EP3530891B1 - 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
EP3530891B1
EP3530891B1 EP19153487.4A EP19153487A EP3530891B1 EP 3530891 B1 EP3530891 B1 EP 3530891B1 EP 19153487 A EP19153487 A EP 19153487A EP 3530891 B1 EP3530891 B1 EP 3530891B1
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EP
European Patent Office
Prior art keywords
connection
working
working connection
valve
piston
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EP19153487.4A
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German (de)
English (en)
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EP3530891A1 (fr
Inventor
Falk Müller
André Seidenschwann
Patrick Ruppert
Udo Bartel
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Eco Holding 1 GmbH
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Eco Holding 1 GmbH
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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 swivel motor adjuster of a camshaft of an internal combustion engine of a motor vehicle.
  • the invention also relates to a valve for a swivel motor adjuster of a camshaft and a method for operating a valve for a swivel motor adjuster of a camshaft.
  • a switching position can first be proportionally controlled, in which the pressure peaks of the working connection to be relieved are blocked with respect to the working connection to be loaded.
  • a further switching position for using the camshaft alternation torques can be controlled in each connection.
  • the DE 10 2008 055 175 A1 discloses a hydraulic valve for a swivel motor adjuster, which has check valves arranged in the piston in the form of ball seat valves for utilizing camshaft alternating torques.
  • a central valve for a swivel motor adjuster can be found, the piston of which has one or more check valves on its outside for utilizing camshaft alternating torques.
  • One object of the invention is to create a valve for a swivel motor adjuster which, in a simple and compact design, enables better system behavior of a swivel motor adjuster, and to provide an efficient concept of a valve and a method for operating a valve of a camshaft adjuster that has improved cold behavior , ie enables an improved function in the lower temperature range.
  • a valve for a swivel motor adjuster of a camshaft is proposed, with a bushing with a piston arranged displaceably in a bore along a longitudinal direction between a first end position and a second end position, a supply connection for supplying a hydraulic fluid, at least one first working connection and a second working connection, and at least one tank drain port for discharging the hydraulic fluid, the first working port and the second working port being designed to be fluidly connectable to one another by suitable positioning of the piston, and the piston having outer annular webs arranged at its axially outer ends in order to surround the tank drain port in the first and the second to completely close the second end position, wherein in the first end position the connection between the first working connection and the tank drain connection and in the second end position the connection between d The second working connection and the tank drain connection are throttled without a control edge.
  • 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 and also 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 into an opposite chamber.
  • the connecting paths can be used for alternating flow, whereby hydraulic fluid flows out of the first chamber as well as flows into the second chamber of the vane adjuster. Accordingly, the fluid can also flow out of the second chamber and flow into the first chamber.
  • the fast phaser function provides a bypass, which enables the fluid to be quickly diverted directly from the first chamber into the second chamber or vice versa.
  • Check valves can also be used to ensure that the bypass function is only possible above a certain threshold value.
  • the improved function in the lower temperature range results from the arrangement according to the invention of the outer ring webs, which in the end positions of the piston completely close the respectively assigned tank outflow, but throttled the opposite tank outflow without control edges.
  • the control edge-free throttling of the opposite tank outlet has the advantage, for example, that the oil exchange works well even with viscous cold oil.
  • the valve according to the invention results in a slightly reduced adjustment speed in the lower speed range compared to a pure fast phaser valve.
  • the socket has two groove-shaped recesses in the region of the bore, which are each assigned to the outer ring webs.
  • the fluid flow can be switched or controlled through an annular gap which can be formed between an outer annular web and an associated groove-shaped recess.
  • the groove-shaped recesses are made wider than the wall thickness of the outer ring webs.
  • the piston has two inner ring webs between the outer ring webs, which are each assigned to the first working connection and the second working connection.
  • the inner ring webs are arranged spaced inwardly from the outer ring webs in the longitudinal direction of the piston. They are made wider in relation to the outer ring webs, since they have to completely close the working connections, depending on their position.
