EP1811139A1 - Rotor d'un dispositif de réglage d'arbre à cames - Google Patents

Rotor d'un dispositif de réglage d'arbre à cames Download PDF

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Publication number
EP1811139A1
EP1811139A1 EP07100664A EP07100664A EP1811139A1 EP 1811139 A1 EP1811139 A1 EP 1811139A1 EP 07100664 A EP07100664 A EP 07100664A EP 07100664 A EP07100664 A EP 07100664A EP 1811139 A1 EP1811139 A1 EP 1811139A1
Authority
EP
European Patent Office
Prior art keywords
rotor
sleeve
locking
supply channel
locking pin
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP07100664A
Other languages
German (de)
English (en)
Other versions
EP1811139B1 (fr
Inventor
Andreas Dipl.-Ing. Knecht (FH)
Dirk Dipl.-Ing. Pohl
Jan Dipl.-Ing. Eimert (FH)
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hilite Germany GmbH
Original Assignee
Hydraulik Ring GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
Priority to US11/655,767 priority Critical patent/US7497193B2/en
Publication of EP1811139A1 publication Critical patent/EP1811139A1/fr
Application granted granted Critical
Publication of EP1811139B1 publication Critical patent/EP1811139B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22F—WORKING METALLIC POWDER; MANUFACTURE OF ARTICLES FROM METALLIC POWDER; MAKING METALLIC POWDER; APPARATUS OR DEVICES SPECIALLY ADAPTED FOR METALLIC POWDER
    • B22F5/00—Manufacture of workpieces or articles from metallic powder characterised by the special shape of the product
    • B22F5/08—Manufacture of workpieces or articles from metallic powder characterised by the special shape of the product of toothed articles, e.g. gear wheels; of cam discs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22F—WORKING METALLIC POWDER; MANUFACTURE OF ARTICLES FROM METALLIC POWDER; MAKING METALLIC POWDER; APPARATUS OR DEVICES SPECIALLY ADAPTED FOR METALLIC POWDER
    • B22F3/00—Manufacture of workpieces or articles from metallic powder characterised by the manner of compacting or sintering; Apparatus specially adapted therefor ; Presses and furnaces
    • B22F3/24—After-treatment of workpieces or articles
    • B22F2003/247—Removing material: carving, cleaning, grinding, hobbing, honing, lapping, polishing, milling, shaving, skiving, turning the surface
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B22—CASTING; POWDER METALLURGY
    • B22F—WORKING METALLIC POWDER; MANUFACTURE OF ARTICLES FROM METALLIC POWDER; MAKING METALLIC POWDER; APPARATUS OR DEVICES SPECIALLY ADAPTED FOR METALLIC POWDER
    • B22F2998/00—Supplementary information concerning processes or compositions relating to powder metallurgy
    • B22F2998/10—Processes characterised by the sequence of their steps
    • 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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • 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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34456—Locking in only one position
    • 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
    • F01L2001/3445—Details relating to the hydraulic means for changing the angular relationship
    • F01L2001/34453—Locking means between driving and driven members
    • F01L2001/34469—Lock movement parallel to camshaft axis
    • 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
    • F01L2303/00—Manufacturing of components used in valve arrangements

