EP1078148A1 - Dispositif pour le reglage de la position de phase d'un arbre - Google Patents
Dispositif pour le reglage de la position de phase d'un arbreInfo
- Publication number
- EP1078148A1 EP1078148A1 EP98929296A EP98929296A EP1078148A1 EP 1078148 A1 EP1078148 A1 EP 1078148A1 EP 98929296 A EP98929296 A EP 98929296A EP 98929296 A EP98929296 A EP 98929296A EP 1078148 A1 EP1078148 A1 EP 1078148A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- stator
- rotary piston
- valve
- teeth
- adjusting device
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000005540 biological transmission Effects 0.000 claims abstract description 26
- 239000012530 fluid Substances 0.000 claims abstract description 15
- 238000007789 sealing Methods 0.000 claims description 4
- 238000001514 detection method Methods 0.000 claims description 3
- 238000010310 metallurgical process Methods 0.000 claims description 2
- 239000000843 powder Substances 0.000 claims description 2
- 230000033001 locomotion Effects 0.000 abstract description 7
- 239000003921 oil Substances 0.000 description 28
- 239000007789 gas Substances 0.000 description 3
- 239000010687 lubricating oil Substances 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000003344 environmental pollutant Substances 0.000 description 2
- 239000000203 mixture Substances 0.000 description 2
- 230000002093 peripheral effect Effects 0.000 description 2
- 231100000719 pollutant Toxicity 0.000 description 2
- WJOHZNCJWYWUJD-IUGZLZTKSA-N Fluocinonide Chemical compound C1([C@@H](F)C2)=CC(=O)C=C[C@]1(C)[C@]1(F)[C@@H]2[C@@H]2C[C@H]3OC(C)(C)O[C@@]3(C(=O)COC(=O)C)[C@@]2(C)C[C@@H]1O WJOHZNCJWYWUJD-IUGZLZTKSA-N 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 238000010009 beating Methods 0.000 description 1
- 230000003197 catalytic effect Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 230000002706 hydrostatic effect Effects 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 238000002360 preparation method Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000005245 sintering Methods 0.000 description 1
- 239000003351 stiffener Substances 0.000 description 1
- 229940052996 vanos Drugs 0.000 description 1
- 230000000007 visual effect Effects 0.000 description 1
- 238000010792 warming 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/352—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 adjusting the phase position of a shaft
- the invention relates to an adjusting device for adjusting the phase position of a shaft, in particular a camshaft, according to the preamble of claim 1.
- valves of internal combustion engines are actuated by means of camshafts.
- the camshafts are driven by a drive shaft or by the crankshaft
- Transfer device set in rotary motion In order to be able to adapt the opening and closing times of valves to the current power output and / or engine speed, transmission devices with adjusters are used to adjust the phase position of the camshaft rotation alignment. Such adjusters enable the control times of the intake and / or exhaust valves to be influenced as required, so that above all the so-called overlap of the valve lift curves can be changed. It is currently preferred to use these rotary angle adjusters on the camshafts of the intake valves. To an increasing extent, however, the camshafts of the exhaust valves are also rotated at the same time.
- the adjuster preferably sits between the camshaft sprocket driven by a chain or a toothed belt and the camshaft.
- a different arrangement of the adjuster for example between the drive shaft and the drive shaft wheel, would also be possible.
- the relative rotational position between the camshaft sprocket and the camshaft can be varied within a predetermined angular range.
- a camshaft rotation range of 0 ° to 30 ° is preferably sufficient. For four-stroke engines in which the camshaft rotates at half the speed of the crankshaft, this range corresponds to a crankshaft
- Rotation range from 0 ° to 60 °. If both camshafts are adjustable at the same time, one speaks of a double variable camshaft control - 2 -
- the task of the adjuster is to determine the beginning and the end of the
- Valve stroke by the camshaft from “late” to “early” and vice versa This must be achievable over a wide engine speed range.
- the adjustment should preferably take place continuously and automatically.
- the advantages of correct adjustment are: more torque in the lower and middle speed range, less unburned residual gases at idle, improved idle, lower pollutant emissions, internal exhaust gas recirculation even at low speed, faster warming up of the catalytic converter and lower raw emissions after a cold start, special functions for the mixture adjustment during warm-up, reduced fuel consumption and lower engine noise.
