WO2011042297A1 - Antriebseinrichtung - Google Patents
Antriebseinrichtung Download PDFInfo
- Publication number
- WO2011042297A1 WO2011042297A1 PCT/EP2010/063880 EP2010063880W WO2011042297A1 WO 2011042297 A1 WO2011042297 A1 WO 2011042297A1 EP 2010063880 W EP2010063880 W EP 2010063880W WO 2011042297 A1 WO2011042297 A1 WO 2011042297A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- exhaust gas
- steam
- gas turbocharger
- exhaust
- drive device
- Prior art date
Links
- 238000002485 combustion reaction Methods 0.000 claims abstract description 62
- 239000012530 fluid Substances 0.000 claims abstract description 45
- 238000011144 upstream manufacturing Methods 0.000 claims description 13
- 238000009834 vaporization Methods 0.000 claims description 4
- 230000008016 vaporization Effects 0.000 claims description 4
- 230000001105 regulatory effect Effects 0.000 abstract description 7
- 238000001704 evaporation Methods 0.000 abstract description 6
- 239000007789 gas Substances 0.000 description 225
- 229920006395 saturated elastomer Polymers 0.000 description 26
- 238000003860 storage Methods 0.000 description 15
- 230000018109 developmental process Effects 0.000 description 12
- 239000000203 mixture Substances 0.000 description 8
- 239000003054 catalyst Substances 0.000 description 7
- 239000012071 phase Substances 0.000 description 6
- 238000006424 Flood reaction Methods 0.000 description 5
- 238000005338 heat storage Methods 0.000 description 4
- 238000002156 mixing Methods 0.000 description 4
- 238000004140 cleaning Methods 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 3
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 239000007788 liquid Substances 0.000 description 3
- 238000000034 method Methods 0.000 description 3
- 238000010025 steaming Methods 0.000 description 3
- 230000001133 acceleration Effects 0.000 description 2
- 230000003197 catalytic effect Effects 0.000 description 2
- 230000001276 controlling effect Effects 0.000 description 2
- 239000000498 cooling water Substances 0.000 description 2
- 238000011049 filling Methods 0.000 description 2
- 239000007791 liquid phase Substances 0.000 description 2
- 238000013021 overheating Methods 0.000 description 2
- 230000002035 prolonged effect Effects 0.000 description 2
- 230000005855 radiation Effects 0.000 description 2
- 230000008929 regeneration Effects 0.000 description 2
- 238000011069 regeneration method Methods 0.000 description 2
- 239000007787 solid Substances 0.000 description 2
- 239000002918 waste heat Substances 0.000 description 2
- XSQUKJJJFZCRTK-UHFFFAOYSA-N Urea Chemical compound NC(N)=O XSQUKJJJFZCRTK-UHFFFAOYSA-N 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 239000003990 capacitor Substances 0.000 description 1
- 239000004202 carbamide Substances 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 239000004020 conductor Substances 0.000 description 1
- 238000001816 cooling Methods 0.000 description 1
- 230000001627 detrimental effect Effects 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000000446 fuel Substances 0.000 description 1
- 239000003517 fume Substances 0.000 description 1
- 238000010438 heat treatment Methods 0.000 description 1
- 239000012535 impurity Substances 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000011068 loading method Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 230000003647 oxidation Effects 0.000 description 1
- 238000007254 oxidation reaction Methods 0.000 description 1
- 239000002245 particle Substances 0.000 description 1
- 239000012041 precatalyst Substances 0.000 description 1
- 238000000746 purification Methods 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000003319 supportive effect Effects 0.000 description 1
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
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/065—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle the combustion taking place in an internal combustion piston engine, e.g. a diesel engine
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
- F01K3/14—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having both steam accumulator and heater, e.g. superheating accumulator
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
- F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
- F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
-
- 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
- F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
-
- 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
- F02B37/02—Gas passages between engine outlet and pump drive, e.g. reservoirs
- F02B37/025—Multiple scrolls or multiple gas passages guiding the gas to the pump drive
-
- 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
- F02B37/10—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump at least one pump being alternatively or simultaneously driven by exhaust and other drive, e.g. by pressurised fluid from a reservoir or an engine-driven 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
- 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
- F02B39/085—Non-mechanical drives, e.g. fluid drives having variable gear ratio the fluid drive using expansion of fluids other than exhaust gases, e.g. a Rankine cycle
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the invention relates to a drive device with a charging device for
- DE 10 2006 057 247 A1 describes a charging device, in particular for charging an internal combustion engine.
