EP2300693A1 - Hydraulic camshaft adjuster - Google Patents
Hydraulic camshaft adjusterInfo
- Publication number
- EP2300693A1 EP2300693A1 EP09765567A EP09765567A EP2300693A1 EP 2300693 A1 EP2300693 A1 EP 2300693A1 EP 09765567 A EP09765567 A EP 09765567A EP 09765567 A EP09765567 A EP 09765567A EP 2300693 A1 EP2300693 A1 EP 2300693A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- camshaft adjuster
- inner body
- elements
- camshaft
- oil inlet
- 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
Links
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
-
- 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
- F01L1/022—Chain drive
-
- 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
- F01L1/024—Belt drive
-
- 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
- F01L1/026—Gear drive
-
- 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
- F01L1/352—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 bevel or epicyclic gear
-
- 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
- F01L2001/34459—Locking in multiple positions
-
- 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
- F01L2001/34466—Locking means between driving and driven members with multiple locking 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
- 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
- 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
- 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
- F01L2001/34483—Phaser return springs
-
- 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 hydraulic camshaft adjuster for a camshaft of an internal combustion engine.
- a camshaft adjuster By means of a camshaft adjuster, it is possible to change a phase angle of a camshaft of an internal combustion engine relative to a crankshaft of the internal combustion engine driving the camshaft. As a result, a fuel consumption and raw emissions of the internal combustion engine can be lowered and improve a performance and torque characteristics of the internal combustion engine.
- a rempligelzellenversteller of the generic type is known for example from the document DE 10 2004 022 097 A1.
- the wellgelzellenversteller thereby comprises an outer body which is drivable via a crankshaft, and an inner lying to the outer body arranged inner body, which is fixedly connected to a camshaft.
- a controlled supply of oil from an oil circuit of an internal combustion engine to individual hydraulic or working chambers of the camshaft adjuster formed in the inner body ⁇ lzulauf- and oil drain lines and a associated with the oil supply pressure build-up in the oil inlet and oil drain lines and the chambers of the inner body the outer body adjusted and thus changed the phase angle of the camshaft relative to the crankshaft.
- Both the outer body and the inner body of such a rempligelzellenverstellers can be known sintered technology.
- metal powders are pressed into workpieces or pressings, also known as green compacts, and the workpieces are subsequently sintered.
- the workpieces are given their final strength by the metal powders forming a coherent crystal structure as they pass through a sintering furnace through diffusion and recrystallization processes.
- a height dimension of the workpieces obtained during pressing of the metal powder can deviate from a desired height dimension.
- a hydraulic camshaft adjuster for a camshaft of an internal combustion engine is proposed, which is designed in the manner of a vane-type adjuster.
- the camshaft adjuster includes an externally drivable by means of a crankshaft of the internal combustion engine outer body with at least one hydraulic chamber, and a preferably coaxially disposed inside the inner body to the inner body, which is firmly connected to the camshaft. Under a fixed connection is a positive and / or non-positive connection between the inner body and the camshaft to understand.
- the inner body comprises at least one pivoting wing, which extends in the radial direction into the hydraulic chamber and thereby divides the hydraulic chamber into a first working chamber and a second working chamber.
- the inner body further comprises at least an oil inlet and outlet line extending from an inside of the shell to a shell outside of the inner body and up to one of the two working chambers, the inner body being exposed to the outside to produce a controlled hydraulic pressure in the oil inlet and outlet conduit and in one of the working chambers.
- body is pivotable for adjusting the camshaft.
- the inner body is further joined together at least from a first element and a second element, wherein the two elements each have at least one geometry on mutually facing end sides, which together with the respective other element forms the oil inlet and oil drain line of the inner part.
- the two elements have a substantially radial extent over the circumference.
- the two elements have a substantially axial extent over the circumference.
- a geometry is to be understood as meaning a recess in the respective element which extends from the shell inner side to the outer shell side of the inner body and which does not penetrate the element in its longitudinal direction.