- the invention particularly relates to adjusters which are operated hydraulically. If necessary, the adjuster is fed by an additional hydraulic pump. Preferably, however, a supply by the lubricating oil pump of the engine should suffice, which is particularly cost-effective and economical.
- a preferred adjuster should be able to set and hold any desired angle adjustment independently of the respective torque acting on the camshaft in a sufficiently short time. To do this, his work capacity or adjustment capacity must be correspondingly large.
- the required feed pressure and / or feed flow should be as low as possible.
- the building dimensions should be so small - 3 -
- the adjuster should preferably find space radially within the camshaft sprocket and short axially.
- a known adjuster uses an axially acting hydraulic piston for axially adjusting a sleeve.
- the sleeve comprises an internal and an external helical toothing, the two toothings being designed with opposite pitch.
- the external toothing of the sleeve engages in an internal toothing firmly connected to the camshaft sprocket and the internal toothing of the sleeve engages in a toothing connected to the camshaft.
- Axial adjustment of the sleeve achieves an angular adjustment between the camshaft sprocket and the camshaft. The adjustment range is limited due to the limited axial length.
- Actuation oil pressure is lower than the pinch pressure from the camshaft torque. In this way, the adjustment speed and the positioning accuracy are reduced. If this is to be avoided, the oil pump must be dimensioned much larger. This leads to higher energy losses, especially at high engine speeds.
- Another disadvantage of opposing helical gears is their complex manufacture.
- Another known adjuster is designed as a so-called wing adjuster.
- An outer housing part is firmly connected to the camshaft sprocket and comprises radially inwardly projecting areas which divide an annular space into subspaces. From a shaft part fastened to the camshaft, wings project radially outwards into a partial space. These wings are laterally and radially on the outside close to the subspace boundary, so that a rotary piston system is created.
- By supplying oil on one side of all vanes and draining oil on the other side of all vanes By supplying oil on one side of all vanes and draining oil on the other side of all vanes, a twist between the outer housing part and the shaft part can be achieved. By integrating the product of radius and working pressure over the
- a transmission and adjustment torque is determined for the wing surfaces.
- the maximum adjustment angle is reduced for a larger number of leaves, because the installation space is limited in the circumferential direction.
- the oil pressure of the lubricating oil pump is too low to generate a torque in the adjuster that is greater than the maximum camshaft torques.
- the peaks of the camshaft torques adjust the rotational position of the adjuster until the wings rest on a partial area boundary. Because the camshaft torques oscillate between positive and negative maxima, if the oil pressure is too low, the adjuster is deflected alternately in both directions of rotation from a desired rotational position until the wing comes into contact. This leads to heavy wear and unpleasant noises.
- a brake element is used, for example, which dampens the oscillating movements at low oil pressure.
- an oil supply valve, a rotational position detection and a control are designed such that deviations from a desired position are corrected by a corresponding valve actuation.
- the required oil pressure and, accordingly, the leakage-related oil consumption of this rotary lobe adjuster is high because the full pressure is also required to maintain a set rotational position or to transmit the camshaft torques.
- high peak values occur in the working spaces of the rotary lobe system. If the oil - 5 -
- the invention is based on the object of finding an adjuster which makes it possible to set any desired angle adjustment, even in the case of torques acting on the shaft, in particular in the torque curve transmitted from the valves to a camshaft. Its working capacity or its adjustment performance should be as large as possible even at low actuation fluid pressure.
- Such machines include at least a stator, a rotor or rotary piston, an output part and a valve device, the rotating parts of the
- Working space between the stator and rotor connects with high and low pressure.
- the number of teeth of the internal teeth of the stator is preferably one greater than that of the external teeth of the rotary piston.
- the individual components of a rotary piston machine can be manufactured with little effort, in particular by means of sintering.
- the ring-shaped machine parts and the work space take up little space.
- a stiffener according to the invention will preferably be arranged directly between the camshaft and the camshaft gear, - 6 -
- camshaft gear is in particular formed directly on the stator, so that only an extremely small additional space is required.
- the rotary position adjuster as a rotary piston machine or hydraulic motor with two ring-shaped rotary connections for supplying and discharging pressure fluid, in addition to the adjustment task required, for example, for camshafts, it can also perform a drive task in other applications.
