WO2002095204A1 - Verfahren und vorrichtung zur steuerung eines elektrisch betriebenen laders - Google Patents
Verfahren und vorrichtung zur steuerung eines elektrisch betriebenen laders Download PDFInfo
- Publication number
- WO2002095204A1 WO2002095204A1 PCT/DE2002/000306 DE0200306W WO02095204A1 WO 2002095204 A1 WO2002095204 A1 WO 2002095204A1 DE 0200306 W DE0200306 W DE 0200306W WO 02095204 A1 WO02095204 A1 WO 02095204A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- charger
- pressure ratio
- speed
- electric charger
- exhaust gas
- Prior art date
Links
Classifications
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- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
-
- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
-
- 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
- F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
- F02B37/12—Control of the pumps
- F02B37/14—Control of the alternation between or the operation of exhaust drive and other drive of a pump, e.g. dependent on speed
-
- 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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/02—Drives of pumps; Varying pump drive gear ratio
- F02B39/08—Non-mechanical drives, e.g. fluid drives having variable gear ratio
- F02B39/10—Non-mechanical drives, e.g. fluid drives having variable gear ratio electric
-
- 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
- F02B39/00—Component parts, details, or accessories relating to, driven charging or scavenging pumps, not provided for in groups F02B33/00 - F02B37/00
- F02B39/16—Other safety measures for, or other control of, pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/0002—Controlling intake air
- F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/04—Engine intake system parameters
- F02D2200/0406—Intake manifold pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/70—Input parameters for engine control said parameters being related to the vehicle exterior
- F02D2200/703—Atmospheric pressure
-
- 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 method and a device for controlling an electrically operated charger (EL).
- EL electrically operated charger
- exhaust gas turbocharger which consists of a turbine and a compressor operated in the air supply to the internal combustion engine.
- Exhaust gas turbochargers particularly in the case of motor vehicle drives, have the disadvantage of a delayed and inadequate response behavior at low engine speeds.
- electrical auxiliary drive To improve the response behavior of the exhaust gas turbocharger, it is known to support the exhaust gas turbocharger by means of an electrical auxiliary drive. This can be achieved, for example, by means of an electric motor integrated in the exhaust gas turbocharger, which supports the shaft of the exhaust gas turbocharger at low engine speeds.
- a need-dependent control or regulation of the electric charger or the auxiliary electric charger (EL) has the advantage that discontinuities in the boost pressure supply and thus discontinuities in the torque of the internal combustion engine are avoided. This improves driving comfort considerably. This advantage is achieved through continuous Control of the loader (e.g. through continuously changing setpoints) reinforced.
- Another advantage of the need-based control or regulation is that the vehicle electrical system load is reduced.
- the demand-dependent control or regulation can be installed in existing engine controls without a significant functional change in the boost pressure control.
- the loader-dependent control or regulation of the loader avoids unnecessary or excessive intervention by the loader.
- FIG. 1 shows an overview block diagram with a flow chart, which describes a first exemplary embodiment, while in FIG. 2 and FIG. 3, a second and a third exemplary embodiment are shown using a flow chart. Description of exemplary embodiments
- FIG. 1 shows a schematic block diagram including a flowchart for the needs-based control or regulation of an electrical auxiliary charger (EL).
- the air intake system 10 of an internal combustion engine is shown schematically.
- the sucked-in air is led, among other things, via an air filter 12, the compressor of an exhaust gas turbocharger 14, the electric auxiliary charger 16 to the charge air cooler 18 and from there via the throttle valve to the internal combustion engine.
- the electric auxiliary charger (EL) is actuated by a drive shaft 20 by an electric motor 22, for example a direct current motor. This is actuated by an electronic control unit 28 via control lines 24 and 26.
- the electronic control unit 28 comprises at least one microcomputer in which programs are implemented which carry out the control of the internal combustion engine and that of the electrical auxiliary charger (EL).
- a preferred exemplary embodiment of a program for controlling the electric auxiliary charger (EL) is outlined as a flowchart in FIG. 1 as part of the control unit 28.
- the blocks used here represent programs, program parts or program steps of such a program, while the connection arrows represent the flow of information.
- a boost pressure setpoint (plsoll) and an air mass setpoint (mlsoll) are determined depending on the load, speed and a large number of other parameters, such as temperature, altitude, knock condition, etc. Concrete solutions for determining these values are known from the prior art mentioned at the beginning.
