Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H53/00—Cams ; Non-rotary cams; or cam-followers, e.g. rollers for gearing mechanisms
  • F16H53/02—Single-track cams for single-revolution cycles; Camshafts with such cams
• • 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
  • F01L1/02—Valve drive
  • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
  • F01L1/047—Camshafts
• • 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
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
  • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
  • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
  • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
  • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
  • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
  • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
  • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
  • F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16H—GEARING
  • F16H53/00—Cams ; Non-rotary cams; or cam-followers, e.g. rollers for gearing mechanisms
  • F16H53/02—Single-track cams for single-revolution cycles; Camshafts with such cams
  • F16H53/04—Adjustable cams
• • 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
  • F01L2001/34479—Sealing of phaser devices
• • 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
• • 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
  • F01L2820/00—Details on specific features characterising valve gear arrangements
  • F01L2820/01—Absolute values

Definitions

• the invention relates to a rotor for a camshaft adjuster.
• the present invention relates to the genus of hydraulic camshaft adjusters.
• Hydraulic camshaft adjusters may for example be designed as a camshaft adjuster, which operate on the vane principle.
• the described invention relates to a type of camshaft adjuster having a stator and a rotor.
• the rotor is located inside the stator and has a number of vanes.
• One or more wings form with corresponding counter-elements of the stator at least two chambers which are offset from each other in such a manner that filling a first chamber results in at least partial emptying of the second chamber and thereby simultaneously rotating the rotor is effected.
• a camshaft joined to the rotor is rotated.
• the camshaft can thus be adjusted by means of a hydraulic use of a fluid, for example an oil, at least between a first position and a second position using such a camshaft adjuster.
• the invention has for its object to improve a rotor for a camshaft adjuster.
• the object is achieved with a rotor for a camshaft adjuster with the features of claim 1.
• the object is achieved with a joining set with the features of claim 12.
• the rotor is intended for rotation about a rotation axis.
• the rotor comprises: a first end face,
• the at least one wing is arranged at the central area. From the central area, the wing extends directed radially pointing away.
• At least two camshaft centering elements are arranged on the inner side surface.
• the camshaft centering elements are designed as elevations.
• the rotor for rotation about an axis of rotation is to be understood in the described situation as providing rotation in an angular range required for adjusting a camshaft from a first position to a second position and back.
• the concept of rotation about a rotation axis is not to be understood as meaning that complete rotation is required.
• the term of the receiving end opposite the first end face is to be understood as being a first end face and a second end face of a same body, wherein the second end face is located as a receiving end face on a side of the rotor other than the first end face.
• the rotor is a body having a basic geometric shape that can be derived from a cylindrical body.
• the first end face and the receiving end face are oriented substantially parallel to one another. A parallel orientation of the first end face to the second end face is not only easier to manufacture but also leads to a much easier to achieve reduction of leakage of the system.
• the term of the receiving end face is to be understood to mean that it is at the receiving end face to a front side, which is suitable and preferably also provided for, the camshaft in a joining of the
• central region designates that part of the rotor which, in the assembled state of the camshaft, comes into contact with the rotor directly or indirectly with the camshaft.
• a wing Arranged starting from the central region is a wing, wherein the wing is preferably connected in a materially bonded manner to the central region.
• the rotor is a rotor having a number of at least three
• Wings The notion of a radially pointing away from the central region alignment of the wing or the wing is to be understood in particular to the effect that a focal plane of the wing, which also includes the axis of rotation, a predominantly radial direction away from the axis of rotation direction component and against this a smaller proportion of a tangential order Having the axis of rotation facing share.
• the wing is bent, for example, in a direction tangential to the axis of rotation.
• the wing has, for example, side surfaces which are tilted relative to a plane containing the axis of rotation.
• the wing or all wings have a plane of symmetry in which the axis of rotation of the camshaft is located.
• the term of the camshaft receiving recess is to be understood that in the central region of the rotor is a depression which is suitable for a partial introduction of the camshaft, provided that this camshaft has a suitable cross-sectional area and cross-sectional shape. It should not be ruled out that the camshaft receiving recess is a through hole that completely penetrates the rotor. Preferably, however, the camshaft receiving recess is a recess which finds a bottom in a volume of the central portion of the rotor.
• this base is positioned completely perpendicular to the axis of rotation, that is to say that the camshaft receiving recess substantially forms a half-space, which forms a cylindrical cavity or a substantially cylindrical cavity with an imaginary completed receiving end-face cover.
• inner side surface refers to the inner surface of the camshaft receiving recess resulting in the central portion of the rotor without the bottom resulting from incomplete penetration of the rotor.
