WO2010145628A1 - Kraftfahrzeug mit einer brennkraftmaschine sowie einem elektromotor - Google Patents
Kraftfahrzeug mit einer brennkraftmaschine sowie einem elektromotor Download PDFInfo
- Publication number
- WO2010145628A1 WO2010145628A1 PCT/DE2010/000410 DE2010000410W WO2010145628A1 WO 2010145628 A1 WO2010145628 A1 WO 2010145628A1 DE 2010000410 W DE2010000410 W DE 2010000410W WO 2010145628 A1 WO2010145628 A1 WO 2010145628A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- internal combustion
- combustion engine
- motor vehicle
- exhaust gas
- cylinder
- 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
- F02B41/06—Engines with prolonged expansion in compound cylinders
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/24—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the combustion engines
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/42—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by the architecture of the hybrid electric vehicle
- B60K6/46—Series type
-
- 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
-
- 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
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
- F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02N—STARTING OF COMBUSTION ENGINES; STARTING AIDS FOR SUCH ENGINES, NOT OTHERWISE PROVIDED FOR
- F02N11/00—Starting of engines by means of electric motors
- F02N11/04—Starting of engines by means of electric motors the motors being associated with current generators
-
- 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
-
- 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
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
Definitions
- the invention relates to a motor vehicle with an internal combustion engine and at least one electromechanical energy converter, which are used in cooperation for propulsion of the motor vehicle, wherein the internal combustion engine is used during operation of the motor vehicle for the vast majority of time in a particularly efficient operating range or is turned off.
- hybrid vehicles various systems for motor vehicles with drive systems are presented on the market, in which at least one internal combustion engine and at least one electric motor are used to drive the respective motor vehicle (so-called hybrid vehicles).
- a hybrid system with serial arrangement of internal combustion engine and electric motor (s) is provided. Its advantage lies in the about 25% more efficient implementation of an internal combustion engine supplied amount of energy of a liquid fuel - compared with an individual operation of the internal combustion engine after the Otto process.
- an internal combustion engine according to Patent No. DE 879183 or as well as an internal combustion engine according to the patent DE 60116942T2 are known as state of the art.
- a so-called 5-stroke combustion method is described in which fuel can be converted into drive power with higher efficiency in each case.
- These as traction motors operated 5-stroke engines have several disadvantages. Used as a traction motor, the stroke volume increases due to the specific design of 2-liter to 4-liter engines (with approx. 20% increased power). This leads to an unacceptable enlargement of the engine and is considered as a reason that this could not enforce technically yet more efficient but disadvantageous machine design. Furthermore, the dynamic operation of such a motor is not adequately represented. An idea to make the engine more powerful by turbocharging was published in the patent DE 60116942 T2.
- the object of the invention is to provide a drive unit for a motor vehicle which, with good practicality, has a particularly high overall efficiency. It is another object of the invention to provide a motor vehicle available that will meet future environmental and consumption requirements in a cost effective manner.
- a drive unit according to the invention for a motor vehicle comprises an internal combustion engine having at least two combustion chambers, in particular combustion cylinders in which each with a time interval (ignition angle) a fuel-air mixture (starting mixture) is chemically exothermically reacted such that an exhaust gas mixture with respect to the starting mixture increased latent heat and with increased pressure is generated, wherein the exhaust gas mixture on the pistons movably mounted in the combustion pistons exerts a compressive force such that with the aid of the piston, an output shaft (crankshaft) is set in rotation, wherein the combustion chambers another working space in the form of an expansion - Cylinder is assigned, in the expelled from the combustion chambers exhaust gas mixture - with the release of mechanical power to the output shaft (crankshaft) - relaxed and subsequently in a Exhaust gas outlet is transferred, wherein a first electromechanical energy converter is mechanically coupled to the output shaft of the internal combustion engine and exchanges electrical energy with an
- combustion chambers of the internal combustion engine have a compression ratio of less than 9: 1, in particular less than 8: 1.
- the internal combustion engine is operated in a predominant operating state approximately stationary in a speed range between 1000 U / min and 5000 U / min or it is shut down.
- a fluctuation range of +/- 250 rpm can be provided by a preferred value of, for example, 2000 rpm.
- the operating state of the internal combustion engine is largely stationarily placed in that region of the torque-speed level in which the lowest specific fuel consumption of the internal combustion engine is located.
- the region of highest efficiency of the first electromechanical energy converter is selected in just the same torque / rpm range.
- the internal combustion engine has at least two operated according to a four-stroke combustion chambers and an acting on the same output shaft expansion cylinder in which expelled from the combustion chambers exhaust gas mixture is relaxed, wherein the first electromechanical energy converter is mechanically coupled to the output shaft of the internal combustion engine and is operated mainly as a generator for charging a storage unit for electrical energy, wherein the further electromechanical energy converter is provided as a drive and brake unit for at least one wheel shaft of the motor vehicle, the internal combustion engine in operation with a less than 500 rev / min fluctuating speed (quasi stationary), in particular in a speed range between 1000 U / min and 5000 U / min is operated or shut down.
- the first electromechanical energy converter is preferably used for setting the load and / or the torque of the internal combustion engine and for starting the internal combustion engine.
- the internal combustion engine is assigned an exhaust gas turbocharger, in which the exhaust gas mixture discharged from the expansion cylinder is further expanded in an exhaust gas turbocharger, the air to be supplied to the combustion chambers being precompressed with the aid of the exhaust gas turbocharger.
- the overall efficiency of the drive can be further increased and exhaust gas energy can be exploited to the greatest possible extent.
- at least one exhaust gas recirculation device is preferably provided for at least part of the exhaust gas, which is expanded in the exhaust gas turbocharger.
