EP2093388A1 - Déphaseur d'arbre à cames de moteur à combustion interne - Google Patents

Déphaseur d'arbre à cames de moteur à combustion interne Download PDF

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Publication number
EP2093388A1
EP2093388A1 EP08101750A EP08101750A EP2093388A1 EP 2093388 A1 EP2093388 A1 EP 2093388A1 EP 08101750 A EP08101750 A EP 08101750A EP 08101750 A EP08101750 A EP 08101750A EP 2093388 A1 EP2093388 A1 EP 2093388A1
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EP
European Patent Office
Prior art keywords
camshaft
adjusting device
rotor
tubular body
hub
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
EP08101750A
Other languages
German (de)
English (en)
Other versions
EP2093388B1 (fr
Inventor
Dipl.-Ing.(BA) Gerold Sluka
Dipl.-Ing.(FH) Frank Heidl
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.)
Hofer Mechatronik GmbH
Original Assignee
Hofer Mechatronik 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 Hofer Mechatronik GmbH filed Critical Hofer Mechatronik GmbH
Priority to EP20080101750 priority Critical patent/EP2093388B1/fr
Publication of EP2093388A1 publication Critical patent/EP2093388A1/fr
Application granted granted Critical
Publication of EP2093388B1 publication Critical patent/EP2093388B1/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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0475—Hollow 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • F01L2001/0476—Camshaft bearings
    • 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