• the inner side surface is, as it were, the part of the lateral surface of the above-described cavity, which does not form the bottom or an imaginary cover of the cavity described above. It should not be prevented by possibly existing on the inner surface edges that in the definition used here, the entire once the axis of rotation circumferential surface is referred to as an inner surface.
• the inner side surface results as a lateral surface of this circular cylindrical cavity.
• At least two Nockenwellenenzentneriata are arranged on the inner side surface.
• the camshaft centering elements are elevations, which rise from the volume of the rotor on the inner side surface.
• camshaft receiving recess has a round opening area.
• the inner side surface is oriented completely parallel to the axis of rotation. This is the case, for example, in an embodiment of the camshaft receiving recess as a substantially cylindrical body.
• a round opening surface of the camshaft receiving recess has the advantage of being particularly suitable for receiving camshafts also round cross-sectional area, which corresponds to the most common design of camshafts. Due to the high rotational symmetry of a round camshaft receiving recess proves to be particularly particularly advantageous in that the production is considerably simplified and a particularly advantageous to achieve maintaining the centering over a high number of rotation cycles is effected.
• the rotor for example, it may also be provided that the rotor has an odd number of camshaft centering elements. An odd number of Nockenwellenzentrierettin results in the advantage that a centering of a camshaft for elementary geometric reasons can be made in a particularly advantageous manner. This is especially true in the case of a round opening area of
• the rotor has exactly three camshaft centering elements.
• the rotor has three Nockenwellenenzentrieriata which in their
• the geometric centers of gravity of the camshaft centering elements form an equilateral triangle in a plan view of the rotor, for example with the axis of rotation as the visual axis.
• This configuration of high symmetry results, in particular in the case of a camshaft having a round cross-section and thereby also resulting round camshaft receiving recess, a particularly advantageous and safe centerability of the camshaft while at the same time having the greatest possible manufacturability.
• the rotor has a number of exactly five camshaft centering elements, which result in a plan view, for example, with the axis of rotation as a visual axis, in their geometric centers of gravity an equilateral pentagon. This results, as well as in the aforementioned embodiment with exactly three Nockenwellenenzentrierianan, an excellent camshaft centering at the same time fertility.
• the number of Nockenwellenzentrieriata is identical to the number of wings. This results in the advantage that a deviation from the centered alignment of the camshaft is avoided by the advantageous geometry particularly efficient.
• an angular distribution of the camshaft centering elements corresponds to an angular distribution of the vanes.
• the term angular distribution here refers to the geometric center of gravity of both the camshaft centering elements and the vanes.
• the geometric center of gravity described above in just this plane of symmetry.
• An embodiment of the rotor can be characterized, for example, in that the at least two camshaft centering elements rise radially in the direction of the axis of rotation along a circumference of the circumference of the inner side surface.
• camshaft centering elements are elevations which are in a part of the circumference of the inner side surface described above in an already described round configuration.
• an angular extent of at least two, preferably all, camshaft centering elements is the same.
• the circular circumferential section of the inner side surface, on which a camshaft centering element designed as an elevation is arranged is the same for at least two camshaft centering elements.
• this angular extent is the same for all camshaft centering elements, since in such a case
• Camshaft centering elements are provided in the same configuration.
• rotor in a further embodiment of the rotor can be provided, for example, that an angular spacing between each two adjacent Nockenwellenenzentrierijnn is the same. In a preferred embodiment, this is the case for all over the entire circumference of the inner side surface existing Nockenwellenenzentrierieri. This results in a high symmetry of the arrangement of the camshaft centering elements with the corresponding advantages associated therewith for a good centering of the camshaft.
• the rotor is joined from exactly two separately manufactured rotor parts.
• a joining of the rotor from two rotor parts has the particular advantage that, for example, lubricant supply lines in the interior of the rotor by means of
• the rotor is made of exactly two parts, which are identical in their shape. This would not least a
• the rotor in a further embodiment of the rotor can be provided, for example, that the rotor is made by means of a powder metallurgical process.
• the rotor is made by means of a powder metallurgical process.
• Injection molding is particularly preferred, that for the production of a rotor or the rotor parts, a method of sintering is provided.
• the rotor is partially or completely made of a sintered metal, a sintered steel or a sintered metal
• Sintered ceramic exists.
• a camshaft centering element, a plurality of camshaft centering elements, preferably all camshaft centering elements are produced by means of a primary molding method.
• the rotor or the rotor parts are produced by means of a powder metallurgical method.
• the rotor or the rotor parts and, as a result, in particular also the camshaft centering elements are produced by means of a sintering process.
• an adjustment of a radial dimension of the camshaft centering elements comprises a calibration.
• Camshaft centering is a step of adjusting a radial dimension.
• calibrating the camshaft centering elements is the last step of adjusting a radial dimension.
• Kalibrierens can be set with particularly good dimensional accuracy, the inner dimensions, for example, in the case of a circular cross-sectional area or the camshaft receiving recess in a configuration with a circular opening cross section, the inner radius, with a particularly high dimensional stability.
• the internal dimensions in particular, for example, in the aforementioned example of the inner radius, optimally no longer results the need to make a mechanical and thus very complex reworking.
