EP3460209B1 - Ölsteuerventil zur steuerung eines nockenwellenverstellers mit einem kolben, der durch einen externen aktuator positioniert wird - Google Patents

Ölsteuerventil zur steuerung eines nockenwellenverstellers mit einem kolben, der durch einen externen aktuator positioniert wird Download PDF

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Publication number
EP3460209B1
EP3460209B1 EP18189919.6A EP18189919A EP3460209B1 EP 3460209 B1 EP3460209 B1 EP 3460209B1 EP 18189919 A EP18189919 A EP 18189919A EP 3460209 B1 EP3460209 B1 EP 3460209B1
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EP
European Patent Office
Prior art keywords
piston
valve
working port
hydraulic
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.)
Active
Application number
EP18189919.6A
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German (de)
English (en)
French (fr)
Other versions
EP3460209A1 (de
Inventor
Daniel Stanhope
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.)
Eco Holding 1 GmbH
Original Assignee
Eco Holding 1 GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from US15/831,078 external-priority patent/US10612430B2/en
Application filed by Eco Holding 1 GmbH filed Critical Eco Holding 1 GmbH
Publication of EP3460209A1 publication Critical patent/EP3460209A1/de
Application granted granted Critical
Publication of EP3460209B1 publication Critical patent/EP3460209B1/de
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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
    • 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
    • F01L1/34409—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 by torque-responsive means
    • 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
    • F01L2301/00—Using particular materials