- the boost pressure setpoint is used to control the boost pressure in conjunction with a boost pressure actual value to control the
- the boost pressure actual value is preferably measured (pressure sensor in Flow direction in front of the throttle valve), but can also be modeled.
- the air mass setpoint is further processed, among other things, to adjust the throttle valve (eg formation of the setpoint fill value).
- the actual boost pressure value used represents the pressure in front of the throttle valve, i.e. H. it contains both the effect of the compressor of the exhaust gas turbocharger and that of the auxiliary electric charger (EL).
- EL auxiliary electric charger
- the speed of the electrical auxiliary loader (EL) is then calculated, which is set, for example, via electronic speed control of the auxiliary loader (EL) or by means of a controller.
- EL electrical auxiliary loader
- the compressor pressure ratio of the electric auxiliary charger itself is regulated in another advantageous exemplary embodiment when using a further pressure sensor upstream of the electric auxiliary charger, the pressure ratio to be set being the setpoint, the pressure ratio determined from the further pressure sensor and the boost pressure sensor Actual value of a control loop.
- the sequence program outlined in FIG. 1 as part of the control unit 28 shows a first exemplary embodiment of a pre- how to determine the pressure ratio to be set.
- the stationary maximum is determined in a first map 30 as a function of the engine speed nmot, which is recorded by a corresponding measuring device 32, and the target air mass flow, which is determined, for example, in accordance with the solution mentioned in 34 in dependence on the driver's request and other operating sizes available compressor pressure ratio of the exhaust gas turbocharger is determined in this operating state.
- the map is applied to a test stand for each engine type, for example.
- the compressor pressure ratio VPATLstat of the exhaust gas turbocharger is then fed to a filter 36, preferably a low-pass filter of at least second order, which simulates the behavior of the exhaust gas turbocharger over time and thus determines the currently available maximum compressor pressure ratio of the exhaust gas turbocharger from the exhaust gas turbocharger.
- the time constant or the time constants of the filter 36 are read from a characteristic curve 38 as a function of the engine speed, with smaller time constants and thus a lower filter effect being generated with increasing engine speed.
- the measured value for the air mass flow can also be used in other embodiments to form the pressure ratio across the exhaust gas turbocharger.
- the result is what is actually achieved, not the achievable pressure ratio as above.
- the corresponding intake manifold pressure values or filling values are also suitable.
- the overall boost pressure ratio ie the product of the compressor pressure ratio of the exhaust gas turbocharger and that of the electric auxiliary charger (EL) is equal to the quotient of a boost pressure value to an ambient pressure value.
- the compressor pressure 40 of the auxiliary electric charger (EL) according to 40 in accordance with the relationship derived from this boundary condition, according to which the compressor pressure ratio VPEL of the auxiliary electric charger (EL) is determined from the quotient of the setpoint pressure and the product of the ambient pressure and the compressor ratio of the exhaust gas turbocharger.
- the pressure at the inlet of the first of the two chargers in the direction of flow can also be used.
- the ambient pressure is preferably determined by a measuring device 42, while a target boost pressure is used as the boost pressure value, which is determined according to 44, for example, as part of the solution mentioned at the outset, depending on the driver's request.
- the compressor pressure ratio of the electrical auxiliary charger VPEL which is formed in FIG. 40, therefore represents a setpoint value for the compressor pressure ratio.
- This is fed to a further map 46, which represents the compressor map of the electrical auxiliary charger (EL).
- the target speed NELSOLL of the auxiliary charger is determined depending on the target pressure ratio of the electrical auxiliary charger (EL). This takes place depending on the desired compressor pressure ratio of the electrical auxiliary charger (EL) calculated as above and the desired air mass flow mlsoll, which is dependent on the driver's request.
- the target speed is determined and fed to a speed control 48. This then forms on the basis of the target speed and an actual speed (for example by measuring the
- the setpoint speed NELSOLL or the actual speed of the engine 22 is limited, so that it does not fall below a predetermined on-board electrical system voltage becomes. This means that if the measured vehicle electrical system voltage falls below a predetermined limit value, a further increase in the target speed or the actual speed is prevented by limiting the corresponding value.