  • Arranged directly on the inner ring webs are check valves which determine the threshold value for releasing the bypass.
  • a distance between an outer diameter of the respective outer ring web and a groove base of the respective groove-shaped recess is smaller than a distance between the groove side surfaces of the groove-shaped recess and the end faces of the ring land.
  • a ratio A2 to A1 greater than 1.4 to 1 is preferably provided. This can significantly increase process reliability in production.
  • the piston can be moved into a first position, the tank outflow connection of both working connections being designed to be closed by the outer annular webs.
  • the second working port is designed to be fluidly connectable to the supply port and the first working port to the second working port.
  • 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 connection can be connected to the second working connection (fast phaser function), only a certain threshold value has to be exceeded so that the associated check valve is opened and a fluid flow takes place directly from the first working connection to the second working connection.
  • the piston In order to suppress any fluid flow and to enable a stable operating state of an internal combustion engine at constant speed, the piston can be moved into a second position, the tank drain connection of both working connections being closed by the outer ring webs and the first working connection and the second working connection each being closed by the inner one Ring webs are formed closed.
  • the piston can be moved into a third position, the tank outflow connection of both working connections being designed to be closed by the outer annular webs.
  • the first working port is designed to be fluidly connectable to the supply port and the first working port to the second working port.
  • the first working port and the second working port are each assigned a check valve and the first working port and the second working port can be alternately connected to one another and / or to the supply port and / or the tank drain port by moving the piston via at least one of the check valves.
  • the check valve (s) can be arranged, for example, on an outside of the piston.
  • 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 is completely closed by an outer ring web.
  • the tank outflow connection of the first working connection is throttled through an annular gap between an outer annular web and a groove-shaped recess without control edges, and the first working connection is fluidly connected to the second working connection.
  • the second working connection is fluidly connected to the supply connection.
  • the method provides a fast phaser function via a bypass, which enables the fluid to be quickly diverted directly from the first chamber to the second chamber or vice versa.
  • An improved function in the lower temperature range results from the operation of the valve according to the invention with the outer ring webs, which in the end positions of the piston completely close the respectively assigned tank drain connection, but throttled the opposite tank drain connection free of control edges.
  • the control edge-free throttling of the opposite tank drain connection has the advantage, for example, that the oil exchange works well even with viscous cold oil.
  • the method according to the invention results in a slightly reduced adjustment speed in the lower speed range compared to operating a pure fast phaser valve.
  • a preferred embodiment relates to the method for operating the valve, the tank outflow connection of both working connections being completely closed by the outer annular webs in a first position. Furthermore, the first working connection fluidly connected to the second working connection, and the second working connection is fluidically connected to the supply connection.
  • the tank outflow 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 outflow connection of both working connections is completely closed by the outer ring webs, the first working connection is fluidly connected to the second working connection, and the first working connection A is fluidically connected to the supply connection P.
  • the tank drain port of the first working port is completely closed by an outer annular web in the second end position and the tank drain port of the second working port is throttled free of control edges by an annular gap between an outer annular web and a groove-shaped recess.
  • the piston is moved 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.
  • Figure 1 shows a hydraulic valve 1 for adjusting a swivel motor adjuster, not shown, according to an exemplary 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 arranged displaceably in a bore 3 along a longitudinal direction L.
  • the piston 4 is supported by a helical compression spring 5 on the bushing 2 or on a washer 6 arranged by a ring 7 in the bushing 2 .
  • the socket 2 has a supply connection P for supplying a hydraulic fluid and a first working connection A and a second working connection B, which are each provided as a radial recess or a plurality of radial recesses in the socket in the sequence 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 on the inside of the socket in the area of the supply termination in order to prevent a backflow of hydraulic fluid in the direction of the pump.
  • the hydraulic valve 1 comprises a first and a second tank outflow connection T1, T2 for discharging the hydraulic fluid, which are each formed axially.
  • the tank outflow connections T1 and T2 can alternatively be connected to one another, for example, via a central bore in the piston 4, so that the entire tank outflow connection can take place via a single tank outflow connection T.
