EP3460209B1 - Oil control valve for controlling a camshaft adjuster with a piston positioned by an external actuator - Google Patents

Oil control valve for controlling a camshaft adjuster with a piston positioned by an external actuator Download PDF

Info

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
Authority
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
Other languages
German (de)
French (fr)
Other versions
EP3460209A1 (en
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/en
Application granted granted Critical
Publication of EP3460209B1 publication Critical patent/EP3460209B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Description

Verwandte AnmeldungenRelated registrations

Die vorliegende Anmeldung beansprucht die Priorität der am 19. September 2017 eingereichten vorläufigen US-Patentanmeldung mit der laufenden Nr. 62/522,624 , auf die hiermit Bezug genommen wird.This application claims priority from U.S. Provisional Patent Application Serial No. 62 / 522,624 , to which reference is hereby made.

Gebiet der ErfindungField of invention

Die Erfindung bezieht sich auf ein Ölsteuerventil für einen Nockenwellenversteller eines Verbrennungsmotors, wobei der Kolben durch einen externen Aktuator positioniert wird.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.

Hintergrund der ErfindungBackground of the invention

Hydraulikventile für Nockenwellenversteller für Verbrennungsmotoren sind in der Technik allseits bekannt. Das Hydraulikventil umfasst einen Kolben, der in einem Ventilgehäuse des Hydraulikventils axial beweglich ist und der eine hydraulische Beaufschlagung des Nockenwellenverstellers steuert. Bei Hydraulikventilen gibt es viele verschiedene Konfigurationen. Das Ventilgehäuse ist hohlzylindrisch konfiguriert. Der Kolben ist auch hohlzylindrisch konfiguriert. Die Steuerung des Nockenwellenverstellers erfolgt hydraulisch durch Positionieren des verschiebbaren Kolbens und entsprechendes Öffnen und Schließen von Verbindungen, die in dem Ventilgehäuse konfiguriert sind.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. There are many different configurations of hydraulic valves. 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.

Die Veröffentlichungsschriften DE 10 2013 104 573 A1 und DE 10 2013 104 575 A1 offenbaren ein Hydraulikventil, das eine Versorgungsanschluss an einem Ventilgehäuseende umfasst, so dass direktes Verschieben des in dem Ventilgehäuse aufgenommenen Kolbens und somit eine direkte Beaufschlagung des Kolbens mit einem Hydraulikfluid, das durch den Versorgungsanschluss zugeführt wird, bereitgestellt werden können. Der Kolben weist eine komplexe Außengeometrie auf, so dass Druckkräfte dahingehend ausgeglichen werden, die Auswirkung von Druck auf die Position des Kolbens auf ein Minimum zu reduzieren.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.

Die Veröffentlichungsschriften US 2014/0311333 A1 und US 2014/0311594 A1 offenbaren ein Hydraulikventil, das Rückschlagventile umfasst, die an einem Umfang des Kolbens konfiguriert sind. Entweder erfordert dies eine komplexe Ventilgehäusekonfiguration zur Aufnahme und Sicherung der Rückschlagventile oder das Ventilgehäuse ist als mehrere Komponenten konfiguriert und bedingt ein hohes Maß an Montagekomplexität. Der Kolben ist als mehrere Komponenten konfiguriert und die einzelnen Komponenten werden konzentrisch verbunden, was eine komplexe Montage bedingt, da axiale Fehlausrichtungen beim Zusammendrücken der Komponenten vermieden werden müssen.The publication fonts US 2014/0311333 A1 and US 2014/0311594 A1 disclose a hydraulic valve including check valves configured on a circumference of the piston. This either requires a complex valve housing configuration for receiving and securing the check valves or the valve housing is configured as several components and requires a high degree of assembly complexity. The piston is configured as multiple components and the individual components are concentrically connected, which requires complex assembly, since axial misalignments must be avoided when the components are pressed together.

Ein weiteres Hydraulikventil, das eine sogenannte Mittenpositionsverriegelung umfasst, stammt aus der Veröffentlichungsschrift EP 2 966 272 A2 . Der Kolben weist eine komplexe Außengeometrie auf, da zusätzliche Verriegelungsverbindungen in dem Ventilgehäuse des Hydraulikventils angeordnet sind.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.

Ein weiteres, gattungsgemäßes Hydraulikventil, das einen besonderen Kolben für ein Hydraulikventil für einen Nockenwellenversteller umfasst, findet sich in der am 26. November 2016 eingereichten Patentanmeldung US 2017/0260882 A1 , auf die hiermit in ihrer Gesamtheit Bezug genommen wird. Dieses Hydraulikventil, das auch von dem Erfinder der vorliegenden Anmeldung erfunden wurde, weist viele allgemeine Merkmale der vorliegenden Erfindung auf.Another, generic hydraulic valve, which comprises a special piston for a hydraulic valve for a camshaft adjuster, can be found in of the patent application filed on November 26, 2016 US 2017/0260882 A1 , to which reference is hereby made in its entirety. This hydraulic valve, also invented by the present inventor, has many of the general features of the present invention.

Aus den Anmeldung JP 2012 122454 A und DE 10 2010 022 896 A1 ist jeweils ein weiteres Hydraulikventil bekannt, welches die Anordnung von Rückschlagventilen im Kolben zeigt.From the registration JP 2012 122454 A and DE 10 2010 022 896 A1 a further hydraulic valve is known, which shows the arrangement of check valves in the piston.

