EP2093388A1 - Cam phaser for an internal combustion engine - Google Patents
Cam phaser for an internal combustion engine Download PDFInfo
- 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
- Authority
- 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
Links
Images
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.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Abstract
Description
Die Erfindung bezieht sich auf eine Verstelleinrichtung für eine Brennkraftmaschine, mit der die relative Lage einer Nockenwelle zur Beeinflussung von Steuerzeiten von Ventilen eines Ventiltriebs der Nockenwelle veränderbar ist nach dem Oberbegriff des Patentanspruchs 1.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.
Es ist eine Vorrichtung zum Verändern der Steuerzeiten von Gaswechselventilen einer Brennkraftmaschine bekannt,
Aus der
Die
Ein sich zur Nockenwelle hin auffächender Rotor ist auch in den Figuren der
Die Idee des Zentralventils in einem endseitigen Bereich einer Hohlnockenwelle, die von einem schwenkmotorartigen Nockenwellenversteller umgriffen wird, lässt sich wenigstens bis zu der Druckschrift
Der als Flügelrad bezeichnete Rotor gem.
Die noch unveröffentlichte Patentanmeldung der gleichen lnhaberin mit dem Amtsaktenzeichen
Aufgabe der Erfindung ist es, eine Verstelleinrichtung für eine Brennkraftmaschine zur Änderung der relativen Lage einer Nockenwelle zu schaffen, die so miteinander verbunden sind, dass bei freier Gestaltung der Nockenvvelle die auftretenden Belastungen gezielt aufgenommen werden.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.
Erfindungsgemäß wird diese Aufgabe durch die Merkmale des Patentanspruchs 1 gelöst. Weitere, die Erfindung ausgestaltende Merkmale sind in den Unteransprüchen enthalten.According to the invention, this object is solved by the features of patent claim 1. Further, the invention ausgestaltende features are included in the subclaims.
Die mit der Erfindung hauptsächlich erzielten Vorteile sind darin zu sehen, dass die Verstelleinrichtung sich hervorragend zur Verbindung mit einer Nockenwelle eignet, die weitgehend frei gestaltbar ist, d. h. die Nockenwelle kann auch gebauter Gattung sein. Dabei werden bspw. ein als Rohrkörper ausgeführter Schaft der Nockenwelle und die Nocken - zur Ventilbetätigung - in getrennten Fertigungsverfahren hergestellt und danach zu der eigentlichen Nockenwelle zusammengebaut. Der Rotor ist mit einer über die Breite der Verstelleinrichtung hinausragenden Verlängerung versehen, in der die Bohrung des Rotors fortgeführt ist. Diese Verlängerung ist zusammen mit dem Rotor als eine die Nockenwelle fest umschließende Nabe ausgeführt, wobei dieser feste Verbund zur Optimierung der Biegesteifigkeit der Nockenwelle beiträgt. Letzteres wird noch dadurch unterstützt, dass die Nabe des Rotors mit dem Nockenwellenlager gezielt zusammenarbeitet. Dabei ist günstig, dass die Verlängerung des Rotors in eine Lagerbohrung des Nockenwellenlagers hineinragt bzw. von besagter Lagerbohrung umgeben wird. Das Bauteil Rotor mit Verlängerung lässt sich auf einfache Weise unter Einsatz vertretbarer Mittel umsetzen. Schließlich eignen sich zur Fixierung der Nabe auf dem Rohrkörper formschlüssige, kraftschlüssige, stoffschlüssige Konstruktionen bzw. eine Kombination aus den besagten Konstruktionen.The advantages achieved by the invention are to be seen in the fact that the adjustment is ideal for connection to a camshaft, which is largely freely designable, ie the camshaft can also be built genus. In this case, for example, a designed as a tubular body shaft of the camshaft and the cams - for valve actuation - produced in separate manufacturing processes and then to the assembled actual camshaft. 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 latter is further supported by the fact that 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. Finally, to fix the hub on the tubular body positive, non-positive, cohesive constructions or a combination of the said constructions are suitable.