- the duty cycle of the electric charger is also limited to a maximum value.
- the auxiliary electric charger is switched off again when the switch-off time is reached.
- the shutdown takes place as a ramp-shaped curtailment with a predetermined gradient, ie. H. the setpoint speed is reduced to a value of zero with a predetermined gradient.
- the maximum time mentioned above depends on the size of the company, in particular on the outside temperature and / or the engine temperature of the electrical auxiliary charger and / or the charge balance of the battery and / or the vehicle electrical system voltage. The maximum value is smaller, the higher the temperature, the worse the charge balance or the lower the vehicle electrical system voltage.
- FIG. 2 Another exemplary embodiment is shown in the flow chart shown in FIG. 2.
- This flow chart also describes the program of a microcomputer of the control unit 28, the individual blocks representing programs, program parts or program steps, the connecting lines representing the flow of information.
- the elements already mentioned with reference to FIG. 1 have the same reference symbols in FIG. 2 and have the same function.
- the main difference between the procedures in FIG. 1 and FIG. 2 is that when determining the compressor pressure ratio of the exhaust gas turbocharger, 2 sizes are used as a function of the ambient pressure Pu and the exhaust gas temperature TABG.
- the Stationarily achievable value of the compressor pressure ratio VPATLSTATT in the map 102 as a function of the exhaust gas temperature TABG which is detected, for example, by means of a sensor or a calculation model, and the engine speed nmot.
- the map 102 is also determined, for example, by test bench measurements.
- the stationary value is then corrected in the multiplication point 100 with a correction value which is formed in the map 101 as a function of the engine temperature and the desired air mass flow MLSOLL. The reason for this correction is that
- the corrected stationary value of the compressor ratio of the exhaust gas turbocharger is corrected in a further multiplication stage 104 depending on a further correction value.
- the latter is formed by the characteristic curve 106 as a function of the ambient pressure pu.
- the characteristic curve 106 is also determined in the context of the application.
- the stationary compressor pressure ratio value of the exhaust gas turbocharger corrected in this way is converted into a current value by the filter 36 as described with reference to FIG. 1 and into a target value for the compressor pressure ratio of the electrical auxiliary charger (EL) by the conversion in step 40.
- the latter is then converted via the map 46 into the target speed, which is set in accordance with the illustration with reference to FIG. 1.
- FIG. 3 Another exemplary embodiment is shown in the flow chart shown in FIG. 3.
- This flow chart also describes the program of a microcomputer of the control unit 28, the individual blocks representing programs, program parts or program steps, the connecting lines representing the flow of information.
- 200 denotes a characteristic diagram for determining a current compressor pressure ratio vpezv of the electrical charger or electrical auxiliary charger 16 in dependence.
- the current compressor pressure ratio vpezv is multiplied by the boost pressure setpoint plsoll, which, as described, is determined as a function of the load, engine speed and a large number of further parameters, such as temperature, high or ambient pressure pu, knock condition, etc.
- the product vpezv * plsoll is then divided in a division element 210 by an actual boost pressure value pvdkds.
- the boost pressure actual value pvdkds is measured in the flow direction after the electric charger 16 and the exhaust gas turbocharger 14 or in front of the throttle valve by means of a pressure sensor, but can also be modeled.
- the setpoint VPEL for the compressor pressure ratio of the electric charger 16 then results at the output of the division element 210.
- VPEL vpezv * plsoll / pvdkds (1)
- the relationship (1) can be derived from the following relationship described for the exemplary embodiment according to FIG. 1:
- the outlet pressure to be set of the exhaust gas turbocharger is the product of the ambient pressure pu and the currently maximum available compressor pressure ratio VPATL of the exhaust gas turbocharger 14, i.e. pu * VPATL. This is then the maximum available input pressure at the electric charger 16.
- VPATL the currently maximum available compressor pressure ratio
- a modeled or measured pressure at the outlet of the air filter 12 can also be used. With the current compressor pressure ratio vpezv of the electrical see charger 16 then results at the output of the electric charger 16, the charge pressure actual value pvdkds as
- the compressor pressure ratio VPEL of the electric charger 16 which is available after the division element 210, thus represents, as also in the embodiment according to FIG. 1, a setpoint value for the compressor pressure ratio.
