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EP2466081A1 - Soupape hydraulique d'un d'un déphaseur d'arbre à cames - Google Patents

Soupape hydraulique d'un d'un déphaseur d'arbre à cames Download PDF

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Publication number
EP2466081A1
EP2466081A1 EP11186299A EP11186299A EP2466081A1 EP 2466081 A1 EP2466081 A1 EP 2466081A1 EP 11186299 A EP11186299 A EP 11186299A EP 11186299 A EP11186299 A EP 11186299A EP 2466081 A1 EP2466081 A1 EP 2466081A1
Authority
EP
European Patent Office
Prior art keywords
piston
valve
hydraulic
hydraulic fluid
connection part
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.)
Granted
Application number
EP11186299A
Other languages
German (de)
English (en)
Other versions
EP2466081B1 (fr
Inventor
Dietmar Schulze
André Selke
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.)
Hilite Germany GmbH
Original Assignee
Hilite Germany 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
Application filed by Hilite Germany GmbH filed Critical Hilite Germany GmbH
Priority to DE102012103300.5A priority Critical patent/DE102012103300B4/de
Publication of EP2466081A1 publication Critical patent/EP2466081A1/fr
Application granted granted Critical
Publication of EP2466081B1 publication Critical patent/EP2466081B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/34409—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear by torque-responsive means
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86574—Supply and exhaust
    • Y10T137/8667—Reciprocating valve
    • Y10T137/86694—Piston valve
    • Y10T137/8671—With annular passage [e.g., spool]

