EP2905434A1 - Déphaseur oscillant doté d'une soupape hydraulique pour arbre à cames - Google Patents

Déphaseur oscillant doté d'une soupape hydraulique pour arbre à cames Download PDF

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Publication number
EP2905434A1
EP2905434A1 EP14198646.3A EP14198646A EP2905434A1 EP 2905434 A1 EP2905434 A1 EP 2905434A1 EP 14198646 A EP14198646 A EP 14198646A EP 2905434 A1 EP2905434 A1 EP 2905434A1
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EP
European Patent Office
Prior art keywords
port
working port
working
tank
hydraulic valve
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
Application number
EP14198646.3A
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German (de)
English (en)
Other versions
EP2905434B1 (fr
Inventor
Bernd Last
Gordon NEUDÖRFER
Udo Diederichs
Matthew Bradfield
Melissa Mei König
Kenneth Parker
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Hilite Germany GmbH
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Hilite Germany GmbH
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Publication date
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Publication of EP2905434A1 publication Critical patent/EP2905434A1/fr
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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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • 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
    • F01L1/3442—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 hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F01L2001/3443—Solenoid driven oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values

Definitions

  • the invention relates to a Schwenkmotornockenwellenversteller with a hydraulic valve having two working ports.
  • the DE 10 2006 012 733 B4 and the DE 10 2006 012 775 B4 already relate to a Schwenkmotornockenwellenversteller with a hydraulic valve having two working ports. These two working ports each have axially adjacent to each other a standard opening and an opening for utilizing pressure peaks due to camshaft alternating torques.
  • a hydraulic pressure can be conducted from a supply connection to the work connection to be loaded, while the work connection to be relieved is guided to a tank connection.
  • the hydraulic valve is designed as a multi-port multi-position valve in cartridge design. In the carrier or central pin check valves are used on the inside, which are designed as band-shaped rings.
  • camshaft alternating torques are used to adjust the camshaft adjuster faster or with a relatively low oil pressure can.
  • the check valves open to utilize pressure spikes due to camshaft alternating torques and obscure the backflow preventive ports into the unloaded port.
  • an embodiment of the present invention provides a swing camshaft phaser that ensures that software can utilize camshaft cycle torques only under conditions where the torque is adequate and / or it is important to reduce flow consumption. If there is a two-stage stroke, and the low-lift camshaft alternating torque is not adequate, the software can position the piston to utilize part of the camshaft alternation torque while passing oil into the tank for faster adjustment.
  • FIG. 1 shows in a circuit diagram a by means of an electromagnet 17 against a spring force of a spring 21 operable hydraulic valve 3 according to an exemplary embodiment of the present invention, which is proportionally controlled.
  • a Schwenkmotornockenwellenversteller 4 is pivotable.
  • the angular position between the crankshaft and the camshaft can be changed during the operation of an internal combustion engine.
  • the opening and closing times of the gas exchange valves are shifted so that the internal combustion engine performs optimally at the respective load and speed.
  • the Schwenkmotornockenwellenversteller 4 allows a continuous adjustment of the camshaft relative to the crankshaft.
  • a first working port A and a second working port B go to the Schwenkmotornockenwellenversteller 4 from.
  • the hydraulic valve 3 has four ports and five main switch positions and can thus also be referred to as a 4/5-way valve with a locking middle position 7.
  • the valve has in principle seven states, but the switch positions 7, 7a and 7b are used to maintain the relative position of the rotor to the stator, with the switch positions 7a and 7b leaving oil in ports B and A, respectively, as required to compensate for system leakage is.
  • the oil guide changes to shift positions, the flow opening of the valve is variable by incremental positioning in a shift state.
  • the hydraulic valve 3 In order to pivot the Schwenkmotornockenwellenversteller 4 in the first direction of rotation 1, the hydraulic valve 3 is in one of the two switching positions 16 or 19, which are represented by the two boxes to the right of the locking center position 7. In the drawing figure 1, the hydraulic valve 3 is moved in the switching position 19 when the hydraulic valve 3 undergoes the full stroke movement by the actuator. In this case, pressure chambers 6 associated with this direction of rotation 1 are pressurized by the first working port A (which comes from the supply port P).
  • the second working port B associated pressure chambers 5 are relieved.
  • the second working port B is performed in switch position 19 via a tank connection T to a tank 20.
  • the pressure chambers 6 are acted upon by the first working port A coming from the supply port P pressure, but the second working port B is blocked against the tank port T.
  • the first working port A associated pressure chambers 6 are relieved.
