US20070056540A1 - Control valve and method for its production - Google Patents
Control valve and method for its production Download PDFInfo
- 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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- US
- 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
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Classifications
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- 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
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- 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
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- 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
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- 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
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Valve Device For Special Equipments (AREA)
- Multiple-Way Valves (AREA)
Abstract
The invention relates to a control valve for influencing the action of a pressure medium on a camshaft adjuster of an internal combustion engine. A control valve of said type comprises a valve housing (72), in which a displaceable control piston (71) is arranged in a blind bore.
According to the invention, the valve housing (72) is produced with a through bore (73) instead of a blind bore, into which through bore (73) a housing insert (79) is clipped into a groove (80). The housing insert can serve to support a pressure spring (76), and can also additionally have recesses, in the region of which the housing insert (79) serves to form a port, for example to a tank T.
Description
- 1. Field of the Invention
- 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.
- 2. Background of the Invention
- 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. In one axial position of the control piston, in the control valve, 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. In another axial position of the control piston, 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.
- According to the invention, 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 fromdependent 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. Here, 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. On the other hand, 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. In addition, 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. For example, 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.
- According to the invention, 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. This means that both the valve housing and the housing insert can be produced separately, as a result of which
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- further manufacturing possibilities can be utilized,
- the housing insert can be produced with defined tolerances,
- the mechanical properties of the housing insert can be configured in a targeted fashion
- and there is greater scope for configuring the geometry of the housing insert than a base of the blind bore.
- 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. On the other hand, for different control valves, it is possible in some circumstances for the same valve housing to be used in connection with different housing inserts, different positions of the housing insert relative to the valve housing and/or different support locations of the spring element by means of different geometries of the housing inserts which are used.
- According to a preferred embodiment of the control valve according to the invention, 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. By way of example, 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.
- There are many possibilities for a connection between the housing insert and the valve housing. For example, the connection can be a form-fitting, force-fitting or cohesive connection. The housing insert can be pressed or screwed into the valve housing. According to one particular proposal for a simple design of the connection of the housing insert to the valve housing, which connection is also simple to assemble and, if appropriate, to disassemble, the invention proposes that the housing insert is clipped into the valve housing.
- According to a refinement of the invention, in longitudinal section, the housing insert is approximately in the form of the longitudinal section of a hat or of a pot. By elastically deforming the housing insert, 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. Accordingly, for manufacture, only one suitably formed groove, if appropriate with at least one insertion slope, must be formed in the lateral surface of the valve housing, while 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.
- According to a further proposal of the invention, 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. In addition, 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.
- According to a refinement of the invention, in addition to the function of supporting a foot point of the spring element and the function of forming the recesses for the port, 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. At the same time, it is possible to avoid the situation where 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.
- A particularly compact design is obtained if the 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.
- To produce a control valve, 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. In the simplest case, 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. In a subsequent working operation, 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. In said state, 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. In the “clipped-in position”, 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.
- According to a refinement of the invention, 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.
- Advantageous refinements of the invention emerge from the dependent patent claims and from the entire description. Further features can be gathered from the drawings—in particular the illustrated geometries and the relative dimensions of several components with respect to to one another and their relative arrangement and operative connection. The combination of features of different embodiments of the invention, or of features of different patent claims, deviating from the selected references back, is likewise possible and is hereby encouraged. This also relates to features which are illustrated in separate drawing figures or are mentioned in the description thereof. Said features can also be combined with features of different patent claims.