- the internal combustion engine comprises two four-stroke cylinders operating in uniform firing intervals of 360 ° and an additional, larger expansion cylinder for a subsequent expansion of the exhaust gas mixture of the four-stroke cylinders, wherein the expansion cylinder alternately relaxes combustion gases received alternately from the two four-stroke cylinders in a two-stroke process , wherein the transfer of gases from the Four-cycle cylinders through openings in a cylindrical wall of the expansion cylinder, in particular with an oriented approximately perpendicular to the cylinder axis flow direction.
- the four-stroke cylinder according to the invention preferably have the same lifting height and the same displacement.
- the expansion cylinder preferably has an increased by at least 25% stroke volume, which is set via an appropriate choice of the cylinder diameter and the lifting height, wherein the lifting height of the expansion cylinder relative to the lifting height of the four-stroke cylinder is increased. More preferably, a series arrangement of the three cylinders described is provided such that the cylinder center axes all come to lie in a common plane. More preferably, the expansion cylinder projects beyond the two four-stroke cylinders in the region of the cylinder head, ie the upper reversing position of the piston in the expansion cylinder has a greater distance from the axis of rotation of the crankshaft than the uppermost positions of the pistons of the four-stroke cylinder.
- an overflow channel between the expansion cylinder and adjacent four-stroke cylinder can be provided which extends between an outlet opening on the substantially round end face of the four-stroke cylinder and a slot-shaped opening in the cylindrical wall of the expansion cylinder.
- Such an overflow channel may preferably have a flow deflection of 90 ° or less.
- a nearly adiabatic expansion of the exhaust gas and / or afterburning can thus be realized.
- the internal combustion engine is assigned a thermally effective insulation such that an internal temperature of the internal combustion engine of more than 100 0 C at standard ambient conditions, especially at an outside temperature of 20 0 C, drops by less than 3 K per minute.
- the fuel according to the invention, the combustion engine has an insulating encapsulation whose constituents can have different thermal insulation properties, but whose overall behavior causes the (stopped) internal combustion engine to cool down by less than 3 K / min.
- the exhaust gas outlet of the expansion cylinder blocking exhaust outlet valve is wholly or partly made of a ceramic material.
- the exhaust valve of the expansion cylinder thus has a low heat storage capacity and contributes significantly to the thermal insulation of the expansion cylinder.
- the outlet-lift valve blocking the exhaust gas outlet of the expansion cylinder has a main axis which is aligned parallel to the main axis of the expansion cylinder, preferably arranged coincident thereto.
- the internal combustion engine has a first cylinder group with two operating in uniform firing interval four-stroke cylinders and an additional expansion cylinder for subsequent expansion of the exhaust gas mixture of the four-stroke cylinder, wherein the expansion cylinder alternately relaxes from the two four-stroke cylinders absorbed combustion gases, and wherein the internal combustion engine at least one second cylinder group, which is configured substantially equal to the first cylinder group and arranged inclined in V-shape, star shape or boxer shape with an angle greater than 0 ° to the first cylinder group, wherein the first and the second cylinder group, a common output shaft (crankshaft ).
- the crankshaft is coupled to one or two electromechanical energy converters which supply electrical energy to a respective one connected to the electromechanical energy converter Dispense battery.
- Such designed engine find especially in boat and aircraft engines use.
- second-order mass forces are compensated by compensating masses moved at twice the crankshaft speed.
- the different lever and mass ratios in the combustion cylinders on the one hand and the expansion cylinder on the other hand can be compensated according to the invention by means of a balance shaft in an advantageous manner.
- a motor vehicle having the features of claim 13.
- a motor vehicle according to the invention comprises a drive unit together with an internal combustion engine with at least two combustion chambers, in particular combustion cylinders, in each of which with a time interval (ignition angle) a fuel-air mixture (Starting mixture) is chemically exothermically reacted such that an exhaust gas mixture with respect to the starting mixture increased latent heat and increased pressure is generated.
- the exhaust gas mixture exerts a compressive force on pistons movably mounted in the combustion chambers in such a way that an output shaft (crankshaft) is set in rotation by means of the pistons, wherein the combustion chambers are assigned a further working space in the form of an expansion cylinder in which the combustion chambers expelled exhaust gas mixture is released while releasing mechanical power to the output shaft (crankshaft) and subsequently transferred to an exhaust gas outlet.
- the drive unit has a first electromechanical energy converter, which is mechanically coupled to the output shaft of the internal combustion engine and exchanges electrical energy with a storage unit for electrical energy, and another electromechanical energy converter, which is mechanically coupled to at least one wheel shaft of the motor vehicle and also electrical energy exchanged with the storage unit for electric power.
- demand is determined essentially on the basis of the state of charge of the storage unit for electrical energy (accumulator, "battery”.) Peak loads can be handled by electric motor as well as start-up processes without making any changes to the operating state of the internal combustion engine or even switching them on Balancing reservoir for energy between the continuous power level of the stationary particularly efficient operable internal combustion engine and the short-term discontinuous power requirements in the operation of modern motor vehicles.
- the drive unit in particular the internal combustion engine, a thermally effective insulation assigned such that an internal temperature of the internal combustion engine of more than 100 0 C at standard ambient conditions (in particular 20 0 C air temperature) and at a constitutionalwindanströmung with a flow speed of 80 km / h, even when the internal combustion engine is stopped or stopped, drops by less than 3 K per minute.
- the internal combustion engine has a first cylinder group with two four-stroke cylinders and an additional expansion cylinder for subsequent expansion of the exhaust gas mixture of the four-stroke cylinder, wherein the expansion cylinder alternately from the two four-stroke cylinders absorbed combustion gases, and wherein the cylinder group has a common exhaust outlet and a subsequent common, thermally insulated exhaust pipe, whose radial thermal conductivity ⁇ is designed lower than 50 W / (m * K).