Definitions

  • the invention relates according to the preamble of claim 1, a hydraulic valve for a Schwenkmotorversteller.
  • a Schwenkmotorversteller with a hydraulic valve is known with which camshaft alternating torques can be used for faster adjustment.
  • camshaft alternating torques caused pressure peaks from the respectively to be emptied pressure chambers of the Schwenkmotorverstellers via a check valve in the flow of the oil pump slides.
  • the additional volume is available in addition to the normal volume flow of the oil pump for the pressure chamber to be filled.
  • a check valve is provided for both pivot directions.
  • the hydraulic valve has two working ports.
  • These two working ports each have, axially adjacent to one another, a normal connecting part and a connecting part for utilizing the pressure peaks as a result of the camshaft alternating torques.
  • the hydraulic pressure can be conducted from a supply connection to the work connection to be loaded, while the work connection to be relieved is led to a tank connection.
  • the DE 102 11 467 A1 concerns a central valve, which takes over the function of a so-called central screw and braces the rotor against the camshaft. Thus occur in a disadvantageous manner voltages in the hydraulic valve.
  • the object of the invention is to provide a Schwenkmotorversteller, which has a high control quality despite a high adjustment speed at low oil pump pressure.
  • non-return valves are provided in the hydraulic valve of the Schwenkmotorverstellers with which camshaft alternating torques for rapid adjustment or adjustment with low oil pressure can be used.
  • the oil pressure is very low, for example, when many consumers depart from the hydraulic circuit or when the oil pump is very small to reduce fuel consumption. Such low pressures can be below 1 bar.
  • the invention can play their particular advantage in three-cylinder engines and six-cylinder engines in V-arrangement.
  • the piston is designed such that this in the DE 10 2006 012 733 B4 and the DE 10 2006 012 775 B4 by the supply pressure already closed check valve of pressure to be acted upon working port A or B additionally closes.
  • shooting is here in addition to the complete closure also meant a state that leaves only a minimum volume flow through control edges in the annulus, in which the band-shaped check valve is used.
  • the check valve need not be designed as a band-shaped check valve, which is inserted into an annular space or an annular groove of the hydraulic valve. It is also possible, for example, to carry out the check valve as a ball check valve in a funnel-shaped valve seat, as such a ball check valve already from the DE 10 2007 012 967 B4 is known.
  • the check valve does not have to be effective radially. It is also possible to execute the check valve axially effective.
  • the method according to the invention can be used in a particularly advantageous manner for both pivoting directions of the camshaft adjustment. However, it is also possible to apply the method according to the invention only for the one direction of rotation and to provide a compensation spring in the other direction of rotation.
  • the hydraulic valve of the Schwenkmotorverstellers is designed as a central valve.
  • a central valve has space advantages.
  • external Hydraulic valve run the hydraulic channels for adjusting the camshaft from Schwenkmotorversteller to a separate timing drive cover with the screwed there hydraulic valve or to the cylinder head with the screwed there hydraulic valve.
  • the hydraulic lines from the swivel motor adjuster to the external hydraulic valve are associated with line losses.
  • the controls are not as dynamic implemented by the external hydraulic valve, as the central valve.
  • the likewise hydraulic central valve is arranged radially inside the rotor hub of the Schwenkmotorverstellers.
  • the hydraulic valve is designed as a central valve
  • the axial fixing of the hydraulic valve with respect to the camshaft can be carried out separately from the axial clamping of the rotor with respect to the camshaft.
  • This allows a great deal of freedom in comparison to central valves, which are also central screws, without having to consider structural mechanical problems. It must therefore find no high-strength material application. For example, as a material light metal - especially aluminum - find application.
  • the hydraulic control edges on the central valve can be designed precisely. On sealing rings - in particular O-rings - for gap bridging can be dispensed with.
  • the central valve can be made with a relatively uniform outer diameter, only relatively little material must be used, which makes the central valve cost.
  • the rotor may be welded or pressed with a micro-toothing.
  • the piston is completely pressure balanced in a particularly advantageous embodiment.
  • the camshaft can be designed in particular as a built-up camshaft.
  • Such built camshafts include a hollow tube on which the cams are shrunk.
