US20150322825A1 - Hydraulic camshaft adjuster with centre locking and adjustable locking play - Google Patents

Hydraulic camshaft adjuster with centre locking and adjustable locking play Download PDF

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Publication number
US20150322825A1
US20150322825A1 US14/406,508 US201314406508A US2015322825A1 US 20150322825 A1 US20150322825 A1 US 20150322825A1 US 201314406508 A US201314406508 A US 201314406508A US 2015322825 A1 US2015322825 A1 US 2015322825A1
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United States
Prior art keywords
rotor
stator
locking pin
cover
camshaft adjuster
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.)
Abandoned
Application number
US14/406,508
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English (en)
Inventor
Michael Busse
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schaeffler Technologies AG and Co KG
Original Assignee
Schaeffler Technologies AG and Co KG
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Filing date
Publication date
Application filed by Schaeffler Technologies AG and Co KG filed Critical Schaeffler Technologies AG and Co KG
Publication of US20150322825A1 publication Critical patent/US20150322825A1/en
Abandoned legal-status Critical Current

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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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34459—Locking in multiple positions
    • 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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34463—Locking position intermediate between most retarded and most advanced positions
    • 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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34466—Locking means between driving and driven members with multiple locking devices
    • 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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34469—Lock movement parallel to camshaft axis
    • 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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34476—Restrict range locking means