Kurzdarstellung der ErfindungSummary of the invention

Eine Aufgabe der Erfindung besteht darin, ein Hydraulikventil für einen Nockenwellenversteller bereitzustellen, das eine Kolbenanordnung, die einen Kolben, der in einer zentralen Öffnung eines Ventilgehäuses axial beweglich ist, umfasst, und ein erstes Rückschlagventil und ein zweites Rückschlagventil, die ein unbeabsichtigtes Herausströmen eines durch die Kolbenanordnung strömenden Hydraulikfluids von einem Innenraum der Kolbenanordnung in einem ersten Fluidstrom durch eine erste Durchströmöffnung des Kolbens hindurch in Richtung eines ersten Arbeitsanschlusses und einem zweiten Fluidstrom durch eine zweite Durchströmöffnung des Kolbens hindurch in Richtung eines zweiten Arbeitsanschlusses verhindern, umfasst. Die Kolbenanordnung weist eine Startposition, eine Mittenposition und eine Endposition auf. Das Hydraulikfluid kann von dem ersten Arbeitsanschluss zu dem zweiten Arbeitsanschluss strömen, wenn sich die Kolbenanordnung in der Startposition befindet, das Hydraulikfluid kann nicht zwischen dem erstenAn 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

Arbeitsanschluss und dem zweiten Arbeitsanschluss strömen, wenn sich die Kolbenanordnung in der Mittenposition befindet, und das Hydraulikfluid kann von dem zweiten Arbeitsanschluss zu dem ersten Arbeitsanschluss strömen, wenn sich die Kolbenanordnung in der Endposition befindet. Der erste Arbeitsanschluss und der zweite Arbeitsanschluss sind in Abhängigkeit einer Position der Kolbenanordnung geöffnet und geschlossen. Ein Versorgungsanschluss ist an einem Ende des Hydraulikventils angeordnet. Die Rückschlagventile sind erfindungsgemäß axial verschieblich im Kolben angeordnet, wobei eines der Rückschlagventile an einem im Kolben angeordneten Versorgungs- oder Rückschlagventilrohr anlegbar ist. Die Kolbenanordnung kann einen spanend bearbeiteten Kolben umfassen. Die Kolbenanordnung kann andere Kolbenteile, die aus Kunststoff, wie z. B. gestanztem oder tiefgezogenem Kunststoff, hergestellt sind, umfassen. Bei den anderen Teilen, die aus Kunststoff hergestellt sind, kann es sich um ein Versorgungsrohr und eine Strömungsscheibe handeln. Der Kolben kann durch externe Betätigung wie ein elektromagnetischer Aktuator positioniert werden. Ein mit Druck beaufschlagtes Hydraulikfluid kann in ein Ende des Hydraulikventils eintreten, wo die resultierende Druckkraft durch einen Differenzialbereich des Kolbens, d.h. durch unterschiedliche wirksame Durchmesser, ausgeglichen wird. Das erste Rückschlagventil und das zweite Rückschlagventil können eine Rückführung von Hydraulikfluid durch Nockenmoment ermöglichen. Das Hydraulikventil kann ein Ölsteuerventil oder ein Verbrennungsmotorölsteuerventil sein. Die Kolbenanordnung kann eine erste Position oder Startposition, eine zweite Position, eine dritte Position oder Mittenposition, eine vierte Position und eine fünfte Position oder Endposition aufweisen. Das Hydraulikfluid strömt von dem ersten Arbeitsanschluss zu dem zweiten Arbeitsanschluss, wenn sich die Kolbenanordnung in der ersten Position (Startposition) oder der zweiten Position befindet, das Hydraulikfluid kann nicht zwischen dem ersten Arbeitsanschluss und dem zweiten Arbeitsanschluss strömen, wenn sich die Kolbenanordnung in der dritten Position (Mittenposition) befindet, und das Hydraulikfluid strömt von dem zweiten Arbeitsanschluss zu dem ersten Arbeitsanschluss, wenn sich die Kolbenanordnung in der vierten Position oder der fünften Position (Endposition) befindet. Der erste Arbeitsanschluss und der zweite Arbeitsanschluss sind in Abhängigkeit einer Position der Kolbenanordnung und einem Druck über das erste Rückschlagventil und das zweite Rückschlagventil hinweg geöffnet und geschlossen. Das Hydraulikventil kann des Weiteren eine Tankverbindung umfassen. Die Tankverbindung ist geöffnet, wenn sich die Kolbenanordnung in der ersten Position (Startposition) oder der fünften Position (Endposition) befindet, und die Tankverbindung ist geschlossen, wenn sich die Kolbenanordnung in der zweiten Position, der dritten Position (Mittenposition) oder der vierten Position befindet.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. According to the invention, 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.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung leiten sich aus der nachfolgenden Beschreibung vorteilhafter Ausführungsformen und aus den Zeichnungsfiguren die Merkmale und Merkmalskombinationen, die in der vorstehenden Beschreibung angeführt werden, und die Merkmale und Merkmalskombinationen, die in der Figurenbeschreibung angeführt und in den Figuren einzeln gezeigt werden, sind nicht nur in der jeweiligen angeführten Kombination, sondern auch in anderen Kombinationen und alleine nutzbar, ohne von dem Gedanken der Erfindung abzuweichen. Identische oder funktional äquivalente Elemente werden mit identischen Bezugszeichen bezeichnet. Der Übersichtlichkeit halber ist es möglich, dass Elemente nicht in allen Figuren mit Bezugszeichen bezeichnet werden, ohne jedoch ihre Zuordnung zu verlieren; in den Zeichnungen zeigen:

