EP2859197A1 - Vorrichtung zur phasenverschiebung des drehwinkels eines antriebsrades zu einer abtriebswelle - Google Patents
Vorrichtung zur phasenverschiebung des drehwinkels eines antriebsrades zu einer abtriebswelleInfo
- Publication number
- EP2859197A1 EP2859197A1 EP13720953.2A EP13720953A EP2859197A1 EP 2859197 A1 EP2859197 A1 EP 2859197A1 EP 13720953 A EP13720953 A EP 13720953A EP 2859197 A1 EP2859197 A1 EP 2859197A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rotation
- output shaft
- drive wheel
- phase shifting
- angle
- 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- Withdrawn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
- 238000006073 displacement reaction Methods 0.000 claims description 9
- 230000003247 decreasing effect Effects 0.000 claims description 2
- 230000033001 locomotion Effects 0.000 description 14
- 230000005540 biological transmission Effects 0.000 description 6
- RDYMFSUJUZBWLH-UHFFFAOYSA-N endosulfan Chemical compound C12COS(=O)OCC2C2(Cl)C(Cl)=C(Cl)C1(Cl)C2(Cl)Cl RDYMFSUJUZBWLH-UHFFFAOYSA-N 0.000 description 4
- 230000010363 phase shift Effects 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 230000004907 flux Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 238000012549 training Methods 0.000 description 1
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
- the invention relates to a device for phase shifting the rotational angle of a drive wheel to an output shaft with a drive gear connected to the drive gear and at least one double gear whose first gear meshes with the drive gear and the second gear engages in a rack and which is rotatably mounted on a rotary axis carrier, whose axes of rotation extend radially and which is connected to the output shaft and an actuator, via which the rack is axially displaceable.
- phase shift devices are known in particular for the phase shift between a crankshaft and a camshaft of an internal combustion engine, but can also be used in the area of internal combustion engines, for example, for the cycle-accurate control of an exhaust gas recirculation system.
- the phase shift is used for variable valve timing to improve the combustion process in the engine.
- vane-type cam phaser, camshaft chain adjuster or axially displaceable toothing elements are known for phase shifting the camshaft.
- electrical phase adjusters has been found, which have a transmission which is similar in construction to a planetary gear or a differential gear. These offer the possibility of a stepless adjustment, so that a high variability is achieved.
- a phase plate in which a planetary gear designed as a crown gear drive gear and also designed as a crown gear output gear, which is connected to the camshaft, and has three designed as a double gear planet gears, via which the movement of the drive gear is transmitted to the output gear.
- the second gears of the double gears are coupled to racks, which are arranged on a rack carrier which is axially displaceable for rotation of the planetary gears, whereby the relative rotation of the drive gear to the driven gear.
- the actuator is rotationally decoupled from the gearbox via a ball bearing.
- a phaser known, in which a drive shaft is fixedly coupled to a drive gear, which meshes with Planetenrädem, which are rotatably mounted on a planet carrier, which in turn is fixedly connected to an output shaft.
- a rack carrier rotates with the rotary axis carrier and is axially displaceable to the axis of rotation of the axis, whereby a rotation of the planet gears takes place, causing a phase shift.
- an actuator of the phaser is to be arranged, on the one hand to ensure an axial force transmission and on the other hand to decouple the actuator rotationally from the transmission.
- a disadvantage of the known embodiments is that no permanent and quiet operation can be ensured. Furthermore, there is the problem that the axial actuating forces must be absorbed on components of the cylinder head, which has considerable requirements for the storage of the camshaft result.
- This object is achieved by a device for phase shifting the angle of rotation between a drive wheel and an output shaft having the features of the main claim.
- the rack is formed on a rack carrier, which is mounted on a radially displaceable actuating body via a radial bearing and at least one axial bearing, the axial actuating forces are absorbed by the thrust bearing, so that no wear by a rotational relative movement of the actuating body to the rack carrier or the axis of rotation support arises and created by axial load of bearings that are not suitable to absorb axial holding and adjusting forces. This ensures a long service life with low wear.
