EP1443184A1 - Variabler nockenwellentrieb - Google Patents
Variabler nockenwellentrieb Download PDFInfo
- Publication number
- EP1443184A1 EP1443184A1 EP03100179A EP03100179A EP1443184A1 EP 1443184 A1 EP1443184 A1 EP 1443184A1 EP 03100179 A EP03100179 A EP 03100179A EP 03100179 A EP03100179 A EP 03100179A EP 1443184 A1 EP1443184 A1 EP 1443184A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- camshaft
- crankshaft
- coupled
- drive
- internal combustion
- 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
- F01L1/34409—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 by torque-responsive means
Definitions
- the invention relates to a variable camshaft drive for an internal combustion engine, which is coupled to the crankshaft of the internal combustion engine Drive element and at least one camshaft coupled to the drive element for controlling the valves of the internal combustion engine. Furthermore concerns the invention a method for variable control of the valve opening times an internal combustion engine, the valves being actuated by a camshaft, which is driven in rotation by the crankshaft of the internal combustion engine.
- Camshaft drives are used to control the intake and exhaust valves of an internal combustion engine to open and close according to the rotation of the crankshaft, to suck in combustion air and exhaust gases Taxes.
- variable camshaft drives In which the opening and closing times of the valves - as well as the valve lift if necessary - have it changed relative to a basic setting. Typically this is achieved by mechanisms that have a limited phase shift allow between the rotations of the crankshaft and the camshaft.
- the Such a variable camshaft is usually adjusted proportionally elaborate actuators that are active, d. H. with external energy, be operated.
- variable camshaft drive for an internal combustion engine contains a drive element coupled to the crankshaft of the internal combustion engine and at least one camshaft coupled to this drive element to control the valves of the internal combustion engine.
- the drive element can For example, a gearwheel sitting on the crankshaft, which over a V-belt or toothed belt, a link chain, or with other gears the camshaft is coupled.
- the camshaft drive is characterized by that the drive element and the camshaft (among other things) via a passive mechanical coupling member are interconnected such that the Camshaft can oscillate rotationally relative to the crankshaft.
- camshaft drives see the most inflexible coupling between the crankshaft and the camshaft driven thereby, in which the Camshaft only within the inevitable tolerance limits of the mechanisms and materials can change their position relative to the crankshaft, whereby this position variability is generally well below ⁇ 1 ° of the camshaft angle lies.
- the camshaft drive according to the invention targeted a "soft" coupling link in the power transmission chain between the crankshaft or drive element and camshaft inserted, which is a significant rotary relative rotation (typically by ⁇ 1 ° to ⁇ 50 °) between Camshaft and crankshaft allowed.
- variable camshaft controls Different from known variable camshaft controls is the relative adjustment between the camshaft and crankshaft not specified from outside and caused by active mechanisms, so that it remains unchanged without operating these mechanisms, but the relative rotation between the camshaft and crankshaft occurs solely on the basis of the passive mechanical properties of the intermediate Coupling member.
- the input / output behavior of the coupling element can therefore take place virtually automatically Variation of the opening behavior of the camshaft take place, which leads to an improved Operation of the internal combustion engine leads.
- one of the Speed of the crankshaft dependent relative oscillation between the camshaft and crankshaft which is a beneficial change (early adjustment and / or late adjustment) of the opening and closing times of the valves.
- a variable camshaft drive can be very simple and therefore can be realized inexpensively and robustly.
- At least the camshaft another passive mechanical coupling element coupled. hereby can have an additional influence on the movement of the camshaft in order to achieve desired behavior in this way.
- the further Coupling member can in particular at the non-driven end of the camshaft be arranged to introduce a more even force into the camshaft cause.
- a coupling member have at least one elasticity between its entrance and its output for the movements or forces to be coupled acts.
- Such elasticity causes that when the output is held (or Input) of the coupling member against movement of the input (output) an increasing elastic restoring force is possible.