Definitions

  • the invention relates to an oil control valve for a camshaft adjuster of an internal combustion engine, the piston being positioned by an external actuator.
  • Hydraulic valves for camshaft adjusters for internal combustion engines are well known in the art.
  • the hydraulic valve comprises a piston which is axially movable in a valve housing of the hydraulic valve and which controls a hydraulic application of the camshaft adjuster.
  • the valve housing is configured as a hollow cylinder.
  • the piston is also configured as a hollow cylinder.
  • the camshaft adjuster is controlled hydraulically by positioning the displaceable piston and corresponding opening and closing of connections that are configured in the valve housing.
  • the publication fonts DE 10 2013 104 573 A1 and DE 10 2013 104 575 A1 reveal a Hydraulic valve, which comprises a supply connection at a valve housing end, so that direct displacement of the piston accommodated in the valve housing and thus direct application of hydraulic fluid to the piston, which is supplied through the supply connection, can be provided.
  • the piston has a complex external geometry so that compressive forces are balanced to minimize the effect of pressure on the position of the piston.
  • Another hydraulic valve which includes a so-called center position lock, comes from the publication EP 2 966 272 A2 .
  • the piston has a complex external geometry, since additional locking connections are arranged in the valve housing of the hydraulic valve.
  • An object of the invention is to provide a hydraulic valve for a camshaft adjuster, which comprises a piston arrangement which comprises a piston which is axially movable in a central opening of a valve housing, and a first check valve and a second check valve that prevent an unintentional outflow of a through the piston assembly preventing hydraulic fluid flowing from an interior of the piston assembly in a first fluid flow through a first flow opening of the piston in the direction of a first working connection and a second fluid flow through a second flow opening of the piston in the direction of a second working connection.
  • the piston arrangement has a start position, a middle position and an end position. The hydraulic fluid can flow from the first working connection to the second working connection when the piston arrangement is in the start position, the hydraulic fluid cannot flow between the first
  • the working port and the second working port flow when the piston arrangement is in the central position, and the hydraulic fluid can flow from the second working port to the first working port when the piston arrangement is in the end position.
  • the first working connection and the second working connection are opened and closed as a function of a position of the piston arrangement.
  • a supply connection is arranged at one end of the hydraulic valve.
  • the check valves are arranged axially displaceably in the piston, one of the check valves being able to be placed against a supply or check valve tube arranged in the piston.
  • the piston assembly may include a machined piston.
  • the piston assembly can other piston parts made of plastic, such as. B. stamped or deep-drawn plastic, are made include.
  • the other parts that are made of plastic can be a supply tube and a flow disk.
  • the piston can be positioned like an electromagnetic actuator by external actuation.
  • a pressurized hydraulic fluid can enter one end of the hydraulic valve, where the resulting compressive force is balanced by a differential area of the piston, ie by different effective diameters.
  • the first check valve and the second check valve can allow hydraulic fluid to be returned by means of cam torque.
  • the hydraulic valve can be an oil control valve or an engine oil control valve.
  • the piston arrangement can have a first position or start position, a second position, a third position or middle position, a fourth position and a fifth position or end position.
  • the Hydraulic fluid flows from the first working port to the second working port when the piston arrangement is in the first position (start position) or the second position; the hydraulic fluid cannot flow between the first working port and the second working port when the piston arrangement is in the third position (Middle position), and the hydraulic fluid flows from the second working port to the first working port when the piston assembly is in the fourth position or the fifth position (end position).
  • the first working port and the second working port are opened and closed as a function of a position of the piston arrangement and a pressure across the first check valve and the second check valve.
  • the hydraulic valve can furthermore comprise a tank connection.
  • the tank connection is open when the piston assembly is in the first position (start position) or the fifth position (end position), and the tank connection is closed when the piston assembly is in the second position, the third position (middle position) or the fourth position is located.
  • the invention relates to an oil control valve for a camshaft adjuster of an internal combustion engine, the piston being positioned by an external actuator.
  • the pressure enters the end of the oil control valve where the resulting compressive force from the differential area of the piston, ie is compensated by different effective diameters of the piston.
  • the piston contains two plate check valves that allow oil to be returned by cam torque from A to B or B to A, depending on the piston position. In the middle position, the piston webs A and B lock to hold the camshaft adjuster position.
  • Fig. 1 shows a view of an oil control valve 100 for a camshaft adjuster of an internal combustion engine in the assembled state.
  • the oil control valve comprises a central valve housing 10, a spring 12, a calibration cap 14, a spring 16, a check valve 18, a flow disk 20, a supply filter 22, a locking ring 24, a piston assembly 26, a piston 30 with lands to block the flow of oil and grooves to permit the flow of oil, a check valve 32, a check valve 33, a supply tube 34, and a flow disc 35, a calibration stop 36 and a spring 38 , 33 are arranged axially in the piston 30 and have opposite opening directions.
