EP1865158A2 - Dispositif de réglage d'arbre à came anti-fuite doté d'un ressort de rappel - Google Patents

Dispositif de réglage d'arbre à came anti-fuite doté d'un ressort de rappel Download PDF

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Publication number
EP1865158A2
EP1865158A2 EP07106499A EP07106499A EP1865158A2 EP 1865158 A2 EP1865158 A2 EP 1865158A2 EP 07106499 A EP07106499 A EP 07106499A EP 07106499 A EP07106499 A EP 07106499A EP 1865158 A2 EP1865158 A2 EP 1865158A2
Authority
EP
European Patent Office
Prior art keywords
spring
rotor
camshaft adjuster
camshaft
spring chamber
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP07106499A
Other languages
German (de)
English (en)
Other versions
EP1865158B1 (fr
EP1865158A3 (fr
Inventor
Andreas Knecht
Dirk Pohl
Jan Eimert
Norbert Lösch
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hilite Germany GmbH
Original Assignee
Hydraulik Ring GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hydraulik Ring GmbH filed Critical Hydraulik Ring GmbH
Publication of EP1865158A2 publication Critical patent/EP1865158A2/fr
Publication of EP1865158A3 publication Critical patent/EP1865158A3/fr
Application granted granted Critical
Publication of EP1865158B1 publication Critical patent/EP1865158B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • 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
    • 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
    • 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
    • F01L2820/00—Details on specific features characterising valve gear arrangements
    • F01L2820/01—Absolute values