Definitions

  • the invention relates to a locking opening of a rotor of a camshaft adjuster, in particular locking openings with locking pins in pivoting motor-like camshaft adjusters.
  • Camshaft adjusters are rotary transmission elements that can adjust the relative phase angle between a driving shaft and an aborted shaft to each other.
  • the opening and closing time of the gas exchange valves with respect to the crankshaft usually hydraulically adjusted by means of the camshaft adjuster.
  • camshaft adjusters which operate on a helical principle
  • camshaft adjusters which operate on a swivel motor principle. While the helical-pitched camshaft adjusters have some self-locking or self-warping due to helical gearing, the rotary engine operated camshaft phasers are so smooth that a separate locking mechanism is provided for a preferential position to be adopted, for example, in a shutdown, load or start condition of the internal combustion engine must become.
  • the rotor is first produced in a first manufacturing step to produce its outer dimensions by cutting from an extruded profile or by turning, and in a next step, a blind hole is drilled in the wing of the rotor.
  • a blind hole is drilled in the wing of the rotor.
  • the rotor of a camshaft adjuster is often in the interior of the stator, which forms a sealed chamber with corresponding covers, wherein the camshaft adjusters according to the swing motor principle, a space between the rotor and stator is given in order to create pressure chambers that are variable in size.
  • the rotor and the stator change their position when a hydraulic medium which can be introduced into the pressure chambers increases the pressure in certain pressure chambers, while a relatively lower pressure sets in the counteracting pressure chambers.
  • a plurality of vanes, for example 5 are typically designed, which are rotatably arranged between webs of the stator at a certain angle of rotation, such as 20 to 25 degrees.
  • wings locking mechanisms may include a locking pin and a locking aperture and other components such as a spring.
  • the locking pin Upon application of a corresponding pressure that can counteract a biasing force, the locking pin returns to its retracted, unlocked position.
  • the wings often go into a rotor core, which represents a circular structure and in which the aborted shaft, such as the camshaft, can intervene.
  • the locking pin When the rotor is arranged to the stator so that the rotor is in its rest position, the locking pin is extendable over the rotor surface.
  • the locking opening itself is a through hole, which is given by the length, preferably the height, continuously, completely, without interruption.
  • the through hole has at least two different cross sections.
  • the average diameter can be determined.
  • the diameters are different. It forms a stepped through hole.
  • the diameters can be chosen so that they can form partially superimposed circular disks or that one of the diameters can rise almost completely in the other diameter.
  • other diameters may be chosen, for example, a very small diameter of a semicircle, which may be considered as an extension of the largest diameter of the contiguous hole.
  • other forms such as ovals, shaped apertures and star shapes are sometimes advantageous, then a cross section is used. The description of the diameters is equivalent to the cross sections.
  • a favorable design of the through hole is given when the larger cross section results from the diameter of a circular hole plus the distance of a lateral bulge.
  • the lateral bulge extends to one embodiment only a few angular degrees, z. B. less than 15 ° or 20 °, the larger, circular hole.
  • the through hole in the area of the larger cross section looks like a mathematical fractal with two centers or a snowman consisting of two balls.
  • the diameter of the distance from a point on the wall to a next selected location is referred to as the diameter of the distance from a point on the wall to a next selected location, preferably exactly opposite. If the through-hole is characterized by two different diameters, it means that in the section of the second diameter two points can be found on the wall of the through-hole which have a different distance than all the distance measurements in the part of the through-hole of the first section.
  • a sleeve is introduced in the locking opening.
  • the sleeve is in a press fit.
  • the press fit is formed between the sleeve wall, preferably outer wall, and the surface wall of the locking opening in a circular arc section.
  • the sleeve is in a cantilevered state, so that the sleeve serves as a partition.
  • the sleeve is completely inserted into the rotor. It ends below the surface, alternatively at the surface, of the rotor, the sleeve not being completely continuous through the height of the rotor.
  • the sleeve itself is a simple circular object, without numerous gradations, so stepless.
  • the circular sleeve serves as a sliding bearing for the extendable locking pin. It is provided with a smooth surface, so that the locking pin can easily extend and retract in the plain bearing. A misjudgment is thus prevented.
  • the insertion of the sleeve in its press fit can be further facilitated by the fact that a stop flange at one end, preferably at the end closer to the surface of the rotor, is present, so that a maximum offset is predetermined.
  • the locking opening can advantageously be designed as a two-stage through-opening. The first stage is very close to the surface, it lies as far inside the wing of the rotor as the thickness of the stop flange is. The next stage lies so far inside the sash that the pressed-in sleeve, which terminates with the surface, does not reach the step.
  • the sleeve in the rotor with its non-press fit portion forms a partition which separates a supply channel from the sliding surface of the lock pin.
  • the supply channel leads to a collar of the locking pin.
  • the locking pin abuts with the sleeve against the sleeve.
  • the sleeve takes over several functions, a channel-forming function, a sliding function and one or more stop functions.
