EP1144810A1 - Mehrzylindrige brennkraftmaschine - Google Patents
Mehrzylindrige brennkraftmaschineInfo
- Publication number
- EP1144810A1 EP1144810A1 EP00974441A EP00974441A EP1144810A1 EP 1144810 A1 EP1144810 A1 EP 1144810A1 EP 00974441 A EP00974441 A EP 00974441A EP 00974441 A EP00974441 A EP 00974441A EP 1144810 A1 EP1144810 A1 EP 1144810A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- exhaust
- cylinders
- internal combustion
- combustion engine
- cylinder
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
- F01L1/02—Valve drive
- F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
- F01L1/047—Camshafts
- F01L1/053—Camshafts overhead type
- F01L1/0532—Camshafts overhead type the cams being directly in contact with the driven valve
-
- 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
- F01L1/08—Shape of cams
-
- 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
- F01L2800/00—Methods of operation using a variable valve timing mechanism
- F01L2800/08—Timing or lift different for valves of different cylinders
Definitions
- the invention is based on a multi-cylinder internal combustion engine according to the features of the preamble of claim 1.
- Opening phase of the exhaust valves overlaps two cylinders arranged in a row of cylinders. This condition becomes particularly critical when the intake and exhaust valves of the cylinder that is the first to be fired are still in the opening overlap phase.
- the exhaust valve of the later igniting and thus later exhausting cylinder By opening the exhaust valve of the later igniting and thus later exhausting cylinder, the exhaust gas provided with a high pressure pulse can get into the cylinder space of the cylinder that previously exhausted the exhaust gas. High residual gas rates with negative consequences on the knock limit, as well as an insufficient cylinder filling with fresh gas are the result.
- the use of variable control times increases the scatter of air expenditure in the individual cylinders, and the greater the adjustment ranges, the more so.
- the reduction in the air expenditure of the disadvantaged cylinders can lead to a reduction in the air expenditure, particularly with intake means below 100 ° crank angle (KW), whereby the desired increase in torque is significantly reduced.
- the object of the invention is therefore to eliminate or reduce such negative consequences and to achieve a uniform, optimal degree of cylinder filling over the entire row of cylinders of the internal combustion engine.
- a satisfactory bundling of the air effort curves for all cylinders over the entire speed range occurs particularly when the cylinders favored by the firing order are equipped with cams that have a smaller cam width than the cylinders in which the exhaust gas exhaust gas surge of the in of the cylinder row that later exhausts enters the opening-overlap phase of the inlet and exhaust valve of the earlier exhausting cylinder.
- the charge exchange disadvantages in such an internal combustion engine are particularly noticeable when the 4-finger exhaust manifold flanged on the exhaust side of the two rows of cylinder banks changes into a common exhaust gas pipe after a short distance.
- This exhaust gas discharge is advantageous since it is thus possible to use starting catalytic converters close to the engine and only one pre-catalytic converter and one lambda probe in each case have to be integrated into the exhaust gas collection pipe provided for each row of cylinders. Due to the short exhaust manifold pipes, however, there is a risk that a large part of the exhaust gas exhaust gas surge of the cylinder that later exhausts gets into the cylinder that exhausts earlier. In a V8 engine with such an exhaust gas discharge, the charge exchange disadvantages can thus be effectively compensated for, so that the effects of variable control times unfold their effect in the entire speed range, so that the desired full torque curve is achieved.
- FIG. 1 shows a sectional view of a V8 engine
- FIG. 2 shows a schematic illustration of the two cylinder rows of a V8 engine
- FIG. 3 shows the ignition sequence of a V8 engine with a partial illustration of the charge exchange of three adjacent cylinders
- FIG. 4 shows a schematic illustration a row of cylinder banks
- FIG. 5 shows a graphical representation of valve lift curves
- FIG. 6 shows an exhaust camshaft provided with different cam widths. Description of the embodiment
- the internal combustion engine designed as a V8 engine has a crankshaft 12 arranged in a crankcase 10.
- the connecting rod feet 16, of which only one is shown visibly, are screwed onto the crankshaft journal 14, which is offset by 90 ° KW, and are in turn connected via connecting rod eyes 20 to the eight pistons 22 arranged in the two rows of cylinder banks.