Definitions

  • the invention relates to an adjusting device for an internal combustion engine, with which the relative position of a camshaft for influencing the timing of valves of a valve train of the camshaft is variable according to the preamble of patent claim 1.
  • the DE 103 46 444 A1 (Applicant: DaimlerChrysler AG, filing date: 07.10.2003) shows two embodiments with an extended rotor of a camshaft adjuster.
  • the stepped rotor abuts in sections on the hollow camshaft as a bearing to support the phaser.
  • an inner body and the camshaft bearing are designed as a one-piece component.
  • the in the DE 103 46 444 A1 disclosed design of camshaft adjusters can gem.
  • impeller acc. FIG. 1 the DE 197 81 754 Cl (patentee: INA Wälzlager Schaeffler oHG; priority date: 15.04.1997) is cap-shaped, so that the bearing of the rotor also clamped on comprises the camshaft to be connected.
  • the object of the invention is to provide an adjusting device for an internal combustion engine for changing the relative position of a camshaft, which are connected to one another such that with free design of the Nockenvvelle the occurring loads are taken up specifically.
  • the adjustment is ideal for connection to a camshaft, which is largely freely designable, ie the camshaft can also be built genus.
  • the rotor is provided with a protruding beyond the width of the adjusting extension, in which the bore of the rotor is continued.
  • This extension, together with the rotor is designed as a hub tightly enclosing the camshaft, this solid composite contributing to optimizing the flexural rigidity of the camshaft.
  • the hub of the rotor specifically cooperates with the camshaft bearing. It is favorable that the extension of the rotor projects into a bearing bore of the camshaft bearing or is surrounded by said bearing bore.
  • the component rotor with extension can be implemented in a simple manner using justifiable means.
  • the adjusting device can be used in an internal combustion engine or internal combustion engine, in particular a gasoline engine type.
  • a corresponding internal combustion engine is equipped with the adjusting device.
  • the internal combustion engine has at least one crankshaft, at least one camshaft and at least one corresponding adjusting device.
  • a corresponding internal combustion engine can halve several camshafts.
  • the adjusting device serves to influence the relative position of a camshaft, in particular with respect to a standing in drive connection drive shaft, such.
  • the camshaft has a low bending stiffness.
  • a low flexural rigidity is a flexural stiffness of 1.8 kNm 2 (with a wall thickness of approximately 2 mm for a typical automobile steel for the camshaft).
  • a bending stiffness of 2,000,000 kNmm 2 is considered to be low.
  • the flexural rigidity of the camshaft is too low for the transmission of the torque introduced from outside onto the adjusting device, in particular the bending moment.
  • the camshaft alone can not span the piece between the adjusting device and its first or even up to its second bearing unsupported.
  • the camshaft is designed with a smaller than the required wall thickness for the transmission of the introduced bending moment.
  • the bending stiffness of the unamplified camshaft is less than designed for the transmission of the bending moment from the endless drive or the torque originating therefrom.
  • the dressing in particular the press fit, should extend beyond the camshaft adjuster width to at least one camshaft bearing if the camshaft itself is designed to be too thin.
  • the adjusting device is used to influence the timing of Valves of a valve train of the internal combustion engine and should be able to change these timing.
  • the adjusting device has a rotor.
  • the rotor can be firmly connected to the camshaft.
  • the adjusting device has a rotor and a stator coupled to a drive device.
  • Rotor and stator work on a pivot motor-like principle. They are also collectively referred to as sogelzellenversteller.
  • An axial bore of the rotor serves to receive a shaft portion of the camshaft. The bore is intended to receive part of the camshaft.
  • the axial bore of the rotor surrounded by the stator has an axial extension extending beyond the width of the adjusting device on at least one side. The extension is continued axially.
  • the rotor and the extension form a hub enclosing the camshaft.
  • the hub is formed in such a way that a camshaft bearing forms with the hub a longitudinal reinforcement which increases the bending stiffness of the camshaft.
  • the longitudinal reinforcement is the cylindrical reinforcement direction along the camshaft. Along the longitudinal axis of the camshaft, in particular in the end region of the camshaft, the camshaft is amplified and the flexural rigidity is increased.