- the rack carrier is mounted on two thrust bearings, which are arranged on two opposite sides of an annular radial extension of the actuating body. Accordingly, the holding and actuating forces are transmitted in both adjustment directions on the extension to a corresponding forces receiving thrust bearing.
- the actuating body is a spindle with internal toothing, which corresponds to an outer toothing of a radially inner spindle, which projects beyond the actuating body at an axial end opposite to the actuator and at this axial end has an annular radial extension against its axial contact surfaces in each case abuts a thrust bearing.
- Axial forces acting on the outer spindle are absorbed by the inner spindle, which is supported on the axis of rotation carrier via the second pair of thrust bearings. Both axial forces introduced via the actuator and axial forces introduced by the alternating torques of the camshaft are thus supported within the transmission.
- the rotary axis carrier is biased by a spring element in the direction of the drive gear.
- the spring element is designed as a corrugated spring, which loads a crown gear, which carries the drive gear, against a support plate which is fixedly connected to the rotary axis support.
- the spring element is guided in a support ring which is fixed to the crown wheel.
- the position of the wave spring is determined in a simple manner, whereby the assembly of the spring is facilitated.
- the at least one second toothed wheel of the at least one double toothed wheel and the corresponding toothed rack preferably have sliding profile displacements, whereby an optimized engagement of the teeth with one another is ensured.
- the at least one double gear is biased radially outwards via a spring element, wherein the profile displacement of the second gear decreases radially outward continuously and the profile displacement of the corresponding rack increases radially outward appropriately.
- a linear sensor is arranged in a housing of the actuator, which corresponds to a magnet which on Actuator is arranged.
- the actuator has a 5 Axial stepmotor.
- the actuating body is rotationally decoupled from the axis of rotation of the rack and the rack carrier.
- the actuator of the actuator can stand still outside the operating times and is not loaded rotationally, o This increases its life.
- the radial bearing is axially and radially against a support ring which is connected to the rack carrier and is axially displaceable relative to the axis of rotation of the support. Accordingly, there is a sliding movement between the support ring and the rotary axis support only when the servo motor.
- the support ring ensures even loading of the radial bearing.
- a thrust washer is biased by a spring element between the rotary axis support and the thrust washer in the direction of extension of the inner spindle and adjacent to the extension thrust bearing.
- a thrust washer is biased by a spring element between the rack carrier and the thrust washer in the direction of extension of the actuator and adjacent to the extension thrust bearing, which again a concern of the bearing on the extension and the thrust washer is ensured in stock.
- Figure 1 shows a side view of a device according to the invention for the phase shift of the rotational angle of a drive wheel to an output shaft in a sectional view.
- FIG. 2 shows a sectional view along the line A - A of the device according to the invention for phase shifting the angle of rotation of a drive wheel to an output shaft according to FIG. 1.
- the inventive device for phase shifting consists of a drive wheel 10, which has an outer toothing 12, in which engages a toothed belt or a chain, via or over the Drive wheel 10 is connected to a crankshaft for transmitting motion.
- the drive wheel 10 is rotatably connected via a crown gear carrier 14 with a crown gear formed as a drive gear 16, the teeth 18 extends correspondingly axially.
- the drive wheel 10 and the drive gear 16 are arranged rotatably about a common axis of rotation 20.
- the crown gear carrier 14 and the drive gear 16 are rotatably mounted on a rotary axis carrier 22, from which three axes of rotation 24 extend radially outward.
- a double gear 26 is rotatably disposed, the radially inner first gear 28 meshes with the drive gear 16 and the radially outer second gear 30 engages in each case a rack 32 which extends axially from a rack carrier 34.
- the respective axis of rotation 24 surrounding a spring element 27 is arranged, via which the double gear 26 is pressed radially outward.