- the two cylinder heads 24 fastened on the crankcase 10 accommodate the known and necessary components for the 4-stroke combustion process, the same components being used for all four cylinders arranged in a row.
- Each cylinder has two intake valves 26 and two exhaust valves 28, of which only one can be seen in each case according to the sectional plane in FIG. 1.
- the inlet valves 26 monitor the inlet channels 32 leading to the combustion chamber 30, while the exhaust valves 28 monitor the outlet channels 34 also leading to the combustion chamber 30.
- the four exhaust ports 34 flanged to each of the two rows of cylinder banks are designed as 4-finger exhaust manifolds, each of which opens into a common exhaust pipe 36 after a short distance.
- the inlet channels 32 on the intake side are supplied with combustion air via an intake system (not shown).
- the intake and exhaust valves 26, 28 are actuated with the aid of an intake camshaft 38 and an exhaust camshaft 40.
- the intake and exhaust camshafts 38, 40 each have four pairs of intake cams 42 and exhaust cams 44, the cylinder-specific design of the cams later is described in more detail.
- the rotational movement of the intake and exhaust camshafts 38, 40 is transferred into a lifting movement of the intake and exhaust valves 26, 28 by means of cup tappets 46 and 48 designed as cam followers.
- valve springs 50, 52 arranged coaxially to the valve stem of the inlet and outlet valves 26, 28 it is ensured, among other things, that the Inlet and outlet valves 26, 28 securely close the inlet and outlet channels 32, 34 during the basic phase of the cams 46, 48.
- injection valves 54 fuel is injected into the inlet channels 32, which is brought to combustion in the combustion chamber 30 when the inlet valve 26 is opened with the aid of an ignition device designed as a spark plug 56.
- Fig. 3 the firing order of the cylinders 1 to 4 and 5 to 8 arranged on the two rows of cylinder banks is shown. As is clear from the figure below, the firing order is asymmetrical with respect to the two rows of cylinder banks and has three different firing intervals for each row of cylinder banks.
- the ignition distance between cylinders 1 and 3 is 90 ° KW, between cylinders 2 and 3 and 1 and 4 180 ° KW and between cylinders 2 and 4 270 ° KW.
- the ignition timing intervals in the second row of cylinders 5 to 8 between cylinders 5 and 6 are 90 ° KW, between cylinders 6 and 7 and between cylinders 5 and 8 180 ° KW and between cylinders 7 and 8 270 ° KW.
- FIG. 3 The upper illustration in FIG. 3, in which the valve lift curves of the exhaust valves 28, of the cylinders 1, 3 and 2 that exhaust with a 90 ° KW and 180 ° KW distance, are shown, the mutual outflow restriction of the 90 ° KW distance igniting or exhausting cylinders 1 and 3 recognizable.
- the exhaust valve overlap phase of the cylinders with a 180 ° KW spacing in a row of cylinder banks is far more serious with regard to the gas exchange.
- the exhaust gas exhaust blow of the cylinder 2 which ignites and exhausts 180 ° later, arrives in the opening overlap phase of the two intake and exhaust valves 26, 28 of the cylinder 3.
- Torque increase is significantly reduced.
- the possibility of adjusting the inlet valve opening times is shown in the upper illustration of FIG. 3 by way of example with the dashed curve E3 ' for cylinder 3, which is shifted in the "early" direction relative to the valve opening curve E3.
- the cylinders 1 and 3 or 1 and 4 exhausting by 180 ° KW distance within the cylinder bank 1 - 4 and the cylinders 6 and 7 or 5 and 8 within the cylinder bank 5 - 8 show the air effort disadvantaged cylinders 3, 4, 5, 7 a larger cam width for the cam 44 arranged on the exhaust camshaft 40.
- Fig. 1 the cylinders 1 and 3 or 1 and 4 exhausting by 180 ° KW distance within the cylinder bank 1 - 4 and the cylinders 6 and 7 or 5 and 8 within the cylinder bank 5 - 8 show the air effort disadvantaged cylinders 3, 4, 5, 7 a larger cam width for the cam 44 arranged on the exhaust camshaft 40.
