground pipe. Approximately at the level of the end face 11, the sleeve 19 is adjoined by a radially outwardly extending flange 20, which is fastened on the sleeve 19 as a separate component. It is also possible, the sleeve 19 and the flange 20 integrally formed with each other.
  • the flange 20 extends within the housing 7 and has only a small distance from the end face 11 having the end wall 21 of the housing. 7
  • the sleeve 19 of the planet carrier 17 is seated on a screw 23, with which the phase divider is connected to the camshaft 1.
  • the screw 23 projects axially beyond the projection 8 and over the cover 9.
  • the protruding over the cover 9 end 24 of the screw 23 is formed as a positive-locking element, in the embodiment in the manner of a Allen screw.
  • the sleeve 19 of the planet carrier 17 is non-rotatably mounted on the screw 23 and extends up to a radial shoulder 25 at the transition from the screw end 24 in the slim screw part.
  • About the circumference of the flange 20 of the planet carrier 17 evenly distributed bolts 26 are provided which extend parallel to the screw axis and reach close to the lid 9.
  • planetary gears 27 which are each mounted with bearings 28, preferably roller bearings, rotatably mounted on the bolt 26.
  • the planetary gears 27 are in engagement with a sun gear 29.
  • a central opening 30 in the lid 9 projects outwardly a Clarradwelle 29 a, which may be fixedly connected to the sun gear 29 or formed integrally with her.
  • the planet gears 27 are also in engagement with a ring gear 31 which is formed by the housing 7 and the projection 8.
  • the housing 7 is provided on the inside with a toothing, in which the planet gears 27 engage.
  • the projecting over the lid 9 Claridwelle 29a sits on the protruding screw end 24. So that the sun gear 29 can be easily rotated, it is between two narrow sliding rings 52, 53. They are located on the two end faces of the sun gear 29 at.
  • the sliding ring 52 is advantageously located in an annular recess 54 on the inside of the lid 9.
  • the diameter of the recess 54 corresponds to the outer diameter of the sliding ring 52, which is thus positioned radially.
  • the sliding ring 53 rests with its inner edge on the sleeve 22.
  • the flange 20 of the planet carrier 17 bears with its underside facing the cover 9 against the sliding ring 53.
  • the sun gear 29 has on its outer side a circumferential collar 55, with which it engages over the edge of the opening 30 of the lid 9 on the inside. As a result, the sun gear 29 is housed axially secured in the housing 7 with the lid 9 attached.
  • the cover 9 is provided on its outer side at a distance from the sun gear 29a with a circumferential ridge 32 which encloses a receiving space 33 for a ring seal 34. It lies with a sealing lip 35- tend on the outside of the sun gear 29a and seals in this way the central opening 30 in the lid 9 from.
  • the sun gear 29 is provided within the housing 7 with an inner circumferential recess 36 into which a bearing 37, preferably a needle bearing, is inserted.
  • the sun gear shaft 29a is externally provided with a profiling 38 serving as positive locking, by means of which a rotationally fixed connection to a coupling element 39 (FIGS. 4 and 6) of an actuator 40 is produced. It is arranged torque-supported in the vehicle, preferably free of lateral forces.
  • the actuator 40 has a motor 41 with which a worm shaft 42 is rotatably driven. It is in engagement with a worm wheel 43 which is non-rotatably mounted on the coupling element 39.
  • the motor 41 may be, for example, a brushless DC motor or a stepping motor.
  • the worm wheel 43 and the sleeve-shaped coupling element 39 are housed in a housing 44. It is connected to a housing 45 of the motor 41.
  • the two housings 44, 45 each consist of two parts.
  • the parts of the housing 44, 45 are each advantageously formed integrally with each other. As a result, a simple assembly of the actuator 40 is ensured. It only needs the two housing parts are joined together, for example, welded or glued together. It is also possible that the housing 44, 45 of the motor 41 and the reduction gear 42, 43 and the ring gear 7, 8, 31 are integrally formed with each other.
  • the coupling element 39 is sleeve-shaped and has on its inside a profiling 38 of the sun gear 29a corresponding profiling 46. It extends only over part of the axial length on the inside of the coupling element 39.
  • the housing 44 has on both end faces in each case a central projection 47, 48.
  • the coupling element 39 protrudes with its two ends respectively into the lugs 47, 48.
  • the lug 47 is closed by a cover 49, which may be formed integrally with the housing 44. But it is also possible to attach the lid 49 at the neck 47 as a separate component. Then there is the possibility of still reaching the screw 23 when the actuator 40 is mounted.
  • the opposite approach 48 is open at the front.
  • the free end face of the coupling element 39 and the free end face of the projection 48 are advantageously in a common plane.
  • the profiling 38, 46 of the sun gear 29a and the coupling element 39 engage each other. In this way, a positive connection between the coupling element 39 and thus between the worm wheel 43 and the sun gear shaft 29a or the sun gear 29 is produced in the direction of rotation.
  • the profiles 38, 46 extend axially and are formed by at least in the circumferential direction one behind the other narrow webs.
  • a reduction gear forming worm gear is self-locking and advantageous in terms of its small dimensions.
  • the worm shaft 42 is advantageously catchy, but may also be designed to be more continuous.
  • a multi-stage spur gear, a bevel gear or a planetary gear can be used as a reduction gear.
