WO2005064137A1 - Antriebsstrang mit abgasnutzung und steuerungsverfahren - Google Patents
Antriebsstrang mit abgasnutzung und steuerungsverfahrenInfo
- Publication number
- WO2005064137A1 WO2005064137A1 PCT/EP2004/013407 EP2004013407W WO2005064137A1 WO 2005064137 A1 WO2005064137 A1 WO 2005064137A1 EP 2004013407 W EP2004013407 W EP 2004013407W WO 2005064137 A1 WO2005064137 A1 WO 2005064137A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- hydrodynamic
- working space
- exhaust gas
- hydrodynamic coupling
- clutch
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
- F02B41/02—Engines with prolonged expansion
- F02B41/10—Engines with prolonged expansion in exhaust turbines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the invention relates to a drive train, in particular a motor vehicle drive train, in which the exhaust gas energy of the exhaust gases of an internal combustion engine is used for driving by means of an exhaust gas turbine.
- the invention further relates to a method for controlling such a drive train.
- exhaust gas turbines in drive trains, in particular in motor vehicle drive trains, is known.
- the crankshaft of the internal combustion engine is additionally driven by the exhaust gas utility turbine, which is connected in a suitable drive connection to the crankshaft, in the use of exhaust gas energy.
- the drive connection comprises a hydrodynamic clutch, which transmits the drive torque of the exhaust gas turbine to the crankshaft. Suitable translations or gears can also be interposed.
- the hydrodynamic clutch is not only used for torque transmission in exhaust gas energy operation, but it is also used as a hydrodynamic brake, i. H. used as a so-called retarder.
- a wheel of the hydrodynamic clutch is mechanically fixed, namely the wheel connected to the exhaust gas turbine.
- two different hydraulic circuits can be used, which specifically fill and empty a clutch chamber and a retarder chamber.
- a multi-plate clutch can be used as a means for braking or locking the one wheel of the hydrodynamic clutch.
- Technical problems have repeatedly occurred with such multi-plate clutches, which were mostly attributed to overload. Accordingly, the multi-plate clutches have been designed to be powerful, ie with considerable structural dimensions and considerable weight. On the one hand, this interpretation leads to high costs. On the other hand, the additional weight is particularly great Motor vehicles to be regarded as disadvantageous, since it is known that the aim today is to minimize fuel consumption.
- the invention has for its object to further develop a drive train with an internal combustion engine, an exhaust gas turbine and a hydrodynamic clutch in the drive connection between a crankshaft and the exhaust gas turbine, the hydrodynamic clutch also being used for hydrodynamic braking, such that the disadvantages of the prior art be cleared out.
- a structurally smaller means in particular a multi-plate clutch, should be able to be used to brake or lock the one clutch wheel.
- a control method for controlling the drive train according to the invention is to be presented.
- the inventor has recognized a possibility of designing a generic drive train in which the hydrodynamic clutch can be designed for high transmission powers and at the same time only a comparatively weak braking or locking device can be used for braking and locking a paddle wheel of the hydrodynamic clutch without it there is a risk of overloading them.
- the areas of greatest load peaks are, as it were, hidden from the operating behavior. This firstly protects the clutch and secondly increases driving comfort when used in a motor vehicle by a smoother transition from clutch operation to retarder operation.
- a control which empties the working space of the hydrodynamic clutch to a predetermined filling level before the primary wheel, ie the bucket wheel, which is assigned to the exhaust gas turbine and is used as a stator in retarder operation, is braked.
- the Emptying takes place together with the braking of the primary wheel of the hydrodynamic coupling. It is only important that the emptying is carried out in good time so that no long-lasting or no stress conditions occur that exceed the performance of the braking device.
- the braking device for braking and mechanically locking the primary wheel of the hydrodynamic clutch is a multi-plate clutch. It is also advantageous if the hydrodynamic coupling is arranged in the cooling circuit of a vehicle and the working medium is the vehicle cooling medium, in particular water or a water mixture.