- valve lift for the exhaust valves 28 of the cylinders 3, 4, 5, 7 is shown, while the smaller valve lift curve A 'shown in dashed lines is assigned to the exhaust valves 28 of the cylinders 1, 2, 6, 8 , Due to the narrower exhaust cams 44 ' for the cylinders 1, 2, 6, 8, the opening overlap phase of the exhaust valves 28 assigned to the cylinders 1, 2, 6, 8 to the exhaust valves 28 of the cylinders 3 opening earlier by 180 ° KW distance is reduced , 4, 5, 7.
- a satisfactory bundling of the air expenditure curves ie uniform air expenditure a per cylinder over the entire speed range, is achieved in particular if the narrower cams 44 'have a cam width smaller by 10 ° to 20 ° KW per 1 mm valve stroke than the wide cams 44.
- the cam width for the cylinders 1, 2, 6, 8 also decreases due to the fixed cam contour profile, as shown in FIG. 5, the maximum valve lift of the exhaust valves 28 assigned to the cylinders.
- the curve E shown on the right in FIG. 5 shows the valve lift curve of the intake valves 26, which is identical for all cylinders 1 to 8.
- Such a camshaft concept especially for V8 engines with 90 ° cranking of the crankshaft and a 4 in 1 exhaust manifold design, has the effects of variable valve timing in the entire speed range, which is associated with the desired full torque curve. Since a 4 in 1 exhaust manifold design with short manifold pipes is desired in V8 engines due to the number of pre-catalytic converters or lambda probes, but with the disadvantageous effects described at the beginning regarding the cylinder filling with fresh gas, the above-described camshaft concept can be used particularly effectively.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Valve Device For Special Equipments (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
- Exhaust Silencers (AREA)
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19954689A DE19954689A1 (de) | 1999-11-13 | 1999-11-13 | Mehrzylindrige Brennkraftmaschine |
DE19954689 | 1999-11-13 | ||
PCT/EP2000/010450 WO2001036793A1 (de) | 1999-11-13 | 2000-10-24 | Mehrzylindrige brennkraftmaschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1144810A1 true EP1144810A1 (de) | 2001-10-17 |
EP1144810B1 EP1144810B1 (de) | 2005-01-12 |
Family
ID=7928958
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP00974441A Expired - Lifetime EP1144810B1 (de) | 1999-11-13 | 2000-10-24 | Mehrzylindrige brennkraftmaschine |
Country Status (9)
Country | Link |
---|---|
US (1) | US6397802B1 (de) |
EP (1) | EP1144810B1 (de) |
JP (1) | JP5010082B2 (de) |
KR (1) | KR100749232B1 (de) |
CN (1) | CN1154788C (de) |
AT (1) | ATE287027T1 (de) |
DE (2) | DE19954689A1 (de) |
ES (1) | ES2231280T3 (de) |
WO (1) | WO2001036793A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11946827B2 (en) | 2021-06-11 | 2024-04-02 | Honda Motor Co., Ltd. | Valve testing apparatus |
Families Citing this family (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10046221A1 (de) * | 2000-09-19 | 2002-10-02 | Bayerische Motoren Werke Ag | Verfahren und Vorrichtung zur Steuerung der zylinderselektiven Füllung bei Verbrennungsmotoren mit variablem Ventiltrieb |
DE102004012428A1 (de) * | 2003-09-23 | 2005-04-28 | Bosch Gmbh Robert | Verfahren, Computerprogramm und Vorrichtung zum Betreiben einer Brennkraftmaschine |
SE531208C8 (de) * | 2004-03-31 | 2009-02-17 | ||
JP4305355B2 (ja) * | 2004-10-04 | 2009-07-29 | トヨタ自動車株式会社 | 多気筒内燃機関 |
DE102005032791A1 (de) * | 2005-07-14 | 2007-01-18 | Deutz Ag | Abgasrückführung durch Zusatzöffnen der Einlassventile während der Auslasshuböffnung der Auslassventile |
JP2007085218A (ja) * | 2005-09-21 | 2007-04-05 | Toyota Motor Corp | 内燃機関の制御装置 |
JP4661511B2 (ja) | 2005-10-03 | 2011-03-30 | トヨタ自動車株式会社 | エンジン |
