US20070056540A1 - Control valve and method for its production - Google Patents

Control valve and method for its production Download PDF

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Publication number
US20070056540A1
US20070056540A1 US11/500,652 US50065206A US2007056540A1 US 20070056540 A1 US20070056540 A1 US 20070056540A1 US 50065206 A US50065206 A US 50065206A US 2007056540 A1 US2007056540 A1 US 2007056540A1
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United States
Prior art keywords
housing
housing insert
control valve
port
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Abandoned
Application number
US11/500,652
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English (en)
Inventor
Jens Hoppe
Andreas Rohr
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.)
IHO Holding GmbH and Co KG
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Individual
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Filing date
Publication date
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Assigned to SCHAEFLER KG reassignment SCHAEFLER KG ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: ROHR, ANDREAS, HOE, JENS
Publication of US20070056540A1 publication Critical patent/US20070056540A1/en
Abandoned legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K31/00—Actuating devices; Operating means; Releasing devices
    • F16K31/02—Actuating devices; Operating means; Releasing devices electric; magnetic
    • F16K31/06—Actuating devices; Operating means; Releasing devices electric; magnetic using a magnet, e.g. diaphragm valves, cutting off by means of a liquid
    • F16K31/0603—Multiple-way valves
    • F16K31/061—Sliding valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34426—Oil control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34436—Features or method for avoiding malfunction due to foreign matters in oil
    • F01L2001/3444—Oil filters

Definitions

  • the invention relates to a control valve for influencing the action of a pressure medium on a camshaft adjuster of an internal combustion engine, in particular according to the preamble of claim 1 .
  • the invention additionally relates to a method for producing a control valve, in particular according to the preamble of claim 10 .
  • a control valve for influencing the action of a pressure medium on a camshaft adjuster of an internal combustion engine is known from the applicant's patent application DE 10 2004 036 096.0, which was not published before the priority date of the present application, in which control valve a control piston is axially displaceable in a blind bore of a valve housing, wherein the action on a spring element is varied with the displacement of the control piston.
  • the spring element is supported with one foot point on an end side of the control piston and with the opposite foot point on the base of the blind bore of the valve housing.
  • the control valve has a pressure medium port, two tank ports and two working ports, which are associated with oppositely-acting working chambers of a hydraulic camshaft adjuster.
  • a first working port is connected to a tank port and the second working port is connected to the pressure medium port, so that it is possible to effect an actuating movement of the camshaft adjuster during which the working chamber which is associated with the second working port increases in volume.
  • the second working port is connected to a tank port and the first working port is connected to the pressure medium port, so that it is possible to effect an actuating movement of the camshaft adjuster during which the working chamber which is associated with the first working port increases in volume.
  • the invention is based on the object of simplifying production of the control valve mentioned in the introduction while further ensuring or improving its functions.
  • the object is achieved by means of a control valve according to the features of independent patent claim 1 .
  • Preferred embodiments of a control valve according to the invention emerge corresponding to the features of dependent patent claims 2 to 9 .
  • a further solution of the object on which the invention is based is provided by means of a method according to independent patent claim 10 .
  • Embodiments of the method according to the invention emerge from dependent patent claims 11 to 13 .
  • the invention is based on the realization that the manufacture of the valve housing with a blind bore for holding the control piston has potential for optimization. Imprecise manufacture of the position of a base of the blind bore corresponding to the prior art can in some circumstances influence the function of the control valve, for example the foot point of a spring element, an end position of the control piston and/or the hydraulic conditions, for which reason the blind bore must be manufactured with a high degree of accuracy. It can additionally be necessary for the base of the blind bore to have an additional opening which forms a port, for example a tank port, and for the production of which a further bore must be formed in the valve housing in the region of the base of the blind bore.
  • impurities and burrs must be carefully avoided in the interior of the valve housing which, in an embodiment with a blind bore, is only completely open at one side, since said impurities and burrs can lead, during operation of the control valve, to adverse mechanical effects, increased wear to the point of failure of the control valve or of components which are hydraulically connected to the control valve.
  • the production of a blind hole requires the use of a special tool, in particular a reamer, which, for example, makes an additional undercut necessary in the region of the base of the blind bore. In some circumstances, this requires an increased installation length of the control valve.
  • the shape of the end face of the tool predefines the shape of the base of the blind bore which can be obtained, so that, in some circumstances, integration of further functions into the base of the blind bore is only possible with difficulty.
  • the base of the blind bore cannot delimit the actuating movement of the control piston.
