EP3530891A1 - Soupape hydraulique pour un dispositif de réglage de moteur oscillant d'un arbre à cames - Google Patents

Soupape hydraulique pour un dispositif de réglage de moteur oscillant d'un arbre à cames Download PDF

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Publication number
EP3530891A1
EP3530891A1 EP19153487.4A EP19153487A EP3530891A1 EP 3530891 A1 EP3530891 A1 EP 3530891A1 EP 19153487 A EP19153487 A EP 19153487A EP 3530891 A1 EP3530891 A1 EP 3530891A1
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EP
European Patent Office
Prior art keywords
port
working port
working
valve
piston
Prior art date
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Granted
Application number
EP19153487.4A
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German (de)
English (en)
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EP3530891B1 (fr
Inventor
Falk Müller
André Seidenschwann
Patrick Ruppert
Udo Bartel
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
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Eco Holding 1 GmbH
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Publication date
Priority claimed from DE102019101159.0A external-priority patent/DE102019101159A1/de
Application filed by Eco Holding 1 GmbH filed Critical Eco Holding 1 GmbH
Publication of EP3530891A1 publication Critical patent/EP3530891A1/fr
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Publication of EP3530891B1 publication Critical patent/EP3530891B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34409—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
    • F01L2001/34433—Location oil control valves