Definitions

  • the present invention relates to a hydraulic camshaft adjuster for an internal combustion engine of a motor vehicle, such as a passenger car or a truck, including a stator, which is drivable by the internal combustion engine, such as via a traction mechanism drive, and including a rotor, which is connectable to a camshaft, the rotor being detachably fixed to the stator with the aid of at least one pin-like locking pin in a center position rotatably fixedly counter to a first direction of rotation, the locking pin being designed to retract into and extend out of a first slotted gate in a first axial direction, which is defined by the rotation axis of the stator and/or the rotor.
  • a rotor which includes radially extending vanes, is situated in a stator and divides chambers in the stator into two opposite working chambers with the aid of the vanes.
  • a pressure medium may be applied to the working chambers using a hydraulic system, when pressure is applied to one working chamber, pressure medium being displaced from the opposite working chamber.
  • the rotor is then adjusted with respect to the stator in one direction of rotation as a function of the pressure application to the working chambers. Since the rotor is connected to the camshaft and the stator to the crankshaft, the rotation angle of the camshaft with respect to the crankshaft also changes.
  • either the alternating torques acting upon the camshaft may be used, the pressure medium being displaced from one working chamber into the other working chamber by the alternating torques acting upon the camshaft, this procedure also being referred to as CTA (Camshaft Torque Actuated), or a pressure may be applied to the working chambers by an external pressure medium supply, and the pressure medium may be removed from the opposite working chamber into a pressure medium reservoir, this procedure also being referred to as OPA (Oil Pressure Actuated).
  • CTA Camshaft Torque Actuated
  • OPA Ole Pressure Actuated
  • the much smaller externally supplied pressure medium flow in the adjustment according to the CTA principle is required exclusively to compensate for the leakage losses of the adjuster, since the pressure medium is displaced from one working chamber into the other working chamber to increase the volume and reduce the size of the working chambers.
  • much higher adjustment speeds may be reached with the aid of an adjustment according to the CTA principle in the case of high alternating torques acting upon the camshaft than is possible in an adjustment according to the OPA principle.
  • a small pressure medium flow is generally desirable, since the hydraulic system as a whole may thus be provided with a smaller design.
  • a camshaft adjusting device of this type is known from DE 10 2006 045 005 A1, with the aid of which the angular position of a camshaft with respect to a crankshaft may be adjusted.
  • the camshaft adjusting device described therein includes a hydraulic system having a multi-way valve for applying pressure to multiple working chambers, in which a pressure is variably applied to the working chambers as a function of the position of the valve body in the multi-way valve, and the camshaft is subsequently adjusted with respect to the crankshaft in the different directions of rotation.
  • a two-sidedly acting check valve including two spring-loaded closure elements, is furthermore provided in the valve body of the multi-way valve, with the aid of which a flow connection between the working chambers is established in certain positions of the valve body.
  • An external pressure application to the working chambers as well as a pressure compensation between the working chambers are possible in certain positions of the valve body, due to the provided check valve in connection with the multi-way valve.
  • the disadvantage of an approach of this type is that the check valve itself requires a complex mounting procedure and is itself formed by spring-loaded valve bodies, which may be excited to vibrations under unfavorable conditions.
  • a pressure medium-actuatable camshaft adjusting device for an internal combustion engine is known from DE 10 2010 022 896 A1, which includes at least two oppositely acting working chambers of a pressure medium pump, a pressure medium reservoir and a housing which includes a multi-way valve and has multiple working chambers, the pressure medium pump and openings assigned to the pressure medium reservoir, through which an inflow and/or outflow of the pressure medium is facilitated, a valve body being used, which blocks or enables the flow of the pressure medium through the openings in the housing with the aid of control edges abutting the housing as a function of the position, and including a check valve device which facilitates the flow of the pressure medium assigned to the valve body from the working chamber into the other working chamber and vice versa.
  • This publication relates to the fact that the valve body includes at least two pressure medium lines, which are each fluidically connectable to one of the working chambers, and the check valve device is formed by spring steel sheets closing the pressure medium lines.
  • a switchable device for supplying pressure is also known from DE 10 2010 024 026 A1.
  • a switchable device for supplying pressure to at least one consumer of an internal combustion engine is described, in particular for supplying pressure to a camshaft adjuster. It includes a displaceable element situated in a cavity, which is, in particular, a piston, as well as an energy store cooperating with the displaceable element, which is, in particular, a spring element, the displaceable element being displaceable against the force of the energy store from a first end position into a second end position by applying pressure to a reservoir with the aid of a pressure medium.
  • a fault-free operation of the switchable device for supplying pressure is ensured even at low oil pressures or at low engine speeds, in that the energy store is situated in an interior in which underpres sure is set with the aid of a vacuum pump at least during the displacement of the displaceable element from the first end position into the second end position.
  • the aforementioned problem may be resolved by the fact that an axial locking is carried out between the inner rotor and a laterally situated locking cover in the camshaft adjuster. At least one locking action is carried out in one of the “retard” or “advance” end stop positions.