  • the term cuff is understood in the present invention description in the sense that it is referred to a hydraulically suppressible bow, which forms, for example, in the transition of a groove to the head of the locking pin.
  • the groove is designed as a hydraulic medium receiving space into which the hydraulic medium flows in order to lift the locking pin out of the locking opening by means of pressure.
  • the collar is the area of the pin which may be arcuate, under which the oil may engage under the hydraulic medium present in the groove.
  • the supply channel is longer than the sleeve. However, the supply channel is not completely continuous through the wing. It ends in a middle zone, inside the wing.
  • the supply channel can advantageously be represented by the second, shorter diameter.
  • the sleeve has the length that it can preferably completely enclose the shaft of the locking pin when the shaft in its extended position partially protrudes from the wing.
  • the sleeve is to be considered in this state as a support sleeve.
  • the sleeve has the length that a Unterström Stud the cuff can remain.
  • the supply channel communicatively communicates with a flow channel in relation to a hydraulic medium, which in turn can be supplied from a pressure space between the rotor and the stator of the camshaft adjuster. The described design contributes to the security of supply of the locking pin.
  • a nearly square notch is notched out of the sleeve, which serves as an opening of the hydraulic medium from the supply channel to the underflow region of the pin.
  • the supply channel has a length. The length may be shorter than the length of the sleeve. But it can also have about the length of the sleeve. The length is thus shorter or has the same length as the length of the sleeve, wherein the sleeve is provided with a notch or stamping at one of the two ends in the region to the supply channel.
  • the rotor blade is disassembled into individual layers, it can be seen that the different diameters are given in different layers of the wing. Beginning from one side of the rotor, all the diameters can be found there first, with a continuous direction on the opposite side of the rotor, individual diameters are no longer to be found as openings. For the particular manufacturability of the rotor, it is beneficial if the rotor is a sintered component.
  • Rotor and stator together with other components form a camshaft adjuster.
  • the rotor which can be designed as a sintered part, is smooth and at the same time fixed to the output in the stator of the camshaft adjuster, the for the locking pin, which runs smoothly in the sleeve, a receiving hole offers.
  • a suitable manufacturing method of a rotor of a camshaft adjuster is that first a rotor sintered mold is loaded with approximately twice to three times, preferably 2.5 times, the amount of metal powder, especially in the direction of the height of the rotor.
  • the height of the rotor is the short side of the rotor.
  • the metal powder is sintered, wherein the rotor sintered form comprises a punch having at least two different diameters.
  • the stamp creates the locking opening.
  • punch also includes a split punch, the first part of which creates the locking opening and the second part of which creates the bulge for the supply channel.
  • Another stamp form consists of a contour, through which both longitudinal opening forms can be created simultaneously, within one working process.
  • the locking opening is created at the same time.
  • the sleeve which can act, inter alia, as a bearing, flush pressed into the wing of the rotor, so that beyond the sleeve, a supply channel is formed, while this side, within the sleeve, the running surface is created for the locking pin.
  • the locking pin is introduced, which has a circumferential horizontal sleeve.
  • the circumferential horizontal sleeve is angled to the direction of movement, the extension direction, the locking pin.
  • the horizontal sleeve is located in the portion facing away from the sleeve.
  • a calibration and preferably a grinding of the surfaces, in particular excluding the end faces, of the rotor can be performed. If the surface is not very sharply outlined by the sintered form, the calibration and, if necessary, the surface treatment by an ablation process will help significantly to ensure dimensional stability.
  • An advantage of the described method is that the rotor including its opening for receiving locking elements in a single Step comprehensive shaping manufacturing process is created, wherein the surface of the rotor including its indentations and recesses during the pressing process is created simultaneously, contiguous. Subsequent drilling, which removes material-removing parts of the rotor, is unnecessary by the outer contour and inner contour of the rotor. It forms a closed surface of the rotor, which extend from the end faces of the rotor via the locking opening to the transverse surfaces of the rotor formed as a closed path.
  • a locking pin When the finished locking element, a locking pin, is installed, according to one embodiment, it may be supported on a spring plate via a spring element that forms at least a partial, if not complete, closure of one side of the surface of the rotor, such that the composite surface is made consists of two parts, a sintered rotor blade and an inserted, firmly connected to the rotor, spring plate.
  • FIGS. 17 and 18 An inventive manufacturing method is shown in FIGS. 17 and 18 graphically.
  • FIG. 19 shows a pin module according to the invention, in which the sleeve can be pressed in together with the locking pin and further components.
  • an open camshaft adjuster 1 is shown with a rotor 3 and a stator 2, which operates on the principle of a hydraulic swing motor.
  • the rotor 3 has a rotor core 7 and a certain number, five in the present example, wings 5, which may be designed to be partially identical to each other.
  • Some vanes 5 still have additional functional elements, such as attenuators, hammer shapes, pressure equalization channels, underflow channels, or increased seal lengths.