  • the central shaft on which the cams line up, the camshaft, which can be built type, is implemented with particularly thin walls.
  • the shaft can be widened more easily, in particular with less effort, at least in the area of a cam and thus determine the cam.
  • the deformation of the camshaft for locking the cam can here by means of mandrel, cone or a hydraulic. Device done. It must be made a lower energy input into the material of the camshaft.
  • the axial extension of the adjusting device can be made according to an embodiment of one piece with the rotor.
  • the axial extension of the adjusting device and the rotor can be made separately from each other and then combined to form a structural unit.
  • the camshaft enclosed by the hub may comprise a tubular body.
  • the internal combustion engine has at least one camshaft bearing. As a rule, two or even three camshaft bearings are provided. Frequently, a camshaft bearing is provided next to each cylinder of the internal combustion engine. A camshaft bearing for the Camshaft is located adjacent to the hub. The camshaft bearing extends there. The camshaft bearing and the hub work together to increase the bending stiffness of the camshaft.
  • the hub protrudes into a bearing bore of the camshaft bearing.
  • the hub thus extends to the bearing, in particular the bearing bore, which is located inside the bearing.
  • the tubular body of the camshaft has seen over the length of the camshaft according to one embodiment, a constant outer diameter.
  • a constant outer diameter is considered to be constant, which has only locally limited indentations.
  • the dents serve, for example, for the tightening tool during assembly, while the rest of the camshaft is designed to be consistent.
  • the tubular body of the camshaft between the rotor and the camshaft bearing may have a smaller outer diameter than in a remaining region of the tubular body. The rest of the area is beyond the adjustment and it is beyond the camshaft bearing.
  • the fixation of the hub on the pipe body can be done by positive locking.
  • the positive connection can be implemented for example by a toothing.
  • the fixation of the hub on the pipe body can be done by adhesion.
  • the adhesion can z. B. be prepared by a Leksspressva or by a transverse compression bandage. The adhesion is thus for example via a press fit.
  • fixation of the hub on the pipe body can be done by material bond. Suitable techniques are welding, gluing, soldering. Similar cohesive manufacturing processes can be selected.
  • a pin-like Insert provided in an interior of said tubular body.
  • Rotor and stator are flat, flat components.
  • the rotor and the stator can be limited seen in the axial direction of the camshaft of closure plates.
  • the closing plates can be formed by prefabricated components.
  • the inner diameter and outer diameter of the tubular body may be substantially constant over the axial length of said tubular body. With a constant wall thickness for the tubular body can be operated.
  • At least the inner diameter of the tubular body over the axial length of said tubular body can be adapted specifically to the occurring loads of the camshaft.
  • the wall thickness of the pipe body is adapted to the expected loads along its extension.
  • the pivoting motor-like adjusting device together with a suitable camshaft, which is reduced in particular in its wall thickness, can be installed in an internal combustion engine so that the camshaft is guided on camshaft bearings in communication with a driving shaft and by the adjustment of the relative position of the camshaft relative to the driving shaft, in particular the crankshaft, can be adjusted and changed.
  • the adjustment performs rotational adjustment movements.
  • the adjusting device is designed for the interaction with a control valve, which is preferably arranged centrally, ie centrally.
  • the cartridge-like control valve is to be inserted intimately.
  • the cartridge-like control valve thus comprises a sleeve from which the valve gets its name.
  • the control valve amplifies the designed as a hollow camshaft camshaft.
  • the tip of the control valve, in particular the end of the hydraulic part extends to a camshaft bearing.
  • the control valve is to be inserted in the hollow camshaft.
  • the sleeve of the hydraulic part of the valve supports the torque transmission initiated by the rotor.
  • the sleeve is designed like a pin to be inserted, so a pin-like use.
  • An internal combustion engine according to the invention with an adjusting device according to the invention has at least one hollow camshaft. At least one adjusting device hangs on the hollow camshaft.
  • the hollow camshaft is tubular.