Die Verstelleinrichtung kann in einer Brennkraftmaschine bzw. Verbrennungskraftmaschine, insbesondere eines Ottomotortyps, verwendet werden. Eine entsprechende Brennkraftmaschine wird mit der Verstelleinrichtung ausgestattet. Die Brennkraftmaschine hat zumindest eine Kurbelwelle, zumindest eine Nockenwelle und zumindest eine entsprechende Verstelleinrichtung. Häufig kann eine entsprechende Brennkraftmaschine mehrere Nockenwellen halben. Häufig hat eine Brennkraftmaschine mit mehreren Nockenwellen auch mehrere Verstelleinrichtungen. Die Verstelleinrichtung dient dazu, die relative Lage einer Nockenwelle zu beeinflussen, insbesondere in Bezug auf eine in Antriebsverbindung stehende Antriebswelle, wie z. B. die Kurbelwelle. Die Nockenwelle hat eine geringe Biegesteifigkeit. Eine geringe Biegesteifigkeit ist zum Beispiel eine Biegesteifigkeit von 1,8 kNm2 (bei einer Wandstärke von ca. 2 mm eines typischen Automobilstahls für die Nockenwelle). Auch gilt im Sinne der vorliegenden Erfindung eine Biegesteifigkeit von 2 000 000 kNmm2 als gering. Die Biegesteifigkeit der Nockenwelle ist zu gering für die Übertragung des von außen auf die Verstelleinrichtung eingeleiteten Moments, insbesondere des Biegemoments. Die Nockenwelle alleine kann nicht freitragend das Stück zwischen Verstelleinrichtung und ihrem ersten oder sogar bis zu ihrem zweiten Lager überspannen. Die Nockenwelle ist mit einer geringeren als die notwendige Wanddicke für die Übertragung des eingeleiteten Biegemoments ausgelegt. Die Biegesteifigkeit der unverstärkten Nockenwelle ist geringer als für die Übertragung des Biegemoments aus dem Endlostrieb bzw. dem hieraus stammenden Drehmoments ausgelegt. Um das erforderliche Drehmoment zwischen NockenwellenversteIler und Nockenwelle übertragen zu können, sollte der Verband, insbesondere der Pressverband, über die Nockenwellenverstellerbreite hinaus mindestens bis zu einem Nockenwellenlager reichen, wenn die Nockenwelle selbst zu dünn ausgelegt ist. Die Verstelleinrichtung dient zur Beeinflussung von Steuerzeiten von Ventilen eines Ventiltriebs der Brennkraftmaschine und soll diese Steuerzeiten verändern können. Die Verstelleinrichtung hat einen Rotor. Der Rotor kann fest mit der Nockenwelle verbunden werden. Die Verstelleinrichtung hat einen Rotor und einen mit einer Antriebsvorrichtung zu gekoppelten Stator. Rotor und Stator arbeiten nach einem schwenkmotorartigen Prinzip. Sie werden auch gemeinsam als Flügelzellenversteller bezeichnet. Eine axiale Bohrung des Rotors dient zur Aufnahme eines Wellenabschnitts der Nockenwelle. Die Bohrung ist zur Aufnahme eines Teils der Nockenwelle bestimmt. Die axiale Bohrung des vom Stator umgebenen Rotors hat eine an wenigstens einer Seite über die Breite der Verstelleinrichtung hinausgehende axiale Verlängerung. Die Verlängerung ist axial fortgeführt. Der Rotor und die Verlängerung bilden eine die Nockenwelle umschließende Nabe. Die Nabe ist der Art gebildet, dass ein Nockenwellenlager mit der Nabe eine die Biegesteifigkeit der Nockenwelle erhöhende Längsverstärkung bildet. Als Längsverstärkung wird die zylindrische Verstärkungsrichtung entlang der Nockenwelle bezeichnet. Entlang der Längsachse der Nockenwelle, insbesondere im Endbereich der Nockenwelle, wird die Nockenwelle verstärkt und die Biegesteifigkeit erhöht.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. Often, a corresponding internal combustion engine can halve several camshafts. Frequently, an internal combustion engine with several camshafts and several adjustment. 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. B. the crankshaft. The camshaft has a low bending stiffness. For example, 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). Also, in the context of the present invention, 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. In order to transfer the required torque between the camshaft changer and the camshaft, 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 Flügelzellenversteller. 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.
Der zentrale Schaft, an dem sich die Nocken aufreihen, der Nockenwelle, die gebauter Art sein kann, ist mit besonders dünnen Wänden umgesetzt. Hierdurch lässt sich nach dem Aufschieben der Nocken auf den Schaft, der als Rohrkörper gestaltet ist, der Schaft zumindest im Bereich eines Nockens leichter, insbesondere mit geringerem Kraftaufwand, aufweiten und so den Nocken feststellen. Die Verformung der Nockenwelle zum Feststellen der Nocken kann hierbei mittels Dorn, Kegel oder einer hydraulischen. Vorrichtung erfolgen. Es muss ein geringerer Energieeintrag in das Material der Nockenwelle vorgenommen werden.The central shaft on which the cams line up, the camshaft, which can be built type, is implemented with particularly thin walls. As a result, after the cams are pushed onto the shaft, which is designed as a tubular body, 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.
Die axiale Verlängerung der Verstelleinrichtung kann nach einer Ausgestaltung aus einem Stück mit dem Rotor hergestellt sein.The axial extension of the adjusting device can be made according to an embodiment of one piece with the rotor.
