Anti-twist protection for the inner part of a split rotor for a hydraulic camshaft adjuster

Abstract

A multi-part rotor (1) for a hydraulic camshaft adjuster, including two partial rotor members (2) which rest against each other along a separation plane (3) extending perpendicular to the axial direction and which jointly define hydraulic medium ducts (4) extending within said separation plane (3) and, including an additional rotor member (5) that conducts hydraulic medium from opposite axial directions in a targeted manner to different hydraulic medium ducts (4). The additional rotor member (5) or at least one positively engaging anti-twist element (6) is secured to one or both partial rotor members (2) for conjoint rotation therewith.

Claims

1. A multipart rotor for a hydraulic camshaft adjuster, the rotor comprising: two rotor partial bodies resting against one another on a separating plane oriented perpendicularly with respect to the axial direction, and the two rotor partial bodies together defining hydraulic medium-conducting channels extending in the separating plane; and a rotor additional body conducting hydraulic medium in a targeted manner from opposite axial directions to different ones of the hydraulic medium-conducting channels; the rotor additional body or at least one anti-twist element acting in a form-fit manner being secured in a rotatably fixed manner to one or both rotor partial bodies.

2. The rotor as recited in claim 1 further comprising the anti-twist element, the anti-twist element being designed as an integral projection or recess at an outer circumferential surface of the rotor additional body cooperating in a form-fit manner with an anti-twist counterelement of one or both rotor partial bodies having a corresponding geometric design.

3. The rotor as recited in claim 1 wherein the rotor additional body has, or the two rotor partial bodies have, a ring-like design.

4. The rotor as recited in claim 1 wherein the two rotor partial bodies are fitted together congruently in the axial direction, and the rotor additional body is situated concentrically and radially within the two rotor partial bodies.

5. The rotor as recited in claim 1 wherein the rotor additional body includes oil-conducting pockets at an outer circumference, the pockets having a design open in alternation over the outer circumference, facing in different axial directions.

6. The rotor as recited in claim 1 wherein one of the rotor partial bodies includes at least one oil-conducting counterpocket, in the form of a depression, the counterpocket being at an inner circumferential surface and leading to a hydraulic medium-conducting channel.

7. The rotor as recited in claim 6 wherein both rotor partial bodies include one of the at least one oil-conducting counterpocket oriented in different or opposite axial directions away from the hydraulic medium-conducting channel.

8. The rotor as recited in claim 6 wherein the oil-conducting counterpocket extends beyond an axial edge of the rotor additional body.

9. The rotor as recited in claim 6 wherein the oil-conducting counterpocket extends by approximately 10% to 100% or more of the distance from an edge of a hydraulic medium-conducting channel remote from the separating plane to a front edge of the rotor additional body present on this side of the separating plane, in the direction of the front side of one of the rotor partial bodies present on this side of the separating plane.

10. The rotor as recited in claim 6 wherein the oil-conducting counterpocket extends to a front side of the rotor partial body remote from the separating plane, the oil-conducting counterpocket being formed at the separating plane.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The present invention is explained in greater detail below with the aid of the drawings, which illustrate various exemplary embodiments.

(2) FIG. 1 shows an exploded view of a first specific embodiment according to the present invention;

(3) FIG. 2 shows a perspective view of one of the two rotor partial bodies of the rotor configuration from FIG. 1, with a rotor additional body, the rotor additional body configuration designed as an oil distribution sleeve being inserted with an angled orientation into one of the two rotor halves/rotor partial bodies;

(4) FIG. 3 shows a side view of the metallic rotor configuration from FIG. 1, also connected using spring suspension pins;

(5) FIG. 4 shows a section along line IV from FIG. 3;

(6) FIG. 5 shows an enlargement of area V from FIG. 4,

(7) FIG. 6 shows a perspective view only of the oil distribution sleeve/the rotor secondary body, with an anti-twist element at the outer diameter, multiple anti-twist elements being usable at regular intervals;

(8) FIG. 7 shows a rotor partial body/a rotor half with a recess for accommodating the anti-twist element of the oil distribution sleeve, and with four axial oil-conducting counterpockets which cooperate with oil-conducting pockets of the oil distribution sleeve and ensure an oil supply to the rotor;