- the respective second gear 30 of the double gears 26 has a radially outwardly continuously decreasing profile displacement, while the racks 32 have a radially outwardly increasing corresponding profile displacement. Accordingly, the teeth of the second gear 30 are pressed into the corresponding toothings of the racks, whereby a backlash is reliably avoided.
- the Drehachsenarme 22 is rotatably secured via a secured against rotation screw 36 to an output shaft, not shown, whose internal thread engages in the external thread 38 of the screw 36.
- the rotary axis carrier 22 is aligned via a centering pin 39 to the output shaft.
- a substantially radially extending support disk 40 is secured to the output shaft side against which a spring element 42 designed as a wave spring presses, which is arranged in a support ring 44 which is fixedly secured to a rear side of the crown wheel carrier 14 i. Accordingly, the rotary axis carrier 22 and thus the double gears 26 is axially biased toward the crown gear 14 and thus to the drive gear 16, which causes the teeth are pressed into each other, so that a game between the teeth is avoided.
- the rotary axle carrier 22 slides on a radially inner support ring 46, which has a rectangular cross-section and rests axially and radially inwardly against a designed as a ball bearing radial bearing 48.
- a disc 50 On the axially opposite side of the radial bearing 48 is a disc 50 which is welded to the rotary axis carrier 22.
- the inner ring of the radial bearing 48 is arranged on a control body 52, which is axially displaceable.
- the actuator 52 is as a locker! formed with internal thread and is secured against rotation on an inner spindle 54 arranged with a cross into the internal thread external thread, which is rotatable via an actuator 56.
- the actuator 56 has an axial flux motor 58, whose output shaft 60 is rotatably coupled to the spindle 54 rotatably.
- a circuit board 64 with a linear sensor 66 is arranged, which corresponds to a magnet 68 which is arranged on a support member 70 fixed to the adjusting body 52 opposite to the sensor 66.
- the adjusting body 52 has a radially extending annular extension 72, abut against the axially on both sides as a needle bearing designed thrust bearing 74, 76.
- the first of the two thrust bearings 74 lies with its axially opposite side against the radially extending part of the support ring 46, while the second thrust bearing 76 abuts against a thrust washer 78, which is arranged via a spring element 80 which is arranged in a ut 81 of the rack carrier 34, in the direction of the thrust bearing 76 and thus is charged to the extension 72.
- annular radially extending extension 72 is formed at a projecting beyond the adjusting body 52 in the direction of the camshaft end against the axially on both sides in each case a thrust bearing 84, 86 in the form of needle bearings.
- thrust bearings 84, 86 At the respective opposite axial sides of the thrust bearings 84, 86, these abut against thrust washers 88, 90, of which the first thrust washer 88 abuts with its first axial bearing 84 opposite side against the fixed to the axis of rotation support 22 disc 50 and the second thrust washer 90 via a is arranged in a groove 92 of the rotary axis carrier 22 arranged spring element 94 in the direction of the thrust bearing 86 is biased.
- the thrust bearing 84, 86 is clamped against the disc 50 and thus secured in position.
- the movement of the drive wheel 10 via the drive gear 16 and the drive gear 16 due to the engagement of the racks 32 stationary double gears 26 is transmitted to the rotary axis carrier 22 and thus to the output shaft.
- the rack carrier 34 which is fixedly connected to the support ring 46, rotated.
- the rotational axis support 22 is also radially by the radial bearing 48 and axially by the thrust bearing 84, 86 stored.
- the inner spindle 54 and the actuator 52 do not move.
- the inner spindle 54 is rotated via the Axialmannmotor 58.
- the actuator body is the entire unit consisting of radial bearings 48 support ring 46, thrust bearing 74, 76 and rack carrier 34 moves axially.