  • the described Tank outflow connections T1 and T2 are understood in this case as a tank outflow assigned to the respective working connection A or B, both being led out of the valve by means of the single tank outflow connection T.
  • the first working port A and the second working port B are each assigned a check valve 15, 16, the first working port A and the second working port B by moving the piston 4 via at least one of the check valves 15, 16 alternately with one another and / or with the supply port P and / or can be connected to one of the tank outflow connections T1, T2.
  • the hydraulic valve 1 has five switching positions 10-14, wherein in a first, in Figure 1 switching position 10 of the piston 4, the second working connection B via the bore 3 and an annular space 17 formed therein around the piston 4 with the supply connection P and the first working connection A via the bore 3 and a fluid path between a first piston attachment 18, which will be explained in more detail below and the inside of the socket is connected to the first tank drain port T1.
  • an outer annular web 27 completely closes the second tank outflow connection T2.
  • the first switching position can also be understood as the first end position of the piston 4.
  • a fluid path can also be opened from the first working port A to the second working port B via the check valve 15 assigned to the first working port A, and the hydraulic fluid becomes in a fast-phaser characteristic second working connection B passed through.
  • a second switching position 11 of the piston 4 the second working connection B is connected to the supply connection P and a connection between the first working connection A and the first tank outflow connection T1 is interrupted by the piston attachment 18, in particular by the outer annular web 25, whereby In this position, too, the fluid path from the first working connection A to the second working connection B can be opened via the check valve 15 assigned to the first working connection A.
  • the tank outflow connection T2 is also 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 the latter is positioned in a central position in which a connection between the working connections A, B and the supply connection P and the tank outflow connections 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 connection A is connected to the supply connection P and a connection between the second working connection B and the second tank outflow connection T2 is interrupted by a second piston attachment 19, in particular by the outer annular web 27.
  • a fluid path from the second working connection B to the first working connection A can be opened via the check valve 16 assigned to the second working connection B by a pressure exceeding a threshold value.
  • the tank outflow connection T1 is also 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 the latter is in a second end position.
  • the first working connection A is via the bore 3 and an annular space 17 formed therein around the piston 4 with the supply connection P and the second working connection B is via the bore 3 and a fluid path between the second piston attachment 19 and the inside of the bushing, which will be explained in more detail below connected to the second tank drain port T2.
  • an outer ring web 25 closes the second tank outflow connection T1 complete.
  • the fifth switching position can also be understood as the second end position of the piston 4.
  • a fluid path can also be opened from the second working connection B to the first working connection A via the check valve 16 assigned to the second working connection B.
  • first working port A and the second working port B are each assigned a check valve 15, 16 on the outside of the piston 4. These are each arranged on the piston attachments 18, 19, which surrounds the piston 4 and is rigidly connected to the piston 4, for example by pressing or welding. This enables a construction of the hydraulic valve that is as compact as possible, and the piston assembly 20 that is produced in this way can be designed simply and inexpensively.
  • Axial projections 46, 47 of the check valves 15, 16 allow secure axial displacement on the piston 4.
  • the piston attachments 18, 19 each have two inner ring webs 24, 25 and two outer ring webs 26, 27, which each have two control edges 28, 29, 30, 31, 32, 33, 34, 35 that interact with recesses in the bushing 2.
  • control edges 28 to 35 the volume 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 is achieved becomes.
  • the control edges 28 to 35 of the inner and outer annular webs 24 to 27 interact with the working connections A, B as radial recesses 38, 39 in the socket 2 and two groove-shaped recesses 36, 37 in the area of the bore 3, the groove-shaped recesses 36 , 37 are arranged in the axial direction between the working port A or B and the associated tank drain port T1 or T2.
  • the groove-shaped recesses 36, 37 in conjunction with the control edges 28 to 30 and 33 to 35, allow the tank drain connections T1, T2 to be opened and closed depending on the position 19 and the inside of the socket, a fluid path is opened between the first and the second working connection A or with the first and the second tank outflow connection T1 and T2, respectively.