- a 3/2-way valve is arranged in the cooling circuit upstream of the hydrodynamic coupling. H. in "normal" driving mode, the inflowing working medium flow in the direction of the hydrodynamic clutch and at the same time in the direction of the internal combustion engine, which is cooled by the working medium or cooling medium, is divided. Immediately before braking and / or braking the primary wheel, the 3/2 switches -Way valve and shuts off the working medium flow in the direction of the hydrodynamic coupling, so that, due to a lack of inflow, the working space of the hydrodynamic coupling is emptied to the desired filling level by continuous outflow.
- a throttling point can be provided in the flow direction upstream of the hydrodynamic clutch, which throttles the working medium flow before braking or when braking the primary wheel.
- This throttle point can be designed in the form of a regulated throttle or by means of a throttle that can be activated, for example in a bypass.
- an expandable drain opening or additional drain openings can be provided behind the hydrodynamic coupling in the flow direction, with which the available flow cross-section is expanded before braking or when braking the primary wheel of the hydrodynamic clutch.
- the working space of the hydrodynamic clutch is kept at a predetermined filling level, which is generally smaller than the filling level in clutch operation, i.e. , H. in exhaust gas energy operation.
- a predetermined filling level which is generally smaller than the filling level in clutch operation, i.e. , H. in exhaust gas energy operation.
- the working space of the hydrodynamic coupling is emptied to a predetermined filling level.
- the switchover begins with the braking of the primary wheel of the hydrodynamic clutch or even before that, in the case of an emptying, immediately before the braking of the primary wheel.
- the working space of the hydrodynamic clutch is completely emptied when switching over.
- this charge state of the retarder operation becomes directly before or when the primary wheel of the hydrodynamic clutch is braked
- a filling state is approached which has a degree of filling less than that of the retarder operation, and the clutch is subsequently refilled to the degree of filling of the retarder operation.
- Figure 1 shows a basic structure of the drive connection between the
- Figure 2 is a control scheme for controlling an inventive
- FIG 3 shows the states of the 3/2-way valve shown in Figure 2 in detail.
- FIG. 1 shows the drive connection between an exhaust gas turbine 2 and a crankshaft 3 of an internal combustion engine, not shown, which is designed in accordance with an embodiment of the present invention.
- the driven shaft of the exhaust gas turbine is connected to the primary wheel 4.1 of the hydrodynamic clutch 4 via a first gear 8.
- the crankshaft 3 is connected to the secondary wheel 4.2 of the hydrodynamic clutch 4 via a second gear 9. Accordingly, when the working space of the hydrodynamic clutch 4 is filled, preferably when it is full, torque or rotational power is transmitted from the exhaust gas turbine 2 to the crankshaft 3.
- the primary wheel 4.1 of the hydrodynamic clutch 4 can be braked and mechanically locked by means of the multi-plate clutch 5.
- the hydrodynamic clutch 4 acts as a retarder, ie the crankshaft 3 continues to drive the secondary wheel 4.2 of the hydrodynamic clutch 4 via the gear 9, via the filled working space of the hydrodynamic clutch 4, advantageously with one filled predetermined filling, torque is transmitted from the secondary gear 4.2 to the primary gear 4.1 and derived via the multi-plate clutch 5. This creates a braking effect that brakes the crankshaft 3.
- the second effect can be seen in the fact that the multi-plate clutch 5 also fixes the rotor of the exhaust gas turbine 2 via the primary wheel 4.1 and the transmission 8. Accordingly, the exhaust gas flow, which flows through the exhaust gas turbine, is throttled, which leads to an increased exhaust gas pressure, which in turn brakes the internal combustion engine, not shown. This effect could be compared to that of an exhaust valve brake.
- FIG. 2 shows a control scheme for a possible control of the drive train according to the invention or a possible control method according to the invention.
- the same reference numerals are used for the components already shown in FIG. 1, so that this description need not be repeated.
- the hydrodynamic clutch 4 is arranged in the cooling circuit 6 of a vehicle.
- a cooler 10 is connected to the cooling circuit 6. If cooling is not required, this can be bypassed using the bypass shown.