- In the figures:
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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 inFIG. 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 toFIG. 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 and -
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 astator 2 and arotor 3 which is arranged concentrically with respect thereto. A drive wheel 4 is rotationally fixedly connected to thestator 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. Thestator 2 is rotatably mounted on therotor 3, wherein in the illustrated embodiment, fiverecesses 5 which are spaced apart from one another in the circumferential direction are provided on the inner lateral surface of thestator 2. Therecesses 5 are delimited in the radial direction by thestator 2 and therotor 3, in the circumferential direction by twoside walls 6 of thestator 2, and in the axial direction by a first and asecond side cover 7, 8. Each of therecesses 5 is closed off in a pressure-tight manner in this way. The first and second side covers 7, 8 are connected to thestator 2 by means of connectingelements 9, for example screws. - Axially running vane grooves 10 are formed on the outer lateral surface of the
rotor 3, with one radially extendingvane 11 being formed in each vane groove 10. - One
vane 11 extends into eachrecess 5, with thevanes 11 bearing against thestator 2 in the radial direction and against the side covers 7, 8 in the axial direction. Eachvane 11 divides arecess 5 into twopressure chambers vane 11 bears against thestator 2 in a pressure-tight manner,leaf spring elements 15 are attached between the groove bases 14 of the vane grooves 10 and thevanes 11, said leaf spring elements exerting a force on thevanes 11 in the radial direction. - The first and
second pressure chambers control valve 18 to a pressuremedium pump 19 or to atank 20 by means of first and secondpressure medium lines stator 2 with respect to therotor 3. Here, it is provided either that all thefirst pressure chambers 12 are connected to the pressuremedium pump 19 and all thesecond pressure chambers 13 are connected to thetank 20, or that the connections are in the exact opposite configuration. If thefirst pressure chambers 12 are connected to the pressuremedium pump 19 and thesecond pressure chambers 13 are connected to thetank 20, thefirst pressure chambers 12 expand at the expense of thesecond pressure chambers 13. This results in a displacement of thevanes 11 in the circumferential direction, in the direction illustrated by thearrow 21. Therotor 3 is rotated relative to thestator 2 as a result of the displacement of thevanes 11. - In the illustrated embodiment, the
stator 2 is driven by means of a crankshaft chain drive (not illustrated) which engages on the drive wheel 4 of saidstator 2. It is likewise conceivable for thestator 2 to be driven by means of a belt drive or toothed drive. Therotor 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 therotor 3 with respect to thestator 2, as a consequence of the inlet or outlet of pressure medium into or out of thepressure chambers pressure chambers - In the illustrated embodiment, the pressure
medium lines central bore 22 of therotor 3 to the outer lateral surface thereof. A central valve (not illustrated) can be arranged within thecentral bore 22, by means of which central valve thepressure chambers medium pump 19 or thetank 20 in a targeted fashion. A further option is to arrange a pressure medium distributor within thecentral bore 22, which pressure medium distributor connects the pressuremedium lines control valve 18. - The substantially radially running
side walls 6 of therecesses 5 are provided withmoldings 23 which extend into therecesses 5 in the circumferential direction. Themoldings 23 serve as stops for thevanes 11 and ensure that thepressure chambers rotor 3 assumes one of its extreme positions relative to thestator 2, in which position thevanes 11 bear against one of theside walls 6. - 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 thestator 2 in an uncontrolled fashion as a result of alternating and drag torques which the camshaft exerts on saidrotor 3. In a first phase, 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 theside walls 6. Subsequently, the alternating torques which the camshaft exerts on therotor 3 lead to reciprocating oscillation of therotor 3 and therefore of thevane 11 in therecesses 5, until at least one of thepressure chambers element 24 is provided in the device 1. In addition, a pot-shapedpiston 26 is arranged in anaxial bore 25 of therotor 3, which pot-shapedpiston 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 aventilation element 28 and is arranged with its remote axial end within the pot-shapedpiston 26. A slottedguide 29 is formed in thefirst side cover 7 such that therotor 3 can be locked, relative to thestator 2, in a position which corresponds to the position during starting of the internal combustion engine. In said position, thepiston 26 is pushed into the slottedguide 29 by means of the spring 27 when there is insufficient pressure medium supply to the device 1. In addition, means are provided to push thepiston 