  • Such delimitation of the actuating movement of the control piston is, however, of increased significance since, for example, when a predefined end position of the control piston is exceeded, for example as a result of tolerances of the components of the control valve, the hydraulic connection to a port is only insufficiently opened or closed.
  • Known solutions operate in that an end stop of the control piston is provided by the spring element “being compressed fully” for the end stop to be reached, wherein the end position is however still dependent on tolerances, also in the manufacture of the blind bore.
  • the previously explained realizations are implemented in that the spring element is supported not on a base of the blind bore, but rather, by means of the foot point situated at the opposite side from the control piston, on a housing insert.
  • the embodiment according to the invention having a housing insert makes it possible, for example, for the bore of the valve housing for holding the control piston to be formed as a through bore, so that said bore can be produced more simply and with greater precision, and the formation of burrs is reliably avoided.
  • the foot point of the spring element is then exactly predefined by inserting the housing insert into the valve housing, as a result of which the position of the foot point can be predefined with high accuracy.
  • the housing insert is embodied in a multifunctional fashion in that, in addition to the support of the foot point for the spring element, said housing insert has recesses through which the pressure medium can pass out of the control valve in order to form a port, in particular a tank port.
  • the production of the recesses in a housing insert is simplified with respect to such production for the design having a blind bore, with additional configuration possibilities for the recesses, for the number of recesses and for their distribution over the housing insert also being provided.
  • the recesses can extend inwards from an outer edge of the housing insert, so that radially outwardly situated webs or spring lips are formed between the recesses, which webs or spring lips can advantageously be used for a connection between the housing insert and the valve housing, while in some circumstances, a closed central region of the housing insert is provided in a radially inward region.
  • connection can be a form-fitting, force-fitting or cohesive connection.
  • the housing insert can be pressed or screwed into the valve housing.
  • the invention proposes that the housing insert is clipped into the valve housing.
  • the housing insert in longitudinal section, is approximately in the form of the longitudinal section of a hat or of a pot.
  • the “brim” of the hat or the edge of the pot can be radially compressed and expanded, so that the edge or brim is clipped into a suitable groove of an inner lateral surface of the valve housing.
  • the housing insert can be produced cost-effectively, for example as a sheet metal part or a shaped part.
  • the previously mentioned recesses can be advantageous in promoting the elastic compression and expansion of the edge or of the brim in the radial direction, said recesses forming elastic webs or spring lips as mentioned previously.
  • the mid-region of the hat is conical, said mid-region adjoining the edge or the brim.
  • the desired deformation for clipping the housing insert in can be provided in this case by elastically deforming the conical mid-region and/or by changing the cone angle of the mid-region.
  • the conical design of the mid-region offers improved possibilities for mounting the housing insert into the valve housing, as will be explained in more detail in the following.
  • the housing insert fulfills the additional function of providing a stop for the control piston, in order to predefine an axial end position of the control piston. This results in a defined end position of the control piston, as a result of which insufficient desired opening positions to one of the ports are avoided.
  • a stop for the control piston is provided only by the spring element “being compressed fully”.
  • the position of the stop can be predefined exactly by means of the separately produced housing insert which is inserted into the valve housing.
  • a spring action and/or damping action for an “impact” of the control piston against the stop can be obtained by suitably configuring the mechanical properties of the housing insert and/or the hydraulic properties in the region of the housing insert.
  • control valve is suitable for being integrated into a camshaft. This additionally results, in some circumstances, in short hydraulic transmission paths between the control valve and the associated working chambers of the camshaft adjuster.
  • a bore is initially formed in the valve housing, said bore being at least of a length which permits it to hold both a control piston and also a housing insert.
  • said bore is a through bore with a constant cross section, wherein different cross-sectional configurations along the length of the bore are, however, also possible.
  • a groove is formed in the bore of the valve housing, into which bore a housing insert can later be clipped.
  • the housing insert is subsequently radially compressed. Said compression preferably takes place in such a way that the outer diameter of the housing insert is less than the diameter of the bore in that region in which the housing insert is inserted into the valve housing.
  • the housing insert is then inserted into the bore of the valve housing, approximately as far as into the region of the groove, where the housing insert is then radially expanded, in particular by means of elastic forces of the housing insert.
  • the radially outer edge of the housing insert is ultimately received in the groove of the valve housing.
  • the radial compression and/or the insertion of the housing insert into the groove can be assisted by means of suitable insertion slopes in the region of the valve housing. Alternatively, or in addition, the compression and expansion can take place using suitable tools.
  • the housing insert has a conical mid-region, wherein the housing insert is radially elastically expanded and compressed by changing the opening angle of the conical mid-region.
