EP1811139B1 - Rotor of a cam phaser - Google Patents

Abstract

The rotor has a rotor core (7), from which blades (5) leave. A locking pin (9) is guided into an interlocking opening (11), such that the pin is extendable from the rotor by a rotor surface. The opening is a sliding hole that passes through one of the blades of the rotor and is provided with two different cross sections. The opening supports a casing (21) in sections, where the casing is fixedly inserted in the opening below a surface (13) of the rotor. An independent claim is also included for a method for manufacturing a rotor of a camshaft adjuster.

Description

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.

Modern motor vehicles are nowadays usually equipped with one or more 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. For internal combustion engines, the opening and closing time of the gas exchange valves with respect to the crankshaft, usually hydraulically adjusted by means of the camshaft adjuster.

Particularly frequently represented are camshaft adjusters, which operate on a helical principle, and 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 assumed, for example, in a shutdown, particular load or start condition of the internal combustion engine must become.

Numerous interlocking mechanisms are known, which are often described as having the ability to extend a pin in the rotor so as to engage the rotatably loosely mounted second camshaft phaser component, the stator, with the rotor. During the engagement time, the hydraulic pressure in the hydraulic chambers forming between the rotor and the stator has no influence on the positional change of the rotor to the stator. Rotor and stator rotate almost synchronously in lock position during lock, driven by an external drive.

When the lock is retracted, that is, the state where the rotor and stator are freely movable at some angular relationship, a relative pressure difference between oppositely acting hydraulic chambers results in a relative rotation of the driven shaft relative to the driven shaft.

There are numerous considerations in the patent literature as to how to design a locking aperture and a suitable locking pin to ensure engagement between the rotor and stator under various operating conditions, such as hot running, idling, depressed, even at high displacement speeds. Above all, many designs have a particularly sophisticated design in mind, based on the respective rotor manufacturing technology, to enable, for example, noise behavior, fault tolerance or increased mobility. By way of example, the following publications may be mentioned for this purpose, DE 196 06 724 A1 the INA Rolling Bearings Schaeffler KG, the DE 196 23 818 A1 the Nippondenso Co, the DE 197 42 947 A1 the DENSO Corporation, the DE 100 38 082 A1 the DENSO Corporation, the DE 101 49 056 A1 the DENSO Corporation and the JP 2001050018 A the DENSO Corporation. In many documents locking openings are seen, which are designed as a blind hole. Hole hole formation is particularly well in the range of reference numerals 19 and 51 in the figures of FIGS US Pat. No. 5,960,757 the Nippondenso Co. ltd. to see.

For completeness reasons should still DE 101 48 687 A1 the Denso Corporation, the DE 100 39 921 A1 the Denso Corporation and the EP 1 762 706 A2 of Delphi Technology Incorporation.

It can be deduced that 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. As a result, it leads to the fact that the rotor component must be re-clamped several times, whereby both the processing effort increases, as well as the error rate is increased with each processing step. Furthermore, an increased cost of materials is given because, for example, after a certain number of holes of the drill must be replaced.

The use of a stepped bore, or possibly also a two-sided bore or suitable other mechanically abhebenendem manufacturing forms, for the installation of Sharing a locking module with locking pin can the German patent DE 10 2005 004 281 B3, filed on 28.01.2005 for the patent holder Hydraulik-Ring GmbH, from the FIG. 5 be removed. The associated patent family member US 2006 201 463 A1 indicates that all the dimensions described in more detail can be found in the front part of the pin and in the area of the pin receiving hole, in the stator but not in the guide hole area.

In the DE 102 13 831 A1 , also published as US 2002 139 332 A1 , Denso Corp., based on priorities from 2001 and 2002, presented numerous academic exercises on how to enable multiple pistons to lock a camshaft phaser of an uncontrolled shutdown internal combustion engine, preventing the onset of the camshaft from lagging the crankshaft should. This is the schematic example FIG. 9 a construction exercise whose practical feasibility in the automotive industry finds many difficulties. One of the pistons is arranged in the stator and therefore stationary. The rotor is partially spaced somewhat in the region of the sleeve of the piston even in the stop position.

Using a ring as an insert into the stator, prior to the priority date, May 16, 2003, of the U.S. application US 2004/0226527 A1 by Delphi Technologies Inc. often used in the art, as a centering aid is associated with a large game, so that the locking pin at higher angular velocities even has a catch probability. However, the ring does not lead the locking pin in the sense of the present invention, but has only slight locking tasks.

In the US 2001/054406 A1 (Applicant: Okada et al. ), in particular paragraph 36, it is described that for sliding guidance improvement of the pin a sliding sleeve can be pressed into the rotor.