- This is supplied to the further map 46, which describes the compressor map, as described in FIG of the electric auxiliary charger 16.
- the target speed NELSOLL of the electric charger 16 determines the target speed NELSOLL of the electric charger 16. This takes place as a function of the compressor pressure ratio VPEL of the electric charger 16 to be set as calculated above and the desired air mass flow mlsoll which is dependent on the driver's wishes.
- the target speed NELSOLL is determined as the target speed value and fed to the speed control 48.
- the target speed NELSOLL and an actual speed which can be determined, for example, by measuring the current through the motor 22 of the electric charger 16, this then forms control signals for the motor 22 of the electric charger 16, which then has the predetermined target speed NELSOLL rotates.
- the map 200 for determining the current compressor pressure ratio vpezv of the electric charger 16 is inverse to the compressor map 46 with regard to the input and output high speed of the motor 22 of the electric charger 16 and the compressor pressure ratio of the electric charger 16.
- a switch 215 can be provided, via which, depending on the switch position, either the target speed NELSOLL or a idle speed NEZVLLS is selected for forwarding to the speed control 48 as the target speed value becomes.
- the idle speed NEZVLLS can only be activated when the clutch is depressed.
- the electric charger 16 is switched off when the engine speed nmot of the internal combustion engine, which can be designed as an internal combustion engine, for example, above a first predetermined one Engine speed is 225.
- the electrical charger 16 is switched on again after the switch-off when the engine speed nmot the
- bit 235 is set. Bit 235 is reset when the engine speed nmot of the internal combustion engine falls below the second predetermined engine speed 230. If bit 235 is set, the electric charger 16 is not required and is switched off. The switch 215 is then brought into a switch position in which it supplies the idle speed NEZVLLS as the target speed value for the electric charger 16 to the speed control 48. If bit 235 is reset, the electric charger 16 is required and switched on. The switch 215 is then brought into a switch position in which it supplies the target speed NELSOLL as the target speed value to the speed control 48.
- the setpoint speed value of the electric charger 16 is filtered by means of a second filter 240, which is to be designed, for example, as a low-pass filter.
- a second filter 240 which is to be designed, for example, as a low-pass filter.
- FIG. 3 shows, by way of example, that the switch 215 is followed by the low pass 240, and the low pass 240 is therefore supplied with either the idle speed NEZVLLS or the set speed NELSOLL as the set speed value.
- the low-pass filter 240 protects the speed control 48 against vibrations.
- the time constant or the time constants of the low-pass filter 240 can be selected as a function of the target speed NELSOLL, in the event that the target speed NELSOLL is to be supplied to the speed control 48.
- a single time constant of the low pass 240 is to be assumed as an example.
- the time constant can be selected by means of a characteristic curve 245 depending on the target speed NELSOLL.
- the course of the characteristic curve can be predetermined, for example, such that a smaller target speed NELSOLL is assigned a smaller time constant and a larger target speed NELSOLL is assigned a larger time constant.
- time constant or the time constants of the low-pass filter 240 could also be set as a function of parameters or map-controlled, for example as a function of the actual air mass value ml and / or the engine speed nezv of the electric charger 16.
- a device 250 is provided for forming the gradient of an accelerator pedal position wped over time t.
- the gradient formed by the device 250 is fed to a comparator 255.
- the comparator 255 compares the gradient with a predetermined value GRWPEDEZV. If the gradient is above the predetermined value GRWPEDEZV, then a maximum speed NEZVHIS for the electric charger 16 is set as the target speed value and either directly or as in FIG. 3 via the low-pass filter 240 to the speed control 48.
- the output of the comparator 255 and on the other hand the bit 235 is fed to an AND gate 260.
- the output of comparator 255 is set when the gradient of the accelerator pedal position is above the predefined value GRWPEDEZV.
- the maximum speed NEZVHIS is supplied to the low-pass filter 240 as the desired speed value. In this way, when there is a very fast torque request and the electric charger 16 is switched off or is operated at a low speed, the electric charger 16 can be started up in a faster calculation grid in a pilot-controlled manner, whereby a considerable gain in dynamics is achieved.
- the charge pressure setpoint plsoll is calculated via the torque structure of the engine control and requires a corresponding runtime.