• a deburring can still be provided, for example.
• a surface of the camshaft centering elements is open-pored. It may also be possible for a surface of the camshaft centering elements to be free from
• Traces of mechanical reworking is.
• a state of the surface is referred to as having an open porosity, in which typical pores remaining on the surface, for example after sintering, are not already closed, for example by turning, honing, lapping or similar, in particular mechanical, aftertreatment processes.
• the joining set should in particular comprise at least one rotor. Furthermore, the joining set should comprise at least one camshaft provided for insertion into a camshaft receiving recess of a rotor.
• the camshaft should be one
• the term of the insertion area hereby designates the area which is provided for the insertion of the rotor into the camshaft receiving device.
• the insertion region of the camshaft may differ, for example, in shape and / or area from other areas of the camshaft.
• Camshaft should have certain cross-sectional dimensions.
• the cross-sectional dimensions have tolerances of 50 ⁇ . It can also be provided that the cross-sectional dimensions have tolerances of 30 ⁇ .
• the cross-sectional dimensions result in an embodiment of the camshaft as a camshaft having a circular cross-sectional area and / or as a camshaft having an insertion area with a circular cross-sectional area as the cross-sectional radius.
• the radial extent of the elevations with the camshaft of the joining set has a tolerance range of less than 30 ⁇ for and more than 10 ⁇ .
• the radial extent of the surveys with the camshaft of the joining set has a tolerance range of less than 25 ⁇ and more than 15 ⁇ .
• the radial extent of the elevations with the camshaft of the joining set has a tolerance range of 20 ⁇ . This tolerance range is important for an insertability of the camshaft in the camshaft receiving device, for which a certain clearance fit is necessary. With the described values, a tolerance range of each individual camshaft centering element is designated in each case. drawings
• FIG. 1 shows a rotor for a camshaft adjuster in a plan view of a
• Fig. 2 shows a rotor for a camshaft adjuster in an oblique view, wherein the oblique view is shown on the receiving end face.
• FIG. 1 shows a rotor 101 for a camshaft adjuster.
• the rotor 101 is shown here in a plan view of a receiving front side 104.
• a first end face which is opposite to the receiving end face and thus present on the other side of the rotor 101, is therefore not shown in the illustration shown.
• the rotor further has a central region, which in the present embodiment of the rotor 101 is designed as a hollow body provided with an approximately round cross section.
• the rotor 101 is hereby a rotor with a circular-cylindrical envelope and a rotation axis 102, which in the embodiment of the rotor 101 shown is identical to the center of the circular cross-section of the rotor
• Central area is. At the central area a first wing 105 is arranged and four further wings, wherein four of the five wings are formed in the illustrated embodiment of the rotor 101 as identically shaped wings and the fifth wing in its configuration due to another function to be performed by the wing in his Forming differentiates.
• the central area has a
• Camshaft receiving recess 106 which is present in the central region. Due to the existing camshaft receiving recess 106, an inner side surface 107 forms on the essentially circular-cylindrical central region. The inner side surface 107 has at least two camshaft centering elements 108.1 and 108.2. Furthermore, the
• Rotor 101 more Nockenwellenzentrieriata 108.3, 108.4 and 108.5.
• the camshaft centering elements are elevations which emerge in the radial direction from the inner side surface 107.
• the camshaft centering elements 108.1, 108.2 are elevations which emerge in the radial direction from the inner side surface 107.
• an angular extent of all camshaft centering elements ie each of the camshaft centering elements 108.1, 108.2, 108.3, 108.4 and 108.5, is identical.
• Rotor 101 is formed such that a distribution of the Nockenwellenzentrierieri evenly done so that an angular spacing of two adjacent camshaft centering elements for each pair of two adjacent Nockenwellenententrierieri is identical.
• the Fig. 2 is a another embodiment of a rotor for a
• the rotor 201 of FIG. 2 is shown here in a perspective oblique view.
• the perspective oblique view is also shown here, comparable to the representation of FIG. 1, with a view of the receiving front side 204.
• the receiving end face opposite the first end face is therefore not visible in Fig. 2.
• an axis of rotation 202 is shown, to the rotation of the rotor 201 is provided.
• the rotor 201 has a central region, which is surrounded in approximately a circular cylindrical envelope.
• a first wing 205 is arranged and in addition to the first wing 205, four further wings, of which three wings in Fig. 2 are visible and a fourth wing in the lower part of Fig. 2 is still indicated indicated.
• a camshaft receiving recess 206 can be seen on the receiving end face, which substantially fills a circular-cylindrical shaped volume in the central region of the rotor. As a result, an inner side surface 207 corresponding to a lateral surface of a circular cylinder is formed.
• a first camshaft centering element 208.1 is indicated, a second camshaft centering element 208.2 and a third camshaft centering element 208.3 are visible, and two further camshaft centering elements are hidden in the perspective view.
• the distribution of the camshaft centering elements is characterized by a uniform angular distribution on the circumference of the inner side surface.
• the angle between the dashed line 209 and the dashed line 210 is the same size as the angle between the dashed line 21 1 and the dashed line 212.
• the angular extent of each individual Nockenwellenenzentrierelements in the embodiment shown is also the same size.
• the angular extent, ie the angle between the dashed line 210 and the dashed line 21 1, is the same size as the angle between the dashed line 212 and the dashed line 213.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Valve Device For Special Equipments (AREA)
• Valve-Gear Or Valve Arrangements (AREA)
• Rotary Pumps (AREA)
• Applications Or Details Of Rotary Compressors (AREA)