Definitions

  • the invention relates to a hydraulic valve, in particular for a Schwenkmotorversteller a camshaft of an internal combustion engine of a motor vehicle. Furthermore, the invention relates to a valve for a Schwenkmotorversteller a camshaft and a method for operating a valve for a Schwenkmotorversteller a camshaft.
  • a switching position is initially proportional actuated, in which the pressure peaks of the work connection to be relieved against the work connection to be loaded are locked.
  • another switching position for the use of the camshaft alternating torques can be controlled.
  • An object of the invention is to provide a hydraulic valve which allows a better system behavior of a Schwenkmotorverstellers in a simple and compact design.
  • a hydraulic valve is proposed, in particular for a swivel motor adjuster of a camshaft, which comprises a bushing with a piston displaceably arranged in a bore along a longitudinal direction, a supply connection for supplying a hydraulic fluid and at least one first working connection and a second working connection.
  • the hydraulic valve comprises at least one tank drain port for discharging the hydraulic fluid, wherein the first working port and the second working port are each associated with a check valve and the first working port and the second working port by displacing the piston via at least one of the check valves alternately with each other and / or with the supply port and / or the tank drain connection are connectable.
  • the hydraulic valve has five switching positions, wherein in a first switching position of the piston, the second working connection with the supply connection and the first Working port is connected to the tank drain port, wherein a fluid path from the first working port to the second working port via the first working port associated with the check valve is openable by a threshold pressure exceeding.
  • a second switching position of the piston the second working port is connected to the supply port and a connection between the first working port and the tank discharge port is interrupted, wherein a fluid path from the first working port to the second working port via the first working port associated with the check valve by one, a threshold overriding pressure can be opened.
  • the piston In a third switching position of the piston, the piston is positioned in a middle position in which a connection between the working connections and the supply connection and the tank discharge connection is interrupted.
  • the first working port In a fourth switching position of the piston, the first working port is connected to the supply port and a connection between the second working port and the tank discharge port is interrupted, wherein a fluid path from the second working port to the first working port via the non-return valve associated with the second working port by one, a threshold overriding pressure can be opened.
  • the first working port is connected to the supply port and the second working port is connected to the tank discharge port, wherein a fluid path from the second working port to the first working port is openable via the non-return valve associated with the second working port by a pressure exceeding a threshold value ,
  • the respective connection between the working connection and the tank drain connection is throttled free of control edges. The throttling of the respective connection between the working connection can be switched or controlled.
  • Pulsed hydraulic pressures are on the one hand alternating moments on the hydraulic piston, which both temporarily have a positive, variable component and a temporary negative component.
  • swelling moments are those moments which, although they change in magnitude, remain over a longer period of several milliseconds in the same sign range of the torque characteristic.
  • a motor hydraulic circuit of a camshaft adjuster with a counter-rotating hydraulic piston with at least two hydraulic chambers acts an external moment that acts either changing or swelling.
  • the hydraulic circuit performs, a hydraulic pump removable, different pressurization of the counter-rotating hydraulic chambers by a change in position.
  • a hydraulic Weichenver ein preferably embodied by a valve which directs the pressurization of the hydraulic fluid to the piston, the negative portion of the alternating torque is used to change the hydraulic piston in position.
  • the swelling portion of the moment is hidden by other means, such as check valves.
  • each hydraulic connection paths can be provided from one chamber to the working port for the other chamber.
  • the valve can pass the hydraulic pressure, as can be derived from the negative portion of the alternating torque on the one working port for each chamber via at least one check valve on the second working port of each other chamber. It can be done alternately.
  • the pressurization of the pressurized port is forwarded to the second working port.
  • the alternate passage of the hydraulic fluid is to be performed by both the one chamber and the other chamber to the corresponding counter-rotating chamber.
  • the function of the check valves can be referred to as a bypass, which feed only the negative part of the alternating force in front of the camshaft adjuster again.
  • a suitable place of re-injection may be the supply connection of the camshaft adjuster.
  • the check valves may then be arranged so that only in the direction of the pressure side of the camshaft adjuster, a passage of the hydraulic pressure, the comes from the chambers of the piston, is made possible above a certain threshold.
  • the tank drain connection can be throttled less in the end positions than in the remaining positions.
  • the respective pressure chamber can thus be emptied faster in the end position.
  • the first working port and the second working port are each assigned a check valve on an outer side of the piston.
  • the check valves are each arranged on a piston attachment, which surrounds the piston and is rigidly connected to the piston. In this way, the piston assembly can be easily and inexpensively formed.
  • check valves are provided as disc-shaped closing body, which are biased by a common compression spring against the piston caps.
  • a preassembled module can be provided, which can be easily mounted in the socket.