  • the pivoting motor-like adjusting device is attached, which comprises a rotor and a stator.
  • the rotation-like adjusting device is arranged endlings on the camshaft and sits there so that an extension of the rotor protrudes from the adjusting device.
  • the extension extends to a camshaft bearing or it extends to the first or second camshaft bearing.
  • the hollow camshaft is undersized for the introduced via the adjusting torque. The hollow camshaft would bend by the introduced torque.
  • the hollow camshaft which is additionally stretched by the widening at least in the region of the cams, is strengthened by the other components located on it.
  • the hollow camshaft is reinforced by at least one component flanking the hollow camshaft.
  • An flanking component may be a valve or a rotor.
  • the hollow camshaft is designed together with the one or more other components for the maximum torque to be expected.
  • the internal combustion engine is very compact because the valve together with the adjusting device forms a compact structural unit on the hollow camshaft.
  • the valve has a hydraulic part which comprises a valve sleeve.
  • the hydraulic part extends to an inner wall of the hollow camshaft.
  • the adjusting device is designed according to the Aus collmngsformen described above.
  • the invention contributes to a material-saving, a very compact, optimally designed for the expected torque, valve train unit can be created, which creates an advantageous compared to the previously known valve trains very light valve train.
  • the camshaft can be strengthened by parallel, additional components enclosing the camshaft.
  • a camshaft 2 is shown - Fig. 1 - Which, for example.
  • a valve drive 3 is used for actuation of a combustion chamber of the internal combustion engine with medium-supplying valves -not shown-.
  • a valve drive 3 is used at one end 4 of the camshaft 2.
  • the adjusting device 5 is of hydraulic design and comprises a rotor 6 and a stator 7.
  • the rotor 6 is fixedly connected to the camshaft 2, and the stator 7 is mediated by a drive wheel 8 of a drive device mechanically via an endless member 8 '- chain, toothed belt - coupled with an unillustrated crankshaft.
  • endless member 8 may also be provided a gear transmission.
  • pressure chambers are formed, via which the adjustment of the rotor 6 or in a cylinder head 9 -.
  • Fig. 2 - The internal combustion engine 1 arranged camshaft 2 is accomplished.
  • an axial bore 10 which surrounds a shaft portion 11 of the camshaft 2.
  • the rotor 6 is provided with an over the width B of the adjusting device 5 projecting axial extension 12 which is made in one piece with the rotor 6; but it is also conceivable extension 12 and the rotor 6 represent as separate parts, which are summarized after their production into a single unit.
  • extension 12 the bore 10 is continued, and extension 12 and bore 10 form a shaft portion 11 of the camshaft 2 firmly surrounding hub thirteenth
  • the camshaft 2 enclosed by the hub 13 comprises a tubular body 14 on which cams 15 and 16 for actuating the valves are fixed by joining, d. H. the camshaft 2 is of built type - lower weight -.
  • the tubular body 14 and the cams 15 and 16 are independently produced workpieces, which are then assembled to the actual camshaft.
  • Adjacent to the adjusting device 5 is a pin-like insert 18 is inserted into an interior 17 of the tubular body 14, which is supported with a pin head 19 on an end face 20 of the tubular body 14.
  • the insert I8 is centrally drilled hollow and receives a valve spool - not shown -.
  • the valve spool serves to supply oil to the adjusting device 5.
  • camshaft bearings For supporting the camshaft 2, axially spaced camshaft bearings, such as the camshaft bearing 22, are provided, of which the camshaft bearing forming from the cylinder head 21 extends adjacent to the hub 13.
  • the camshaft bearing on the cylinder head 21 and the hub 13 together increase the stiffness.
  • the hub 13 protrudes with a free end 23 of the extension 10 into a bearing bore 24 of the camshaft bearing of the cylinder head 21, differently disengaged, the hub 13 rotates with an outer side 25 in the bearing bore 24.
  • An inner diameter D i and an outer diameter D a of Pipe body 14 of the camshaft 2 are substantially constant over the entire length of the said camshaft 2.
  • a tubular body 28 is provided, which is provided in a region of a hub 29 of a rotor 30 having an outer diameter D ak , which is smaller than an outer diameter D ag in the remaining region of the tubular body 28.
  • Die Inner diameter D il and D ill are adapted accordingly in this embodiment.