  • check valves 32, 33 are arranged axially displaceably on the supply pipe 34, which has radial supply bores between the check valves.
  • Fig. 2 represents the oil control valve 100 with a stroke of 0 mm (start position). In the start position, the two plate check valves lead to the return of oil by cam torque from A to B.
  • A, B, P, T1 positioned in the middle of the valve housing 10
  • T2 positioned at the left end
  • Fig: 3 shows the oil control valve 100 with a stroke of 1.5 mm (central or holding position). In the central position, the piston webs A and B block to hold the camshaft adjuster position. In the center position there is no return and no ejection.
  • Fig. 4 represents the oil control valve 100 with a stroke of 3 mm (end position). In the end position, the two plate check valves lead to the return of oil by cam torque from B to A.
  • FIG. 13 shows a symbolic view of the oil control valve 100 in various positions.
  • the right-hand area of the symbolic view shown in FIG Fig. 5 is illustrated, establishes a flow of fluid through the oil control valve 100 according to a start position (first position) shown in FIG Fig. 2 is shown.
  • the middle area of the in Fig. 5 The symbolic view illustrated illustrates fluid flow through the oil control valve 100 according to a center position (second position) shown in FIG Fig. 3
  • the left area of the icon view, which is shown in Fig. 5 is illustrated, provides fluid flow through the oil control valve 100 according to an end position (third position) shown in FIG Fig. 4 is represented.
  • hydraulic fluid is applied to the second working connection B.
  • hydraulic fluid can flow from the first working connection A at least partially through a first connection opening 17 of the valve housing 10, a first throughflow opening 19 (A1) of the piston 30, the flow disk 35 and by opening the check valve 33 located furthest to the right, the hydraulic fluid can flow from a Interior 21 of piston 30 flow into first throughflow opening 13. From there, the hydraulic fluid flows through the second connection opening 15 into the second working connection B.
  • the additional part of the fluid that flows out of the first working connection A flows through the opening 17 and a first outlet channel 23 of the piston 30 into a third connection opening 25, which is assigned to a tank connection T1, directly next to the first connection opening 17 in the valve housing 10.
  • hydraulic fluid is applied to the first working connection A.
  • hydraulic fluid can flow from the second working connection B at least partially through the second connection opening 15, a second throughflow opening 31 (B1) of the piston 30 and by opening the check valve 32 located furthest to the left, the hydraulic fluid can flow into the interior 21 into the first throughflow opening 13 stream. From there, the hydraulic fluid flows through the first connection opening 17 into the first working connection A.
  • Fig. 6 10 shows an exemplary piston assembly 26.
  • Laser weld 702 is a 360 degree weld for holding piston 30 and calibration stop 36 in place and sealed against leakage.
  • Some of the parts may be made from stamped or deep drawn parts 706.
  • the supply pipe 34 and the flow disk 35 can be made in one piece from plastic.
  • the flow disk 35 is pressed lightly into the piston 30 to seal off the oil (press connection 708). It can be held by a welded stop.
  • FIG. 7 Figure 3 illustrates another exemplary piston assembly.
  • the piston assembly (sometimes referred to as a piston) includes an alternative piston that is easier to machine and easier to clean without a blind bore.
  • the piston 30 according to Fig. 7 is a hollow piston with two open ends.
  • a disk 40 is fixed in the piston 30 and seals the interior space 21 at the left end.
  • Fig. 8 shows a view of an oil control valve 1000 for a camshaft adjuster of an internal combustion engine according to a second embodiment of the invention in the assembled state.
  • the oil control valve comprises a central valve housing 10, a spring 12, a calibration cap 14, a spring 16, a check valve 18, a flow disk 20, a supply filter 22, a locking ring 24, a piston assembly 26, a piston 30 with lands to block the flow of oil and grooves to allow the flow of oil, check valves 32 and 33, a spring 38, a disc 902, a check valve disc 904 and a check valve tube 43.
  • This Oil control valve 1000 has an alternative piston assembly 26 that holds the check valves 32,33. The inside diameter of the piston 30 is easier to machine, thereby providing a less expensive piston assembly 26.
  • Fig. 9 , Fig. 10 , Fig. 12 and Fig. 13 set positions on either side of the "hold" position (not ejection) of Fig. 11
  • the positions shown in Fig. 9 and Fig. 13 are shown, represent the tank opening at both ends of the stroke. This process is particularly advantageous in four-cylinder applications, where feedback by cam torque is advantageous for an adjustment speed at low engine speed and oil pressure actuation is advantageous for an adjustment speed at high engine speed.
  • This function can be added to various piston designs.
  • Fig. 9 shows the oil control valve 1000 according to a second embodiment of the invention with a stroke of 0 mm (start or first position).
  • hydraulic fluid flows from a supply port P through a piston extension 41, which is guided in the calibration cap 14, the check valve tube 43, the first throughflow opening 13 of the piston and the second connection opening 15 to the second working connection B.
  • the right end of the check valve tube 43 is positioned in a recess 51 of the piston 30.
  • the plate check valve 33 opens for a return of oil by cam torque from A to B via the first connection opening 17, the first flow opening 19, the openings 45 of the check valve tube 43 (see dotted lines in FIG Fig. 9 ), the interior 21, the first throughflow opening 13 to the second connection opening 15.