Alternativ können die axiale Verlängerung der Verstellvorrichtung und der Rotor getrennt voneinander hergestellt sein und dann zu einer Baueinheit zusammengefasst sein.Alternatively, 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.
Die von der Nabe umschlossene Nockenwelle kann einen Rohrkörper umfassen.The camshaft enclosed by the hub may comprise a tubular body.
Die Brennkraftmaschine weist zumindest ein Nockenwellenlager auf. In der Regel sind zwei oder auch drei Nockenwellenlager vorgesehen. Häufig wird neben jedem Zylinder der Brennkraftmaschine ein Nockenwellenlager vorgesehen. Ein Nockenwellenlager für die Nockenwelle befindet sich benachbart der Nabe. Das Nockenwellenlager erstreckt sich dort. Das Nockenwellenlager und die Nabe arbeiten zur Erhöhung der Biegesteifigkeit der Nockenwelle zusammen.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.
Die Nabe ragt in eine Lagerbohrung des Nockenwellenlagers hinein. Die Nabe erstreckt sich somit bis zu dem Lager, insbesondere der Lagerbohrung, die sich im Inneren des Lagers befindet.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.
Der Rohrkörper der Nockenwelle hat über die Länge der Nockenwelle gesehen nach einer Ausgestaltung einen konstanten Außendurchmesser. Im Sinne der vorliegenden Erfindung wird auch ein solcher Außendurchmesser als konstant angesehen, der nur lokal begrenzt Eindellungen aufweist. Die Eindellungen dienen zum Beispiel für das Schrauberwerkzeug während der Montage, während der Rest der Nockenwelle gleich bleibend gestaltet ist.The tubular body of the camshaft has seen over the length of the camshaft according to one embodiment, a constant outer diameter. For the purposes of the present invention, such an 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.
In einer alternativen Ausgestaltung kann der Rohrkörper der Nockenwelle zwischen Rotor und Nockenwellenlager einen kleineren Außendurchmesser aufweisen als in einem übrigen Bereich des Rohrkörpers. Der übrige Bereich liegt jenseits der Verstelleinrichtung und er liegt jenseits des Nockenwellenlagers.In an alternative embodiment, 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.
Die Fixierung der Nabe auf dem Rohrkörper kann durch Formschluss erfolgen. Der Formschluss kann zum Beispiel durch eine Verzahnung umgesetzt sein.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.
Alternativ oder ergänzend kann die Fixierung der Nabe auf dem Rohrkörper durch Kraftschluss erfolgen. Der Kraftschluss kann z. B. durch einen Längspressverband oder durch einen Querpressverband hergestellt sein. Der Kraftschluss erfolgt also zum Beispiel über einen Pressverband.Alternatively or additionally, the fixation of the hub on the pipe body can be done by adhesion. The adhesion can z. B. be prepared by a Längspressverband or by a transverse compression bandage. The adhesion is thus for example via a press fit.
Wiederum alternativ oder in Ergänzung kann die Fixierung der Nabe auf dem Rohrkörper durch Stoffschluss erfolgen. Geeignete Techniken sind Schweißen, Kleben, Löten. Auch ähnliche stoffschlussbildende Herstellverfahren können gewählt werden.Again, alternatively or in addition, the 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.
Natürlich ist es möglich, die Fixierung der Nabe auf dem Rohrkörper durch eine Kombination aus Form- und Kraftschluss bzw. Form- und Stoffschluss bzw. Kraft- und Stoffschluss zu realisieren und durchzuführen.Of course, it is possible to realize the fixation of the hub on the tubular body by a combination of positive and non-positive or form and material connection or force and material connection and perform.
Auf einem dem Rotor benachbart anzuordnenden Ende des Rohrkörpers ist ein zapfenartiger Einsatz in einem Innenraum des besagten Rohrkörpers vorgesehen.On a rotor adjacent to be arranged end of the tubular body is a pin-like Insert provided in an interior of said tubular body.
Rotor und Stator sind flächige, platte Bauteile. Der Rotor und der Stator können in axialer Richtung der Nockenwelle gesehen von Schließplatten begrenzt werden.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.
Die Schließplatten können durch vorgefertigte Bauteile gebildet werden.The closing plates can be formed by prefabricated components.
Der Innendurchmesser und der Außendurchmesser des Rohrkörpers können über die axiale Länge des besagten Rohrkörpers gesehen im Wesentlichen konstant sein. Mit einer gleich bleibenden Wandstärke für den Rohrkörper kann operiert werden.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.