  • the locking play may be adjusted relatively problem-free by correspondingly positioning the inner rotor with respect to the outer rotor before mounting the camshaft adjuster. On the one hand, this play may not be too large, since unwanted noises will otherwise occur; on the other hand, it may also not be too small, since the locking pin, which may also be referred to as the locking rod or locking piston, may otherwise no longer reliably engage or disengage.
  • V-shaped locking gates for the purpose of making the locking play adjustable, namely by radially shifting the cover.
  • the locking play is adjustable, but the location of the center locking position itself is also determined by this adjustment.
  • a radial shifting of the cover causes an additional imbalance on the camshaft adjuster, which, however, is to be avoided.
  • the locking play in particular, is to be adjustable, negative effects are, however, to be avoided.
  • the locking play should also be easier to adjust than before.
  • An object is therefore to provide an improvement for hydraulic camshaft adjusters, as well as to improve an internal combustion engine as such.
  • the present invention provides a generic hydraulic camshaft adjuster by the fact that a second locking pin is retractable into a second slotted gate in a second axial direction, which is parallel to the first axial direction but in a different direction, so as to secure the rotor relative to the stator in a center position counter to a second direction of rotation, which is in a different direction from the first direction of rotation, and is extendable from the second slotted gate.
  • the rotor is rotatably supported relative to the stator when the first locking pin is not in a form-locked fit with the slotted gate. It is similarly advantageous if the rotor is rotatable relative to the stator in an opposite direction when the second locking pin is not in a form-locked fit with the second slotted gate.
  • first locking pin and the second locking pin are extendably supported in the rotor.
  • a form-locked fit may be easily established between the first locking pin and a first slotted gate or between the second locking pin and the second slotted gate.
  • the blocking of a rotary motion of the rotor relative to the stator in a first direction of rotation or in a second direction of rotation may then be efficiently ensured.
  • first locking pin is extendable from a first front surface of the rotor and the second locking pin is extendable from a second front surface of the rotor, which is situated on the other side of the rotor.
  • the locking pin it is, of course, also possible for the locking pin to extend from the stator into a slotted gate of the rotor, although the extension out of the rotor is more advantageous.
  • the functions of the determination of the center locking position and the adjustment of the locking play may be separated from each other if the first slotted gate is formed in a first cover rotatably securable on the stator, and/or the second slotted gate is formed in a second cover rotatably securable on the stator. It is also possible, in principle, for the slotted gate to be situated in the rotor, if the locking pin is retractably and extendably supported in the cover or in the stator. The slotted gate may also be situated in the stator if the locking pin is retractably and extendably supported in the rotor or the cover.
  • stator is situated axially between the first cover and the second cover.
  • safety during operation may be optimized as needed if the first or second locking pin is separated from a cartridge by a spring in the axial direction, and if the cartridge, the spring and the locking pin are preferably at least partially situated in a hole oriented in the axial direction, such as a blind hole or a through-hole in the manner of a bore.
  • the first cover and/or the second cover is/are fixable on the stator with the aid of at least one screw, preferably if one of the two covers has a threaded section for fastening the screw, the threaded section furthermore preferably being designed as a threaded cover which is rotatably fixedly mountable on the first or second cover, for example in the manner of a ring, or if it is an integral part of the first or second cover.
  • multiple, evenly distributed screws are used, in particular those having a screw head on one end and a threaded section in at least one area of the other end.
  • threaded rods without screw heads, rivets and/or bolts.
  • the ability to shift the covers with respect to each other when the screw is inserted may be ensured if the screw projects through a kidney-shaped or fan-shaped recess, such as an elongated hole, in the first or second cover.
  • the present invention also relates to an internal combustion engine, which includes a camshaft and a camshaft adjuster controlling the camshaft, which is designed according to the present invention.
  • the locking gates are accommodated in two covers, the covers being rotatable with respect to each other during mounting and ensuring the adjustment of the center locking position and the adjustment of the locking play independently of each other.
  • the center locking is thus achieved in a hydraulic camshaft adjuster with the aid of two locking gates in the cover, a first locking gate being contained in a front cover and a second locking gate being contained in a rear cover, two locking units including a locking pin, a locking spring and a cartridge being accommodated in the rotor.
  • the locking units are installed in the rotor in an oppositely oriented manner.
  • the first locking pin engages with a first unpressurized locking gate and is pressed back into the rotor by oil pressure coming from a first oil bore or a first oil groove.
  • the second locking pin engages with an unpressurized second locking gate and is pressed back into the rotor by oil pressure coming from a second oil bore or a second oil groove.
  • the oil supply for both locking gates takes place via a separate oil line, separated from the oil supply for the oil chambers.
  • the camshaft adjuster is thus completely premountable, the cover screws then being not yet tightened, and the front cover being rotatably supported within the elongated holes in the stator and being rotatable into a desired position until the locking play is adjusted, only then this position being mechanically fixed from the outside.
  • a stop in the first locking gate determines the center locking position, since friction torques of the camshaft always press the rotor or the first locking pin in the retard direction, i.e., counterclockwise in the present case.
  • the rear cover is rotatable within the elongated holes formed in the rear cover. The rear cover is initially rotated in such a way that a stop in the second locking gate comes into contact with the locking pin.
  • the locking play may then be 0°. However, play values of 0.6° to 1.2°, preferably 0.8°, are preferably set.