- the calculation path also contains functions such as the load shock damping, which leads to a delayed build-up of the boost pressure setpoint plsoll, which therefore lags behind the pedal signal resulting from the actuation of the accelerator pedal in the form of the gradient of the accelerator pedal position.
- the charge pressure setpoint plsoll and the air mass target flow mlsoll could also be determined using a prediction calculation.
- the prediction of the speed of the electric charger 16 can also be precontrolled or implemented more quickly by such a prediction.
- the prediction calculation can, for example, determine the difference between the last and the penultimate boost pressure target value or air mass target flow and, based on this difference, an extrapolation to a subsequent boost pressure target value or air mass target flow can be carried out and thus a prediction can be implemented.
- the invention described on the basis of the above exemplary embodiments ensures precise and at the same time demand-dependent control or regulation of the electric charger 16 without unnecessary on-board electrical system load and without additional effort with regard to the required sensors.
- the current compressor pressure ratio vpezv can be determined by forming the quotient pnach / pvor pnach / pvor of the electric charger 16 can be determined.
- the map 200 for determining the current compressor pressure ratio vpezv of the electric charger 16 can be dispensed with.
- the electric charger 16 is connected downstream of the exhaust gas turbocharger 14.
- the order of the two chargers 14, 16 is arbitrary with regard to the regulation of the compressor pressure ratio of the electric charger 16 according to the invention.
- the electric charger 16 is arranged upstream of the exhaust gas turbocharger 14 in the direction of flow, this is due to thermodynamics - Good view for the electric charger 16 cheaper.
Abstract
Description
Claims
Priority Applications (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US10/478,246 US7210296B2 (en) | 2001-05-19 | 2002-01-19 | Method and device for controlling an electrically driven charger |
EP02706642A EP1440231B1 (de) | 2001-05-19 | 2002-01-29 | Verfahren und vorrichtung zur steuerung eines elektrisch betriebenen laders |
BR0209880-6A BR0209880A (pt) | 2001-05-19 | 2002-01-29 | Processo e dispositivo para controle de um sobrealimentador acionado eletricamente |
DE50205515T DE50205515D1 (de) | 2001-05-19 | 2002-01-29 | Verfahren und vorrichtung zur steuerung eines elektrisch betriebenen laders |
JP2002591646A JP2004525305A (ja) | 2001-05-19 | 2002-01-29 | 電気的に作動されるチャージャの制御方法および装置 |
KR10-2003-7014995A KR20040007574A (ko) | 2001-05-19 | 2002-01-29 | 전동식 과급기의 제어를 위한 방법 및 장치 |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10124543A DE10124543A1 (de) | 2001-05-19 | 2001-05-19 | Verfahren und Vorrichtung zur Steuerung eines elektrisch betriebenen Laders |
DE10124543.2 | 2001-05-19 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2002095204A1 true WO2002095204A1 (de) | 2002-11-28 |
Family
ID=7685465
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2002/000306 WO2002095204A1 (de) | 2001-05-19 | 2002-01-29 | Verfahren und vorrichtung zur steuerung eines elektrisch betriebenen laders |
Country Status (7)
Country | Link |
---|---|
US (1) | US7210296B2 (de) |
EP (1) | EP1440231B1 (de) |
JP (1) | JP2004525305A (de) |
KR (1) | KR20040007574A (de) |
BR (1) | BR0209880A (de) |
DE (2) | DE10124543A1 (de) |