In einer alternativen Ausführung der Nockenwelle bzw des Teils der Nockenwelle, der den Rohrkörper bildet, kann zumindest der Innendurchmesser des Rohrkörpers über die axiale Länge des besagten Rohrkörpers gesehen gezielt an die auftretenden Belastungen der Nockenwelle angepasst sein. Die Wandstärke des Rohrkörpers ist auf die zu erwartenden Belastungen entlang seiner Erstreckung angepasst.In an alternative embodiment of the camshaft or of the part of the camshaft which forms the tubular body, 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.
Die schwenkmotorartige Verstelleinrichtung, zusammen mit einer geeigneten Nockenwelle, die insbesondere in ihrer Wandstärke reduziert ist, kann in einer Brennkraftmaschine so verbaut sein, dass die Nockenwelle auf Nockenwellenlagern geführt mit einer antreibenden Welle in Verbindung steht und durch die Verstelleinrichtung die relative Lage der Nockenwelle gegenüber der antreibenden Welle, insbesondere der Kurbelwelle, verstellt und verändert werden kann. Die Verstelleinrichtung führt rotatorische Verstellbewegungen durch.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.
Die Verstelleinrichtung ist für das Zusammenspiel mit einem Steuerventil, das vorzugsweise zentral, also mittig angeordnet ist, gestaltet. In die in die Verstelleinrichtung aufzunehmende Nockenwelle ist wiederum das cartridgeartige Steuerventil innwandig einzusetzen. Das cartridgeartige Steuerventil umfasst also eine Hülse, aus der das Ventil seinen Namen bezieht. Das Steuerventil verstärkt die als Hohlnockenwelle gestaltete Nockenwelle. Die Spitze des Steuerventils, insbesondere das Ende des Hydraulikteils, reicht bis zu einem Nockenwellenlager. Das Steuerventil ist in die Hohlnockenwelle einzusetzen. Die Hülse des hydraulischen Teils des Ventils unterstützt die vom Rotor eingeleitete Drehmomentenübertragung. Die Hülse ist wie ein einzusetzender Zapfen, also ein zapfenartiger Einsatz, gestaltet.The adjusting device is designed for the interaction with a control valve, which is preferably arranged centrally, ie centrally. In the camshaft to be accommodated in the adjusting device, in turn, 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.
Eine erfindungsgemäße Brennkraftmaschine mit einer erfindungsgemäßen Verstelleinrichtung hat zumindest eine Hohlnockenwelle. An der Hohlnockenwelle hängt zumindest die eine Verstelleinrichtung. Die Hohlnockenwelle ist rohrförmig. An der Hohlnockenwelle ist die schwenkmotorartige Verstelleinrichtung befestigt, die einen Rotor und einen Stator umfasst. Die rotationsartige Verstelleinrichtung ist endlings an der Nockenwelle angeordnet und sitzt dort so, dass ein Fortsatz des Rotors aus der Verstelleinrichtung hinausragt. Der Fortsatz reicht bis zu einem Nockenwellenlager bzw. er erstreckt sich bis zu dem ersten oder zweiten Nockenwellenlager. Die Hohlnockenwelle ist für das über die Verstelleinrichtung eingeleitete Drehmoment unterdimensioniert. Die Hohlnockenwelle würde durch das eingeleitete Drehmoment verbiegen. Die Hohlnockenwelle, die durch das Aufweiten zumindest im Bereich der Nocken noch zusätzlich gestreckt ist, wird durch die weiteren an ihr befindlichen Bauteile gestärkt. Die Hohlnockenwelle wird durch zumindest ein die Hohlnockenwelle flankierendes Bauteil verstärkt. Ein flankierendes Bauteil kann ein Ventil oder ein Rotor sein. Die Hohlnockenwelle ist zusammen mit dem oder die weiteren Bauteile für das maximal zu erwartende Drehmoment ausgelegt.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. On the hollow camshaft, 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.
Die Brennkraftmaschine ist sehr kompakt, weil das Ventil zusammen mit der Verstelleinrichtung eine kompakte Baueinheit an der Hohlnockenwelle bildet. Das Ventil hat einen eine Ventilhülse umfassenden Hydraulikteil. Der Hydraulikteil reicht bis zu einer Innenwand der Hohlnockenwelle. Die Verstelleinrichtung ist entsprechend der zuvor beschriebenen Ausfülmngsformen gestaltet.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 Ausfülmngsformen described above.
Die Erfindung trägt dazu bei, dass materialsparend eine sehr kompakte, für die zu erwartenden Drehmomente optimal ausgelegte, Ventiltriebeinheit geschaffen werden kann, die in vorteilhafter Weise einen im Vergleich zu den bisher bekannten Ventiltrieben sehr leichten Ventiltrieb schafft.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.