26 back into theaxial bore 25, and therefore to release the locking, when there is sufficient pressure medium supply to the device 1. This is conventionally achieved by means of pressure medium which is conducted via pressure medium lines (not illustrated) into a cut-out 30 which is formed on the cover-side face end of thepiston 26. In order to be able to conduct leakage oil out of the spring space of theaxial bore 25, theventilation 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 thepressure medium circuit 31. A pressure medium port P of acontrol valve 18 is supplied with pressure medium from atank 20 by means of a pressuremedium pump 19. At the same time, pressure medium is conducted from thecontrol valve 18 into thetank 20 via a tank port T. Thecontrol valve 18 additionally has two working ports A, B. Thecontrol valve 18 can be placed in 3 positions by means of anelectromagnetic actuating element 32 which acts counter to the spring force of afirst spring element 33. In a first position of thecontrol valve 18, which corresponds to a state of theactuating element 32 in which no electrical current is supplied, 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 thesecond pressure chamber 13. In a middle position, 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. In a third position of thecontrol valve 18, the pressure medium port P is connected to the working port A and consequently to thefirst pressure chamber 12, while thesecond pressure chamber 13 is connected to the tank port T via the working port B. -
FIG. 3 illustrates acontrol valve 18 in longitudinal section. The substantially hollowcylindrical valve housing 34 is provided with a radial pressure medium port P, a radial tank port T1, two working ports A, B and an axial tank port T2. The radial ports P, T1, A, B are formed as firstannular grooves 35 which are spaced apart from one another axially and are formed in the outer lateral surface of thevalve housing 34. The firstannular grooves 35 are provided with a plurality offirst openings 36 which open out into the interior of thevalve housing 34. - A
control piston 37 which is likewise of substantially hollow cylindrical form is arranged in an axially displaceable fashion within thevalve housing 34. One axial end of the control piston is delimited in a pressure-tight fashion by means of awall section 37 a. Thewall section 37 a can be formed in one piece with the control piston or can be formed separately from the latter. Thecontrol piston 37 can be placed and held in any desired position within two extreme values, counter to the spring force of thefirst 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 fourthannular groove annular grooves 38, 39 communicate with the interior of thecontrol piston 37 via second andthird openings annular groove 38 is formed in such a way that it communicates with thefirst openings 36 of the firstannular groove 35 of the pressure medium port P in all positions of thecontrol piston 37 relative to thevalve housing 34. - During operation of the internal combustion engine, pressure medium passes from the pressure medium port P, via the second
annular groove 38 and thesecond openings 41, into the interior of thecontrol piston 37. In the first position of thecontrol piston 37, illustrated inFIG. 3 , the pressure medium passes via thethird openings 42 and the third annular groove 39 to the working port B. As a result of the action of pressure medium on thesecond pressure chambers 13 via the working port B, pressure medium is pushed out of thesecond pressure chambers 12 to the working port A, and passes to the axially arranged tank port T2 via thefirst openings 36 of said working port A. - If the
electromagnetic actuating element 32 is supplied with electrical current, thecontrol piston 37 is displaced counter to the spring force of thefirst spring element 33. As a result, the overlap of thefirst openings 36 of the working port B by a first control edge 43 of the third annular groove 39 increases. The overlap of thefirst openings 36 of the working port A by asecond control edge 44 of thecontrol piston 37 likewise increases. When thecontrol piston 37 reaches a middle position (not illustrated), the working port A is no longer connected to the axial tank port T2 as a result of complete overlap of thesecond control edge 44. In addition, neither the working port A nor the working port B communicates with the third annular groove 39. Alternatively, thecontrol 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. - If the
control piston 37 is displaced further counter to the spring force of thefirst spring element 33, athird control edge 45 unblocks thefirst 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. At the same time, the fourthannular groove 40 communicates both with the working port B and with the radial tank port Tl. In this way, pressure medium passes from the pressuremedium pump 19 into thefirst pressure chambers 12 which leads to a relative rotation of therotor 3 with respect to thestator 2. The pressure medium which is pushed out of thesecond pressure chambers 13 passes via the working port B and the fourthannular groove 40 to the radial tank port T1. Thethird control edge 45 and the fourthannular groove 40 can be formed in such a way that, during displacement of thecontrol piston 37, the working port A is initially connected to the pressuremedium pump 19 and the working port B is then connected to thetank 20. Alternatively, both connections can be produced at the same time. - A substantially