  • the first working port A is led to the tank 20 via the tank connection T.
  • the pressure chambers 5 are acted upon by the second working port B with a pressure coming from the supply port P, but the first working port A is blocked against the tank port T.
  • a connection of the supply connection P with the second working connection B is present in the switching position 7a, whereas the first working connection A is blocked against the tank connection T.
  • switching position 7a prevents interaction between the inner web of the piston and the web of the cartridge or the central valve pin, that the first working port A opposite to the supply port P is opened. Therefore, in the switching position 7a, it is prevented that the first working port A is opened to the tank port T as well as to the supply port P.
  • switching position 7b is a connection of the supply port P with the first working port A, while the second working port B is blocked against the tank port T.
  • switching position 7b prevents interaction between the inner web of the piston with the web of the cartridge or the central valve pin, that the second working port B is open to the supply port P. Therefore, in the switching position 7b, it is prevented that the second working port B is opened to both the tank port T and the supply port P.
  • the switch positions 7a and 7b offer the advantage that the adjuster remains completely filled with oil at lower pump pressures. By blocking a working port against the supply port P, the supply port P can better fill the other working port.
  • the adjustment of the camshaft is accomplished by loading one side of the vanes by utilizing recirculated oil available as a result of camshaft alternating torques in conjunction with oil supplied from the supply port P. Pressure is relieved from the other side of the wings by returning oil to the loaded wings while simultaneously passing oil into the tank.
  • a hydraulic fluid volume flow coming from a check valve RSV-A assigned to the first working port A is made available to the supply port P and B.
  • an additional A port which does not contain a check valve, can be discharged via the tank connection T to the tank 20.
  • a hydraulic fluid volume flow coming from a check valve RSV-B assigned to the first working port A is made available to the supply port P and A. Furthermore, in the switching position 19, an additional B connection, which does not contain a check valve, can be discharged via the tank connection T to the tank 20.
  • the adjustment of the camshaft is accomplished by loading one side of the vanes by utilizing recirculated oil available as a result of camshaft alternating torques, in conjunction with oil supplied from the supply port P.
  • pressure from the other side of the vanes is relieved only by returning oil to the loaded vanes.
  • one of the first working port A is assigned in shift position 15
  • a hydraulic fluid volume flow coming from a check valve RSV-B assigned to the second working port B is made available to the supply port P and A. In switching positions 15 and 16, however, no connection of any connection with the tank 20 is made.
  • this additional volume flow from the working port A or B to be relieved is fed into the volumetric flow coming from an oil pump 12 at the supply port P.
  • This pump check valve RSV-P blocks the pressures in the hydraulic valve 3, so that peak pressures coming from the work connection A or B to be relieved can be made available to a larger proportion of the adjustment assistance than is the case with an open oil pump line 14a, 14b would.
  • FIG. 4 to FIG. 10 show exemplary structural embodiments of the hydraulic valve 3 in the seven switching positions 18, 15, 7a, 7, 7b, 16, 19 according to Fig. 1 ,
  • FIG. 4 shows the hydraulic valve 3 in the first switching position 18, in which the electromagnet 17 according to Fig. 1 a piston 22 of the hydraulic valve 3 does not move.
  • the stroke of the piston 22 is thus at zero.
  • the piston 22 is within a central bolt 27 against the force of as Helical compression spring running spring 21 slidably.
  • the electromagnet 17 facing the end 50 of the piston 22 is closed to produce a contact surface for an actuating plunger of the electromagnet 17, whereas the other end 52 of the piston 22 for receiving one end of the spring 21 is open.
  • the piston 22 is held in the central bolt 27 via a retaining ring 54.
  • the piston 22 has at its two ends outer webs 23, 24, which are guided relative to the central pin 27.
  • the two outer webs 23, 24 have partially over the webs flat flow surfaces 29, 30, so that along these flow surfaces 29, 30 from the ends of the central bolt 27 access to the tank port T is present.
  • the piston 22 is hollow and that axial connection bores for flow to the tank connection T are contained.
  • two narrow ribs or webs 31, 32 are provided, which run around the piston 22.
  • These circumferential ribs 31, 32 correspond to two annular webs 33, 34 extending radially inwardly from the central pin 27.
  • two axially outer annular webs 35, 36 are provided.
  • These four ring lands 33, 34, 35, 36 are formed by five inner ring grooves 37, 38, 39, 40, 41 are hollowed out of the central pin 27.
  • this five réelleringnuten 37, 38, 39, 40, 41 open five connecting holes 60, 62, 64, 66, 68, which are drilled through the wall of the central pin 27. Depending on the flow requirements more than one hole per ring groove are possible.