  • Such built-up camshafts are inexpensive and lightweight.
  • Claim 4 shows a particularly advantageous embodiment of the invention, in which the hydraulic valve is used as a central valve within the rotor. Since thus the paths between the hydraulic valve and the pressure chambers are very kuzrz, such a hydraulic valve has advantages in the effectiveness and dynamics. Also go space advantages. If the central valve is designed as a central screw, it must be dimensioned accordingly to absorb the stresses to tension the rotor. The central valve is used within the meaning of this application even within the rotor when the camshaft is in the form of a hollow shaft.
  • Claim 5 shows a particularly advantageous embodiment of the invention, in which recesses are provided in the displaceable piston, which have a plurality of functions for guiding the hydraulic fluid.
  • the recesses direct the hydraulic fluid from a supply channel within the piston into the working chambers.
  • these recesses lead due to the camshaft alternating moments pressure peaks from the working chambers in the supply channel.
  • these recesses are not intended to remove hydraulic fluid to the tank drain.
  • These recesses may, for example, have annular grooves, so that the piston does not have to be oriented at an angle to the bore or the bushing. Such annular groove for distributing the hydraulic fluid over the circumference can also be incorporated in the inner wall of the socket.
  • the Schwenkmotorversteller 14 has a cylindrical stator 1 which is rotatably connected to the drive wheel 2.
  • the drive wheel 2 is a sprocket over which a chain, not shown, is guided.
  • the drive wheel 2 may also be a toothed belt wheel, via which a drive belt is guided as a drive element.
  • the stator 1 is drivingly connected to the crankshaft.
  • the stator 1 comprises a cylindrical stator base body 3, on the inside of which protrude webs 4 at equal intervals radially inwardly. Between adjacent webs 4 gaps 5 are formed, in which, via an in Fig. 2 controlled hydraulic valve 12 shown controlled, pressure medium is introduced.
  • the hydraulic valve 12 is designed as a central valve. Between adjacent webs 4 protrude wings 6, which project radially outward from a cylindrical rotor hub 7 of a rotor 8. These wings 6 divide the spaces 5 between the webs 4 in each case in two pressure chambers 9 and 10th
  • the webs 4 lie with their end faces sealingly against the outer circumferential surface of the rotor hub 7.
  • the wings 6 in turn lie with their end faces sealingly against the cylindrical inner wall of the stator main body 3.
  • the rotor 8 is rotatably connected to the camshaft 18. In order to change the angular position between the camshaft 18 and the drive wheel 2, the rotor 8 is rotated relative to the stator 1. For this purpose, depending on the desired direction of rotation, the pressure medium in the pressure chambers 9 or 10 is pressurized, while the respective other pressure chambers 10 or 9 are relieved to the tank. In order to pivot the rotor 8 counterclockwise relative to the stator 1 into the illustrated position, an annular first rotor channel in the rotor hub 7 is pressurized by the hydraulic valve 12. From this first rotor channel then lead further channels 11 in the pressure chambers 10. This first rotor channel is assigned to the first working port A.
  • the hydraulic valve 12 pressurizes a second annular rotor channel in the rotor hub 7.
  • This second rotor channel is assigned to the second working port B.
  • These two rotor channels are arranged with respect to a central axis 22 axially spaced from each other.
  • the Schwenkmotorverstellers 14 is placed on the designed as a hollow tube 16 built camshaft 18th For this purpose, the rotor 8 is placed on the camshaft 18.
  • the Schwenkmotorversteller 14 is by means of in Fig. 2 pivotable hydraulic valve 12 visible.
  • a sleeve 15 associated with the hydraulic valve 12 is inserted coaxially.
  • a hollow piston 19 is slidably guided against the force of a helical compression spring 24.
  • the helical compression spring 24 is supported on the one hand on the piston 19 and on the other hand fixed to the housing.
  • a shoulder 88 is provided within the piston 19, which connects to the end of the piston 19 toward a radial spring guide 103.
  • a plunger 20 of an electromagnetic actuator On camshaft outer side - ie rear - end of the bush 15 is located on the piston 19, a plunger 20 of an electromagnetic actuator.
  • the hollow piston 19 has axially spaced apart four circumferential cam grooves 28 to 31. Moreover, axially spaced from each other four recesses 41, 38, 39, 40 are provided in the bush 15. The axially outermost recesses 41, 40 are designed as through holes 25, 26. The axially inner recesses 38, 39, however, are each formed from a pair of a through hole 23, 27 and an inner ring groove 34, 33.
  • control edges between the control grooves 28, 29, 30, 31 and the adjacent recesses 41, 38, 39, 40 so-called control edges.