- the output values of a thermostat 11 are used to divide the corresponding coolant flow, either through the cooler 10 or through the bypass.
- the cooling medium or the working medium is circulated in the cooling circuit by the cooling water pump 12. As can be seen, only a single cooling water pump 12 is provided in the entire cooling circuit.
- a 3/2-way valve 7 which divides the cooling medium flow or working medium flow into two directions, namely in the direction of the hydrodynamic coupling 4 and in the direction of the motor 1.
- the working space of the hydrodynamic coupling 4 should now be targeted are emptied, whereby emptying also means an emptying to a partial filling and complete emptying, the changeover valve 7 is switched from the position shown (in the drawing in the direction to the left), so that the flow of working medium in the direction of the hydrodynamic coupling 4 is interrupted.
- the working space of the hydrodynamic coupling 4 is emptied accordingly, specifically via the line branch 6.1 of the cooling circuit 6, in which the outlet control valve 19 is connected.
- the effective flow cross-section of the line which discharges the working medium from the hydrodynamic coupling 4 can be set by means of the outlet control valve 19.
- the outlet control valve 19 can advantageously be arranged directly on the hydrodynamic clutch 4 or in the hydrodynamic clutch 4, but it is also possible to arrange the outlet control valve 19 in a line carrying the working medium behind the hydrodynamic clutch 4.
- the outlet control valve 19 is not absolutely necessary for the control according to the invention, but merely represents an option for faster emptying.
- the hydrodynamic chamber could be emptied Coupling 4 also use a throttle (not shown). In this case, there would always be a flow into the working space of the hydrodynamic clutch 4, which would be throttled accordingly when switching from clutch operation to retarder operation.
- the 3/2-way valve 7 is shown again in detail in FIG. As can be seen, it has two switching positions, namely switching position I, in which the working medium flow supplied via the connection 7.1 is divided between the two outlets 7.2 and 7.3, the outlet 7.2 leading to the hydrodynamic coupling 4 and the outlet 7.3 to the internal combustion engine 1 , as shown in Figure 2.
- switching position I in which the working medium flow supplied via the connection 7.1 is divided between the two outlets 7.2 and 7.3, the outlet 7.2 leading to the hydrodynamic coupling 4 and the outlet 7.3 to the internal combustion engine 1 , as shown in Figure 2.
- switch position II the working medium supplied via connection 7.1 is only used for outlet 7.3, i.e. H. in the direction of the internal combustion engine 1, while the outlet 7.2 is shut off.
- the working space of the hydrodynamic clutch is advantageously emptied to a predetermined filling level before mechanical braking and / or when the primary wheel of the hydrodynamic clutch is mechanically braked.
- this degree of filling can be determined, for example, by a predetermined period of time over which the work space is emptied.
- the valve 7 can be switched to the position II for a specific time interval, and alternatively or additionally the cross section of the outlet control valve 19 can be enlarged for a specific period of time.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Throttle Valves Provided In The Intake System Or In The Exhaust System (AREA)