- the Elasticity kinetic energy temporarily stored and thus at the entrance evenly supplied energy at the output released non-uniformly again become.
- the coupling members can have at least one inert mass between them have their input and their output, which on the transmitted Movement takes part and influences this through its inertia.
- the coupling elements can have at least one between their input and their output have acting viscosity, through which a transferred Movement under energy consumption is damped.
- Components acting between the input and the output of a coupling element Components can also have linear or non-linear behavior. Such characteristics can be, for example, those described above Components (elasticity, inert mass, damping) can be achieved.
- the mechanical parameters of the coupling member can be changed externally.
- the characteristic of the coupling member, for example, by the engine control can be set so that a desired valve control is effected.
- an actuator the position of the camshaft is actively influenced from outside
- there is only a change in parameters from the outside while the System otherwise remains autonomous.
- the camshaft drive preferably has (at least) two camshafts, which each have their own passive mechanical coupling links with the drive element the crankshaft are coupled.
- the coupling members are advantageously interpreted differently, so that this is a different Show input / output behavior.
- One of the camshafts can, for. B. with the input valves and the other camshaft with the output valves of the Internal combustion engine to be connected.
- the opening behavior of these valves leaves then corresponding to the coupling members on the respective camshafts vary separately. For example, an early adjustment of the inlet valves take place with simultaneous late adjustment of the exhaust valves.
- the invention further relates to a method for variable control of the valve opening times an internal combustion engine, the valves being driven by a camshaft are actuated, which in turn rotating by the crankshaft of the internal combustion engine is driven.
- the method is characterized in that the crankshaft and the camshaft are passively coupled such that the camshaft oscillates rotationally relative to the crankshaft.
- the rotary Oscillation of the camshaft relative to the crankshaft takes place depending on the speed. D. that is, the oscillation is dependent on its amplitude and / or phase position of the respective speed of the crankshaft. In this way - in particular at low engine speeds - a different opening behavior of the valves than can be achieved at higher engine speeds.
- the camshaft drive includes a driven by the crankshaft 1 of the internal combustion engine (not shown) Drive element 2, which is z. B. a mounted on the crankshaft Gear can act.
- the drive element 2 is via a toothed belt 3 coupled with a gear 4.
- the gear 4 is in turn via a coupling member A coupled to the camshaft 5, the camshaft 5 being known Way eccentric cams 6 for moving the valves (not shown) the internal combustion engine.
- a second camshaft 5 ' coupled to the gear 4 by cams 6 'via a further coupling member A'.
- the first camshaft 5 can, for. B. the intake valves and the second camshaft 5 'control the exhaust valves.
- the coupling member is A, A 'designed so that it is an "inflexible” or rigid or functional clear coupling between the gear 4 and the camshaft 5, 5 'causes.
- the coupling member in the prior art can be simply as continuous solid shaft be formed. If necessary, in known Systems with variable camshaft control also from the outside controllable active actuators change the phase position between the Input and output of the coupling element are effected. Without active External intervention, however, this phase shift remains constant, so that at conventional camshaft drives a fixed functional relationship between the angle of the crankshaft and the resulting angle of Camshaft exists.
- FIG. 2 schematically shows the relationship between the time profile of the crankshaft angle ⁇ K and the associated time profile of the camshaft angle ⁇ N.
- the crankshaft angle ⁇ k is linear over time t. In the case of conventional camshaft drives, this would also result in a linear course of the camshaft angle ⁇ N , ie rotation of the camshaft at a constant speed.
- the curves of the crankshaft angle ⁇ K and the camshaft angle ⁇ N would differ only in the slope (by a factor of 2) and in an offset due to a predetermined transmission ratio of the camshaft drive.
- the ripple looks different at low speeds n I and high speeds n h .