  • the motor shaft 42 is in a plane which is perpendicular to the camshaft 1 and to the axis of the screw 23. If the reduction gear, as in the preferred embodiment, a worm gear, then the motor shaft 42 is in a plane which is about the pitch angle of the chord gkenvertechnikung from the perpendicular to the camshaft 1 and the axis of the screw 23 is arranged rotated.
  • the shoulder 8 is distributed over its circumference with openings 50 (FIG. 5), in which the sprocket 10 engages with corresponding radial projections 51.
  • the radial inner projections 51 of the sprocket 10 are advantageously so long that they are in contact with the outer ring 14 of the rolling bearing 13.
  • a metallic connection between the bearing ring 14 and the sprocket 10 is achieved, which leads to a high rigidity.
  • the bearing 13 is located substantially in the plane of action of the sprocket 10. It is, based on the axial length of the bearing 13, arranged centrally to him. This ensures optimal force transmission.
  • the bearing 13 is provided in the projection 8 of the ring gear 7, 8, 31 and is therefore close to the camshaft end of the planet carrier 17. If the phase splitter by means of the screw 23 in a known manner with the camshaft 1, then results from this position of the bearing 13 with respect to the planet carrier 17, the advantage that the camshaft 1 and the connection region between it and the phaser undergoes only a small deflection, which does not adversely affect the function of the phaser.
  • the ring gear 7, 8, 31 and the sprocket 10 with the chain 3 have approximately the same diameter. In practice, this diameter is advantageously less than 100 mm.
  • the phaser requires only a small installation space due to these small dimensions.
  • the outer diameter of the phase adjuster is smaller than twice the pitch circle diameter of the crankshaft-side drive wheel 2 '.
  • the drive takes place in the phase divider via the sun gear 29. The output then takes place via the planet 17.
  • the stationary during operation sun gear 29 has the advantage that in case of failure of the actuator 40, the further function of the phaser is guaranteed.
  • the sun gear 29 is rotated only when the actuator 40 is operated to move the camshaft 1 relative to the crankshaft.
  • the camshaft 1 rotates at a stationary sun gear 29 at half the speed of the crankshaft speed.
  • the gear parts of the planetary gear advantageously made of plastic, such as POM or polyamide. At least one of the gear parts, preferably the sun gear 29, consists of metallic material. About such a transmission part, the resulting heat within the phaser during operation can be easily dissipated to the outside.
  • the ring gear 7, 8, 31 may also be formed as a sintered part, which is optionally encapsulated in plastic.
  • the gear parts themselves may be sintered parts.
  • the parts of the phaser can be made of any suitable material.
  • the cover 9 and the ring gear 7, 8, 31 are advantageously made of plastic. Appropriately, these two parts are welded together, so that a screw is not required. In the case of welding, a weld is formed between the cover 9 and the housing 7, which leads to an increased strength of the phaser.
  • the welding between the lid 9 and the housing 7 can take place axially or in the circumferential direction.
  • the chain 3 and the sprocket 10 form the primary ratio between the camshaft 1 and the crankshaft 2.
  • a secondary ratio is achieved by the planetary gear 18 described.
  • the planetary gear described In the drive connection between the crankshaft 2 and the camshaft 1 thus sits the planetary gear described as a phaser. With him is a very comfortable pakte training of the camshaft drive and the phaser itself possible.
  • the phase divider can thus also be installed where only small installation spaces are available in a vehicle.
  • a sensor e.g. a pulse generator, mounted, with which the exact rotational position of the worm shaft can be determined.
  • the actuator 40 may be provided (not shown) stop, whereby it is possible to bring the actuator 40 and its worm shaft 42 to a basic position. From this basic position then the count takes place by means of the pulse generator.
  • the crankshaft 2 drives the camshaft 1 via the chain 3. Since the chain 3 is guided over the sprocket 10 and this rotatably connected to the ring gear 7, 8, 31, this rotates about its axis. Since the planet gears 27 are in engagement with the internal teeth of the ring gear, they roll on the sun gear 29, which thus does not rotate about its axis. If the opening and closing times of the valves of the internal combustion engine are to be adjusted, the actuator 40 is actuated. About the reduction gear 42, 43, the coupling element 39 and thus the sun gear 29 is rotated about its axis.
  • the planetary wheel is formed by the preferably formed as a ground pipe sleeve 19 and the flange 20 in which the axes 26 of the planet gears 27 are fixed.
  • the sleeve 19 is operatively connected to the camshaft 1 via the screw 23.
  • the sleeve 19 as part of the planet carrier 17 of the plane tengetriebes 18 thus forms the connecting element with which the phaser is to be connected to the camshaft 1.
  • the sleeve 19 can also sit directly on the camshaft 1.
  • the sleeve 19 as a connecting element with the camshaft 1 by means of a press connection, preferably a cylindrical press connection, operatively connected.
  • the connecting element 19 is formed by a portion of the camshaft 1 itself. Then the flange 20 sits directly on the camshaft first.
  • the camshaft 1 is not made as a cast component, but consists of a preferably centerless ground pipe on which the cams are mounted. None changes in the mode of operation of the adjusting device and in particular of the phasing actuator.