US7275511B1 (en) * | 2006-07-26 | 2007-10-02 | Gm Global Technology Operations, Inc. | Intake manifold assembly |
FR2910526A1 (fr) * | 2006-12-22 | 2008-06-27 | Renault Sas | Moteur a combustion interne adapte a ameliorer la vidange de ses cylindres. |
DE102009053269A1 (de) | 2009-11-13 | 2011-05-26 | Bayerische Motoren Werke Aktiengesellschaft | Brennkraftmaschine |
US9316151B2 (en) * | 2011-02-18 | 2016-04-19 | GM Global Technology Operations LLC | Engine assembly including crankshaft for V8 arrangement |
DE102011084834A1 (de) | 2011-10-20 | 2013-04-25 | Ford Global Technologies, Llc | Brennkraftmaschine mit mehreren Auslaßöffnungen je Zylinder und Ladungswechselverfahren für eine derartige Brennkraftmaschine |
KR101316857B1 (ko) | 2011-12-15 | 2013-10-08 | 현대자동차주식회사 | 배기 밸브 제어 시스템 |
GB2501311B (en) * | 2012-04-20 | 2014-08-13 | Ford Global Tech Llc | Camshaft for the exhaust side of a multiple-cylinder four-stroke internal combustion engine |
DE102012210303B4 (de) * | 2012-06-19 | 2014-05-15 | Ford Global Technologies, Llc | Fremdgezündete Mehrzylinder-Brennkraftmaschine mit Teilabschaltung und Verfahren zum Betreiben einer derartigen Brennkraftmaschine |
US9594226B2 (en) | 2013-10-18 | 2017-03-14 | Corning Optical Communications LLC | Optical fiber cable with reinforcement |
JP2016217217A (ja) * | 2015-05-18 | 2016-12-22 | ヤマハ発動機株式会社 | V型8気筒エンジン及び船外機 |
DE112016004372T5 (de) | 2015-11-06 | 2018-06-07 | Borgwarner Inc. | Ventilbetätigungssystem, das einen variablen ventilhub und/oder variable ventilzeitsteuerung bereitstellt |
DE102017123136A1 (de) * | 2017-10-05 | 2019-04-11 | Man Truck & Bus Ag | Brennkraftmaschine mit Ventiltaschen |
CN108150238B (zh) * | 2018-01-11 | 2019-11-05 | 东阳市天齐科技有限公司 | 凸凹轮转子双缸四冲程发动机 |
DE102018122342A1 (de) * | 2018-09-13 | 2020-03-19 | Man Truck & Bus Se | Verfahren zum Betreiben einer Brennkraftmaschine |
Family Cites Families (16)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4068630A (en) * | 1975-12-12 | 1978-01-17 | General Motors Corporation | Engine with noise reducing exhaust valve arrangement |
JPS5770914A (en) * | 1980-10-20 | 1982-05-01 | Yamaha Motor Co Ltd | Air intake controller for multi-valvetype internal combustionn engine |
JPS5946310A (ja) * | 1982-09-10 | 1984-03-15 | Mazda Motor Corp | エンジンのバルブタイミング制御装置 |
JPH0424085Y2 (de) * | 1985-03-04 | 1992-06-05 | ||
JPH079187B2 (ja) * | 1985-06-07 | 1995-02-01 | ヤマハ発動機株式会社 | 並列4気筒エンジンの排気装置 |
DE3523791A1 (de) * | 1985-07-03 | 1987-01-08 | Odilo Schwaiger | Ventilsteuerung fuer brennkraftmaschinen |
JPS63192908A (ja) * | 1987-02-05 | 1988-08-10 | Mazda Motor Corp | エンジンの動弁装置 |
JPH01159417A (ja) * | 1987-12-15 | 1989-06-22 | Nissan Motor Co Ltd | 内燃機関の弁装置 |
EP0319956B1 (de) * | 1987-12-08 | 1992-10-28 | Nissan Motor Co., Ltd. | Ventilsteuervorrichtung |
JP2736997B2 (ja) * | 1989-04-27 | 1998-04-08 | 本田技研工業株式会社 | 内燃機関の弁駆動装置および弁駆動方法 |
JPH039016A (ja) * | 1989-06-06 | 1991-01-16 | Mazda Motor Corp | 多気筒エンジンの排気構造 |
JP2962894B2 (ja) * | 1991-09-30 | 1999-10-12 | マツダ株式会社 | 車両のパワートレイン構造 |
JP3249163B2 (ja) * | 1992-01-10 | 2002-01-21 | マツダ株式会社 | タ−ボ過給機付きエンジンの吸気装置 |
DE19606054C2 (de) * | 1996-02-19 | 1998-07-30 | Porsche Ag | Ventiltrieb einer Brennkraftmaschine |
JP3834921B2 (ja) * | 1997-04-02 | 2006-10-18 | 三菱自動車工業株式会社 | 可変動弁機構 |
DE19806054A1 (de) * | 1998-02-13 | 1999-08-19 | Lre Technology Partner Gmbh | Testkarte für eine optische oder amperometrische Bestimmung der Konzentration einer Substanz in einer Flüssigkeit |
-
1999
- 1999-11-13 DE DE19954689A patent/DE19954689A1/de not_active Ceased
-
2000
- 2000-10-24 AT AT00974441T patent/ATE287027T1/de active
- 2000-10-24 EP EP00974441A patent/EP1144810B1/de not_active Expired - Lifetime
- 2000-10-24 CN CNB008027579A patent/CN1154788C/zh not_active Expired - Fee Related