Applications Claiming Priority (4)

Publications (1)

Family

ID=52106086

Family Applications (2)

Family Applications After (1)

Country Status (5)

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• 2013
  • 2013-07-12 DE DE102013107434.0A patent/DE102013107434B4/de not_active Expired - Fee Related
  • 2013-07-12 DE DE102013107431.6A patent/DE102013107431A1/de not_active Withdrawn
• 2014
  • 2014-06-30 WO PCT/EP2014/063885 patent/WO2015000862A2/de active Application Filing
  • 2014-06-30 EP EP14734803.1A patent/EP3017155A2/de not_active Withdrawn
  • 2014-06-30 CN CN201480019494.6A patent/CN105121795B/zh not_active Expired - Fee Related
  • 2014-07-01 CN CN201480030268.8A patent/CN105264186B/zh not_active Expired - Fee Related
  • 2014-07-01 EP EP14734809.8A patent/EP3017156B1/de not_active Not-in-force
  • 2014-07-01 WO PCT/EP2014/063936 patent/WO2015000883A1/de active Application Filing
• 2015
  • 2015-10-15 US US14/884,260 patent/US10598267B2/en not_active Expired - Fee Related
  • 2015-10-29 US US14/926,779 patent/US10054210B2/en not_active Expired - Fee Related

Non-Patent Citations (2)

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