WO2010050856A1 - A device and method for automatically adjusting torque transmitting ability of a turbocompound transmission - Google Patents
A device and method for automatically adjusting torque transmitting ability of a turbocompound transmission Download PDFInfo
- Publication number
- WO2010050856A1 WO2010050856A1 PCT/SE2008/000621 SE2008000621W WO2010050856A1 WO 2010050856 A1 WO2010050856 A1 WO 2010050856A1 SE 2008000621 W SE2008000621 W SE 2008000621W WO 2010050856 A1 WO2010050856 A1 WO 2010050856A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- combustion engine
- hydrodynamic coupling
- power turbine
- braking
- transmission
- 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
-
- 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 present invention relates to a device and method for controlling the torque transmitting ability of a transmission arranged between a crankshaft of an turbocompound combustion engine and a power turbine of said turbocompound combustion engine.
- the invention will find its application in connection with automotive vehicles, and relates to a device (see claim 1) and method (see claims 6 and 10) for improved control of said transmission.
- the invention also relates to a computer program, when run on a computer, computer program product and a storage medium, such as a computer memory.
- a turbocompound combustion engine such as disclosed in for example US5884482, is equipped with a turbocharger turbine arranged for receiving exhaust gas from said combustion engine.
- Such a turbocompound combustion engine is further equipped with a power turbine arranged for receiving said exhaust gas from said turbocharger turbine.
- Pressure force from the exhaust gases is transmitted to a crank shaft of the engine via a transmission to be used for vehicle propulsion.
- Said transmission driven by the power turbine and connected to the crankshaft comprises a hydrodynamic coupling.
- the hydrodynamic coupling is used in order to avoid transmission of damaging irregular rotation to the power turbine and gearing on the power turbine side of the hydrodynamic coupling.
- the irregular rotation is the result of the combustions occurring in the different cylinders of the engine during a relatively very short period of time of a turn of the crank shaft.
- a combustion creates a sudden temporary rotational acceleration of the crank shaft, which has negative exhaustive effect on mechanical parts of the engine.
- Said hydrodynamic coupling reduces the transmission of said negative effect.
- a technical problem addressed by the present invention is how to provide a more advanced transmission between the power turbine and the crank shaft, which will be able to offer an increased overall combustion engine control.
- An object of the present invention is to provide an improved transmission between the power turbine and the crank shaft that will increase the controllability of the hydrodynamic coupling and the power turbine.
- the present invention seeks to provide increased control of the transmission between the power turbine and the crank shaft in order to increase the overall performance of the engine, especially for lowering noise and exhaust emissions from the engine, and accelerated heating of the combustion engine during cold starts but also for a better auxiliary braking performance .
- the primary object of the present invention is to solve the above problems and to provide an improved method for controlling said transmission. This is achieved by a device as discussed in the introduction, the characteristics of which are defined by claim 1. The object is also achieved by a method as discussed in the introduction, the characteristics of which are defined by claims 6 and 10 respectively.
- the device according to the invention is a combustion engine of the turbocompound type, which comprises
- a turbocharger turbine arranged for receiving exhaust gas from a combustion in said combustion engine; a power turbine arranged for receiving said exhaust gas from said turbocharger turbine; a transmission driven by the power turbine and connected to a crankshaft of the combustion engine; said transmission comprising a hydrodynamic coupling.
- This embodiment is characterized in that a braking device is arranged for braking a power turbine side of the hydrodynamic coupling.
- said torque transmitting ability of said hydrodynamic coupling is continuously adjustable.
- said braking device is arranged to brake said power turbine side of the hydrodynamic coupling to at least a rotational speed below a rotational speed of a combustion engine side of the hydrodynamic coupling.
- said braking device is arranged to brake said power turbine side of the hydrodynamic coupling to zero rotational speed.
- said torque transmitting ability of said hydrodynamic coupling is arranged to be adjustable when said braking device is braking said power turbine side of the hydrodynamic coupling to a rotational speed at least below a rotational speed of said combustion engine side of the hydrodynamic coupling in order to continuously adjust retarding torque.
- said combustion engine further comprises a first cooling device of said hydrodynamic coupling that is integrated with a second cooling device of said combustion engine, and where the embodiment according to the invention is characterized in that said first and second cooling devices are arranged to transport heat to said combustion engine during a cold start of said combustion engine and where said heat is produced when said braking device is braking said power turbine side.
- the method according to the invention is a method for automatically adjusting torque transmitting ability of a transmission arranged between a power turbine and a crank shaft in a turbocompound combustion engine, said transmission comprising a hydrodynamic coupling, and said method comprising the steps of:
- said method is characterized in braking said power turbine side of the hydrodynamic coupling to at least a rotational speed below a rotational speed of a turbocompound combustion engine side of the hydrodynamic coupling. In one further embodiment said power turbine side is braked to zero rotational speed.
- said method is characterized in that continuously adjusting — £ — said torque transmitting ability in such a way and until a registered value for each of said one or several parameters a to c has returned back and passed said predetermined value in an opposite direction compared to said first direction.