- the phase and amplitude of the rotational oscillation of the camshaft can be freely selected in a wide range by appropriately setting the parameters of the coupling element. In this way it can be achieved that the valves open at low speeds only for a short time and with a small overlap in order to bring about a low engine torque. At high speeds, however, longer opening times and / or a larger overlap of opening times of intake and exhaust valves can be created to provide the desired engine output.
- Coupling members B, B 'pointed out which also to the camshaft 5, 5 '(but not in the power transmission path between crankshaft 1 and camshaft 5, 5 ') and due to its passive mechanical properties Influence on the movement behavior of the camshaft 5, 5 '.
- the coupling links A and A '(also B and B') on the various camshafts 5, 5 ' can be designed differently in order to have a different speed-dependent Behavior associated valves to generate.
- FIGS. 3 to 5 show different implementation options for the coupling elements shown, which can be combined with each other as desired.
- an inertial mass M 1 is coupled to the gear 4.
- the inertial mass M 1 is further coupled to the camshaft 5, 5 'via an elasticity C 1 (e.g. a torsion spring or a torsion bar).
- the realization of the further coupling member B, B 'according to FIG. 5 consists of an elasticity C 3 (e.g. a torsion spring or a torsion bar) which connects the camshafts 5, 5' and an otherwise freely oscillating inertial mass M 3 .
- C 3 e.g. a torsion spring or a torsion bar
- the parameters of the coupling elements A, A ', B, B', ie in the examples of FIGS. 3 to 5 by specifying the masses M 1 , M 2 and M 3 and the elasticity constants of C 1 , C 2 , C 2 'and C 3 , the natural frequencies and the eigenvalue behavior of the rotatingly oscillating camshaft 5, 5' can be determined in a desired manner by the designer.
- the coupling elements than shown in FIGS. 3 to 5 can also be provided, in particular the inclusion of dampers is possible.
- the arrangement of the coupling elements A, A ', B, B' shown in FIG. 1 is only one of several possibilities.
- camshaft drive can start from a basic length the valve opening changes when the engine is idling cause a maximum length at a nominal speed.
- the coupling elements A, A ', B, B' can be both linear and non-linear Components (elasticities, dampers, etc.) included. Furthermore, these components be “active” or “passive”, with “passive” components by definition, do not change their parameters while the parameters are "more active” Components can be activated and / or changed from outside or inside. Examples of passive components are steel springs, air springs or rubber elements. Examples of active components are dampers with an electroactive Change in damping coefficient, air springs with variable pressure and Eddy current brakes.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
- Fig. 1
- schematisch die Komponenten eines erfindungsgemäßen variablen Nockenwellentriebs;
- Fig. 2
- schematisch den Verlauf des Kurbelwellenwinkels αK und des zugehörigen Nockenwellenwinkels αN über der Zeit t bei verschiedenen Drehzahlen;
- Fig. 3
- die Ausgestaltung eines Kopplungsgliedes zwischen Kurbelwelle und Nockenwelle mit einer Serienschaltung einer trägen Masse und einer Elastizität;
- Fig. 4
- die Ausgestaltung eines Kopplungsgliedes zwischen Kurbelwelle und Nockenwelle mit der Serienschaltung einer Elastizität, einer trägen Masse und einer weiteren Elastizität, und
- Fig. 5
- die Ausgestaltung eines zusätzlich an der Nockenwelle angreifenden Kopplungsgliedes mit der Serienschaltung einer Elastizität und einer Masse.