  • control edges we determined the amount of hydraulic fluid passed through, wherein at these control edges at a correspondingly large coverage of the flow of hydraulic fluid can be almost completely blocked.
  • locked control edge thus forms a sealing gap between the piston 19 and the sleeve 15th
  • the front two recesses 41, 38 are associated with the first working port A.
  • the rear two recesses 39, 40 are associated with the second working port B.
  • the foremost working port A is divided into two connecting parts A1, A *.
  • the rear working port B is also divided into two ports B1, B *.
  • the first - i. Foremost - recess 41 is associated with the first connection part A1 and provided for guiding hydraulic fluid in the pressure chambers 9 of the Schwenkmotorverstellers associated with a pivoting direction.
  • hydraulic fluid can also be conveyed to a first tank outlet T1 via this first connection part A1.
  • the second recess 38 is the second connection part A * associated and provided for discharging hydraulic fluid from these pressure chambers 9 to a arranged within the piston 19 supply channel 32. This diversion takes place when due to camshaft alternating torques, the pressure in these pressure chambers 9 increases accordingly.
  • the third recess 39 is the second connection part B * of the second working port B associated and provided for discharging hydraulic fluid from the pressure chambers 10 to the supply channel 32. This diversion takes place when due to camshaft alternating torques, the pressure in these pressure chambers 10 increases accordingly.
  • the fourth - i.e. The rearmost recess 40 is associated with the first connection part B1 of the second working connection B and is provided for guiding hydraulic fluid into the pressure chambers 10. Moreover, hydraulic fluid can also be conveyed from the pressure chambers 10 to a second tank outlet T2 via this connection part B1.
  • the two axially central ports A *, B * each have a band-shaped check valve 35 and 36, respectively.
  • the front check valve 35 is inserted into the annular inside the sleeve 15 circumferential inner ring groove 34 radially within the through hole 23 of the terminal A *.
  • the rear non-return valve 36 is inserted into the annular inner ring groove 33, which is annular in the bushing 15, inside the through-hole 27 of the connection B *.
  • Both check valves 35, 36 open independently of each other against small external pressures.
  • the two check valves 35, 36 separated from each other by means of a radially inwardly projecting web 37, which has a very small sealing gap to a very wide web 42 of the piston 19.
  • control grooves 29, 30, which are separated by means of radially outwardly projecting webs 43, 44 against the tank drains T1, T2 associated with control grooves 28, 31.
  • These two control grooves 28, 31 each lead to a tank outlet T1 or T2, when the piston 19 is in the corresponding position.
  • the second working port B is supplied with hydraulic pressure from a central supply channel 32 within the piston 19.
  • the hydraulic fluid is discharged from the first working port A associated pressure chambers 9 via the control groove 28 to the front tank drain T1, the purpose transverse holes 102nd in the socket 15 has.
  • the hydraulic fluid, together with the hydraulic fluid coming from the oil pump is fed into the second working port B.
  • Its second connection part B * is closed in this case by the wide web 42.
  • the check valve 36 is shut off from the internal pressure.
  • the hydraulic fluid is directed to the first working port A.
  • the hydraulic fluid flows from the supply channel 32 via the cam 29 in the recess 37 and then to the first working port A.
  • the hydraulic fluid from the second port B associated pressure chambers 10 is discharged via the control groove 31 to the rear tank outlet T1.
  • the rear non-return valve 36 opens and the hydraulic pressure from these pressure chambers 10 can be fed into the supply channel 32. From there, the hydraulic fluid, together with the hydraulic fluid coming from the oil pump, is fed into the first connection part A1 of the first working connection A.
  • the second connection part A * of the first working port A is closed in this case by the wide web 42.
  • the piston 19 can still be adjusted in a middle blocking position in which both working ports A, B are pressurized to a greater extent than the hydraulic fluid can be discharged.
  • the Schwenkmotorversteller 14 is fixed in this angular position.
  • the hydraulic valve 12 has a radial supply port P, which introduces the hydraulic fluid at the front end of the piston 19 through an opening 89 in the central supply passage 32 within the piston 19.
  • transverse bores 90 are provided at this front end in the bush 15, to which the hydraulic fluid is supplied via a sieve 100. From the cross holes 90 to the Openings 89, the hydraulic fluid is passed through a check valve 101, which shuts off pressure peaks within the supply channel 32 in the hydraulic valve 12 against the supply port P.