- the adjuster according to the invention can be used both as an alignment or positioning unit and as a movement unit on rotating shafts.
- the rotational position or the rotational speed of a shaft which can be set in rotation by a drive shaft via a transmission device with at least one transmission wheel seated on a shaft, the rotational position or
- Rotation speed of the transmission wheel relative to the shaft with pressure fluid which can be supplied and removed via two ring-shaped rotary connections, changed.
- a fluid supply device with a control, a rotational position or rotational speed detection and at least one control valve is used for actuation, so that the setting of a desired rotational position or
- phase position of a camshaft is to be adjustable within a predetermined angular range, a sufficiently large one in particular becomes
- a rotary piston machine is now preferably provided, in which the rotation transmission from the rotary piston to the driven part takes place at a speed ratio of 1: 1.
- the valve device of the rotary piston machine then preferably comprises first and second radial valve channels which rotate with the driven part, in particular are formed thereon, and are evenly distributed over the circumference and which have internal connection areas of radial, evenly distributed over the circumference, WO 99/58821. ⁇ _ PCT / EP98 / 02759
- the outer connection areas of the stator channels open into the working area between the teeth of the internal teeth of the stator.
- the number of first or second valve channels differs from the number of stator channels by one channel each, so that the inner connection areas of the stator channels are connected to first valve channels in a first peripheral section and to second valve channels in a second peripheral section.
- the first valve channels are connected via an inner ring channel in the driven part to the one annular rotary connection and the second valve channels are connected to the other annular rotary connection via a space between the driven part and the rotary piston and an outer connecting channel in the driven part.
- Output part are formed.
- CH 676 490 the power or torque transmission can take place, for example, with a cardan shaft.
- Another transmission device mentioned in CH 676 490 comprises a coupling by means of bolts which are accommodated in suitable bores in one part and in bores with a diameter that is twice the eccentricity larger than the bolt diameter.
- the bolts roll along the edges of the larger bores.
- This bolt transmission also leads to an increased overall length in the axial direction.
- a preferred solution according to CH 676 490 due to the small overall length comprises an internal toothing on the rotary piston and an external toothing on the driven part.
- the axis of rotation of which can be stationary, interacting teeth with tooth contours are provided which are adapted to the present eccentricity.
- Tooth contour to a triangular shape can still be increased.
- the adjuster can thus only be adjusted in its rotational angle position by supplying oil, but not by applying torque from the outside. This ensures that high torque peaks of the camshaft cannot lead to high squeezing pressures in the working chambers of the hydraulic system and that for the
- Adjustment phases is available. This would reduce the amount of pressure oil required by the oil pressure pump, which reduces the demands on the pump and correspondingly its power loss.
- the adjuster is preferably arranged on the camshaft, but possibly on the drive shaft or on an additional transmission shaft.
- the preferred adjusters operate on the orbit principle of the high-torque hydraulic motors known in high-pressure hydraulics. This results in an extremely high work capacity.
- the rotation position adjustment is infinitely variable and has no angular restriction. Because of the interlocking tooth shapes and the self-locking formed in the preferred designs, no beating noises occur.
- the adjusters according to the invention are simple to manufacture and require only a few
- Fig. 1 shows a vertical section along the camshaft axis by an adjuster attached to the camshaft
- FIG. 2 shows a vertical section E-E according to FIG. 1
- FIG. 3 shows a vertical section D-D according to FIG. 1
- FIG. 4 shows a vertical section C-C according to FIG. 1;
- FIG. 5 shows a view of the camshaft end with the adjuster
- Fig. 1 shows an adjuster 1, which is arranged at a free end of a camshaft 2.
- the adjuster 1 is designed as a rotary piston machine and comprises at least one driven part 3, a rotary piston 4 and a stator 5.
- An external toothing 6 of the stator 5 forms the camshaft gear 6 ', which could possibly also be attached to the stator 5 as a separate part.
- a rotation between the stator 5 and the driven part 3 is achieved.
- a part of working chambers 7 between the stator 5 and the rotary piston 4 must be supplied with pressure fluid or oil under pressure and fluid must be let out of another part of working chambers 7.