- said method is characterized in that releasing said braking device when a registered value for each of said one or several parameters a to c has returned back and passed said predetermined value in an opposite direction compared to said first direction.
- the method according to the invention is also a method for automatically adjusting torque transmitting ability of a transmission arranged between a power turbine and a crank shaft in a turbocompound combustion engine, said transmission comprising a hydrodynamic coupling, and said method comprising at least the steps of: - registering that auxiliary braking power is demanded;
- said braking of the power turbine side is performed only during a decrease of output torque of said turbocompound combustion engine in order to substantially decrease exhaust gas pressure produced by said turbocompound combustion engine.
- braking of the power turbine side is performed only when exhaust gas flow is bypassed said power turbine in order to substantially decrease exhaust gas pressure driving said power turbine.
- said power turbine side is braked to zero rotational speed.
- the invention also relates to a computer program comprising program code means for performing all the steps of any one of the method claims when said program is run on a computer.
- the invention also relates to a computer program product comprising program code means stored on a computer readable medium for performing all steps of anyone of the method claims when said program product is run on a computer.
- the invention also relates to a storage medium, such as a computer memory or a nonvolatile data storage medium, for use in a computing environment, the memory comprising a computer readable program code to perform the method of method claim.
- a storage medium such as a computer memory or a nonvolatile data storage medium
- Figure 1 diagrammatically shows a view of a turbocompound combustion engine according to one embodiment of the invention.
- Figure 2 diagrammatically shows a more detailed view of the transmission arranged between a crankshaft and a power turbine of said turbocompound combustion engine.
- Figure 3 discloses a computer arrangement for controlling said transmission according to the invention.
- Figure one discloses one example embodiment of the invention, where a turbocompound combustion engine 1 comprises at least one cylinder-piston arrangement 2 connected to a crankshaft 3 in a known manner.
- the crankshaft can be connected to driven wheels (not shown) of a vehicle (not shown) .
- said crankshaft 3 is connected to a power turbine 4, via a transmission comprising a first set of gear wheels 5, a hydrodynamic coupling ⁇ , a braking device 7 and a second set of gear wheels 8.
- the power turbine 4 can be driven by exhaust gases from the combustion in said cylinder.
- the exhaust gases are provided to said power turbine 4 via a first exhaust pipe 9, a turbocharger turbine 10 according to known art arranged for receiving exhaust gas from a combustion in said cylinder and for supercharging inlet air to the combustion in said cylinder, and a second exhaust pipe 11. Down stream of said power turbine 4 said exhaust gases can be further processed in an exhaust after treatment system 12 according to known art.
- the torque transmitting ability of the hydrodynamic coupling and the braking arrangement can be controlled by a control unit 13. Said control unit can be arranged to control said hydrodynamic coupling and the braking arrangement in dependence of different parameters, which can be measured by different sensors 14.
- Figure.2 discloses a more detailed exemplified embodiment of said transmission 21 according to the invention.
- two of the three gear wheels in the first gear wheel set 5 are not disclosed in figure 2.
- Only one gear wheel 25 is disclosed.
- gear wheel 28 is disclosed of said second gear wheel set 8.
- Gear wheel 25 is non- rotatably attached to a shaft 22, which is non- rotatably attached to an engine ' side of said hydrodynamic coupling 23.
- a power turbine side of the hydrodynamic coupling 24 is via another shaft 25 non- rotatably connected to said gear wheel 28 and also an outer wall 34 of the hydrodynamic coupling.
- the gear wheel 28 meshes with a gear wheel connected to said power turbine 4.
- a space 29 between the two sides of the hydrodynamic coupling can be filled with different volumes of a working fluid (for example oil) .
- the amount of working fluid in said space decides the torque transmitting ability of the hydrodynamic coupling according to known art.
- the working fluid flows into the hydrodynamic coupling via a channel 30 in said shaft (see arrow 31) .
- the emptying of working fluid is in the exemplified embodiment regulated by a tube 32, which can be positioned in different levels in an axial direction of the tube (indicated by arrows 33) is performed according to known art (see for example GB2182121) .
- the level of the tube decides the amount of working fluid in said space and, thus, the torque transmitting ability of the hydrodynamic coupling.
- the braking device 7 disclosed in figure 1 can be arranged to lock or brake one of ' the parts fixedly or rotatably connected to the power turbine side of the hydrodynamic coupling.
- Said brake or lock as such is known art, and can be realized for example via one or several wet couplings or other known braking arrangement.
- Said parts can be one of or several of the parts between said power turbine side of the hydrodynamic coupling 24 and said power turbine 4.
- the braking device when braking, slows down or hinders the power turbine side of the hydrodynamic coupling from rotating faster that the engine side of the hydrodynamic coupling 6.
- the tube 33 can be positioned with a swivel arm (not shown) connected to a lower end (when looking at figure 2) of the tube 33.
- the arm can be driven by, for example, an electric servo motor and controlled by said control unit 13. In this way the torque transmitting ability of said hydrodynamic coupling can be continuously adjustable both when the braking device 7 is active, that is, braking and when said braking device is released.