  • Fig. 1 eine Ansicht eines Ölsteuerventils für einen Nockenwellenversteller eines Verbrennungsmotors im zusammengebauten Zustand, wobei das Ölsteuerventil zusammengesetzt ist;
  • Fig. 2 ein Ölsteuerventil mit einem Hub von 0 mm (Startposition);
  • Fig. 3 das Ölsteuerventil mit einem Hub von 1,5 mm (Mittenposition);
  • Fig. 4 das Ölsteuerventil mit einem Hub von 3 mm (Endposition);
  • Fig. 5 eine Symbolansicht des Ölsteuerventils in verschiedenen Positionen;
  • Fig. 6 eine beispielhafte Kolbenanordnung;
  • Fig. 7 eine weitere beispielhafte Kolbenanordnung;
  • Fig. 8 eine Ansicht eines Ölsteuerventils für einen Nockenwellenversteller eines Verbrennungsmotors gemäß einer zweiten Ausführungsform der Erfindung im zusammengebauten Zustand, wobei das Ölsteuerventil zusammengesetzt ist;
  • Fig. 9 das Ölsteuerventil gemäß einer zweiten Ausführungsform der Erfindung mit einem Hub von 0 mm (Start- oder erste Position);
  • Fig. 10 das Ölsteuerventil gemäß einer zweiten Ausführungsform der Erfindung mit einem Hub von 0,6 mm (zweite Position);
  • Fig. 11 das Ölsteuerventil gemäß einer zweiten Ausführungsform der Erfindung mit einem Hub von 1,5 mm (Mitten- oder Halteposition);
  • Fig. 12 das Ölsteuerventil gemäß einer zweiten Ausführungsform der Erfindung mit einem Hub von 2,7 mm (vierte Position);
  • Fig. 13 das Ölsteuerventil gemäß einer zweiten Ausführungsform der Erfindung mit einem Hub von 3,2 mm (fünfte Position oder Endposition);
  • Fig. 14 eine Symbolansicht des Ölsteuerventils gemäß einer zweiten Ausführungsform der Erfindung in verschiedenen Positionen; und
  • Fig. 15 das Ölsteuerventil 1000 gemäß einer zweiten Ausführungsform der Erfindung, bei der verschiedene Sicherungsverfahren verwendet werden.
Further advantages, features and details of the invention are derived from the following description of advantageous embodiments and from the drawing figures, the features and combinations of features given in the description above, and the features and combinations of features given in the description of the figures and shown individually in the figures are not only listed in the respective Combination, but can also be used in other combinations and alone without deviating from the concept of the invention. Identical or functionally equivalent elements are denoted by identical reference symbols. For the sake of clarity, it is possible that elements are not designated with reference symbols in all figures without, however, losing their assignment; in the drawings show:
  • Fig. 1 a view of an oil control valve for a camshaft adjuster of an internal combustion engine in the assembled state, wherein the oil control valve is assembled;
  • Fig. 2 an oil control valve with a stroke of 0 mm (starting position);
  • Fig. 3 the oil control valve with a stroke of 1.5 mm (center position);
  • Fig. 4 the oil control valve with a stroke of 3 mm (end position);
  • Fig. 5 a symbolic view of the oil control valve in different positions;
  • Fig. 6 an exemplary piston assembly;
  • Fig. 7 another exemplary piston assembly;
  • Fig. 8 a view of an oil control valve for a camshaft adjuster of an internal combustion engine according to a second embodiment of the invention in the assembled state, wherein the oil control valve is assembled;
  • Fig. 9 the oil control valve according to a second embodiment of the invention with a stroke of 0 mm (start or first position);
  • Fig. 10 the oil control valve according to a second embodiment of the invention with a stroke of 0.6 mm (second position);
  • Fig. 11 the oil control valve according to a second embodiment of the invention with a stroke of 1.5 mm (middle or holding position);
  • Fig. 12 the oil control valve according to a second embodiment of the invention with a stroke of 2.7 mm (fourth position);
  • Fig. 13 the oil control valve according to a second embodiment of the invention with a stroke of 3.2 mm (fifth position or end position);
  • Fig. 14 a symbolic view of the oil control valve according to a second embodiment of the invention in different positions; and
  • Fig. 15 the oil control valve 1000 according to a second embodiment of the invention, in which various securing methods are used.

Detaillierte Beschreibung der ErfindungDetailed description of the invention

Die Erfindung bezieht sich auf ein Ölsteuerventil für einen Nockenwellenversteller eines Verbrennungsmotors, wobei der Kolben von einem externen Aktuator positioniert wird. Der Druck tritt in das Ende des Ölsteuerventils ein, wo die resultierende Druckkraft von dem Differenzialbereich des Kolbens, d.h. durch unterschiedlich wirksame Durchmesser des Kolbens, ausgeglichen wird. Der Kolben enthält zwei Plattenrückschlagventile, die eine Rückführung von Öl durch Nockenmoment von A nach B oder B nach A in Abhängigkeit von der Kolbenposition ermöglichen. In der Mittenposition sperren die Kolbenstege A und B zum Halten der Nockenwellenverstellerposition.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 stellt eine Ansicht eines Ölsteuerventils 100 für einen Nockenwellenversteller eines Verbrennungsmotors im zusammengebauten Zustand dar. Das Ölsteuerventil umfasst ein mittiges Ventilgehäuse 10, eine Feder 12, eine Kalibrierungskappe 14, eine Feder 16, ein Rückschlagventil 18, eine Strömungsscheibe 20, ein Zufuhrfilter 22, einen Sicherungsring 24, eine Kolbenanordnung 26, einen Kolben 30 mit Stegen zum Sperren des Ölstroms und Nuten zum Gestatten des Ölstroms, ein Rückschlagventil 32, ein Rückschlagventil 33, ein Versorgungsrohr 34, und eine Strömungsscheibe 35, einen Kalibrierungsanschlag 36 und eine Feder 38. Die Plattenrückschlagventile 32, 33 sind axial in dem Kolben 30 angeordnet und weisen entgegengesetzte Öffnungsrichtungen auf. Sie liegen an einer Vertiefung von dem Kolben 30, der Strömungsscheibe 35 oder einer separaten Rückschlagventilscheibe 904 als Alternative an (siehe Fig. 8). Eine weitere, nicht gezeigte Alternative sieht vor, die Rückschlagventile 32, 33 auf dem Versorgungsrohr 34 axial verschieblich anzuordnen, welches radiale Versorgungsbohrungen zwischen den Rückschlagventilen aufweist. 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. They rest against a recess in the piston 30, the flow disk 35 or a separate check valve disk 904 as an alternative (see FIG Fig. 8 ). Another alternative, not shown, provides for the check valves 32, 33 to be arranged axially displaceably on the supply pipe 34, which has radial supply bores between the check valves.

Fig. 2 stellt das Ölsteuerventil 100 mit einem Hub von 0 mm (Startposition) dar. In der Startposition führen die beiden Plattenrückschlagventile zur Rückführung von Öl durch Nockenmoment von A nach B. Zur hydraulischen Versorgung des Nockenwellenverstellers sind mehrere Verbindungen A, B, P, T1 (in der Mitte des Ventilgehäuses 10 positioniert), T2 (an dem linken Ende positioniert) vorgesehen. 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. To hydraulic supply of the camshaft adjuster, several connections A, B, P, T1 (positioned in the middle of the valve housing 10), T2 (positioned at the left end) are provided.