- the catalytic converter is assigned a catalytic converter in the region of an exhaust gas line, exhaust gas being taken from the exhaust gas pipeline downstream of the catalytic converter and directed via targeted exhaust gas recirculation to a heat exchanger via which heat is transferred from the exhaust gas to the cooling water wherein the cooled exhaust gas is then supplied either to the intake side of the internal combustion engine or to the exhaust pipe again.
- exhaust gas the internal combustion engine fed after exiting the expansion cylinder an exhaust gas turbocharger.
- an exhaust gas purifying catalyst and a pipe branching element are installed in the exhaust gas line, wherein by means of the pipe branching element at least a part of the exhaust gas can be supplied to said heat exchanger and optionally subsequently to the internal combustion engine.
- the drive unit is designed as a serial hybrid system such that the Auslege ancient is less than or equal to the associated power value according to the driving - resistance of the motor vehicle in the plane, at 145 at a defined reference speed, in particular at 125 km / h km / h or 160 km / h in the plane is reached.
- a reference speed in particular a continuous travel speed is assumed in the plane, which may otherwise be chosen differently from country to country and / or standard or sport PKW.
- the vehicle preferably has a power requirement at a constant speed with reference speed in the plane, which is selected as the output power of the internal combustion engine and as the output power of the entire hybrid system. Higher power requirements than the Auslege ancient - for example, when driving uphill and / or higher vehicle speed - according to the invention essentially covered by short-term power extraction from the electrochemical energy storage (accumulator, battery).
- 1 is a schematic diagram of a first motor vehicle according to the invention with an internal combustion engine ("5-stroke engine”) in a serial hybrid arrangement
- 2 shows a schematic diagram of a second motor vehicle according to the invention with an internal combustion engine (“5-stroke engine”) in a serial hybrid arrangement
- 3 is a longitudinal section of a third engine according to the invention with three cylinders
- FIG. 3a shows a cylinder head for a fourth internal combustion engine according to the invention in a longitudinal section, a cross section and a view from below,
- FIG. 4 shows a longitudinal section of a detail of the internal combustion engine according to FIG. 3, FIG.
- FIG. 5b is a temperature-time diagram showing a temperature profile of an internal combustion engine according to the invention when the internal combustion engine is initially stopped;
- Fig. 5c is a schematic diagram of the state of charge of the battery [in percent of the nominal state of charge] in a motor vehicle according to the invention when driving through a NEDC driving cycle and
- Fig. 6 is a schematic diagram of a driving resistance curve of a motor vehicle according to the invention.
- a motor vehicle according to the invention in the form of a passenger car 1 is equipped with a drive unit 2 according to the invention, which is explained in more detail below with reference to FIGS. 1 to 5.
- the motor vehicle can be used as vehicle be designed for the transport of goods as well as a motorcycle, bus, construction vehicle or the like. Alternatively, the motor vehicle can also be operated track-bound on rails. In any case, it has a driven wheel shaft 4 rotated by the drive unit and at least one driven wheel 5.
- the drive unit 2 essentially comprises an internal combustion engine 2.1, which is referred to elsewhere as a "5-stroke engine.”
- the internal combustion engine 2.1 in turn has at least two combustion chambers V, in particular combustion cylinders 2.2, in each case with a time interval Fuel-air mixture (starting mixture) is converted chemically exothermically such that an exhaust gas mixture with respect to the starting mixed increased latent heat and increased pressure is generated, the exhaust gas mixture in the combustion chambers V movably mounted piston Z a compressive force exerts such that by means of the piston Z, an output shaft 2.4 (“crankshaft”) is set in rotation, wherein the combustion chambers V is assigned a further working space in the form of an expansion cylinder 2.3, in the exhaust gas mixture ejected from the combustion chambers, releasing mechanical power to the output shaft 2.4 relaxed and subsequently into a Abgasla Ausla ss 20 überge-> leads.
- the internal combustion engine 2.1 receives the operation of liquid or gaseous fuel, in the form of a preferably organic substance, for.
- liquid or gaseous fuel in the form of a preferably organic substance, for.
- gasoline or diesel fuel or gasoline alcohol, biogas or methane or hydrogen gas or the like from a entrained in the motor vehicle 1 fuel tank. 3
- the internal combustion engine 2.1 has, in particular, at least two reciprocating cylinders 2.2 (two-stroke or four-stroke cylinders) operating at an ignition interval of 360 ° with combustion chambers V, in which the fuel is preferably ignited externally ignited by an Otto process with ambient air ,
- the internal combustion engine 2.1 has a further reciprocating cylinder 2.3 (expansion cylinder) for a subsequent further expansion of the combustion gases (fifth cycle). This relaxes from the two combustion cylinders 2.2 overflowed combustion gases and pushes them via an exhaust gas outlet in a downstream exhaust pipe 6.1, 6.2.
- the further reciprocating cylinder 2.3 (expansion cylinder) preferably operates in a kind of two-stroke process, wherein the exhaust gas of the combustion cylinder 2.2 is released substantially adiabatically while releasing mechanical work.
- the piston of the expansion cylinder 2.3 gives its power, like the pistons of the other two cylinders 2.2, preferably to a common output shaft 2.4 (crankshaft) (compare, in particular, FIG. 3).
- a first electromechanical energy converter G (“generator”) is coupled to the crankshaft 2.4 via a clutch and / or a gearbox
- a specific refinement of the first electromechanical energy converter G can be found in US 2009/0224628 A1, with respect to its construction (in particular, for the construction of the stator and the rotor using permanent magnets) and the operating conditions of the generator G.
- This generator G exchanges electrical energy with a storage unit B for electrical energy by means of power electronics E via electrical connection cables 2.5, 2.6. "Battery”, accumulator) off.
- a process computer or a control unit C controls both the operating state of the generator G and the operating state of the battery B and the internal combustion engine 2.1.
- the first electromechanical energy converter G is for the most part used as a generator to pick up mechanical energy of the internal combustion engine 2.1 and to transfer it to the battery B in the form of electrical energy.