Die Erfindung kann auch an Hand der nachfolgenden Gleichungen leicht nachvollzogen werden, nämlich:The invention can also be easily understood by reference to the following equations, namely:
Die Biegesteifigkeit lässt sich aus dem Elastizitätsmodul E und dem Trägheitsmoment I berechnen nach B = E * I.The bending stiffness can be calculated from the elastic modulus E and the moment of inertia I to B = E * I.
Das Trägheitsmoment I bestimmt sich aus der kreisringförmigen Abmessung der parallel angeordneten Bauteile Ventilhülse, rohrförmige Nockenwelle und Rotornabe durch den jeweiligen Innenradius und den äußeren Radius. Sind die Bauteile aus ungefähr oder tatsächlich dem gleichen Material gefertigt, so kann mit der gleichen Masse gerechnet werden, zu I = 1/2 * m *(r2 2 + r1 2).The moment of inertia I is determined from the annular dimension of the components arranged in parallel valve sleeve, tubular camshaft and rotor hub by the respective inner radius and the outer radius. If the components are made of approximately or actually the same material, then the same mass can be expected, to I = 1/2 * m * (r 2 2 + r 1 2).
Ist die Masse der Nockenwelle zu gering, so kann durch parallel verlaufende, zusätzliche, die Nockenwelle einfassende Bauteile die Nockenwelle gestärkt werden.If the mass of the camshaft is too low, the camshaft can be strengthened by parallel, additional components enclosing the camshaft.
In der Zeichnung werden Ausführungsbeispiele der Erfindung gezeigt, die nachstehend näher beschrieben werden.In the drawings, embodiments of the invention are shown, which are described in more detail below.
Es zeigen
-
Fig. 1 einen Teillängsschnitt durch eine Brennkraftmaschine im Bereich einer Nockenwelle mit der Verstelleinrichtung nach der Erfindung, -
Fig. 2 eine Ansicht in Pfeilrichtung A derFig. 1 , -
Fig. 3 eine Ansicht entsprechendFig. 1 mit einer anderen Ausführungsform der Erfindung, -
Fig. 4 eine Einzelheit X derFig. 1 als Schrägansicht, -
Fig. 5 eine weitere Ausführungsform der Erfindung mit einem zentral angeordneten Ventil, -
Fig. 6 eine Einzelheit Y der Ausführungsform nachFig. 5 .
-
Fig. 1 a partial longitudinal section through an internal combustion engine in the region of a camshaft with the adjusting device according to the invention, -
Fig. 2 a view in the direction of arrow A ofFig. 1 . -
Fig. 3 a view accordinglyFig. 1 with another embodiment of the invention, -
Fig. 4 a detail X theFig. 1 as an oblique view, -
Fig. 5 a further embodiment of the invention with a centrally located valve, -
Fig. 6 a detail Y of the embodiment according toFig. 5 ,
Von einer Brennkraftmaschine 1 ist eine Nockenwelle 2 dargestellt -
Der Rotor 6 ist mit einer über die Breite B der Verstelleinrichtung 5 hinausragenden axialen Verlängerung 12 versehen, die aus einem Stück mit dem Rotor 6 hergestellt ist; denkbar ist aber auch Verlängerung 12 und den Rotor 6 als getrennte Teile darzustellen, die nach ihrer Fertigung zu einer Baueinheit zusammengefasst werden. In der Verlängerung 12 ist die Bohrung 10 fortgeführt, und Verlängerung 12 und Bohrung 10 bilden eine den Wellenabschnitt 11 der Nockenwelle 2 fest umschließende Nabe 13.The
Die von der Nabe 13 umschlossene Nockenwelle 2 umfasst einen Rohrkörper 14, auf dem Nocken 15 und 16 zur Betätigung der Ventile durch Fügen festgesetzt sind, d. h. die Nockenwelle 2 ist von gebauter Gattung - geringeres Gewicht -. Der Rohrkörper 14 und die Nocken 15 und 16 sind unabhängig voneinander produzierte Werkstücke, die dann zu der eigentlichen Nockenwelle zusammengebaut werden. Benachbart der Verstelleinrichtung 5 ist in einen Innenraum 17 des Rohrkörpers 14 ein zapfenartiger Einsatz 18 eingebracht, der sich mit einem Zapfenkopf 19 an einer Stirnseite 20 des Rohrkörpers 14 abstützt. Der Einsatz I8 ist zentrisch hohl gebohrt und nimmt einen Ventilschieber auf - nicht abgebildet -. Der Ventilschieber dient zur Ölversorgung der Verstelleinrichtung 5.The
Zur Lagerung der Nockenwelle 2 sind axial beabstandete Nockenwellenlager, wie das Nockenwellenlager 22, vorgesehen, wovon das sich aus dem Zylinderkopf 21 ausbildende Nockenwellenlager sich benachbart der Nabe 13 erstreckt. Um die Biegesteifigkeit der Nockenwelle 2 zusätzlich zu erhöhen, wirken das Nockenwellenlager am Zylinderkopf 21 und die Nabe 13 steifigkeitserhöhend zusammen. Hierzu ragt die Nabe 13 mit einem freien Ende 23 der Verlängerung 10 in eine Lagerbohrung 24 des Nockenwellenlagers des Zylinderkopfs 21 hinein, anders ausgerückt, die Nabe 13 rotiert mit einer Außenseite 25 in der Lagerbohrung 24. Ein Innendurchmesser Di und ein Außendurchmesser Da des Rohrkörpers 14 der Nockenwelle 2 sind über die gesamte Länge der besagten Nockenwelle 2 im Wesentlichen konstant.For supporting the