Definitions

  • the invention relates to a pivoting motor-like camshaft adjuster.
  • Camshaft adjusters according to the swing motor principle are classified in the art according to a usual categorization into two classes, the chain-driven camshaft adjuster and the belt-driven camshaft adjuster.
  • the phaser adjusts the opening and closing times of the gas exchange valves with respect to the driving shaft, such as the crankshaft, at an earlier or later time to take more environmentally friendly interventions in the combustion process in the combustion chambers of the internal combustion engine.
  • the camshaft is adjusted either in the direction of "early” or in the direction of "late” by the oil filling, or by filling with another suitable hydraulic medium, which forms between the rotor and the stator of the camshaft adjuster opposing chambers.
  • the adjustment is forcibly controlled by a return spring, for example, to ensure a certain preferred position of the rotor relative to the stator in the absence of oil pressure, and thus to ensure an emergency running property of the internal combustion engine despite damage to the oil circuit.
  • the rotor is biased according to known embodiments with a spiral or a compression spring-like spring, so that the rotor urges in a rest position on the unloading movement of the spring, if there is no sufficient counter torque in the camshaft adjuster.
  • Spiral springs in the sense of this disclosure are those springs that run with increasing radius in a plane from the inside out.
  • a certain type of chain driven camshaft adjuster is from the German patent application DE 103 39 668 A1 (Aisin Seiki KK dated 28.08.2003) or from the equivalent US script US Pat. No. 6,782,854 B2 1, which schematically represents a camshaft adjuster with compression spring in FIG. 1, whose spring space is arranged both in the rotor and in the stator cover. From the same house also comes the representation of a chain-driven camshaft adjuster, the gem.
  • the European patent EP 0 806 550 B1 (Aisin Seiki KK dated 26.03.1996) or the equivalent US script US 5775279 A in Figure 8 has arranged its pressure spring-like forced adjustment completely in the lid.
  • a special elevation in the cover of the stator is provided, which circumferentially around the center of the phaser, in which the camshaft is connected, forms a cavity below, in which the spring can be arranged.
  • the camshaft adjuster according to the published patent application DE 198 49 959 A1 (Aisin Seiki KK of 29.10.1998) or the equivalent US script US 6039016 A ,
  • the chain-driven camshaft adjusters are usually arranged leaking in the oil circuit of the internal combustion engine to surface-washed, both innewalled and externally, to constantly coat the camshaft adjuster with oil.
  • the belt-driven camshaft adjuster has another idea.
  • the camshaft adjuster is constructed as completely as possible to the outside except for connection points for the ⁇ lzu- and the oil drain in the forming chambers so that the least possible engine oil can pollute the environment.
  • a leakage oil passage can be provided, which returns the hydraulic oil, which diffuses, for example, from the hydraulic chambers in the Fedsteilsebene, in the oil circuit, without giving off oil to the environment.
  • a camshaft adjuster with the three oil passage points feed channel, discharge channel and leakage oil channel, which is otherwise tight, is considered as a hydraulically dense camshaft adjuster in the sense of this invention disclosure.
  • the rotor is located in the oil-containing space, which is divided into a plurality of chambers, wherein common rotors on a rotor designed as a ring core formed wings.
  • FIG JP-A-2002 29 52 09 A camshaft adjuster with a compression spring-like winding which is to be driven by a chain drive can be seen in FIG JP-A-2002 29 52 09 be removed.
  • the phaser shows a multi-fold spring chamber, starting in the sprocket, which, in order to offer a guide for the spring can, the spring outer contour is modeled with tapered walls. Also is from the DE 103 49 176 A1 a camshaft adjuster known, the spring chamber also extends into the cover of the camshaft adjuster. The spring chamber is elongated because of the compression spring used.
  • the selected multiple graduation levels lead to an increased structure of the components that must be sealed to each other.
  • the inventors wanted to show that the prejudice is unjustified and looked for a design that resolves the view that the design can be used for small-volume mass engines.
  • Flachversteller these are those adjusters, with a maximum height of less than 6 cm, preferably less than 4 cm, get along in the, formed by the space formed by the belt drive of Belt drive resulting, maximum height to stay.
  • the lid of the stator or a corresponding height of the bottom protrudes below the belt drive.
  • the camshaft adjuster is referred to in its, considered from one side, cutting plane then called stepped, if he has almost rectangular spaces that can be merging into each other, but their corners manufacturing certain conditional rounding, z. B. by a router, have.
  • Such curves may, for example, show a radius of up to 5 mm.
  • the space in the rotor is referred to, which is held so that a spring can be accommodated.
  • the spring clearance in coil springs, which only require an annular spring space, forms a spring clearance, which lies in the interior, between the wire of the springs.
  • the spring clearance is totally empty.
  • the spring clearance is used to place functional components or functions. In this case, viewed from the side, the rotor initially runs in a decreasing height and then building outward.
  • the camshaft adjuster can be made of different materials, it is advisable to use either a metal or a plastic. If the structural structure of the material does not have sufficient tightness, a further treatment step is necessary to finally make the oil-tightness of the component.