  • One of the illustrated wings 5 is equipped with the additional functional element locking opening 11. Shown is the rotor 3 with a wing without lateral damping throttle 6, which has the locking opening 11, and four wings 5, the lateral damping chokes 6 have.
  • the wings 5 separate different pressure chambers 33, 34, which are formed on each shorter side of the wing 5 and form between pivoting wings 5 and webs 4.
  • the pressure chambers 33, 34 which are provided as oppositely designed, oppositely acting chambers, changed their width. The change in width is accompanied by a change in volume of the pressure chambers 33, 34.
  • the pressure chambers 33, 34 are filled with a hydraulic medium 31, such as engine oil.
  • the locking opening 11 in Figures 1 and 2 is made by a conventional drilling method.
  • the result of the manufacturing process by means of double drilling with different drill sizes or stepped drilling by a single step drill shows a locking opening 11, in which a sleeve 21, preferably by a press fit, can be used.
  • the openings with different Diameters ends with a different diameter on one side of the blade 5, the rotor surface 13, than on the other, opposite side 14 of the same wing 5.
  • the locking hole 11 is located approximately centrally on the rotor surface 13 of the one wing 5, which is the broad side of the Rotor 3 represents. The largest part of the wing width is taken out of the wing 5 through the hole.
  • the different diameters are substantially coaxial parallel to the camshaft axis.
  • the sleeve 21 has a stop flange 23.
  • the locking hole 11 is continuous with the height H of the rotor 3 which is the shorter height.
  • the locking opening 11 is stepped.
  • the step is the result of a stepped drilling.
  • the stop flange 23 of the sleeve 21 rests on the step.
  • From the side which is the height side of the rotor 3, has a supply channel 27 from a pressure chamber 33 in the locking opening 11.
  • the supply channel 27 is located at approximately half the height of the rotor 3.
  • the supply channel 27 opens at the stage of the locking opening eleventh
  • the locking opening 11 is a circular through hole.
  • the sleeve 21 has such an outer diameter which is larger than the bore diameter of the smaller opening diameter portion.
  • the sleeve 21 is press fit in the smaller diameter opening portion.
  • the stop flange rests on the shoulder that forms between the two consecutive diameters.
  • the rotor 3 is shown without its stator 2 in a front view, which shows one of the large-area rotor surfaces 13 to the viewer.
  • wings 5 are evenly distributed over its circumference.
  • the continuous locking opening 11 is arranged with its locking pin 9 extending from a rotor surface 13 on the opposite rotor surface 13 extends.
  • the pin 9 runs in the sleeve 21st
  • the locking opening 11 is shown in greater detail in FIG.
  • the locking opening 11 of the locking pin 9 which includes a sleeve 10 and a shaft 12, slidably mounted.
  • the locking pin 9 is inserted into the through hole 19, the two different diameter 15, 17th
  • the cuff 10 has a larger diameter than the shaft 12.
  • Cuff 10 and shaft 12 lie one above the other in the same alignment on the same axis, they are coaxial, integrally formed.
  • the locking opening 11 runs from the one side of the rotor surface starting with a cross-section that is large enough to guide the shaft, up to about the height of the wing, in which a lateral inflow channel 29 opens
  • the taper can be created by a round, rotationally balanced sleeve spanning the entire circumference, forming a stepped locking opening through the sleeve, the cross-sections of which are narrowed along the height H to the shaft cross-section
  • the pin 11 moves in the extension direction R.
  • the sleeve 21 has a smaller diameter than the widest point of the locking hole 11 and a larger inner diameter than the outer diameter of the shaft 12 of the locking pin 9.
  • the reaching under the sleeve 10 inflow channel 29 passes under hydraulic fluid the cuff 10 to allow the hydraulic fluid to drive the cuff, and hence the resulting pin, into the wider diameter space of the locking aperture 11.
  • FIGS. 3 and 4 Another embodiment can be seen in Figures 5 to 8. Similar parts as in FIGS. 3 and 4 may be explained similarly for readability reasons, as already explained above.
  • the locking opening 11 looks somewhat more complicated overall than the embodiment of Figures 3 and 4, wherein the production of the illustrated shape is performed just as easily.
  • the basic shape of the locking opening 11 is a circular hole with a lateral, z. B. aligned on the wing outside or on the wings far side, recess, which is preferably also present over the entire rotor height.
  • the opening looks like a fractal with two centers from the front.
  • the sleeve 21 is inserted in the opening.
  • the sleeve 21 forms an inner, for the shaft 12 of the Locking pin 9 formed, plain bearing area and an outer region, which is equipped as a supply channel 27 with a significantly smaller diameter than that of the locking pin 9.
  • the supply channel 27 opens approximately centrally in the wing 5 in the Unterström Society 35 of the locking pin 9.
  • the underflow region 35 is at least partially formed circumferentially around the substantially round pin by a penetration depth before the cuff 10 of the locking pin 9 comes.
  • the cuff 10 which is a horizontal stop cuff, delimits the hydraulic medium of the supply channel and the underflow region 35 against the pressure side facing the locking pin 9.
  • the sleeve 21 is seated in a partially contacting interference fit in the opening of the rotor 3, the cantilever portion of which is at the same time a part of the supply channel 27. Further parts of the Versorungskanals 27 are formed by the wall 28, formed from the wing 5.
  • the sleeve 21 thus assumes two functions, the slide bearing and the oil guide. As can be seen in Figure 7, the pin 9 is spring-biased by the spring 8.