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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 des dispositifs de réglage ayant un actionneur qui permet d'actionner un diviseur de phase conçu essentiellement comme un engrenage planétaire (18) de préférence plan. L'ajusteur de phase a une roue solaire (29) dans laquelle s'engrènent des roues planétaires (27) et une couronne (31) dans la denture intérieure de laquelle les roues planétaires (27) s'engrènent. Le but de l'invention est de permettre un ajustement précis de la position angulaire relative de l'arbre à cames par rapport au vilebrequin, pour une fabrication et un montage simples et d'un coût avantageux. A cet effet, la roue solaire (29) de l'engrenage planétaire (18) entoure un élément de liaison (19) avec lequel l'ajusteur de phase est à relier à l'arbre à cames ou lequel fait partie de l'arbre à cames. Le dispositif de réglage est utilisé pour des réglages de l'arbre à cames qui changent, pendant le fonctionnement du moteur, la position angulaire entre le vilebrequin et l'arbre à cames.
PCT/EP2010/000190 2009-01-31 2010-01-15 Dispositif de réglage pour arbres à cames de moteurs à combustion interne de véhicules tels que véhicules à moteur, embarcations, bateaux ou similaires WO2010086090A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10700809.6A EP2396521B1 (fr) 2009-01-31 2010-01-15 Dispositif de réglage pour arbres à cames de moteurs à combustion interne de véhicules tels que véhicules à moteur, embarcations, bateaux ou similaires