- the Working chambers 7 are formed according to FIG. 2 between a stator internal toothing 5a and a circular piston external toothing 4a.
- the number of teeth of the stator internal toothing 5a is preferably twelve and that of the rotary piston external toothing 4a is eleven.
- the rotary movement of the rotary piston arises from the expansion of the working chambers 7 of the one due to the fluid feed
- a valve device is provided in order to control the fluid supply or to connect the working chambers 7 in a rotating manner with high or low pressure in such a way that the desired rotary piston movement occurs.
- the valve device comprises a channel system which rotates with the speed of the rotary piston 4 (FIG. 3) and a channel system which is fixedly connected to the stator 5 (FIG. 4). Because the rotating channel system of the embodiment shown is formed on the driven part 3, the driven part 3 is preferably shown by the
- Embodiment also the number of teeth of the rotary piston outer teeth 4a the same size as that of the rotary piston inner teeth 4b.
- the valve device comprises, with the output part 3, rotating, preferably formed on it, first 8 and second 9, radial valve channels evenly distributed over the circumference, which interact with inner connection areas 10 of radial, uniformly distributed over the circumference, stator channels 11, the outer ones Connection areas 1 2 between the teeth of the internal teeth 5a of the stator
- the number of first and second valve channels 8, 9 differs from the number of stator channels 1 1 by one channel each, so that the inner connection areas 10 of the stator channels 11 in a first circumferential partial area with first valve channels 8 and in a second Circumferential portion are connected to second valve channels 9.
- the inner ones and outer connection areas 1 0 and 1 2 of the stator channels 1 1 are formed as bores through a control disk 1 9 which is firmly connected to the stator 5.
- the stator channels 1 1 are preferably formed as depressions in the outer stator cover 20.
- the first valve channels 8 connect via an inner ring channel 13 in the driven part 3 and in the camshaft 2, as well as at least one first wheel bore 15a to an annular first rotary connection 14a.
- the second valve channels 9 close via an open space 1 6 between the driven part 3 and the rotary piston 4, an outer connection channel 1 7 in
- the stator housing comprises the outer stator closure cover 20, the control disk 19, the stator 5 and an inner stator closure cover 21.
- the stator housing is held together by screws 22.
- the rotary piston 4 is in the axial direction with the inside of the control disc 1 9 and the inner stator cover 21 in sliding contact.
- the stator housing is in
- the driven part 3 is connected to the camshaft 2 in a rotationally fixed manner, wherein preferably an axially arranged screw part 23 screwed to the camshaft 2 extends through an driven end part 24 and the driven part 3.
- the inner ring channel 1 3 is formed between the screw part 23 and the driven part 3.
- the stator housing is rotatably held in an annular groove between the driven end part 24 and the driven part 3 and sealed to the outside by means of a sealing unit 25.
- a guide ring 26 is inserted between the driven part and the camshaft end to form a rotary guide or seal for the inner stator closure cover 21.
- a rotational range limitation is preferably formed between the driven end part 24 and the outer stator cover 20. This includes, for example, two radially outwardly projecting end part abutment surfaces 27, each one
- Stator stop surface 28 is assigned so that the adjustment is only possible within a predetermined range of rotation angles.
- the arrangement of the rotation range limitation on the outer stator closure cover 20 shows with a simple visual check in which rotational position the camshaft 2 is.
- stator 5 with the internal toothing and / or the rotary piston 4 and / or the driven part 3 and / or the stator sealing covers 20, 21 are preferably produced in the powder metallurgical process. If necessary, a rotary piston 4 made of plastic is used. To reduce the weight are in
- Orbital piston 4 optionally formed axial cavities 29.