  • Assembly is particularly simple if the housing insert is held in the compressed state by means of a tool which “retains” the previously mentioned reduced opening angle of the cone until the housing insert is arranged in the valve housing at the appropriate position for expansion.
  • FIG. 1 shows a longitudinal section through a device for changing the control times of an internal combustion engine having a pressure medium circuit
  • FIG. 2 shows a cross section through the device illustrated in FIG. 1 , along the line II-II,
  • FIG. 3 shows a longitudinal section through a control valve
  • FIG. 4 shows a longitudinal section through a second embodiment of a control valve
  • FIG. 5 shows a longitudinal section through a third embodiment of a control valve
  • FIG. 6 shows a longitudinal section though a fourth embodiment of a control valve
  • FIG. 7 shows a longitudinal section through a further embodiment of a control valve
  • FIG. 8 shows the control valve according to FIG. 7 in an end position predefined by a housing insert
  • FIG. 9 shows a front view of a housing insert
  • FIG. 10 shows a longitudinal section of a housing insert
  • FIG. 11 shows an assembly step for inserting the housing insert into the valve housing with a tool for holding the housing insert in a compressed state.
  • FIGS. 1 and 2 show a device 1 for changing the control times of an internal combustion engine.
  • the device 1 substantially comprises a stator 2 and a rotor 3 which is arranged concentrically with respect thereto.
  • a drive wheel 4 is rotationally fixedly connected to the stator 2 and in the illustrated embodiment is embodied as a sprocket. Embodiments of the drive wheel 4 as a belt or as a gearwheel are likewise conceivable.
  • the stator 2 is rotatably mounted on the rotor 3 , wherein in the illustrated embodiment, five recesses 5 which are spaced apart from one another in the circumferential direction are provided on the inner lateral surface of the stator 2 .
  • the recesses 5 are delimited in the radial direction by the stator 2 and the rotor 3 , in the circumferential direction by two side walls 6 of the stator 2 , and in the axial direction by a first and a second side cover 7 , 8 . Each of the recesses 5 is closed off in a pressure-tight manner in this way.
  • the first and second side covers 7 , 8 are connected to the stator 2 by means of connecting elements 9 , for example screws.
  • Axially running vane grooves 10 are formed on the outer lateral surface of the rotor 3 , with one radially extending vane 11 being formed in each vane groove 10 .
  • Each vane 11 extends into each recess 5 , with the vanes 11 bearing against the stator 2 in the radial direction and against the side covers 7 , 8 in the axial direction.
  • Each vane 11 divides a recess 5 into two pressure chambers 12 , 13 which act counter to one another.
  • leaf spring elements 15 are attached between the groove bases 14 of the vane grooves 10 and the vanes 11 , said leaf spring elements exerting a force on the vanes 11 in the radial direction.
  • the first and second pressure chambers 12 , 13 can be connected via a control valve 18 to a pressure medium pump 19 or to a tank 20 by means of first and second pressure medium lines 16 , 17 .
  • the stator 2 is driven by means of a crankshaft chain drive (not illustrated) which engages on the drive wheel 4 of said stator 2 . It is likewise conceivable for the stator 2 to be driven by means of a belt drive or toothed drive.
  • the rotor 3 is connected to a camshaft (not illustrated) in a force-fitting, form-fitting or cohesive fashion, for example by means of a press fit or by a screw connection by means of a central screw.
  • the relative rotation of the rotor 3 with respect to the stator 2 as a consequence of the inlet or outlet of pressure medium into or out of the pressure chambers 12 , 13 , results in a phase shift between the camshaft and the crankshaft.
  • Targeted inlet and outlet of pressure medium into the pressure chambers 12 , 13 can therefore be used to vary the control times of the gas exchange valves of the internal combustion engine in a targeted fashion.
  • the pressure medium lines 16 , 17 are formed as substantially radially arranged bores which extend from a central bore 22 of the rotor 3 to the outer lateral surface thereof.
  • a central valve (not illustrated) can be arranged within the central bore 22 , by means of which central valve the pressure chambers 12 , 13 can be connected to the pressure medium pump 19 or the tank 20 in a targeted fashion.
  • a further option is to arrange a pressure medium distributor within the central bore 22 , which pressure medium distributor connects the pressure medium lines 16 , 17 via pressure medium ducts and annular grooves to the ports of an externally attached control valve 18 .
  • the substantially radially running side walls 6 of the recesses 5 are provided with moldings 23 which extend into the recesses 5 in the circumferential direction.