Bei einer Nockenwelle 26 -
Die Nabe 13 - und auch die Nabe 29 - sind unter Vermittlung von Formschluss mit dem Rohrkörper 14 verbunden. Hierzu dient eine Verzahnung 35 zwischen Nabe 13 und Rohrkörper 14. Es ist aber auch möglich, die Fixierung der Nabe 13 auf dem Rohrkörper 14 mittels Kraftschluss vorzunehmen, wofür sich ein Längspressverband - axiales Zusammenpressen bspw. ohne Erwärmung der Teile -, ein Querpressverband - Aufschrumpfen, und zwar durch Erwärmung der Nabe oder Abkühlung der Welle- oder dgl. eignet. Denkbar ist darüber hinaus die Nabe 13 auf dem Rohrkörper 14 stoffschlüssig, will heißen durch Schweißen, Kleben, Löten oder dgl. zu fixieren. Außerdem eignet sich ferner zur Fixierung der Nabe 13 auf dem Rohrkörper 14 eine Kombination von unterschiedlichen Verbindungskonstruktionen betreffend Form- und Kraftschluss.The hub 13 - and also the hub 29 - are connected by means of positive engagement with the
Schließlich werden der Rotor 6 und der Stator 7 in axialer Richtung der Nockenwelle 2, gesehen von Schließplatten 36 und 37, begrenzt, die als vorgefertigte Bauteile ausgeführt sind. Diese Schließplatten 36 und 37 werden unter Vermittlung von Schrauben - nicht gezeigtan der Verstelleinrichtung 5 in Lage gehalten.Finally, the
Weitere Einzelheiten des Bereichs Y der
Obwohl die Nockenwelle 39 eigentlich zu dünnwandig für Drehmomente, die mit Werten von 500 N bis 3.000 N über die Kette eingeleitet werden, ausgelegt ist, kann die über den Hebelarm von ca. 40 mm erzeugte Belastung auf das ca. 20 mm im Durchmesser große Lager unter Zurhilfenahme der axialen Verlängerung und der innen unterstützenden Ventilhülse geschickt bis in die Nockenwellenlager geführt werden. Wie in den dargestellten Schnittansichten zu sehen ist, wird die Nockenwelle inn- und/oder außenwandig eingefasst und achsparallel verstärkt. Die rohr- oder hülsenförmige, hohle Nockenwelle schafft so durch das Ventil oder durch den Rotor oder durch Rotor und Ventil, insbesondere Ventilhülse, zusammen einen mehrschichtigen, annulus- bzw. kreisringausfüllenden Nockenwellenendbereich. Es werden einzelne übereinander, sich gegenseitig verstärkende Lagen gebildet, die insgesamt einen so dicken Nockenwellenendbereich schaffen, dass über das Ende bis in eines der ersten Nockenwellenlager ein hohes, für die Nockenwelle alleine zu großes Drehmoment übertragbar ist. Eine erfindungsgemäße Brennkraftmaschine kommt ohne zusätzliche, am Zylinderkopf anzuordnende Stützbrille aus. Die bisher übliche seitliche Verlängerung des ersten Nockenwellenlagers durch eine zusätzliche Brille zur Abstützung kann somit entfallen. Die axiale Verlängerung des Rotors sorgt folglich für weitere Materialersparnis. Die Ventilhülse kann aus Stahl gefertigt sein. Weniger günstig wäre eine Ventilhülse aus Aluminium. Die Ventilhülse ist so bemessen, dass der innen laufende Kolben leichtgängig von dem Stößel angetrieben werden kann.Although the
Claims (11)
dadurch gekennzeichnet, dass
die axiale Bohrung (10) des vom Stator (7) umgebenen Rotors (6; 30) in wenigstens einer über die Breite der Verstelleinrichtung (5; 27) hinausgehenden axialen Verlängerung (12) fortgeführt ist und dass der Rotor (6; 30) und die Verlängerung (12) eine die Nockenwelle (2; 26) umschließende Nabe (13; 29) der Art bilden, dass ein Nockenwellenlager (21; 31, 32) mit der Nabe (13; 39) eine die Biegesteifigkeit der Nockenwelle (2; 26) erhöhende Längsverstärkung bildet.Adjusting device (5, 27) for an internal combustion engine (1), with which the relative position of a camshaft (2; 26), which has a low bending stiffness, to influence the timing of valves of a valve train (3) of the internal combustion engine (1) which adjusting device (5, 27) comprises a rotor (6; 30) to be fixedly connected to the camshaft (2; 26) and a stator (7) to be coupled to a drive device, wherein an axial bore (10) of the rotor (10) 6) for receiving a shaft portion (11) of the camshaft (2; 26) is determined,
characterized in that
the axial bore (10) of the rotor (6; 30) surrounded by the stator (7) is continued in at least one axial extension (12) extending beyond the width of the adjusting device (5; 27) and in that the rotor (6; 30) and the extension (12) forms a hub (13; 29) enclosing the camshaft (2; 26) such that a camshaft bearing (21; 31,32) forms with the hub (13; 39) a flexural rigidity of the camshaft (2; 26) forming increasing longitudinal reinforcement.