  • FIG. 1 The first switching position 10 shown, the outer annular web 25 of the first piston attachment 18 in the area of the groove-shaped recess 36 and a fluid flow between the annular web 25 and the inside of the socket in the direction of the tank drain connection T1 is possible.
  • Figure 8 As can be seen, which shows an enlarged section of the hydraulic valve 1 in the first switching position 10 or the first end position, in this first end position a distance A1 between an outer diameter 50 of the annular web 25 and a groove base 51 of the groove-shaped recess 36 is smaller than a Distance A2 between groove side surfaces 52, 53 of groove-shaped recess 36 and end faces 54, 55 of annular web 25.
  • a relatively high tank throttling is created by the described design of the piston 4 and the bushing 2 outside the end positions 10, 14. In the end positions, however, the respective pressure chambers can be quickly emptied.
  • the specified ratio between A2 and A1 thus enables a lower throttling of the fluid flow in the direction T1 in the first end position shown, this lower throttling being able to be used to more quickly empty the pressure chamber of the swivel motor adjuster assigned to the working connection A.
  • the outer ring web 27 of the second piston attachment 19, on the other hand, is located outside the groove-shaped recess 37, so that no fluid flow in the direction of the tank outflow connection T2 is possible through the closed control edges 34, 35.
  • both outer annular webs 25 and 27 are located outside the groove-shaped recesses 36 and 37, so that through the closed control edges 34, 35, 28, 29 no fluid flow in the direction of the tank outflow connections T1 or .T2 is possible.
  • Figure 7 shows the volume flow / travel characteristic curve of hydraulic valve 1.
  • the volume flow / travel characteristic curve shows the resulting volume flow, depending on the position (five switching positions 10 to 14) of piston 4.
  • Lines 40 and 40 ' show the volume flow from A to B and lines 41 and 41' show the volume flow from P to B during the first and second switching positions 10 and 11.
  • the middle position 12 is reached, in which a connection between the working connections A, B and the supply connection P is reached as well as the tank drain connections T1, T2 is completely interrupted.
  • Lines 42 and 42 ' show the volume flow from P to A and lines 43 and 43' show the volume flow from B to A during the fourth and fifth switching positions 13 and 14.
  • connection A to T1 is only open in the first switching position 10.
  • connection B to T2 is, as shown by the lines 45 and 45 ', only open 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)

Claims (16)

  1. Soupape (1) pour un dispositif de réglage à moteur oscillant d'un arbre à cames, comportant une douille (2) dotée d'un piston (4) disposé de manière déplaçable dans un alésage (3) le long d'une direction longitudinale (L) entre une première position finale et une deuxième position finale,
    un raccord d'alimentation (P) pour l'acheminement d'un fluide hydraulique,
    au moins un premier raccord de travail (A) et un deuxième raccord de travail (B),
    ainsi qu'au moins un raccord de sortie de réservoir (T1, T2) pour l'évacuation du fluide hydraulique,
    le premier raccord de travail (A) et le deuxième raccord de travail (B) étant réalisés de manière à pouvoir être reliés fluidiquement l'un à l'autre par positionnement approprié du piston,
    et le piston (4) comprenant respectivement des listels extérieurs (25, 27) disposés à ses extrémités axialement extérieures, afin de fermer complètement le raccord de sortie de réservoir (T1, T2) dans la première ou la deuxième position finale et, dans la première position finale, la liaison entre le premier raccord de travail (A) et le raccord de sortie de réservoir (T1) et, dans la deuxième position finale, la liaison entre le deuxième raccord de travail (B) et le raccord de sortie de réservoir (T2) étant étranglées sans arête de commande, de telle sorte que l'étranglement puisse être obtenu pratiquement uniquement par une surface annulaire entre le listel (25, 27) et un évidement (36, 37) en forme de rainure, associé au listel (25, 27), de la douille (2) dans la région de l'évidement (3).