- Transmission Of Braking Force In Braking Systems (AREA)
- Supercharger (AREA)
- Control Of Vehicle Engines Or Engines For Specific Uses (AREA)
- Control Of Fluid Gearings (AREA)
- Braking Arrangements (AREA)
Abstract
Description
Claims
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/583,911 US20070275820A1 (en) | 2003-12-20 | 2004-11-26 | Drive Train With Exhaust Gas Utilization and Control Method |
EP04798084A EP1694949A1 (de) | 2003-12-20 | 2004-11-26 | Antriebsstrang mit abgasnutzung und steuerungsverfahren |
JP2006544254A JP2007515585A (ja) | 2003-12-20 | 2004-11-26 | 排気エネルギ利用式動力伝達系およびその制御方法 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10360155.4 | 2003-12-20 | ||
DE10360155A DE10360155A1 (de) | 2003-12-20 | 2003-12-20 | Antriebsstrang mit Abgasnutzung und Steuerungsverfahren |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005064137A1 true WO2005064137A1 (de) | 2005-07-14 |
Family
ID=34683682
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2004/013407 WO2005064137A1 (de) | 2003-12-20 | 2004-11-26 | Antriebsstrang mit abgasnutzung und steuerungsverfahren |
Country Status (8)
Country | Link |
---|---|
US (1) | US20070275820A1 (de) |
EP (1) | EP1694949A1 (de) |
JP (1) | JP2007515585A (de) |
KR (1) | KR100838588B1 (de) |
CN (1) | CN100580232C (de) |
DE (1) | DE10360155A1 (de) |
RU (1) | RU2348821C2 (de) |
WO (1) | WO2005064137A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006013003B3 (de) * | 2006-03-22 | 2007-09-20 | Voith Turbo Gmbh & Co. Kg | Hydrodynamische Baugruppe mit einem Retarder und einer hydrodynamischen Kupplung |
WO2011160833A1 (en) * | 2010-06-22 | 2011-12-29 | Volvo Lastvagnar Ab | A turbo compound transmission and a method for controlling a turbo compound transmission |
Families Citing this family (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006011987A1 (de) * | 2006-03-16 | 2007-09-20 | Daimlerchrysler Ag | Antriebsstrang mit einem Turboverbundsystem |
DE102006028235A1 (de) * | 2006-06-20 | 2007-12-27 | Daimlerchrysler Ag | Turbocompound |
DE102007006420A1 (de) * | 2007-02-05 | 2008-08-07 | Voith Patent Gmbh | Kraftfahrzeugantriebsstrang eines Kraftfahrzeugs mit einem Druckluftsystem |
DE102007022042A1 (de) * | 2007-05-08 | 2008-11-13 | Voith Patent Gmbh | Antriebsstrang, insbesondere für Kraftfahrzeuge |
EP2340366B1 (de) * | 2008-10-30 | 2015-06-17 | Volvo Lastvagnar AB | Vorrichtung und verfahren zur automatischen einstellung des drehmomentübertragungsvermögens eines turbocompound-getriebes |
DE102011012861A1 (de) * | 2011-03-02 | 2012-09-06 | Voith Patent Gmbh | Turbo-Compound-System, insbesondere eines Kraftfahrzeugs |
CN103216313A (zh) * | 2013-03-26 | 2013-07-24 | 龙口中宇热管理系统科技有限公司 | 柔性动力涡轮装置 |
JP6184741B2 (ja) * | 2013-05-15 | 2017-08-23 | 日野自動車株式会社 | 内燃機関 |
DE102014107126A1 (de) * | 2014-05-20 | 2015-11-26 | Harald Wenzel | Mehrstufige Verdichteranlage zur Erzeugung eines komprimierten Gase |
DE102017201840A1 (de) | 2017-02-06 | 2018-08-09 | Mahle International Gmbh | Brennkraftmaschinenanordnung |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3904399A1 (de) * | 1989-02-14 | 1990-08-16 | Renk Tacke Gmbh | Abgasenergie-rueckgewinnungseinrichtung |
WO2002070877A1 (de) * | 2001-03-01 | 2002-09-12 | Voith Turbo Gmbh & Co. Kg | Antriebseinheit mit einem verbrennungsmotor und einem abgasturbolader |
EP1473450A1 (de) * | 2003-04-30 | 2004-11-03 | Voith Turbo GmbH & Co. KG | Kraftfahrzeugantriebsstrang mit einer Abgasnutzturbine und einer hydrodynamischer Kupplung |
Family Cites Families (13)