- the working fluid flowing through said hydrodynamic coupling can be part of a closed loop fluid system 15 with connecting pipes and a fluid pump.
- Said fluid system 15 can also be a part of or integrated with an lubricating system of said turbocompound combustion engine 1.
- This heat can be cooled by a cooling system integrated in said fluid system 15, which cooling system can be a cooling system of the turbocompound combustion engine or a separate hydrodynamic coupling cooling system.
- control unit 13 is programmed to automatically adjust the torque transmitting ability of said transmission .
- the control unit is programmed to continuously register a value for one or several of; a. engine load parameter for said combustion engine and/or, b. temperature in said combustion engine and/or, c. parameters for indicating NVH in said transmission;
- control unit 13 is programmed to brake a power turbine side of said hydrodynamic coupling and to continuously adjust said torque transmitting ability of said hydrodynamic coupling in dependence of the development of one or several of said parameters a to c.
- the engine load parameter can be measured by said sensor 14 in a known way, for example via torque sensor or measuring injected fuel amount in the engine and calculating torque to be produced from the injected fuel amount.
- the control unit can be programmed to brake the power turbine side of said hydrodynamic coupling and to continuously adjust said torque transmitting ability of said hydrodynamic coupling, when registering an engine load value below a predetermined first engine load value, for example corresponding to when the engine is idling.
- said control can be programmed to adjust the torque transmitting performance (retarding performance when braking device is active) of said hydrodynamic coupling in such a way that the engine will be exposed to an engine load that is at least said predetermined first engine load value.
- said control unit can be programmed to expose the engine to a load that lies within an interval of which range lies just above said predetermined first engine load value. Noxious emissions produced in a combustion engine during low engine load will be decreased.
- said control unit can be programmed to release said braking device, thus the retarding effect from the hydrodynamic coupling will end, and the control unit will regulate the torque transmitting ability of the hydrodynamic coupling to a level which results in a rotational speed of the power turbine that will be optimized for best power turbine efficiency.
- control unit can be programmed to register the temperature of the combustion engine, for example in the cooling system of the combustion engine via a temperature sensor 14, which can also be used in said cooling system of the combustion engine to regulate the cooling performance of said cooling system.
- control unit can be programmed to brake the power turbine side of said hydrodynamic coupling and to continuously adjust said torque transmitting ability of said hydrodynamic coupling, when registering a temperature value below a predetermined first engine temperature value, for example a value that indicates the limit for a combustion engine cold start.
- said control unit can be programmed to adjust the torque transmitting performance (retarding performance when the braking device is active) of said hydrodynamic coupling in such a way that the engine will be exposed to an increased engine load that will accelerate engine temperature increase so that engine working time during cold start temperatures will decrease.
- the amount of working fluid in said hydrodynamic coupling can be controlled in such a way so that a certain amount of heat will be produced, which for a specific engine and environmental configuration gives a certain temperature rise in said engine. This is beneficial with regard to decreasing noxious emissions produced in a combustion engine.
- said control unit is programmed to release said braking device and said hydrodynamic coupling will be controlled as to maximize efficiency of said power turbine.
- said control unit can be programmed to register said parameters for indicating NVH in said transmission (especially NVH in gear wheels 5) .
- Said parameters for indicating NVH can for example be a combination of amount of injected fuel in the combustion engine and combustion engine rotational speed (a combustion engine rotational speed map) . NVH is most likely to occur during idle rotational speed of said combustion engine in combination with low load on the combustion engine.
- said control can be programmed to adjust the torque transmitting performance (retarding performance when the braking device is active) of said hydrodynamic coupling in such a way that the engine will be exposed to an slightly increased engine load that will tighten the transmission between the crank shaft and the braking device and, thus, no NVH will occur between the gear wheels 5.
- the benefit of this is that noise emissions from said transmission will decrease.
- Methods for cylinder balancing or correction of amount of injected fuel in each cylinder in relation to injected fuel amount in the other cylinders is something that is well known in the art.
- the registration of NVH. as described above can be a measure of how well the balancing of fuel amount between the cylinders has been performed. Irregularities between the cylinders can create noise from rattling gear wheels such as gear wheels 5.
- control unit can be arranged to control said hydrodynamic coupling and the braking arrangement in dependence of each of said mentioned parameters, which can be measured by different sensors 14.
- said control unit 13 can be programmed to register a value for two or several of said three parameters and control said hydrodynamic coupling and said braking arrangement in dependence of the development of those parameters.
- said hydrodynamic coupling is used as an auxiliary vehicle brake, which completes the braking power of an, for example, engine compression brake (not showed) arranged in said turbocompound combustion engine 1.
- said control unit 13 can be programmed to activate said braking device 7 and fill said hydrodynamic coupling so that an additional braking power will be transmitted to driven wheels of the vehicle.
- the braking power of an engine compression brake according to known art is dependent of rotational speed of the combustion engine 1. Said compression brake produces more braking power at high rotational speeds compared to low rotational speeds.
