EP2466081A1 - Hydraulic valve for a camshaft phaser - Google Patents

Hydraulic valve for a camshaft phaser 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)
French (fr)
Other versions
EP2466081B1 (en
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/en
Publication of EP2466081A1 publication Critical patent/EP2466081A1/en
Application granted granted Critical
Publication of EP2466081B1 publication Critical patent/EP2466081B1/en
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.

Abstract

The hydraulic valve (12) has a connection part (A1) of a working connection (A) for guidance of hydraulic fluid into a pressure chamber of a swivel motor adjuster. A piston (19) is equipped, where another connection part locks in a position of a feed line of hydraulic fluid from a supply channel (32) to the pressure chamber.

Description

Die Erfindung betrifft gemäß dem Oberbegriff von Patentanspruch 1 ein Hydraulikventil für einen Schwenkmotorversteller.The invention relates according to the preamble of claim 1, a hydraulic valve for a Schwenkmotorversteller.

Aus der DE 10 2006 012 733 B4 und der DE 10 2006 012 775 B4 ist bereits ein Schwenkmotorversteller mit einem Hydraulikventil bekannt, mit welchem Nockenwellenwechselmomente zur schnelleren Verstellung genutzt werden können. Dazu werden infolge der Nockenwellenwechselmomente bedingte Druckspitzen aus den jeweils zu entleerenden Druckkammern des Schwenkmotorverstellers über ein Rückschlagventil in den Strom der Ölpumpe gleitet. Somit steht das Zusatzvolumen zusätzlich zum normalen Volumenstrom der Ölpumpe für die zu befüllenden Druckkammer zur Verfügung. Um die schnellere Verstellung in beiden Schwenkrichtungen zu ermöglichen, ist für beide Schwenkrichtungen jeweils ein Rückschlagventil vorgesehen. Konstruktiv weist das Hydraulikventil dazu zwei Arbeitsanschlüssen auf. Diese beiden Arbeitsanschlüsse weisen jeweils axial benachbart zueinander einen normalen Anschlussteil und einen Anschlussteil zur Nutzung der Druckspitzen infolge der Nockenwellenwechselmomente auf. Der hydraulische Druck ist von einem Versorgungsanschluss auf den zu belastenden Arbeitsanschluss leitbar, während der zu entlastende Arbeitsanschluss auf einen Tankanschluss geführt wird.From the DE 10 2006 012 733 B4 and the DE 10 2006 012 775 B4 already a Schwenkmotorversteller with a hydraulic valve is known with which camshaft alternating torques can be used for faster adjustment. For this purpose, due to the 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. Thus, the additional volume is available in addition to the normal volume flow of the oil pump for the pressure chamber to be filled. In order to enable the faster adjustment in both pivoting directions, a check valve is provided for both pivot directions. Constructively, 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.

Um auch bei Verbrennungsmotoren mit sehr stark schwankenden Nockenwellenwechselmomenten die Regelgüte hoch zu halten, sieht die nicht vorveröffentlichte DE 10 2010 014 500.9 vor, dass eine Schaltstellung des Hydraulikventils proportional ansteuerbar ist, in welcher die Druckspitzen des zu entlastenden Arbeitsanschluss gegenüber dem Versorgungsanschluss und dem zu belastenden Arbeitsanschluss gesperrt sind.In order to keep the quality of control high in internal combustion engines with very fluctuating camshaft alternating torques, the not previously published DE 10 2010 014 500.9 before, that a switching position of the hydraulic valve can be proportionally controlled, in which the pressure peaks of the work port to be relieved against the supply connection and the work connection to be loaded are blocked.

Die DE 102 11 467 A1 betrifft ein Zentralventil, das die Funktion einer sogenannten Zentralschraube übernimmt und den Rotor gegen die Nockenwelle verspannt. Damit treten in nachteilhafter Weise Spannungen im hydraulischen Ventil auf.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.

Aus der EP 1 476 642 B1 ist bereits ein Hydraulikventil für einen Schwenkmotorversteller bekannt, das zwei hohle Kolben aufweist, die über eine Spiralfeder aneinander abgestützt sind. Damit ist ein Spalt zwischen den beiden Kolben öffenbar und schließbar.From the EP 1 476 642 B1 A hydraulic valve for a Schwenkmotorversteller is already known, which has two hollow piston, which are supported by a coil spring to each other. This is a gap between the two pistons openable and closable.

Aufgabe der Erfindung ist es, einen Schwenkmotorversteller zu schaffen, der trotz einer hohen Verstellgeschwindigkeit bei niedrigem Ölpumpendruck eine hohe Regelgüte aufweist.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.

Diese Aufgabe wird erfindungsgemäß mit den Merkmalen von Patentanspruch 1 gelöst.This object is achieved with the features of claim 1.

In besonders vorteilhafter Weise sind im Hydraulikventil des Schwenkmotorverstellers Rückschlagventile vorgesehen, mit denen Nockenwellenwechselmomente zur schnellen Verstellung bzw. zur Verstellung mit geringem Öldruck nutzbar sind. Der Öldruck ist beispielsweise dann sehr gering, wenn viele Verbraucher vom Hydraulikkreis abgehen oder wenn die Ölpumpe zur Verringerung des Kraftstoffverbrauchs sehr klein dimensioniert ist. Solche niedrigen Drücke können unter 1 bar liegen.In a particularly advantageous manner, 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.

Dieses auch in der DE 10 2006 012 733 B4 und der DE 10 2006 012 775 B4 dargestellte Hydraulikkonzept zur schneller Nockenwellenverstellung mittels Rückschlagventilen funktioniert prinzipiell umso besser,

  • je höher der Ölpumpendruck ist,
  • je stärker die Nockenwellenwechselmomente sind,
  • je dichter die Rückschlagventile sind und
  • umso geringer die Vorspannung dieser Rückschlagventile ist.
This also in the DE 10 2006 012 733 B4 and the DE 10 2006 012 775 B4 shown hydraulic concept for quick camshaft adjustment by means of check valves works in principle all the better
  • the higher the oil pump pressure,
  • the stronger the camshaft alternating torques are,
  • the closer the check valves are and
  • the lower the bias of these check valves.

Denn mit steigender Vorspannung steigt auch der notwendige Druck, um das Rückschlagventil zu öffnen. Die Dichtheit hängt aber mit der Vorspannung zusammen, so dass hier ein Optimierungsprozess notwendig ist. In diesem Optimierungsprozess spielen noch die Qualität und damit die Kosten des elektromagnetischen Stellgliedes zur Verschiebung des Kolbens eine Rolle, da mit zunehmenden Anteil der genutzten Nockenwellenwechselmomente die Anforderungen an die Regelbarkeit des Hydraulikventils bzw. der dieses regelnden Elektronik steigen.Because with increasing bias also increases the pressure necessary to open the check valve. The tightness is related to the bias, so that an optimization process is necessary here. In this optimization process, the quality and thus the costs of the electromagnetic actuator for the displacement of the piston also play a role, because with an increasing proportion of the used camshaft alternating torques Demands on the controllability of the hydraulic valve or of this regulating electronics increase.

Die Nockenwellenwechselmomente sind umso stärker, je geringer die Anzahl der Zylinder pro Nockenwelle - d.h. pro Zylinderbank - ist. Damit kann die Erfindung im besonderen Maße ihren Vorteil bei Dreizylindermotoren und Sechszylindermotoren in V-Anordung ausspielen.The smaller the number of cylinders per camshaft - i. per cylinder bank - is. Thus, the invention can play their particular advantage in three-cylinder engines and six-cylinder engines in V-arrangement.

Erfindungsgemäß ist der Kolben derart ausgeführt, dass dieser das bei der DE 10 2006 012 733 B4 und der DE 10 2006 012 775 B4 durch den Versorgungsdruck ohnehin bereits geschlossene Rückschlagventil der mit Druck zu beaufschlagenden Arbeitsanschlusses A bzw. B zusätzlich verschließt. Unter "Verschießen" ist hier neben dem kompletten Verschluss auch ein Zustand gemeint, der über Steuerkanten lediglich einen minimalen Volumenstrom in den Ringraum lässt, in welchem das bandförmige Rückschlagventil eingesetzt ist.According to the invention, 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. By "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.

Dabei muss das Rückschlagventil jedoch nicht als bandförmiges Rückschlagventil ausgeführt sein, welches in einen Ringraum bzw. eine Ringnut des Hydraulikventils eingesetzt ist. Es ist beispielsweise auch möglich, das Rückschlagventil als Kugelrückschlagventil in einem trichterförmigen Ventilsitz auszuführen, wie ein solches Kugelrückschlagventil bereits aus der DE 10 2007 012 967 B4 bekannt ist.However, 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.

Das Rückschlagventil muss aber nicht radial wirksam sein. Es ist auch möglich, das Rückschlagventil axial wirksam auszuführen.The check valve does not have to be effective radially. It is also possible to execute the check valve axially effective.

Das erfindungsgemäße Verfahren kann in besonders vorteilhafter Weise für beide Schwenkrichtungen der Nockenwellenverstellung Anwendung finden. Es ist jedoch auch möglich, das erfindungsgemäße Verfahren nur für die eine Drehrichtung anzuwenden und in der anderen Drehrichtung eine Kompensationsfeder vorzusehen.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.