It is advantageous to design a locking mechanism that can actually be produced as a part suitable for automotive use. Where's the problem is not lost from the eye, with as few and simply designed parts a lock, preferably in a rotor blade to make so that the locking mechanism is reliably easy to manufacture or manufacture.

The object of the invention is achieved by a rotor according to claim 1, claim 9 shows how a camshaft adjuster according to the invention is designed, and according to claim 10, a suitable manufacturing method is described.

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. In the unlocked state, 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. In order to increase the effect of the pivoting principle, 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. In some wings locking mechanisms are provided which may include a locking pin and a locking aperture and other components such as a spring. 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. 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. If the cross sections describe nearly circular openings, the average diameter can be determined. The diameters are different. It forms a stepped through hole. Here, 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. Optionally, 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. However, 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. On average, 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.

For the purposes of this invention 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.

In the locking opening a sleeve is introduced. 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. In a further 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. By the simple Design of the through hole of the locking hole and the simple design of the sleeve, the error rate is minimized, further contributing to the simple interference fit that dictates a simple, defined insertion depth.

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. In such a case, 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. According to one embodiment, the locking pin abuts with the sleeve against the sleeve. As a result, 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 Unterströmbereich 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.

In an alternative embodiment, 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.

If 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 according to the invention 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. The term stamp 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. During sintering, the locking opening is created at the same time. Thereafter, the sleeve, which can act, inter alia, as a bearing, flush pressed into the wing of the rotor so that a supply channel is formed beyond the sleeve, while on this side, within the sleeve, the running surface is created for the locking pin. From the other side, from the side from which the sleeve has not been inserted, the sleeves facing away from the side, the locking pin is introduced, which has a circumferential horizontal sleeve. The circumferential horizontal collar 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.

Between the sintering step and the pressing of 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.

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 which forms at least a partial, if not complete, closure of one side of the surface of the rotor so that the composite surface is made consists of two parts, a sintered rotor blade and an inserted, firmly connected to the rotor, spring plate.

• Figur 1 einen Nockenwellenversteller mit konventioneller Bearbeitungstechnik zeigt,
• Figur 2 einen Nockenwellenversteller nach Figur 1 aus einer gedrehten Perspektive darstellt,
• Figur 3 einen Rotor eines Nockenwellenverstellers aus einer Draufsicht darstellt,
• Figur 4 einen Schnitt durch einen Flügel eines Rotors nach Figur 3 darstellt,
• Figur 5 einen Rotor ähnlich zu Figur 3 mit einem erfindungsgemäßen Versorgungskanal darstellt,
• Figur 6 einen Schnitt durch einen Teil eines Flügels des Rotors nach Figur 5 darstellt,
• Figur 7 einen zu Figur 6 ähnlichen Schnitt durch einen Teil eines Flügels eines Rotors mit geänderten Dimensionen,
• Figur 8 eine Frontansicht eines Flügelteilschnittes eines Rotors nach Figur 5,
• Figur 9 eine weitere Ausführungsform eines erfindungsgemäßen Rotors, und
• Figur 10 einen Schnitt durch einen Flügel eines Rotors nach Figur 9 zeigt.

In den Figuren 11 bis 14 wird ein weiteres Ausführungsbeispiel offenbart.
Die Figuren 15 und 16 zeigen eine weitere Ausgestaltung einer erfindungsgemäßen Hülse.The invention can be understood even better by referring to the FIGS. 1 to 10 Reference is made to FIG

• FIG. 1 shows a camshaft adjuster with conventional machining technology,
• FIG. 2 a camshaft adjuster after FIG. 1 from a rotated perspective,
• FIG. 3 shows a rotor of a camshaft adjuster from a plan view,
• FIG. 4 a section through a wing of a rotor after FIG. 3 represents,
• FIG. 5 a rotor similar to FIG. 3 with a supply channel according to the invention,
• FIG. 6 a section through a part of a wing of the rotor after FIG. 5 represents,
• FIG. 7 one too FIG. 6 similar section through a part of a wing of a rotor with changed dimensions,
• FIG. 8 a front view of a wing section section of a rotor after FIG. 5 .
• FIG. 9 a further embodiment of a rotor according to the invention, and
• FIG. 10 a section through a wing of a rotor after FIG. 9 shows.

In the FIGS. 11 to 14 another embodiment is disclosed.
The FIGS. 15 and 16 show a further embodiment of a sleeve according to the invention.

An inventive manufacturing method is described in the FIGS. 17 and 18 shown graphically.
The FIG. 19 shows a pin module according to the invention, in which the sleeve can be pressed together with the locking pin and other components.