  • the piston caps preferably each have two annular webs, which each have two cooperating with recesses in the socket control edges.
  • control edges of the annular webs with the working ports act as radial recesses in the bushing and two groove-shaped Recesses in the bore together, wherein the groove-shaped recesses are arranged in the axial direction respectively between the working port and the tank drain port.
  • the groove-shaped recesses allow in conjunction with the control edges a position-dependent opening and closing of the tank drain port, so that the hydraulic valve in the control range a pure so-called FastPhaser characteristic (passing the hydraulic fluid from one chamber into the other chamber without tank drain) and in the end positions a FastPhaser- Characteristics with tank drain has.
  • a distance between an outer diameter of the respective annular web and a groove bottom of the respective groove-shaped recess is smaller than a distance between Nutrich vom the groove-shaped recess and end faces of the annular web.
  • a ratio A2 to A1 greater than 1.4 to 1 is preferably provided. This can significantly increase process reliability in production.
  • a valve for a swing motor phaser of a camshaft having a bushing with a piston slidably disposed in a bore along a longitudinal direction between a first end position and a second end position, a supply port for supplying a hydraulic fluid, at least a first working port and a second working port, and at least one tank drain port for discharging the hydraulic fluid, wherein the first working port and the second working port are formed by suitably positioning the piston fluidly connectable to each other and the piston each having at its axially outer ends arranged outer annular lands to the Tankab Wegan gleich in the first or completely close the second end position, wherein in the first end position, the connection between the first working port and the Tankab Wegan gleich and in the second end position, the connection between the second working port and the tank drain port is throttled control edge free.
  • the throttling of the respective connection between the working connection can be switched or controlled.
  • the technical advantage can be achieved that, on the one hand, the so-called fast-phaser function as well as an improved function in the lower temperature range can be ensured in a valve.
  • hydraulic communication paths are provided from one chamber via a valve to an opposite chamber.
  • the connection paths can be used for alternating flow through which hydraulic fluid is both flowed out of the first chamber and also flows into the second chamber of the vane-type adjuster. Accordingly, the fluid can also flow out of the second chamber and can be flowed into the first chamber.
  • the fast phaser function provides a bypass that allows fluid to be redirected directly from the first chamber to the second chamber or vice versa.
  • the bypass function is possible only from a certain threshold.
  • the improved function in the lower temperature range results from the arrangement according to the invention of the outer annular webs, which completely close the respectively assigned tank outflow in the end positions of the piston, but throttles the opposite tank outflow free of control edges.
  • the control edge-free throttling of the opposite tank runoff brings, for example, the advantage that the oil exchange works well even with viscous cold oil.
  • results in the valve according to the invention a slightly reduced adjustment speed in the lower speed range compared to a pure fast phaser valve.
  • the tank drain in the end positions can be throttled less than in the remaining positions.
  • the respective pressure chamber can thus be emptied faster in the end position.
  • the bushing in the region of the bore has two groove-shaped recesses, which are respectively assigned to the outer annular webs.
  • the fluid flow can be switched or controlled.
  • the groove-shaped recesses are made wider than the wall thickness of the outer ring lands.
  • the flow rate of the fluid can be controlled exactly, as long as an outer ring land is in the region of the groove-shaped recess.
  • the groove-shaped recesses are arranged in the longitudinal direction in each case between the working connection and the tank discharge connection. As a result, for example, a particularly compact design of the valve is realized.
  • the piston between the outer ring lands on two inner ring lands which are respectively associated with the first working port and the second working port.
  • the inner ring lands are spaced inwardly from the outer ring lands in the longitudinal direction of the piston. They are wider in relation to the outer ring lands, since they must completely close the working connections depending on the position.
  • check valves Located directly on the inner ring lands, there are check valves which determine the threshold for the release of the bypass.
  • a distance between an outer diameter of the respective outer ring land and a groove bottom of the respective groove-shaped recess is smaller than a distance between Nutrich vom the groove-shaped recess and end faces of the annular web.
  • the piston can be transferred to a first position, wherein the tank drain port of both working ports is formed closed by the outer annular webs.
  • the second working connection is formed with the supply connection and the first working connection is fluidly connectable to the second working connection.
  • This first position is part of the classic control range of a Fast Phaser valve.
  • the tank drain connections are closed. So that the working port can be connected to the second working port (fast-phaser function), only a certain threshold must be exceeded so that the associated check valve is opened and a fluid flow takes place directly from the first working port to the second working port.
  • the piston In order to suppress any fluid flow and to allow a stable operating condition of an internal combustion engine at a constant speed, the piston is transferred to a second position, the tank drain port of both working ports is formed closed by the outer annular lands and the first working port and the second working port respectively through the inner Ring webs are formed sealed.