  • the metallurgical powder is often pressed to a density of about 7 kg / dm 3 .
  • the actual final density of the material is in the range of 7.85 kg / dm 3 . Therefore, the sintered member is inherently with a porosity that allows the through-diffusion of the hydraulic medium.
  • possible methods are the application of water vapor to the surface of the component, the impregnation with a suitable plastic, the galvanic surface coating, the galvanic nanocoating and the edge density increase, for example by rolling or shot peening.
  • the molecular surface structure of the sintered component is changed by an oxide formation, so that the molecules are larger and produce an oil-tight layer.
  • sintering it also makes sense to manufacture the stator and other components of the camshaft adjuster by casting or die casting.
  • a casting skin is formed, which has sufficient impermeability to diffused oil, unless it is damaged by subsequent processing steps. If the assembly hashenzerstörneigungen, the casting skin can still be improved by impregnating the component with a plastic or a galvanic surface coating. The same can be said for extrusion or massive forming.
  • suitable plastic options such as, for example, with stone powder added plastics, components can be created in plastic injection molding, which have a sufficient tightness over the life to be guaranteed.
  • the spring chamber which is the space that lies in the rotor without spring space, has a width and a height.
  • the width extends from the rotor center outgoing into the wing extremities.
  • the height of the spring chamber results from the direction, which usually has the narrowest extent.
  • the spring chamber has a greater width than height.
  • the ratio can be specified as at least 2: 1. In such dimensions may be a coil spring with sufficient torque.
  • the spring chamber is located on the side facing away from the camshaft receiving side with its recess side.
  • On one side of the rotor is arranged a camshaft receiving recess with a circumferential shoulder, while the spring space is provided on the opposite side of the rotor.
  • the rotor core has a rotor core edge.
  • the rotor core edge runs around the spring chamber. He circles around the spring chamber and lies between the spring chamber and the wings.
  • the rotor core edge need only have a width such that the oil in the hydraulic chambers between the Statorstegen and the wings is certainly sufficiently retained.
  • the width of the spring chamber is in this case a multiple of the width of the rotor core edge. This design contributes to weight savings. At the same time this reduces the inertia of the rotor relative to the stator.
  • the spring chamber is a flushed with a hydraulic medium space.
  • the spring chamber is a dry spring chamber. If the spring chamber designed as a hydraulic medium flushed space, the density requirement is reduced to the rotor core edge. If the spring space is a dry spring space, the camshaft adjuster includes a smaller amount of oil. Both design variants can be designed according to the wishes of the engine manufacturer in the camshaft adjuster according to the invention.
  • the camshaft adjuster has been designed with a stator and a separate cover in a selected embodiment. If the cover and stator are two separate components, a circumferential, insertable ring density or a circumferential, injected ring seal, in particular as a two-component material or as a silicone rubber, can be provided to increase the oil-tightness.
  • the ring seal seals the hydraulic chamber in the direction of the pulley. The pulley is thus not lubricated by oil.
  • the lid itself can also be made in two parts. In this case, in the middle of a fixable, for example by screwing to secure, sealing plug. This design assures additional oil-tightness by using the (not shown) Central screw, with the camshaft adjuster is to be screwed to the camshaft, leak-tight sealed.
  • the pulley itself may have a stabilizing inner wall, which is at the same time one of the outer walls of the stator. This integration step contributes to further increase the compactness of the camshaft adjuster.
  • the hydraulically tight space is then formed from covers, stator and inner wall of the pulley. There is no further division level. Dividing plane free, the spring lies completely in the rotor. The spring itself hangs at its one end in a Ein monstattstatt the rotor, while the other end of the spring may be mounted in a Ein developmentalstatt the stator cover.
  • an intermediate plate 23 is provided which hydraulically separates the hydraulic region from the region of the spring 9 hydraulically tight over numerous seals 31, 33, 35.
  • the exemplary embodiment shows that even on classic belt-driven camshaft adjusters with an additional dividing plane, the two-part stator cover 21 can be arranged through the intermediate plate 23.
  • One of the seals, the seal 35 hydraulically seals the wall of the pulley 95 with the stator 3.
  • the oil supply takes place via the central flow 57 through the camshaft (not shown), which opens into the camshaft receptacle 79.
  • the camshaft itself extends in such a case into the camshaft receiving recess 81, which lies partially in the rotor 5.
  • the rotor 5 itself has in the region of its rotor center 67 a central inflow 57 which points laterally toward the rotor extremities 73.
  • the rotor 5 is located with its rotor blades 7.
  • the rotor 5 has a spring chamber 53, coinciding in the center with the rotor center 67 a spring chamber 101 is present.
  • the spring chamber 53 is delimited in the direction of the rotor extremities 73 by the rotor core edge 29.
  • the channel guide can be chosen so that it goes through the spring chamber 53 of the spring 9.
  • the rotor 5 is flush or slightly below the edge of the pulley 11 with its teeth 15 which extend over the entire width of the tread.