(9) FIG. 8 shows a perspective view (three-dimensional view) of the rotor from FIG. 1, with 2×4 axial pockets/oil-conducting counterpockets which are used for supplying oil to working chambers A and B in a camshaft adjuster;

(10) FIG. 9 shows an enlargement of area IX from FIG. 8;

(11) FIG. 10 shows a perspective view of the rotor from FIG. 1 in cross section, with 2×4 oil-conducting counterpockets for supplying oil to working chambers A and B in the camshaft adjuster, which extend approximately beyond an edge of the rotor additional body/the oil distribution sleeve in the axial direction;

(12) FIG. 11 shows an enlargement of area XI from FIG. 10;

(13) FIG. 12 shows another specific embodiment comparable to the specific embodiment illustrated in FIG. 10, but with oil-conducting counterpockets extending further in the axial direction, namely, to the free end face of the rotor partial body;

(14) FIG. 13 shows an enlargement of area XIII from FIG. 12;

(15) FIGS. 14 and 15 show one specific embodiment in an exploded view, from the side of the camshaft and from the side facing away from the camshaft, respectively; and

(16) FIGS. 16 and 17 show assembled perspective depictions according to the exploded view from FIGS. 14 and 15.

DETAILED DESCRIPTION

(17) The figures are merely schematic, and are used only for an understanding of the present invention. Identical elements are provided with the same reference numerals. Elements of the individual exemplary embodiments may be interchanged with one another.

(18) FIG. 1 illustrates a multipart rotor 1 as used for a hydraulic camshaft adjuster. Rotor 1 is a first exemplary embodiment, and includes two rotor partial bodies 2 which abut one another at a separating plane 3, clearly apparent in FIG. 3, and which together define hydraulic medium-conducting channels 4. Hydraulic medium-conducting channels 4 are present in separating plane 3. Separating plane 3 is oriented perpendicularly with respect to the axial direction of rotor 1. Rotor partial bodies 2 may also be referred to as rotor halves. One rotor half is then used as the rotor main body, and the other rotor half is used as the first rotor secondary body.

(19) Hydraulic medium-conducting channels 4 may also be referred to as oil channels when oil is used as hydraulic medium, as is usually the case. One hydraulic medium-conducting channel 4 then supplies a working chamber A, while the other hydraulic medium-conducting channel 4 supplies working chamber B. Eight hydraulic medium-conducting channels 4 are present, four of which supply a working chamber A and four of which supply a working chamber B. Every two working chambers, namely, a working chamber A and a working chamber B in each case, are part of a vane cell, which is divided by a radially inwardly protruding projection of a stator, not illustrated here.

(20) A rotor additional body 5 is inserted in the area of separating plane 3, in contact with both rotor partial bodies 2. Rotor additional body 5 may also be referred to as an oil distributor sleeve or oil distribution sleeve. It is preferably not inserted into rotor partial bodies 2 in a floating manner, although this is possible, but, rather, is held in a rotatably fixed manner on one or both rotor partial bodies 2 via a form-fit connection. The anti-twist protection is achieved via anti-twist elements 6, as is particularly clearly apparent in FIGS. 4 and 5.

(21) Two anti-twist elements 6 which are offset by 180° are present on outer circumferential surface 7 of rotor additional body 5. These anti-twist elements 6 are designed as integral projections 8, and have a domed shape which engages with anti-twist counterelements 9 of at least one of the rotor partial bodies 2 at its inner circumferential surface 10. Anti-twist counterelements 9 are two concavely shaped depressions 11.

(22) Anti-twist counterelements 9 may be present on both rotor partial bodies 2, and together or individually may accommodate one anti-twist element 6.

(23) Returning to FIG. 1, reference is made to the use of four pins 12, three of which have a width that is greater than that of rotor 1, and one pin that is much shorter. The width is measured in the axial direction, and could also be referred to as the height. The shorter of the four pins is also referred to as short pin 13, and is used only for anti-twist protection and/or axial securing of the two rotor partial bodies 2 with respect to one another.