- the use of said hydrodynamic coupling as an auxiliary brake is especially beneficial at low engine rotational speeds.
- the braking power produced by said hydrodynamic coupling auxiliary brake can be controlled by varying the filling level of said hydrodynamic coupling and/or by varying braking power from the braking device 7. This can be done in dependence of, for example, at least demanded vehicle speed.
- said control unit can be programmed to only activate said hydrodynamic coupling auxiliary brake during a gearshift of a gearbox arranged between said combustion engine 1 and said driven wheels.
- a gearshift output torque from the engine is decreased to around zero.
- exhaust gas pressure is decreased substantially and said turbine 4 will be substantially relieved from driving force from the exhaust gases.
- said hydrodynamic coupling auxiliary brake can be activated during a decrease of combustion engine output torque without a gearshift. This will also decrease driving force on the power turbine from said exhaust gas pressure. Said decrease of engine output torque can be an output torque decrease due to ordinary engine control or engine control due to demanded auxiliary braking power.
- said hydrodynamic coupling auxiliary brake can be activated only during when the exhaust gas flow bypasses said power turbine. This can be done by a bypassing conduit (not shown) connecting the second exhaust pipe 11 with the aftertreatment system 12.
- the exhaust flow through said bypass conduit can be controlled by said control unit 13 through a valve arranged in said bypass conduit according to known art. This will also substantially decrease exhaust gas pressure driving said power turbine and stress on the power turbine 4 and said second gear wheel set 8 will be minimized during the retardation of said turbine side .
- control unit can be programmed to control the filling level of said hydrodynamic coupling (that is torque transmitting ability of said hydrodynamic coupling) so that overspeed of said power turbine 4 is avoided.
- said hydrodynamic coupling can be used alone as an auxiliary brake, that is without additional braking power from other auxiliary brakes such as an engine compression brake.
- the amount of braking power must be so that rotational speed of the turbine side of the hydrodynamic coupling drops below the rotational speed of the engine side of the hydrodynamic coupling in order to gain the mentioned beneficial effects of the different embodiments of the invention.
- the most powerful beneficial effect of the different embodiments of the invention will usually occur when the power turbine side of the hydrodynamic coupling is braked to zero rotational speed.
- said control unit 13 can be programmed to brake said power turbine side to zero rotational speed in all above mentioned embodiments of the invention.
- the only regulation of the retarding performance of the hydrodynamic coupling will be performed by regulating the torque transmitting ability of the hydrodynamic coupling 6.
- Figure 3 shows an apparatus 500 according to one embodiment of the invention, comprising a nonvolatile memory 520, a processor 510 and a read and write memory
- the memory 520 has a first memory part 530, in which a computer program for controlling the apparatus
- the computer program in the memory part 530 for controlling the apparatus 500 can be an operating system.
- the apparatus 500 can be enclosed in, for example, a control unit, such as the control unit 13.
- the data- processing unit 510 can comprise, for example, a microcomputer.
- the memory 520 also has a second memory part 540, in which a program for controlling the transmission according to the invention is stored.
- the program for controlling the transmission is stored in a separate nonvolatile data storage medium 550, such as, for example, a CD or an exchangeable semiconductor memory.
- the program can be stored in an executable form or in a compressed state.
- the data-processing unit 510 runs a specific function, it should be clear that the data-processing unit 510 is running a specific part of the program stored in the memory 540 or a specific part of the program stored in the nonvolatile recording medium 550.
- the data-processing unit 510 is tailored for communication with the memory 550 through a data bus 514.
- the data-processing unit 510 is also tailored for communication with the memory 520 through a data bus 512.
- the data-processing unit 510 is tailored for communication with the memory 560 through a data bus 511.
- the data-processing unit 510 is also tailored for communication with a data port 590 by the use of a data bus 515.