  • the openings 89 are adjacent to a plug 87 within the hollow piston 19, which closes the piston 19 at the front end.
  • Fig. 3 shows a hydraulic valve 44 also with a radial supply port P, but which lies axially between the two working ports A and B.
  • This supply connection P leads through bores 55 in a bushing 115 from the oil pump, not shown, of the internal combustion engine to an oil supply groove 43 in the piston 119.
  • This piston 119 is axially displaceable in a central bore 185 of the bushing 115.
  • the ⁇ lskisnut 43 thus divides in comparison to the previous embodiment, the wide web of the piston 119 in two webs 46, 47. From this ⁇ lmakerssnut 43, the hydraulic fluid through holes 48 in the bottom of this ⁇ lmakerssnut 43 is guided to a supply channel 132, which leads the hydraulic fluid to the respective pressure chambers 9 and 10 respectively.
  • Fig. 3 is the piston 45 in contrast to Fig. 2 shown with disengaged electromagnetic actuator or plunger 20.
  • the piston 119 is in the front position and guides the hydraulic fluid via the first connector A1 to the first working port A.
  • the associated second connector A * to use the camshaft alternating torques is blocked by the front web 47.
  • the other working port B is relieved via port B1 to the second tank outlet T2.
  • the supply channel 132 extends to within the piston 119, within which, however, a central channel 17 is guided to the two tank outlets T1, T2.
  • a tube 21 is inserted into the piston 119, on which at its two ends rings 45, 49 are pressed firmly. With these rings 45, 49, the tube 21 is immovably inserted into the piston 119, so that the two tank outflows T1, T2 are hydraulically separated from the supply port P.
  • Fig. 4 shows in a half section in a third embodiment, a hydraulic valve 54 for adjusting the Schwenkmotorverstellers 14 according to Fig. 1 ,
  • a second tank connection T2 terminates axially at the end of the bushing 215.
  • the first working connection A is divided again into the first connection part A1 and the second connection part A *.
  • the second working port B divides again into the first connection part B1 and the second connection part B *.
  • a hollow piston 219 axially closed on both sides is arranged to be axially displaceable.
  • a helical compression spring 24 and at the other end a plunger 20 of an electromagnetic actuator is supported.
  • the helical compression spring 24 abuts a bottom 56 at the rear end of the piston 219, whereas the plunger 20 bears against a bottom 57 at the front end of the piston 219.
  • the piston 219 has axially spaced from each other five circumferential annular grooves 58 to 62.
  • the annular groove 62 closest to the electromagnetic actuator is open to the second tank outlet T2.
  • the two working ports A, B associated annular grooves 60, 61 respectively have two axially spaced apart bores 63, 64 and 65, 66, which lead into lying within the hollow piston 219 supply channel 232.
  • an annular axially displaceable check valve 67, 68 is arranged in each case, which has a sleeve 69 and 70, respectively.
  • These two sleeves 69 and 70 are each supported by a small helical compression spring 71 and 72 on the side facing away from each other on the piston 219.
  • one end of the respective helical compression spring 71 or 72 is supported on the inner wall 73 or 74 of the annular groove 60 or 61, which is assigned to the connection part A * or B * for use of the camshaft alternating torques.
  • the other end of the small helical compression spring 71 or 72 is supported on an annular piston 75, 76, which extends radially outward from the sleeve 69, 70.
  • a part region 77 or 78 of the sleeve 69 or 70 which extends axially beyond the annular piston 75 or 76 and out of the sleeve 69 or 70 serves as spring centering.
  • the sleeve is 69 or 70 at the front end on the other inner wall 79 and 80 of the annular groove 60 and 61 at. Consequently, this inner wall 79 or 80 faces the first connection part A1 or B1, which is the first connection part A1 or B1 regular supply and discharge of hydraulic fluid in the pressure chambers 9 and 10 is assigned.
  • the closest standing holes 64, 65 in the piston 219 of the sleeve 69 and 70 are closed.
  • a ring space 81 or 82 lying radially outside these bores 64, 65 forms.
  • Both check valves 67, 68 thus open independently of each other against slight overpressures from the outside through the respective second connection part A * or B *.
  • the two check valves 67, 68 are separated from each other by means of a very wide web 83 of the piston 219. This wide web 83 is bounded by the inner walls 79, 80.
  • a bore 86 is provided, which guides the hydraulic fluid from the supply port P into the central supply channel 232.
  • the annular groove 59 is arranged, with the hydraulic fluid in the illustrated position of the piston 219 from the first connection part A1 of the first working port A to the first tank outlet T1 is passed.
  • the piston 219 is at the very rear.