  • connection A, B, P, T1 (positioned directly next to connection A in the valve housing 10), T2 (at the left end of the valve housing 10 positioned) is provided.
  • T1 is open, allowing fluid flow from A through a land 47 at the right end to the third connection port 25 and T1.
  • Fig. 10 shows the oil control valve 1000 according to a second embodiment of the invention with a stroke of 0.6 mm (second position).
  • the plate check valve 33 leads to the return of oil by cam torque from A to B.
  • the fluid flow to the third connection opening 25 and thus T1 is closed by the web 47 at the right end of the piston 30.
  • Fig. 11 shows the oil control valve 1000 according to a second embodiment of the invention with a stroke of 1.5 mm (middle or holding position). In this position, the piston webs 27, 29 A and B block to hold the camshaft adjuster position. There is no return in the center or hold position.
  • Fig. 12 shows the oil control valve 1000 according to a second embodiment of the invention with a stroke of 2.7 mm (fourth position). In the fourth position, the plate check valves 32 lead to the return of oil by cam torque from B to A. T2 is through a web 49 on left end of the piston 30 closed.
  • Fig. 13 shows the oil control valve 1000 according to a second embodiment of the invention with a stroke of 3.2 mm (end position).
  • hydraulic fluid flows from the supply port P through a piston extension 41, the check valve tube 43, the first throughflow opening 13 of the piston and the first Connection opening 17 to the first working port A.
  • the plate check valve 32 opens for the return of oil by cam torque from B to A via the second connection opening 15, the second flow opening 31, the check valve 32, the interior 21, the first flow opening 13 to the first connection opening 17.
  • T2 is open, allowing fluid to flow from B via land 49 at the left end to fourth connection port 37 and T2.
  • FIG. 10 shows a symbolic view of the oil control valve 1000 according to a second embodiment of the invention in various
  • the rightmost area of the Icon View that is shown in Fig. 14 is shown provides fluid flow through the oil control valve 1000 according to a first position shown in FIG Fig. 9
  • the area next to the rightmost area of the Icon View that is shown in Fig. 14 is shown provides fluid flow through the oil control valve 1000 according to a second position shown in FIG Fig. 10
  • the middle area of the icon view, which is shown in Fig. 14 is illustrated, provides fluid flow through the oil control valve 1000 according to a center position (third position) shown in FIG Fig. 11
  • FIG. 14 provides fluid flow through the oil control valve 1000 according to a fourth position shown in FIG Fig. 12
  • the leftmost area of the Icon View, which is shown in Fig. 14 is shown provides fluid flow through the oil control valve 1000 according to a fifth (end or final) position shown in FIG Fig. 13 is represented.
  • hydraulic fluid is applied to the second working connection B.
  • hydraulic fluid can flow from the first working connection A at least partially through the first connection opening and by opening the check valve 32 located furthest to the right, the hydraulic fluid can flow into the interior space in the first Flow through flow opening. From there, the hydraulic fluid flows through the second connection opening into the second working connection B.
  • the additional part of the fluid that flows out of the first working connection A flows through the opening into a third connection opening which is assigned to the tank connection T1.
  • the second position acts similarly to the start position.
  • hydraulic fluid is applied to the first working connection A.
  • hydraulic fluid can flow from the second working connection B at least partially through the second connection opening and by opening the check valve 32 located furthest to the left, the hydraulic fluid can flow into the interior into the first throughflow opening. From there, the hydraulic fluid flows through the first connection opening into the first working connection A.
  • the additional part of the hydraulic fluid that is in the tank connection T2 on the flows on the left side flows out of the second working port B.
  • the fourth position acts similarly to the fifth position.
  • Fig. 15 shows the oil control valve 1000 according to a second embodiment of the invention, in which various securing methods are used.
  • a crimp connection or a spot weld can be used at a first location 1702
  • a spot weld or press connection can be used at a second location 1704
  • a spot weld or a press fit can be used at a third location 1706
  • a press fit connection can be used at a fourth location 1708.
  • the invention has a number of advantages, including that it is inexpensive, has good flow through with returned oil, and ease of assembly.
  • the piston assembly can be manufactured inexpensively.
  • the piston 30 is machined while the other piston parts in the piston assembly are machined by more cost effective methods such as machining. Stamping or deep drawing, or any other suitable cost effective method, and the other piston parts in the piston assembly can be made of plastic or any other suitable inexpensive material or any other suitable inexpensive materials.
  • the good flow with returned oil occurs because the axial check valves 18, 32, 33 compared to other valves, such as B. band check valves, allow improvements in the flow.
  • the invention facilitates assembly since the concentricity of the supply pipe to the piston can be maintained by fastening means during the butt welding.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP18189919.6A 2017-09-19 2018-08-21 Ölsteuerventil zur steuerung eines nockenwellenverstellers mit einem kolben, der durch einen externen aktuator positioniert wird Active EP3460209B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US201762560273P 2017-09-19 2017-09-19
US15/831,078 US10612430B2 (en) 2017-06-20 2017-12-04 Oil control valve to control a cam phaser with a spool positioned by external actuator