- 2000-10-24 ES ES00974441T patent/ES2231280T3/es not_active Expired - Lifetime
- 2000-10-24 WO PCT/EP2000/010450 patent/WO2001036793A1/de active IP Right Grant
- 2000-10-24 KR KR1020017008800A patent/KR100749232B1/ko not_active IP Right Cessation
- 2000-10-24 DE DE50009217T patent/DE50009217D1/de not_active Expired - Lifetime
- 2000-10-24 JP JP2001538652A patent/JP5010082B2/ja not_active Expired - Fee Related
- 2000-10-24 US US09/889,224 patent/US6397802B1/en not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO0136793A1 * |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11946827B2 (en) | 2021-06-11 | 2024-04-02 | Honda Motor Co., Ltd. | Valve testing apparatus |
Also Published As
Publication number | Publication date |
---|---|
KR100749232B1 (ko) | 2007-08-13 |
CN1154788C (zh) | 2004-06-23 |
WO2001036793A1 (de) | 2001-05-25 |
JP2003515025A (ja) | 2003-04-22 |
EP1144810B1 (de) | 2005-01-12 |
DE50009217D1 (de) | 2005-02-17 |
JP5010082B2 (ja) | 2012-08-29 |
ATE287027T1 (de) | 2005-01-15 |
ES2231280T3 (es) | 2005-05-16 |
CN1336980A (zh) | 2002-02-20 |
US6397802B1 (en) | 2002-06-04 |
DE19954689A1 (de) | 2001-05-23 |
KR20010102974A (ko) | 2001-11-17 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP1144810B1 (de) | Mehrzylindrige brennkraftmaschine | |
EP1296043B1 (de) | Brennkraftmaschine | |
DE19546549C5 (de) | Verfahren zum Ab- und Zuschalten einzelner Zylinder | |
EP0663042B1 (de) | Hybridgesteuerter viertakt-ottomotor | |
EP0615058B1 (de) | Zylinderkopf für eine Brennkraftmaschine | |
DE3600408C2 (de) | ||
DE102004046534B4 (de) | Verfahren und Vorrichtung zum Betreiben eines Motors | |
DE102016209957A1 (de) | Verfahren zum Betreiben einer Brennkraftmaschine und Brennkraftmaschine | |
DE102011084834A1 (de) | Brennkraftmaschine mit mehreren Auslaßöffnungen je Zylinder und Ladungswechselverfahren für eine derartige Brennkraftmaschine | |
EP2499346B1 (de) | Brennkraftmaschine mit acht zylindern in v-bauart | |
DE10303749A1 (de) | Oben liegender Ventiltrieb für einen Motor mit drei Ventilen und einer Nockenwelle | |
DE102010033493A1 (de) | Brennkraftmaschine und Verfahren zum Betreiben einer Brennkraftmaschine | |
DE102014208950A1 (de) | Verbrennungsmotor und Verfahren zum Betreiben eines solchen Verbrennungsmotors | |
DE102005032791A1 (de) | Abgasrückführung durch Zusatzöffnen der Einlassventile während der Auslasshuböffnung der Auslassventile | |
DE19628024C2 (de) | Brennkraftmaschine | |
DE102013206898A1 (de) | Nockenwelle | |
EP2209972A1 (de) | Einrichtung zur steuerung des restgasgehaltes von zylindern einer verbrennungskraftmaschine | |
WO2020053081A1 (de) | Verfahren zum betreiben einer brennkraftmaschine | |
AT523632B1 (de) | Brennkraftmaschine und verfahren zum betrieb einer brennkraftmaschine | |
EP1573178A1 (de) | Verfahren zum verändern der ventilsteuerzeiten einer brennkr aftmaschine | |
EP3728818B1 (de) | Verfahren zum betreiben einer brennkraftmaschine und brennkraftmaschine | |
DE102004027474B4 (de) | Viertakt-Verbrennungsmotor mit Abgasturbolader und Verfahren zur Optimierung seines Betriebs | |
DE102005008453B4 (de) | Abgasrückführung durch verlängertes Offenhalten oder Nachöffnen der Auslassventile einer Hubkolbenbrennkraftmaschine | |
DE102017104845B4 (de) | Verbrennungsmotor mit hubvariabler Gaswechselventil-Betätigung | |
DE102015200598A1 (de) | Fremdgezündete Brennkraftmaschine mit variablem Ventiltrieb und Verfahren zum Betreiben einer derartigen Brennkraftmaschine |
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 CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE |
|
17P | Request for examination filed |
Effective date: 20011126 |
|
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): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20050112 Ref country code: IE 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: 20050112 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: 20050112 |