Gemäß einem Vorteil der Erfindung ist das hydraulische Ventil des Schwenkmotorverstellers als Zentralventil ausgeführt. Ein solches Zentralventil hat Bauraumvorteile. Außer Zentralventilen gibt es noch die dezentralen bzw. externen Hydraulikventile zur Betätigung des Schwenkmotorverstellers. Beim externen Hydraulikventil verlaufen die Hydraulikkanäle zur Nockenwellenverstellung vom Schwenkmotorversteller zu einem gesonderten Steuertriebdeckel mit dem dort eingeschraubten Hydraulikventil oder aber zum Zylinderkopf mit dem dort eingeschraubten Hydraulikventil. Mit den hydraulischen Leitungen vom Schwenkmotorversteller zum externen Hydraulikventil gehen Leitungsverluste einher. Zudem werden die Steuerungen vom externen Hydraulikventil nicht so dynamisch umgesetzt, wie beim Zentralventil. Das ebenfalls hydraulische Zentralventil ist radial innerhalb der Rotornabe des Schwenkmotorverstellers angeordnet.According to an advantage of the invention, the hydraulic valve of the Schwenkmotorverstellers is designed as a central valve. Such a central valve has space advantages. In addition to central valves, there are also the decentralized or external hydraulic valves for actuating the Schwenkmotorverstellers. When 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. In addition, 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.

Wird das Hydraulikventil als Zentralventil ausgeführt, so kann die axiale Festlegung des Hydraulikventils gegenüber der Nockenwelle getrennt von der axialen Verspannung des Rotors gegenüber der Nockenwelle ausgeführt sein. Dies ermöglicht gegenüber Zentralventilen, die zugleich Zentralschraube sind, einen großen Gestaltungsspielraum, ohne dass strukturmechanische Probleme zu berücksichtigen sind. Es muss somit kein hochfester Werkstoff Anwendung finden. Beispielsweise kann als Werkstoff Leichtmetall - insbesondere Aluminium - Anwendung finden. Auch können die hydraulischen Steuerkanten am Zentralventil genau ausgelegt werden. Auf Dichtringe - insbesondere O-Ringe - zur Spaltüberbrückung kann verzichtet werden. Da kein großer Schraubenkopf am Zentralventil notwendig ist, sondern das Zentralventil mit einem relativ einheitlichen Außendurchmesser gefertigt sein kann, muss nur relativ wenig Material eingesetzt werden, was das Zentralventil kostengünstig macht. Um den Rotor dabei dennoch mit der Nockenwelle drehfest zu verbinden, kann der Rotor aufgeschweißt sein oder mit einer Mikroverzahnung aufgepresst sein. In einer besonders vorteilhaften Ausgestaltung ist es auch möglich, den Rotor mit einer Mutter gegen einen Absatz auf der Nockenwelle axial zu verspannen. Die Mutter kann dabei auf ein Außengewinde am Ende der Nockenwelle aufgeschraubt sein. Die Mutter hält das Zentralventil frei von Spannungen.If 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. Also, 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. Since no large screw head on the central valve is necessary, but 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. In order to non-rotatably connect the rotor while still with the camshaft, the rotor may be welded or pressed with a micro-toothing. In a particularly advantageous embodiment, it is also possible to axially clamp the rotor with a nut against a shoulder on the camshaft. The nut can be screwed onto an external thread at the end of the camshaft. The mother keeps the central valve free of tension.

Der Kolben ist in einer besonders vorteilhaften Ausgestaltung komplett druckausgeglichen.The piston is completely pressure balanced in a particularly advantageous embodiment.

Die Nockenwelle kann insbesondere als gebaute Nockenwelle ausgeführt sein. Solche gebauten Nockenwellen umfassen ein Hohlrohr, auf das die Nocken aufgeschrumpft sind. Solche gebauten Nockenwellen sind kostengünstig und leicht.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.

Patentanspruch 4 zeigt eine besonders vorteilhafte Ausgestaltung der Erfindung, bei welcher das Hydraulikventil als Zentralventil innerhalb des Rotors eingesetzt ist. Da somit die Wege zwischen dem Hydraulikventil und den Druckkammern sehr kuzrz sind, hat eine solches Hydraulikventil Vorteile in der Effektivität und der Dynamik. Auch gehen Bauraumvorteile einher. Ist das Zentralventil als Zentralschraube ausgeführt, muss es entsprechend dimensioniert sein, um die Spannungen zur Verspannung des Rotors aufzunehmen. Das Zentralventil ist im Sinne dieser Anmeldung auch dann noch innerhalb des Rotors eingesetzt, wenn die Nockenwelle als Hohlwelle dazwischen liegt.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.

Patentanspruch 5 zeigt eine besonders vorteilhafte Ausgestaltung der Erfindung, bei welcher im verschiebbaren Kolben Ausnehmungen vorgesehen sind, die mehrere Funktionen zur Leitung des Hydraulikfluids haben. Die Ausnehmungen leiten das Hydraulikfluid aus einem Versorgungskanal innerhalb des Kolbens in die Arbeitskammern. Außerdem leiten diese Ausnehmungen infolge der Nockenwellenwechselmomente Druckspitzen aus den Arbeitskammern in den Versorgungskanal. Jedoch sind diese Ausnehmungen nicht zur Abfuhr von Hydraulikfluid zum Tankabfluss vorgesehen. Diese Ausnehmungen können beispielsweise Ringnuten aufweisen, damit der Kolben nicht im Winkel gegenüber der Bohrung bzw. der Buchse orientiert sein muss. Solche Ringnut zur Verteilung des Hydraulikfluids über den Umfang kann aber auch in der Innenwand der Buchse eingearbeitet sein.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. In addition, these recesses lead due to the camshaft alternating moments pressure peaks from the working chambers in the supply channel. However, 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.

Weitere Vorteile der Erfindung gehen aus den weiteren Patentansprüchen, der Beschreibung und der Zeichnung vor.Further advantages of the invention will become apparent from the other claims, the description and the drawings.

Die Erfindung ist nachfolgend anhand von zwei Ausführungsbeispielen näher erläutert.The invention is explained in more detail below with reference to two exemplary embodiments.

Dabei zeigen

  • Fig. 1 einen Schwenkmotorversteller in einer geschnittenen Ansicht,
  • Fig. 2 in einem Halbschnitt ein Hydraulikventil zur Verstellung des Schwenkmotorverstellers gemäß Fig. 1,
  • Fig. 3 in einem Halbschnitt in einer zweiten Ausgestaltungsform ein Hydraulikventil zur Verstellung des Schwenkmotorverstellers gemäß Fig. 1 und
  • Fig. 4 in einem Halbschnitt in einer dritten Ausgestaltungsform ein Hydraulikventil zur Verstellung des Schwenkmotorverstellers gemäß Fig. 1.
Show
  • Fig. 1 a Schwenkmotorversteller in a sectional view,
  • Fig. 2 in a half section, a hydraulic valve for adjusting the Schwenkmotorverstellers according to Fig. 1 .
  • Fig. 3 in a half section in a second embodiment, a hydraulic valve for adjusting the Schwenkmotorverstellers according to Fig. 1 and
  • Fig. 4 in a half section in a third embodiment, a hydraulic valve for adjusting the Schwenkmotorverstellers according to Fig. 1 ,

Mit einem Schwenkmotorversteller 14 gemäß Fig. 1 wird während des Betriebes eines Verbrennungsmotors die Winkellage an der Nockenwelle 18 gegenüber einem Antriebsrad 2 stufenlos verändert. Durch Verdrehen der Nockenwelle 18 werden die Öffnungs- und Schließzeitpunkte der Gaswechselventile so verschoben, dass der Verbrennungsmotor bei der jeweiligen Drehzahl seine optimale Leistung bringt. Der Schwenkmotorversteller 14 weist einen zylindrischen Stator 1 auf, der drehfest mit dem Antriebsrad 2 verbunden ist. Im Ausführungsbeispiel ist das Antriebsrad 2 ein Kettenrad, über das eine nicht näher dargestellte Kette geführt ist. Das Antriebsrad 2 kann aber auch ein Zahnriemenrad sein, über das ein Antriebsriemen als Antriebselement geführt ist. Über dieses Antriebselement und das Antriebsrad 2 ist der Stator 1 mit der Kurbelwelle antriebsverbunden.With a Schwenkmotorversteller 14 according to Fig. 1 During operation of an internal combustion engine, the angular position on the camshaft 18 is changed continuously with respect to a drive wheel 2. By turning the camshaft 18, the opening and closing times of the gas exchange valves are shifted so that the engine brings its optimum performance at the respective speed. The Schwenkmotorversteller 14 has a cylindrical stator 1 which is rotatably connected to the drive wheel 2. In the exemplary embodiment, 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. About this drive element and the drive wheel 2, the stator 1 is drivingly connected to the crankshaft.