  2. Soupape (1) selon la revendication 1, caractérisée en ce que les évidements (36, 37) en forme de rainures sont disposés respectivement entre le raccord de travail (A, B) et le raccord de sortie de réservoir (T1, T2) dans la direction longitudinale (L).
  3. Soupape (1) selon l'une des revendications 1 et 2, caractérisée en ce que le piston (4) comprend, entre les listels extérieurs (25, 27), deux listels intérieurs (24, 26), lesquels sont associés respectivement au premier raccord de travail (A) et au deuxième raccord de travail (B) .
  4. Soupape (1) selon l'une des revendications 2 et 3, caractérisée en ce que, dans la première position finale ou la deuxième position finale, une distance (A1) entre un diamètre extérieur (50, 60) du listel extérieur respectif (25, 27) et un fond de rainure (51, 61) de l'évidement (36, 37) en forme de rainure respectif est réalisée de manière inférieure à une distance (A2) entre des surfaces latérales de rainure (52, 53, 62, 63) de l'évidement (36, 37) en forme de rainure et des côtés frontaux (54, 55, 64, 65) du listel (25, 27).
  5. Soupape (1) selon la revendication 4, caractérisée en ce qu'un rapport A2:A1 est supérieur à 1,4:1.
  6. Soupape (1) selon l'une des revendications 1 à 5, caractérisée en ce que le piston (4) peut être transféré à une première position, le raccord de sortie de réservoir (T1, T2) des deux raccords de travail (A, B) étant réalisé de manière fermée par les listels extérieurs (25, 27) et le deuxième raccord de travail (B) étant réalisé de manière à pouvoir être relié fluidiquement au raccord d'alimentation (P) et le premier raccord de travail (A) étant réalisé de manière à pouvoir être relié fluidiquement au deuxième raccord de travail (B) .
  7. Soupape (1) selon l'une des revendications 1 à 6, caractérisée en ce que le piston (4) peut être transféré à une deuxième position, le raccord de sortie de réservoir (T1, T2) des deux raccords de travail (A, B) étant réalisé de manière fermée par les listels extérieurs (25, 27) et le premier raccord de travail (A) et le deuxième raccord de travail (B) étant réalisés de manière fermée respectivement par les listels intérieurs (24, 26).
  8. Soupape (1) selon l'une des revendications 1 à 7, caractérisée en ce que le piston (4) peut être transféré à une troisième position, le raccord de sortie de réservoir (T1, T2) étant réalisé de manière fermée par les listels extérieurs (25, 27) et le premier raccord de travail (A) étant réalisé de manière à pouvoir être relié fluidiquement au raccord d'alimentation (P) et le premier raccord de travail (A) étant réalisé de manière à pouvoir être relié fluidiquement au deuxième raccord de travail (B) .
  9. Soupape (1) selon l'une des revendications 1 à 8, caractérisée en ce qu'une soupape anti-retour (15, 16) est associée respectivement au premier raccord de travail (A) et au deuxième raccord de travail (B), et le premier raccord de travail (A) et le deuxième raccord de travail (B), par un déplacement du piston (4), peuvent être, par le biais d'au moins l'une des soupapes anti-retour (15, 16), reliés alternativement l'un à l'autre et/ou au raccord d'alimentation (P) et/ou au raccord de sortie de réservoir (T1, T2).
  10. Dispositif de réglage à moteur oscillant doté d'une soupape (1) selon l'une des revendications précédentes, la soupape (1) étant prévue comme soupape centrale.
  11. Procédé de fonctionnement d'une soupape (1) selon l'une des revendications 1 à 10, dans lequel, dans la première position finale,
    le raccord de sortie de réservoir (T2) du deuxième raccord de travail (B) est fermé complètement par un listel extérieur (27),
    le raccord de sortie de réservoir (T1) du premier raccord de travail (A) est étranglé sans arête de commande par un interstice annulaire entre un listel extérieur (25) et un évidement (36) en forme de rainure, de telle sorte que l'étranglement puisse être obtenu pratiquement uniquement par une surface annulaire entre le listel (25) et l'évidement (36) en forme de rainure, associé au listel (25), de la douille (2) dans la région de l'évidement (3),
    le premier raccord de travail (A) est relié fluidiquement au deuxième raccord de travail (B), et
    le deuxième raccord de travail (B) est relié fluidiquement au raccord d'alimentation (P).