  • the wall thickness Wd of the tubular body 28, viewed over the longitudinal extent of the tubular body 28, be constant or else dimensioned differently, such that in the latter case the wall thickness Wd of Tube body 28 - and that of the tubular body 14 - is adapted to the loads of the camshaft 26.
  • camshaft bearings 31 and 32 are provided at an axial distance. Due to the diameter configuration D ak and D ag of the tubular body 28 and D at the hub 29, bearing bores 33 and 34 have a same diameter, which contributes to the simplification of the mechanical processing of these bearing bores 31 and 32.
  • the hub 13 - and also the hub 29 - are connected by means of positive engagement with the tubular body 14. But it is also possible to make the fixation of the hub 13 on the tubular body 14 by means of adhesion, for which a longitudinal compression bandage - axial compression, for example. Without heating the parts -, a transverse compression bandage - shrinking , by heating the hub or cooling the shaft or the like. Is suitable. It is conceivable beyond the hub 13 on the tubular body 14 cohesively, to be hot by welding, gluing, soldering or the like. To fix. In addition, is also suitable for fixing the hub 13 on the tubular body 14, a combination of different connection structures in terms of form and adhesion.
  • Fig. 5 shows a section of an internal combustion engine 38.
  • the camshaft 39 is part of the valve train 40.
  • an adjusting device 42 according to the invention is arranged.
  • the adjusting device 42 may on the outside of the camshaft 39 by a suitable connection technique, such as. B. a positive connection via toothed elements, a material connection via welding or a frictional connection via a press fit, produce a torque-transmitting connection.
  • the adjusting device 42 operates according to a pivot motor-type adjustment principle.
  • the adjusting device 42 may also be referred to as wellgelzellenversteller. For this reason, the adjusting device 42 has a rotor 43 and a stator 44.
  • Rotor 43 and stator 44 are coaxially arranged flat, disk-like components, wherein parallel to the rotor 43, a return spring 45, in particular in the form of a spiral spring, is arranged, which the rotor 43rd against the stator 44 in a forced position, when the hydraulic pressure between the rotor 43 and stator 44 in the hydraulic chambers is not sufficiently high work against the spring force of the return spring 45 in opposite directions.
  • a drive wheel 46 preferably formed in the stator 44.
  • the, z. B. as shown may be a chain drive.
  • the cutout of the internal combustion engine 38 is primarily the cylinder head 48.
  • the rotor 43 is designed such that a bore-like camshaft receptacle 49 is provided in the center, the coaxial coincident center with the stator 44, into which the one end 41 of the camshaft 39 is inserted can.
  • a chain drive cover 50 is stretched, inter alia, as protection against contact.
  • the chain drive cover 50 has a recess into which a valve 51 with the electromagnetic part 52 can be inserted and which can be attached via the valve flange 55 to the chain drive cover 50. From the outside, the electromagnetic part 52 can be electrically contacted via the plug 53.
  • the plunger 54 protrudes from the electromagnetic part 52 of the valve 51.
  • the plunger opens into a valve sleeve 56.
  • the valve sleeve 56 is preferably made of a particularly strong metal, for. B. steel.
  • a piston 58 of the valve 51 which can take a preferred position, in particular in the de-energized state by a piston biasing spring 57 runs.
  • the valve 51 has a length such that a shaft connection 59 of the camshaft 39 in the form of a hollow camshaft is supported by the valve 51 in an innermost manner. Approximately the same shaft portion is reformed on the outside of the camshaft 39 by the axial extension 60 of the rotor 43. As in FIG.
  • the axial extension 60 after FIG. 5 be traversed with oil guide channels 61, which ensure the supply of oil for the adjustment 42.
  • oil guide channel 61 may be designed such that oil for bearing lubrication of the camshaft bearing 68 of the hub 62 (FIG. FIG. 6 ) can be used.
  • the camshaft 39 is designed in its central shaft as a tubular body 63. At selected locations of the tubular body 63 are located, in particular by widening of the tubular body 63, fixed cams 64, 65. Between the individual cams 64, 65 more camshaft bearing 69 may be provided.
  • the hub 62 ( Fig.
  • the adjusting device 42 extends at least as far as the first camshaft bearing 68, preferably through the camshaft bearing 68.
  • the designed as a valve sleeve 56 for guiding the piston 58 extension which is pin-like, is widened in an end region so that the valve sleeve 56 comes to an end 67 of the tubular body 63 of the camshaft 39 in a locking manner to the stop.