cylindrical filter 46 is arranged within thecontrol piston 37. Thefilter 46 comprises aframe 47, preferably made from plastic, and at least onefilter section 48. Thefilter section 48 is preferably composed of a mesh of plastic or metal, with theframe 47 being non-detachably connected to thefilter sections 48. At the axial ends of thefilter 46, theframe 47 has in each case one substantiallycircular segment 49, with thecircular segments 49 being connected to one another by means of a plurality oflongitudinal struts 50. Thefilter 46 is fixed within thecontrol piston 37 in a force-fitting fashion by means of thecircular segments 49. Here, it is advantageous to form anaxial stop 51 within thecontrol piston 37, saidaxial stop 51 serving as a travel delimitation when pressing thefilter 46 into thecontrol piston 37. Alternatively, thefilter 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, thesecond openings 41. Thefilter 46 bears, at one of its axial ends, against theaxial stop 51. The other axial end rests on a pot-shapedsleeve 52 which is fixed in the interior of thecontrol piston 37 in a force-fitting manner. This ensures that thefilter 46 maintains its position during operation of the internal combustion engine. - The
sleeve 52 additionally closes off thecontrol piston 37 in the axial direction and can serve as an engagement point of a plunger rod (not illustrated) of theactuating element 32. - The
circular segments 49 of thefilter 46 are connected in the radial direction to an innerlateral surface 53 of thecontrol piston 37 in a pressure-tight manner, while agap 54 is provided between thelongitudinal struts 50 and the innerlateral 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 thefilter sections 48 and the innerlateral surface 53 and runs around thefilter 46. The pressure medium passes via thefilter sections 48 into the interior of thecontrol 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 acontrol valve 18. The design and function of said variant are approximately identical to the first embodiment. In contrast to the first embodiment, noaxial stop 51 is formed in the innerlateral surface 53 of thecontrol piston 37 here. During assembly of thecontrol valve 18, thefilter 46 is pressed into thecontrol piston 37 in a manner which is controlled in terms of travel. In said embodiment, anon-return valve 55 is arranged between thefilter 46 and the working ports A, B. Saidnon-return valve 55 comprises ahousing 56 which is arranged within thecontrol piston 37 in a force-fitting manner. A blockingbody 57, which is pressed into aseat 59 of thenon-return valve 55 by means of asecond spring element 58, is situated within thehousing 56. Instead of the 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 thenon-return valve 55 after passing through thefilter 46. As a result of the arrangement of thefilter 46 directly downstream of the pressure port P, the control edges 43, 44, 45 and thenon-return valve 55 are effectively protected from damage on account of dirt particles in the pressure medium. Above a certain pressure within thecontrol piston 37, the blockingbody 57 is displaced counter to the spring force of thesecond spring element 58, and pressure medium can pass to the working ports A, B viafourth openings 60, which are formed in thehousing 56, and thethird openings 42. - During operation of the internal combustion engine, pressure pulsations are generated within the device 1 as a result of alternating torques of the camshaft. In the process, pressure peaks occur which are transmitted into the hydraulic system and can damage other consumers. The arrangement of a
non-return valve 55 between thepressure chambers medium pump 19 and further consumers which are connected to said pressure medium circuit. In said embodiment, thenon-return valve 55 is advantageously arranged within thecontrol piston 37, and thus requires no additional installation space. A further advantage is that, specifically when using thecontrol valve 18 as a central valve, the path between the location at which the pressure pulsations are generated and thenon-return valve 55 is a minimum. Pressure fluctuations are intercepted practically at the point of generation. -
FIG. 5 illustrates a further embodiment of acontrol valve 18. The design and function of saidcontrol valve 18 are approximately identical to the variant shown inFIG. 4 . In this embodiment, thefilter 46 is advantageously arranged within thehousing 56 of thenon-return valve 55. Thehousing 56 can be embodied as a cost-effective plastic shaped part. By integrating thefilter 46 into thehousing 56 of thenon-return valve 55, the assembly outlay when assembling thecontrol valve 18 is reduced considerably. Only one component must now be positioned and fastened within thecontrol piston 37. - In this embodiment, that face end of the