  • the first supply part B1 of the second working port B is supplied with hydraulic pressure from the central supply channel 232 within the piston 219.
  • the internal pressure in the hydraulic valve 54 thereby supports the closing force of the rear non-return valve 68.
  • the hydraulic fluid is discharged from the working port A associated pressure chambers 9 via the annular groove 59 to the front tank outlet T1. If, within the pressure chambers 8 assigned to this working port A, the pressure due to camshaft alternating torques rises above the pressure inside the supply channel 232, then the front non-return valve 67 opens and the hydraulic pressure from the pressure chambers 9 can be fed into the supply channel 232 via the bores 64. From there The hydraulic fluid is fed together with the coming of the oil pump hydraulic fluid through the bores 66 in the working port B.
  • the connection B * is closed in this case by the wide web 83.
  • the hydraulic fluid is passed to the first working port A.
  • the hydraulic fluid flows from the supply channel 232 through the holes 63 in an annular space 84, in which the small helical compression spring 71 is arranged and then to the first working port A.
  • the hydraulic fluid from the second port B associated pressure chamber 10 via the annular groove 62 for rear tank drain T2 discharged.
  • the rear check valve 68 opens and the hydraulic pressure from these pressure chambers 10 can be fed into the supply passage 232. From there, the hydraulic fluid is fed together with the coming of the oil pump hydraulic fluid in the working port A.
  • the connection A * is closed in this case by the wide web 83.
  • Both check valves 67, 68 are designed such that they are arranged in an annular groove 60 and 61 of the piston 219 and are axially displaceable relative to the piston 219 against a spring force. It is also possible to perform only a check valve 67 axially displaceable.
  • the piston 219 is constructed as a built-up piston 219, as shown by the dotted line 97, only the one check valve 68 needs to be inserted in the annular groove 61 which is bounded by the inner wall 74 which is disposed on a ring 99. which is pressed onto a tubular portion 98 of the piston 119.
  • a micro-toothing which may look similar to a knurling.
  • the sleeve 70 can be designed as a closed component.
  • the sleeve 69 or 70 can also be made split.
  • the sleeve slotted so that the slotted sleeve 69 and 70 has a pitch.
  • the sleeve 69 and 70 at the not closer in the drawing apparent slot are bent and pushed over the piston 219 until the sleeve 69 and 70 in the annular groove 60 and 61 together snaps.
  • the piston 219 need not be designed as a built piston 219.
  • plastic as a material is beneficial.
  • a thermoplastic with a low coefficient of friction compared to steel or aluminum can be used. Plastic does not damage the running surfaces of the piston 219 during assembly.
  • piston 219 it is also possible to design the piston 219 as a built-in piston, in which all the annular grooves 58, 59, 60, 61 are formed by pressing rings similar to the ring 99.
  • the second embodiment according to Fig. 3 shows that by means of the tube 21, a connection between the two tank outlets T1, T2 is created.
  • this tube 21 can therefore be dispensed with a tank drain T1 or T2.
  • This is particularly advantageous if, due to the installation space conditions on the camshaft drive only the removal of hydraulic fluid in one direction is possible. This is the case, for example, with a dry toothed belt, since this does not provide a chain case for guiding the hydraulic fluid into an oil sump.
  • the hydraulic fluid can be discharged on both sides, can be dispensed with the tube 21 and the piston can be closed on both sides.
  • the piston can still be adjusted in a middle blocking position in which both working ports are pressurized to a greater extent than the hydraulic fluid can be removed.
  • the Schwenkmotorversteller is fixed in this angular position.
  • the pistons 19, 119, 219 of the aforementioned embodiments are pressure balanced.
  • connection parts A1, A * or B1, B * assigned to a working connection A or B must be separate in the outlet from the central bore 85, 185, 285, since the piston 19, 119, 219 must supply the hydraulic fluid separately. Outside the check valve, however, the two connection parts A1, A * or B1, B * can be brought together again. This combination can even take place within the bushing 15, 115, 215 or a rotor hub designed in one piece with the bushing.
  • the rotor 8 may be biased torsionally elastic in an alternative embodiment by means of a compensation spring against the stator 1.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
EP11186299.1A 2010-12-20 2011-10-24 Soupape hydraulique d'un actionneur d'un déphaseur d'arbre à cames Not-in-force EP2466081B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE102012103300.5A DE102012103300B4 (de) 2010-12-20 2012-04-17 Schwenkmotorversteller mit einem Zentralventil