- An advantage of the proposed camshaft adjuster is that there is no further machining required in connection with the above-described sintering production of such inner bodies in order to produce the oil feed and oil drain line.
- the further machining can also include a deburring of the oil inlet and outlet line. Rather, this ⁇ lzulauf- and ⁇ lablauftechnisch created by the joining of the two elements, which together form the inner body. The parting line formed by the two elements closes hydraulically tight.
- the inner body preferably has at least two pivoting wings which each extend into a hydraulic chamber of the outer body.
- the inner body has four pivoting wings which extend each extending into a hydraulic chamber of the outer body.
- the inner body has five pivoting vanes which each extend into a hydraulic chamber of the outer body.
- At least one of the two elements has at least one projection on the front side, which engages in a form-fitting manner for connecting the two elements into a corresponding recess of the other element and forms an interference fit with the recess.
- the projection may be formed in the manner of a claw or a web, wherein a web is a similar to a feather trained projection to understand.
- at least one of the two elements on the front side a plurality of projections which engage positively in the joining of the two elements in corresponding recesses of the other element, wherein under the projections both claw-like and web-like projections may be.
- the two joined elements are identical and each have at least one extending from the shell inside to the shell outside projection which positively engages the connection of the two elements in a corresponding recess of the other element and thereby with the recess forms an interference fit, wherein the two projections together with the associated recesses each form a ⁇ lzulauf- and oil drain line of the inner part.
- An advantage of this embodiment is that in connection with the above-described sintering production of such inner body only a pressing tool is needed to produce workpieces of the same configuration.
- the oil inlet and outlet pipe preferably extends in the radial direction from the shell inside to the outer shell side of the inner body.
- the oil inlet and outlet pipe preferably has a quadrangular cross-sectional shape, which is due to the frontal geometries of the two elements joined together.
- the frontal geometries can also form other cross-sectional shapes, such as a circular or a triangular shape.
- a spring is arranged in the other working chamber between the outer body and the pivoting wing, which acts in a restoring manner in relation to the pivoting of the inner body.
- At least a first oil inlet and oil drain line and a second oil inlet and ⁇ lab- are provided, wherein the first oil inlet and drain line extends to one of the two working chambers, while the second ⁇ lzulauf- and Oil drain line extends to the other working chamber.
- the pivoting wing may be formed integrally with the inner body. Alternatively, the pivoting wing may be inserted into the inner body on the outside of the jacket.
- a receptacle for the swing-wing is provided on the outer shell side of at least one of the two elements.
- the recording can also be performed in two parts and be provided on both elements depending on a receptacle for the swing-wing.
- the receptacle is preferably formed on the projection. Further, the receptacle is preferably formed in the manner of a slot and aligned with the longitudinal direction of the inner body.
- the pivoting wing is preferably guided movably in the receptacle.
- a planetary gear is arranged between the pivoting wing and the outer body, wherein on the outer body a corresponding to the planetary gear segment is formed, which cooperates with the planetary gear, and wherein on the pivoting wing a pocket is formed in the the planetary gear is inserted.
- a planetary gear is disposed on both sides of the hydraulic chamber between a hollow cylindrical core of the inner body and the outer body, wherein on both sides of the hydraulic chamber on the hollow cylinder core corresponding to the associated planet gear segment is formed, which cooperates with the planetary gear, and wherein to both Side of the hydraulic chamber on the outer body, a pocket is formed, in which the associated planetary gear is used.
- both the outer body and the two joined elements of the inner body are formed as sintered parts.
- the two elements are already as compacts or green compacts joined together, which receive as workpieces their final strength during sintering.
- FIG. 1 is a front view of a unit of a vane cell
- FIG. 2 is a perspective view of the unit shown in FIG. 1; FIG.