WO (1) | WO2002095204A1 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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DE102014019640A1 (de) * | 2014-12-31 | 2016-06-30 | Audi Ag | Verfahren zum Betreiben einer Antriebseinrichtung sowie entsprechende Antriebseinrichtung |
US20210302270A1 (en) * | 2020-03-31 | 2021-09-30 | Gm Cruise Holdings Llc | Controlled testing environment for autonomous vehicle in simulated event |
Families Citing this family (41)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2003227341A (ja) * | 2002-01-31 | 2003-08-15 | Robert Bosch Gmbh | 排気ガス・ターボチャージャのチャージ圧力の制御方法および装置 |
DE10203974A1 (de) | 2002-01-31 | 2003-08-14 | Bosch Gmbh Robert | Verfahren und Vorrichtung zur Steuerung eines elektrisch betriebenen Laders |
JP2003227342A (ja) | 2002-01-31 | 2003-08-15 | Robert Bosch Gmbh | チャージャの操作または制御方法および装置 |
DE10228350A1 (de) | 2002-06-25 | 2004-01-15 | Robert Bosch Gmbh | Energiebordnetz zur Versorgung eines Hochleistungsverbrauchers |
DE10307132B4 (de) | 2003-02-20 | 2021-09-23 | Robert Bosch Gmbh | Verfahren zum Betreiben einer Brennkraftmaschine |
DE10318240A1 (de) * | 2003-04-23 | 2004-11-11 | Robert Bosch Gmbh | Verfahren und Vorrichtung zum Betrieb einer Brennkraftmaschine |
DE102004003607B4 (de) * | 2004-01-23 | 2009-01-29 | Continental Automotive Gmbh | Verfahren und Vorrichtung zur Steuerung eines elektrisch angetriebenen Verdichters einer Verbrennungskraftmaschine |
KR100749620B1 (ko) * | 2005-03-02 | 2007-08-14 | 가부시키가이샤 덴소 | 과급기 부착 내연 기관용 제어 장치 |
FR2885388A1 (fr) * | 2005-05-03 | 2006-11-10 | Renault Sas | Procede de commande d'un moteur de vehicule comprenant un compresseur electrique |
SE0501177L (sv) * | 2005-05-25 | 2007-01-25 | Gm Global Tech Operations Inc | Kontrollenhet vid en förbränningsmotor försedd med ett överladdarsystem samt ett system, ett fordon och en metod innefattande en sådan kontrollenhet |
JP2007205306A (ja) * | 2006-02-03 | 2007-08-16 | Mazda Motor Corp | 過給機付きエンジン |
US7802427B2 (en) * | 2006-05-19 | 2010-09-28 | Caterpillar Inc | System and method for monitoring boost leak |
JP4743045B2 (ja) * | 2006-08-28 | 2011-08-10 | マツダ株式会社 | エンジンの過給装置 |
DE102007017823B4 (de) * | 2007-04-16 | 2019-10-02 | Continental Automotive Gmbh | Turbolader mit einer Einrichtung zum Feststellen einer Fehlfunktion des Turboladers und ein Verfahren zum Feststellen einer solchen Fehlfunktion |
US7730724B2 (en) * | 2007-05-10 | 2010-06-08 | Ford Global Technologies, Llc | Turbocharger shaft over-speed compensation |
WO2009106275A2 (de) * | 2008-02-28 | 2009-09-03 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Verfahren und vorrichtung zum steuern eines abtriebsdrehmomentes eines mit einer verbrennungskraftmaschine gekoppelten automatisierten getriebes |
DE102008031317A1 (de) * | 2008-07-02 | 2010-01-07 | Knorr-Bremse Systeme für Nutzfahrzeuge GmbH | Kompressorsystem mit beschränktem Ansaugladedruck |
JP4916554B2 (ja) * | 2010-01-15 | 2012-04-11 | 三菱電機株式会社 | 電動過給機の電源制御装置 |
FR2966516B1 (fr) * | 2010-10-26 | 2015-11-13 | Peugeot Citroen Automobiles Sa | Methode et dispositif de controle du fonctionnement d'un circuit d'admission d'air equipant un moteur a combustion suralimente pour vehicule automobile |
JP5874161B2 (ja) * | 2010-10-28 | 2016-03-02 | いすゞ自動車株式会社 | ターボ過給システム |
US9157363B2 (en) | 2012-08-21 | 2015-10-13 | Ford Global Technologies, Llc | Twin independent boosted I4 engine |
FR2998924B1 (fr) | 2012-11-30 | 2014-11-21 | IFP Energies Nouvelles | Procede de commande d'un moteur thermique equipe d'une double suralimentation |