  • the piston can be transferred to a third position, wherein the tank drain port of both working ports is formed closed by the outer annular webs.
  • the first working connection is formed with the supply connection and the first working connection is fluidly connectable to the second working connection.
  • the object is achieved with a method for operating a valve according to one of the preceding embodiments.
  • the tank drain connection of the second working connection in the first end position, is completely closed by an outer annular web.
  • the tank drain connection of the first working connection is throttled through an annular gap between an outer annular web and a groove-shaped recesses without control edges, and the first working connection is fluidly connected to the second working connection.
  • the second working port is fluidly connected to the supply port.
  • the method provides a fast phaser function via a bypass, which allows for a quick bypass of the fluid directly from the first chamber to the second chamber or vice versa.
  • An improved function in the lower temperature range results from the operation according to the invention of the valve with the outer annular webs, which in the end positions of the piston completely close the respectively assigned tank drain port, but throttles the opposite tank drain port free of control edges.
  • the control edge-free throttling of the opposite tank drain connection brings, for example, the advantage that the oil exchange works well even with viscous cold oil.
  • the method according to the invention compared to the operation of a pure fast phaser valve results in a slightly reduced adjustment speed in the lower speed range.
  • a preferred embodiment relates to the method for operating the valve, wherein in a first position, the tank drain port of both working ports is completely closed by the outer annular webs. Furthermore, the first working port is fluidly connected to the second working port, and the second working port is fluidly connected to the supply port.
  • the tank drain connection of both working connections in a second position, is completely closed by the outer annular webs, and the first working connection and the second working connection are each fluidly closed by the inner annular webs.
  • the tank drain port of both working ports is completely closed by the outer annular lands, the first work port is fluidly connected to the second work port, and the first work port A is fluidly connected to the supply port P.
  • the tank discharge connection of the first working connection is completely closed by an outer annular web and the tank discharge connection of the second working connection is throttled through an annular gap between an outer annular web and a groove-shaped recesses.
  • the transfer of the piston takes place continuously between the first end position and a second end position.
  • Each valve can be designed as a hydraulic valve and each hydraulic valve can be designed as a valve.
  • FIG. 1 shows a hydraulic valve 1 for adjusting a Schwenkmotorverstellers not shown according to an embodiment of the invention in a first switching position 10, shown in a longitudinal section.
  • the hydraulic valve 1 comprises a bushing 2 with a piston 4 displaceably arranged in a bore 3 along a longitudinal direction L.
  • the piston 4 is supported by a helical compression spring 5 on the bush 2 or on a disk 6 arranged in the bush 2 by a ring 7 ,
  • the bush 2 has a supply port P for supplying a hydraulic fluid and a first working port A and a second working port B, which are respectively provided as a radial recess or a plurality of radial recesses in the bush in the order A - P - B.
  • the supply connection P is protected from contamination by a sieve 8 arranged on the outside of the socket 2.
  • a band check valve 9 is arranged in the region of the supply termination on a female inside to prevent a backflow of hydraulic fluid in the direction of the pump.
  • the hydraulic valve 1 comprises a first and a second tank drain port T1, T2 for discharging the hydraulic fluid, which are each formed axially.
  • the tank outlet connections T1 and T2 may alternatively be connected to one another, for example via a central bore in the piston 4, so that the complete tank drain connection can take place via a single tank discharge connection T.
  • the described Tank drainage connections T1 and T2 are understood in this case to be a tank outlet assigned to the respective working connection A or B, both being led out of the valve by means of the single tank drain connection T.
  • the first working port A and the second working port B are each assigned a check valve 15, 16, wherein the first working port A and the second working port B by displacing the piston 4 via at least one of the check valves 15, 16 alternately with each other and / or with the supply port P and / or with one of the tank drain connections T1, T2 are connectable.
  • the hydraulic valve 1 five switch positions 10-14, wherein in a first, in FIG. 1 illustrated switching position 10 of the piston 4 of the second working port B via the bore 3 and an annular space formed therein around the piston 4 around with the supply port P and the first working port A via the bore 3 and a further explained below fluid path between a first piston attachment 18th and female inside with the first tank drain port T1 is connected.
  • the first switching position can also be understood as the first end position of the piston 4.
  • a second switching position 11 of the piston 4 the second working port B is connected to the supply port P and a connection between the first working port A with the first tank drain port T1 is interrupted by the piston cap 18, in particular by the outer annular rib 25, wherein Also in this position, the fluid path from the first working port A to the second working port B via the first working port A associated check valve 15 can be opened.
  • the tank drain connection T2 is closed by the annular web 27, which is arranged on the piston attachment 19.
  • the hydraulic valve 1 has a pure fast-phaser characteristic.
  • This second switching position can also be understood as the first position of the piston 4 within the control range of the fast-phaser characteristic.
