EP1173675B1 - Starter - Google Patents
Starter Download PDFInfo
- Publication number
- EP1173675B1 EP1173675B1 EP01913708A EP01913708A EP1173675B1 EP 1173675 B1 EP1173675 B1 EP 1173675B1 EP 01913708 A EP01913708 A EP 01913708A EP 01913708 A EP01913708 A EP 01913708A EP 1173675 B1 EP1173675 B1 EP 1173675B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- transmission ratio
- starter
- gear ratio
- starting
- changeover
- 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.)
- Expired - Lifetime
Links
- 239000007858 starting material Substances 0.000 title claims description 44
- 230000005540 biological transmission Effects 0.000 claims description 27
- 238000002485 combustion reaction Methods 0.000 claims description 22
- 238000000034 method Methods 0.000 claims description 18
- 230000001419 dependent effect Effects 0.000 claims description 5
- 230000001105 regulatory effect Effects 0.000 claims description 3
- 230000001133 acceleration Effects 0.000 description 4
- 230000006835 compression Effects 0.000 description 3
- 238000007906 compression Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000033001 locomotion Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 239000000969 carrier Substances 0.000 description 1
- 230000009365 direct transmission Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000007613 environmental effect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 238000009499 grossing Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000009955 starching Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N15/00—Other power-operated starting apparatus; Component parts, details, or accessories, not provided for in, or of interest apart from groups F02N5/00 - F02N13/00
- F02N15/02—Gearing between starting-engines and started engines; Engagement or disengagement thereof
- F02N15/04—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears
- F02N15/06—Gearing between starting-engines and started engines; Engagement or disengagement thereof the gearing including disengaging toothed gears the toothed gears being moved by axial displacement
Definitions
- the invention relates to a starter of an internal combustion engine, with those mentioned in the preamble of claim 1 Features as disclosed in DE-C-198 52 085.
- Starters of the generic type are known.
- the gear such a starter can, for example, by a single-track transmission be formed, the thrust movements of the Engagement relay and the rotary motion of the electric starter motor transfers to the pinion in a suitable manner.
- Electric motors are DC, AC or three-phase motors.
- the DC series motor is particularly suitable as a starter motor, because it has the required high starting torque to overcome the starting resistance and developed to accelerate engine masses.
- the torque of the starter is predominantly above one Pinion and a ring gear on the flywheel on the crankshaft of the internal combustion engine.
- the pinion starter can because of the large Ratio between starter pinion and ring gear of the engine flywheel be interpreted so that the Torque is high at low speeds.
- the Exhaust emissions value during the starting process is comparatively high because the combustion process is below idle speed of the internal combustion engine is not optimal.
- the starter has a transmission that has at least a first transmission ratio and has a second gear ratio which is lower than the first gear ratio, where at least during a first starting phase of a starting process the first gear ratio is used, and whereby, at least from exceeding a predetermined Ambient temperature, during a time behind the first start phase lying second start phase the second Gear ratio is used characterized in that the change from the first gear ratio to the second gear ratio time-controlled and / or torque-dependent he follows, it is possible that Internal combustion engine with a single starter on one Towing up speed that is close to idling speed of the internal combustion engine lies before fuel in the cylinders is injected and ignited.
- the first start phase preferably begins with the beginning of the starting process.
- the first compression strokes due to the high initial translation with good acceleration and high torque passed through. This can be done at the beginning of the starching process higher load moment, which is partly due to the gas spring torque and additional torque losses of the internal combustion engine is generated, overcome by the higher moments of inertia an additional smoothing effect arises.
- the change from the first gear ratio to the second gear ratio is controlled or regulated.
- the change takes place in this context from the first gear ratio to the second gear ratio, depending on special properties of the internal combustion engine, time-controlled.
- the change from the first gear ratio to the second gear ratio can also be done if the torque transmitted to the gearbox becomes negative, i.e. if there is drive torque from the internal combustion engine on the gearbox is transferred to the starter. In this case it would be self-regulation.
- the change from the first gear ratio to the second gear ratio can, for example, by a Planetary gears are made.
- the drive of the planetary gear on the sun gear and the output lie on the planet carrier.
- the ring gear of the planetary gear can be fixed at the first gear ratio and in the second gear ratio via a clutch be connected to the sun gear side.
- a clutch between Ring gear and planet carrier or between planet carriers and sun gear is to represent the second gear ratio also conceivable.
- the starter according to the invention can be in the form of a Starter generator are present, which during the operation of the Internal combustion engine remains connected to the crankshaft and feeds energy into the electrical system.
- an embodiment of the present invention is the starter with S and the associated gear designated GT.