DE102014210028A1 (de) * | 2014-05-26 | 2015-11-26 | Volkswagen Aktiengesellschaft | Verfahren und Steuerung zum Steuern eines Aufladungssystems für eine Verbrennungskraftmaschine |
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FR3041696B1 (fr) * | 2015-09-25 | 2019-11-29 | Renault S.A.S. | Methode d'elaboration d'une consigne de pilotage d'un compresseur electrique |
KR20170041321A (ko) * | 2015-10-06 | 2017-04-17 | 현대자동차주식회사 | 수퍼차저의 제어방법 |
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US10815875B2 (en) | 2017-03-30 | 2020-10-27 | Ford Global Technologies, Llc | Method and system for boosted engine system |
US10731545B2 (en) | 2017-03-30 | 2020-08-04 | Ford Global Technologies, Llc | Method and system for boosted engine system |
US10711729B2 (en) | 2017-07-19 | 2020-07-14 | Ford Global Technologies, Llc | Diesel engine dual fuel injection strategy |
US10422289B2 (en) * | 2017-08-31 | 2019-09-24 | Ford Global Technologies, Llc | Method and system for a boosted engine |
DE102017220404A1 (de) * | 2017-11-15 | 2019-05-16 | Robert Bosch Gmbh | Verfahren und Vorrichtung zur Drehzahlregelung einer elektrisch betriebenen Aufladeeinrichtung für einen Verbrennungsmotor |
US11060525B2 (en) * | 2019-11-15 | 2021-07-13 | GM Global Technology Operations LLC | Closed loop temperature control system for turbocharger compressor outlet temperature |
DE102021126385A1 (de) | 2021-10-12 | 2023-04-13 | Audi Aktiengesellschaft | Verfahren zum Betreiben einer Antriebseinrichtung für ein Kraftfahrzeug sowie entsprechende Antriebseinrichtung |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3411496A1 (de) * | 1983-09-30 | 1985-04-18 | Aisin Seiki K.K., Kariya, Aichi | Vorrichtung zur steuerung der aufladung in einer brennkraftmaschine |
EP0420704A1 (de) * | 1989-09-29 | 1991-04-03 | Isuzu Motors Limited | Steuersystem für Turbolader mit elektrischer Drehmaschine |
DE19757661C1 (de) * | 1997-12-23 | 1999-03-04 | Siemens Ag | Verfahren für die Ladedruckregelung einer Brennkraftmaschine mit Turbolader |
DE19924274A1 (de) * | 1998-05-27 | 1999-12-02 | Cummins Engine Co Inc | System und Verfahren zum Steuern eines Turboladers zur Maximierung der Leistung eines Verbrennungsmotors |
DE19905112A1 (de) * | 1999-02-09 | 2000-08-10 | Fev Motorentech Gmbh | Verfahren zum Betreiben einer Kolbenbrennkraftmaschine mit Vorverdichtung der Verbrennungsluft und Kolbenbrennkraftmaschine zur Durchführung des Verfahrens |
US6205787B1 (en) * | 1995-11-15 | 2001-03-27 | Honeywell International Inc. | Charge air systems for turbocharged four-cycle internal combustion engines |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS59211720A (ja) * | 1983-05-16 | 1984-11-30 | Kawasaki Heavy Ind Ltd | 複合過給4サイクルデイ−ゼル機関 |
JPS6293423A (ja) * | 1985-10-19 | 1987-04-28 | Isuzu Motors Ltd | タ−ボコンパウンドエンジンのエネルギ−回収装置 |
DE19608630A1 (de) | 1996-03-06 | 1997-09-11 | Bosch Gmbh Robert | Verfahren und Anordnung zum Steuern oder Regeln der Leistung einer aufladbaren Brennkraftmaschine |
DE19740968B4 (de) | 1997-09-17 | 2007-11-29 | Robert Bosch Gmbh | Verfahren zum Betreiben einer Brennkraftmaschine |
US6705084B2 (en) * | 2001-07-03 | 2004-03-16 | Honeywell International Inc. | Control system for electric assisted turbocharger |
DE10136977A1 (de) * | 2001-07-28 | 2003-02-06 | Bosch Gmbh Robert | Verfahren und Vorrichtung zum Betreiben eines elektrischen Laders |
DE10140120A1 (de) * | 2001-08-16 | 2003-03-06 | Bosch Gmbh Robert | Verfahren und Vorrichtung zum Betreiben eines Verbrennungsmotors |
US6609375B2 (en) * | 2001-09-14 | 2003-08-26 | Honeywell International Inc. | Air cooling system for electric assisted turbocharger |