dadurch gekennzeichnet, dass
die Hohlnockenwelle (2, 26, 39) für das über die Verstelleinrichtung (5, 42) eingeleitete Drehmoment unterdimensioniert ist, jedoch die Hohlnockenwelle (2, 26, 39) durch zumindest ein die Hohlnockenwelle (2, 26, 39) flankierendes Bauteil wie ein Ventil (51) oder der Rotor (6, 43) für das maximal zu erwartende Drehmoment ausgelegt ist.Internal combustion engine (1, 38) with at least one adjusting device (5, 42) and a tubular hollow camshaft (2, 26, 39) on which the pivoting motor-like adjusting device (5, 42), a rotor (6, 43) and a stator ( 7, 44) arranged endlings (41) arranged so that an extension (29) of the rotor (6, 43) from the adjusting device (5, 42) protruding to a camshaft bearing (31, 68),
characterized in that
the hollow camshaft (2, 26, 39) is underdimensioned for the torque introduced via the adjusting device (5, 42), but the hollow camshaft (2, 26, 39) is supported by at least one component flanking the hollow camshaft (2, 26, 39) Valve (51) or the rotor (6, 43) is designed for the maximum torque to be expected.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP20080101750 EP2093388B1 (en) | 2008-02-19 | 2008-02-19 | Cam phaser for an internal combustion engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP20080101750 EP2093388B1 (en) | 2008-02-19 | 2008-02-19 | Cam phaser for an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2093388A1 true EP2093388A1 (en) | 2009-08-26 |
EP2093388B1 EP2093388B1 (en) | 2014-10-08 |
Family
ID=39596465
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20080101750 Not-in-force EP2093388B1 (en) | 2008-02-19 | 2008-02-19 | Cam phaser for an internal combustion engine |
Country Status (1)
Country | Link |
---|---|
EP (1) | EP2093388B1 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2322769A1 (en) * | 2009-11-13 | 2011-05-18 | Hydraulik-Ring GmbH | Cartridge for a cam shaft |
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 (en) * | 2015-04-15 | 2016-03-24 | Schaeffler Technologies AG & Co. KG | Camshaft adjuster with hydraulic fluid conduits in / at torque-transmitting interlocking elements |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000110526A (en) * | 1998-10-05 | 2000-04-18 | Aisin Seiki Co Ltd | Valve opening and closing timing control device |
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 (en) * | 2003-10-07 | 2005-06-09 | Daimlerchrysler Ag | Camshaft displacement device for internal combustion engines, has inner body of actuator and camshaft bearing integrated into single part |
EP1696107A1 (en) * | 2005-02-23 | 2006-08-30 | Mechadyne plc | Camshaft assembly |
US7228831B1 (en) * | 2005-12-14 | 2007-06-12 | Ford Global Technologies, Llc | Camshaft and oil-controlled camshaft phaser for automotive engine |
-
2008
- 2008-02-19 EP EP20080101750 patent/EP2093388B1/en not_active Not-in-force
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2000110526A (en) * | 1998-10-05 | 2000-04-18 | Aisin Seiki Co Ltd | Valve opening and closing timing control device |
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 (en) * | 2003-10-07 | 2005-06-09 | Daimlerchrysler Ag | Camshaft displacement device for internal combustion engines, has inner body of actuator and camshaft bearing integrated into single part |
EP1696107A1 (en) * | 2005-02-23 | 2006-08-30 | Mechadyne plc | Camshaft assembly |
US7228831B1 (en) * | 2005-12-14 | 2007-06-12 | Ford Global Technologies, Llc | Camshaft and oil-controlled camshaft phaser for automotive engine |
Cited By (7)
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 (en) * | 2009-11-13 | 2011-05-18 | Hydraulik-Ring GmbH | Cartridge for a cam shaft |
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 (en) * | 2015-04-15 | 2016-03-24 | Schaeffler Technologies AG & Co. KG | Camshaft adjuster with hydraulic fluid conduits in / at torque-transmitting interlocking elements |
Also Published As
Publication number | Publication date |
---|---|
EP2093388B1 (en) | 2014-10-08 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1860286B1 (en) | Camshaft | |
EP0335083B1 (en) | Device for the relative angular displacement between two geared shafts | |
EP0469332B1 (en) | Method for changing valve timing in an internal combustion engine | |
DE4218082C2 (en) | Device for continuously adjusting the angle between two shafts connected in the drive | |
DE102006039371A1 (en) | Adjusting device for internal combustion engine, has rotor, which is firmly connected with camshaft, where stator is coupled with drive device, and axial bore of rotor, takes shaft section of camshaft, where stator surrounds axial bore | |
DE4218078C5 (en) | Device for automatic, continuous angle adjustment between two shafts in drive connection | |
EP2286067B1 (en) | Adjustable camshaft arrangement | |
DE102011076652B4 (en) | Device for adjusting the relative angular position of nested camshafts | |
EP2093388B1 (en) | Cam phaser for an internal combustion engine | |