  • connection bores 60, 62, 64, 66, 68 form from the sides of the electromagnet 17 axially along the Bolt 27 comprises: a standard opening B associated with the second working port B, an opening B1 associated with the second working port B for utilizing camshaft alternating torques, the supply port P, an opening A1 associated with the first working port A, and an opening A associated with the first working port A for the use of camshaft alternating torques.
  • the axially inner openings A1, B1 are provided for a camshaft alternating torque utilization.
  • the axially inner openings A1, B1 have the band-shaped check valves RSV-A, RSV-B.
  • one of the band-shaped check valves RSV-A and RSV-B is inserted into an inner ring groove 40 or 38 radially inside the axially inner openings A1 and B1 of the central pin 27.
  • the band-shaped pump check valve RSV-P is still provided in an inner ring groove 39.
  • the pump check valve RSV-P has basically the same structure as the two check valves RSV-A, RSV-B. However, this pump check valve RSV-P may have a different response force.
  • the two central ribs 31, 32 are axially spaced from the two annular ribs 33, 34, so that hydraulic fluid can pass through the gap therebetween.
  • hydraulic fluid can pass through the gap between the foremost outer web 23 and the corresponding annular web 35 on the central pin 27.
  • the other outer bar 24 blocks the rearmost inner annular groove 41 or the standard opening A associated with the first working port A.
  • the outer bar 24 and the rearmost annular bar 36 overlap over a large sealing length.
  • FIG. 5 shows the piston 22 at a stroke of 0.4 mm.
  • Shift position 15 is very similar to shift position 18, except that the piston 22 has advanced to a position in which the first working port A by the interaction of web 24 with the bolt surface 98 against the tank port T is locked, whereby no connection from A to the flow surface 30 can be made.
  • the first working port A is increasingly opened to the tank port T. This allows both hydraulic fluid return from the first working port A to the second working port B and guiding the first working port A to the tank (that is, hydraulic fluid flow from the first working port A to the tank port T).
  • FIG. 6 shows the piston 22 at a stroke of 1.1 mm.
  • the hydraulic valve 3 is in the switching position 7a.
  • Shift position 7a is greatly similar in that switching position 15, as the first working port A is blocked by the interaction of web 24 with surface 98 against the tank port T.
  • the first working port A is blocked via the interaction of web 32 with web 34 against the second working port B.
  • FIG. 7 shows the piston 22 at a stroke of 1.7 mm.
  • the hydraulic valve 3 is in the locking middle position 7.
  • the supply port P is closed by the two ribs 31, 32.
  • the corresponding annular ridges 33, 34 in a correspondingly large extent.
  • the two working ports A, B are blocked due to the interaction of web 24 with the surface 98 and the interaction of web 23 with the surface 99 and against the tank drain T.
  • FIG. 7 shown locking middle position 7 is practically the holding position
  • the piston between this switching position and either the in FIG. 6 shown switching position 7a or in FIG. 8 move shown switching position 7b to compensate for hydraulic fluid leakage.
  • FIG. 8 shows the piston 22 at a stroke of 2.3 mm.
  • the hydraulic valve 3 is in the switching position 7b, and a second working port B is locked via the interaction of web 23 with the surface 99 against the tank port T.
  • switching position 7b of the second working port B is blocked by the interaction of web 31 with web 33 and against the first working port A.
  • FIG. 9 shows the piston 22 at a stroke of 3.0 mm.
  • the hydraulic valve 3 is in the switching position 16, and the second working port B is blocked by the interaction of web 23 with the surface 99 against the tank port T. Furthermore, short-term peak pressures are transmitted from the second working port B associated opening B1 through its check valve RSV-B due to the camshaft alternating torques.
  • the first working port A is pressurized by the supply port P, and pressure from the second working port B is returned (via port B1) from B to A.
  • FIG. 10 shows the piston 22 at a stroke of 3.4 mm.
  • this switching position 19 the two middle ribs 31, 32 axially spaced from the two annular ridges 33, 34, so that hydraulic fluid can pass through the gaps between them.
  • hydraulic fluid can pass through the gap between the rearmost outer web 24 and the corresponding annular web 36.
  • the other outer web 23 blocks the foremost inner annular groove 37 or the standard opening B associated with the second working port B.
  • the outer web 23 and the foremost annular web 35 overlap over a large sealing length. This can be done in This switching position 19 hydraulic fluid from the supply port P via the pump check valve RSV-P to the first working port A associated standard opening A arrive.
  • the second working port B is increasingly opened to the tank port T. This allows both hydraulic fluid return from the second working port B to the first working port A and guiding the second working port B to the tank (that is, hydraulic fluid flow from the second working port B to the tank port T).
  • the duty cycle (or current) may be limited to allowing feedback only (switch positions 15 and 16) when there is adequate cam torque to achieve desired phase rates , It may also be limited to the switch positions 15 and 16 when insufficient current is present in the engine oil system and further loading is undesirable.