Fig: 3 stellt das Ölsteuerventil 100 mit einem Hub von 1,5 mm (Mitten- oder Halteposition) dar. In der Mittenposition sperren die Kolbenstege A und B zum Halten der Nockenwellenverstellerposition. In der Mittenposition gibt es keine Rückführung und keinen Ausstoß. 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 stellt das Ölsteuerventil 100 mit einem Hub von 3 mm (Endposition) dar. In der Endposition führen die beiden Plattenrückschlagventile zur Rückführung von Öl durch Nockenmoment von B zu A. 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. 5 stellt eine Symbolansicht des Ölsteuerventils 100 in verschiedenen Positionen dar. Der rechte Bereich der Symbolansicht, die in Fig. 5 dargestellt wird, stellt einen Fluidstrom durch das Ölsteuerventil 100 gemäß einer Startposition (ersten Position), die in Fig. 2 dargestellt wird, dar. Der Mittenbereich der in Fig. 5 dargestellten Symbolansicht stellt einen Fluidstrom durch das Ölsteuerventil 100 gemäß einer Mittenposition (zweiten Position), die in Fig. 3 dargestellt wird, dar. Der linke Bereich der Symbolansicht, die in Fig. 5 dargestellt wird, stellt einen Fluidstrom durch das Ölsteuerventil 100 gemäß einer Endposition (dritten Position), die in Fig. 4 dargestellt wird, dar. Fig. 5 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.

In der Startposition gemäß Fig. 2 wird der zweite Arbeitsanschluss B mit Hydraulikfluid beaufschlagt. Dies bedeutet, dass das Hydraulikfluid von der ersten Versorgungsanschluss P durch einen Innenraum 11 des Ventilgehäuses 10, das Versorgungsrohr 34 und eine erste Durchströmungsöffnung 13 des Kolbens 30 strömt, wodurch eine zweite Verbindungsöffnung 15 des Ventilgehäuses 10, die mit dem zweiten Arbeitsanschluss B verbunden ist, freigegeben wird. Weiterhin kann Hydraulikfluid von dem ersten Arbeitsanschluss A zumindest zum Teil durch eine erste Verbindungöffnung 17 des Ventilgehäuses 10, eine erste Durchströmungsöffnung 19 (A1) des Kolbens 30, die Strömungsscheibe 35 strömen und durch Öffnen des am weitesten rechts befindlichen Rückschlagventils 33 kann das Hydraulikfluid von einem Innenraum 21 des Kolbens 30 in die erste Durchströmungsöffnung 13 strömen. Von dort aus strömt das Hydraulikfluid durch die zweite Verbindungsöffnung 15 in den zweiten Arbeitsanschluss B. Der zusätzliche Teil des Fluids, der aus dem ersten Arbeitsanschluss A herausströmt, strömt durch die Öffnung 17 und einen ersten Ablasskanal 23 des Kolbens 30 in eine dritte Verbindungsöffnung 25, die einer Tankverbindung T1 zugeordnet ist, direkt neben der ersten Verbindungsöffnung 17 in dem Ventilgehäuse 10.In the starting position according to Fig. 2 hydraulic fluid is applied to the second working connection B. This means that the hydraulic fluid from the first supply port P through a Inside 11 of the valve housing 10, the supply pipe 34 and a first throughflow opening 13 of the piston 30 flows, whereby a second connection opening 15 of the valve housing 10, which is connected to the second working port B, is exposed. Furthermore, 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.

In der Mitten- oder Halteposition gemäß Fig. 3 werden die Ströme aufgrund der Position der Stege 27, 29 des Kolbens 30 blockiert. Die Stege 27, 29 weisen einen unterschiedlichen Außendurchmesser auf, wodurch ein Druckausgleich des Kolbens 30 erfolgen kann.In the middle or holding position according to Fig. 3 the flows are blocked due to the position of the webs 27, 29 of the piston 30. The webs 27, 29 have a different outer diameter, as a result of which the pressure of the piston 30 can be equalized.