In the Figures 1 and 2 is an open camshaft adjuster 1 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. By the term "sideways" is meant the sides of the blade located at a nearly right angle to the rotor surface 13, which are often the shorter sides of the vanes. It is also conceivable, however, that several functional elements are united in one wing or that several wings also show a locking opening 11. 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. By pivoting the wings 5, 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. Laterally, to one of the pressure chambers 33, 34, performs a flow channel 29. The pressure chambers 33, 34 are filled with a hydraulic medium 31, such as engine oil.

The locking opening 11 in the Figures 1 and 2 is manufactured according to 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.

In FIG. 3 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. Around the rotor core 7 wings 5 are evenly distributed over its circumference. In the wing, which is provided laterally, angled from the rotor surface 13 without further contours, only by a vertical, smooth, shorter, almost quadrangular surface, 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 in more detail in FIG FIG. 4 shown. In 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.

As seen from the top view FIG. 3 is easily removed, 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 hydraulic fluid under the sleeve 10, so that the hydraulic medium drive the cuff and thus the resulting pen in the space of the wider diameter of the locking hole 11.

Another embodiment is in the FIGS. 5 to 8 to see. Similar parts as in the FIGS. 3 and 4 may be explained similarly for readability reasons, as already explained before. In a wing 5 of the protruding from the rotor core 7 bulge turn the locking hole 11 is provided with its locking pin 9. The locking opening 11 looks somewhat more complicated than the embodiment of the FIGS. 3 and 4 The production of the illustrated form is just as simple. 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 Unterströmbereich 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.
Like in the FIG. 7 can be seen, the pin 9 is spring biased by the spring 8.

In the embodiment according to FIG. 9 and FIG. 10 is a similar structure as in the FIGS. 5 to 8 shown, 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 hole 11, with hydraulic medium from one of Hydraulic rooms (see in the 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. In order to get under the cuff 10 with its underflow region 35, 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.

The embodiment of FIGS. 11 to 14 shows a rotor 3 according to the invention with five rotor blades 5 around a rotor core 7 around, in which a rotor blade 5, a locking pin 9 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. In the in FIG. 13 illustrated embodiment, the stop flange 23 narrows on the surface 13 of the rotor 3, the inflow passage 29 a little. The supply channel 27 then extends evenly into the underflow region 35. In the retracted position of the locking pin 9, 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.

In the FIGS. 15 and 16 an alternative embodiment is shown. In particular, 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. At the other end 22 of the sleeve 21, a flanging towards the outer wall 25 of the sleeve 21 is present. By notching in a circular portion of the sleeve 21, a connection between the supply channel 27 and the underflow region 35 of the locking pin 9 is provided. 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

In the FIGS. 17 and 18 is a Sinterherstellverfahren a manufacturing step of a rotor 3 of the invention FIGS. 1 to 14 in a rotor sinter 51 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. As a rule, approximately twice the volume V of the rotor 3 is filled with the metal powder 55. The metal powder 55 is as in FIG. 16 shown pressed. Afterwards, the sleeve 21 can be pressed in. When the locking pin 9 is inserted, the rotor 3 is finished after an optional grinding operation.

In FIG. 19 an embodiment example is disclosed, which can be used as a complete module 37 in the through hole 19 of the rotor 5 in a press fit. Starting from one of the two rotor surfaces 13, 14, similarly to the previously described examples, the supply channel 27 aligns with the horizontal center of the rotor 5. In the exemplary embodiment, 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. Thus, a wall, namely the outer wall of the sleeve 5, is bent. End of the supply channel 27, which does not go over the entire height H of the rotor 5, the sleeve is broken or interrupted to direct the hydraulic medium 31 in the Unterströmbereich 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 Unterströmbereich 35 of the locking pin 9 accessible.

Although only a few embodiments have been illustrated, it is to be understood that of course any combination of the sleeve 21 with any number of locking apertures 11 in a plurality of wings 5 can be selected, with some sleeves 21 may be equipped with and without stop flange 23. An advantage of the invention is that the sleeve 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. In this case, the sleeve does not extend completely from surface to surface of the rotor according to a preferred embodiment, but it ends below the surface.