  • a third switching position 12 of the piston 4 this is positioned in a middle position, in which a connection between the working ports A, B and the supply port P and the tank drain ports T1, T2 is completely interrupted.
  • This third switching position can also be understood as the second position of the piston 4 within the control range of the fast-phaser characteristic.
  • a fourth switching position 13 of the piston 4 the first working port A is connected to the supply port P and a connection between the second working port B with the second tank discharge port T2 is interrupted by a second piston attachment 19, in particular by the outer annular web 27.
  • a fluid path from the second working port B to the first working port A can be opened via the non-return valve 16 assigned to the second working port B by a pressure exceeding a threshold value.
  • the tank drain port T1 is closed by the annular web 25, which is arranged on the piston attachment 18.
  • This third switching position can also be understood as the third position of the piston 4 within the control range of the fast-phaser characteristic.
  • a fifth switching position of the piston 4 this is in a second end position.
  • the first working port A via the bore 3 and an annular space formed therein 17 around the piston 4 with the supply port P and the second working port B is via the bore 3 and a further explained below fluid path between the second piston attachment 19 and female inside connected to the second tank discharge port T2.
  • an outer ring land 25 closes the second tank discharge port T1 completely.
  • the fifth shift position can also be understood as the second end position of the piston 4.
  • a fluid path from the second working connection B to the first working connection A can also be opened via the non-return valve 16 assigned to the second working connection B.
  • the first working port A and the second working port B each have a check valve 15, 16 assigned to the outside of the piston 4. These are each arranged on the piston caps 18, 19, which surrounds the piston 4 and is connected to the piston 4 rigidly, for example by pressing or welding. As a result, the most compact construction possible of the hydraulic valve and the resulting piston assembly 20 can be easily and inexpensively formed.
  • the check valves 15, 16 are each provided as disc-shaped closing body, which are biased by a common compression spring 21 against the piston caps 18, 19 and so openings 22, 23 close, through which from the above-described pressure threshold hydraulic fluid through the check valves 15, 16 is Wegleitbar ,
  • a preassembled piston assembly 20 can be provided, which can be easily mounted in the socket 2.
  • Axial projections 46, 47 of the check valves 15, 16 allow a secure axial displacement on the piston 4th
  • the piston caps 18, 19 each have two inner annular ribs 24, 25 and two outer annular ribs 26, 27, which each have two cooperating with recesses in the sleeve 2 control edges 28, 29, 30, 31, 32, 33, 34, 35.
  • control edges 28 to 35 By means of these control edges 28 to 35, the volumetric flow of the hydraulic fluid can be controlled in an improved manner in such a way that a significant increase in the adjustment speed, in particular in the upper speed range, as well as a better force behavior are achieved becomes.
  • the groove-shaped recesses 36, 37 allow in conjunction with the control edges 28 to 30 and 33 to 35 a position-dependent opening and closing of the tank drain connections T1, T2, by in the switch positions 10 and 14 respectively between the outer ring lands 25 and 27 of the piston caps 18 and 19 and the bushing inside a fluid path between the first and the second working port A and with the first and the second tank drain port T1 and T2 is opened. So is in the in FIG. 1 shown first switching position 10 of the outer annular ridge 25 of the first piston attachment 18 in the region of the groove-shaped recess 36 and a fluid flow between the annular ridge 25 and the female inside towards Tankab Wegan gleich T1 is possible. How out FIG.
  • a distance A1 between an outer diameter 50 of the annular rib 25 and a groove bottom 51 of the groove-shaped recess 36 is formed smaller than a Distance A2 between groove side surfaces 52, 53 of the groove-shaped recess 36 and end faces 54, 55 of the annular web 25.
  • the distance A1 is formed smaller than the distance A2, so that a ratio of A2 to A1 is greater than 1.4 to 1. This creates a control edge-free orifice with a fluid flow in the direction of the tank discharge port T1, which is constant only in the end positions.
  • Concrete edge free concrete means that the throttling of the tank runoff almost alone by an annular surface between the annular rib 25 (or 27 in the fifth switching position or second end position) and the groove-shaped recess 36 (or 37 in the fifth switching position) is achieved.
  • the throttling is therefore made by the described annular gap, not by the Socket 2 and ring lands 25, 27 formed control edges.
  • outer annular web 27 of the second piston attachment 19 is located outside the groove-shaped recess 37, so that no fluid flow in the direction of the tank outlet connection T2 is possible due to the closed control edges 34, 35.
  • FIG. 7 shows the flow path characteristic of the hydraulic valve 1.
  • the flow path characteristic shows the resulting flow, depending on the position (five switching positions 10 to 14) of the piston. 4
  • the lines 40 and 40 ' show the volume flow from A to B and the lines 41 and 41' the volume flow from P to B during the first and the second switching position 10 and 11th
  • the lines 42 and 42 ' show the volume flow from P to A and the lines 43 and 43' the volume flow from B to A during the fourth and the fifth switching position 13 and 14th
  • connection A is open to T1 only in the first switching position 10.
  • connection B to T2 is, as shown by the lines 45 and 45 ', open only in the fifth switching position 14.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Multiple-Way Valves (AREA)
EP19153487.4A 2018-02-21 2019-01-24 Soupape hydraulique pour un dispositif de réglage de moteur oscillant d'un arbre à cames Active EP3530891B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018103915 2018-02-21
DE102019101159.0A DE102019101159A1 (de) 2018-02-21 2019-01-17 Hydraulikventil für einen Schwenkmotorversteller einer Nockenwelle