- the output shaft of the starter electric motor can be non-positively connected to the GT gearbox, which in turn is non-positive with the internal combustion engine VM can be connected, for example by an engagement gear part of the transmission GT.
- the gearbox GT has a control input ST to which a control signal can be applied, which can trigger a change from the first gear stage i 1 to the second gear stage i 2 , and vice versa, whereby it is of course also conceivable that more than just two gear stages are provided.
- the starter S has only a single electrical machine, and the change from the first gear ratio i 1 to the second gear ratio i 2 is, as mentioned above, time-controlled and / or speed-dependent or suitably controlled or regulated in some other way.
- the higher first gear ratio i 1 is preferably optimized with regard to the cold start limit temperature.
- the lower second gear ratio i 2 is preferably optimized for the generator ratio at higher crankshaft speeds and for the start-up support at the start or for towing up to a speed which is in the range of the idle speed of the internal combustion engine VM.
- the optimization is preferably carried out for an ambient temperature range which is above 20 ° C.
- Figure 2 is the torque of the crankshaft in Nm plotted on the left vertical axis 11, the power in W is plotted on the right vertical axis 12, and the speed of the crankshaft in l / min is up the horizontal axis 10 plotted.
- the change from the first gear ratio i 1 to the second gear ratio i 2 is speed-dependent at the speed at which the torque achieved with the first gear ratio i 1 is equal to that achieved at this crankshaft speed with the second gear ratio i 2 Torque is, or is exceeded by this.
- the curve profiles shown in FIG. 2 apply to the starting process of a V6 internal combustion engine, i.e. For an internal combustion engine VM which has six cylinders, three of which are in a row, the two rows are arranged V-shaped to each other. Farther apply the curves shown in Figure 2 for a Ambient temperature of 20 ° C.
- the starting process is in the area of the first Compression very uncertain, which in the illustration at about 0.18 seconds takes place because of the speed to this Time is only about 60 revolutions per minute.
- An internal combustion engine VM with a slightly higher one Drag torque would not be in these circumstances more, or at least not safe to start.
- the change between the gear ratios can be from other environmental conditions or engine parameters such be made dependent on the fact that not all existing gear ratios can be used.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Transmission Devices (AREA)
Description
- Figur 1
- Ein schematisches Blockschaltbild einer Ausführungsform der vorliegenden Erfindung.
- Figur 2
- Den Verlauf des auf die Kurbelwelle übertragenen Drehmoments, der Kurbelwellendrehzahl und der Leistung, in einem Fall, in dem die erste Getriebeübersetzung gleich neun und die zweite Getriebeübersetzung gleich drei ist.
- Figur 3
- Die bei einem Startvorgang auftretenden Drehzahlverläufe in Abhängigkeit von der Zeit, bei einer ausschließlichen Verwendung einer ersten Getriebeübersetzung, die gleich neun ist, bei einer ausschließlichen Verwendung einer zweiten Getriebeübersetzung, die gleich drei ist, und bei einem erfindungsgemäßen Wechsel von der genannten ersten zu der genannten zweiten Getriebeübersetzung.
Claims (11)
- Starter (S) für einen Verbrennungsmotor (VM), wobei der Starter (S) ein Getriebe (GT) aufweist, das zumindest eine erste Getriebeübersetzung (i1) und eine zweite Getriebeübersetzung (i2) aufweist, die niedriger als die erste Getrieberübersetzung (i1) ist, wobei zumindest während einer ersten Startphase eines Startvorgangs die erste Getriebeübersetzung (i1) verwendet wird und wobei, zumindest ab der Überschreitung einer vorgegebenen Umgebungstemperatur, während einer zeitlich hinter der ersten Startphase liegenden zweiten Startphase die zweite Getriebeübersetzung (i2) verwendet wird, dadurch gekennzeichnet, dass der Wechsel von der ersten Getriebeübersetzung (i1) zu der zweiten Getriebeübersetzung (i2) zeitgesteuert und/oder drehmomentabhängig erfolgt.
- Starter (S) nach Anspruch 1, dadurch gekennzeichnet, dass die erste Startphase mit dem Anfang des Startvorgangs beginnt.
- Starter (S) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sich die zweite Startphase an die erste Startphase anschließt.
- Starter (S) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Wechsel von der ersten Getriebeübersetzung (i1) zu der zweiten Getriebeübersetzung (i2) gesteuert oder geregelt erfolgt.
- Starter (S) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Wechsel von der ersten Getriebeübersetzung (i1) zu der zweiten Getriebeübersetzung (i2) bei der Drehzahl erfolgt, bei der die Drehmomente an der Kurbelwelle für die erste Getriebeübersetzung (i1) und die zweite Getriebeübersetzung (i2) zumindest annähernd gleich groß sind.