- FIG. 3 is a side view of the unit shown in FIG. 1,
- FIG. 4 shows a sectional view along the section line A - A in the direction of the arrows shown in FIG. 3
- FIG. 5 shows a further sectional view along the section line A - A shown in FIG. 3, in the direction opposite to the direction of the arrows,
- FIG. 7 shows an exploded view of a first embodiment of an inner body in a first perspective view
- FIG. 88 shows an exploded view of the first embodiment of the inner body in a second perspective view
- FIG. 9 is a perspective view of the first embodiment of the inner body in an assembled state
- 10 is a perspective view of a first element of the first embodiment of the inner body
- 11 is a perspective view of a second element of the first embodiment of the inner body
- FIG. 12 is an exploded view of a second embodiment of the inner body
- FIG. 13 is a perspective view of the second embodiment of the inner body in an assembled state
- FIG. 14 is a perspective view of a first element of the second embodiment of the inner body
- FIG. 15 is a perspective view of a second element of the second embodiment of the inner body
- Fig. 16 is a perspective view of a known in the prior art
- FIG. 18 is a perspective view of a third embodiment of the inner body in an assembled state
- FIG. 19 is a perspective view of an element of the third embodiment of the FIG inside the body
- FIG. 20 shows a perspective view of a fourth embodiment of the inner body in an assembled state
- FIG. 21 is a perspective view of an element of the fourth embodiment of the inner body
- FIG. 22 is a front view of another unit of a vane-type adjuster
- the assembly 2 forms a unit of a hydraulic camshaft adjuster in the form of a so-called rempligelzellenverstellers.
- the outer body 4 is drivable by means of a crankshaft of an internal combustion engine, such as a gear drive, wherein a toothed belt drive or a chain drive is possible.
- the inner body 6, however, is firmly connected to a camshaft of the internal combustion engine, which is insertable into the circular recess 26. Under a solid compound is a positive and / or non-positive connection to understand.
- the outer body 4 comprises Preferably, five hydraulic chambers 18, which are formed by five radially inwardly projecting body portions 20 of the outer body 4.
- a pivot wing 8 of the inner body 6 extends in the radial direction.
- the individual swing vanes 8 divide the individual hydraulic chambers 18 into a first working chamber 22 and a second working chamber 24.
- a drive torque of the crankshaft is transmitted to the camshaft adjuster by means of the outer body 4 introduced and transmitted via the working chambers 22, 24 on the inner body 6, which is fixedly connected to the camshaft.
- the inner body 6 preferably comprises ten oil inlet and oil drain lines 14, 16, each extending preferably in the radial direction from an inner shell side 10 to a shell outer side 12 of the inner body 6 to one of the ten working chambers 22, 24, so that each of the five Hydraulikkammem 18th two of the ten oil inlet and ⁇ lablauftechnischen 14, 16 are assigned.
- the inner body 6 is pivoted relative to the outer body 4 for adjusting the camshaft in one direction. Such pivoting in the clockwise direction is illustrated in FIG. 6 by means of arrows, in which the lines 14 and the associated working chambers 22 are subjected to the controlled hydraulic pressure.
- the lines 14 in this illustration act as oil feed lines, while the lines 16 function as oil drain lines.
- the arrows shown in Fig. 6 further illustrate the flow direction of the oil.
- the individual hydraulic chambers 18 are designed to be concave in accordance with the circular movement described by the vanes 8, so that a pivoting movement of the inner body 6 relative to the outer body 4 can be initiated via the pivot vanes 8.
- the pivoting vanes 8, which are movably guided in the individual receptacles 36 are pressed against the outer body 4 by the action of a centrifugal force, the individual working chambers 22, 24 being sealed against one another.
- the outer wing 4 facing pivot wing sides 8a are preferably flat, so that the sealing of the working chambers 22, 24 via a pressure of the respective longitudinal edges of the swing wing sides 8a takes place.
- the swing wing sides 8a may also be designed convex.
- Sealing strip can also be arranged on the individual radial projections 21 of the outer body 4 in a groove provided for this purpose, so that the individual hydraulic chambers 18 are sealed against each other.
- a spring between the outer body and the associated pivoting wing is arranged in the individual hydraulic chambers in one of two working chambers, which acts with respect to a pivoting of the inner body restoring.
- the inner body 6 illustrated in Figs. 7-9, 12 and 13 is preferably assembled from a first element 28 and a second element 30 which describe a substantially hollow cylindrical core.