Der Stator 1 umfasst einen zylindrischen Statorgrundkörper 3, an dessen Innenseite radial nach innen in gleichen Abständen Stege 4 abstehen. Zwischen benachbarten Stegen 4 werden Zwischenräume 5 gebildet, in die, über ein in Fig. 2 näher dargestelltes Hydraulikventil 12 gesteuert, Druckmedium eingebracht wird. Das Hydraulikventil 12 ist dabei als Zentralventil ausgeführt. Zwischen benachbarten Stegen 4 ragen Flügel 6, die radial nach außen von einer zylindrischen Rotornabe 7 eines Rotors 8 abstehen. Diese Flügel 6 unterteilen die Zwischenräume 5 zwischen den Stegen 4 jeweils in zwei Druckkammern 9 und 10.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

Die Stege 4 liegen mit ihren Stirnseiten dichtend an der Außenmantelfläche der Rotornabe 7 an. Die Flügel 6 ihrerseits liegen mit ihren Stirnseiten dichtend an der zylindrischen Innenwand des Statorgrundkörpers 3 an.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.

Der Rotor 8 ist drehfest mit der Nockenwelle 18 verbunden. Um die Winkellage zwischen der Nockenwelle 18 und dem Antriebsrad 2 zu verändern, wird der Rotor 8 relativ zum Stator 1 gedreht. Hierzu wird je nach gewünschter Drehrichtung das Druckmedium in den Druckkammern 9 oder 10 unter Druck gesetzt, während die jeweils anderen Druckkammern 10 oder 9 zum Tank hin entlastet werden. Um den Rotor 8 gegenüber dem Stator 1 entgegen dem Uhrzeigersinn in die dargestellte Stellung zu verschwenken, wird vom Hydraulikventil 12 ein ringförmiger erster Rotorkanal in der Rotornabe 7 unter Druck gesetzt. Von diesem ersten Rotorkanal führen dann weitere Kanäle 11 in die Druckkammern 10. Dieser erste Rotorkanal ist dem ersten Arbeitsanschluss A zugeordnet. Um den Rotor 8 hingegen im Uhrzeigersinn zu verschwenken, wird vom Hydraulikventil 12 ein zweiter ringförmiger Rotorkanal in der Rotornabe 7 unter Druck gesetzt. Dieser zweite Rotorkanal ist dem zweiten Arbeitsanschluss B zugeordnet. Diese beiden Rotorkanäle sind bezüglich einer Zentralachse 22 axial beabstandet zueinander angeordnet.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. In contrast, in order to pivot the rotor 8 in a clockwise direction, 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.

Der Schwenkmotorverstellers 14 ist auf die als Hohlrohr 16 ausgeführte gebaute Nockenwelle 18 aufgesetzt. Dazu ist der Rotor 8 auf die Nockenwelle 18 gesteckt. Der Schwenkmotorversteller 14 ist mittels des in Fig. 2 ersichtlichen Hydraulikventils 12 schwenkbar.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.

Innerhalb des Hohlrohrs 16 ist eine dem Hydraulikventil 12 zugehörige Buchse 15 koaxial eingesetzt. In die zentrale Bohrung 85 dieser Buchse 15 ist ein hohler Kolben 19 gegen die Kraft einer Schraubendruckfeder 24 verschiebbar geführt. Dazu stützt sich die Schraubendruckfeder 24 einerseits am Kolben 19 und andererseits gehäusefest ab. Zur Anlage für die Schraubendruckfeder 24 ist innerhalb des Kolbens 19 einen Absatz 88 vorgesehen, dem sich zum Ende des Kolbens 19 hin eine radiale Federführung 103 anschließt.Within the hollow tube 16, a sleeve 15 associated with the hydraulic valve 12 is inserted coaxially. In the central bore 85 of this bushing 15, a hollow piston 19 is slidably guided against the force of a helical compression spring 24. For this purpose, the helical compression spring 24 is supported on the one hand on the piston 19 and on the other hand fixed to the housing. For installation for the helical compression spring 24, a shoulder 88 is provided within the piston 19, which connects to the end of the piston 19 toward a radial spring guide 103.

Am nockenwellenaußenseitigen - d.h. hinteren - Ende der Buchse 15 liegt an dem Kolben 19 ein Stößel 20 eines elektromagnetischen Stellgliedes an.On camshaft outer side - ie rear - end of the bush 15 is located on the piston 19, a plunger 20 of an electromagnetic actuator.

Der hohle Kolben 19 weist axial beabstandet zueinander vier umfangsmäßige Steuernuten 28 bis 31 auf. Überdies sind axial beabstandet zueinander vier Ausnehmungen 41, 38, 39, 40 in der Buchse 15 vorgesehen. Die axial äußersten Ausnehmungen 41, 40 sind als Durchgangsbohrungen 25, 26 ausgeführt. Die axial inneren Ausnehmungen 38, 39 werden hingegen jeweils aus einer Paarung von einer Durchgangsbohrung 23, 27 und einer Innenringnut 34, 33 gebildet.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.

Damit bilden sich zwischen den Steuernuten 28, 29, 30, 31 und den angrenzenden Ausnehmungen 41, 38, 39, 40 sogenannte Steuerkanten. An diesen Steuerkanten wir die Menge des durchgeleiteten Hydraulikfluids bestimmt, wobei an diesen Steuerkanten bei entsprechend großer Überdeckung der Fluss von Hydraulikfluid nahezu gänzlich gesperrt werden kann. Bei gesperrter Steuerkante bildet sich somit ein Dichtspalt zwischen dem Kolben 19 und der Buchse 15.Thus, between the control grooves 28, 29, 30, 31 and the adjacent recesses 41, 38, 39, 40 so-called control edges. At these 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. When locked control edge thus forms a sealing gap between the piston 19 and the sleeve 15th

Die vorderen beiden Ausnehmungen 41, 38 sind dem ersten Arbeitsanschluss A zugeordnet. Die hinteren beiden Ausnehmungen 39, 40 sind dem zweiten Arbeitsanschluss B zugeordnet. Der vorderste Arbeitsanschluss A ist auf zwei Anschlussteile A1, A* aufgeteilt. Der hintere Arbeitsanschluss B ist ebenfalls auf zwei Anschlüsse B1, B* aufgeteilt.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 *.

Die erste - d.h. vorderste - Ausnehmung 41 ist dem ersten Anschlussteil A1 zugehörig und zur Führung von Hydraulikfluid in die der einen Schwenkrichtung zugeordneten Druckkammern 9 des Schwenkmotorverstellers vorgesehen. Überdies kann über dieses erste Anschlussteil A1 auch Hydraulikfluid zu einem ersten Tankabfluss T1 gefördert werden.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. In addition, hydraulic fluid can also be conveyed to a first tank outlet T1 via this first connection part A1.

Die zweite Ausnehmung 38 ist dem zweiten Anschlussteil A* zugehörig und zur Ausleitung von Hydraulikfluid aus diesen Druckkammern 9 zu einem innerhalb des Kolbens 19 angeordneten Versorgungskanal 32 vorgesehen. Diese Ausleitung erfolgt dann, wenn infolge von Nockenwellenwechselmomenten der Druck in diesen Druckkammern 9 entsprechend ansteigt.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.

Die dritte Ausnehmung 39 ist dem zweiten Anschlussteil B* des zweiten Arbeitsanschlusses B zugehörig und zur Ausleitung von Hydraulikfluid aus den Druckkammern 10 zum Versorgungskanal 32 vorgesehen. Diese Ausleitung erfolgt dann, wenn infolge von Nockenwellenwechselmomenten der Druck in diesen Druckkammern 10 entsprechend ansteigt.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.

Die vierte - d.h. hinterste - Ausnehmung 40 ist dem ersten Anschlussteil B1 des zweiten Arbeitsanschlusses B zugehörig und zur Führung von Hydraulikfluid in die Druckkammern 10 vorgesehen. Überdies kann über diesen Anschlussteil B1 auch Hydraulikfluid aus den Druckkammern 10 zu einem zweiten Tankabfluss T2 gefördert werden.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.

Die beiden axial mittleren Anschlüsse A*, B* weisen jeweils ein bandförmiges Rückschlagventil 35 bzw. 36 auf. Das vordere Rückschlagventil 35 ist in die ringförmig innen in der Buchse 15 umlaufende Innenringnut 34 radial innerhalb der Durchgangsbohrung 23 des Anschlusses A* eingesetzt. Hingegen ist das hintere Rückschlagventil 36 in die ringförmig innen in der Buchse 15 umlaufende Innenringnut 33 innerhalb der Durchgangsbohrung 27 des Anschlusses B* eingesetzt. Beide Rückschlagventile 35, 36 öffnen unabhängig voneinander gegen geringe Überdrücke von außen. Dazu sind die beiden Rückschlagventile 35, 36 voneinander mittels eines radial nach innen ragenden Steges 37 getrennt, der einen sehr geringen Dichtspalt zu einem sehr breiten Steg 42 des Kolbens 19 aufweist.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 *. On the other hand, 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. For this purpose, 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.

An den beiden axialen Enden dieses breiten Steges 42 grenzen die Steuernuten 29, 30, die mittels radial nach außen ragenden Stegen 43, 44 gegen die den Tankabläufen T1, T2 zugeordneten Steuernuten 28, 31 abgegrenzt sind. Diese beiden Steuernuten 28, 31 führen jeweils zu einem Tankablauf T1 bzw. T2, wenn sich der Kolben 19 in der entsprechenden Stellung befindet.At the two axial ends of this wide web 42, the 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.