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009006957A DE102009006957A1 (de) 2009-01-31 2009-01-31 Verstelleinrichtung für Nockenwellen von Verbrennungsmotoren von Fahrzeugen, wie Kraftfahrzeuge, Boote, Schiffe oder dergleichen
DE102009006957.7 2009-01-31

Publications (1)

Publication Number Publication Date
WO2010086090A1 true WO2010086090A1 (fr) 2010-08-05

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ID=41818461

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2010/000190 WO2010086090A1 (fr) 2009-01-31 2010-01-15 Dispositif de réglage pour arbres à cames de moteurs à combustion interne de véhicules tels que véhicules à moteur, embarcations, bateaux ou similaires

Country Status (3)

Country Link
EP (1) EP2396521B1 (fr)
DE (1) DE102009006957A1 (fr)
WO (1) WO2010086090A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109124023A (zh) * 2018-09-28 2019-01-04 济南大学 一种内外异向旋转的钢丝绳刷头

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017115882B4 (de) 2017-07-14 2023-11-09 Schaeffler Technologies AG & Co. KG Elektrischer Nockenwellenversteller zur variablen Einstellung der Ventilsteuerzeiten einer Brennkraftmaschine

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4104872A1 (de) * 1991-02-18 1992-08-20 Wolfgang Schieck Verfahren zur drosselfreien laststeuerung fuer ottomotoren
DE29714816U1 (de) 1997-08-19 1997-10-23 Paul, Uwe, 97084 Würzburg Stufenlose Nockenwellenverstellung
JPH11153008A (ja) * 1997-11-21 1999-06-08 Mazda Motor Corp 回転位相制御装置
DE10054796A1 (de) * 2000-11-04 2002-06-13 Ina Schaeffler Kg Vorrichtung zur Drehwinkelverstellung einer Welle gegenüber ihrem Antrieb
US20030070641A1 (en) * 2001-10-12 2003-04-17 Hitachi Unisia Automotive, Ltd. Valve timing control device of internal combustion engine
WO2003056141A1 (fr) * 2001-12-26 2003-07-10 Nittan Valve Co., Ltd. Dispositif de reglage de distribution variable de type engrenage planetaire
WO2005080757A1 (fr) * 2004-02-25 2005-09-01 Schaeffler Kg Dispositif de reglage electrique d'arbre a cames
US20050217621A1 (en) * 2002-07-24 2005-10-06 Jens Schafer Device for varying valve timing in an internal combustion engine

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4104872A1 (de) * 1991-02-18 1992-08-20 Wolfgang Schieck Verfahren zur drosselfreien laststeuerung fuer ottomotoren
DE29714816U1 (de) 1997-08-19 1997-10-23 Paul, Uwe, 97084 Würzburg Stufenlose Nockenwellenverstellung
JPH11153008A (ja) * 1997-11-21 1999-06-08 Mazda Motor Corp 回転位相制御装置
DE10054796A1 (de) * 2000-11-04 2002-06-13 Ina Schaeffler Kg Vorrichtung zur Drehwinkelverstellung einer Welle gegenüber ihrem Antrieb
US20030070641A1 (en) * 2001-10-12 2003-04-17 Hitachi Unisia Automotive, Ltd. Valve timing control device of internal combustion engine
WO2003056141A1 (fr) * 2001-12-26 2003-07-10 Nittan Valve Co., Ltd. Dispositif de reglage de distribution variable de type engrenage planetaire
US20050217621A1 (en) * 2002-07-24 2005-10-06 Jens Schafer Device for varying valve timing in an internal combustion engine
WO2005080757A1 (fr) * 2004-02-25 2005-09-01 Schaeffler Kg Dispositif de reglage electrique d'arbre a cames

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109124023A (zh) * 2018-09-28 2019-01-04 济南大学 一种内外异向旋转的钢丝绳刷头

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Publication number Publication date
DE102009006957A1 (de) 2010-08-05
EP2396521B1 (fr) 2017-03-15
EP2396521A1 (fr) 2011-12-21

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