  • the moldings 23 serve as stops for the vanes 11 and ensure that the pressure chambers 12 , 13 can be supplied with pressure medium even when the rotor 3 assumes one of its extreme positions relative to the stator 2 , in which position the vanes 11 bear against one of the side walls 6 .
  • the rotor 3 In the event of insufficient pressure medium supply to the device 1 , for example during the starting phase of the internal combustion engine, the rotor 3 is moved relative to the stator 2 in an uncontrolled fashion as a result of alternating and drag torques which the camshaft exerts on said rotor 3 .
  • the drag torques of the camshaft push the rotor relative to the stator in a circumferential direction which opposes the rotational direction of the stator, until said rotor and stator come into contact at the side walls 6 .
  • alternating torques which the camshaft exerts on the rotor 3 lead to reciprocating oscillation of the rotor 3 and therefore of the vane 11 in the recesses 5 , until at least one of the pressure chambers 12 , 13 is completely filled with pressure medium.
  • a locking element 24 is provided in the device 1 .
  • a pot-shaped piston 26 is arranged in an axial bore 25 of the rotor 3 , which pot-shaped piston 26 is acted on with force in the axial direction by means of a spring 27 .
  • the spring 27 is supported at one side in the axial direction on a ventilation element 28 and is arranged with its remote axial end within the pot-shaped piston 26 .
  • a slotted guide 29 is formed in the first side cover 7 such that the rotor 3 can be locked, relative to the stator 2 , in a position which corresponds to the position during starting of the internal combustion engine. In said position, the piston 26 is pushed into the slotted guide 29 by means of the spring 27 when there is insufficient pressure medium supply to the device 1 .
  • means are provided to push the piston 26 back into the axial bore 25 , and therefore to release the locking, when there is sufficient pressure medium supply to the device 1 .
  • the ventilation element 28 is provided with axially running grooves, along which the pressure medium can be conducted to a bore in the second side cover 8 .
  • FIG. 1 additionally illustrates the pressure medium circuit 31 .
  • a pressure medium port P of a control valve 18 is supplied with pressure medium from a tank 20 by means of a pressure medium pump 19 .
  • pressure medium is conducted from the control valve 18 into the tank 20 via a tank port T.
  • the control valve 18 additionally has two working ports A, B.
  • the control valve 18 can be placed in 3 positions by means of an electromagnetic actuating element 32 which acts counter to the spring force of a first spring element 33 .
  • the working port A is connected to the tank port T and the pressure medium port P is connected to the working port B and therefore to the second pressure chamber 13 .
  • both the working port A and the working port B are disconnected both from the pressure medium port P and from the tank port T.
  • the pressure medium port P is connected to the working port A and consequently to the first pressure chamber 12
  • the second pressure chamber 13 is connected to the tank port T via the working port B.
  • FIG. 3 illustrates a control valve 18 in longitudinal section.
  • the substantially hollow cylindrical valve housing 34 is provided with a radial pressure medium port P, a radial tank port T 1 , two working ports A, B and an axial tank port T 2 .
  • the radial ports P, T 1 , A, B are formed as first annular grooves 35 which are spaced apart from one another axially and are formed in the outer lateral surface of the valve housing 34 .
  • the first annular grooves 35 are provided with a plurality of first openings 36 which open out into the interior of the valve housing 34 .
  • a control piston 37 which is likewise of substantially hollow cylindrical form is arranged in an axially displaceable fashion within the valve housing 34 .
  • One axial end of the control piston is delimited in a pressure-tight fashion by means of a wall section 37 a .
  • the wall section 37 a can be formed in one piece with the control piston or can be formed separately from the latter.
  • the control piston 37 can be placed and held in any desired position within two extreme values, counter to the spring force of the first spring element 33 , by means of an actuating element 32 (not illustrated).
  • the outer lateral surface of the control piston 37 is provided with a second, a third and a fourth annular groove 38 , 39 , 40 .
  • the second and the third annular grooves 38 , 39 communicate with the interior of the control piston 37 via second and third openings 41 , 42 .
  • the second annular groove 38 is formed in such a way that it communicates with the first openings 36 of the first annular groove 35 of the pressure medium port P in all positions of the control piston 37 relative to the valve housing 34 .
  • pressure medium passes from the pressure medium port P, via the second annular groove 38 and the second openings 41 , into the interior of the control piston 37 .
  • the pressure medium passes via the third openings 42 and the third annular groove 39 to the working port B.
  • pressure medium is pushed out of the second pressure chambers 12 to the working port A, and passes to the axially arranged tank port T 2 via the first openings 36 of said working port A.