Dargestellt ist die Stellung, in welcher sich der Kolben 19 ganz hinten befindet. Dabei wird von einem zentralen Versorgungskanal 32 innerhalb des Kolbens 19 der zweite Arbeitsanschluss B mit Hydraulikdruck versorgt. Im Gegenzug wird das Hydraulikfluid aus den dem ersten Arbeitsanschluss A zugeordneten Druckkammern 9 über die Steuernut 28 zum vorderen Tankablauf T1 abgeführt, der dazu Querbohrungen 102 in der Buchse 15 aufweist. Steigt innerhalb dieser Druckkammern 9 der Druck infolge von Nockenwellenwechselmomenten sprunghaft über den Druck innerhalb des Versorgungskanals 32, so öffnet das vordere Rückschlagventil 35 und der Hydraulikdruck aus dieser Druckkammer 9 kann in den Versorgungskanal 32 eingespeist werden. Von dort wird das Hydraulikfluid mitsamt dem von der Ölpumpe kommenden Hydraulikfluid in den zweiten Arbeitsanschluss B eingespeist. Dessen zweiter Anschlussteil B* ist in diesem Fall von dem breiten Steg 42 verschlossen. Damit ist das Rückschlagventil 36 vom Innendruck abgesperrt.Shown is the position in which the piston 19 is located at the very back. In this case, the second working port B is supplied with hydraulic pressure from a central supply channel 32 within the piston 19. In return, 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. Increases within these pressure chambers 9, the pressure due to camshaft alternating torques abruptly on the pressure within the supply channel 32, so opens the front check valve 35 and the hydraulic pressure from this pressure chamber 9 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 second working port B. Its second connection part B * is closed in this case by the wide web 42. Thus, the check valve 36 is shut off from the internal pressure.

Wird der Kolben 19 mittels des Stößels 20 des elektromagnetischen Stelleglieds in die andere Endstellung verschoben, so wird das Hydraulikfluid auf den ersten Arbeitsanschluss A geleitet. Dabei fließt das Hydraulikfluid vom Versorgungskanal 32 über die Steuernut 29 in die Ausnehmung 37 und dann zum ersten Arbeitsanschluss A. Im Gegenzug wird das Hydraulikfluid aus den dem zweiten Anschluss B zugeordneten Druckkammern 10 über die Steuernut 31 zum hinteren Tankablauf T1 abgeführt. Steigt innerhalb der Druckkammern 10 der Druck infolge von Nockenwellenwechselmomenten sprunghaft über den Druck innerhalb des Versorgungskanals 32, so öffnet das hintere Rückschlagventil 36 und der Hydraulikdruck aus diesen Druckkammern 10 kann in den Versorgungskanal 32 eingespeist werden. Von dort wird das Hydraulikfluid mitsamt dem von der Ölpumpe kommenden Hydraulikfluid in den ersten Anschlussteil A1 des ersten Arbeitsanschlusses A eingespeist. Der zweite Anschlussteil A* des ersten Arbeitsanschlusses A ist in diesem Fall von dem breiten Steg 42 verschlossen.If the piston 19 is displaced by means of the plunger 20 of the electromagnetic actuator in the other end position, the hydraulic fluid is directed to the first working port A. In this case, 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. In return, 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. If, within the pressure chambers 10, the pressure due to camshaft alternating torques suddenly rises above the pressure within the supply channel 32, 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.

Überdies kann der Kolben 19 noch in einer mittleren Sperrstellung eingeregelt werden in der beide Arbeitsanschlüsse A, B im stärkeren Maß mit Druck beaufschlagt werden als das Hydraulikfluid abgeführt werden kann. Damit ist der Schwenkmotorversteller 14 in dieser Winkelstellung fixiert.Moreover, 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. Thus, the Schwenkmotorversteller 14 is fixed in this angular position.

Das Hydraulikventil 12 weist einen radialen Versorgungsanschluss P auf, der das Hydraulikfluid am vorderen Ende des Kolbens 19 durch eine Öffnung 89 in den zentralen Versorgungskanal 32 innerhalb des Kolbens 19 einleitet. Dazu sind an diesem vorderen Ende in der Buchse 15 Querbohrungen 90 vorgesehen, denen das Hydraulikfluid über ein Sieb 100 zugeführt wird. Von den Querbohrungen 90 zu den Öffnungen 89 wird das Hydraulikfluid über ein Rückschlagventil 101 geführt, welches Druckspitzen innerhalb des Versorgungskanals 32 im Hydraulikventil 12 gegen den Versorgungsanschluss P absperrt. Den Öffnungen 89 ist ein Stopfen 87 innerhalb des hohlen Kolbens 19 benachbart, welcher den Kolben 19 am vorderen Ende verschließt.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. For this purpose, 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.

Alternativ ist es auch möglich, den Versorgungsanschluss P auf die Seite des Stößels 20 zu legen. Auch sind alternative Ausgestaltungen mit axialer Zuführung des Versorgungsanschlusses P machbar.Alternatively, it is also possible to place the supply terminal P on the side of the plunger 20. Also, alternative embodiments with axial feed of the supply connection P are feasible.

Fig. 3 zeigt ein Hydraulikventil 44 ebenfalls mit einem radialen Versorgungsanschluss P, der jedoch axial zwischen den beiden Arbeitsanschlüssen A und B liegt. Dieser Versorgungsanschluss P führt durch Bohrungen 55 in einer Buchse 115 von der nicht näher dargestellten Ölpumpe des Verbrennungsmotors zu einer Ölversorgungsnut 43 in dem Kolben 119. Dieser Kolben 119 ist axialverschieblich in einer zentralen Bohrung 185 der Buchse 115 geführt. Die Ölversorgungsnut 43 teilt somit im Vergleich zu dem vorangegangenen Ausführungsbeispiel den breiten Steg des Kolbens 119 in zwei Stege 46, 47 auf. Von dieser Ölversorgungsnut 43 wird das Hydraulikfluid durch Bohrungen 48 im Grund dieser Ölversorgungsnut 43 zu einem Versorgungskanal 132 geführt, welcher das Hydraulikfluid auf die jeweiligen Druckkammern 9 bzw. 10 führt. 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 Ölversorgungsnut 43 thus divides in comparison to the previous embodiment, the wide web of the piston 119 in two webs 46, 47. From this Ölversorgungsnut 43, the hydraulic fluid through holes 48 in the bottom of this Ölversorgungsnut 43 is guided to a supply channel 132, which leads the hydraulic fluid to the respective pressure chambers 9 and 10 respectively.

In der Fig. 3 ist der Kolben 45 im Gegensatz zu Fig. 2 bei ausgerücktem elektromagnetischen Stellglied bzw. Stößel 20 dargestellt. Dabei befindet sich der Kolben 119 in der vorderen Stellung und führt das Hydraulikfluid über den ersten Anschlussteil A1 auf den ersten Arbeitsanschluss A. Der zugehörige zweite Anschlussteil A* zur Nutzung der Nockenwellenwechselmomente wird von dem vorderen Steg 47 gesperrt.In the Fig. 3 is the piston 45 in contrast to Fig. 2 shown with disengaged electromagnetic actuator or plunger 20. In this case, 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.

Der andere Arbeitsanschluss B wird über den Anschluss B1 zum zweiten Tankabfluss T2 hin entlastet.The other working port B is relieved via port B1 to the second tank outlet T2.

Steigt innerhalb der Druckkammer 10 der Druck infolge von Nockenwellenwechselmomenten sprunghaft an, so führt der Überdruck am zweiten Anschlussteil B* des zweiten Arbeitsanschlusses B gegenüber dem Versorgungskanal 132 zur Öffnung eines hinteren Rückschlagventils 136. Der Hydraulikdruck wird über eine Ringnut 52 und eine Bohrung 53 in deren Grund in den Versorgungskanal 132 eingespeist und unterstützt damit die schnelle Verstellung des Rotors 8 gegenüber dem Stator 1.If, within the pressure chamber 10, the pressure rises abruptly as a result of camshaft alternating torques, the overpressure at the second connection part B * of the The hydraulic pressure is fed via an annular groove 52 and a bore 53 in the bottom of the supply channel 132 and thus supports the rapid adjustment of the rotor 8 relative to the stator first

Der Versorgungskanal 132 verläuft dazu innerhalb des Kolbens 119, innerhalb dessen jedoch auch ein zentraler Kanal 17 zu den beiden Tankabflüssen T1, T2 geführt ist. Dazu ist in den Kolben 119 ein Rohr 21 eingesteckt, auf welches an dessen beiden Enden Ringe 45, 49 fest aufgepresst sind. Mit diesen Ringen 45, 49 ist das Rohr 21 bewegungsfest in den Kolben 119 eingesteckt, so dass die beiden Tankabflüsse T1, T2 hydraulisch vom Versorgungsanschluss P getrennt sind.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. For this purpose, 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.

Wird der Kolben 119 von dem elektromagnetischen Stellglied über den Stößel 20 entlastet, so drückt die Schraubendruckfeder 24 den Kolben 119 in die hintere Stellung.If the piston 119 is relieved of the electromagnetic actuator via the plunger 20, the helical compression spring 24 pushes the piston 119 in the rear position.