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010061337.1A DE102010061337B4 (de) 2010-12-20 2010-12-20 Hydraulikventil für einen Schwenkmotorversteller

Publications (2)

Publication Number Publication Date
EP2466081A1 true EP2466081A1 (fr) 2012-06-20
EP2466081B1 EP2466081B1 (fr) 2017-03-15

Family

ID=44992564

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11186299.1A Not-in-force EP2466081B1 (fr) 2010-12-20 2011-10-24 Soupape hydraulique d'un actionneur d'un déphaseur d'arbre à cames

Country Status (5)

Country Link
US (1) US8752514B2 (fr)
EP (1) EP2466081B1 (fr)
JP (1) JP5941602B2 (fr)
CN (1) CN102562208B (fr)
DE (2) DE102010061337B4 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104110286A (zh) * 2013-04-22 2014-10-22 德国海利特有限公司 用于可逆式电动机调节器的中心阀
EP2924248A1 (fr) * 2014-03-13 2015-09-30 Hilite Germany GmbH Soupape hydraulique pour un déphaseur d'arbre à came
EP2927439A1 (fr) * 2014-02-27 2015-10-07 Hilite Germany GmbH Soupape hydraulique pour un moteur oscillant d'un arbre à came
WO2015198085A1 (fr) * 2014-06-24 2015-12-30 Hilite Germany Gmbh Vanne hydraulique pour un moteur à combustion interne
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EP1447602A1 (fr) * 2003-02-17 2004-08-18 Delphi Technologies, Inc. Soupape de contrôle de débit d'huile pour un déphaseur d'arbre à cames
DE102006012775A1 (de) * 2006-03-17 2007-09-20 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102006012775B4 (de) 2006-03-17 2008-01-31 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102006012733B4 (de) 2006-03-17 2008-03-27 Hydraulik-Ring Gmbh Fast cam phaser-Hydraulikkreis, insbesondere für Nockenwellenversteller, und entsprechendes Steuerelement
DE102007012967B4 (de) 2007-03-14 2009-01-08 Hydraulik-Ring Gmbh Ventil, insbesondere Cartridgeventil, mit integriertem Rückschlagsventil
US20090133652A1 (en) * 2007-11-28 2009-05-28 Denso Corporation Valve timing control apparatus
US20090133651A1 (en) * 2007-11-28 2009-05-28 Denso Corporation Valve timing control apparatus

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* Cited by examiner, † Cited by third party
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US9322419B2 (en) 2013-04-22 2016-04-26 Hilite Germany Gmbh Central valve for pivot motor actuator
CN104110287A (zh) * 2013-04-22 2014-10-22 德国海利特有限公司 用于可逆式电动机调节器的中心阀
CN104110286B (zh) * 2013-04-22 2017-04-12 德国海利特有限公司 用于可逆式电动机调节器的中心阀
CN104110286A (zh) * 2013-04-22 2014-10-22 德国海利特有限公司 用于可逆式电动机调节器的中心阀
EP2927439A1 (fr) * 2014-02-27 2015-10-07 Hilite Germany GmbH Soupape hydraulique pour un moteur oscillant d'un arbre à came
US9587528B2 (en) 2014-03-13 2017-03-07 Hilite Germany Gmbh Hydraulic valve for cam phaser
EP2924248A1 (fr) * 2014-03-13 2015-09-30 Hilite Germany GmbH Soupape hydraulique pour un déphaseur d'arbre à came
WO2015198085A1 (fr) * 2014-06-24 2015-12-30 Hilite Germany Gmbh Vanne hydraulique pour un moteur à combustion interne
CN105275908A (zh) * 2014-06-27 2016-01-27 德国海利特有限公司 液压阀
CN105275908B (zh) * 2014-06-27 2017-11-17 德国海利特有限公司 液压阀
EP3219943A1 (fr) * 2016-03-14 2017-09-20 ECO Holding 1 GmbH Piston pour une soupape hydraulique d'un moteur oscillant et soupape hydraulique pour un moteur oscillant d'un arbre à came
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
EP3267012A1 (fr) * 2016-07-08 2018-01-10 ECO Holding 1 GmbH Clapet anti-retour pour une bielle de moteur à combustion interne à compression variable
US10221760B2 (en) 2016-07-08 2019-03-05 ECO Holding 1 GmbH Check valve for connecting rod for variable compression internal combustion engine
US12134976B2 (en) * 2022-03-07 2024-11-05 Mikuni Corporation Fluid control valve and valve timing changing device

Also Published As

Publication number Publication date
CN102562208A (zh) 2012-07-11
JP5941602B2 (ja) 2016-06-29
EP2466081B1 (fr) 2017-03-15
DE102010061337A1 (de) 2012-06-21
US8752514B2 (en) 2014-06-17
US20120152195A1 (en) 2012-06-21
DE102012103300B4 (de) 2017-08-24
CN102562208B (zh) 2016-01-20
DE102012103300A1 (de) 2013-04-25
DE102010061337B4 (de) 2015-07-09
JP2012132449A (ja) 2012-07-12

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