  • One end of the spring 9 is fixed in the spring retainer 57, the spring 9 is clamped away from the camshaft holder 79 (not visible).
  • One end of the spring is attached to a fixed to the stator rotationally fixed part, such as mounting pins of the stator cover. That is, the other end, the end not hung in the spring retainer 57, is secured between pins of the stator cover.
  • Figures 5 and 6 show two different embodiments of a camshaft adjuster 1 according to the invention, which differ, inter alia, on which side with respect to the camshaft holder 79 with its camshaft receiving recess 81, the spring 9 is arranged in its spring chamber 53.
  • the spring chamber 53 faces away from the stator cover 21, while in the embodiment of Figure 6, the two-part stator cover 21 with its screwed closure plug 25 in the vicinity, immediately adjacent to the spring chamber 53.
  • the rotor channels 55 which are supplied by the central inflow 57, are located on the stator cover on the farther side.
  • the hydraulically tight space is composed of the Riemenradsteg 17, the stator 3 and the seals on 65 by screws 59 to the pulley firmly clamped stator cover 21 together.
  • the shoulder 87 of the camshaft receptacle 79 is formed from the pulley 11.
  • the camshaft adjuster 1 is constructed substantially symmetrically to the rotor center 67. Hydraulically sealed against the environment, the hydraulic oil passes over the Camshaft receiving recess 81 and the Monanströmung 57 in the rotor channels 55 in the rotor 5.
  • the rotor which adjusts the driven shaft, as the camshaft, relative to the driving shaft, such as the crankshaft, which drives a belt drive on the pulley, in its phase position, is functional designed so that it not only has rotor channels 55, but also a spring chamber 53 with a spring 9.
  • the rotor 5 itself provides space for its positive control via a spring 9, which does not claim any additional space in the cover 21.
  • the stopper 25 is provided with a stopper screw thread 77 which hydraulically seals the spring oil space 71 from the environment. Other sealing tasks are performed by the Verspannschrauben 59.
  • the shoulder 87 of the camshaft receptacle 79 lies on the spring-facing side 83, while the side averted from the spring 85 has the cover 21 with its closure plug 25 which can be screwed in via the plug screw thread 77.
  • the Verspannschraube 59 which is present several times, braces the lid 21 with the pulley 11 and its intermediate webs.
  • the rotor 5 may be referred to from its center 67 as an elongated, flat star with individual wings, on its center, the center 67 of the rotor 5 surrounding, the spring chamber 53 is provided as a flat, circular ring, to which the camshaft receiving recess 81st followed.
  • the rotor surface 75 has a total of a uniform profile, but is increasing to the rotor extremities 73 out.
  • the flat, circular, surface-guided spring chamber 53 covers the rotor core 27, which is delimited by the rotor core edge 29.
  • the rotor core edge 29 is compared to the width of the spring chamber 53 is significantly narrower, it is less than five with respect to the width of the spring chamber 53.
  • the shoulder 87 of the camshaft is dimensioned so that it can engage around the camshaft, with only a short remainder the escape, which results from the pulley 11, protrudes in the direction of the camshaft.
  • Below the spring chamber 53 rotor channels 55 extend in almost parallel extent to the spring chamber 53, which may be in hydraulic communication with the Primaanströmung 57. Individual space-forming components are optionally sealed against each other with seals 65.
  • FIG. 7 shows the rotor 5 removed from the stator 3, at which the rotor height profile 69 becomes more apparent.
  • the spring chamber 53 for the spring 9 with its width 103 and its height 105, a spring drying space 61.
  • the hydraulic medium passes through the camshaft receiving recess 81 and the Monanströmung 57 only into the rotor channels 55.
  • the spring cavity 101, the inside between the Spring chamber 53 is located, is designed mainly hydraulically dry, only leaks through the rotor core edge 29 must be led out centrally.
  • Both spring chamber 101 and spring chamber 53 are in the region of the rotor core 27.
  • the region of the rotor extremities 73 which are in the form of vanes 7, follows.
  • the rotor core 27 is bounded by the rotor core edge 29, which spans only a fraction of the dimension of the rotor core in its width. If the rotor surface 75 is viewed starting from the rotor blades inwardly toward the central inflow 57, then a stepped rotor height profile 69 can be seen, the highest height of which can be found in the area of the rotor extremities 73. Due to the recess for the camshaft receiving recess 81 in the region of the center of the rotor 5, the overall height profile forming in the middle is smaller even with a component for spring suspension than in the rotor extremities.
  • the spring suspension 9 of the spring 9, which has already been indicated in FIG. 4, can be better understood by reference to FIG. 8, by considering in more detail how the spring 9 can be preloaded between the hooking pin 89 on the rotor 5 and the hooking pin 91.
  • the spring 9 is in an area remote from the camshaft seat.
  • the camshaft receiving recess 81 behind the camshaft receptacle 79 is located on the side facing away from the spring.
  • a spring chamber 53rd demarcating ring 98 has been used as an additional component.
  • the pulley 11 is located in order to clearly show the volume ratios of the rotor 5 relative to the pulley 11 can.
  • the rotor is positively controlled and can supply all the hydraulic chambers, the rotor height is less than half the height of the pulley.
  • the height of the camshaft adjuster is primarily determined by the width of the drive belt. It is left only a maximum of one cover width from the escape of the pulley.