- Starter (S) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Wechsel von der ersten Getriebeübersetzung (i1) zu der zweiten Getriebeübersetzung (i2) dann erfolgt, wenn das am Getriebe (GT) übertragene Drehmoment negativ wird.
- Starter (S) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Wechsel von der ersten Getriebeübersetzung (i1) zu der zweiten Getriebeübersetzung (i2) über ein Planetengetriebe erfolgt.
- Starter (S) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Eintrieb des Planetengetriebes am Sonnenrad und der Abtrieb am Planetenträger liegt.
- Starter (S) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Hohlrad des Planetengetriebes bei der ersten Getriebeübersetzung (i1) fixiert ist, und dass das Hohlrad des Planetengetriebes bei der zweiten Getriebeübersetzung (i2) über eine Kupplung mit der Sonnenradseite verbunden ist.
- Starter (S) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass es sich um einen Startergenerator handelt.
- Starter (S) nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass bei einem Abbruch des Startvorgangs automatisch auf die erste Getriebeübersetzung (i1) umgeschaltet wird, sofern diese zum Abbruchzeitpunkt nicht ohnehin schon verwendet wird.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10007959 | 2000-02-22 | ||
DE10007959A DE10007959A1 (de) | 2000-02-22 | 2000-02-22 | Starter |
PCT/DE2001/000667 WO2001063123A1 (de) | 2000-02-22 | 2001-02-22 | Starter |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1173675A1 EP1173675A1 (de) | 2002-01-23 |
EP1173675B1 true EP1173675B1 (de) | 2003-12-10 |
Family
ID=7631786
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01913708A Expired - Lifetime EP1173675B1 (de) | 2000-02-22 | 2001-02-22 | Starter |
Country Status (10)
Country | Link |
---|---|
US (1) | US20020123408A1 (de) |
EP (1) | EP1173675B1 (de) |
JP (1) | JP2003524114A (de) |
CN (1) | CN1363016A (de) |
AU (1) | AU3919401A (de) |
BR (1) | BR0104574A (de) |
DE (3) | DE10007959A1 (de) |
MX (1) | MXPA01010690A (de) |
WO (1) | WO2001063123A1 (de) |
ZA (1) | ZA200108572B (de) |
Families Citing this family (28)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102004024976B4 (de) * | 2004-05-21 | 2008-01-24 | Motorenfabrik Hatz Gmbh & Co. Kg | Startvorrichtung für Stromerzeuger als Einheit aus Verbrennungsmotor und Generator |
GB2416600B (en) | 2004-07-23 | 2008-06-04 | Ford Global Tech Llc | System and method for starting a vehicle |
FR2917467A3 (fr) * | 2007-06-18 | 2008-12-19 | Renault Sas | Demarreur a rapport d'entrainement variable pour ameliorer le depart a froid des moteurs diesel |
JP4784567B2 (ja) * | 2007-07-05 | 2011-10-05 | 株式会社デンソー | スタータ |
DE102011087697A1 (de) * | 2010-12-24 | 2012-06-28 | Schaeffler Technologies Gmbh & Co. Kg | Verfahren zur Steuerung eines schaltbaren Planetengetriebes in einer Riemenscheibenebene eines Antriebsstrangs |
CN107989733A (zh) * | 2016-10-27 | 2018-05-04 | 宝沃汽车(中国)有限公司 | 一种起动装置及具有其的发动机和车辆 |
DE102017218870B4 (de) | 2017-02-17 | 2021-03-18 | Ford Global Technologies, Llc | Anlassverfahren für einen Verbrennungsmotor |
DE102018212995B4 (de) | 2018-08-03 | 2021-03-18 | Mahle Lnternational Gmbh | Anlasseinrichtung für eine Brennkraftmaschine |
US10920730B2 (en) * | 2019-04-16 | 2021-02-16 | Deere & Company | Multi-mode integrated starter-generator device with dog clutch arrangement |
US11156270B2 (en) | 2019-04-16 | 2021-10-26 | Deere & Company | Multi-mode integrated starter-generator device with transmission assembly mounting arrangement |
US10920733B2 (en) | 2019-04-16 | 2021-02-16 | Deere & Company | Multi-mode integrated starter-generator device with preloaded clutch |
US10933731B2 (en) | 2019-04-16 | 2021-03-02 | Deere & Company | Multi-mode integrated starter-generator device with magnetic cam assembly |
US10968985B2 (en) | 2019-04-16 | 2021-04-06 | Deere & Company | Bi-directional integrated starter-generator device |