LIST OF REFERENCE NUMBERS

1 Phaser 2 stator 3 rotor 4 web 5 wing 6 damping throttle 7 rotor core 8th feather 9 locking pin 10 Cuff of the locking pin, in particular horizontal sleeve 11 locking opening 12 shaft 13 rotor surface 14 remote surface 15 first cross section, preferably diameter 17 second cross section, preferably diameter 19 hole 21 shell 22 End of the sleeve 23 stop flange 25 Outer wall of the sleeve 27 supply channel 28 wall 29 inflow 31 hydraulic medium 33 Pressure chamber, first type 34 Pressure chamber, second type 35 Unterströmbereich 37 lock module 51 Rotor Interform 53 stamp 55 metal powder H height R of extension S, S ', S " layer V volume

Claims (12)

1. Rotor (3) of a camshaft adjuster (1), in particular according to the swivel motor principle, with a plurality of vanes (5) and a rotor core (7), from which the vanes (5) emanate, and a locking pin (9), which is guided in a locking opening (11) in such a manner that it can be retracted from the rotor (3) via the rotor surface (13),
   wherein the locking opening (11) is a stepped hole (19), which is provided with at least two different cross-section (15, 17), passes through a vane (5) of the rotor (3), and bears a sleeve (21),
   characterised in that
   the sleeve (21) forms a supply duct (27) by means of its outer wall (25) in that the sleeve (21) separates the supply duct (27) from a sliding face of the locking pin (9) by the formation of a separating wall in such a manner that the supply duct (27), which runs at least in sections parallel to the sleeve (21), is delimited by the outer wall (25) of the sleeve (21) and the walls (28) of the hole (19).
2. Rotor (3) according to Claim 1, characterised in that
   the locking opening (11) bears in sections a sleeve (21), which fits in a press fit, which is formed by a circular arc between the sleeve (21) and the wall (28) of the locking opening (11), and ends securely in the locking opening (11) below the surface (13) of the rotor (3), wherein the locking opening (11) is longer than the sleeve (21).
3. Rotor (3) according to one of the preceding claims, characterised in that the sleeve (21) is a circular sleeve (21), which is used as a sliding bearing for the retractable locking pin (9), wherein in particular a stop flange (23) at one end (22), preferably at the end which is closer to the surface (13) of the rotor, defines a maximum pressing-in depth of the sleeve (21).
4. Rotor (3) according to one of the preceding claims, characterised in that the sleeve (21) forms a supply duct (27) by means of its outer wall (25), together with a wall (28) of the supply duct (27) of the locking opening (11), which is formed by means of one of the two cross-sections (15, 17) of the locking opening (11), which supply duct (27) leads to a collar (10) of the locking pin (9).
5. Rotor (3) according to Claim 4, characterised in that the supply duct (27) is longer than the sleeve (21) but shorter than the locking opening (11), and the sleeve (21) preferably encloses the shaft (12) of the locking pin (9) completely in such a manner that the part of the shaft (12), which remains in the vane (5) is spanned by the sleeve (21) minus an underflow region (35) of the collar (10).
6. Rotor (3) according to Claim 4, characterised in that the supply duct (27) has a length up to the same length of the sleeve (21), wherein the sleeve (21) is provided with a notch or punched section at one or both ends in the region to the supply duct (27).
7. Rotor (3) according to Claim 4 or 5, characterised in that the supply duct (27) can be supplied with hydraulic medium (31) by an inflow duct (29), which is present on the surface (13), in particular on the end face, in particular from a pressure space (33) of the camshaft adjuster (1).
8. Rotor (3) according to one of the preceding claims, characterised in that the cross-sections (15, 17) occur in different layers (S) of the vane.
9. Rotor (3) according to one of the preceding claims, characterised in that the rotor (3) is a sintered component.
10. Camshaft adjuster (1) with a rotor (3) according to one of the preceding claims, wherein in particular a stator inner wall forms an inflow duct (29) from a pressure region to the supply duct.
11. Method of manufacturing a rotor (3) of a camshaft adjuster (1) according to one of Claims 1 to 9, comprising the following steps:

    - loading a rotor sinter mould (51) with a quantity of metal powder (55), which forms at least double the volume (V), in particular by a supplied volume (V) at the level (H) of the rotor (3),

    - pressing the metal powder (55), wherein the rotor sinter mould (51) comprises a stamp (53) with at least two different cross-sections (15, 17), preferably diameters, which stamp creates the locking opening (11),

    - sintering the pressed rotor mould,

    - flush pressing a sleeve (21), which functions as a bearing and forms a supply duct (27) in the rotor (3), and

    - inserting a locking pin (9), which is in particular provided with a spring (8) and has a circumferential horizontal collar (10), which is arranged in such a manner that it is angled towards the retraction direction (R) of the locking pin (9) from the surface (14) of he rotor (3), which faces away from the sleeve (21).
12. Method of manufacture according to Claim 11, characterised in that calibration and preferably grinding of the surfaces (13), in particular exclusively of the end faces, of the rotor (3) are carried out between the sintering step and the pressing of the sleeve (21).

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