  • the reset function of the spring 9, which lies in a single plane in the spring chamber realized by the different suspension of the pins 89 and 91 to two mutually rotatable components of the camshaft adjuster. As a result, the twistability and the torsion of the spring is made possible by the different suspension of the pins 89, 91.
  • the spring chamber 53 extends uniformly along the rotor 5.
  • the spring chamber 53 is a simply contiguous, predominantly circular space having a recess in its center.
  • the spring chamber 53 lies exclusively in the rotor 5.
  • the spring chamber 53 may be oil-filled according to one embodiment.
  • the spring 9 is then oil-stored.
  • the rotor 9 shows a rotor 5, with its spring chamber 53.
  • the spring chamber 53 is the spring 9, with the camshaft adjuster can be rotated in a predicament.
  • the rotor 5 also has a plurality of outwardly directed wings 7, which are distributed circumferentially.
  • One of the wings 7 is slightly different in design than most of the other wings.
  • One of the wings 7 has a form-locking element.
  • the positive locking element is a groove 107.
  • In the groove 107 is a form-fitting spring engagement end 109.
  • the spring engagement end 109 is the end of the spring 9, which ensures the mechanically fixed connection to the rotor 5.
  • the end of the spring 9 is unwound laterally from the orientation of the spring guided on the tip of the wing 7 and its extremity region 73.
  • the helical spring 9 lies in its spring chamber 53 except for the spring engagement end 109, which along a wing surface, the wing approximately centered nuttief divided to fill the groove formed by the spring engagement end 109.
  • the spring engagement end 109 points to the edge or the wide tread side of the wing. 7
  • a further exemplary embodiment of a camshaft adjuster 1 according to the invention can be taken from FIGS. 10 and 11.
  • the pins 115 which arranged offset from one another in the spring chamber 53 from the cover 21 provide a spring guide, tension the an end 113 of the spring 9 by deflecting the spring end 113 a.
  • the spring 9 extends completely in the rotor recess 51, which can receive the spring 9 in one position.
  • the spring retainer 97 is located in the middle of the camshaft adjuster 1.
  • the spring retainer 97 is preferably pierced centrally, so that a slot together with one end of the camshaft 117 can form.
  • the slot is designed as a central screw hole 121 with an internal thread, so that a central screw can connect the rotor 5 with the camshaft 117.
  • From the spring 9 go the two spring ends 111, 113, which are configured as spring engagement ends 111, 113, bent, it can also be said deflected, from. At least two of the pins 115 are spaced so that the thickness of the spring 9 fits exactly therebetween and is thus arranged in a press fit.
  • One end of the spring 9, the engagement end 111 is seated in a groove 119.
  • the connection is configured as similar as shown in Figure 9.
  • the camshaft adjuster 1 limits at one end the camshaft 117 arranged behind it, which is aligned by a fixing pin 99 to the rotor 5 of the camshaft adjuster 1.
  • the centering sleeve 23 serves as a further alignment means.
  • the spring 9 is perpendicular to the axis of the camshaft 117. It is arranged on the side of the rotor 5 remote from the camshaft 117.
  • the camshaft 117 rests in the camshaft receiving 79 of the pulley 11. The pulley 11 is thus on the end of the camshaft 117 stored.
  • the spring 9 is wound in the same plane as the wings 7 protrude from the rotor 5. As a result, a layered structure of the lid 21, the rotor 5 and the inserted under the cover 21 in the rotor 5 spring 9 can be realized. Spring 9 and rotor 5 are pierced only by the central screw to be provided.
  • the camshaft 117 connects to the one of the two sides of the camshaft adjuster 1. The camshaft 117 does not completely penetrate the camshaft adjuster 1, but instead only adjoins on one side.
  • the new camshaft adjuster according to the invention is characterized by many positive characteristics, it is more compact, lighter, smaller and faster than many conventional belt-driven camshaft adjuster.
  • the rotor 5 is repeatedly used functionally, wherein the wall thicknesses of the rotor between its hydraulic fluid-carrying areas are selected so that a fürdiffund Schlieren is successfully prevented.
  • the invention has been graphically illustrated by a coil spring, it is understood One skilled in the art, that such embodiments fall within the scope of the patent teaching, which manage with a different spring, as long as the positively controlling spring for determining the preferred rotational direction is completely in the rotor.
  • the lid itself may be slightly curved, but it is all in one plane, which is not interrupted by the spring.
  • the spring and cover extend parallel and flat to each other over the substantial area of the rotor diameter.
  • the individual components such as cover, spring, spring chamber, rotor with rotor channels and Riemenradinnenwand, each other a parallel arrangement, the parts remain in their respective spaces, without interfering with the adjacent spaces of the other components or interrupting them , Therefore, the components are executed without interruption.
  • the height of the rotor is minimized, the additional space resulting in the stator is utilized by means such as positive control, oil supply, rotor lock, deadlock, or sliding friction reduction while no oil is applied to the rotor Outside of the pulley in the area of the running surface of the pulley passes.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
EP07106499A 2006-05-11 2007-04-19 Dispositif de réglage d'arbre à came anti-fuite doté d'un ressort de rappel Not-in-force EP1865158B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006022219A DE102006022219B4 (de) 2006-05-11 2006-05-11 Leckagedichter Nockenwellenversteller mit Rückstellfeder