Abstract
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/EP1998/002759 WO1999058821A1 (fr) | 1998-05-12 | 1998-05-12 | Dispositif pour le reglage de la position de phase d'un arbre |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1078148A1 true EP1078148A1 (fr) | 2001-02-28 |
EP1078148B1 EP1078148B1 (fr) | 2003-05-14 |
Family
ID=8166954
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP98929296A Expired - Lifetime EP1078148B1 (fr) | 1998-05-12 | 1998-05-12 | Dispositif pour le reglage de la position de phase d'un arbre |
Country Status (13)
Country | Link |
---|---|
US (1) | US6386165B1 (fr) |
EP (1) | EP1078148B1 (fr) |
JP (1) | JP2002514705A (fr) |
KR (1) | KR20010043542A (fr) |
CN (1) | CN1292845A (fr) |
AT (1) | ATE240452T1 (fr) |
AU (1) | AU7911398A (fr) |
BR (1) | BR9815968A (fr) |
CA (1) | CA2330144A1 (fr) |
DE (1) | DE59808397D1 (fr) |
HU (1) | HUP0101674A3 (fr) |
SK (1) | SK16982000A3 (fr) |
WO (1) | WO1999058821A1 (fr) |
Families Citing this family (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AU2001250234A1 (en) * | 2000-05-13 | 2001-11-26 | Krupp Presta Ag | Adjusting device for adjusting the relative position of a shaft |
DE10027857A1 (de) * | 2000-06-06 | 2001-12-20 | Trochocentric International Ag | Getriebe mit Federglied |
JP3546002B2 (ja) * | 2000-08-29 | 2004-07-21 | 株式会社日立ユニシアオートモティブ | バルブタイミング制御装置の製造方法 |
DE10351223B4 (de) * | 2003-10-28 | 2010-02-18 | Hydraulik-Ring Gmbh | Nockenwellenverstelleinrichtung für Fahrzeuge, vorzugsweise für Kraftfahrzeuge |
CN100510324C (zh) * | 2004-03-17 | 2009-07-08 | 力帆实业(集团)股份有限公司 | 摩托车发动机配气凸轮调相装置 |
DE102004032141A1 (de) * | 2004-07-02 | 2006-02-23 | Ina-Schaeffler Kg | Nockenwellenversteller |
DE102004047817B3 (de) * | 2004-09-29 | 2005-12-08 | Gkn Sinter Metals Gmbh | Nockenwellenversteller für eine Verbrennungskraftmaschine |
DE102005041393A1 (de) * | 2005-09-01 | 2007-03-08 | Schaeffler Kg | Steuerventil für eine Vorrichtung zur Veränderung der Steuerzeiten einer Brennkraftmaschine |
GB2431977A (en) * | 2005-11-02 | 2007-05-09 | Mechadyne Plc | Camshaft assembly |
JP4640616B2 (ja) * | 2006-08-23 | 2011-03-02 | アイシン精機株式会社 | 弁開閉時期制御装置 |
WO2009130770A1 (fr) * | 2008-04-23 | 2009-10-29 | 日鍛バルブ株式会社 | Dispositif de commande de phase variable pour moteur d'automobile |
DE102008036182A1 (de) * | 2008-08-02 | 2010-02-04 | Schaeffler Kg | Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine |
DE102009008056A1 (de) * | 2009-02-09 | 2010-08-12 | Schaeffler Technologies Gmbh & Co. Kg | Steuerventile zur Steuerung von Druckmittelströmen |
CN102494114B (zh) * | 2011-12-20 | 2014-03-12 | 上海沛愉机械制造有限公司 | 一种链轮相位便捷调节方法 |
US8919309B2 (en) * | 2012-02-06 | 2014-12-30 | Braydon Jensen | Method and mechanism to confirm engine timing |
DE102014107459A1 (de) | 2014-05-27 | 2015-12-03 | Thyssenkrupp Presta Teccenter Ag | Ventilsteuersystem mit einer verstellbaren Nockenwelle |
CN107461228B (zh) * | 2017-06-22 | 2019-09-13 | 中车大连机车车辆有限公司 | 大功率柴油机凸轮轴相位调整方法 |
CN109281724B (zh) * | 2017-07-21 | 2022-07-26 | 舍弗勒技术股份两合公司 | 凸轮轴调节器和内燃机 |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4025243A (en) * | 1973-01-05 | 1977-05-24 | Gresen Manufacturing Company | Orbital device |
FR2641832B1 (fr) * | 1989-01-13 | 1991-04-12 | Melchior Jean | Accouplement pour la transmission de couples alternes |