  • the rear cover is subsequently rotated in the other direction until the desired total locking play is set.
  • the rear cover is also mechanically fixed.
  • the cover screws are tightened only at the end.
  • the threaded cover is tightened on the adjuster and clamps both covers to the stator.
  • FIG. 1 shows a perspective representation of the assembly of a hydraulic camshaft adjuster according to the present invention
  • FIG. 2 shows a view of the camshaft adjuster from FIG. 1 from the front, however including a translucent representation of a first, front cover;
  • FIG. 3 shows the view of the camshaft adjuster in FIGS. 1 and 2 from the rear, including a translucently represented second, rear cover;
  • FIG. 4 shows a singular representation of the rotor, including two locking devices situated therein and extendable in a different direction;
  • FIG. 5 shows a view of this camshaft adjuster in FIGS. 1 through 3 from the rear, i.e., in a representation as in FIG. 3 , however, unlike in this figure, including only one threaded cover.
  • FIG. 1 shows a first specific embodiment of a hydraulic camshaft adjuster 1 .
  • a camshaft adjuster 1 of this type uses a pressure provided by a fluid.
  • a fluid of this type may be oil and is conducted into different pressure chambers between a stator 2 and a rotor 3 .
  • FIG. 2 the pressure chambers are provided with reference numeral 4 .
  • Pressure chambers 4 are divided into a first pressure space and a second pressure space 7 with the aid of vanes 5 , which are fixedly situated in rotor 3 .
  • rotor 3 is radially situated within stator 2 .
  • a first, front cover 9 on the front side of rotor 3 is fastened to stator 2 , with the aid of preferably five screws 8 , which may also be referred to as cover screws.
  • Rotor 3 is connectable or connected to a camshaft.
  • Stator 2 has teeth 10 on its outside, which ensure a connection to a crankshaft of an internal combustion engine via a traction mechanism drive.
  • first slotted gate 11 is present in first cover 9 .
  • This first slotted gate 11 may also be referred to as a locking gate and is used to fix a position of rotor 3 relative to stator 2 , since first cover 9 is rotatably fixedly connected to stator 2 with the aid of screws 8 .
  • a first pin-like locking pin 12 which could also be referred to as a locking rod or locking piston, is extendably supported in rotor 3 in a first axial direction, so that it achieves a form fit, abutting on one side, with first slotted gate 11 when it is extended.
  • the first axial direction is oriented in parallel to a rotation axis 13 .
  • First locking pin 12 is part of a first locking device, which additionally also has a first locking spring 14 , as well as a first cartridge 15 , locking spring 14 being designed as a spiral spring and being situated upright between first locking pin 12 and first cartridge 15 and being in contact with them both. This is illustrated, for example, in FIG. 4 .
  • a second locking pin 16 exists, which, together with a second locking spring 17 and a second cartridge 18 , is part of a second locking device.
  • the two locking devices are continuously provided with the same design but are inserted in a different direction into rotor 3 , so that first locking pin 12 is extendable from a first front side 19 of rotor 3 , and second locking pin 16 is extendable from a second front side 20 of rotor 3 .
  • First front side 19 may also be referred to as the first front surface, just as second front side 20 may also be referred to as the second front surface.
  • First cartridge 15 and second cartridge 18 are situated within rotor 3 , as are first locking spring 14 and second locking spring 17 .
  • the two locking devices are situated in two different through-holes 21 .
  • the two locking devices may also be situated in a single through-hole 21 . Only two locking devices are provided here, which, however, does not prevent multiple locking devices, for example four or six locking devices, from being present. However, it is advantageous if this is limited to two locking devices.
  • hydraulic fluid such as oil
  • first oil bore 22 and a first oil groove 23 from an innermost radial area in first slotted gate 11 which may be referred to as a locking gate, for the purpose of forcing first locking pin 12 back into rotor 3 .
  • through-holes 21 are provided with radially inwardly running venting grooves 24 .
  • screws 8 project into stator 2 through through-holes designed as elongated holes 25 .
  • Elongated holes are also provided in a second cover 26 , which, however, are provided with reference numeral 27 . Screws 8 also project through these elongated holes 27 . Either the one elongated holes 25 or the other elongated holes 27 may be used.
  • a second slotted gate 28 which engages with second locking pin 16 , is situated in second cover 26 .
  • oil may also be supplied to second locking pin 16 via a second oil bore 29 and a second oil groove 30 .
  • first locking pin 12 establishes a form-locked fit with first slotted gate 11 upon reaching the center locking position
  • second locking pin 16 simultaneously establishes a form-locked fit with second slotted gate 28 , the form-locked surfaces or stops being situated opposite each other.
  • the form-locked fit between first locking pin 12 and first slotted guide 11 prevents the rotation of the rotor relative to the stator in one direction of rotation
  • the form-locked fit between second locking pin 16 and second slotted gate 28 prevents the rotation in the other direction.
  • the two directions of rotation are thus opposed to each other, once in the “retard” direction and once in the “advance” direction.
  • screws as is apparent in FIG. 1 , for example, have screw heads 31 on the one side, they have only a threaded area 32 on the other side, which establishes a pivot fit with a threaded section 33 of second cover 26 .
  • threaded section 33 is designed as a separate component from second cover 26 , namely as an independent threaded cover 34 .
  • Threaded cover 34 is in the shape of a ring.
  • Threaded cover 34 is rotatably immovably connected to second cover 26 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
US14/406,508 2012-07-06 2013-04-24 Hydraulic camshaft adjuster with centre locking and adjustable locking play Abandoned US20150322825A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102012211870.5 2012-07-06
DE102012211870.5A DE102012211870A1 (de) 2012-07-06 2012-07-06 Hydraulischer Nockenwellenversteller mit Mittenverriegelung und einstellbarem Verriegelungsspiel
PCT/EP2013/058418 WO2014005739A1 (de) 2012-07-06 2013-04-24 Hydraulischer nockenwellenversteller mit mittenverriegelung und einstellbarem verriegelungsspiel