- This movement initially has an axial movement of the racks 32 and consequently a rotational movement of the double gears 26 result, which roll on the drive gear 16, whereby a relative movement between the drive gear 16 and axis of rotation support 22, and thus between the drive wheel 10 and output shaft.
- a phase adjustment is performed.
- the size of this phase adjustment can be detected via the signal of the sensor 66, since the axial movement of the actuator 52 is followed by an axial movement of the magnet 68, which causes a signal change on the sensor 66, which is proportional to the displacement.
- the rotational movement also causes centrifugal forces on the double gears 26, which are thus pressed radially outward, thereby additionally the teeth of the double gears 26 are pressed into the corresponding profile-shifted teeth of the racks 32 to prevent play in the engagement area.
- the described device for phase adjustment has a long service life, since the mechanical load of the actuator is minimized because it is rotationally decoupled.
- the life increases by reducing the wear, since the two thrust bearing 74, 76, 84, 86, the introduced by the camshaft alternating moments, which are converted via the double gears 26 in axial alternating forces between the axis of rotation support 22 and the rack carrier 34 record.
- the thrust bearing pair 74, 76 the forces of the rack carrier 34 are transmitted to the actuator body 52.
- These forces are absorbed by the inner spindle 54, which is supported via the thrust bearing pair 84, 86 on the rotary axis carrier 22. Accordingly, no axial forces must be absorbed outside of the transmission.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Transmission Devices (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102012104921A DE102012104921A1 (de) | 2012-06-06 | 2012-06-06 | Vorrichtung zur Phasenverschiebung des Drehwinkels eines Antriebsrades zu einer Abtriebswelle |
PCT/EP2013/059476 WO2013182364A1 (de) | 2012-06-06 | 2013-05-07 | Vorrichtung zur phasenverschiebung des drehwinkels eines antriebsrades zu einer abtriebswelle |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2859197A1 true EP2859197A1 (de) | 2015-04-15 |
Family
ID=48325723
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP13720953.2A Withdrawn EP2859197A1 (de) | 2012-06-06 | 2013-05-07 | Vorrichtung zur phasenverschiebung des drehwinkels eines antriebsrades zu einer abtriebswelle |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2859197A1 (de) |
DE (1) | DE102012104921A1 (de) |
WO (1) | WO2013182364A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017114176B3 (de) | 2017-06-27 | 2018-09-20 | Schaeffler Technologies AG & Co. KG | Elektrischer Nockenwellenversteller zur variablen Einstellung der Ventilsteuerzeiten einer Brennkraftmaschine |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3224423A (en) * | 1965-06-03 | 1965-12-21 | John L Ostborg | Valve timing control system for supercharged automotive engine |
GB2202917A (en) | 1987-03-17 | 1988-10-05 | Ford Motor Co | Variable phase shift mechanism |
DE102008055837A1 (de) * | 2008-11-04 | 2010-05-06 | Schaeffler Kg | Nockenwellenversteller mit Radialschieber |
DE102008060219B4 (de) | 2008-12-04 | 2011-07-14 | Pierburg GmbH, 41460 | Vorrichtung zur Phasenverschiebung des Drehwinkels eines Antriebsrades zu einer Abtriebswelle |
DE102011103373A1 (de) * | 2011-06-03 | 2011-12-01 | Erkan Agackiran | Verstellgetriebe für die relative Drehwinkelverstellung |
-
2012
- 2012-06-06 DE DE102012104921A patent/DE102012104921A1/de not_active Withdrawn
-
2013
- 2013-05-07 WO PCT/EP2013/059476 patent/WO2013182364A1/de active Application Filing
- 2013-05-07 EP EP13720953.2A patent/EP2859197A1/de not_active Withdrawn
Non-Patent Citations (1)
Title |
---|
See references of WO2013182364A1 * |
Also Published As
Publication number | Publication date |
---|---|
WO2013182364A1 (de) | 2013-12-12 |
DE102012104921A1 (de) | 2013-12-12 |
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