  • Figure 9 and Figure 10 is a similar construction as shown in Figures 5 to 8, wherein the elongated in the height of the rotor 3 extending supply channel 27 is supplemented by a lateral, out of the wing 5, inflow channel 29, the supply of the locking pin 9, which runs in sections in the locking opening 11, with hydraulic medium from one of the hydraulic chambers (see in Figures 1 and 2, the reference numerals 33, 34) between the wings 5 of the rotor 3 allows.
  • the Anströmkanal 29 is a parallel limited, designed on the shortest path, flat rectangular channel, which finds its completion on the sleeve 21 and one of the ends 22 of the sleeve 21.
  • the hydraulic medium passes through different flow areas whose flow directions are deflected several times in comparison to the wing 5 of the rotor 3.
  • the baffles contribute to pressure propagation during pressure changes with hydraulic fluid almost at rest.
  • a wing 5 described in this way hangs one or more times on the rotor core 7.
  • the shaft 12 of the pin is slidably mounted on the inside of the sleeve.
  • FIGS. 11 to 14 shows a rotor 3 according to the invention with five rotor blades 5 around a rotor core 7, in whose one rotor blade 5 a locking pin 9 is inserted in a sleeve 21.
  • the sleeve 21 is limited in its insertion depth by a stop flange 23 so that the sleeve 21 with its stop flange 23 surface-locked with the rotor surface 13.
  • the stop flange 23 is formed at the one end 22 of the sleeve 21.
  • the opposite surface 14, the opposite surface 14, of the rotor 3 shows only one locking opening 11.
  • the circular sleeve 21 has a likewise circular Anschlagungsflansch 23, but also in an alternative embodiment may be present only in a circular arc.
  • the stop flange 23 on the surface 13 of the rotor 3 narrows the inflow channel 29 slightly.
  • the supply channel 27 then extends evenly into the underflow region 35.
  • the underflow region 35 can be underflowed.
  • a partial section of the outer wall 25 of the sleeve 21 simultaneously forms a region of the inner wall of the supply channel 27.
  • FIGS. 15 and 16 show an alternative embodiment.
  • the supply channel 27 with the sleeve 21 is slightly different in its length than in the embodiments previously.
  • the sleeve 21 has a notch endlings.
  • a flanging towards the outer wall 25 of the sleeve 21 is present.
  • the supply channel is shorter or the same length as the sleeve. This arrangement has the advantage that manufacturing tolerances can be more easily absorbed. However, care must be taken that the sleeve is always properly inserted in the sense of their orientation in the locking hole 11.
  • the entire assembly is, as in the similar embodiments, at a suitable location of the wings. 5
  • FIGS. 17 and 18 a sintering manufacturing method of a manufacturing step of a rotor 3 according to the invention of FIGS. 1 to 14 in a rotor sinter 51 is shown represented with locking opening 11 for later insertion of a sleeve 21.
  • the rotor sinter 51 has at least two punches 53, the larger punches of which lie in the center of the rotor sinter 51. It forms the axle connection of the camshaft adjuster to the camshaft. Laterally, a punch 53 pierces the rotor 3, which can either be equipped with a thickening for the supply channel or offers a further partial punch.
  • the metal powder 55 is compacted after loading the rotor sinter 51.
  • FIG. 19 discloses a design example which can be inserted as a complete module 37 into the through hole 19 of the rotor 5 in an interference fit.
  • the supply channel 27 aligns with the horizontal center of the rotor 5.
  • the supply channel 27 is arranged at a virtually or actual right angle to the surface 13.
  • the supply channel 27 is formed as at least partially completely enclosed and closed channel whose walls are made up of a longitudinal region of the sleeve 5, which preferably only a small circle segment of the sleeve 21 and covers, and from inner walls of the rotor 5 of the through hole 19.
  • a wall, namely the outer wall of the sleeve 5 is bent.
  • the sleeve is broken or interrupted to direct the hydraulic medium 31 in the Unterström Scheme of the locking pin 9, in particular in the area below its sleeve 10.
  • the sleeve 5 extends according to an advantageous embodiment not over the entire height H, but the ends 22 terminate at least on one side below the corresponding surface 13 or 14.
  • the supply channel 27 is from the outside, the outer wall 25, the sleeve 21 and the Walls 28 of the hole 19 limited.
  • the supply channel 27 runs parallel to the sleeve 5.
  • the wider diameter of the through hole 19 ends, as in previously discussed examples, in the area, in particular below the maximum extension position of Cuff 10 of the locking pin 9 to make the Unterström Scheme 35 of the locking pin 9 accessible.
  • the sleeve 21 is repeatedly used functionally as a simple molded part can be easily inserted into the rotor in order to develop a locking hole and at the same time to guide the locking pin.
  • the rotor can be produced as a sintered part, whereby the post-processing steps can be reduced to a minimum. For example, hardly any drilling with their clamping operations are necessary.
  • the sleeve 21 is not only a filling member but the sleeve 21 is a guide member for the lock pin 9, and the sleeve 21 is a functional member for forming the supply passage 27 of the rotor 5.
  • the present invention relates to a novel rotor and a corresponding manufacturing method for a rotor according to the invention, in which a sleeve takes over as a structural component oil guiding functions in addition to locking pin bearing functions, wherein the sleeve is flush-mounted in a wing of the rotor by means of press fit.
  • the sleeve does not extend completely from surface to surface of the rotor according to a preferred embodiment, but it ends below the surface.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP07100664A 2006-01-18 2007-01-17 Rotor d'un dispositif de réglage d'arbre à cames Not-in-force EP1811139B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US11/655,767 US7497193B2 (en) 2006-01-18 2007-01-18 Rotor of a camshaft adjuster