- the generator G can also be used for starting and accelerating the internal combustion engine 2.1 from a standstill. It is preferable to convert the internal combustion engine 2.1 as quickly as possible from a rest state (standstill) into the optimum operating state with the aid of the first electromechanical energy converter G. lead by the internal combustion engine 2.1 is dragged by the generator G in an operating state with rated speed.
- the rated speed should be within a range of the (mathematical-physical) torque-rpm diagram of the internal combustion engine in which the internal combustion engine has a particularly low specific fuel consumption.
- the first electromechanical energy converter G is provided, the then working internal combustion engine 2.1 to provide a nominal load, which is also in a range of torque-torque diagram of the internal combustion engine, in which the internal combustion engine has a particularly low specific fuel consumption.
- the generator G should have the best possible efficiency, in particular not deviate more than 15% of its maximum efficiency.
- the internal combustion engine is thus assigned an electromechanical energy converter in the form of a generator G, which is mechanically coupled with an output shaft of the internal combustion engine 2.1 with or without transmission or clutch and can be driven by the internal combustion engine 2.1.
- the generator G can, as shown in detail in Fig. 3, be set on the rotor side directly to a crankshaft of the internal combustion engine.
- the generator G is designed in such a way that it also has the highest possible efficiency in the best point (selected for the internal combustion engine 2.1), the currents to be delivered and the voltage (s) of the generator G being in turn matched to the current storage unit B. Because the previously described subsystem (internal combustion engine, generator, electronics, battery) operates essentially under the same conditions, all design parameters can be optimized for these conditions.
- the internal combustion engine is operated quasi stationary at a rated speed of 2000 U / min with a nearly constant torque of 150 Nm against the load of the first electromechanical energy converter G in a preferred embodiment.
- a preferred fluctuation range of the rotational speed during a driving cycle of the motor vehicle 1 is 500 rpm at the nominal speed. speed (ie about +/- 250 rpm).
- the rated speed can be adjusted (possibly permanently) even in such a bandwidth - depending, for example, on permanently changed power requirements for the internal combustion engine, on (varying) fuel properties or ambient conditions.
- the internal combustion engine is operated quasi stationary at a rated speed of about 3500 U / min and a nominal torque of about 100 Nm.
- the performance parameters of the mutually associated components internal combustion engine, generator, power electronics and battery are adjusted accordingly to this operating condition.
- the internal combustion engine is preferably operated as long as in particular at nominal conditions until the battery B by supplying electrical energy at a share of 75% (or optionally optionally of 85% or 100%) of the intended maximum maximum storage capacity for the operation (set state of charge SOC) arrived is.
- the internal combustion engine 2.1 Upon reaching such a state of charge of the battery should be stopped by the computer unit C, the internal combustion engine 2.1 and only when needed, e.g. when the state of charge decreases to below 50% below the desired state of charge SOC (or at a state of charge of 45% or 60% of the desired state of charge) or in the case of power requirements of the motor vehicle above the power level of the battery B.
- 100% of the desired state of charge preferably corresponds to between 50% and 75% of the physically possible maximum charge state of the battery.
- the level of the desired state of charge is preferably selected as a function of average downtimes of the vehicle.
- the drive unit 2 of the motor vehicle 1 (as can be seen from FIGS. 1 and 2) has a further electromechanical energy converter in the form of a (Drive) motor-generator unit M / G on.
- the (drive motor) generator unit M / G is, for example via a differential D and / or a transmission (not shown) verbiinden with a drive shaft (wheel shaft 4), which directly drives the wheels of the motor vehicle.
- the further electromechanical energy converter M / G (motor-generator unit) exchanges via electrical connection cable 2.6, 2.7 and electronics also electrical energy with the storage unit B for electrical energy.
- the process computer or the control unit C controls both the operating state of the motor-generator unit M / G and the operating state of the battery B.
- the operating parameters of the motor-generator unit M / G are tuned to the operating behavior of the motor vehicle, since the motor-generator unit M / G draws their energy from the battery and is largely decoupled on this particular of the components internal combustion engine and generator.
- separate drive e-motors may be provided for the axles individually associated with the wheels, which in turn could draw their power from a central power storage unit.
- One or more drive motor-generator units M / G are used according to the invention as traction motors, which transmit the required torque for the propulsion of the motor vehicle to the wheels.
- both the motor-generator unit M / G and the internal combustion engine via a differential and / or a (planetary) gear and / or a clutch to the wheel shaft 4 to be coupled or be coupled, so that results in an alternative configuration of the drive unit 2.
- a load proportion of the internal combustion engine can be lower than the nominal load of the internal combustion engine 2.1, when at the same time the battery B is charged.
- an internal combustion engine 2.1 for a drive unit 2 comprises several cylinder groups each consisting of two high-pressure cylinders and one (substantially) larger expansion cylinder (low-pressure cylinder).
- the cylinder groups mentioned can be arranged in a row form, in V-shape, in box form or in star form (not shown in detail).
- second-order mass forces are compensated by compensating masses moving at twice the crankshaft speed, if necessary.
- a coupled via a fixed gear to the crankshaft balancing shaft is provided with balancing weights.
- a further variant of the drive unit 2 according to the invention according to FIG. 2 includes a further variant of an internal combustion engine according to the invention, which can be removed in detail from DE 60116942 T2.
- DE 60116942 T2 is in terms of a possible structure and principle operating method of the internal combustion engine
- an exhaust gas turbocharger unit 7 (exhaust gas turbocharger, ATL) explained in detail in DE 60116942 T2 is provided, which is inserted in the exhaust gas lines 6.1,
- the exhaust gas turbocharger unit 7 is released from the internal combustion engine discharged exhaust gas mixture and precompressed by means of the recovered energy fresh air for supply to the internal combustion engine.
- the exhaust gas expelled from the expansion cylinder 2.3 is fed via the exhaust gas line 6.1 to an expansion turbine of the exhaust gas turbocharger 7.