- At least one heat exchanger of a circuit of the working medium is housed.
- the at least one exhaust gas heat exchanger is preceded by a delivery unit in the circulation of the working medium.
- the cycle of the working medium contains at least one turbine part, via which at least one compressor part arranged in the intake tract of the internal combustion engine is driven.
- the charging device is thus operated to increase the pressure in the intake tract of the internal combustion engine.
- DE 199 39 289 C1 describes a method and a device for the treatment of gas mixtures.
- charge air compression is known, for example, by means of piston compressors or turbines.
- the energy required to increase the pressure and mass flow is added to the exhaust gas of the combustion taken by evaporating fluid by means of a steam generator using the thermal energy of the exhaust gas.
- a steam generator using the thermal energy of the exhaust gas.
- the drive device with the features of claim 1 has the advantage that the efficiency of the internal combustion engine can be further increased, in particular by an increased use of the energy contained in the exhaust gas of the internal combustion engine.
- the steam generator is connected to a steam accumulator and that the supercharger is an exhaust gas turbocharger, the drive turbine is at least partially acted upon with both exhaust gas and steam from the steam accumulator, wherein the vapor pressure and / or steam mass flow of the exhaust gas turbocharger supplied steam is controllable and / or controllable.
- the exhaust-gas turbocharger is used to improve the degree of filling or the volumetric efficiency of the internal combustion engine and to reduce the suction work to be performed by the same during an intake stroke.
- the exhaust gas turbocharger usually has at least one drive turbine and at least one air compressor, wherein the drive turbine drives the air compressor.
- the drive device has an exhaust tract and a steam cycle. The former is the exhaust of the
- the exhaust gas turbine is also supplied with hot and / or saturated steam in addition to the exhaust gas.
- the exhaust gas tract and the steam cycle can run completely separated from one another, but can also be connected to each other at least in regions, so that a mixing of the steam with the exhaust gas can take place.
- the vapor is generated by evaporating the fluid by means of the steam generator using the thermal energy contained in the exhaust gas of the internal combustion engine. It is not necessary to supply the charging device or the exhaust-gas turbocharger with all the exhaust gas and / or the entire steam generated. Rather, it is advantageous if the guided portions of the exhaust gas and the steam are adjustable.
- the drive device provides the steam accumulator or steam pressure accumulator (steam boiler), from which the steam is taken for charging the exhaust gas turbocharger, for example in the form of saturated steam or for introduction into a superheater and subsequent admission of the exhaust gas turbocharger.
- the control and / or regulation can be provided continuously and takes place, in particular, as a function of an exhaust gas pressure and / or an exhaust gas mass flow.
- the exhaust gas turbocharger is mainly operated with the exhaust gas of the internal combustion engine. However, with the generated steam he is at least supportive operable. This can in particular serve an instant boost in boost pressure of the exhaust gas turbocharger and thus a rapid increase in engine speed and / or torque independent of engine and / or exhaust gas turbocharger rotational speed, boost pressure, air mass flow into the internal combustion engine, exhaust gas pressure and / or exhaust gas mass flow.
- the usually sluggish response of the exhaust gas turbocharger is overcome by the drive turbine of the exhaust gas turbocharger is accelerated very quickly, as soon as an agile power delivery is required. This is the case in particular when the internal combustion engine is accelerated with a high torque requirement from the part-load range or in overtaking maneuvers at higher speeds-if the drive device is used in a motor vehicle.
- the drive device also has the advantage of being able to cool the exhaust gas of the internal combustion engine to controlled temperature and / or controlled mode of operation to the desired temperature range before it enters an exhaust gas aftertreatment device. This is necessary in particular in gasoline engines with peak exhaust gas temperatures of higher than 1000 ° C before entering the exhaust aftertreatment device, since the usually provided as exhaust aftertreatment device 3-way or NO x storage in a temperature range optimal reduction rates of 400 ° C. up to 750 ° C. be operated at 300 ° C to 450 ° C are. Furthermore, a heat radiation of the internal combustion engine, in particular of an exhaust manifold, and of a portion of the exhaust tract close to the engine into an engine compartment is reduced.