  • the control piston 37 is displaced counter to the spring force of the first spring element 33 .
  • the overlap of the first openings 36 of the working port B by a first control edge 43 of the third annular groove 39 increases.
  • the overlap of the first openings 36 of the working port A by a second control edge 44 of the control piston 37 likewise increases.
  • the control piston 37 reaches a middle position (not illustrated)
  • the working port A is no longer connected to the axial tank port T 2 as a result of complete overlap of the second control edge 44 .
  • neither the working port A nor the working port B communicates with the third annular groove 39 .
  • the control piston 37 can be designed in such a way that, in the middle position, both working ports A, B communicate with the third annular groove 39 .
  • a third control edge 45 unblocks the first openings 36 of the working port A to the third annular groove 39 .
  • Pressure medium which flows in from the pressure medium port P now passes only to the working port A.
  • the fourth annular groove 40 communicates both with the working port B and with the radial tank port T l . In this way, pressure medium passes from the pressure medium pump 19 into the first pressure chambers 12 which leads to a relative rotation of the rotor 3 with respect to the stator 2 .
  • the pressure medium which is pushed out of the second pressure chambers 13 passes via the working port B and the fourth annular groove 40 to the radial tank port T 1 .
  • the third control edge 45 and the fourth annular groove 40 can be formed in such a way that, during displacement of the control piston 37 , the working port A is initially connected to the pressure medium pump 19 and the working port B is then connected to the tank 20 . Alternatively, both connections can be produced at the same time.
  • a substantially cylindrical filter 46 is arranged within the control piston 37 .
  • the filter 46 comprises a frame 47 , preferably made from plastic, and at least one filter section 48 .
  • the filter section 48 is preferably composed of a mesh of plastic or metal, with the frame 47 being non-detachably connected to the filter sections 48 .
  • the frame 47 has in each case one substantially circular segment 49 , with the circular segments 49 being connected to one another by means of a plurality of longitudinal struts 50 .
  • the filter 46 is fixed within the control piston 37 in a force-fitting fashion by means of the circular segments 49 .
  • an axial stop 51 within the control piston 37 , said axial stop 51 serving as a travel delimitation when pressing the filter 46 into the control piston 37 .
  • the filter 46 can be pressed in in a manner which is controlled in terms of travel.
  • the filter 46 is arranged in the region of, and completely overlaps, the second openings 41 .
  • the filter 46 bears, at one of its axial ends, against the axial stop 51 .
  • the other axial end rests on a pot-shaped sleeve 52 which is fixed in the interior of the control piston 37 in a force-fitting manner. This ensures that the filter 46 maintains its position during operation of the internal combustion engine.
  • the sleeve 52 additionally closes off the control piston 37 in the axial direction and can serve as an engagement point of a plunger rod (not illustrated) of the actuating element 32 .
  • the circular segments 49 of the filter 46 are connected in the radial direction to an inner lateral surface 53 of the control piston 37 in a pressure-tight manner, while a gap 54 is provided between the longitudinal struts 50 and the inner lateral surface 53 .
  • Pressure medium flowing in from the pressure port P passes via the second openings 41 into an annular groove which is formed between the filter sections 48 and the inner lateral surface 53 and runs around the filter 46 .
  • the pressure medium passes via the filter sections 48 into the interior of the control piston 37 , as a result of which any impurities which are present in the pressure medium are effectively kept away from the control edges 43 , 44 , 45 .
  • FIG. 4 illustrates a further embodiment of a control valve 18 .
  • the design and function of said variant are approximately identical to the first embodiment.
  • no axial stop 51 is formed in the inner lateral surface 53 of the control piston 37 here.
  • the filter 46 is pressed into the control piston 37 in a manner which is controlled in terms of travel.
  • a non-return valve 55 is arranged between the filter 46 and the working ports A, B.
  • Said non-return valve 55 comprises a housing 56 which is arranged within the control piston 37 in a force-fitting manner.
  • a blocking body 57 which is pressed into a seat 59 of the non-return valve 55 by means of a second spring element 58 , is situated within the housing 56 .
  • a second spring element 58 is situated within the housing 56 .
  • ball non-return valve illustrated here other embodiments, for example a plate non-return valve, can also be used.
  • Pressure medium flowing into the control valve 18 passes to the non-return valve 55 after passing through the filter 46 .
  • the control edges 43 , 44 , 45 and the non-return valve 55 are effectively protected from damage on account of dirt particles in the pressure medium.