In der Endposition gemäß Fig. 4 wird der erste Arbeitsanschluss A mit Hydraulikfluid beaufschlagt. Das bedeutet, dass das Hydraulikfluid von der ersten Versorgungsanschluss P durch den Innenraum 11 und das Versorgungsrohr 34 in den Innenraum 21 des Kolbens 30 und die erste Durchströmungsöffnung 13 strömt, wodurch die erste Verbindungsöffnung 17, die mit dem ersten Arbeitsanschluss A verbunden ist, freigegeben wird. Weiterhin kann Hydraulikfluid von dem zweiten Arbeitsanschluss B zumindest zum Teil durch die zweite Verbindungsöffnung 15, eine zweite Durchströmungsöffnung 31 (B1) des Kolbens 30 strömen und durch Öffnen des am weitesten links befindlichen Rückschlagventils 32 kann das Hydraulikfluid in den Innenraum 21 in die erste Durchströmungsöffnung 13 strömen. Von dort aus strömt das Hydraulikfluid durch die erste Verbindungsöffnung 17 in den ersten Arbeitsanschluss A. Der zusätzliche Teil des Fluids, der aus dem zweiten Arbeitsanschluss B herausströmt, strömt durch die Öffnung 15 und einen zweiten Ablasskanal 39 des Kolbens 30 in eine vierte Verbindungöffnung 37 des Ventilgehäuses 10, die der Tankverbindung T2 auf der linken Seite zugeordnet ist. Fig. 6 zeigt eine beispielhafte Kolbenanordnung 26. Eine Laserschweißung 702 ist eine 360-Grad-Schweißung zum Halten des Kolbens 30 und des Kalibrierungsanschlags 36 in Position und gegen Auslauf abgedichtet. Eine Schweißung oder Pressverbindung 704 zum Sichern des Versorgungsrohrs 34. Einige der Teile können aus gestanzten oder tiefgezogenen Teilen 706 hergestellt sein. Das Versorgungsrohr 34 und die Strömungsscheibe 35 können einstückig aus Kunststoff hergestellt sein. Die Strömungsscheibe 35 wird zur Ölabdichtung leicht in den Kolben 30 gepresst (Pressverbindung 708). Das Halten kann durch einen geschweißten Anschlag erfolgen.In the end position according to Fig. 4 hydraulic fluid is applied to the first working connection A. This means that the hydraulic fluid flows from the first supply connection P through the interior 11 and the supply pipe 34 into the interior 21 of the piston 30 and the first throughflow opening 13, whereby the first connection opening 17, which is connected to the first working connection A, is released . Furthermore, 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. The additional part of the fluid that flows out of the second working connection B flows through the opening 15 and a second outlet channel 39 of the piston 30 into a fourth connection opening 37 of the Valve housing 10, which is assigned to the tank connection T2 on the left. 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. A weld or press fit 704 to secure the service pipe 34. 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 stellt eine weitere beispielhafte Kolbenanordnung dar. Die Kolbenanordnung (die gelegentlich als Kolben bezeichnet wird) umfasst einen alternativen Kolben, der leichter maschinell auszuarbeiten und ohne eine Grundbohrung leichter zu reinigen ist. Der Kolben 30 gemäß Fig. 7 ist ein Hohlkolben mit zwei offenen Enden. Eine Scheibe 40 ist in dem Kolben 30 fixiert und dichtet den Innenraum 21 an dem linken Ende ab. 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 stellt eine Ansicht eines Ölsteuerventils 1000 für einen Nockenwellenversteller eines Verbrennungsmotors gemäß einer zweiten Ausführungsform der Erfindung im zusammengebauten Zustand dar. Das Ölsteuerventil umfasst ein mittiges Ventilgehäuse 10, eine Feder 12, eine Kalibrierungskappe 14, eine Feder 16, ein Rückschlagventil 18, eine Strömungsscheibe 20, ein Zufuhrfilter 22, einen Sicherungsring 24, eine Kolbenanordnung 26, einen Kolben 30 mit Stegen zum Sperren des Ölstroms und Nuten zum Gestatten des Ölstroms, Rückschlagventile 32 und 33, eine Feder 38, eine Scheibe 902, eine Rückschlagventilscheibe 904 und ein Rückschlagventilrohr 43. Dieses Ölsteuerventil 1000 weist eine alternative Kolbenanordnung 26, die die Rückschlagventile 32, 33 hält, auf. Der Innendurchmesser des Kolbens 30 ist leichter maschinell auszuarbeiten, wodurch eine weniger kostenintensive Kolbenanordnung 26 bereitgestellt wird. 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 und Fig. 13 stellen Positionen auf beiden Seiten der "Halte"-Position (nicht Ausstoß) von Fig. 11 dar. Die Positionen, die in Fig. 9 und Fig. 13 gezeigt werden, stellen die Tanköffnung an beiden Enden des Hubs dar. Dieser Vorgang ist insbesondere bei Vierzylinderanwendungen von Vorteil, wo eine Rückführung durch Nockenmoment für eine Verstellgeschwindigkeit bei niedriger Motordrehzahl von Vorteil ist und eine Öldruckbetätigung für eine Verstellgeschwindigkeit bei hoher Motordrehzahl von Vorteil ist. Diese Funktion kann verschiedenen Kolbenkonstruktionen hinzugefügt werden. 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 stellt das Ölsteuerventil 1000 gemäß einer zweiten Ausführungsform der Erfindung mit einem Hub von 0 mm (Start- oder erste Position) dar. In der ersten Position strömt Hydraulikfluid von einem Versorgungsanschluss P durch eine Kolbenverlängerung 41, die in der Kalibrierungskappe 14 geführt wird, das Rückschlagventilrohr 43, die erste Durchströmungsöffnung 13 des Kolbens und die zweite Verbindungöffnung 15 zu dem zweiten Arbeitsanschluss B. Das rechte Ende des Rückschlagventilrohrs 43 ist in einer Vertiefung 51 des Kolbens 30 positioniert. Das Plattenrückschlagventil 33 öffnet sich für eine Rückführung von Öl durch Nockenmoment von A zu B über die erste Verbindungsöffnung 17, die erste Durchströmungsöffnung 19, die Öffnungen 45 des Rückschlagventilrohrs 43 (siehe gepunktete Linien in Fig. 9), den Innenraum 21, die erste Durchströmungsöffnung 13 zu der zweiten Verbindungsöffnung 15. Zur hydraulischen Versorgung des Nockenwellenverstellers sind mehrere Verbindungen A, B, P, T1 (direkt neben der Verbindung A in dem Ventilgehäuse 10 positioniert), T2 (an dem linken Ende des Ventilgehäuses 10 positioniert) vorgesehen. T1 ist geöffnet, wodurch ein Fluidstrom von A über einen Steg 47 am rechten Ende zu der dritten Verbindungsöffnung 25 und T1 gestattet wird. 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). In the 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. For the hydraulic supply of the camshaft adjuster there are several connections 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 stellt das Ölsteuerventil 1000 gemäß einer zweiten Ausführungsform der Erfindung mit einem Hub von 0,6 mm (zweite Position) dar. In der zweiten Position führt das Plattenrückschlagventil 33 zur Rückführung von Öl durch Nockenmoment von A zu B. Im Gegensatz zu der ersten Position gemäß Fig. 9 wird der Fluidstrom zu der dritten Verbindungsöffnung 25 und somit T1 durch den Steg 47 am rechten Ende des Kolbens 30 verschlossen. 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). In the second position, the plate check valve 33 leads to the return of oil by cam torque from A to B. In contrast to the first position according to FIG Fig. 9 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 stellt das Ölsteuerventil 1000 gemäß einer zweiten Ausführungsform der Erfindung mit einem Hub von 1,5 mm (Mitten- oder Halteposition) dar. In dieser Position sperren die Kolbenstege 27, 29 A und B zum Halten der Nockenwellenverstellerposition. In der Mitten- oder Halteposition gibt es keine Rückführung. 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 stellt das Ölsteuerventil 1000 gemäß einer zweiten Ausführungsform der Erfindung mit einem Hub von 2,7 mm (vierte Position) dar. In der vierten Position führen die Plattenrückschlagventile 32 zur Rückführung von Öl durch Nockenmoment von B zu A. T2 wird durch einen Steg 49 am linken Ende des Kolbens 30 verschlossen. 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 stellt das Ölsteuerventil 1000 gemäß einer zweiten Ausführungsform der Erfindung mit einem Hub von 3,2 mm (Endposition) dar. In der Endposition strömt Hydraulikfluid von dem Versorgungsanschluss P durch eine Kolbenverlängerung 41, das Rückschlagventilrohr 43, die erste Durchströmungsöffnung 13 des Kolbens und die erste Verbindungsöffnung 17 zu dem ersten Arbeitsanschluss A. Das Plattenrückschlagventil 32 öffnet sich zur Rückführung von Öl durch Nockenmoment von B zu A über die zweite Verbindungsöffnung 15, die zweite Durchströmungsöffnung 31, das Rückschlagventil 32, den Innenraum 21, die erste Durchströmungsöffnung 13 zu der ersten Verbindungsöffnung 17. T2 ist geöffnet, wodurch ein Fluidstrom von B über den Steg 49 am linken Ende zu der vierten Verbindungsöffnung 37 und T2 gestattet wird. 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). In the 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. 14 stellt eine Symbolansicht des Ölsteuerventils 1000 gemäß einer zweiten Ausführungsform der Erfindung in verschiedenen Positionen dar. Der am weitesten rechts befindliche Bereich der Symbolansicht, die in Fig. 14 dargestellt wird, stellt einen Fluidstrom durch das Ölsteuerventil 1000 gemäß einer ersten Position, die in Fig. 9 dargestellt wird, dar. Der Bereich neben dem am weitesten rechts befindlichen Bereich der Symbolansicht, die in Fig. 14 dargestellt wird, stellt einen Fluidstrom durch das Ölsteuerventil 1000 gemäß einer zweiten Position, die in Fig. 10 dargestellt wird, dar. Der mittlere Bereich der Symbolansicht, die in Fig. 14 dargestellt wird, stellt einen Fluidstrom durch das Ölsteuerventil 1000 gemäß einer Mittenposition (dritten Position), die in Fig. 11 dargestellt wird, dar. Der Bereich links von dem mittleren Bereich der Symbolansicht, die in Fig. 14 dargestellt wird, stellt einen Fluidstrom durch das Ölsteuerventil 1000 gemäß einer vierten Position, die in Fig. 12 dargestellt wird, dar. Der am weitesten links befindliche Bereich der Symbolansicht, die in Fig. 14 dargestellt wird, stellt einen Fluidstrom durch das Ölsteuerventil 1000 gemäß einer fünften (End- oder letzten) Position, die in Fig. 13 dargestellt wird, dar. Fig. 14 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 The area to the left of the center area of the Icon View shown in Fig. 14 is shown 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.