(24) Longer pins 12 are designed as spring suspension pins 14, and are used for supporting/guiding/fastening a mechanical restoring spring, not illustrated here. The individual parts, i.e., the two rotor partial bodies 2 and rotor additional body 5, may be connected via caulkings and/or axial projections which engage with corresponding recesses, similarly as in EP 2 300 693 B1. The contents disclosed in the cited publication with regard to connection techniques are hereby incorporated herein.

(25) As is clearly apparent in FIG. 2, rotor 1 has four vanes 15. Holes 16 are present in two of the vanes 15 to allow accommodation of a locking pin. Thus, a locking pin is accommodated in a borehole. A second, smaller borehole is used for imbalance correction. Grooves 17 are formed at the radial outer end faces of vanes 15, into which sealing elements such as elastic strips are introducible. However, these sealing elements are not illustrated here.

(26) Only rotor additional body 5, which includes oil-conducting pockets 18 between ribs 19 on its circumferential surface 7, is apparent in FIG. 6. While an oil-conducting pocket 18 is open toward a first end face 20 in the absence of a rib present there, oil-conducting pocket 18 adjoining same is open with respect to opposite, second end face 21. Anti-twist element 6 is positioned adjacent to second end face 21.

(27) One of the two rotor partial bodies 2 is illustrated in FIG. 7 and, as is clearly apparent, includes anti-twist counterelements 9 in the form of curved depressions at inner circumferential surface 10. Fixing holes 22 are provided, offset from holes 16 with respect to the center axis of rotor partial body 2, for accommodating pins 12. Four uniformly distributed fixing holes 22 having circular cross sections are present. Holes 16 or fixing holes 22 are implemented as boreholes.

(28) Assembled rotor partial bodies 2 are apparent in FIG. 8. Oil-conducting counterpockets 23 are present on inner circumferential surface 10. The oil-conducting counterpockets are only partially concealed by rotor additional body 5, viewed in the radial direction, and protrude beyond an end face 24 of rotor additional body 5 in the axial direction.

(29) While oil-conducting counterpockets 23 in FIGS. 10 and 11 have a relatively short axial design, oil-conducting counterpockets 23 are much longer in the specific embodiment in FIGS. 12 and 13. End face 24 of rotor additional body 5 is either first end face 20 or second end face 21 of rotor additional body 5. In the specific embodiment according to FIGS. 12 and 13, the oil-conducting counterpockets extend in the axial direction to a rotor partial body end face. This rotor partial body end face 25 is present either at the one rotor partial body 2 or at the other rotor partial body 2. One variant is illustrated in FIGS. 14 and 15, which illustrate the view from the camshaft side and from the side facing away from the camshaft, respectively.

(30) The special feature here is that two journal receptacles 26 are present in a rotor partial body 2, with which journals 27 of the other rotor partial body 2 engage in a form-fit and/or force-fit manner. This is possible in addition to or as an alternative to caulking approaches, pinning approaches, or integral bond connections.

(31) FIGS. 16 and 17 illustrate views from the camshaft side and from the side facing away from the camshaft on assembled rotors 1, respectively, as shown in FIGS. 14 and 15. Also clearly apparent are individual hydraulic medium-conducting channels 4 for supplying the particular working chambers A and B. The two rotor partial bodies 2 are designed mirror-symmetrically with respect to separating plane 3. Journals are provided on the one rotor partial body 2 in the axial direction, and engage with identical recesses on the other rotor partial body 2.

LIST OF REFERENCE NUMERALS

(32) 1 rotor 2 rotor partial body 3 separating plane 4 hydraulic medium-conducting channel 5 rotor additional body 6 anti-twist element 7 outer circumferential surface 8 projection 9 anti-twist counterelement 10 inner circumferential surface 11 depression 12 pin 13 short pin 14 spring suspension pin 15 vane 16 hole/locking borehole/borehole 17 groove 18 oil-conducting pocket 19 rib 20 first end face of the rotor additional body 21 second end face of the rotor additional body 22 fixing hole/borehole for imbalance correction 23 oil-conducting counterpocket 24 end face of the rotor additional body 25 rotor partial body end face 26 journal receptacle 27 journal