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006002599 2006-01-18
DE102006019435A DE102006019435B4 (de) 2006-01-18 2006-04-24 Rotor eines Nockenwellenverstellers

Publications (2)

Publication Number Publication Date
EP1811139A1 true EP1811139A1 (fr) 2007-07-25
EP1811139B1 EP1811139B1 (fr) 2008-10-08

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EP07100664A Not-in-force EP1811139B1 (fr) 2006-01-18 2007-01-17 Rotor d'un dispositif de réglage d'arbre à cames

Country Status (4)

Country Link
EP (1) EP1811139B1 (fr)
AT (1) ATE410587T1 (fr)
DE (2) DE102006019435B4 (fr)
ES (1) ES2314959T3 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102705029A (zh) * 2012-05-30 2012-10-03 绵阳富临精工机械股份有限公司 一种低泄漏高寿命凸轮相位器
WO2015070846A1 (fr) * 2013-11-15 2015-05-21 Schaeffler Technologies AG & Co. KG Dispositif de réglage d'arbre à cames
WO2016030206A1 (fr) * 2014-08-28 2016-03-03 Robert Bosch Automotive Steering Gmbh Procédé de production de composants d'un moteur pivotant pour système de direction

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008050112B4 (de) 2008-10-06 2010-07-15 Hydraulik-Ring Gmbh Verfahren zur Herstellung eines Flügelzellennockenwellenverstellers mit einem Blechdeckel
DE102008058110B4 (de) 2008-11-18 2014-08-21 Hilite Germany Gmbh Nockenwellenversteller
DE102016123580B4 (de) * 2016-12-06 2021-09-09 Gkn Sinter Metals Engineering Gmbh Rotorteil eines Rotors für einen Nockenwellenversteller und Presswerkzeug zu dessen pulvermetallurgischer Herstellung