Publications (2)

Publication Number Publication Date
EP3460209A1 EP3460209A1 (de) 2019-03-27
EP3460209B1 true EP3460209B1 (de) 2021-05-26

Family

ID=63350399

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18189919.6A Active EP3460209B1 (de) 2017-09-19 2018-08-21 Ölsteuerventil zur steuerung eines nockenwellenverstellers mit einem kolben, der durch einen externen aktuator positioniert wird

Country Status (2)

Country Link
EP (1) EP3460209B1 (zh)
CN (1) CN109519246B (zh)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109958489A (zh) * 2019-04-25 2019-07-02 绵阳富临精工机械股份有限公司 一种往复式调节中心阀结构
CN110374708A (zh) * 2019-08-20 2019-10-25 杰锋汽车动力系统股份有限公司 一种发动机凸轮轴相位器液压阀

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Publication number Priority date Publication date Assignee Title
JP4544294B2 (ja) * 2007-11-28 2010-09-15 株式会社デンソー バルブタイミング調整装置
DE102008030058B4 (de) * 2008-06-27 2010-06-17 Hydraulik-Ring Gmbh Nockenwellenverstelleinrichtung und geeignetes Ventil dafür
DE102010022896B4 (de) * 2010-06-07 2021-11-11 Schaeffler Technologies AG & Co. KG Druckmittelbetätigbare Nockenwellenverstelleinrichtung für eine Brennkraftmaschine
JP2012122454A (ja) * 2010-12-10 2012-06-28 Denso Corp バルブタイミング調整装置
DE102011056264B4 (de) * 2011-12-12 2020-03-05 Hilite Germany Gmbh Hydraulikventil
EP2796673B1 (de) 2013-04-22 2018-03-07 Hilite Germany GmbH Zentralventil für einen Schwenkmotorversteller
DE102013104051B4 (de) 2013-04-22 2016-09-22 Hilite Germany Gmbh Zentralventil für einen Schwenkmotorversteller
DE102013104573B4 (de) 2013-05-03 2018-05-17 Hilite Germany Gmbh Hydraulikventil und Schwenkmotorversteller
DE102013104575B4 (de) 2013-05-03 2018-03-08 Hilite Germany Gmbh Hydraulikventil und Schwenkmotorversteller
US9422840B2 (en) * 2014-06-24 2016-08-23 Hilite Germany Gmbh Hydraulic valve for an internal combustion engine
US9784143B2 (en) 2014-07-10 2017-10-10 Hilite Germany Gmbh Mid lock directional supply and cam torsional recirculation
US10041385B2 (en) 2016-03-14 2018-08-07 ECO Holding 1 GmbH Piston for a hydraulic valve for a cam phaser and hydraulic valve for the cam phaser

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Title
None *

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Publication number Publication date
CN109519246B (zh) 2021-10-08
CN109519246A (zh) 2019-03-26
EP3460209A1 (de) 2019-03-27

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