  • the blocking body 57 is displaced counter to the spring force of the second spring element 58 , and pressure medium can pass to the working ports A, B via fourth openings 60 , which are formed in the housing 56 , and the third openings 42 .
  • pressure pulsations are generated within the device 1 as a result of alternating torques of the camshaft.
  • pressure peaks occur which are transmitted into the hydraulic system and can damage other consumers.
  • the arrangement of a non-return valve 55 between the pressure chambers 12 , 13 and the pressure medium port P prevents transmission of said pressure peaks into the hydraulic system. This protects both the pressure medium pump 19 and further consumers which are connected to said pressure medium circuit.
  • the non-return valve 55 is advantageously arranged within the control piston 37 , and thus requires no additional installation space.
  • a further advantage is that, specifically when using the control valve 18 as a central valve, the path between the location at which the pressure pulsations are generated and the non-return valve 55 is a minimum. Pressure fluctuations are intercepted practically at the point of generation.
  • FIG. 5 illustrates a further embodiment of a control valve 18 .
  • the design and function of said control valve 18 are approximately identical to the variant shown in FIG. 4 .
  • the filter 46 is advantageously arranged within the housing 56 of the non-return valve 55 .
  • the housing 56 can be embodied as a cost-effective plastic shaped part.
  • That face end of the control piston 37 which faces away from the tank port T 2 is formed such that it is closed off.
  • the housing 56 is H-shaped in longitudinal section, with the filter 46 being arranged in one chamber of the H and the blocking body 57 with the second spring element 58 being arranged in the other chamber.
  • the second spring element 58 is supported on a closure 61 .
  • the radially running part of the housing 56 is provided with an opening which is matched to the blocking body 57 and serves as a seat 59 .
  • FIG. 6 shows a fourth variant of a control valve 18 , in which a control piston 37 is arranged in an axially displaceable fashion within a substantially hollow cylindrical valve housing 34 .
  • the control piston 37 is likewise of substantially hollow cylindrical design, with that end side which faces toward the axially aligned pressure medium port P being formed such that it is open.
  • the outer lateral surface of the control piston 37 is provided with a first annular groove 35 and a group of first openings 36 .
  • pressure medium passes into the interior of the valve housing 34 via the axially aligned pressure medium port P.
  • the pressure medium passes either via second openings 41 to the working port B or via third openings 42 to the working port A.
  • the respective working port A, B which is not being acted on by pressure medium is connected via the first annular groove 35 to the tank port T.
  • a filter 46 is arranged between the pressure medium port P and the working ports A, B.
  • the filter 46 is formed in the shape of a pot and comprises a frame 47 and filter sections 48 .
  • the frame 47 is provided with a radially extending collar which serves as an axial stop of the filter 46 .
  • a non-return valve 55 can also be arranged between the pressure medium port P and the working ports A, B here.
  • a control valve 70 has a control piston 71 which is arranged in a valve housing 72 in an axially displaceable fashion.
  • the control valve 70 and the control piston 71 are, for example, formed corresponding to one of the exemplary embodiments illustrated in FIGS. 1 to 6 .
  • the bore 73 of the valve housing 72 is formed according to FIG. 7 as a through bore of constant diameter, with end-side chamfers 74 , 75 which widen outwards.
  • a pressure spring 76 which substantially corresponds to the spring element 33 in the exemplary embodiments of FIG. 1 to FIG.
  • the control piston 71 has a foot point 77 , which is supported on an end side of the control piston 71 , and a foot point 78 , which is supported on a housing insert 79 .
  • the housing insert 79 is clipped into a groove 80 of the inner lateral surface 81 of the valve housing 72 .
  • the control piston 71 radially surrounds the pressure spring 76 by means of an annular shoulder 82 , resulting, in some circumstances, in the pressure spring 76 being guided.
  • a stop 83 here having an annular stop face, projects from the annular shoulder 82 in the direction of the housing insert 79 , said stop 83 coming into contact with the housing insert 79 in the end position of the control valve 70 as illustrated in FIG. 8 .
  • FIG. 9 shows a front view of the housing insert 79
  • FIG. 10 shows a longitudinal section of the housing insert 79 .
  • the housing insert 79 is substantially of pot-shaped or hat-shaped form with
  • the pressure spring 78 is held in the mid-region 86 , so that, in some circumstances, the housing insert 79 can radially guide the pressure spring 76 .
  • three notches or recesses 88 extend radially inwards from the edge 85 , said notches or recesses 88
  • Annular corners 89 or tapers are provided in the transition region between the recesses 88 and the edge 85 , said annular corners 89 or tapers, together with the rest of the design of the housing insert 79 , being intended to prevent the housing insert 79 becoming jammed in the valve housing during assembly.