- the recovered mechanical energy is transmitted from the expansion turbine to a compressor wheel of the exhaust gas turbocharger 7, with which the internal combustion engine 2.1 ambient air to be supplied can be pre-compressed.
- Downstream of the ATL is an exhaust gas purifying catalyst CC.
- the internal combustion engine 2.1 (“5-stroke engine”) is particularly efficiently operated substantially stationary with almost constant speed (or in a small speed range of +/- 250 rpm around the rated speed) and integrated into a serial hybrid system, such as
- the constant speed as well as the power of the internal combustion engine to be output are preferably chosen such that a point of the best possible efficiency or maximum efficiency of the internal combustion engine (best point) is approximated as well as possible can be shut down and restarted at the given time.
- the best point is according to the invention in a speed range from 1000 U / min to about 5000 U / min, in particular between 1000 U / min to about 3500 U / min.
- a serial hybrid system for a traction drive with an average drive power of significantly more than 30 kW can be interpreted.
- such an overall system is designed so that the permanently deliverable by means of internal combustion engine 2.1 and generator G power is less than or equal to the drive power to be required at statutory or otherwise predetermined maximum speed and / or at a predetermined continuous travel speed.
- rated power values of 28 kW, 40 kW and 60 kW are selected for continuous travel speeds of a mid-range car of 125 km / h, 145 km / h and 160 km / h, respectively. For smaller or larger vehicles deviating values are provided accordingly.
- Fig. 6 results in a preferred interpretation of a drive concept for a motor vehicle 1 according to the invention according to the previous embodiments.
- the electric power provided by the internal combustion engine 2.1 together with the generator G should be just high enough for a predetermined nominal speed v Dma ⁇ to be able to be displayed permanently by the internal combustion engine 2.1 and the directly coupled generator G at rated power.
- a maximum steady-state speed v Dmax is set at approximately 120 km / h.
- a driving resistance curve FK of a middle class vehicle according to FIG Nominal power P N of generator G and internal combustion engine 2.1 are determined: These are at 120 km / h continuous speed of the vehicle about 28 kW, which results from the Cartesian coordinates of the point Fl on the driving resistance line FK.
- the described configuration are required for today's passenger cars displacement between 0.6 1 and 1.6 1 on the 5-stroke engine.
- electromotive operating state all load conditions in city traffic are electrically covered in real driving operation. From speeds of about 60 km / h, the internal combustion engine 2.1 is temporarily switched on, and the battery B is temporarily charged - with simultaneous removal of energy by the (drive) motor-generator unit M / G.
- FIG. 3 a simplified longitudinal section through a 5-stroke engine according to the invention
- FIG. 4 an enlarged detail of the same engine.
- the combustion cylinders 2.2 (four-stroke cylinders) are preferably operated in a four-stroke cycle, which is why they each have an intake valve 12 and an exhaust valve 13 in a cylinder head K assigned.
- the valves are caused in operation (in a conventional manner) by a camshaft 14 to a translational movement against the forces of a respective closing spring 19, wherein the camshaft 14 is coupled via a belt or chain transmission 15 to the crankshaft 2.4 and stored on the cylinder head K.
- Spark plugs are not shown, but are preferably used to carry out a four-stroke Otto combustion process.
- the combustion cylinders 2.2 are arranged with the expansion cylinder 2.3 substantially in one and the same plane, the respective pistons of the cylinders 2.2, 2.3 acting on the common crankshaft 2.4 via preferably connecting rods of the same length.
- a piston mass of the piston 11 in the expansion cylinder 2.3 is approximately twice as large as the mass of a piston in a combustion chamber of a combustion cylinder 2.2.
- the diameter of the expansion cylinder 2.3 by about 25% to 45%, in particular by about 40% larger than the diameter of a combustion chamber V.
- the stroke volume of the expansion cylinder 2.3 by about 100% greater than the displacement of a combustion cylinder , In particular, it can be seen from Fig.
- an overflow channel 16 has at the upper front end of the combustion chamber of a combustion cylinder 2.2 a substantially circular opening L (outlet opening of the combustion cylinder), which can be closed by the outlet valve 13 of the associated combustion cylinder 2.2.
- the overflow channel 16 has over its length initially a circular cross section and finally a substantially rectangular cross section, with which it opens at the upper end in the expansion cylinder 2.3.
- the overflow channel 16 has a length of less than 5 cm.
- the overflow channels 16 have not only a small length but also a small curvature with a correspondingly reduced deflection angle (with a change in direction of, for example, 70 ° to 90 °) - the harmful dead space in the overflow channels 16 is correspondingly low.
- the transfer of the gases from the combustion cylinders 2.2 thus takes place through slot-shaped openings 17 in the cylindrical wall of the expansion cylinder 2.3 with a flow direction approximately perpendicular to the cylinder axis of the expansion cylinder 2.3.
- the compression ratio equal expansion ratio
- the compression ratio is selected as high as possible. This results in the highest demands on the knock resistance of the fuel and the highest pressures or forces on many parts.
- a clear advantage is achieved by the combustion cylinders 2.2 undergoing structurally lower loads.
- FIG. 3 for a erfin 1 is shown in fragmentary longitudinal section through the internal combustion engine 2.1 (or a section through a single cylinder group).
- the overflow channels 16 which can be shut off by outlet valves 13 between the 4-cycle cylinders 2.2 (combustion chamber cylinders, right and left in FIG. 4) and the central, larger expansion cylinder 2.3 are particularly well recognizable here.
- the expansion cylinder preferably has an enlarged length relative to the combustion chamber cylinder 2.2 and / or an enlarged diameter relative to the combustion chamber ZyI 2.2.
- the walls of the additional expansion cylinder 2.3 have a heat loss-reducing coating Tl, T2, T3, T4 of suitable material.