JP2003227341A (ja) * | 2002-01-31 | 2003-08-15 | Robert Bosch Gmbh | 排気ガス・ターボチャージャのチャージ圧力の制御方法および装置 |
US6938420B2 (en) * | 2002-08-20 | 2005-09-06 | Nissan Motor Co., Ltd. | Supercharger for internal combustion engine |
JP3925397B2 (ja) * | 2002-11-20 | 2007-06-06 | トヨタ自動車株式会社 | 電動機付ターボチャージャ制御装置 |
JP3846463B2 (ja) * | 2003-08-07 | 2006-11-15 | 日産自動車株式会社 | 電動過給装置 |
US6931850B2 (en) * | 2003-09-10 | 2005-08-23 | The Regents Of The Univesity Of California | Exhaust gas driven generation of electric power and altitude compensation in vehicles including hybrid electric vehicles |
-
2001
- 2001-05-19 DE DE10124543A patent/DE10124543A1/de not_active Withdrawn
-
2002
- 2002-01-19 US US10/478,246 patent/US7210296B2/en not_active Expired - Fee Related
- 2002-01-29 JP JP2002591646A patent/JP2004525305A/ja not_active Withdrawn
- 2002-01-29 KR KR10-2003-7014995A patent/KR20040007574A/ko not_active Application Discontinuation
- 2002-01-29 EP EP02706642A patent/EP1440231B1/de not_active Expired - Lifetime
- 2002-01-29 DE DE50205515T patent/DE50205515D1/de not_active Expired - Lifetime
- 2002-01-29 WO PCT/DE2002/000306 patent/WO2002095204A1/de active IP Right Grant
- 2002-01-29 BR BR0209880-6A patent/BR0209880A/pt not_active IP Right Cessation
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3411496A1 (de) * | 1983-09-30 | 1985-04-18 | Aisin Seiki K.K., Kariya, Aichi | Vorrichtung zur steuerung der aufladung in einer brennkraftmaschine |
EP0420704A1 (de) * | 1989-09-29 | 1991-04-03 | Isuzu Motors Limited | Steuersystem für Turbolader mit elektrischer Drehmaschine |
US6205787B1 (en) * | 1995-11-15 | 2001-03-27 | Honeywell International Inc. | Charge air systems for turbocharged four-cycle internal combustion engines |
DE19757661C1 (de) * | 1997-12-23 | 1999-03-04 | Siemens Ag | Verfahren für die Ladedruckregelung einer Brennkraftmaschine mit Turbolader |
DE19924274A1 (de) * | 1998-05-27 | 1999-12-02 | Cummins Engine Co Inc | System und Verfahren zum Steuern eines Turboladers zur Maximierung der Leistung eines Verbrennungsmotors |
DE19905112A1 (de) * | 1999-02-09 | 2000-08-10 | Fev Motorentech Gmbh | Verfahren zum Betreiben einer Kolbenbrennkraftmaschine mit Vorverdichtung der Verbrennungsluft und Kolbenbrennkraftmaschine zur Durchführung des Verfahrens |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE112005000486B4 (de) * | 2004-03-04 | 2014-08-07 | Toyota Jidosha Kabushiki Kaisha | Steuervorrichtung für Ladevorrichtung mit Elektromotor |
DE102014019640A1 (de) * | 2014-12-31 | 2016-06-30 | Audi Ag | Verfahren zum Betreiben einer Antriebseinrichtung sowie entsprechende Antriebseinrichtung |
US20210302270A1 (en) * | 2020-03-31 | 2021-09-30 | Gm Cruise Holdings Llc | Controlled testing environment for autonomous vehicle in simulated event |
US11644385B2 (en) * | 2020-03-31 | 2023-05-09 | GM Cruise Holdings LLC. | Controlled testing environment for autonomous vehicle in simulated event |
US11802815B2 (en) | 2020-03-31 | 2023-10-31 | Gm Cruise Holdings Llc | Controlled testing environment for autonomous vehicle in simulated event |
Also Published As
Publication number | Publication date |
---|---|
US20040194465A1 (en) | 2004-10-07 |
JP2004525305A (ja) | 2004-08-19 |
EP1440231A1 (de) | 2004-07-28 |
KR20040007574A (ko) | 2004-01-24 |
EP1440231B1 (de) | 2006-01-04 |
DE10124543A1 (de) | 2002-11-21 |
US7210296B2 (en) | 2007-05-01 |
DE50205515D1 (de) | 2006-03-30 |
BR0209880A (pt) | 2004-06-08 |
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