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US20150322825A1 true US20150322825A1 (en) 2015-11-12

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US14/406,508 Abandoned US20150322825A1 (en) 2012-07-06 2013-04-24 Hydraulic camshaft adjuster with centre locking and adjustable locking play

Country Status (4)

Country Link
US (1) US20150322825A1 (de)
CN (1) CN104812996A (de)
DE (1) DE102012211870A1 (de)
WO (1) WO2014005739A1 (de)

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CN110998071A (zh) * 2017-08-08 2020-04-10 舍弗勒技术股份两合公司 具有机械和液压棘轮的液压凸轮轴调节器

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DE102015205162A1 (de) 2015-03-23 2016-03-31 Schaeffler Technologies AG & Co. KG Nockenwellenversteller
DE102017115724A1 (de) 2017-07-13 2018-05-17 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller
DE102017126169B4 (de) 2017-11-09 2019-08-29 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller
CN110761952B (zh) * 2018-07-26 2021-02-02 福建金风科技有限公司 风力发电机组转子盘车系统及其盘车模块
DE102018130094A1 (de) 2018-11-28 2020-05-28 Schaeffler Technologies AG & Co. KG Hydraulischer Nockenwellenversteller
DE102019123987A1 (de) * 2019-09-06 2021-03-11 ECO Holding 1 GmbH Verfahren zur Herstellung eines Nockenwellenverstellers

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CN102367749B (zh) * 2011-10-18 2013-03-27 奇瑞汽车股份有限公司 一种可变气门正时装置

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US10844756B2 (en) * 2017-08-08 2020-11-24 Schaeffler Technologies AG & Co. KG Hydraulic camshaft adjuster having a mechanical and a hydraulic ratchet

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DE102012211870A1 (de) 2014-01-09
CN104812996A (zh) 2015-07-29

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