- FIGS. 7 to 9 illustrate a first embodiment of the inner body 6, while FIGS. 12 and 13 illustrate a second embodiment of the inner body 6.
- Both the outer body 4 and the two joined elements 28, 30 are preferably formed as sintered parts.
- the two elements 28, 30 have on facing end faces 38, 40 in each case five geometries 39, 41, 50, 52, which together with the respective other element 28, 30 form the oil inlet and oil drain lines 14, 16 of the inner body 6.
- the two elements 28, 30 have a substantially radial extent over the circumference.
- the two elements 28, 30 have a substantially axial extent over the circumference.
- a geometry 39, 41, 50, 52 means a recess in the respective element 28, 30 extending from the shell inner side 10 to the outer shell 12 of the inner body 6, which does not penetrate the element 28, 30 in its longitudinal direction.
- the oil inlet and outlet lines 14, 16 preferably have a quadrangular cross-sectional shape, which is variable in terms of their dimensions in the first embodiment of the inner body 6 and initially increases in the radial direction from the inner shell side 10 and then up to the outer shell side 12th reduced.
- the geometries 39, 41 each have a curvature 39a, 41a, which, however, are irrelevant with regard to the mode of operation of the vane cell adjuster. Rather, such a configuration of the two elements 28, 30 is based in a design of a pressing tool, which aims to reinforce the pressing tool.
- the quadrangular cross-sectional shape of the second embodiment is consistently constant with respect to its dimensions.
- the element 28 comprises, on the front side or on the end faces 40 facing the element 30, five projections 34 which are each designed in the manner of a claw and which respectively correspond to one another Recess 32 of the element 30 engage positively.
- the projections 34 in each case form an interference fit with the associated recesses 32.
- the parting line formed by the two elements 28, 30 also closes hydraulically tight.
- the individual preferably integrally formed pivoting vanes 8 are inserted into the inner body 6 on the outer side 12 of the casing.
- five preferably designed in the manner of a slot receptacles 36 are provided for the swing vanes 8, which are each formed on one of the projections 34 on the outer shell side 29 of the element 28.
- the receiving slots 36 are preferably aligned to the longitudinal direction of the inner body (6).
- the element 28 comprises, on the front side or on the end face 40 facing the element 30, five projections 42 and five projections 44 which are each designed in the manner of a web or a feather key and which respectively engage in a corresponding recess or groove 46, 48 of the element 30 positively.
- the individual webs 42, 44 and recesses 46, 48 extend in the radial direction of the inner body 6.
- the projections 42, 44 in each case with the associated recesses 46, 48 each have a press fit.
- the parting line formed by the two elements 28, 30 also closes hydraulically tight.
- the two elements 28, 30 each comprise, on the front side, five grooves 50, each of which is assigned to one of them.
- Neten casing inside 33, 35 extend to an associated outer shell side 29, 31 and in the assembled state of the two elements 28, 30 form a quadrangular cross-sectional shape, which is invariable in terms of their dimensions in contrast to the first embodiment.
- the individual slot receptacles 36 are designed in two parts.
- five receptacles 36a are provided on the outer shell side 29 of the element 28, while on the outer shell side 31 of the element 30 five receptacles 36b are provided, which terminate flush with the receptacles 36a.
- Figures 16 and 17 illustrate a prior art embodiment of a one-piece inner body 6 sintered from a metal powder mixture.
- the oil inlet and outlet lines 14, 16 have been drilled into the inner body 6 following a sintering process.
- the bores 54, 56, 58 are provided for so-called spring-loaded and hydraulically unlockable locking pins, which engage in the bores 54, 56, 58 in order to prevent unwanted pivoting of the inner body 6 relative to an outer body, not shown.
- Fig. 18 illustrates a third embodiment of the inner body 6, in which the two assembled elements 29b - one of which is illustrated in Fig. 19 - are formed identically, and each preferably five from the shell inside 10 to the outer shell side 12 of the inner body 6 extending projections 64 which engage positively for connection of the two elements 29b in a corresponding recess 62 of the other element 29b and thereby form an interference fit with the associated recesses 62.