US10975938B2 (en) | 2019-04-16 | 2021-04-13 | Deere & Company | Multi-mode integrated starter-generator device with electromagnetic actuation assembly |
US10948054B2 (en) | 2019-04-16 | 2021-03-16 | Deere & Company | Multi-mode integrated starter-generator device with solenoid cam actuation apparatus |
US11060496B2 (en) | 2019-04-16 | 2021-07-13 | Deere & Company | Multi-mode integrated starter-generator device |
US10975937B2 (en) * | 2019-04-16 | 2021-04-13 | Deere & Company | Multi-mode integrated starter-generator device with cam arrangement |
US10821820B1 (en) | 2019-04-16 | 2020-11-03 | Deere & Company | Multi-mode starter-generator device transmission with single valve control |
US10926779B1 (en) * | 2019-08-23 | 2021-02-23 | Ford Global Technologies, Llc | Method and system for controlling a vehicle |
US10900454B1 (en) | 2020-04-03 | 2021-01-26 | Deere & Company | Integrated starter-generator device with unidirectional clutch actuation utilizing a biased lever assembly |
US11193560B1 (en) | 2020-05-29 | 2021-12-07 | Deere & Company | Work vehicle multi-speed drive assembly with bifurcated clutches |
US11415199B2 (en) | 2020-05-29 | 2022-08-16 | Deere & Company | Bi-directional multi-speed drive |
US11326570B1 (en) | 2020-10-26 | 2022-05-10 | Deere & Company | Multi-mode integrated starter-generator device with unidirectional input |
US11866910B2 (en) | 2021-02-25 | 2024-01-09 | Deere & Company | Work vehicle multi-speed drive assembly with output control clutch |
US11624170B2 (en) | 2021-02-25 | 2023-04-11 | Deere & Company | Work vehicle multi-speed drive assembly with clutch retention mechanism |
US11719209B2 (en) | 2021-03-29 | 2023-08-08 | Deere & Company | Integrated starter-generator device with unidirectional clutch actuation utilizing biased lever assembly |
US11761515B2 (en) | 2021-05-20 | 2023-09-19 | Deere & Company | Work vehicle multi-speed drive assembly with guided dog clutch |
US11686374B2 (en) | 2021-07-23 | 2023-06-27 | Deere & Company | Work vehicle multi-speed drive assembly providing multiple gear ratios at same step ratio |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS63195383A (ja) * | 1987-02-10 | 1988-08-12 | Mitsubishi Electric Corp | スタ−タ装置 |
JPH0422755A (ja) * | 1990-05-15 | 1992-01-27 | Mitsubishi Electric Corp | 同軸形スタータ |
DE19852085C1 (de) * | 1998-11-12 | 2000-02-17 | Daimler Chrysler Ag | Starteinrichtung für eine Brennkraftmaschine und Verfahren zum Starten der Brennkraftmaschine |
-
2000
- 2000-02-22 DE DE10007959A patent/DE10007959A1/de not_active Withdrawn
-
2001
- 2001-02-22 JP JP2001561912A patent/JP2003524114A/ja active Pending
- 2001-02-22 CN CN01800293A patent/CN1363016A/zh active Pending
- 2001-02-22 MX MXPA01010690A patent/MXPA01010690A/es unknown
- 2001-02-22 DE DE10190619T patent/DE10190619D2/de not_active Expired - Fee Related
- 2001-02-22 WO PCT/DE2001/000667 patent/WO2001063123A1/de active IP Right Grant
- 2001-02-22 DE DE50101115T patent/DE50101115D1/de not_active Expired - Fee Related
- 2001-02-22 BR BR0104574-1A patent/BR0104574A/pt not_active IP Right Cessation
- 2001-02-22 US US10/030,768 patent/US20020123408A1/en not_active Abandoned
- 2001-02-22 EP EP01913708A patent/EP1173675B1/de not_active Expired - Lifetime
- 2001-02-22 AU AU39194/01A patent/AU3919401A/en not_active Abandoned
- 2001-10-18 ZA ZA200108572A patent/ZA200108572B/en unknown
Also Published As
Publication number | Publication date |
---|---|
EP1173675A1 (de) | 2002-01-23 |
DE50101115D1 (en) | 2004-01-22 |
BR0104574A (pt) | 2002-01-08 |
US20020123408A1 (en) | 2002-09-05 |
AU3919401A (en) | 2001-09-03 |
DE10190619D2 (de) | 2002-05-16 |
DE10007959A1 (de) | 2001-08-30 |
MXPA01010690A (es) | 2002-06-04 |
JP2003524114A (ja) | 2003-08-12 |
CN1363016A (zh) | 2002-08-07 |
ZA200108572B (en) | 2003-01-20 |
WO2001063123A1 (de) | 2001-08-30 |
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