In diesem zeichnerisch nicht dargestellten Zustand wird das Hydraulikfluid von der Ölpumpe auf den zweiten Anschlussteil B1 des zweiten Arbeitsanschlusses B geführt. Der Druck infolge von Nockenwellenwechselmomenten wird über den zweiten Anschlussteil A* des ersten Arbeitsanschlusses A und ein vorderes Rückschlagventil 135 in eine Ringnut 51 im Kolben 119 geführt. Im Grund dieser Ringnut 51 sind Bohrungen 50 vorgesehen, von denen das Hydraulikfluid dann in den Versorgungskanal 132 eingespeist wird. Somit steht zusammen mit dem Versorgungsanschluss P ausreichend Hydraulikfluid für eine schnelle Verstellung des Schwenkmotorverstellers 14 zur Verfügung. Der erste Arbeitsanschluss A wird über den ersten Anschlussteil A1 zum ersten Tankabfluss T1 hin entlastet. Der Anschluss B* ist vom Steg 46 versperrt.In this state, not shown graphically, the hydraulic fluid from the oil pump to the second connection part B1 of the second working port B is performed. The pressure due to camshaft alternating torques is guided via the second connection part A * of the first working port A and a front check valve 135 in an annular groove 51 in the piston 119. In the bottom of this annular groove 51 holes 50 are provided, of which the hydraulic fluid is then fed into the supply channel 132. Thus, together with the supply connection P, sufficient hydraulic fluid is available for rapid adjustment of the swivel motor adjuster 14. The first working connection A is relieved via the first connection part A1 to the first tank outlet T1. The connection B * is blocked by the bridge 46.

Fig. 4 zeigt in einem Halbschnitt in einer dritten Ausgestaltungsform ein Hydraulikventil 54 zur Verstellung des Schwenkmotorverstellers 14 gemäß Fig. 1. Fig. 4 shows in a half section in a third embodiment, a hydraulic valve 54 for adjusting the Schwenkmotorverstellers 14 according to Fig. 1 ,

Der radiale Versorgungsanschluss P des Hydraulikventils 54 ist an dem einen Ende einer Buchse 215 angeordnet. Diesem Versorgungsanschluss P folgen axial aufeinander von vorne nach hinten gesehen

  • — ein radialer Tankabfluss T1,
  • — der erste radiale Arbeitsanschluss A und
  • — der zweite radiale Arbeitsanschluss B.
The radial supply port P of the hydraulic valve 54 is disposed at the one end of a sleeve 215. This supply port P follow axially successively seen from front to back
  • A radial tank outlet T1,
  • - The first radial working port A and
  • - the second radial working connection B.

Ein zweiter Tankanschluss T2 geht hingegen axial am Ende der Buchse 215 ab. Der erste Arbeitsanschluss A teilt sich wieder in den ersten Anschlussteil A1 und den zweiten Anschlussteil A* auf. Ebenso teilt sich der zweite Arbeitsanschluss B wieder in den ersten Anschlussteil B1 und den zweiten Anschlussteil B* auf.On the other hand, 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 *. Likewise, the second working port B divides again into the first connection part B1 and the second connection part B *.

In einer zentralen Bohrung 285 der Buchse 215 ist ein hohler beidseitig axial verschlossener Kolben 219 axialverschiebbar angeordnet. Dazu stützt sich an dessen einem Ende eine Schraubendruckfeder 24 und an dessen anderem Ende ein Stößel 20 eines elektromagnetischen Stellgliedes ab. Die Schraubendruckfeder 24 liegt an einem Boden 56 am hinteren Ende des Kolbens 219 an, wohingegen der Stößel 20 an einem Boden 57 am vorderen Ende des Kolbens 219 anliegt. Der Kolben 219 weist axial beabstandet zueinander fünf umfangsmäßige Ringnuten 58 bis 62 auf. Die dem elektromagnetischen Stellglied am nächsten stehende Ringnut 62 ist zum zweiten Tankabfluss T2 hin offen. Die beiden den Arbeitsanschlüssen A, B zugeordneten Ringnuten 60, 61 weisen jeweils zwei axial zueinander beanstandete Bohrungen 63, 64 bzw. 65, 66 auf, die in den innerhalb des hohlen Kolbens 219 liegenden Versorgungskanal 232 führen. In diesen beiden den Arbeitsanschlüssen A, B zugeordneten Ringnuten 60, 61 ist jeweils ein ringförmiges axialverschiebbares Rückschlagventil 67, 68 angeordnet, das eine Hülse 69 bzw. 70 aufweist. Diese beiden Hülsen 69 bzw. 70 stützen sich jeweils über eine kleine Schraubendruckfeder 71 bzw. 72 auf deren voreinander abgewandter Seite am Kolben 219 ab. Dazu stützt sich das eine Ende der jeweiligen Schraubendruckfeder 71 bzw. 72 an der Innenwand 73 bzw. 74 der Ringnut 60 bzw. 61 ab, welche dem Anschlussteil A* bzw. B* zur Nutzung der Nockenwellenwechselmomente zugeordnet ist. Das andere Ende der kleinen Schraubendruckfeder 71 bzw. 72 stützt sich an einem Ringkolben 75, 76 ab, der sich radial nach außen von der Hülse 69, 70 erstreckt. Ein sich über den Ringkolben 75 bzw. 76 axial hinaus von der Hülse 69 bzw. 70 fluchtend erstreckender Teilbereich 77 bzw. 78 der Hülse 69 bzw. 70 dient als Federzentrierung. Infolge der Federkraft liegt die Hülse 69 bzw. 70 stirnseitig an der anderen Innenwand 79 bzw. 80 der Ringnut 60 bzw. 61 an. Diese Innenwand 79 bzw. 80 ist demzufolge dem ersten Anschlussteil A1 bzw. B1 zugewandt, welcher der regulären Zufuhr und Abfuhr von Hydraulikfluid in die Druckkammern 9 bzw. 10 zugeordnet ist. In der zeichnerisch dargestellten Stellung des Rückschlagventils 67 bzw. 68 sind die einander am nächsten stehenden Bohrungen 64, 65 im Kolben 219 von der Hülse 69 bzw. 70 verschlossen. Es bildet sich ein radial außerhalb dieser Bohrungen 64, 65 liegender Ringraum 81 bzw. 82. Wird dieser Ringraum 81 bzw. 82 mit Hydraulikdruck ausreichender Höhe beaufschlagt, so wird die jeweilige Bohrung 64, 65 der beiden einander am nächsten stehenden Bohrungen 64, 65 freigegeben. Im Gegenzug wird die Bohrung 63 bzw. 66 der beiden einander fern stehenden Bohrungen 63, 66 verschlossen.In a central bore 285 of the sleeve 215, a hollow piston 219 axially closed on both sides is arranged to be axially displaceable. For this purpose, at its one end 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. In these two the working ports A, B associated annular grooves 60, 61, 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. For this purpose, 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. As a result of the spring force, 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. In the position shown in the drawing of the check valve 67 and 68, 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. If this annular space 81 or 82 is acted upon by hydraulic pressure of sufficient height, the respective bore 64, 65 of the two bores 64, 65 closest to one another is released , In return, the bore 63 and 66 of the two distant bores 63, 66 is closed.

Beide Rückschlagventile 67, 68 öffnen somit unabhängig voneinander gegen geringen Überdrücken von außen durch den jeweiligen zweiten Anschlussteil A* bzw. B*. Dazu sind die beiden Rückschlagventile 67, 68 voneinander mittels eines sehr breiten Steges 83 des Kolbens 219 getrennt. Dieser breite Steg 83 wird durch die Innenwände 79, 80 begrenzt.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 *. For this purpose, 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.

Im Grund der vordersten Ringnut 58 ist eine Bohrung 86 vorgesehen, die das Hydraulikfluid vom Versorgungsanschluss P in den zentralen Versorgungskanal 232 führt. Zwischen dieser Ringnut 58 und den Ringnuten 60, 61 der Arbeitsanschlüsse A, B ist die Ringnut 59 angeordnet, mit der in der zeichnerisch dargestellten Stellung des Kolbens 219 das Hydraulikfluid vom ersten Anschlussteil A1 des ersten Arbeitsanschlusses A zum ersten Tankabfluss T1 geleitet wird.At the bottom of the foremost annular groove 58, a bore 86 is provided, which guides the hydraulic fluid from the supply port P into the central supply channel 232. Between this annular groove 58 and the annular grooves 60, 61 of the working ports A, B, 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.

In dieser dargestellten Stellung befindet sich der Kolben 219 ganz hinten. Dabei wird von dem zentralen Versorgungskanal 232 innerhalb des Kolbens 219 der erste Anschlussteil B1 des zweiten Arbeitsanschlusses B mit Hydraulikdruck versorgt. Der Innendruck im Hydraulikventil 54 unterstützt dabei die Schließkraft des hinteren Rückschlagventils 68. Im Gegenzug wird das Hydraulikfluid aus der dem Arbeitsanschluss A zugeordneten Druckkammern 9 über die Ringnut 59 zum vorderen Tankablauf T1 abgeführt. Steigt innerhalb der diesem Arbeitsanschluss A zugeordneten Druckkammern 8 der Druck infolge von Nockenwellenwechselmomenten über den Druck innerhalb des Versorgungskanals 232, so öffnet das vordere Rückschlagventil 67 und der Hydraulikdruck aus den Druckkammern 9 kann über die Bohrungen 64 in den Versorgungskanal 232 eingespeist werden. Von dort wird das Hydraulikfluid mitsamt dem von der Ölpumpe kommenden Hydraulikfluid über die Bohrungen 66 in den Arbeitsanschluss B eingespeist. Der Anschluss B* ist in diesem Fall von dem breiten Steg 83 verschlossen.In this illustrated position, the piston 219 is at the very rear. In this case, 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. In return, 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.