In dieser Startposition wird der zweite Arbeitsanschluss B mit Hydraulikfluid beaufschlagt. Das bedeutet, dass das Hydraulikfluid von der ersten Versorgungsanschluss P durch einen Innenraum und die erste Durchströmungsöffnung strömt, wodurch die zweite Verbindungsöffnung, die mit dem zweiten Arbeitsanschluss B verbunden ist, freigegeben wird. Das Weiteren kann Hydraulikfluid von dem ersten Arbeitsanschluss A zumindest zum Teil durch die erste Verbindungsöffnung strömen und durch Öffnen des am weitesten rechts befindlichen Rückschlagventils 32 kann das Hydraulikfluid in den Innenraum in die erste Durchströmungsöffnung strömen. Von dort aus strömt das Hydraulikfluid durch die zweite Verbindungsöffnung in den zweiten Arbeitsanschluss B. Der zusätzliche Teil des Fluids, der aus dem ersten Arbeitsanschluss A herausströmt, strömt durch die Öffnung in eine dritte Verbindungsöffnung, die der Tankverbindung T1 zugeordnet ist.In this starting position, hydraulic fluid is applied to the second working connection B. This means that the hydraulic fluid flows from the first supply connection P through an interior space and the first through-flow opening, whereby the second connection opening, which is connected to the second working connection B, is released. Furthermore, 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.

Die zweite Position wirkt abgesehen davon, dass die Tankverbindung T1 geschlossen ist, ähnlich der Startposition.Apart from the fact that the tank connection T1 is closed, the second position acts similarly to the start position.

In dieser Mitten- oder Halteposition werden die Ströme blockiert.In this middle or stop position, the currents are blocked.

In dieser End- oder fünften Position wird der erste Arbeitsanschluss A mit Hydraulikfluid beaufschlagt. Dies bedeutet, dass das Hydraulikfluid von der ersten Versorgungsanschluss P durch einen Innenraum und die zweite Durchströmungsöffnung strömt, wodurch die zweite Verbindungsöffnung, die mit dem ersten Arbeitsanschluss A verbunden ist, freigegeben wird. Das Weiteren kann Hydraulikfluid von dem zweiten Arbeitsanschluss B zumindest zum Teil durch die zweite Verbindungsöffnung strömen und durch Öffnen des am weitesten links befindlichen Rückschlagventils 32 kann das Hydraulikfluid in den Innenraum in die erste Durchströmungsöffnung strömen. Von dort aus strömt das Hydraulikfluid durch die erste Verbindungsöffnung in den ersten Arbeitsanschluss A. Der zusätzliche Teil des Fluids, der aus dem zweiten Arbeitsanschluss B herausströmt, strömt durch die Öffnung in eine vierte Verbindungsöffnung, die der Tankverbindung T2 auf der linken Seite zugeordnet ist. Der zusätzliche Teil des Hydraulikfluids, der in die Tankverbindung T2 auf der linken Seite strömt, strömt aus den zweiten Arbeitsanschluss B heraus.In this end or fifth position, hydraulic fluid is applied to the first working connection A. This means that the hydraulic fluid flows from the first supply connection P through an interior space and the second through-flow opening, whereby the second connection opening, which is connected to the first working connection A, is released. Furthermore, 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 fluid that flows out of the second working connection B flows through the opening into a fourth connection opening, which is assigned to the tank connection T2 on the left side. 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.

Die vierte Position wirkt abgesehen davon, dass die Tankverbindung T2 geschlossen ist, ähnlich der fünften Position.Apart from the fact that the tank connection T2 is closed, the fourth position acts similarly to the fifth position.