- An annular region near the cylinder head K may have a 0.1 mm to 2 mm thick coating and / or an annular insert Tl of a material with the lowest possible thermal conductivity.
- coatings or inserts of stainless steel, in particular of nickel-containing steel or of a ceramic, more preferably of an aluminum oxide, of a (hard) anodized aluminum, nickel, titanium or the like are provided on the remaining cylinder wall of the expansion cylinder 2.3.
- an optional coating or surface treatment T2 of up to 100 ⁇ m may be made of similar material.
- a 0.1 mm to 2 mm thick coating and / or a disk-shaped insert T3 made of one of the abovementioned materials with the lowest possible thermal conductivity can be provided in the region of the expansion cylinder 2.3.
- a 0.1 mm to 2 mm thick coating and / or a dome-shaped attachment T4 made of a material with the lowest possible thermal conductivity is also preferably provided on an upper side of the piston 11 of the expansion cylinder.
- the Piston of the expansion cylinder to more than 50% of its volume made of a ceramic material.
- the walls In the combustion chamber ZyI in 2.2, the walls must be kept at a relatively low temperature by liquid cooling so that the amount of charge does not become smaller as a result of heating on the walls and no ignition by condensation on a hot wall is allowed to occur.
- these requirements are eliminated in the expansion cylinder 2.3, so that at a constant high temperature (especially in adiabatic relaxation) mechanical work can be obtained and less cooling heat must be dissipated.
- cylinder liners made of ceramic materials, in particular nickel-containing stainless steel, titanium or the like, are provided for the expansion cylinder 2.3.
- the expansion cylinder is centered, i. preferably associated with an identical (symmetry) axis an exhaust valve 18, via the exhaust gas can be transferred from the additional expansion cylinder in the exhaust system.
- the outlet (stroke) valve 18 which blocks the exhaust gas outlet H, 20 of the expansion cylinder (2.3) has a main axis which is aligned parallel to the main axis AH of the expansion cylinder, preferably coincident thereto.
- Said outlet (stroke) valve 18 may be wholly or partly made of a ceramic material and / or of a light metal such as titanium and / or provided with a ceramic coating.
- the low mass has a positive effect, e.g. noises and lower mass forces.
- Lower heat dissipation in conjunction with increased valve temperature may result in a reduction in heat loss of the expansion cylinder.
- FIG. 3a shows, starting from the top right: longitudinal cut through the cylinder head K of an internal combustion engine similar to the engine shown in Figures 3 and 4; a cross section through the cylinder head in the region of the expansion cylinder along the line I -I; View from below of the cylinder head along the level II-II.
- FIG. 3 a shows a view of a slot-shaped outlet opening 17 of the overflow channel in the expansion cylinder in the upper right-hand illustration.
- the approximately crescent-shaped three-dimensional design of the overflow channels can also be taken from the left upper illustration in FIG. 3a.
- the inlet openings I and the outlet openings A of the combustion cylinders are just as recognizable as the (single) outlet opening H of the expansion cylinder, through which the entire exhaust gas of the internal combustion engine passes into an exhaust tract, not shown in detail.
- FIG. 5 shows a section through an intake valve 12 of an internal combustion engine 2.1 for a further, modified drive unit 2 according to the invention.
- the essential aspect here is that the internal combustion engine according to FIG. 5 has an essentially complete encapsulation 50, which serves as heat and sound insulation.
- Such an encapsulation 50 according to the invention is intended in particular to be penetrated by an intake pipe 20A, an exhaust pipe and optionally one or more electricity lines (cables) and a fuel line. Otherwise, such optimized insulation could be completely closed.
- the insulation can be configured by a Kunststoffkapsei 51 with trapped air layer, by a foam sheathing 52 and / or other housing with low heat transfer rates.
- the insulation is continued in the region of an exhaust pipe 6.2, so that the exhaust gas supplied to an exhaust gas purifying catalyst CC arrives as warm as possible at the catalyst.
- the encapsulation comprises a plurality of different insulation elements 50, 51, 52, which extend over at least 80% of the outer surface of the internal combustion engine, so that it is effectively protected against heat losses as a result of heat radiation and ambient air inflow.
- the drive unit in particular the internal combustion engine according to FIG.
- FIGS. 5b and 5c an estimation in FIGS. 5b and 5c is shown, from which an exemplary profile of the engine core temperature MT results when the internal combustion engine is switched off and a motor vehicle according to the invention passes through a NEDC driving cycle.
- the engine core temperature MT is inventively measured on the cylinder head K or on the crankcase.
- Fig. 5c (in addition to the engine core temperature MT) in a solid line, the battery state of charge SOC [in percent of maximum] and the vehicle speed v [in km / h] over the test cycle time [in seconds] are shown.
- mass m 1300 kg
- drag coefficient cw 0.32
- frontal area A 2.17 m 2
- iges 6.5, f_rek 0.9.
- FIG. 5 a illustrates a system and a method for exhaust gas energy recovery according to the invention, which can be combined with the previously described exemplary embodiments. Accordingly, identical reference numerals are assigned for identical or equivalent elements.
- the exhaust gas energy recovery system comprises a multi-cylinder internal combustion engine 2.1 according to one of the embodiments described above, an exhaust gas turbocharger 7 and an exhaust gas catalytic converter CC.
- a multi-cylinder internal combustion engine 2.1 5-stroke engine, so
- energy is removed from the exhaust gas in a first stage by the exhaust gas in the expansion cylinder 2.3 is nachentspannt.
- the heat and pressure of the exhaust gas are treated as in a fifth working clock converted into mechanical work and brought directly to the crankshaft 2.4 of the internal combustion engine 2.1.
- the thus relaxed exhaust gas is supplied to the exhaust gas turbocharger 7 via an exhaust gas line 6.1.
- the exhaust gas is extracted by the exhaust gas turbocharger 7 further energy before the exhaust gas enters an exhaust aftertreatment system (catalyst CC).