Wird der Kolben 219 mittels des Stößels 20 in die andere Position verschoben, so wird das Hydraulikfluid auf den ersten Arbeitsanschluss A geleitet. Dabei fließt das Hydraulikfluid vom Versorgungskanal 232 über die Bohrungen 63 in einen Ringraum 84, in welchem die kleine Schraubendruckfeder 71 angeordnet ist und dann zum ersten Arbeitsanschluss A. Im Gegenzug wird das Hydraulikfluid aus der dem zweiten Anschluss B zugeordneten Druckkammer 10 über die Ringnut 62 zum hinteren Tankablauf T2 abgeführt. Steigt innerhalb der Druckkammer 10 der Druck infolge von Nockenwellenwechselmomenten über den Druck innerhalb des Versorgungskanals 232, so öffnet das hintere Rückschlagventil 68 und der Hydraulikdruck aus dieser Druckkammern 10 kann in den Versorgungskanal 232 eingespeist werden. Von dort wird das Hydraulikfluid mitsamt dem von der Ölpumpe kommenden Hydraulikfluid in den Arbeitsanschluss A eingespeist. Der Anschluss A* ist in diesem Fall von dem breiten Steg 83 verschlossen.If the piston 219 is displaced by means of the plunger 20 in the other position, the hydraulic fluid is passed to the first working port A. In this case, 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. In return, the hydraulic fluid from the second port B associated pressure chamber 10 via the annular groove 62 for rear tank drain T2 discharged. If, within the pressure chamber 10, the pressure due to camshaft alternating torques rises above the pressure within the supply passage 232, 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.

Es ist nicht unbedingt notwendig, dass gemäß Fig. 4 beide Rückschlagventile 67, 68 derart ausgeführt sind, dass diese in einer Ringnut 60 bzw. 61 des Kolbens 219 angeordnet sind und dabei gegenüber dem Kolben 219 gegen einer Federkraft axial verschiebbar sind. Es ist auch möglich, nur ein Rückschlagventil 67 axial verschiebbar auszuführen. Insbesondere, wenn der Kolben 219 als gebauter Kolben 219 ausgeführt ist, wie dies die punktierte Linie 97 darstellt, braucht nur das eine Rückschlagventil 68 in die Ringnut 61 eingesetzt sein, welche von der Innenwand 74 begrenzt wird, die an einem Ring 99 angeordnet ist, welcher auf einen rohrförmigen Bereich 98 des Kolbens 119 aufgepresst ist. Zur Verbesserung der Verbindung ohne Erhöhung der Presskräfte auf den Kolben 219 kann eine Mikroverzahnung vorgesehen sein, die ähnlich einer Rändelung aussehen kann. In dem Fall kann die Hülse 70 als geschlossenes Bauteil ausgeführt sein.It is not absolutely necessary that according to Fig. 4 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. In particular, when 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. To improve the connection without increasing the pressing forces on the piston 219 may be provided a micro-toothing, which may look similar to a knurling. In that case, the sleeve 70 can be designed as a closed component.

Die Hülse 69 bzw. 70 kann aber auch geteilt ausgeführt sein. So ist es möglich die Hülse geschlitzt auszuführen, so dass die geschlitzte Hülse 69 bzw. 70 eine Teilung aufweist. Dann kann die Hülse 69 bzw. 70 an dem in der Zeichnung nicht näher ersichtlichen Schlitz aufgebogen werden und über den Kolben 219 geschoben werden, bis die Hülse 69 bzw. 70 in der Ringnut 60 bzw. 61 zusammen schnappt. Demzufolge braucht in diesem Fall der Kolben 219 nicht als gebauter Kolben 219 ausgeführt sein. Bei der Ausführungsform als geschlitzte Hülse ist Kunststoff als Werkstoff von Vorteil. Insbesondere kann ein Thermoplast mit geringem Reibkoeffizienten gegenüber Stahl oder Aluminium verwendet werden. Kunststoff beschädigt bei der Montage nicht die Laufflächen des Kolbens 219.However, the sleeve 69 or 70 can also be made split. Thus, it is possible to make the sleeve slotted, so that the slotted sleeve 69 and 70 has a pitch. Then, 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. Accordingly, in this case, the piston 219 need not be designed as a built piston 219. In the embodiment as a slotted sleeve plastic as a material is beneficial. In particular, 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.

Es ist jedoch auch möglich, das Rückschlagventil 67 bzw. 68 in Halbschalen aufzuteilen. Dabei kann entsprechend Fig. 4 die Hülse 69 bzw. 70 einen Teilbereich 77 bzw. 78 aufweisen, an dem die beiden Halbschalen von einer Schraubendruckfeder 71 bzw. 72 zusammengehalten werden.However, it is also possible to divide the check valve 67 and 68 in half shells. It can be done accordingly Fig. 4 the sleeves 69 and 70 have a portion 77 and 78, respectively, on which the two half-shells are held together by a helical compression spring 71 and 72, respectively.

Es ist auch möglich, den Kolben 219 als gebauten Kolben auszuführen, bei dem sämtliche Ringnuten 58, 59, 60, 61 gebildet werden, indem Ringe ähnlich dem Ring 99 aufgepresst werden.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.

Das zweite Ausführungsbeispiel gemäß Fig. 3 zeigt, dass mittels des Rohres 21 eine Verbindung zwischen den beiden Tankabflüssen T1, T2 geschaffen wird. Mittels dieses Rohres 21 kann demzufolge aber auch auf einen Tankabfluss T1 oder T2 verzichtet werden. Das ist insbesondere dann von Vorteil, wenn infolge der Bauraumverhältnisse am Nockenwellentrieb nur die Abfuhr von Hydraulikfluid in einer Richtung möglich ist. Das ist beispielsweise bei einem trockenen Zahnriemen der Fall, da bei diesem nicht ein Kettenkasten zur Leitung des Hydraulikfluids in einen Ölsumpf zur Verfügung steht. Wenn das Hydraulikfluid jedoch beidseitig abgeführt werden kann, kann auch auf das Rohr 21 verzichtet werden und der Kolben kann beidseitig verschlossen sein.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. By means of this tube 21 but 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. However, if 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.

Überdies kann der Kolben noch in einer mittlere Sperrstellung eingeregelt werden in der beide Arbeitsanschlüsse im stärkeren Maß mit Druck beaufschlagt werden als das Hydraulikfluid abgeführt werden kann. Damit ist der Schwenkmotorversteller in dieser Winkelstellung fixiert.Moreover, 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. Thus, the Schwenkmotorversteller is fixed in this angular position.

Die Kolben 19, 119, 219 der vorgenannten Ausführungsbeispiele sind druckausgeglichen.The pistons 19, 119, 219 of the aforementioned embodiments are pressure balanced.

Anstelle der Schraubendruckfeder für den Kolben bzw. der Schraubendruckfedern für die Rückschlagventile können auch Tellerfedern Anwendung finden.Instead of the helical compression spring for the piston or the helical compression springs for the check valves also disc springs can be used.

Die beiden einem Arbeitsanschluss A bzw. B zugeordneten Anschlussteile A1, A* bzw. B1, B* müssen im Abgang von der zentralen Bohrung 85, 185, 285 getrennt sein, da der Kolben 19, 119, 219 das Hydraulikfluid separat zuleiten muss. Außerhalb des Rückschlagventils können die beiden Anschlussteile A1, A* bzw. B1, B* aber wieder zusammengeführt werden. Diese Zusammenführung kann sogar innerhalb der Buchse 15, 115, 215 bzw. einer einteilig mit der Buchse ausgeführten Rotornabe erfolgen.The two 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.

Der Rotor 8 kann in einer alternativen Ausgestaltung mittels einer Kompensationsfeder gegen den Stator 1 drehelastisch vorgespannt sein.The rotor 8 may be biased torsionally elastic in an alternative embodiment by means of a compensation spring against the stator 1.