- the method according to the present invention can be executed by the data-processing unit 510, by the data- processing unit 510 running the program stored in the memory 540 or the program stored in the nonvolatile recording medium 550.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
- Braking Arrangements (AREA)
Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP08877822.0A EP2340366B1 (en) | 2008-10-30 | 2008-10-30 | A device and method for automatically adjusting torque transmitting ability of a turbocompound transmission |
US13/120,472 US9932890B2 (en) | 2008-10-30 | 2008-10-30 | Device and method for automatically adjusting torque transmitting ability of a turbocompound transmission |
PCT/SE2008/000621 WO2010050856A1 (en) | 2008-10-30 | 2008-10-30 | A device and method for automatically adjusting torque transmitting ability of a turbocompound transmission |
RU2011121517/06A RU2478802C2 (en) | 2008-10-30 | 2008-10-30 | Automatic control method of turbo-compound transmission ability to transfer torque moment |
CN200880131586.8A CN102187071B (en) | 2008-10-30 | 2008-10-30 | For the method automatically adjusted to the torque-transfer capability of turbo compound transmission |
BRPI0823134-6A BRPI0823134A2 (en) | 2008-10-30 | 2008-10-30 | A device and method for automatically adjusting the torque transmission capacity of a composite turbo transmission. |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/SE2008/000621 WO2010050856A1 (en) | 2008-10-30 | 2008-10-30 | A device and method for automatically adjusting torque transmitting ability of a turbocompound transmission |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010050856A1 true WO2010050856A1 (en) | 2010-05-06 |
Family
ID=42129039
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/SE2008/000621 WO2010050856A1 (en) | 2008-10-30 | 2008-10-30 | A device and method for automatically adjusting torque transmitting ability of a turbocompound transmission |
Country Status (6)
Country | Link |
---|---|
US (1) | US9932890B2 (en) |
EP (1) | EP2340366B1 (en) |
CN (1) | CN102187071B (en) |
BR (1) | BRPI0823134A2 (en) |
RU (1) | RU2478802C2 (en) |
WO (1) | WO2010050856A1 (en) |
Cited By (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2011160833A1 (en) * | 2010-06-22 | 2011-12-29 | Volvo Lastvagnar Ab | A turbo compound transmission and a method for controlling a turbo compound transmission |
CN103189617A (en) * | 2011-03-02 | 2013-07-03 | 福伊特专利公司 | Turbo-compound system, in particular of a motor vehicle |
US8866334B2 (en) | 2010-03-02 | 2014-10-21 | Icr Turbine Engine Corporation | Dispatchable power from a renewable energy facility |
US8984895B2 (en) | 2010-07-09 | 2015-03-24 | Icr Turbine Engine Corporation | Metallic ceramic spool for a gas turbine engine |
US9051873B2 (en) | 2011-05-20 | 2015-06-09 | Icr Turbine Engine Corporation | Ceramic-to-metal turbine shaft attachment |
WO2015180745A1 (en) * | 2014-05-28 | 2015-12-03 | Volvo Truck Corporation | A turbocompound unit |
US10094288B2 (en) | 2012-07-24 | 2018-10-09 | Icr Turbine Engine Corporation | Ceramic-to-metal turbine volute attachment for a gas turbine engine |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10344644B2 (en) * | 2013-12-19 | 2019-07-09 | Volvo Truck Corporation | Engine arrangement and method for heating exhaust after treatment equipment in an exhaust after treatment system |
US9855936B2 (en) * | 2015-10-28 | 2018-01-02 | Ford Global Technologies, Llc | System and method to improve engagement shift quality in automatic transmissions using engagement brake torque control |
CN105464769B (en) * | 2015-12-30 | 2017-11-17 | 东风商用车有限公司 | Double-flow-passage power turbine system and control method thereof |
CN108223107B (en) * | 2017-12-08 | 2021-01-15 | 中国北方发动机研究所(天津) | Flexible supercharged engine of electromechanical complex |
FR3082225B1 (en) * | 2018-06-07 | 2020-06-05 | Safran Helicopter Engines | ASYMMETRIC PROPULSIVE HEAT RECOVERY SYSTEM |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2182121A (en) | 1985-10-26 | 1987-05-07 | Dowty Meco Ltd | Hydrodynamic couplings and control means therefor |
US5884482A (en) | 1994-05-13 | 1999-03-23 | Scania Cv Aktiebolag | Combustion engine of turbocompound type with exhaust gas brake |
US20040068986A1 (en) | 2001-03-01 | 2004-04-15 | Friedrich Juergen | Drive unit with an internal combustion engine and an exhaust gas turbocharger |
US20070012037A1 (en) * | 2003-12-22 | 2007-01-18 | Voith Turbo Gmbh & Co. | Hydrodynamic coupling |
US20070275820A1 (en) | 2003-12-20 | 2007-11-29 | Markus Kley | Drive Train With Exhaust Gas Utilization and Control Method |