control piston 37 which faces away from the tank port T2 is formed such that it is closed off. Thehousing 56 is H-shaped in longitudinal section, with thefilter 46 being arranged in one chamber of the H and the blockingbody 57 with thesecond spring element 58 being arranged in the other chamber. Thesecond spring element 58 is supported on aclosure 61. The radially running part of thehousing 56 is provided with an opening which is matched to the blockingbody 57 and serves as aseat 59. -
FIG. 6 shows a fourth variant of acontrol valve 18, in which acontrol piston 37 is arranged in an axially displaceable fashion within a substantially hollowcylindrical valve housing 34. Thecontrol 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 thecontrol piston 37 is provided with a firstannular groove 35 and a group offirst openings 36. - During operation of the internal combustion engine, pressure medium passes into the interior of the
valve housing 34 via the axially aligned pressure medium port P. Depending on the position of thecontrol piston 37 within thevalve housing 34, the pressure medium passes either viasecond openings 41 to the working port B or viathird openings 42 to the working port A. At the same time, the respective working port A, B which is not being acted on by pressure medium is connected via the firstannular groove 35 to the tank port T. - A
filter 46 is arranged between the pressure medium port P and the working ports A, B. Thefilter 46 is formed in the shape of a pot and comprises aframe 47 andfilter sections 48. At the side which faces toward the pressure port P, theframe 47 is provided with a radially extending collar which serves as an axial stop of thefilter 46. In addition, it is possible to fix thefilter 46 to thevalve housing 34 in a form-fitting, force-fitting or cohesive manner. As in the embodiments described previously, anon-return valve 55 can also be arranged between the pressure medium port P and the working ports A, B here. - A
control valve 70 according to the invention has acontrol piston 71 which is arranged in avalve housing 72 in an axially displaceable fashion. Thecontrol valve 70 and thecontrol piston 71 are, for example, formed corresponding to one of the exemplary embodiments illustrated in FIGS. 1 to 6. However, thebore 73 of thevalve housing 72 is formed according toFIG. 7 as a through bore of constant diameter, with end-side chamfers pressure spring 76, which substantially corresponds to thespring element 33 in the exemplary embodiments ofFIG. 1 toFIG. 6 , has afoot point 77, which is supported on an end side of thecontrol piston 71, and afoot point 78, which is supported on ahousing insert 79. Thehousing insert 79 is clipped into agroove 80 of the innerlateral surface 81 of thevalve housing 72. In the region of that end face of thecontrol piston 71 which bears against thefoot point 77, thecontrol piston 71 radially surrounds thepressure spring 76 by means of anannular shoulder 82, resulting, in some circumstances, in thepressure spring 76 being guided. In addition, astop 83, here having an annular stop face, projects from theannular shoulder 82 in the direction of thehousing insert 79, saidstop 83 coming into contact with thehousing insert 79 in the end position of thecontrol valve 70 as illustrated inFIG. 8 . -
FIG. 9 shows a front view of thehousing insert 79, whileFIG. 10 shows a longitudinal section of thehousing insert 79. Thehousing insert 79 is substantially of pot-shaped or hat-shaped form with -
- a
circular brim 84 having a radiallyouter edge 85 which is received in thegroove 80, - a
conical mid-region 86 and - an approximately circular
central region 87.
- a
- As illustrated in
FIG. 7 , thepressure spring 78 is held in themid-region 86, so that, in some circumstances, thehousing insert 79 can radially guide thepressure spring 76. According toFIG. 9 , three notches or recesses 88 extend radially inwards from theedge 85, said notches or recesses 88 -
- being approximately rectangular in the exemplary embodiment illustrated in
FIG. 9 , - ending approximately in the
central region 78 or the edge thereof and - being uniformly distributed about the circumference.
- being approximately rectangular in the exemplary embodiment illustrated in
-
Annular corners 89 or tapers are provided in the transition region between therecesses 88 and theedge 85, saidannular corners 89 or tapers, together with the rest of the design of thehousing insert 79, being intended to prevent thehousing insert 79 becoming jammed in the valve housing during assembly. Theconical mid-region 86 has anopening angle 90. For elastic radial compression of thehousing insert 79, theopening angle 90 is reduced and/or themid-region 86 is elastically deformed. During radial expansion for clipping thehousing insert 79 into thegroove 80, theopening angle 90 increases again. - The