- the projections 64, together with the associated recesses 62 respectively form an oil inlet and oil discharge line 14, 16 of the inner part 6.
- An advantage of this embodiment is that, in connection with the above-described sintered production of such internal bodies only a pressing tool is required to produce workpieces of the same configuration.
- FIG. 20 illustrates a fourth embodiment of the inner body 6, after which also the two joined elements 29b are formed identically.
- FIG. 21 illustrates one of the two elements 29b.
- swing vanes 8 formed integrally with the hollow cylindrical core of the respective element 29b are provided (FIG. 21).
- one of the pivoting vanes 8 extends radially outward from the hollow cylindrical core of the inner body 6.
- the projections 64 and recesses 62 are configured analogously to the third embodiment of the inner body 6 (FIGS. 18 and 19).
- FIG. 22 shows an alternative arrangement 2 of a preferably integrally formed outer body 4 and a preferably two-part inner body 6, which is preferably arranged coaxially inwardly to the outer body 4.
- the arrangement 2 preferably forms four hydraulic chambers 18, in each of which a pivoting wing 8 of the inner body 6 extends.
- the individual pivoting vanes 8 are preferably formed integrally with the hollow cylindrical core of the inner body 6. Zwi see the individual swing wings 8 and the outer body 4 is a planetary gear 68 a arranged, which is inserted into a pocket 70 a, which is formed on the pivoting wing 8.
- a corresponding to the planetary gear 68a gear segment 66 is formed at the respective individual planetary gears 68a associated body portions of the outer body 4, which cooperates with the planetary gear 68a.
- the individual planet gears 68a thereby seal the working chambers 22, 24 from each other hydraulically.
- a planetary gear 68b is arranged on both sides of the respective hydraulic chambers 18 between the hollow cylindrical core of the inner body 6 and the outer body 4.
- the individual planet gears 68b are inserted into a pocket 70b which is formed on the respective radially inwardly projecting body portion 20 of the outer body 4.
- a gear segment 72 is further formed on the hollow cylindrical core of the inner body 6, which is formed according to the associated planetary gear 68b and cooperates with this.
- the individual planet gears 68b each seal two adjacent hydraulic chambers 18 against each other hydraulically.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102008028640A DE102008028640A1 (en) | 2008-06-18 | 2008-06-18 | Hydraulic camshaft adjuster |
PCT/EP2009/004172 WO2009152987A1 (en) | 2008-06-18 | 2009-06-10 | Hydraulic camshaft adjuster |
Publications (2)
Publication Number | Publication Date |
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EP2300693A1 true EP2300693A1 (en) | 2011-03-30 |
EP2300693B1 EP2300693B1 (en) | 2012-08-15 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP09765567A Active EP2300693B1 (en) | 2008-06-18 | 2009-06-10 | Hydraulic camshaft adjuster |
Country Status (7)
Country | Link |
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US (1) | US8550046B2 (en) |
EP (1) | EP2300693B1 (en) |
JP (1) | JP5313342B2 (en) |
CN (1) | CN102124188B (en) |
DE (1) | DE102008028640A1 (en) |
ES (1) | ES2393085T3 (en) |
WO (1) | WO2009152987A1 (en) |
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JP5987868B2 (en) * | 2014-07-22 | 2016-09-07 | 株式会社デンソー | Valve timing adjustment device |
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DE102014112377A1 (en) * | 2014-08-28 | 2016-03-03 | Robert Bosch Automotive Steering Gmbh | MANUFACTURING METHOD FOR COMPONENTS OF A SWIVELING MOTOR FOR A STEERING SYSTEM |