  12. Procédé de fonctionnement d'une soupape (1) selon la revendication 11, dans lequel, dans la première position,
    le raccord de sortie de réservoir (T1, T2) des deux raccords de travail (A, B) est réalisé de manière complètement fermée par les listels extérieurs (25, 27), le premier raccord de travail (A) est relié fluidiquement au deuxième raccord de travail (B), et
    le deuxième raccord de travail (B) est relié fluidiquement au raccord d'alimentation (P).
  13. Procédé de fonctionnement d'une soupape (1) selon la revendication 11 ou 12, dans lequel, dans la deuxième position,
    le raccord de sortie de réservoir (T1, T2) des deux raccords de travail (A, B) est fermé complètement par les listels extérieurs (25, 27), et
    le premier raccord de travail (A) et le deuxième raccord de travail (B) sont fermés fluidiquement respectivement par les listels intérieurs (24, 26).
  14. Procédé de fonctionnement d'une soupape (1) selon l'une des revendications 11 à 13, dans lequel, dans la troisième position,
    le raccord de sortie de réservoir (T1, T2) des deux raccords de travail (A, B) est complètement fermé par les listels extérieurs (25, 27),
    le premier raccord de travail (A) est relié fluidiquement au deuxième raccord de travail (B), et
    le premier raccord de travail (A) est relié fluidiquement au raccord d'alimentation (P).
  15. Procédé de fonctionnement d'une soupape (1) selon l'une des revendications 11 à 14, dans lequel, dans la deuxième position finale,
    le raccord de sortie de réservoir (T1) du premier raccord de travail (A) est fermé complètement par un listel extérieur (25),
    le raccord de sortie de réservoir (T2) du deuxième raccord de travail (B) est étranglé sans arête de commande par un interstice annulaire entre un listel extérieur (27) et un évidement (37) en forme de rainure, de telle sorte que l'étranglement puisse être obtenu pratiquement uniquement par une surface annulaire entre le listel (27) et l'évidement (37) en forme de rainure, associé au listel (27), de la douille (2) dans la région de l'évidement (3),
    le premier raccord de travail (A) est relié fluidiquement au deuxième raccord de travail (B), et
    le premier raccord de travail (A) est relié fluidiquement au raccord d'alimentation (P).
  16. Procédé de fonctionnement d'une soupape (1) selon l'une des revendications 11 à 15, dans lequel le transfert du piston (4) entre la première position finale et une deuxième position finale s'effectue de manière continue.
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

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EP3530891B1 true EP3530891B1 (fr) 2021-03-03

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Family Cites Families (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.
DE102006012775B4 (de) 2006-03-17 2008-01-31 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
JP4518149B2 (ja) * 2008-01-10 2010-08-04 株式会社デンソー バルブタイミング調整装置
DE102010005604A1 (de) * 2010-01-25 2011-07-28 Schaeffler Technologies GmbH & Co. KG, 91074 Druckmittelbetätigte Nockenwellenverstelleinrichtung für eine Brennkraftmaschine
DE102010045358A1 (de) 2010-04-10 2011-10-13 Hydraulik-Ring Gmbh Schwenkmotornockenwellenversteller mit einem Hydraulikventil
EP2796673B1 (fr) * 2013-04-22 2018-03-07 Hilite Germany GmbH Soupape centrale pour un moteur pivotant à l'ajustage
US9341090B2 (en) * 2014-02-06 2016-05-17 Hilite Germany Gmbh Oscillating-motor camshaft adjuster having a hydraulic valve

Non-Patent Citations (1)

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

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