  • the software allows the use of the shift positions 18 and 19 for phasing. High revolutions per minute also do not allow enough time to make good use of cam torque pulses, thus utilizing switch positions 18 and 19 can increase phase-up speeds at high revolutions per minute, if required.
  • the amount of flow opening to the tank port T and the valve lift positions in which the shift positions 18 and 19 begin can be tailored to the application.
  • the standard opening A or B and the opening A1 or B1 are combined to initially utilize camshaft alternating moments outside of the central pin 27 to the working port A and B, respectively.
  • ball check valves may be used instead of tape check valves.
  • the hydraulic valve ball check valves such as the DE 10 2007 012 967 B4 shows.
  • the ball check valves need not necessarily be installed in the central valve of a cartridge valve. It is also possible, for example, to use ball check valves in a rotor and to perform the piston as a central valve which is arranged coaxially and centrally within the rotor hub slidably.
  • valve may be provided in the flow direction in front of one or more or even all ports and filters that protect the running surfaces between the piston and the central valve.
  • a use of the camshaft alternating torques can be provided for both directions of rotation, in which case, however, is dispensed with one of the two bypass check valves RSV-A, RSV-B.
  • switch positions are possible. For example, it is possible to dispense with one or more positions or states or add one or more additional switch positions or states.
  • On the hydraulic valve can also be provided a further switching position, wherein oil is metered through a self-centering center lock A and B, with one side is relieved to centering.
  • the pin is relieved, allowing it to fall into the locking pin hole, locking the stage in the middle locking position.
  • Center lock is used for example in the DE 10 2004 039 800 and DE 10 2009 022 869.1-13 shown.
  • FIG. 2 shows a preferred piston 22 and is self-explanatory, especially in view of the above description.
  • the webs 31, 32 are provided in the form of a shark fin shape, as in FIG FIG. 3 showing an enlarged view of the web 32.
  • a preferred piston provides ridges which, for example, have a thickness of only 0.3 mm at their base, but taper at least on one side 90, so that they actually engage with the ridges 33, 34 on the surface 92 the central pin 27 cooperates, only have a thickness in the range of 0.1 mm to 0.3 mm.
  • FIG. 3 presents FIG. 3 an enlarged view of the web 32 ready. An enlarged view of the other land 31 would look very similar, but would give an inverted image with the tapered surface 90 on the opposite side.
  • one or more tapered ridges may be provided on piston 22 or on bolt 27 or both.
  • the web the webs only rejuvenated (rejuvenated) on one side or on both sides of the web.
  • FIG. 4 There is preferably an opening of 1.5 mm at the point P to B1, preferably an opening of 1.5 mm at the location of B1 to B, preferably an overlap of 3.0 mm at the point B to T, preferably one Opening of 1.1 mm at the point P to A1, preferably an overlap of 1.6 mm at the point A1 to A and preferably an opening of 0.4 mm at the point A to T.
  • FIG. 5 there is preferably an opening of 1.1 mm at the point P to B1, preferably an opening of 1.1 mm at the point B1 to B, preferably an overlap of 2.6 mm at the point B to T, preferably an opening from 0.7 mm at the point P to A1, preferably an overlap of 1.5 mm at the point A1 to A and preferably an overlap of 0.0 mm at the point A to T.
  • FIG. 6 There is preferably an opening of 0.4 mm at the point P to B1, preferably an opening of 0.4 mm at the location of B1 to B, preferably an overlap of 1.9 mm at the point B to T, preferably one Opening of 0.0 mm at the point P to A1, preferably an overlap of 0.8 mm at the Place A1 to A and preferably an overlap of 0.7 mm at location A to T.
  • FIG. 7 there is preferably an overlap of 0.2 mm at the point P to B1, preferably an overlap of 0.2 mm at the point B1 to B, preferably an overlap of 1.3 mm at the point B to T, preferably an overlap from 0.2 mm at the point P to A1, preferably an overlap of 0.2 mm at the point A1 to A and preferably an overlap of 1.3 mm at the point A to T.
  • FIG. 8 There is an opening of 0.0 mm at the point P to B1, preferably an overlap of 0.8 mm at the point B1 to B, preferably an overlap of 0.7 mm at the point B to T, preferably an opening of 0.4 mm at the point P to A1, preferably an opening of 0.4 mm at the point A1 to A and preferably an overlap of 1.9 mm at the point A to T.
  • FIG. 9 there is preferably an opening of 0.7 mm at the point P to B1, preferably an overlap of 1.5 mm at the point B1 to B, preferably an opening of 0.0 mm at the point B to T, preferably an opening from 1.1 mm at the point P to A1, preferably an opening of 1.1 mm at the point A1 to A and preferably an overlap of 2.6 mm at the point A to T.
  • FIG. 10 there is preferably an opening of 1.1 mm at the point P to B1, preferably an overlap of 1.6 mm at the point B1 to B, preferably an opening of 0.4 mm at the point B to T, preferably an opening from 1.5 mm at the point P to A1, preferably an opening of 1.5 mm at the Place A1 to A, and preferably overlap 3.0 mm at location A to T.
  • check valves may be configured as ball or plate check valves.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Check Valves (AREA)
  • Multiple-Way Valves (AREA)
EP14198646.3A 2014-02-06 2014-12-17 Déphaseur oscillant doté d'une soupape hydraulique pour arbreà cames Active EP2905434B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US14/174,594 US9341090B2 (en) 2014-02-06 2014-02-06 Oscillating-motor camshaft adjuster having a hydraulic valve