|
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: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: TRGR |
|
REF | Corresponds to: |
Ref document number: 50009217 Country of ref document: DE Date of ref document: 20050217 Kind code of ref document: P |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: GERMAN |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20050412 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2231280 Country of ref document: ES Kind code of ref document: T3 |
|
GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 20050422 |
|
NLV1 | Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act | ||
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FD4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20051024 |
|
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: 20051031 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20051031 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20051031 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20051031 Ref country code: MC Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20051031 |
|
ET | Fr: translation filed | ||
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: 20051013 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
BERE | Be: lapsed |
Owner name: DR.ING. H.C.F. PORSCHE A.G. Effective date: 20051031 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: PT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050612 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20050112 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: TP |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: CD |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: ES Payment date: 20091023 Year of fee payment: 10 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: TP |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: 732E Free format text: REGISTERED BETWEEN 20110310 AND 20110316 |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: 732E Free format text: REGISTERED BETWEEN 20110331 AND 20110406 |
|
REG | Reference to a national code |
Ref country code: ES Ref legal event code: FD2A Effective date: 20111121 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20101025 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 16 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 17 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20161020 Year of fee payment: 17 Ref country code: GB Payment date: 20161020 Year of fee payment: 17 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20161019 Year of fee payment: 17 Ref country code: AT Payment date: 20161020 Year of fee payment: 17 Ref country code: IT Payment date: 20161024 Year of fee payment: 17 |
|
REG | Reference to a national code |
Ref country code: SE Ref legal event code: EUG |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 287027 Country of ref document: AT Kind code of ref document: T Effective date: 20171024 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20171024 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20180629 |
|
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: 20171024 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171025 Ref country code: AT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171024 Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20171031 |
|
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 NON-PAYMENT OF DUE FEES Effective date: 20171024 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20190923 Year of fee payment: 20 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R071 Ref document number: 50009217 Country of ref document: DE |