housing insert 79 is preferably inserted into thevalve housing 72 using atool 91 according toFIG. 11 . Thetool 91 is rotationally symmetrical about the longitudinal axis 95-95. Thetool 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 openingangle 90 of thehousing 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. Accordingly, thehousing insert 79 can be inserted in the radially compressed state into the blind bore 92, with the outer diameter of thehousing insert 79 approximately corresponding to the diameter of thebore 73 or being less than said diameter. In said state, thehousing insert 79 can be inserted into thevalve housing 72 by means of thetool 91, as illustrated inFIG. 11 . Here, ashoulder 93 of thetool 91 can predefine how far thetool 91, with thehousing insert 79, can be pushed into thevalve housing 72. When thehousing insert 79 is approximately in the region of thegroove 80, thehousing insert 79 can be pushed out of or ejected from thetool 91. Here, an ejecting force can be exerted on thehousing insert 79 by means of an auxiliary device which is inserted into alongitudinal bore 94 which opens out into theblind bore 92. If the blind bore 92 is conical rather than cylindrical, the radial outer diameter of thehousing 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. Here, a suitable selection of the ratio between the flow cross sections at port B in thecontrol valve 70 and therecesses 88 is significant. If the outflow cross section, which is predefined by therecesses 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. - In an assembly process, the
housing insert 79 can be supplied continuously, for example by means of an oscillating conveyer. Through suitable selection of the geometry of the housing insert, of the sheet metal thickness, and by specifying the curvatures and theopening angle 90 as well as the material and suitable material treatment processes, the force required for deforming thehousing insert 79 and the securing effect which can be obtained by clipping thehousing insert 79 into thegroove 80 can be structurally predefined. The mechanical strength of thehousing insert 79 and/or the surface hardness, in particular in the support region of thepressure spring 76, is preferably increased by means of case-hardening and tempering. - 1 Device
- 2 Stator
- 3 Rotor
- 4 Drive wheel
- 5 Recesses
- 6 Side wall
- 7 First side cover
- 8 Second side cover
- 9 Connecting element
- 10 Vane groove
- 11 Vane
- 12 First pressure chamber
- 13 Second pressure chamber
- 14 Groove base
- 15 Leaf spring element
- 16 First pressure medium line
- 17 Second pressure medium line
- 18 Control valve
- 19 Pressure medium pump
- 20 Tank
- 21 Arrow
- 22 Central bore
- 23 Moldings
- 24 Locking element
- 25 Axial bore
- 26 Piston
- 27 Spring
- 28 Ventilation element
- 29 Slotted guide
- 30 Cut-out
- 31 Pressure medium circuit
- 32 Actuating element
- 33 First spring element
- 34 Valve housing
- 35 First annular groove
- 36 First openings
- 37 Control piston
- 37 a Wall section
- 38 Second annular groove
- 39 Third annular groove
- 40 Fourth annular groove
- 41 Second opening
- 42 Third opening
- 43 First control edge
- 44 Second control edge
- 45 Third control edge
- 46 Filter
- 47 Frame
- 48 Filter section
- 49 Segment
- 50 Longitudinal struts
- 51 Axial stop
- 52 Sleeve
- 53 Lateral surface
- 54 Gap
- 55 Non-return valve
- 56 Housing
- 57 Blocking body
- 58 Second spring element
- 59 Seat
- 60 Fourth opening
- 61 Closure
- 70 Control valve
- 71 Control piston
- 72 Valve housing
- 73 Bore
- 74 Chamfer
- 75 Chamfer
- 76 Pressure spring
- 77 Foot point, left
- 78 Foot point, right
- 79 Housing insert
- 80 Groove
- 81 Lateral surface
- 82 Annular insert
- 83 Stop
- 84 Brim
- 85 Edge
- 86 Mid-region
- 87 Central region
- 88 Recesses
- 89 Annular corner
- 90 Opening angle
- 91 Tool
- 92 Blind bore
- 93 Shoulder
- 94 Bore
- 95 Longitudinal axis
- P Pressure medium port
- T Tank port
- T1Radial tank port
- T2Axial tank port
- A First working port
- B Second working port
Claims (13)
1. Control valve for influencing the action of a pressure medium on a camshaft adjuster of an internal combustion engine, having
a valve housing (72),
a control piston (71) which is arranged in the valve housing (72) and is axially displaceable under the action of a spring element (pressure spring 76), and
a pressure medium port (P), a tank port (T) and two working ports (A, B),
wherein, for one axial position of the control piston (71), a first working port (A) can be connected to the or a tank port (T2), and the second working port (B) can be connected to the pressure medium port (P), while for another axial position of the control piston (71), the second working port (B) can be connected to the or a tank port (T1) and the first working port (A) can be connected to the pressure medium port (P), characterized in that the spring element (pressure spring 76) is supported, by means of the foot point (78) situated at the opposite side from the control piston (71), on a housing insert (79).
2. Control valve according to claim 1 , characterized in that the housing insert (79) has recesses (88), through which the pressure medium can pass out of the control valve (70) in order to form a port (T2).
3. Control valve according to claim 2 , characterized in that the recesses (88) extend inwards from an outer edge (85) of the housing insert (79).
4. Control valve according to one of the preceding claims, characterized in that the housing insert (79) is clipped into the valve housing (72).