EP1573176B1 (en) | Internal combustion engine comprising a device for hydraulically adjusting the angle of rotation of the camshaft thereof relative to the crankshaft thereof, and a vacuum pump for a servo consumer, especially a brake booster | |
DE102006007651A1 (en) | Camshaft adjuster with a superposition gearbox | |
DE102004026863A1 (en) | Camshaft adjuster for internal combustion engines has output part fixed on camshaft through force-locking engagement secured for example through thermal shrink fitting | |
DE10346448A1 (en) | Camshaft displacement device for internal combustion engines, has module incorporated into camshaft for directing hydraulic fluid between camshaft and actuator valve | |
WO2011042391A1 (en) | Camshaft arrangement | |
WO2008009548A1 (en) | Group of multiple camshafts with camshaft adjusters | |
EP0469334A1 (en) | Method for changing the angular position of shafts for an internal combustion engine | |
DE102009042228A1 (en) | Device for changing the relative angular position of a camshaft relative to a crankshaft of an internal combustion engine | |
DE102006012348A1 (en) | Crankshaft`s phasing adjusting device e.g. hydraulic phase controller, for use in internal combustion engine, has locking unit, which locks and unlocks fixed unit and covers with camshaft and inner body, and enables flow of hydraulic medium | |
DE102011077020A1 (en) | Camshaft adjusting device for adjusting valve timings of gas shuttle valves of e.g. diesel engine, has camshaft connected with adjuster via screw connection that is made by screw element, where element includes two threaded sections | |
DE102006052998A1 (en) | Adjusting device i.e. variable adjusting device, for combustion chamber of internal-combustion engine, has gear wheel and adjuster housing, which are made of e.g. aluminum alloy having high silicon portion | |
DE10346447B4 (en) | Method for fastening a camshaft adjuster to a camshaft of an internal combustion engine | |
DE102009022868B4 (en) | Vane phaser | |
DE102004019190A1 (en) | Variable phase camshaft drive for IC engine is fitted onto the camshaft by a circular wedge lock axial compactness | |
DE19850947A1 (en) | Device for controlling opening and closing times of gas exchange valves of internal combustion engine comprises at least one drive device, at least one camshaft with at least one cam for operating at least one valve | |
EP2536925B1 (en) | Device for variable adjustment of the control times of gas exchange valves of an internal combustion engine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20081004 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL BA MK RS |
|
17Q | First examination report despatched |
Effective date: 20091103 |
|
AKX | Designation fees paid |
Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: HOFER MECHATRONIK GMBH |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20140522 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MT NL NO PL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 690758 Country of ref document: AT Kind code of ref document: T Effective date: 20141015 Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502008012292 Country of ref document: DE Effective date: 20141113 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: VDEP Effective date: 20141008 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150108 Ref country code: IS Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150208 Ref country code: LT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150209 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LV Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150109 Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 Ref country code: HR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 Ref country code: PL Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150228 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502008012292 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 Ref country code: DK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 |
|
26N | No opposition filed |
Effective date: 20150709 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20150219 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20150219 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150228 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150228 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20151030 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150219 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150219 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150302 Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 690758 Country of ref document: AT Kind code of ref document: T Effective date: 20150219 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150219 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20080219 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20141008 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20190222 Year of fee payment: 12 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 502008012292 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200901 |