Family Cites Families (59)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3023639A (en) * | 1959-03-25 | 1962-03-06 | Voith Getriebe Kg | Transmission brake system |
DE2203319A1 (en) * | 1972-01-25 | 1973-08-02 | Daimler Benz Ag | PERMANENT BRAKE FOR VEHICLES, ESPECIALLY FOR MOTOR VEHICLES, ESPECIALLY HEAVY COMMERCIAL VEHICLES |
US3805928A (en) * | 1972-08-18 | 1974-04-23 | Bennes Marrel | Regulation device for hydraulic turbo-retarders |
US4244187A (en) * | 1979-03-30 | 1981-01-13 | Lane Jeff K | Vehicle engine with turbine bypass for exhaust treatment device warm-up |
JPS58200855A (en) * | 1982-05-20 | 1983-11-22 | Nissan Motor Co Ltd | Speed-change control method for v-belt type of stepless tansmission gear box |
DE3224006A1 (en) * | 1982-06-26 | 1983-12-29 | J.M. Voith Gmbh, 7920 Heidenheim | Turbocharger group for internal-combustion engines |
EP0292010B1 (en) * | 1987-05-22 | 1991-11-06 | Isuzu Motors Limited | Engine braking system |
SU1537852A1 (en) * | 1988-04-14 | 1990-01-23 | Волгоградский моторный завод | Ic-engine |
SU1714172A1 (en) * | 1989-08-07 | 1992-02-23 | Камское объединение по производству большегрузных автомобилей | Turbocompound internal combustion engine |
SE469850B (en) * | 1990-07-10 | 1993-09-27 | Saab Scania Ab | Monitoring arrangement for a turbo compound engine system |
DE4133736C2 (en) * | 1991-10-11 | 1993-10-07 | Daimler Benz Ag | Exhaust gas turbocharger for an internal combustion engine |
US5158056A (en) * | 1991-11-04 | 1992-10-27 | Torque Converters, Inc. | Integral magnetic ignition pickup trigger |
US5890468A (en) * | 1994-01-25 | 1999-04-06 | Komatsu Ltd. | Differential driving supercharger and method for controlling the same |
SE502614C2 (en) * | 1994-03-29 | 1995-11-20 | Volvo Ab | Apparatus for controlling the engine braking power of an internal combustion engine |
SE502914C2 (en) * | 1994-06-17 | 1996-02-19 | Volvo Ab | Device for controlling the engine braking power of an internal combustion engine |
DE19532164A1 (en) * | 1995-08-31 | 1997-03-06 | Clouth Gummiwerke Ag | Drive system, in particular for a motor vehicle, and method for operating the same |
US5618242A (en) * | 1995-09-06 | 1997-04-08 | Wu; Cheng-Hsiung | Apparatus for torque-converter clutch transmission |
SE511836C2 (en) * | 1996-04-29 | 1999-12-06 | Volvo Ab | Arrangement and method of transmission of power in combustion engine |
JPH1038067A (en) * | 1996-07-18 | 1998-02-13 | Toyota Motor Corp | Control device of vehicle |
JP3358452B2 (en) * | 1996-07-22 | 2002-12-16 | 日産自動車株式会社 | Vehicle engine brake control device |
EP1346870B1 (en) * | 1998-04-17 | 2005-07-20 | Toyota Jidosha Kabushiki Kaisha | Control device for restarting engine of vehicle |
JP3799903B2 (en) * | 1999-02-24 | 2006-07-19 | 株式会社豊田自動織機 | Industrial vehicle parking brake device |
DE69901441T2 (en) * | 1999-07-06 | 2002-12-12 | Doornes Transmissie Bv | Method for operating a continuously variable transmission with a continuously sliding clutch |
SE521262C2 (en) * | 2000-06-28 | 2003-10-14 | Volvo Lastvagnar Ab | Combustion engine with exhaust gas recirculation |
EP1234129B1 (en) * | 2000-08-30 | 2005-10-12 | Voith Turbo GmbH & Co. KG | Method for regulating the speed of a drive motor |
EP1313967A1 (en) * | 2000-08-31 | 2003-05-28 | Voith Turbo GmbH & Co. KG | Starter unit and method for matching starter units in drive systems to different limiting conditions, in particular different drive engines |
US6508346B1 (en) * | 2000-10-16 | 2003-01-21 | Ford Global Technologies, Inc. | Torque converter assembly |
JP3642018B2 (en) * | 2000-10-27 | 2005-04-27 | 日産自動車株式会社 | Slip control device for torque converter |
SE519018C2 (en) * | 2000-11-27 | 2002-12-23 | Volvo Lastvagnar Ab | Enclosure for fluid lubricated rotating elements |
JP3939295B2 (en) * | 2001-06-26 | 2007-07-04 | ボルボ ラストバグナー アーベー | Exhaust turbine equipment |
JP2003097696A (en) * | 2001-09-25 | 2003-04-03 | Jatco Ltd | Lockup capacity control device on coasting of torque converter |
SE520230C2 (en) * | 2001-10-31 | 2003-06-10 | Volvo Lastvagnar Ab | Stepper gearbox for motor vehicles |
SE0200847L (en) * | 2002-03-19 | 2003-09-09 | Volvo Lastvagnar Ab | Hydrodynamic coupling |
JP2003314684A (en) * | 2002-03-26 | 2003-11-06 | Robert Bosch Gmbh | Method of protecting torque converter for automatic transmission from overheating, and driving slip control device equipped with protecting function |
DE10251620A1 (en) * | 2002-11-06 | 2004-05-19 | Bayerische Motoren Werke Ag | Control device for automatic transmission gear, comprising at least one sensor checking level of vibration for appropriate adjusting of slip |