Publications (2)

Publication Number Publication Date
EP3530891A1 true EP3530891A1 (fr) 2019-08-28
EP3530891B1 EP3530891B1 (fr) 2021-03-03

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EP19153487.4A Active EP3530891B1 (fr) 2018-02-21 2019-01-24 Soupape hydraulique pour un dispositif de réglage de moteur oscillant d'un arbre à cames

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US12134976B2 (en) * 2022-03-07 2024-11-05 Mikuni Corporation Fluid control valve and valve timing changing device
US12209514B2 (en) * 2022-03-10 2025-01-28 Mikuni Corporation Fluid control valve unit and valve timing changing device

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1910392U (de) * 1962-09-19 1965-02-18 Barmag Barmer Maschf Vollhydraulische bremsvorrichtung.
DE102006012775A1 (de) 2006-03-17 2007-09-20 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102008055175A1 (de) * 2008-01-10 2009-07-16 Denso Corporation, Kariya Ventilzeitabstimmungseinsteller
DE102010005604A1 (de) * 2010-01-25 2011-07-28 Schaeffler Technologies GmbH & Co. KG, 91074 Druckmittelbetätigte Nockenwellenverstelleinrichtung für eine Brennkraftmaschine
EP2375014A1 (fr) 2010-04-10 2011-10-12 Hydraulik-Ring GmbH Dispositif de réglage d'un arbre à cames avec une soupape hydraulique
EP2796673A1 (fr) * 2013-04-22 2014-10-29 Hilite Germany GmbH Soupape centrale pour un moteur pivotant à l'ajustage
EP2905434A1 (fr) * 2014-02-06 2015-08-12 Hilite Germany GmbH Déphaseur oscillant doté d'une soupape hydraulique pour arbre à cames

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EP2375014A1 (fr) 2010-04-10 2011-10-12 Hydraulik-Ring GmbH Dispositif de réglage d'un arbre à cames avec une soupape hydraulique
EP2796673A1 (fr) * 2013-04-22 2014-10-29 Hilite Germany GmbH Soupape centrale pour un moteur pivotant à l'ajustage
EP2905434A1 (fr) * 2014-02-06 2015-08-12 Hilite Germany GmbH Déphaseur oscillant doté d'une soupape hydraulique pour arbre à cames

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US12134976B2 (en) * 2022-03-07 2024-11-05 Mikuni Corporation Fluid control valve and valve timing changing device
US12209514B2 (en) * 2022-03-10 2025-01-28 Mikuni Corporation Fluid control valve unit and valve timing changing device

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