  • the camshaft 39 is a hollow camshaft, the camshaft 39 provides an internal space 66 which is partially defined by the hydraulic parts of the valve 51 is filled in the end region of the camshaft 39.
  • end plates 70, 71 are arranged for the hydraulic closing of the hydraulic chambers between the stator 44 and the rotor 43.
  • the end plates 70, 71 may be provided with countersunk recesses 72, 73, in which the countersunk screws which brace the two end plates 70, 71 can save space.
  • the hydraulic part of the valve 51 is constructed in several parts with the centrally arranged piston 58.
  • the piston 58 as more clearly in FIG. 6 can be seen is held by the piston biasing spring 57 in a selected position of rest.
  • the piston 58, as in FIG. 5 can be seen is bordered by the valve sleeve 56.
  • As a further component for axial alignment and orientation of the piston 58 is a - in FIG.
  • the camshaft 39 is of a built-up manner.
  • the camshaft 39 is designed so thin-walled, in particular to promote the manufacturability of the built camshaft, that the introduced torque on the hollow cylindrical camshaft would not be transferable.
  • the tubular body 63 has an interior 66.
  • the interior 66 is partially filled.
  • the piston 58 is in the valve sleeve 56 arranged.
  • the valve sleeve 56 is supported in the region of a valve sleeve stop 75 on the tubular body 63 frontally.
  • the valve sleeve 56 is not designed solid.
  • valve sleeve 56 provides Wegsenhydraulikstoff Adjust 76, 77 for the supply and discharge of hydraulic fluid, such as oil to the adjusting device 42 (see FIG. 5 ). Between the valve sleeve 56 and piston 58 cavities and Absperr Schemee by webs 78, 79 and corresponding piston grooves 81, 82 realized.
  • the hydraulic behavior can be influenced as a function of the plunger position of the tappet 54 due to the electrical energization of the electromagnetic part 52 by means of corresponding overlaps, edge-edge controls and actuation edges.
  • the piston 58 has a piston central channel 80, which can serve as a P-channel or as a T-channel within the hollow camshaft 39.
  • a stator cover 83 can be arranged, which can be brought flush with the valve sleeve stop 75 to the outer diameter of the tubular body 63.
  • the hub 62 extends to a camshaft bearing parallel to Tubular body 63 in the form of an axial extension 60.
  • the tubular body 63 of the camshaft 39 is additionally and additionally supported by the valve 51.
  • the valve 51 is reinforced by the valve sleeve 56 along the end portion of the tubular body 63 to at least the first bearing.
  • valve sleeve 56 As in FIG. 6 shown, are partially hollow, because essential are the outer, cylindrically created support walls for the tubular body 63.
  • the valve sleeve 56 is, apart from the recesses, as the sleeve hydraulic center guide 76 and 77 an externally seen solid part, the center different Recesses, z. B. for the piston 58 may have.
  • the camshaft 39 is actually designed to be thin-walled for torques that are introduced via the chain at values of 500 N to 3,000 N, the load generated via the lever arm of approximately 40 mm can be placed on the bearing approximately 20 mm in diameter With the aid of the axial extension and the internally supporting valve sleeve, they can be cleverly guided into the camshaft bearing.
  • the camshaft is enclosed inside and / or outside walls and reinforced axially parallel.
  • the tubular or sleeve-shaped, hollow camshaft thus provides through the valve or through the rotor or through the rotor and valve, in particular valve sleeve, together a multi-layer, annulus or nikringausberichtden Nockenwellenend Scheme.
  • the valve sleeve can be made of steel. Less favorable would be a valve sleeve made of aluminum. The valve sleeve is dimensioned so that the inside running piston can be easily driven by the plunger.
  • valve train Fig. 5 41 End of the camshaft Fig. 5 42 adjustment Fig. 5 43 rotor Fig. 5 . Fig. 6 44 stator Fig. 5 45 Return spring Fig. 5 . Fig. 6 46 drive wheel Fig. 5 47 Endless drive, in particular as a chain drive Fig. 5 48 cylinder head Fig. 5 49 boring camshaft holder Fig. 5 50 Chain drive cover Fig. 5 51 Valve Fig. 5 52 Electromagnetic part Fig. 5 . Fig. 6 53 plug Fig. 5 54 tappet Fig. 5 . Fig. 6 55 valve flange Fig. 5 56 valve sleeve Fig. 5 . Fig. 6 57 Piston biasing spring Fig. 5 .
  • Fig. 6 58 piston Fig. 5 . Fig. 6 59 shaft section Fig. 5 60 Axial extension Fig. 5 . Fig. 6 61 Oil guide channel Fig. 6 62 hub Fig. 6 63 pipe body Fig. 5 . Fig. 6 64 cam Fig. 5 65 cam Fig. 5 66 inner space Fig. 5 . Fig. 6 67 Front side of the tubular body 63 Fig. 5 68 camshaft bearings Fig. 5 69 camshaft bearings Fig. 5 70 First face plate Fig. 5 71 Second face plate Fig. 5 72 counterbore Fig. 5 73 counterbore Fig. 5 74 guide sleeve Fig. 6 75 Valve sleeve stop Fig.