Fig. 15 stellt das Ölsteuerventil 1000 gemäß einer zweiten Ausführungsform der Erfindung, bei der verschiedene Sicherungsverfahren verwendet werden, dar. Insbesondere kann eine Crimpverbindung oder eine Punktschweißung an einer ersten Stelle 1702 verwendet werden, eine Punktschweißung oder Pressverbindung kann an einer zweiten Stelle 1704 verwendet werden, eine Punktschweißung oder Pressverbindung kann an einer dritten Stelle 1706 verwendet werden und eine Pressverbindung kann an einer vierten Stelle 1708 verwendet werden. Fig. 15 shows the oil control valve 1000 according to a second embodiment of the invention, in which various securing methods are used. In particular, 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 and a press fit connection can be used at a fourth location 1708.

Die Erfindung weist eine Reihe von Vorteilen auf, darunter dass sie kostengünstig ist, eine gute Durchströmung mit rückgeführtem Öl aufweist und Einfachheit der Montage. Die Kolbenanordnung kann kostengünstig hergestellt werden. Insbesondere wird der Kolben 30 maschinell ausgearbeitet, während die anderen Kolbenteile in der Kolbenanordnung durch kosteneffizientere Verfahren, wie z. B. Stanzen oder Tiefziehen, oder beliebige andere geeignete kosteneffiziente Verfahren hergestellt werden können und die anderen Kolbenteile in der Kolbenanordnung aus Kunststoff oder einem beliebigen anderen geeigneten günstigen Material oder beliebigen anderen geeigneten günstigen Materialien hergestellt werden können.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. In particular, 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.

Die gute Durchströmung mit rückgeführtem Öl tritt auf, da die axialen Rückschlagventile 18, 32, 33 gegenüber anderen Ventilen, wie z. B. Bandrückschlagventile, Verbesserungen bei der Durchströmung gestatten. Die Erfindung erleichtert die Montage, da die Konzentrizität des Versorgungsrohrs zu dem Kolben durch Befestigungsmittel während der Anschlagschweißung aufrechterhalten werden kann.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.

Obgleich einige Ausführungsformen der vorliegenden Erfindung und ihre Vorteile genauer beschrieben worden sind, versteht sich, dass Änderungen, Ersetzungen, Umwandlungen, Modifikationen, Variationen, Austausche und Abänderungen daran vorgenommen werden können, ohne von den Lehren und dem Gedanken der Erfindung abzuweichen.Although some embodiments of the present invention and their advantages have been described in detail, it is to be understood that changes, substitutions, conversions, modifications, variations, substitutions, and changes can be made therein without departing from the teachings and spirit of the invention.

Claims (13)

  1. Hydraulic valve (100, 1000) for a camshaft adjuster, which hydraulic valve comprises the following:
    a piston arrangement (26) which comprises a piston (30) which is axially movable in a central opening of a valve housing (10); and
    a first check valve (32) and a second check valve (33), which are arranged in the piston (30) and which prevent a hydraulic fluid which is flowing through the piston arrangement (26) from unintentionally flowing out of an interior space (21) of the piston arrangement (26) in a first fluid flow through a first throughflow opening (19) of the piston (30) in the direction of a first working port (A) and in a second fluid flow through a second throughflow opening (31) of the piston (30) in the direction of a second working port (B);
    wherein the piston arrangement (26) has a start position, a middle position and an end position,
    wherein the hydraulic fluid flows from the first working port (A) to the second working port (B) when the piston arrangement (26) is in the start position,
    wherein the hydraulic fluid cannot flow between the first working port (A) and the second working port (B) when the piston arrangement (26) is in the middle position,
    wherein the hydraulic fluid flows from the second working port (B) to the first working port (A) when the piston arrangement (26) is in the end position,
    wherein the first working port (A) and the second working port (B) are opened and closed in a manner dependent on a position of the piston (30), wherein the hydraulic valve (100, 1000) furthermore comprises a supply port (P) which is arranged at an end of the hydraulic valve (100, 1000), characterized in that the check valves (32, 33) are arranged in axially displaceable fashion in the piston (30), wherein one of the check valves (32, 33) can be placed in contact against a supply or check valve pipe (34, 43) arranged in the piston (30).
  2. Hydraulic valve (100, 1000) according to Claim 1, characterized in that the piston arrangement (26) comprises a piston machined by cutting.
  3. Hydraulic valve (100, 1000) according to any of the preceding claims, characterized in that the piston arrangement (26) comprises other piston parts which are produced from plastic.
  4. Hydraulic valve (100, 1000) according to Claim 3, characterized in that the other parts, which are produced from plastic, are produced from punched or deep-drawn plastic.
  5. Hydraulic valve (100, 1000) according to Claim 1, characterized in that the piston (30) is positioned by external actuation.
  6. Hydraulic valve (100, 1000) according to Claim 1, characterized in that a pressurized hydraulic fluid enters the end of the hydraulic valve (100, 1000), wherein the resulting pressure force on the piston (30) is compensated by means of a differential region of the piston (30).
  7. Hydraulic valve (100, 1000) according to Claim 1, characterized in that the first check valve (32) and the second check valve (33) allow a return of hydraulic fluid by way of a cam moment.
  8. Hydraulic valve (100, 1000) according to Claim 1, characterized in that the first check valve (32) and the second check valve (33) have opposite opening directions.
  9. Hydraulic valve (100, 1000) according to Claim 1, characterized in that the hydraulic valve (100, 1000) is an oil control valve.
  10. Hydraulic valve (100, 1000) according to Claim 1, characterized in that the hydraulic valve (100, 1000) is an internal combustion engine oil control valve.
  11. Hydraulic valve (100, 1000) according to Claim 1, characterized in that the check valves (32, 33) are arranged in axially displaceable fashion on the supply pipe (34), wherein the supply pipe (34) has radial supply bores between the check valves (32, 33).
  12. Hydraulic valve (100, 1000) according to Claim 1, characterized in that the piston arrangement (26) has 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,
    wherein the hydraulic fluid flows from the first working port (A) to the second working port (B) when the piston arrangement (26) is in the first position or the second position,
    wherein the hydraulic fluid cannot flow between the first working port (A) and the second working port (B) when the piston arrangement (26) is in the third position,
    wherein the hydraulic fluid flows from the second working port (B) to the first working port (A) when the piston arrangement (26) is in the fourth position or the fifth position,
    wherein the first working port (A) and the second working port (B) are opened and closed in a manner dependent on a position of the piston arrangement.
  13. Hydraulic valve (100, 1000) according to Claim 12, characterized in that the hydraulic valve (100, 1000) furthermore comprises the following:
    a tank connection (T1, T2),
    wherein the tank connection (T1, T2) is open when the piston arrangement (26) is in the first position (start position) or the fifth position (end position), and
    wherein the tank connection (T1, T2) is closed when the piston arrangement (26) is in the second position, the third position (middle position) or the fourth position.
EP18189919.6A 2017-09-19 2018-08-21 Oil control valve for controlling a camshaft adjuster with a piston positioned by an external actuator Active EP3460209B1 (en)