DE10348967B4 (en) * | 2003-10-22 | 2006-11-02 | Voith Turbo Gmbh & Co. Kg | Method for optimizing the degree of utilization in a drive unit and drive unit |
US20050148478A1 (en) * | 2004-01-07 | 2005-07-07 | Nubar Ozbalik | Power transmission fluids with enhanced anti-shudder characteristics |
DE102004002215B3 (en) * | 2004-01-15 | 2005-09-08 | Voith Turbo Gmbh & Co. Kg | Driving force transmission device with hydrodynamic reverse clutch |
DE102004006358B4 (en) * | 2004-02-09 | 2012-11-15 | Voith Turbo Gmbh & Co. Kg | Temperature controlled hydrodynamic machine |
US7070032B2 (en) * | 2004-04-16 | 2006-07-04 | Borgwarner Inc. | Hydrodynamic coupling apparatus |
DE102004059833A1 (en) * | 2004-12-10 | 2006-06-14 | Voith Turbo Gmbh & Co. Kg | Method for controlling the maximum speed of a work machine and hydrodynamic coupling therefor |
DE102004059836A1 (en) * | 2004-12-10 | 2006-06-14 | Voith Turbo Gmbh & Co. Kg | Hydrodynamic coupling |
DE102005004058B3 (en) * | 2005-01-28 | 2006-05-24 | Voith Turbo Gmbh & Co. Kg | Turbo compound system with cylinder shaft and exhaust gas turbine |
US7485734B2 (en) * | 2005-01-28 | 2009-02-03 | Afton Chemical Corporation | Seal swell agent and process therefor |
WO2006085802A1 (en) * | 2005-02-11 | 2006-08-17 | Volvo Lastvagnar Ab | Device for combustion engine |
DE102005048530A1 (en) * | 2005-10-11 | 2007-04-12 | Daimlerchrysler Ag | Turbo charger monitoring method for motor vehicle, involves determining anticipated malfunction of turbo charger based of parameter, controlling turbo charger of vehicle, and reducing or limiting load of turbo charger |
US7277790B1 (en) * | 2006-04-25 | 2007-10-02 | Ut-Battelle, Llc | Combustion diagnostic for active engine feedback control |
EP2068042B1 (en) * | 2006-09-12 | 2012-08-08 | Toyota Jidosha Kabushiki Kaisha | Driving force control device for vehicle |
EP2084336B1 (en) * | 2006-10-06 | 2012-07-04 | Volvo Construction Equipment AB | A method for operating a working machine and a working machine |
US7912687B2 (en) * | 2006-12-29 | 2011-03-22 | Caterpillar Inc. | Methods of predicting cavitation damage |
DE102007022042A1 (en) * | 2007-05-08 | 2008-11-13 | Voith Patent Gmbh | Powertrain, especially for motor vehicles |
DK2071213T3 (en) * | 2007-12-11 | 2015-01-19 | Gen Electric | Gearbox noise reduction with electric drive control |
US20090192063A1 (en) * | 2008-01-25 | 2009-07-30 | Afton Chemical Corporation | Final Drive and Powershift Transmission Lubricants |
US7703788B2 (en) * | 2008-04-04 | 2010-04-27 | Tanouye Ted K | Force channeling mountain bike rear suspension |
DE102009005504A1 (en) * | 2009-01-19 | 2010-07-22 | Voith Patent Gmbh | Vehicle cooling circuit with a retarder or a hydrodynamic coupling |
US20100292937A1 (en) * | 2009-05-18 | 2010-11-18 | Diaa Hosny | Turbocharger bearing health monitor |
US8622859B2 (en) * | 2009-06-10 | 2014-01-07 | Czero Holding Company, Llc | Systems and methods for hybridization of a motor vehicle using hydraulic components |
US20110046029A1 (en) * | 2009-08-20 | 2011-02-24 | Milner Jeffrey L | Combinations of Phosphorus-Containing Compounds For Use As Anti-Wear Additives In Lubricant Compositions |
JP4923097B2 (en) * | 2009-11-30 | 2012-04-25 | 本田技研工業株式会社 | Baffle plate support structure for transmission |
-
2008
- 2008-10-30 EP EP08877822.0A patent/EP2340366B1/en active Active
- 2008-10-30 CN CN200880131586.8A patent/CN102187071B/en active Active
- 2008-10-30 US US13/120,472 patent/US9932890B2/en active Active
- 2008-10-30 RU RU2011121517/06A patent/RU2478802C2/en not_active IP Right Cessation
- 2008-10-30 WO PCT/SE2008/000621 patent/WO2010050856A1/en active Application Filing
- 2008-10-30 BR BRPI0823134-6A patent/BRPI0823134A2/en not_active IP Right Cessation
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB2182121A (en) | 1985-10-26 | 1987-05-07 | Dowty Meco Ltd | Hydrodynamic couplings and control means therefor |
US5884482A (en) | 1994-05-13 | 1999-03-23 | Scania Cv Aktiebolag | Combustion engine of turbocompound type with exhaust gas brake |
US20040068986A1 (en) | 2001-03-01 | 2004-04-15 | Friedrich Juergen | Drive unit with an internal combustion engine and an exhaust gas turbocharger |
US20070275820A1 (en) | 2003-12-20 | 2007-11-29 | Markus Kley | Drive Train With Exhaust Gas Utilization and Control Method |
US20070012037A1 (en) * | 2003-12-22 | 2007-01-18 | Voith Turbo Gmbh & Co. | Hydrodynamic coupling |
Non-Patent Citations (1)
Title |
---|
See also references of EP2340366A4 * |
Cited By (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8866334B2 (en) | 2010-03-02 | 2014-10-21 | Icr Turbine Engine Corporation | Dispatchable power from a renewable energy facility |