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US2375852A (en) * | 1941-05-17 | 1945-05-15 | Sulzer Ag | Reversible supercharged twostroke internal-combustion engine |
US3058296A (en) * | 1956-09-08 | 1962-10-16 | Daimler Benz Ag | Fan driving system including variable slip hydro-kinetic coupling |
US4452043A (en) * | 1980-07-22 | 1984-06-05 | South Western Industrial Research Limited | Differential compound engine |
JPS63142U (de) * | 1986-06-17 | 1988-01-05 | ||
JPS63162936A (ja) * | 1986-12-26 | 1988-07-06 | Isuzu Motors Ltd | タ−ボコンパウンドエンジン |
EP0292010B1 (de) * | 1987-05-22 | 1991-11-06 | Isuzu Motors Limited | Motorbremssystem |
JPS6435026A (en) * | 1987-07-30 | 1989-02-06 | Isuzu Motors Ltd | Turbo compound engine |
JPH0639901B2 (ja) * | 1987-10-28 | 1994-05-25 | いすゞ自動車株式会社 | ターボコンパウンドエンジン |
JPH01257722A (ja) * | 1988-04-08 | 1989-10-13 | Komatsu Ltd | ターボコンパウンド機関の動力伝達装置 |
US5119633A (en) * | 1990-09-25 | 1992-06-09 | Cummins Engine Company, Inc. | Power turbine bypass for improved compression braking |
DE4429855C1 (de) * | 1994-08-23 | 1995-08-17 | Daimler Benz Ag | Aufgeladene Brennkraftmaschine mit mechanischer Hochtriebsmöglichkeit eines Abgasturboladers |
DE10360055A1 (de) * | 2003-12-22 | 2005-07-21 | Voith Turbo Gmbh & Co. Kg | Hydrodynamische Kupplung |
DE102004002215B3 (de) * | 2004-01-15 | 2005-09-08 | Voith Turbo Gmbh & Co. Kg | Antriebskraftübertragungsvorrichtung mit hydrodynamischer Gegenlaufkupplung |
-
2003
- 2003-12-20 DE DE10360155A patent/DE10360155A1/de not_active Ceased
-
2004
- 2004-11-26 JP JP2006544254A patent/JP2007515585A/ja active Pending
- 2004-11-26 WO PCT/EP2004/013407 patent/WO2005064137A1/de active Application Filing
- 2004-11-26 RU RU2006126159/06A patent/RU2348821C2/ru not_active IP Right Cessation
- 2004-11-26 CN CN200480038217A patent/CN100580232C/zh not_active Expired - Fee Related
- 2004-11-26 KR KR1020067011888A patent/KR100838588B1/ko not_active IP Right Cessation
- 2004-11-26 EP EP04798084A patent/EP1694949A1/de not_active Withdrawn
- 2004-11-26 US US10/583,911 patent/US20070275820A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3904399A1 (de) * | 1989-02-14 | 1990-08-16 | Renk Tacke Gmbh | Abgasenergie-rueckgewinnungseinrichtung |
WO2002070877A1 (de) * | 2001-03-01 | 2002-09-12 | Voith Turbo Gmbh & Co. Kg | Antriebseinheit mit einem verbrennungsmotor und einem abgasturbolader |
EP1473450A1 (de) * | 2003-04-30 | 2004-11-03 | Voith Turbo GmbH & Co. KG | Kraftfahrzeugantriebsstrang mit einer Abgasnutzturbine und einer hydrodynamischer Kupplung |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006013003B3 (de) * | 2006-03-22 | 2007-09-20 | Voith Turbo Gmbh & Co. Kg | Hydrodynamische Baugruppe mit einem Retarder und einer hydrodynamischen Kupplung |
WO2011160833A1 (en) * | 2010-06-22 | 2011-12-29 | Volvo Lastvagnar Ab | A turbo compound transmission and a method for controlling a turbo compound transmission |
US9127589B2 (en) | 2010-06-22 | 2015-09-08 | Volvo Lastvagnar Ab | Turbo compound transmission and a method for controlling a turbo compound transmission |
Also Published As
Publication number | Publication date |
---|---|
KR20060109491A (ko) | 2006-10-20 |
CN100580232C (zh) | 2010-01-13 |
CN1898463A (zh) | 2007-01-17 |
US20070275820A1 (en) | 2007-11-29 |
JP2007515585A (ja) | 2007-06-14 |
RU2006126159A (ru) | 2008-01-27 |
EP1694949A1 (de) | 2006-08-30 |
DE10360155A1 (de) | 2005-07-21 |
RU2348821C2 (ru) | 2009-03-10 |
KR100838588B1 (ko) | 2008-06-19 |
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