Claims (10)
- Variabler Nockenwellentrieb für eine Brennkraftmaschine, enthaltenda) ein mit der Kurbelwelle (1) der Brennkraftmaschine gekoppeltes Antriebselement (2);b) mindestens eine mit dem Antriebselement (2) gekoppelte Nockenwelle (5, 5') zur Steuerung der Ventile der Brennkraft-
das Antriebselement (2) und die Nockenwelle (5, 5') über ein passives mechanisches Kopplungsglied (A, A') derart miteinander verbunden sind, daß die Nockenwelle (5, 5') relativ zur Kurbelwelle rotatorisch oszillieren kann. - Nockenwellentrieb nach Anspruch 1,
dadurch gekennzeichnet, daß
an die Nockenwelle (5, 5') ein zweites passives mechanisches Kopplungsglied (B, B') angekoppelt ist. - Nockenwellentrieb nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß
das Kopplungsglied (A, A', B, B') mindestens eine zwischen seinem Eingang und seinem Ausgang wirkende Elastizität (C1, C2, C2', C3) aufweist. - Nockenwellentrieb nach mindestens einem der Ansprüche 1 bis 3,
dadurch gekennzeichnet, daß
das Kopplungsglied (A, A', B, B') mindestens eine zwischen seinem Eingang und seinem Ausgang wirkende träge Masse (M1, M2, M3) aufweist. - Nockenwellentrieb nach mindestens einem der Ansprüche 1 bis 4,
dadurch gekennzeichnet, daß
das Kopplungsglied (A, A', B, B') mindestens eine zwischen seinem Eingang und seinem Ausgang wirkende Viskosität aufweist. - Nockenwellentrieb nach mindestens einem der Ansprüche 1 bis 5,
dadurch gekennzeichnet, daß
die zwischen dem Eingang und dem Ausgang des Kopplungsgliedes (A, A', B, B') wirkenden Komponenten (C1, C2, C2', C3, M1, M2, M3) linear und/oder nicht linear sind. - Nockenwellentrieb nach mindestens einem der Ansprüche 1 bis 6,
dadurch gekennzeichnet, daß
die mechanischen Parameter des Kopplungsgliedes (A, A', B, B') extern veränderbar sind. - Nockenwellentrieb nach mindestens einem der Ansprüche 1 bis 7,
dadurch gekennzeichnet, daß
dieser zwei Nockenwellen (5, 5') enthält, welche jeweils über passive mechanische Kopplungsglieder (A, A') von vorzugsweise unterschiedlicher Auslegung mit dem Antriebselement (2) gekoppelt sind. - Verfahren zur variablen Steuerung der Ventilöffnungszeiten einer Brennkraftmaschine, wobei die Ventile von einer Nockenwelle (5, 5') betätigt werden, die von der Kurbelwelle (1) der Brennkraftmaschine rotierend angetrieben wird,
dadurch gekennzeichnet, daß
die Kurbelwelle (1) und die Nockenwelle (5, 5') derart passiv gekoppelt werden, daß die Nockenwelle (5, 5') relativ zur Kurbelwelle (1) rotatorisch oszilliert. - Verfahren nach Anspruch 9,
dadurch gekennzeichnet, daß
die Nockenwelle (5, 5') drehzahlabhängig rotatorisch oszilliert.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE50311827T DE50311827D1 (de) | 2003-01-29 | 2003-01-29 | Variabler nockenwellentrieb |
EP03100179A EP1443184B1 (de) | 2003-01-29 | 2003-01-29 | Variabler nockenwellentrieb |
JP2004019625A JP2004340125A (ja) | 2003-01-29 | 2004-01-28 | 可変カムシャフト機構及び開弁時期の可変制御方法 |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP03100179A EP1443184B1 (de) | 2003-01-29 | 2003-01-29 | Variabler nockenwellentrieb |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1443184A1 true EP1443184A1 (de) | 2004-08-04 |
EP1443184B1 EP1443184B1 (de) | 2009-08-19 |
Family
ID=32605387
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03100179A Expired - Fee Related EP1443184B1 (de) | 2003-01-29 | 2003-01-29 | Variabler nockenwellentrieb |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP1443184B1 (de) |
JP (1) | JP2004340125A (de) |
DE (1) | DE50311827D1 (de) |
Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1095017A (en) * | 1965-04-28 | 1967-12-13 | John Robert Cribbs | Automatic variable valve timing device for internal combustion engines |
DE1980468U (de) | 1967-12-16 | 1968-03-07 | Basf Ag | Radkoerper aus thermoplastischem kunststoff. |
US4177773A (en) * | 1977-12-27 | 1979-12-11 | Cribbs John R | Damped automatic variable valve timing device for internal combustion engines |
JPS5969549A (ja) * | 1982-10-14 | 1984-04-19 | Honda Motor Co Ltd | 内燃機関のカムシヤフト振動抑制装置 |
WO1991005941A1 (en) | 1989-10-13 | 1991-05-02 | Rover Group Limited | An internal combustion engine camshaft drive mechanism |
US5235939A (en) * | 1992-11-05 | 1993-08-17 | Ford Motor Company | Automotive engine torsional pulse enhancer |
DE29708574U1 (de) * | 1996-05-29 | 1997-08-21 | Palsis Schwingungstechnik GmbH & Co., 59227 Ahlen | Bauteil zur Übertragung von Drehbewegungen und zur Drehschwingungsdämpfung |
DE19752194A1 (de) | 1997-11-25 | 1999-05-27 | Hyundai Motor Co Ltd | Verfahren und System zum Messen der Interferenz zwischen einem Ventil und einem Kolben eines Verbrennungsmotors |
DE19815270A1 (de) | 1998-04-04 | 1999-10-07 | Volkswagen Ag | Nockenwellentrieb einer Brennkraftmaschine |
US20020128099A1 (en) | 1999-04-29 | 2002-09-12 | Gerhard Winklhofer | Method and device for reducing vibrations of a control chain in a camshaft drive of an internal combustion engine |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19520508A1 (de) * | 1995-06-03 | 1996-12-05 | Audi Ag | Umschlingungstrieb |
-
2003
- 2003-01-29 DE DE50311827T patent/DE50311827D1/de not_active Expired - Lifetime
- 2003-01-29 EP EP03100179A patent/EP1443184B1/de not_active Expired - Fee Related
-
2004
- 2004-01-28 JP JP2004019625A patent/JP2004340125A/ja active Pending
Patent Citations (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB1095017A (en) * | 1965-04-28 | 1967-12-13 | John Robert Cribbs | Automatic variable valve timing device for internal combustion engines |
DE1980468U (de) | 1967-12-16 | 1968-03-07 | Basf Ag | Radkoerper aus thermoplastischem kunststoff. |
US4177773A (en) * | 1977-12-27 | 1979-12-11 | Cribbs John R | Damped automatic variable valve timing device for internal combustion engines |
JPS5969549A (ja) * | 1982-10-14 | 1984-04-19 | Honda Motor Co Ltd | 内燃機関のカムシヤフト振動抑制装置 |
WO1991005941A1 (en) | 1989-10-13 | 1991-05-02 | Rover Group Limited | An internal combustion engine camshaft drive mechanism |
US5235939A (en) * | 1992-11-05 | 1993-08-17 | Ford Motor Company | Automotive engine torsional pulse enhancer |
DE29708574U1 (de) * | 1996-05-29 | 1997-08-21 | Palsis Schwingungstechnik GmbH & Co., 59227 Ahlen | Bauteil zur Übertragung von Drehbewegungen und zur Drehschwingungsdämpfung |
DE19752194A1 (de) | 1997-11-25 | 1999-05-27 | Hyundai Motor Co Ltd | Verfahren und System zum Messen der Interferenz zwischen einem Ventil und einem Kolben eines Verbrennungsmotors |
DE19815270A1 (de) | 1998-04-04 | 1999-10-07 | Volkswagen Ag | Nockenwellentrieb einer Brennkraftmaschine |
US20020128099A1 (en) | 1999-04-29 | 2002-09-12 | Gerhard Winklhofer | Method and device for reducing vibrations of a control chain in a camshaft drive of an internal combustion engine |
Non-Patent Citations (1)
Title |
---|
PATENT ABSTRACTS OF JAPAN vol. 008, no. 177 (M - 317) 15 August 1984 (1984-08-15) * |
Also Published As
Publication number | Publication date |
---|---|
JP2004340125A (ja) | 2004-12-02 |
DE50311827D1 (de) | 2009-10-01 |
EP1443184B1 (de) | 2009-08-19 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE102006041417B3 (de) | Zugmitteltrieb mit einer Ausgleichsvorrichtung zur Schwingungsreduktion | |