Publications (2)

Publication Number Publication Date
EP2905434A1 true EP2905434A1 (fr) 2015-08-12
EP2905434B1 EP2905434B1 (fr) 2017-09-27

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US (1) US9341090B2 (fr)
EP (1) EP2905434B1 (fr)
JP (1) JP6218129B2 (fr)
KR (1) KR101614777B1 (fr)
CN (1) CN104832239B (fr)

Cited By (4)

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Publication number Priority date Publication date Assignee Title
EP3530891A1 (fr) * 2018-02-21 2019-08-28 ECO Holding 1 GmbH Soupape hydraulique pour un dispositif de réglage de moteur oscillant d'un arbre à cames
EP3530892A1 (fr) * 2018-02-21 2019-08-28 ECO Holding 1 GmbH Soupape hydraulique pour un dispositif de réglage de moteur oscillant d'un arbre à cames
WO2020007709A1 (fr) * 2018-07-04 2020-01-09 Delphi Automotive Systems Luxembourg Sa Dispositif de commande d'un dephaseur d'arbre a cames
US11111826B2 (en) 2018-02-21 2021-09-07 ECO Holding 1 GmbH Hydraulic valve for a cam phaser

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DE112018000447T5 (de) * 2017-01-19 2019-10-10 Denso Corporation Ventiltimingeinstellvorrichtung
DE102018126302A1 (de) * 2018-01-30 2019-08-01 ECO Holding 1 GmbH Schwenkmotorversteller für eine Nockenwelle und Nockenwellenanordnung mit einer Nockenwelle und einem Schwenkmotorversteller
US11174760B2 (en) * 2018-12-11 2021-11-16 Delphi Technologies Ip Limited Camshaft phaser

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JP2015148229A (ja) 2015-08-20
CN104832239A (zh) 2015-08-12
CN104832239B (zh) 2017-12-15
KR101614777B1 (ko) 2016-06-03
EP2905434B1 (fr) 2017-09-27
US9341090B2 (en) 2016-05-17
US20150218976A1 (en) 2015-08-06
JP6218129B2 (ja) 2017-10-25

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