5. Control valve according to claim 4 , characterized in that, in longitudinal section, the housing insert (79) is approximately in the form of the longitudinal section of a hat or of a pot, and the “brim” (84) of the hat or the edge (85) of the pot is clipped into a groove (80) of an inner lateral surface (81) of the valve housing (72).
6. Control valve according to claim 5 , characterized in that the mid-region (86) of the hat-shaped housing insert (79) is conical, said mid-region (86) adjoining the brim (84).
7. Control valve according to one of the preceding claims, characterized in that the diameter of a bore (73) for holding the housing insert (79) approximately corresponds to the diameter of the region for holding the control piston (71) in an axially displaceable fashion.
8. Control valve according to one of the preceding claims, characterized in that the housing insert (79) forms a stop (83) for the control piston (71), in order to predefine an axial end position of the control piston (71).
9. Control valve according to one of the preceding claims, characterized in that the control valve (70) is suitable for being integrated into a camshaft.
10. Method for producing a control valve for influencing the action on a camshaft adjuster of an internal combustion engine, in particular a control valve according to one of claims 1 to 9 , characterized by the following method steps:
a) forming a bore (73) in the valve housing (72), said bore (73) being at least of a length which permits it to hold both a control piston (71) and also a housing insert (79),
b) forming a groove (80) in the bore (73) of the valve housing (72),
c) radially compressing a housing insert (79),
d) inserting the housing insert (79), in the radially compressed state, into the bore (73) of the valve housing (72) and
e) radially expanding the housing insert (72) in such a way that the radially outer edge (85) of the housing insert (79) is received in the groove (80) of the valve housing (72).
11. Method according to claim 10 , characterized in that the bore (73) is formed in the valve housing (72) in the form of a through bore.
12. Method according to claim 10 or 11 , characterized in that a housing insert (79) is produced in the form of a “hat”, with a conical mid-region (86), and the housing insert (79) is radially elastically expanded and compressed by changing the opening angle (90) of the conical mid-region (86).
13. Method according to claim 12 , characterized in that, in order to insert the housing insert (79) into the valve housing (72), the housing insert (79) is held in a tool (91) such that the opening angle (90) of the conical mid-region (86) is reduced.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102005037480A DE102005037480A1 (en) | 2005-08-09 | 2005-08-09 | Control valve and method of making the same |
DE102005037480.8 | 2005-08-09 |
Publications (1)
Publication Number | Publication Date |
---|---|
US20070056540A1 true US20070056540A1 (en) | 2007-03-15 |
Family
ID=37478903
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US11/500,652 Abandoned US20070056540A1 (en) | 2005-08-09 | 2006-08-08 | Control valve and method for its production |
Country Status (4)
Country | Link |
---|---|
US (1) | US20070056540A1 (en) |
EP (1) | EP1752691B1 (en) |
JP (1) | JP2007046786A (en) |
DE (2) | DE102005037480A1 (en) |
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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 |
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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DE102005047641A1 (en) | 2005-10-05 | 2007-04-12 | Schaeffler Kg | Control valve for a camshaft adjuster |
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DE102008006179A1 (en) | 2008-01-26 | 2009-07-30 | Schaeffler Kg | Control valve for a device for the variable adjustment of the timing of gas exchange valves in internal combustion engines |
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US10280818B2 (en) | 2014-05-12 | 2019-05-07 | Volvo Truck Corporation | Fluid control valve |
JP6653631B2 (en) * | 2016-07-01 | 2020-02-26 | 日立オートモティブシステムズ株式会社 | Hydraulic control valve and valve timing control device for internal combustion engine |
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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 |
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US8893676B2 (en) * | 2009-07-04 | 2014-11-25 | Schaeffler Technologies AG & Co. KG | Central valve of a camshaft adjuster of an internal combustion engine |
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US8695548B2 (en) | 2010-12-10 | 2014-04-15 | Denso Corporation | Valve timing control apparatus |
US8662039B2 (en) * | 2011-03-16 | 2014-03-04 | Delphi Technologies, Inc. | Camshaft phaser with coaxial control valves |
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 |
---|---|
EP1752691B1 (en) | 2008-10-15 |
EP1752691A1 (en) | 2007-02-14 |
DE502006001806D1 (en) | 2008-11-27 |
JP2007046786A (en) | 2007-02-22 |
DE102005037480A1 (en) | 2007-02-15 |
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