  • the conical mid-region 86 has an opening angle 90 .
  • the opening angle 90 is reduced and/or the mid-region 86 is elastically deformed.
  • the opening angle 90 increases again.
  • the housing insert 79 is preferably inserted into the valve housing 72 using a tool 91 according to FIG. 11 .
  • the tool 91 is rotationally symmetrical about the longitudinal axis 95 - 95 .
  • the tool 91 has a central blind bore which can be of cylindrical or conical form. In each case, the opening angle of the blind bore 92 is less than the opening angle 90 of the housing insert 79 in the expanded state. Consequently, the conical mid-region is radially outwardly pressed against the inner face of the blind bore and is held therein in a force-fitting manner.
  • the housing insert 79 can be inserted in the radially compressed state into the blind bore 92 , with the outer diameter of the housing insert 79 approximately corresponding to the diameter of the bore 73 or being less than said diameter.
  • the housing insert 79 can be inserted into the valve housing 72 by means of the tool 91 , as illustrated in FIG. 11 .
  • a shoulder 93 of the tool 91 can predefine how far the tool 91 , with the housing insert 79 , can be pushed into the valve housing 72 .
  • the housing insert 79 is approximately in the region of the groove 80 , the housing insert 79 can be pushed out of or ejected from the tool 91 .
  • an ejecting force can be exerted on the housing insert 79 by means of an auxiliary device which is inserted into a longitudinal bore 94 which opens out into the blind bore 92 . If the blind bore 92 is conical rather than cylindrical, the radial outer diameter of the housing insert 79 can be increased continuously with displacement.
  • the recesses 88 form a flow cross section to the port, for example in the direction of the tank.
  • a suitable selection of the ratio between the flow cross sections at port B in the control valve 70 and the recesses 88 is significant. If the outflow cross section, which is predefined by the recesses 88 , is too small relative to the flow cross sections of the other ports involved, an undesired dynamic pressure can build up in the valve.
  • the housing insert 79 can be supplied continuously, for example by means of an oscillating conveyer.
  • the force required for deforming the housing insert 79 and the securing effect which can be obtained by clipping the housing insert 79 into the groove 80 can be structurally predefined.
  • the mechanical strength of the housing insert 79 and/or the surface hardness, in particular in the support region of the pressure spring 76 is preferably increased by means of case-hardening and tempering.
US11/500,652 2005-08-09 2006-08-08 Control valve and method for its production Abandoned US20070056540A1 (en)

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DE102005037480A DE102005037480A1 (de) 2005-08-09 2005-08-09 Steuerventil und Verfahren zur Herstellung desselben
DE102005037480.8 2005-08-09

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EP (1) EP1752691B1 (de)
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DE (2) DE102005037480A1 (de)

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US20110174253A1 (en) * 2007-12-05 2011-07-21 Schaeffler Technologies Gmbh & Co. Kg Device for variably adjusting control times of gas exchange valves of an internal combustion engine
US20120111296A1 (en) * 2009-07-04 2012-05-10 Schaeffler Technologies Gmbh & Co. Kg Central valve of a camshaft adjuster of an internal combustion engine
US20120234275A1 (en) * 2011-03-16 2012-09-20 Delphi Technologies, Inc. Camshaft phaser with coaxial control valves
US20120304953A1 (en) * 2009-11-20 2012-12-06 Schaeffler Technologies AG & Co. KG Switchable pressure supply device
US20130092113A1 (en) * 2011-10-05 2013-04-18 Schwabische Huttenwerke Automotive Gmbh Control Valve Comprising an Integrated Filter and Cam Shaft Phase Setter Comprising Said Control Valve
US8695548B2 (en) 2010-12-10 2014-04-15 Denso Corporation Valve timing control apparatus
US20180003090A1 (en) * 2015-01-15 2018-01-04 Schaeffler Technologies AG & Co. KG Control valve having an outflow channel