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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)
EP20080101750 2008-02-19 2008-02-19 Déphaseur d'arbre à cames de moteur à combustion interne Not-in-force EP2093388B1 (fr)

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EP20080101750 EP2093388B1 (fr) 2008-02-19 2008-02-19 Déphaseur d'arbre à cames de moteur à combustion interne

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20080101750 EP2093388B1 (fr) 2008-02-19 2008-02-19 Déphaseur d'arbre à cames de moteur à combustion interne

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EP2093388A1 true EP2093388A1 (fr) 2009-08-26
EP2093388B1 EP2093388B1 (fr) 2014-10-08

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2322769A1 (fr) * 2009-11-13 2011-05-18 Hydraulik-Ring GmbH Insert d'un arbre à cames
US8453616B2 (en) 2009-10-27 2013-06-04 Hilite Germany Gmbh Vane-type motor cam phaser with a friction disc and mounting method
US8505582B2 (en) 2010-05-03 2013-08-13 Hilite Germany Gmbh Hydraulic valve
US8662040B2 (en) 2010-04-10 2014-03-04 Hilite Germany Gmbh Oscillating-motor camshaft adjuster having a hydraulic valve
US8752514B2 (en) 2010-12-20 2014-06-17 Hilite Germany Gmbh Hydraulic valve for an oscillating motor adjuster
DE102015206699A1 (de) * 2015-04-15 2016-03-24 Schaeffler Technologies AG & Co. KG Nockenwellenversteller mit Hydraulikmittelleitkanälen in /an drehmomentübertragenden Formschlusselementen

Citations (6)

* Cited by examiner, † Cited by third party
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JP2000110526A (ja) * 1998-10-05 2000-04-18 Aisin Seiki Co Ltd 弁開閉時期制御装置
US6799544B1 (en) * 2003-05-29 2004-10-05 Delphi Technologies, Inc. Method and apparatus for actuating a cam phaser
US6814037B1 (en) * 2003-06-24 2004-11-09 Borgwarner Inc. Variable camshaft timing for internal combustion engine with actuator locking
DE10346444A1 (de) * 2003-10-07 2005-06-09 Daimlerchrysler Ag Nockenwellenversteller für eine Brennkraftmaschine mit Hydraulikmittelführungen
EP1696107A1 (fr) * 2005-02-23 2006-08-30 Mechadyne plc Système d'arbre à cames
US7228831B1 (en) * 2005-12-14 2007-06-12 Ford Global Technologies, Llc Camshaft and oil-controlled camshaft phaser for automotive engine

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Publication number Priority date Publication date Assignee Title
JP2000110526A (ja) * 1998-10-05 2000-04-18 Aisin Seiki Co Ltd 弁開閉時期制御装置
US6799544B1 (en) * 2003-05-29 2004-10-05 Delphi Technologies, Inc. Method and apparatus for actuating a cam phaser
US6814037B1 (en) * 2003-06-24 2004-11-09 Borgwarner Inc. Variable camshaft timing for internal combustion engine with actuator locking
DE10346444A1 (de) * 2003-10-07 2005-06-09 Daimlerchrysler Ag Nockenwellenversteller für eine Brennkraftmaschine mit Hydraulikmittelführungen
EP1696107A1 (fr) * 2005-02-23 2006-08-30 Mechadyne plc Système d'arbre à cames
US7228831B1 (en) * 2005-12-14 2007-06-12 Ford Global Technologies, Llc Camshaft and oil-controlled camshaft phaser for automotive engine

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8453616B2 (en) 2009-10-27 2013-06-04 Hilite Germany Gmbh Vane-type motor cam phaser with a friction disc and mounting method
US8794201B2 (en) 2009-10-27 2014-08-05 Hilite Germany Gmbh Vane-type motor cam phaser with a friction disc and method for mounting a friction disc on a rotor
EP2322769A1 (fr) * 2009-11-13 2011-05-18 Hydraulik-Ring GmbH Insert d'un arbre à cames
US8662040B2 (en) 2010-04-10 2014-03-04 Hilite Germany Gmbh Oscillating-motor camshaft adjuster having a hydraulic valve
US8505582B2 (en) 2010-05-03 2013-08-13 Hilite Germany Gmbh Hydraulic valve
US8752514B2 (en) 2010-12-20 2014-06-17 Hilite Germany Gmbh Hydraulic valve for an oscillating motor adjuster
DE102015206699A1 (de) * 2015-04-15 2016-03-24 Schaeffler Technologies AG & Co. KG Nockenwellenversteller mit Hydraulikmittelleitkanälen in /an drehmomentübertragenden Formschlusselementen

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