- the admission pressure and exhaust gas mass flow of the exhaust gas turbocharger of the exhaust gas turbocharger can be made uniform with the steam. This is possible, in particular, with exhaust gas turbochargers flowed in with multiple floods.
- two embodiments of the drive device according to the invention are technically advantageous: first, in the form of an open steam cycle, in which the
- Shaft is provided, such as an exhaust gas turbine, which is flowed only with exhaust gas. Exhaust tract and steam cycle are thus separated. It can also be provided to introduce the steam in addition to the exhaust gas flow in an exhaust gas turbine with double-flow of the turbine wheel.
- the steam storage For storing the generated steam, the steam storage is provided. After the generation of the steam by means of the steam generator this is therefore not immediately supplied to the exhaust gas turbocharger, but cached in the steam storage.
- the steam stored in the steam accumulator is preferably a saturated steam, the steam accumulator can therefore also be referred to as a saturated steam storage or saturated steam boiler.
- the steam storage the steam is only temporarily stored, there is no removal of energy contained in the steam.
- the storage capacity of the steam accumulator allows without mechanical additional units with rotating elements and additional moments of inertia a very agile response of the exhaust gas turbocharger even at low speeds of the internal combustion engine and at low exhaust gas and charge air mass flows of the internal combustion engine.
- the steam accumulator depending on the temperature of the injected steam, a saturation vapor pressure is established.
- the steam accumulator can be continuously supplied with steam as long as the internal combustion engine is operated with sufficiently high exhaust gas temperatures.
- the wall of the vapor accumulator is ther- mixed isolated.
- its capacity is large enough to be able to hold sufficient steam even during prolonged operating phases of the internal combustion engine with low power output and low exhaust gas temperature and low exhaust gas mass flow for the purpose of rapid acceleration of the drive turbine.
- This in turn has the desired agile response of the exhaust gas turbocharger or its air compressor even at low engine speeds and low exhaust gas and charge air mass flows result.
- it can be provided to feed at least a portion of the steam taken off from the steam accumulator, in particular saturated steam, directly to the exhaust gas turbocharger.
- a further development of the invention provides that a heat exchanger, in particular arranged downstream of the exhaust gas turbocharger, is provided for removing the thermal energy.
- a heat exchanger in particular arranged downstream of the exhaust gas turbocharger, is provided for removing the thermal energy.
- thermal energy is taken from the exhaust gas and fed to the steam generator. It is advantageous to arrange the heat exchanger such that residual energy can be withdrawn with it, which is still contained in the exhaust gas after flowing through the exhaust gas turbocharger.
- the heat exchanger and the steam generator can also be designed integrated.
- a development of the invention provides that at least part of the steam is combined with the exhaust gas upstream of the exhaust gas turbocharger or in the exhaust gas turbocharger.
- the exhaust gas tract and the steam cycle can certainly overlap at least in certain areas.
- the steam is conducted together with the exhaust gas, for example in a common line.
- the mixture of exhaust gas and steam can be supplied together to the exhaust gas turbocharger or its drive turbine.
- the turbine wheel is subjected to the single-flow with only one nozzle with the exhaust-steam mixture.
- the merging of steam and exhaust gas is provided only within the exhaust gas turbocharger, but preferably before or in the drive turbine.
- the mass flow passing through the exhaust gas turbocharger is increased and, at the same time, the temperature of the exhaust gas is lowered, as long as the steam temperature does not exceed the exhaust gas temperature, which is the case in particular in the full load range of petrol and diesel engines is, so that the thermal load of the exhaust gas turbocharger can be reduced.
- a development of the invention provides a downstream of the exhaust gas turbocharger arranged capacitor and / or separator for the recovery of the
- Fluids from the exhaust before When the vapor is combined with the exhaust gas, it makes sense not to deliver it together with the exhaust gas from the drive device in an environment of the drive device. Instead, the fluid is to be recovered from the exhaust gas for reuse.
- the separator and / or condenser is provided. With this, the fluid or the vaporized fluid is separated from the exhaust gas, so that it can be supplied to the steam cycle again.
- only a comparatively small supply of fluid with the drive means must be carried and only from time to time unavoidable losses of the fluid to be compensated.
- the exhaust gas turbocharger has at least one exhaust gas flow and at least one steam flow, which are fluidically separated from each other.
- the steam is not combined with the exhaust gas, but is passed separately through the exhaust gas turbocharger.