US20190257222A1 (en) * 2018-02-21 2019-08-22 ECO Holding 1 GmbH Center bolt oil control valve to control a cam phaser with a calibration cap having a pressure check valve and filter

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DE102007015333B4 (de) * 2007-03-30 2020-08-27 Schaeffler Technologies AG & Co. KG Steuerventil und Herstellungsverfahren für das Steuerventil
WO2009010332A1 (de) * 2007-07-18 2009-01-22 Schaeffler Kg Ventilteil eines hydraulischen steuerventils
JP4518149B2 (ja) * 2008-01-10 2010-08-04 株式会社デンソー バルブタイミング調整装置
DE102008006179A1 (de) 2008-01-26 2009-07-30 Schaeffler Kg Steuerventil für eine Vorrichtung zur variablen Einstellung der Steuerzeiten von Gaswechselventilen in Brennkraftmaschinen
JP5360173B2 (ja) * 2011-09-15 2013-12-04 株式会社デンソー バルブタイミング調整装置
DE102011056264B4 (de) * 2011-12-12 2020-03-05 Hilite Germany Gmbh Hydraulikventil
DE102012106096B3 (de) * 2012-07-06 2014-05-15 Hilite Germany Gmbh Schwenkmotorversteller mit einem Hydraulikventil
JP6015605B2 (ja) * 2013-09-17 2016-10-26 株式会社デンソー バルブタイミング調整装置
EP3143262B1 (de) 2014-05-12 2019-07-10 Volvo Truck Corporation Fluidsteuerungsventil
JP6653631B2 (ja) * 2016-07-01 2020-02-26 日立オートモティブシステムズ株式会社 油圧制御弁及び内燃機関のバルブタイミング制御装置
DE102021108361A1 (de) 2021-04-01 2022-10-06 Schaeffler Technologies AG & Co. KG Hydraulikeinheit für eine elektrohydraulische Gaswechselventilsteuerung

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US8215273B2 (en) * 2007-05-02 2012-07-10 Schaeffler Technologies AG & Co. KG Camshaft adjuster for an internal combustion engine with integrated valve slide
US20080271690A1 (en) * 2007-05-02 2008-11-06 Schaeffler Kg Camshaft adjuster for an internal combustion engine with integrated valve slide
US20110174253A1 (en) * 2007-12-05 2011-07-21 Schaeffler Technologies Gmbh & Co. Kg Device for variably adjusting control times of gas exchange valves of an internal combustion engine
US8522733B2 (en) * 2007-12-05 2013-09-03 Schaeffler Technologies AG & Co. KG Device for variably adjusting control times of gas exchange valves of an internal combustion engine
US20120111296A1 (en) * 2009-07-04 2012-05-10 Schaeffler Technologies Gmbh & Co. Kg Central valve of a camshaft adjuster of an internal combustion engine
US8893676B2 (en) * 2009-07-04 2014-11-25 Schaeffler Technologies AG & Co. KG Central valve of a camshaft adjuster of an internal combustion engine
US20120304953A1 (en) * 2009-11-20 2012-12-06 Schaeffler Technologies AG & Co. KG Switchable pressure supply device
US8813709B2 (en) * 2009-11-20 2014-08-26 Schaeffler Technologies Gmbh & Co. Kg Switchable pressure supply device
US8695548B2 (en) 2010-12-10 2014-04-15 Denso Corporation Valve timing control apparatus
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US20120234275A1 (en) * 2011-03-16 2012-09-20 Delphi Technologies, Inc. Camshaft phaser with coaxial control valves
US9127575B2 (en) 2011-03-16 2015-09-08 Delphi Technologies, Inc. Camshaft phaser with coaxial control valves
US20130092113A1 (en) * 2011-10-05 2013-04-18 Schwabische Huttenwerke Automotive Gmbh Control Valve Comprising an Integrated Filter and Cam Shaft Phase Setter Comprising Said Control Valve
US8910602B2 (en) * 2011-10-05 2014-12-16 Schwabische Huttenwerke Automotive Gmbh Control valve comprising an integrated filter and cam shaft phase setter comprising said control valve
US20180003090A1 (en) * 2015-01-15 2018-01-04 Schaeffler Technologies AG & Co. KG Control valve having an outflow channel
US10247060B2 (en) * 2015-01-15 2019-04-02 Schaeffler Technologies AG & Co. KG Control valve having an outflow channel
US20190257222A1 (en) * 2018-02-21 2019-08-22 ECO Holding 1 GmbH Center bolt oil control valve to control a cam phaser with a calibration cap having a pressure check valve and filter
US10662827B2 (en) * 2018-02-21 2020-05-26 ECO Holding 1 GmbH Center bolt oil control valve to control a cam phaser with a calibration cap having a pressure check valve and filter

Also Published As

Publication number Publication date
JP2007046786A (ja) 2007-02-22
DE102005037480A1 (de) 2007-02-15
DE502006001806D1 (de) 2008-11-27
EP1752691A1 (de) 2007-02-14
EP1752691B1 (de) 2008-10-15

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