- the exhaust-gas turbocharger compresses combustion air, which is supplied to the combustion cylinders 2.2 via an intake pipe 20A, and thus transfers energy extracted from the exhaust gas to the combustion air to be compressed.
- a third stage for example, in a cold start process, residual exhaust heat (after the catalyst CC) can be transferred via an exhaust gas / water heat exchanger W to a cooling water circuit 2.8 of the internal combustion engine 2.1.
- a control valve 6.3 is arranged in an exhaust branch pipe 6.4.
- the exhaust gas thus cooled should be recirculated to an intake pipe 2OB in a cold start process after an air filter F of the internal combustion engine, resulting in a quasi-fourth stage of energy recovery or energy retention.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- Transportation (AREA)
- General Engineering & Computer Science (AREA)
- Hybrid Electric Vehicles (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112010002535.5T DE112010002535B4 (de) | 2009-06-15 | 2010-04-12 | Kraftfahrzeug mit einer brennkraftmaschine sowie einem elektromotor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009025288 | 2009-06-15 | ||
DE102009025288.6 | 2009-06-15 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2010145628A1 true WO2010145628A1 (de) | 2010-12-23 |
Family
ID=42335187
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2010/000410 WO2010145628A1 (de) | 2009-06-15 | 2010-04-12 | Kraftfahrzeug mit einer brennkraftmaschine sowie einem elektromotor |
Country Status (2)
Country | Link |
---|---|
DE (1) | DE112010002535B4 (de) |
WO (1) | WO2010145628A1 (de) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014116302A1 (de) * | 2014-11-07 | 2016-05-12 | Obrist Technologies Gmbh | Hybridfahrzeug |
DE102016210825B4 (de) | 2015-06-26 | 2019-06-27 | GM Global Technology Operations LLC | Einzelwellen-verbrennungsmotor mit doppelter expansion |
DE102019128935A1 (de) * | 2019-10-25 | 2021-04-29 | DKS Hublifter GmbH | Brennkraftmaschine und Verfahren zum Betrieb einer Brennkraftmaschine |
CN113167116A (zh) * | 2018-09-25 | 2021-07-23 | 燃料节省有限公司 | 具有可调节的发动机单元连接的内燃机 |
DE202022001090U1 (de) | 2022-05-06 | 2023-08-08 | Ulrich Bruhnke | Antriebssystem für ein Fahrzeug und ein damit ausgerüstetes Fahrzeug |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE879183C (de) | 1951-01-31 | 1953-06-11 | Johann Janssens | Insbesondere gemischverdichtende Brennkraftmaschine, bei der einem Zylinder mit Frischgaszufuehrung ein Zylinder mit Abgaszufuehrung aus dem ersteren Zylinder zugeordnetist |
EP0223419A1 (de) * | 1985-10-19 | 1987-05-27 | Isuzu Motors Limited | Energierückgewinnungsvorrichtung für eine aufgeladene Brennkraftmaschine |
EP0463818A1 (de) * | 1990-06-22 | 1992-01-02 | Haring, Betty Jean | Verbrennungskraftmaschine und Verfahren dazu |
DE19625449A1 (de) * | 1995-08-02 | 1997-11-20 | Alexander Dr Ing Waberski | Kombi-Verbundverfahren für Dieselmotoren |
WO2004085187A1 (en) * | 2003-03-21 | 2004-10-07 | New Power Concepts Llc | Hybrid electric vehicles using a sterling engine |
DE60116942T2 (de) | 2000-10-26 | 2006-10-26 | Gerhard Schmitz | Fünftakt Brennkraft Maschine |
WO2008075130A1 (en) * | 2006-12-19 | 2008-06-26 | Renault Trucks | Power unit for an automotive vehicle and vehicle including such a power unit |
WO2009050456A2 (en) * | 2007-10-15 | 2009-04-23 | Langford Performance Engineering Limited | A hybrid powertrain |
US20090224628A1 (en) | 2005-07-20 | 2009-09-10 | Hideharu Hiwaki | Twin rotor type motor |
Family Cites Families (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0755816A3 (de) | 1995-07-28 | 1998-09-02 | Isuzu Ceramics Research Institute Co., Ltd. | Hybrides Elektrofahrzeug |
-
2010
- 2010-04-12 WO PCT/DE2010/000410 patent/WO2010145628A1/de active Application Filing
- 2010-04-12 DE DE112010002535.5T patent/DE112010002535B4/de not_active Expired - Fee Related
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE879183C (de) | 1951-01-31 | 1953-06-11 | Johann Janssens | Insbesondere gemischverdichtende Brennkraftmaschine, bei der einem Zylinder mit Frischgaszufuehrung ein Zylinder mit Abgaszufuehrung aus dem ersteren Zylinder zugeordnetist |
EP0223419A1 (de) * | 1985-10-19 | 1987-05-27 | Isuzu Motors Limited | Energierückgewinnungsvorrichtung für eine aufgeladene Brennkraftmaschine |
EP0463818A1 (de) * | 1990-06-22 | 1992-01-02 | Haring, Betty Jean | Verbrennungskraftmaschine und Verfahren dazu |
DE19625449A1 (de) * | 1995-08-02 | 1997-11-20 | Alexander Dr Ing Waberski | Kombi-Verbundverfahren für Dieselmotoren |
DE60116942T2 (de) | 2000-10-26 | 2006-10-26 | Gerhard Schmitz | Fünftakt Brennkraft Maschine |
WO2004085187A1 (en) * | 2003-03-21 | 2004-10-07 | New Power Concepts Llc | Hybrid electric vehicles using a sterling engine |
US20090224628A1 (en) | 2005-07-20 | 2009-09-10 | Hideharu Hiwaki | Twin rotor type motor |