Bei den beschriebenen Ausführungsformen handelt es sich nur um beispielhafte Ausgestaltungen. Eine Kombination der beschriebenen Merkmale für unterschiedliche Ausführungsformen ist ebenfalls möglich. Weitere, insbesondere nicht beschriebene Merkmale der zur Erfindung gehörenden Vorrichtungsteile, sind den in den Zeichnungen dargestellten Geometrien der Vorrichtungsteile zu entnehmen.The described embodiments are only exemplary embodiments. A combination of the described features for different embodiments is also possible. Further, in particular not described features of the device parts belonging to the invention are to be taken from the geometries of the device parts shown in the drawings.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Statorstator
22
Antriebsraddrive wheel
33
Statorgrundkörperstator base
44
StegeStege
55
Zwischenräumeinterspaces
66
Flügelwing
77
Rotornaberotor hub
88th
Rotorrotor
99
Druckkammernpressure chambers
1010
Druckkammernpressure chambers
1111
Kanälechannels
1212
Zentralventilcentral valve
1313
Rotorkanalrotor channel
1414
SchwenkmotorverstellerSchwenkmotorversteller
1515
BuchseRifle
1616
Hohlrohrhollow tube
1717
Zentraler KanalCentral channel
1818
Nockenwellecamshaft
1919
Kolbenpiston
2020
Stößeltappet
2121
Rohrpipe
2222
Zentralachsecentral axis
2323
DurchgangsbohrungThrough Hole
2424
SchraubendruckfederHelical compression spring
2525
DurchgangsbohrungThrough Hole
2626
DurchgangsbohrungThrough Hole
2727
DurchgangsbohrungThrough Hole
2828
Steuernutcontrol groove
2929
Steuernutcontrol groove
3030
Steuernutcontrol groove
3131
Steuernutcontrol groove
3232
Versorgungskanalsupply channel
3333
Innenringnutinner annular
3434
Innenringnutinner annular
3535
Rückschlagventilcheck valve
3636
Rückschlagventilcheck valve
3737
Stegweb
3838
Ausnehmungrecess
3939
Ausnehmungrecess
4040
Ausnehmungrecess
4141
Ausnehmungrecess
4242
breiter Stegwide footbridge
4343
Ölversorgungsnutoil supply groove
4444
Hydraulikventilhydraulic valve
4545
Ringring
4646
hinterer Stegrear jetty
4747
vorderer Stegfront dock
4848
Bohrungendrilling
4949
Ringring
5050
Bohrungendrilling
5151
Ringnutring groove
5252
Ringnutring groove
5353
Bohrungdrilling
5454
Hydraulikventilhydraulic valve
5555
Bohrungendrilling
5656
Bodenground
5757
Bodenground
5858
Ringnutring groove
5959
Ringnutring groove
6060
Ringnutring groove
6161
Ringnutring groove
6262
Ringnutring groove
6363
Bohrungendrilling
6464
Bohrungendrilling
6565
Bohrungendrilling
6666
Bohrungendrilling
6767
Rückschlagventilcheck valve
6868
Rückschlagventilcheck valve
6969
Hülseshell
7070
Hülseshell
7171
kleine Schraubendruckfedersmall helical compression spring
7272
kleine Schraubendruckfedersmall helical compression spring
7373
Innenwandinner wall
7474
Innenwandinner wall
7575
Ringkolbenannular piston
7676
Ringkolbenannular piston
7777
Teilbereichsubregion
7878
Teilbereichsubregion
7979
Innenwandinner wall
8080
Innenwandinner wall
8181
Ringraumannulus
8282
Ringraumannulus
8383
breiter Stegwide footbridge
8484
Ringraumannulus
8585
Zentrale BohrungCentral drilling
8686
Bohrungdrilling
8787
StopfenPlug
8888
Absatzparagraph
8989
Öffnungenopenings
9090
Querbohrungencross holes
100100
Siebscreen
101101
Rückschlagventilcheck valve
102102
Querbohrungencross holes
103103
Federführungleadership
115115
BuchseRifle
119119
Kolbenpiston
132132
Versorgungskanalsupply channel
135135
Rückschlagventilcheck valve
136136
Rückschlagventilcheck valve
185185
Zentrale BohrungCentral drilling
285285
zentrale Bohrungcentral hole
215215
BuchseRifle
219219
Kolbenpiston
232232
Versorgungskanalsupply channel
285285
Zentrale BohrungCentral drilling
AA
erster Arbeitsanschlussfirst work connection
BB
zweiter Arbeitsanschlusssecond work connection
A1A1
erster Anschlussteilfirst connection part
A*A *
zweiter Anschlussteilsecond connection part
B1B1
erster Anschlussteilfirst connection part
B*B *
zweiter Anschlussteilsecond connection part
T1T1
erster Tankabflussfirst tank drain
T2T2
zweiter Tankabflusssecond tank drain

Claims (15)