DE4244550C2 (de) | Vorrichtung zur Verdrehung von Nockenwellen von Brennkraftmaschinen | |
EP1753974A1 (de) | Zugmittelanordnung | |
WO2011080163A1 (de) | Feder-dämpfer-einheit | |
EP2598776A1 (de) | Schaltvorrichtung für ein getriebe | |
EP2596191B1 (de) | Dämpfungsaggregat zur diskontinuierlichen dämpfung einer drehbewegung | |
WO2014202071A1 (de) | Vorrichtung zur dämpfung von drehschwingungen in einem antriebsstrang eines kraftfahrzeuges | |
WO2006012955A1 (de) | Zugmitteltrieb | |
DE102005010484B3 (de) | Verstellvorrichtung für variable Ventilsteuerung | |
DE102008039009A1 (de) | Nockenwellenversteller | |
DE10353588A1 (de) | Nockenverstelleinrichtung und Steuerglied hierfür | |
WO2006122728A1 (de) | Nockenwellenverstelleinrichtung | |
EP2906789B1 (de) | Variabler ventiltrieb zur betätigung eines ventils eines verbrennungsmotors | |
EP1443184B1 (de) | Variabler nockenwellentrieb | |
DE69114855T2 (de) | Brennkraftmaschine mit variabler ventilzeitsteuerung. | |
EP3578769B1 (de) | Verstellvorrichtung, insbesondere nockenwellenversteller | |
EP1832718A1 (de) | Vorrichtung zur Nockenwellenverstellung | |
DE19620473A1 (de) | Schwingungsdämpfer für eine Kraftstoffanlage | |
DE102005014883A1 (de) | Nockenwellenversteller | |
WO2007059817A1 (de) | Zugmitteltrieb mit dämpfungseinrichtung | |
DE102018211576B4 (de) | Drehschwingungstilger | |
DE202007013390U1 (de) | Verstellvorrichtung zur axialen Verstellung einer Nockenwelle mittels eines Verstellaktuators | |
DE102014201981A1 (de) | Anordnung zum Antreiben einer Verstellwelle zum Verstellen des Expansionshubes und/oder des Verdichtungsverhältnisses eines Verbrennungsmotors | |
DE1550899C (de) | Stellgerat fur die Ubersetzungseinstellung eines Getriebes, insbesondere eines Umschhngungsgetnebes | |
DE10259134A1 (de) | Vorrichtung zum Verstellen der Phasenlage zwischen Nockenwelle und Kurbelwelle |
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 |
|
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 HU IE IT LI LU MC NL PT SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL LT LV MK RO |
|
17P | Request for examination filed |
Effective date: 20050204 |
|
AKX | Designation fees paid |
Designated state(s): DE FR GB |
|
RBV | Designated contracting states (corrected) |
Designated state(s): DE FR GB |
|
17Q | First examination report despatched |
Effective date: 20080320 |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: FORD GLOBAL TECHNOLOGIES, LLC |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
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): DE FR GB |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
REF | Corresponds to: |
Ref document number: 50311827 Country of ref document: DE Date of ref document: 20091001 Kind code of ref document: P |
|
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 |
|
26N | No opposition filed |
Effective date: 20100520 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GB Payment date: 20141230 Year of fee payment: 13 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20141226 Year of fee payment: 13 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20150126 Year of fee payment: 13 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 50311827 Country of ref document: DE |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20160129 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20160930 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160129 Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20160802 |
|
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: 20160201 |