WO2008075130A1 (en) * | 2006-12-19 | 2008-06-26 | Renault Trucks | Power unit for an automotive vehicle and vehicle including such a power unit |
WO2009050456A2 (en) * | 2007-10-15 | 2009-04-23 | Langford Performance Engineering Limited | A hybrid powertrain |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102014116302A1 (de) * | 2014-11-07 | 2016-05-12 | Obrist Technologies Gmbh | Hybridfahrzeug |
US10384528B2 (en) | 2014-11-07 | 2019-08-20 | Obrist Technologies Gmbh | Hybrid vehicle and generating set |
DE102016210825B4 (de) | 2015-06-26 | 2019-06-27 | GM Global Technology Operations LLC | Einzelwellen-verbrennungsmotor mit doppelter expansion |
US10590841B2 (en) | 2015-06-26 | 2020-03-17 | GM Global Technology Operations LLC | Single shaft dual expansion internal combustion engine |
CN113167116A (zh) * | 2018-09-25 | 2021-07-23 | 燃料节省有限公司 | 具有可调节的发动机单元连接的内燃机 |
CN113167116B (zh) * | 2018-09-25 | 2023-08-22 | 燃料节省有限公司 | 具有可调节的发动机单元连接的内燃机 |
DE102019128935A1 (de) * | 2019-10-25 | 2021-04-29 | DKS Hublifter GmbH | Brennkraftmaschine und Verfahren zum Betrieb einer Brennkraftmaschine |
DE102019128935B4 (de) | 2019-10-25 | 2021-10-28 | DKS Hublifter GmbH | Brennkraftmaschine und Verfahren zum Betrieb einer Brennkraftmaschine |
DE202022001090U1 (de) | 2022-05-06 | 2023-08-08 | Ulrich Bruhnke | Antriebssystem für ein Fahrzeug und ein damit ausgerüstetes Fahrzeug |
WO2023213358A1 (de) | 2022-05-06 | 2023-11-09 | Ulrich Bruhnke | Antriebssystem für ein fahrzeug und ein damit ausgerüstetes fahrzeug |
Also Published As
Publication number | Publication date |
---|---|
DE112010002535A5 (de) | 2012-09-20 |
DE112010002535B4 (de) | 2022-10-27 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
DE69821750T2 (de) | Hybridantriebssystem zur Verwendung im Fahrzeugbetrieb | |
DE102013208962B4 (de) | Verfahren und System zum Verringern der Turboverzögerung von Motoren | |
DE102010035085B4 (de) | Kraftwagen mit einer Verbrennungskraftmaschine sowie Verfahren zum Betreiben einer Verbrennungskraftmaschine | |
DE112010002535B4 (de) | Kraftfahrzeug mit einer brennkraftmaschine sowie einem elektromotor | |
DE102007017777A1 (de) | Turboladeranordnung und turboaufladbare Brennkraftmaschine | |
EP3038848B1 (de) | Verfahren zum antrieb eines kraftfahrzeuges sowie antriebssystem für ein kraftfahrzeug | |
EP2576984B1 (de) | Aggregat, insbesondere hybridmotor, stromgenerator oder kompressor | |
DE102004035341B4 (de) | Hybridfahrzeug | |
EP2069609B1 (de) | Umlaufkolben-brennkraftmaschine | |
DE102019124337A1 (de) | Stromerzeugungssystem und antriebsvorrichtung, die dieses aufweist | |
DE102017110855B4 (de) | Verfahren zum Betreiben einer Brennkraftmaschine, Einrichtung, Brennkraftmaschine | |
WO2012113379A2 (de) | Hybridisierung der brennkraftmotorsysteme nach dem additionsprinzip | |
EP3421762A2 (de) | Aufgeladene brennkraftmaschine | |
WO2011144188A1 (de) | Brennkraftmaschine | |
WO2018050349A1 (de) | Kombinierter elektro- und verbrennungsmotor, antriebsstrang und verfahren zum betrieb eines kraftfahrzeugs | |
DE202015101927U1 (de) | Aufgeladene Brennkraftmaschine mit Kompressor und Elektromaschine | |
WO2015169861A1 (de) | Schwenkkolbenmotor, verfahren zum betreiben eines schwenkkolbenmotors, motorsystem und kraftfahrzeug | |
EP0012329B1 (de) | Rotations-Schwinglader für Verbrennungskraftmaschinen | |
WO2023213358A1 (de) | Antriebssystem für ein fahrzeug und ein damit ausgerüstetes fahrzeug | |
DE2743149A1 (de) | Verbrennungsmotor | |
DE102012011086A1 (de) | Verbrennungskraftmaschine für einen Kraftwagen sowie Verfahren zum Betreiben einer solchen Verbrennungskraftmaschine | |
DE102011010742A1 (de) | Verbrennungskraftmaschine sowie Verfahren zum Betreiben einer solchen Verbrennungskraftmaschine | |
DE4241403A1 (en) | Gas-generator engine assembly - keeps gas outlet temp. from expansion unit to min. by controlling gas inlet temp. and pressure | |
DE102021208602A1 (de) | Hybrides Antriebssystem für ein Kraftfahrzeug | |
DE102015205324A1 (de) | Drei-Zylinder-Brennkraftmaschine mit Zylinderabschaltung und Verfahren zum Betreiben einer derartigen Drei-Zylinder-Brennkraftmaschine |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
121 | Ep: the epo has been informed by wipo that ep was designated in this application |
Ref document number: 10722918 Country of ref document: EP Kind code of ref document: A1 |
|
WWE | Wipo information: entry into national phase |
Ref document number: 1120100025355 Country of ref document: DE Ref document number: 112010002535 Country of ref document: DE |
|
122 | Ep: pct application non-entry in european phase |
Ref document number: 10722918 Country of ref document: EP Kind code of ref document: A1 |
|
REG | Reference to national code |
Ref country code: DE Ref legal event code: R225 Ref document number: 112010002535 Country of ref document: DE Effective date: 20120920 |