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 (en) 2019-03-27
EP3460209B1 true EP3460209B1 (en) 2021-05-26

Family

ID=63350399

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18189919.6A Active EP3460209B1 (en) 2017-09-19 2018-08-21 Oil control valve for controlling a camshaft adjuster with a piston positioned by an external actuator

Country Status (2)

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

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109958489A (en) * 2019-04-25 2019-07-02 绵阳富临精工机械股份有限公司 A kind of reciprocating adjusting center valve arrangement
CN110374708A (en) * 2019-08-20 2019-10-25 杰锋汽车动力系统股份有限公司 A kind of engine camshaft phase device hydraulic valve

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP4544294B2 (en) * 2007-11-28 2010-09-15 株式会社デンソー Valve timing adjustment device
DE102008030058B4 (en) * 2008-06-27 2010-06-17 Hydraulik-Ring Gmbh Camshaft adjusting device and suitable valve for it
DE102010022896B4 (en) * 2010-06-07 2021-11-11 Schaeffler Technologies AG & Co. KG Camshaft adjusting device for an internal combustion engine that can be actuated by pressure medium
JP2012122454A (en) * 2010-12-10 2012-06-28 Denso Corp Valve timing adjusting device
DE102011056264B4 (en) * 2011-12-12 2020-03-05 Hilite Germany Gmbh Hydraulic valve
DE102013104051B4 (en) 2013-04-22 2016-09-22 Hilite Germany Gmbh Central valve for a Schwenkmotorversteller
EP2796673B1 (en) 2013-04-22 2018-03-07 Hilite Germany GmbH Central valve for a pivotable motor adjuster
DE102013104575B4 (en) 2013-05-03 2018-03-08 Hilite Germany Gmbh Hydraulic valve and Schwenkmotorversteller
DE102013104573B4 (en) 2013-05-03 2018-05-17 Hilite Germany Gmbh Hydraulic valve and 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

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

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

Similar Documents

Publication Publication Date Title
DE102013104573B4 (en) Hydraulic valve and Schwenkmotorversteller
EP2796674B1 (en) Central valve for a pivotable motor adjuster
WO2018206316A1 (en) Valve
EP2927439B1 (en) Hydraulic valve for a pivoting engine adjuster of a camshaft
DE102013104575B4 (en) Hydraulic valve and Schwenkmotorversteller
EP1212517B1 (en) Camshaft adjuster for internal combustion engines
WO2009010332A1 (en) Valve part for a hydraulic control valve
EP3219943A1 (en) Piston for a hydraulic valve of a hydraulic valve for a pivoting motor adjuster and hydraulic valve for a pivoting motor adjuster of a camshaft
WO2010139522A1 (en) Control valve for controlling pressure-medium flows comprising an integrated check valve
DE102015200543B4 (en) Control valve with drain channel and internal combustion engine
EP2370714B1 (en) Electromagnetic actuating unit
EP3460209B1 (en) Oil control valve for controlling a camshaft adjuster with a piston positioned by an external actuator
DE3302000A1 (en) HYDRAULIC VALVE
DE102015200542B4 (en) Central valve for a camshaft adjusting device
DE102007032873A1 (en) Control valve has at least one cut-out in valve seat and/or in valve piston that is fully covered in valve closed position and at least partly exposed in valve open position
EP2466155B1 (en) Hydraulically unlocked return-seat valve
EP1753985B1 (en) Hydraulic linear drive, especially hydraulic transmission actuator
DE102008006377A1 (en) Hydraulic valve unit for control valve for controlling hydraulic fluid flows for use in camshaft adjuster, has valve housing with multiple fluid channels that penetrate housing wall and opens into housing cavity
EP3015662B1 (en) Hydraulic valve and a tilt motor adjuster
DE102010013777A1 (en) Central valve for oscillating motor adjuster, has hollow piston that is guided within connector which has radial oil supply connection and two radial working connections
DE3732445C2 (en) Pressure control valve
DE102012208808A1 (en) Control valve for controlling pressure medium flow of camshaft adjusting device, has radial bores which are spaced apart from each other in control sleeve and formed with greater diameter than the width of inner annular groove
EP3865746B1 (en) Electrohydraulic control valve
EP3686465B1 (en) Quick switch valve
DE102021103446A1 (en) Control valve for a camshaft adjuster

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN PUBLISHED

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20190424

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

INTG Intention to grant announced

Effective date: 20201116

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

GRAL Information related to payment of fee for publishing/printing deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR3

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

INTC Intention to grant announced (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: GRANT OF PATENT IS INTENDED

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

INTG Intention to grant announced

Effective date: 20210401

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 1396425

Country of ref document: AT

Kind code of ref document: T

Effective date: 20210615

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502018005397

Country of ref document: DE

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG9D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210826

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20210819

Year of fee payment: 4

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20210526

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210927

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210826

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210827

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210926

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20210819

Year of fee payment: 4

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502018005397

Country of ref document: DE

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20210831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210831

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210831

26N No opposition filed

Effective date: 20220301

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210926

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210821

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210821

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210831

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502018005397

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20220821

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20180821

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220831

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20230301

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20220821

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20210526