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DE19756015A1 (en) * | 1997-12-17 | 1999-06-24 | Porsche Ag | Device for the hydraulic rotation angle adjustment of a shaft to a drive wheel |
JP2000240414A (en) * | 1999-02-16 | 2000-09-05 | Mitsubishi Electric Corp | Vane type hydraulic actuator |
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US6412462B1 (en) * | 2000-01-18 | 2002-07-02 | Delphi Technologies, Inc. | Cam phaser apparatus having a stator integral with a back plate or a front cover plate |
DE102004024222A1 (en) * | 2003-08-15 | 2005-03-10 | Ina Schaeffler Kg | Hydraulic device for use in internal combustion engine, has rotor that is rotationally fixed via central fastener to camshaft, groove running in circumferential direction, and ring shaped intermediate unit for adapting to device |
DE102004024221A1 (en) * | 2003-08-15 | 2005-03-10 | Ina Schaeffler Kg | Internal combustion engine, has pressurized medium adapter to connect axial channel in camshaft and axial channel in driven unit to each other, where adapter is arranged between end of camshaft and driven unit |
DE102004022097A1 (en) | 2004-05-05 | 2005-12-08 | Daimlerchrysler Ag | Hydraulic camshaft adjuster and method of mounting same |
JP4110479B2 (en) * | 2004-09-28 | 2008-07-02 | アイシン精機株式会社 | Valve timing control device |
DE102004047817B3 (en) * | 2004-09-29 | 2005-12-08 | Gkn Sinter Metals Gmbh | Camshaft adjuster for an internal combustion engine |
DE102005026553B3 (en) * | 2005-06-08 | 2006-09-07 | Hydraulik-Ring Gmbh | Reduced-leakage adjuster for camshaft has a rotor consisting of at least cover and core, forming covered channel sector parallel to one side when in contact |
DE102005037525A1 (en) * | 2005-08-09 | 2007-02-15 | Schaeffler Kg | Serial production method for a component for a motor vehicle warms planar components to temperature below the melting temperature and applies pressure to diffusion weld |
JP4640616B2 (en) * | 2006-08-23 | 2011-03-02 | アイシン精機株式会社 | Valve timing control device |
JP2008057397A (en) * | 2006-08-30 | 2008-03-13 | Aisin Seiki Co Ltd | Valve opening and closing timing control device |
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2008
- 2008-06-18 DE DE102008028640A patent/DE102008028640A1/en not_active Ceased
-
2009
- 2009-06-10 CN CN200980123117.6A patent/CN102124188B/en active Active
- 2009-06-10 JP JP2011513924A patent/JP5313342B2/en active Active
- 2009-06-10 WO PCT/EP2009/004172 patent/WO2009152987A1/en active Application Filing
- 2009-06-10 EP EP09765567A patent/EP2300693B1/en active Active
- 2009-06-10 ES ES09765567T patent/ES2393085T3/en active Active
-
2010
- 2010-12-13 US US12/966,774 patent/US8550046B2/en active Active
Non-Patent Citations (1)
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10267188B2 (en) | 2014-08-25 | 2019-04-23 | Schaeffler Technologies AG & Co. KG | Rotor for a hydraulic camshaft adjuster and manufacturing method for a rotor for a camshaft adjuster |
WO2018010714A2 (en) | 2016-07-14 | 2018-01-18 | Schaeffler Technologies AG & Co. KG | Multi-part rotor of a camshaft phaser, in which the rotor comprises at least one cylindrical receiving bore that extends through all rotor parts |
DE102016212861A1 (en) | 2016-07-14 | 2018-01-18 | Schaeffler Technologies AG & Co. KG | Multi-part rotor of a camshaft adjuster, wherein the rotor has at least one extending through all rotor parts cylindrical receiving bore |
Also Published As
Publication number | Publication date |
---|---|
WO2009152987A1 (en) | 2009-12-23 |
JP2011524495A (en) | 2011-09-01 |
ES2393085T3 (en) | 2012-12-18 |
CN102124188A (en) | 2011-07-13 |
US20110126785A1 (en) | 2011-06-02 |
CN102124188B (en) | 2014-10-29 |
EP2300693B1 (en) | 2012-08-15 |
DE102008028640A1 (en) | 2009-12-24 |
JP5313342B2 (en) | 2013-10-09 |
US8550046B2 (en) | 2013-10-08 |
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