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US5960757A (en) * 1995-06-14 1999-10-05 Nippondenso Co., Ltd. Controlling apparatus for varying a rotational or angular phase between two rotational shafts
DE19916644A1 (de) * 1999-04-14 2000-10-19 Schaeffler Waelzlager Ohg Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber der Kurbelwelle einer Hubkolben-Brennkraftmaschine
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DE10039921A1 (de) * 1999-08-17 2001-04-05 Denso Corp Variables Ventileinstell-Regelsystem für eine Brennkraftmaschine
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DE102005004281B3 (de) * 2005-01-28 2006-01-05 Hydraulik-Ring Gmbh Nockenwellenversteller mit spielfreier Verriegelung

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DE19606724A1 (de) * 1996-02-23 1997-08-28 Schaeffler Waelzlager Kg Vorrichtung zum Verändern der Öffnungs- und Schließzeiten von Gaswechselventilen einer Brennkraftmaschine
JP3262207B2 (ja) * 1996-10-02 2002-03-04 株式会社デンソー 内燃機関用バルブタイミング調整装置
JP4058580B2 (ja) * 1999-08-06 2008-03-12 株式会社デンソー バルブタイミング調整装置
JP4257477B2 (ja) * 2000-06-23 2009-04-22 株式会社デンソー バルブタイミング調整装置
JP4507151B2 (ja) * 2000-10-06 2010-07-21 株式会社デンソー バルブタイミング調整装置
DE10213831A1 (de) * 2001-03-28 2002-11-07 Denso Corp Variables Ventilsteuerzeitengerät
US6883478B2 (en) * 2003-05-16 2005-04-26 Delphi Technologies Inc. Fast-acting lock pin assembly for a vane-type cam phaser
US7421989B2 (en) * 2005-09-13 2008-09-09 Delphi Technologies, Inc. Vane-type cam phaser having increased rotational authority, intermediate position locking, and dedicated oil supply

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Publication number Priority date Publication date Assignee Title
US4127684A (en) * 1977-12-23 1978-11-28 Ford Motor Company Crack protection method
US5960757A (en) * 1995-06-14 1999-10-05 Nippondenso Co., Ltd. Controlling apparatus for varying a rotational or angular phase between two rotational shafts
DE19916644A1 (de) * 1999-04-14 2000-10-19 Schaeffler Waelzlager Ohg Vorrichtung zur Drehwinkelverstellung einer Nockenwelle gegenüber der Kurbelwelle einer Hubkolben-Brennkraftmaschine
DE10038082A1 (de) * 1999-08-06 2001-03-29 Denso Corp Ventilsteuerzeiteneinstellgerät
DE10039921A1 (de) * 1999-08-17 2001-04-05 Denso Corp Variables Ventileinstell-Regelsystem für eine Brennkraftmaschine
DE10148687A1 (de) * 2000-10-04 2002-06-27 Denso Corp Verfahren zur Herstellung einer Ventileinstellungsanpassvorrichtung
DE10227140A1 (de) * 2001-06-18 2003-03-13 Aisin Seiki Gleitmechanismus und Ventilmechanismus mit variabler Zeitgebung für eine Verbrennungskraftmaschine
DE102005004281B3 (de) * 2005-01-28 2006-01-05 Hydraulik-Ring Gmbh Nockenwellenversteller mit spielfreier Verriegelung

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102705029A (zh) * 2012-05-30 2012-10-03 绵阳富临精工机械股份有限公司 一种低泄漏高寿命凸轮相位器
CN102705029B (zh) * 2012-05-30 2014-12-10 绵阳富临精工机械股份有限公司 一种凸轮相位器
WO2015070846A1 (fr) * 2013-11-15 2015-05-21 Schaeffler Technologies AG & Co. KG Dispositif de réglage d'arbre à cames
CN105723056A (zh) * 2013-11-15 2016-06-29 舍弗勒技术股份两合公司 凸轮轴调节装置
WO2016030206A1 (fr) * 2014-08-28 2016-03-03 Robert Bosch Automotive Steering Gmbh Procédé de production de composants d'un moteur pivotant pour système de direction

Also Published As

Publication number Publication date
EP1811139B1 (fr) 2008-10-08
DE502007000144D1 (de) 2008-11-20
ATE410587T1 (de) 2008-10-15
ES2314959T3 (es) 2009-03-16
DE102006019435B4 (de) 2010-06-02
DE102006019435A1 (de) 2007-07-19

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