WO2011160833A1 (en) * | 2010-06-22 | 2011-12-29 | Volvo Lastvagnar Ab | A turbo compound transmission and a method for controlling a turbo compound transmission |
CN102947565A (en) * | 2010-06-22 | 2013-02-27 | 沃尔沃拉斯特瓦格纳公司 | A turbo compound transmission and a method for controlling a turbo compound transmission |
CN102947565B (en) * | 2010-06-22 | 2015-04-15 | 沃尔沃拉斯特瓦格纳公司 | 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 |
US8984895B2 (en) | 2010-07-09 | 2015-03-24 | Icr Turbine Engine Corporation | Metallic ceramic spool for a gas turbine engine |
CN103189617A (en) * | 2011-03-02 | 2013-07-03 | 福伊特专利公司 | Turbo-compound system, in particular of a motor vehicle |
US9051873B2 (en) | 2011-05-20 | 2015-06-09 | Icr Turbine Engine Corporation | Ceramic-to-metal turbine shaft attachment |
US10094288B2 (en) | 2012-07-24 | 2018-10-09 | Icr Turbine Engine Corporation | Ceramic-to-metal turbine volute attachment for a gas turbine engine |
WO2015180745A1 (en) * | 2014-05-28 | 2015-12-03 | Volvo Truck Corporation | A turbocompound unit |
JP2017524854A (en) * | 2014-05-28 | 2017-08-31 | ボルボトラックコーポレーション | Turbo compound equipment |
EP3273028A1 (en) * | 2014-05-28 | 2018-01-24 | Volvo Truck Corporation | A turbocompound unit |
Also Published As
Publication number | Publication date |
---|---|
BRPI0823134A2 (en) | 2015-06-16 |
EP2340366B1 (en) | 2015-06-17 |
RU2478802C2 (en) | 2013-04-10 |
CN102187071A (en) | 2011-09-14 |
EP2340366A1 (en) | 2011-07-06 |
US20110196587A1 (en) | 2011-08-11 |
CN102187071B (en) | 2015-11-25 |
EP2340366A4 (en) | 2014-05-14 |
RU2011121517A (en) | 2012-12-10 |
US9932890B2 (en) | 2018-04-03 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2340366B1 (en) | A device and method for automatically adjusting torque transmitting ability of a turbocompound transmission | |
US9797300B2 (en) | Supercharging system and method for operating a supercharging system | |
US8195370B2 (en) | Association of torque requesting modules in a coordinated torque architecture | |
JP5119541B2 (en) | Method and system for controlling engine speed, engine torque and torque converter output | |
JP4844342B2 (en) | Vehicle control device | |
RU147835U1 (en) | VEHICLE MANAGEMENT SYSTEM | |
CN106274881B (en) | Method and system for operating a driveline disconnect clutch | |
EP2573356B1 (en) | Supercharging system and method for operation | |
EP2634404B1 (en) | Turbocharge system | |
US20140031170A1 (en) | Method and system for operating a vehicle powertrain | |
US7534192B2 (en) | Vehicle power transmission device using a fluid coupling | |
CN102785663A (en) | Start-stop operation of an internal combustion engine of a motor vehicle | |
JP3846112B2 (en) | Drive device | |
JP5696433B2 (en) | Engine brake system for internal combustion engine and control method thereof | |
JP3166592B2 (en) | Engine for vehicles with mechanical supercharger | |
JP5742178B2 (en) | Engine brake system for internal combustion engine and control method thereof | |
JP2008115901A (en) | Control device for variable capacity type torque converter | |
BR112015025085B1 (en) | METHOD FOR THE PROPULSION OF A VEHICLE, COMPUTER READABLE MEDIA, SYSTEM FOR THE PROPULSION OF A VEHICLE, AND, VEHICLE | |
JP4840410B2 (en) | Exhaust gas recovery device | |
JPS595832A (en) | Turbocharger mechanism | |
CN115306538B (en) | Supercharging system of engine and control method thereof | |
JP2010031819A (en) | Control device for internal combustion engine | |
JP2543987Y2 (en) | Power assist device for internal combustion engine | |
JP5218387B2 (en) | Fluid transmission device | |
JP5664123B2 (en) | Engine supercharger |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
WWE | Wipo information: entry into national phase |
Ref document number: 200880131586.8 Country of ref document: CN |
|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 08877822 Country of ref document: EP Kind code of ref document: A1 |
|
DPE1 | Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101) | ||
WWE | Wipo information: entry into national phase |
Ref document number: 2008877822 Country of ref document: EP |
|
WWE | Wipo information: entry into national phase |
Ref document number: 13120472 Country of ref document: US |
|
WWE | Wipo information: entry into national phase |
Ref document number: 855/MUMNP/2011 Country of ref document: IN |
|
NENP | Non-entry into the national phase |
Ref country code: DE |
|
WWE | Wipo information: entry into national phase |
Ref document number: 2011121517 Country of ref document: RU |
|
ENP | Entry into the national phase |
Ref document number: PI0823134 Country of ref document: BR Kind code of ref document: A2 Effective date: 20110429 |