US5507254A (en) * | 1989-01-13 | 1996-04-16 | Melchior; Jean F. | Variable phase coupling for the transmission of alternating torques |
DE3929621A1 (de) * | 1989-09-06 | 1991-03-07 | Bayerische Motoren Werke Ag | Vorrichtung zur relativen drehwinkelverstellung einer welle zu einem antriebsrad, insbesondere nockenwelle einer brennkraftmaschine |
DE3930157A1 (de) * | 1989-09-09 | 1991-03-21 | Bosch Gmbh Robert | Einrichtung zur verstellung der drehwinkelzuordnung einer nockenwelle zu ihrem antriebselement |
DE4116169A1 (de) * | 1991-05-17 | 1992-11-19 | Bosch Gmbh Robert | Vorrichtung zur verstellung der drehwinkelzuordnung einer nockenwelle zu ihrem antriebselement |
US5293845A (en) * | 1991-09-02 | 1994-03-15 | Toyota Jidosha Kabushiki Kaisha | Control mechanism for engine valve timing |
DE4237193A1 (de) * | 1992-11-04 | 1994-05-05 | Bosch Gmbh Robert | Verfahren zur Ansteuerung einer Einrichtung zum relativen Verdrehen einer Welle und Einrichtung zum relativen Verdrehen der Welle einer Brennkraftmaschine |
DE19645688C2 (de) * | 1996-11-06 | 2002-09-26 | Ina Schaeffler Kg | Vorrichtung zum Verändern der Steuerzeiten einer Brennkraftmaschine |
EP0911492B1 (fr) * | 1997-10-21 | 2002-03-06 | TCG UNITECH Aktiengesellschaft | Dispositif pour modifier la phase angulaire d'un arbre à cames de moteur à combustion interne |
DE69818946T2 (de) * | 1997-11-21 | 2004-05-13 | Mazda Motor Corp. | Vorrichtung zur Steuerung der Drehphase |
US6267089B1 (en) * | 1999-09-24 | 2001-07-31 | Ina Walzlager Schaeffler Ohg | Appliance for modifying the timing of gas-exchange valves of an internal combustion engine, in particular hydraulic camshaft adjustment device of rotary piston type |
-
1998
- 1998-05-12 EP EP98929296A patent/EP1078148B1/fr not_active Expired - Lifetime
- 1998-05-12 WO PCT/EP1998/002759 patent/WO1999058821A1/fr not_active Application Discontinuation
- 1998-05-12 AT AT98929296T patent/ATE240452T1/de not_active IP Right Cessation
- 1998-05-12 HU HU0101674A patent/HUP0101674A3/hu unknown
- 1998-05-12 JP JP2000548594A patent/JP2002514705A/ja active Pending
- 1998-05-12 KR KR1020007012654A patent/KR20010043542A/ko not_active Application Discontinuation
- 1998-05-12 DE DE59808397T patent/DE59808397D1/de not_active Expired - Fee Related
- 1998-05-12 CN CN988140292A patent/CN1292845A/zh active Pending
- 1998-05-12 US US09/700,085 patent/US6386165B1/en not_active Expired - Fee Related
- 1998-05-12 SK SK1698-2000A patent/SK16982000A3/sk unknown
- 1998-05-12 CA CA002330144A patent/CA2330144A1/fr not_active Abandoned
- 1998-05-12 AU AU79113/98A patent/AU7911398A/en not_active Abandoned
- 1998-05-12 BR BR9815968-2A patent/BR9815968A/pt active Search and Examination
Non-Patent Citations (1)
Title |
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See references of WO9958821A1 * |
Also Published As
Publication number | Publication date |
---|---|
SK16982000A3 (sk) | 2001-04-09 |
AU7911398A (en) | 1999-11-29 |
WO1999058821A1 (fr) | 1999-11-18 |
BR9815968A (pt) | 2001-10-23 |
ATE240452T1 (de) | 2003-05-15 |
KR20010043542A (ko) | 2001-05-25 |
HUP0101674A2 (hu) | 2001-08-28 |
US6386165B1 (en) | 2002-05-14 |
CA2330144A1 (fr) | 1999-11-18 |
JP2002514705A (ja) | 2002-05-21 |
DE59808397D1 (de) | 2003-06-18 |
EP1078148B1 (fr) | 2003-05-14 |
CN1292845A (zh) | 2001-04-25 |
HUP0101674A3 (en) | 2002-01-28 |
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