Hydraulikventil (12 bzw. 44 bzw. 54) für einen Schwenkmotorversteller (14) einer Nockenwelle (18), der einen längsverschiebbar in einer Bohrung (85 bzw. 185 bzw. 285) eingesetzten Kolben (19 bzw. 119 bzw. 219) zur Verteilung auf zwei Arbeitsanschlüsse (A, B) aufweist, wobei von dieser Bohrung (85 bzw. 185 bzw. 285) axial beabstandet zueinander - eine erster Anschlussteil (A1) des ersten Arbeitsanschlusses (A) zur Führung von Hydraulikfluid in eine erste Druckkammer (9) des Schwenkmotorverstellers (14), - eine zweiter Anschlussteil (A*) zur Ausleitung von Hydraulikfluid aus dieser ersten Druckkammer (9) zu einem innerhalb des Kolbens (19 bzw. 119 bzw. 219) angeordneten Versorgungskanal (32 bzw. 132 bzw. 232), - eine erster Anschlussteil (B1) des zweiten Arbeitsanschlusses (B) zur Führung von Hydraulikfluid in eine der ersten Druckkammer (9) entgegen gerichteten zweiten Druckkammer (10) des Schwenkmotorverstellers (14) und - eine zweiter Anschlussteil (B*) zur Ausleitung von Hydraulikfluid aus der zweiten Druckkammer (10) zum Versorgungskanal (32 bzw. 132 bzw. 232) abgehen,
wobei im Fluss von den Druckkammern (9, 10) zu den beiden zweiten Anschlussteilen (A*, B*) jeweils ein Rückschlagventil (35, 36,) angeordnet ist, das den Druck in der vom Versorgungskanal (85 bzw. 185 bzw. 285) zu den Druckkammern (9, 10) weisenden Richtung sperrt, dadurch gekennzeichnet, dass der Kolben (19 bzw. 119 bzw. 219) - in der einen Stellung der Zuleitung von Hydraulikfluid vom Versorgungskanal (32 bzw. 132 bzw. 232) zu der einen Druckkammer (9 bzw. 10) den der anderen Druckkammer (10 bzw. 9) zugeordneten zweiten Anschlussteil (B* bzw. A*) sperrt und - in der anderen Stellung der Zuleitung von Hydraulikfluid vom Versorgungskanal (32 bzw. 132 bzw. 232) zu der anderen Druckkammer (10 bzw. 9) den der einen Druckkammer (10 bzw. 9) zugeordneten zweiten Anschlussteil (A* bzw. B*) sperrt. Hydraulic valve (12 or 44 or 54) for a Schwenkmotorversteller (14) of a camshaft (18) having a longitudinally displaceable in a bore (85 or 185 or 285) used piston (19 or 119 or 219) for distribution on two working ports (A, B), wherein from this bore (85 or 185 or 285) axially spaced from each other - A first connection part (A1) of the first working port (A) for guiding hydraulic fluid in a first pressure chamber (9) of the Schwenkmotorverstellers (14), - A second connection part (A *) for discharging hydraulic fluid from said first pressure chamber (9) to a within the piston (19 or 119 or 219) arranged supply channel (32 or 132 or 232), - A first connection part (B1) of the second working port (B) for guiding hydraulic fluid in one of the first pressure chamber (9) directed against the second pressure chamber (10) of the Schwenkmotorverstellers (14) and a second connection part (B *) for discharging hydraulic fluid from the second pressure chamber (10) to the supply channel (32 or 132 or 232),
wherein in the flow of the pressure chambers (9, 10) to the two second connection parts (A *, B *) each have a check valve (35, 36,) is arranged, the pressure in the from the supply channel (85 or 185 and 285 ) to the pressure chambers (9, 10) facing direction, characterized in that the piston (19 or 119 or 219) - In the one position of the supply of hydraulic fluid from the supply channel (32 or 132 or 232) to the one pressure chamber (9 or 10) of the other pressure chamber (10 or 9) associated second connector part (B * or A * ) locks and - In the other position of the supply of hydraulic fluid from the supply channel (32 or 132 or 232) to the other pressure chamber (10 or 9) of the one pressure chamber (10 or 9) associated with the second connector part (A * or B * ) locks. Hydraulikventil (12 bzw. 44 bzw. 54) nach Patentanspruch 1, dadurch gekennzeichnet, dass die beiden zweiten Anschlussteile (A*, B*) axial zwischen den beiden ersten Anschlussteilen (A1, B1) liegen.Hydraulic valve (12 or 44 or 54) according to claim 1, characterized in that the two second connection parts (A *, B *) are located axially between the two first connection parts (A1, B1). Hydraulikventil (12 bzw. 44 bzw. 54) nach einem der vorhergehenden Patentansprüche, dadurch gekennzeichnet, dass die Bohrung (85 bzw. 185 bzw. 285) zentral innerhalb einer Buchse (15, 115, 215) eingebracht ist, die separat zur Nockenwelle (18) und zu einem Rotor (8) des Schwenkmotorverstellers (14) ausgeführt ist.Hydraulic valve (12 or 44 or 54) according to one of the preceding claims, characterized in that the bore (85 or 185 or 285) centrally within a bush (15, 115, 215) is introduced, which is separate from the camshaft ( 18) and to a rotor (8) of the Schwenkmotorverstellers (14) is executed. Hydraulikventil (12 bzw. 44 bzw. 54) nach Patentanspruch 3, dadurch gekennzeichnet, dass die Buchse (15, 115, 215) als Zentralventil ausgeführt ist, das radial innerhalb des Rotors (8) eingesetzt ist.Hydraulic valve (12 or 44 or 54) according to claim 3, characterized in that the bushing (15, 115, 215) is designed as a central valve which is inserted radially inside the rotor (8). Hydraulikventil (12 bzw. 54) nach einem der vorhergehenden Patentansprüche, dadurch gekennzeichnet, dass der Kolben (19, 219) hohl ist, wobei innerhalb des Kolbens der Versorgungskanal (32, 232) verläuft, wobei in dem Kolben (19, 219) axial beabstandet zueinander Ausnehmungen (29, 30, 51, 52) vorgesehen sind, wobei in der einen Stellung des Kolbens (19, 219) über die eine Ausnehmung (30, 52) Hydraulikfluid vom zweiten Anschlussteil (B*) des zweiten Arbeitsanschlusses (B) über den Versorgungskanal (32 bzw. 232) durch die andere Ausnehmung (29, 51) Hydraulikfluid auf den ersten Anschlussteil (A1) des ersten Arbeitsanschlusses (A) führbar ist und wobei in der anderen Stellung des Kolbens (19, 219) über die andere Ausnehmung (29, 51) Hydraulikfluid vom zweiten Anschlussteil (A*) des ersten Arbeitsanschlusses (A) über den Versorgungskanal (32 bzw. 232) durch die eine Ausnehmung (30, 52) Hydraulikfluid auf den ersten Anschlussteil (B1) des zweiten Arbeitsanschlusses (B) führbar ist, und wobei axial zwischen den beiden Ausnehmungen (29, 30, 51, 52) ein breiter Steg vorgesehen ist, mit dem die beiden zweiten Anschlussteile (A*, B*) sperrbar sind.Hydraulic valve (12 or 54) according to one of the preceding claims, characterized in that the piston (19, 219) is hollow, wherein within the piston of the supply channel (32, 232) extends, wherein in the piston (19, 219) axially spaced apart from one another recesses (29, 30, 51, 52) are provided, wherein in the one position of the piston (19, 219) via the one recess (30, 52) hydraulic fluid from the second connecting part (B *) of the second working port (B) via the supply channel (32 or 232) through the other recess (29, 51) hydraulic fluid on the first connection part (A1) of the first working port (A) is feasible and wherein in the other position of the piston (19, 219) on the other Recess (29, 51) hydraulic fluid from the second connection part (A *) of the first working port (A) via the supply channel (32 or 232) through the one recess (30, 52) hydraulic fluid to the first connection part (B1) of the second working port ( B) is feasible, and wherein axially between the two recesses (29, 30, 51, 52), a wide web is provided, with which the two second connection parts (A *, B *) are lockable. Hydraulikventil (44) nach Patentanspruch 5, dadurch gekennzeichnet, dass der breite Steg durch eine Ausnehmung (43) zur Zufuhr eines Versorgungsdrucks vom Versorgungsanschluss (P) in den Versorgungskanal (132) unterbrochen ist.Hydraulic valve (44) according to claim 5, characterized in that the wide web is interrupted by a recess (43) for supplying a supply pressure from the supply port (P) in the supply channel (132). Hydraulikventil (44) nach Patentanspruch 6, dadurch gekennzeichnet, dass innerhalb der Buchse (115) ein Rohr (21) eingesetzt ist, dass beidseitig gegenüber der Buchse (115) radial nach außen verschlossen ist, wobei innerhalb des Rohres (21) Hydraulikfluid zum Tankabfluss (T1 bzw. T2) geführt wird.Hydraulic valve (44) according to claim 6, characterized in that within the bushing (115) a tube (21) is inserted, that is closed on both sides relative to the bushing (115) radially outward, wherein within the tube (21) hydraulic fluid to the tank outlet (T1 or T2) is performed. Hydraulikventil (12 bzw. 44) nach einem der vorhergehenden Patentansprüche, dadurch gekennzeichnet, dass der Kolben (19, 119) mittels eines elektromagnetischen Stellgliedes gegen die Kraft einer Feder (24) verschieblich ist, wobei die Rückschlagventile (35, 36, 135, 136) bandförmig ausgeführt sind und im Grund von Innenringnuten (34, 33) anliegen.Hydraulic valve (12 or 44) according to any one of the preceding claims, characterized in that the piston (19, 119) by means of an electromagnetic actuator against the force of a spring (24) is displaceable, wherein the check valves (35, 36, 135, 136 ) are designed band-shaped and abut in the bottom of Innenringnuten (34, 33). Hydraulikventil (54) nach einem der vorhergehenden Patentansprüche, dadurch gekennzeichnet, dass dem Arbeitsanschluss (P) in folgender Reihenfolge axial - ein erster radialer Tankabfluss (T1), - der erste radiale Anschlussteil (A1) des ersten Arbeitsanschlusses (A), - der zweite radiale Anschlussteil (A*) des ersten Arbeitsanschlusses (A), - der zweite radiale Anschlussteil (B*) des zweiten Arbeitsanschlusses (B) und - der erste radiale Anschlussteil (B1) des zweiten Arbeitsanschlusses (B), folgen. Hydraulic valve (54) according to one of the preceding claims, characterized in that the working port (P) in the following order axially a first radial tank drain (T1), the first radial connection part (A1) of the first working connection (A), the second radial connection part (A *) of the first working connection (A), - The second radial connection part (B *) of the second working port (B) and - The first radial connection part (B1) of the second working port (B), follow. Hydraulikventil (54) nach einem der vorhergehenden Patentansprüche, dadurch gekennzeichnet, dass zumindest ein Rückschlagventil (67 bzw. 68) in einer Ringnut (60 bzw. 61) des Kolbens (219) angeordnet ist, wobei das Rückschlagventil (67 bzw. 68) gegenüber dem Kolben (219) gegen einer Federkraft axial verschiebbar ist.Hydraulic valve (54) according to one of the preceding claims, characterized in that at least one check valve (67 or 68) in an annular groove (60 or 61) of the piston (219) is arranged, wherein the check valve (67 or 68) opposite the piston (219) is axially displaceable against a spring force. Hydraulikventil (54) nach Patentanspruch 10, dadurch gekennzeichnet, dass das Rückschlagventil (67 bzw. 68) eine geschlitzte Hülse (69 bzw. 70) mit einer Teilung aufweist.Hydraulic valve (54) according to claim 10, characterized in that the check valve (67 or 68) has a slotted sleeve (69 or 70) with a pitch. Hydraulikventil (54) nach Patentanspruch 11, dadurch gekennzeichnet, dass die geschlitzte Hülse (69 bzw. 70) aus einem Kunststoff besteht.Hydraulic valve (54) according to claim 11, characterized in that the slotted sleeve (69 or 70) consists of a plastic. Hydraulikventil (54) nach Patentanspruch 10, dadurch gekennzeichnet, dass das Rückschlagventil (67 bzw. 68) eine in Halbschalen geteilte Hülse (69 bzw. 70) aufweist.Hydraulic valve (54) according to claim 10, characterized in that the check valve (67 or 68) has a half-shells split sleeve (69 or 70). Hydraulikventil (54) nach Patentanspruch 13, dadurch gekennzeichnet, dass die Hülse (69 bzw. 70) einen Teilbereich (77 bzw. 78) aufweist, an dem die beiden Halbschalen von einer Schraubendruckfeder (71 bzw. 72) zusammengehalten werden, welche die Federkraft aufbringt.Hydraulic valve (54) according to claim 13, characterized in that the sleeve (69 or 70) has a portion (77 or 78), on which the two half-shells are held together by a helical compression spring (71 or 72), which the spring force applies. Hydraulikventil (54) nach Patentanspruch 10, dadurch gekennzeichnet, dass das eine Rückschlagventil (68) in eine Ringnut (61) eingesetzt ist, welche von einer Innenwand (74) begrenzt wird, die an einem Ring (99) angeordnet ist, welcher auf einen rohrförmigen Bereich (98) des Kolbens (119) aufgepresst ist.Hydraulic valve (54) according to claim 10, characterized in that the one check valve (68) is inserted in an annular groove (61) bounded by an inner wall (74) disposed on a ring (99) which is placed on a tubular portion (98) of the piston (119) is pressed.
EP11186299.1A 2010-12-20 2011-10-24 Hydraulic valve for a camshaft phaser Not-in-force EP2466081B1 (en)

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JP2012132449A (en) 2012-07-12
US8752514B2 (en) 2014-06-17
DE102012103300B4 (en) 2017-08-24
CN102562208A (en) 2012-07-11
DE102010061337B4 (en) 2015-07-09
EP2466081B1 (en) 2017-03-15
DE102010061337A1 (en) 2012-06-21
JP5941602B2 (en) 2016-06-29
CN102562208B (en) 2016-01-20
US20120152195A1 (en) 2012-06-21

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