Publications (3)

Publication Number Publication Date
EP1865158A2 true EP1865158A2 (fr) 2007-12-12
EP1865158A3 EP1865158A3 (fr) 2007-12-19
EP1865158B1 EP1865158B1 (fr) 2008-12-17

Family

ID=38607765

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07106499A Not-in-force EP1865158B1 (fr) 2006-05-11 2007-04-19 Dispositif de réglage d'arbre à came anti-fuite doté d'un ressort de rappel

Country Status (5)

Country Link
EP (1) EP1865158B1 (fr)
KR (1) KR101404661B1 (fr)
CN (1) CN101196131B (fr)
DE (2) DE102006022219B4 (fr)
ES (1) ES2317619T3 (fr)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008023066A1 (de) 2008-05-09 2009-11-12 Hydraulik-Ring Gmbh Nockenwellenverstellung mit trockener Lauffläche
DE102008032412A1 (de) 2008-07-10 2010-01-14 Hydraulik-Ring Gmbh Gestreckter Nockenwellenversteller
EP2184450A1 (fr) * 2008-11-11 2010-05-12 Schaeffler AG Organe de réglage à piston rotatif doté d'un ressort de torsion
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DE102008032412A1 (de) 2008-07-10 2010-01-14 Hydraulik-Ring Gmbh Gestreckter Nockenwellenversteller
EP2184450A1 (fr) * 2008-11-11 2010-05-12 Schaeffler AG Organe de réglage à piston rotatif doté d'un ressort de torsion
EP2199548A1 (fr) * 2008-12-17 2010-06-23 Feintool Intellectual Property AG Dispositif de rappel d'un déphaseur pour un arbre à came
WO2011003681A1 (fr) * 2009-07-07 2011-01-13 Schaeffler Technologies Gmbh & Co. Kg Dispositif de réglage d'arbre à cames
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WO2011098331A1 (fr) * 2010-02-15 2011-08-18 Schaeffler Technologies Gmbh & Co. Kg Roue à aubes d'un dispositif pour l'ajustement variable des temps de commande de soupapes d'échange gazeux d'un moteur à combustion interne
WO2011160994A1 (fr) * 2010-06-22 2011-12-29 Schaeffler Technologies Gmbh & Co. Kg Dispositif de commande des temps de commande de soupapes d'un moteur à combustion interne
US8931447B2 (en) 2010-06-22 2015-01-13 Schaeffler Technologies Gmbh & Co. Kg Device for controlling the valve control times of an internal combustion engine
DE102011100011A1 (de) 2011-04-29 2012-10-31 Daimler Ag Nockenwellenversteller
WO2014048588A1 (fr) * 2012-09-26 2014-04-03 Schaeffler Technologies AG & Co. KG Mécanisme de positionnement d'arbre à cames
US9441508B2 (en) 2012-09-26 2016-09-13 Schaeffler Technologies Gmbh & Co. Kg Camshaft adjuster
WO2016045669A1 (fr) * 2014-09-26 2016-03-31 Schaeffler Technologies AG & Co. KG Liaison d'un dispositif de réglage d'arbre à cames à l'arbre à cames

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KR20070109948A (ko) 2007-11-15
DE502007000296D1 (de) 2009-01-29
CN101196131A (zh) 2008-06-11
EP1865158B1 (fr) 2008-12-17
CN101196131B (zh) 2011-08-24
EP1865158A3 (fr) 2007-12-19
DE102006022219A1 (de) 2007-11-22
DE102006022219B4 (de) 2008-01-03
KR101404661B1 (ko) 2014-06-09
ES2317619T3 (es) 2009-04-16

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