- the at least one exhaust gas flow and the at least one steam flow are provided, in each of which a turbine wheel is preferably arranged.
- the exhaust gas flows through the exhaust gas, the steam flows through the steam.
- the turbine wheels, which are assigned to the floods, are connected to one another via a common shaft, which is simultaneously connected to the air compressor.
- the exhaust tract and the steam cycle run completely separated from each other, so the steam is never in contact with the exhaust gas at any time.
- each flood can be matched to the respective pressure or the respective temperature of the exhaust gas or the vapor.
- the steam and the exhaust gas flow are conducted separately from one another until just in front of a turbine wheel of the drive turbine and independently of each other by a respective steam nozzle and an exhaust nozzle (hot gas nozzle) has flowed into the exhaust gas turbocharger, without mixing before the application.
- the steam nozzle and the exhaust nozzle can be applied independently of each other advantageously to the fluid mechanical and thermal conditions in the exhaust gas and the steam.
- a development of the invention provides that the exhaust gas flow and the steam flow are provided in a housing of the exhaust gas turbocharger. It is thus formed a common housing, which preferably receives all the floods of the exhaust gas turbocharger. Alternatively, however, each flood could have its own housing and the turbines associated with the floods could only be connected to one another via a common shaft.
- a two-part drive turbine may be provided.
- the housing has at least one exhaust gas flow chamber, which contains an exhaust gas turbine wheel, and a separate steam flow chamber, which contains a steam turbine wheel. The steam and the exhaust gas act independently of each other, the two-piece drive turbine, without mixing and flow separately from this from.
- a plurality of steam fumes are provided, that is, the exhaust gas turbocharger is thus subjected to a plurality of vapor streams.
- a saturated steam flow and a hot steam flow can be provided, which are supplied to the exhaust gas turbocharger in addition to the secondary flow.
- a further development of the invention provides that the drive turbine of the exhaust gas turbocharger has at least one exhaust turbine wheel and at least one steam turbine wheel, the steam turbine wheel and the exhaust gas turbine wheel being provided on a common shaft.
- the exhaust turbine wheel is preferably associated with the exhaust gas flow and the steam turbine wheel of the steam flow.
- About the common shaft of the air compressor of the exhaust gas turbocharger is driven.
- a further development of the invention provides that, in terms of flow, a superheater is provided between the steam generator and / or the steam accumulator and the exhaust gas turbocharger.
- the superheater is traversed by steam from the steam generator and / or the steam storage. It is arranged upstream of the exhaust gas turbocharger.
- the steam which in particular as
- Saturated steam is present, further heated.
- the steam present after the superheater can therefore be called superheated steam.
- This hot steam is then fed to the exhaust gas turbocharger.
- these proportions are controlling and / or regulating adjustable.
- the steaming of the exhaust gas turbocharger can advantageously be adapted to the exhaust gas temperature and the operating state and the desired power output of the internal combustion engine.
- the hot and / or saturated steam flow acting upon the steam turbine described above can be supplied to the exhaust-gas turbocharger in one-flow or two-flow.
- a development of the invention provides that the superheater can be acted upon by a further, in particular upstream of the turbocharger arranged, high-temperature turebenleye with thermal energy.
- the high-temperature heat exchanger like the heat exchanger, removes thermal energy from the exhaust gas.
- the expression "high-temperature heat exchanger” merely means that the temperature range in which the high-temperature heat exchanger operates is higher than that of the heat exchanger, for which it is advantageous if the exhaust-gas turbocharger is arranged at a location of the exhaust-gas tract at which the exhaust gas still compares high temperature.
- a development of the invention provides that the steam accumulator is arranged in an exhaust gas duct or encloses this.
- the exhaust pipe is part of the exhaust tract.
- the exhaust gas guide tube essentially designates all (pipe) lines through which exhaust gas flows.
- the steam accumulator should preferably be constantly exposed to heat. This is achieved by arranging the steam accumulator in the area of the exhaust gas guide tube. In this case, both an arrangement may be provided in the exhaust pipe and around the exhaust pipe. In the former case, care must be taken that the steam accumulator opposes the exhaust gas flowing in the exhaust gas duct to the lowest possible flow resistance.
- the steam storage can be designed aerodynamically. If the steam accumulator encloses the exhaust gas guide tube, it makes sense that this is good at least in this area thermally conductive material.
- the exhaust duct may also include an exhaust manifold.
- a development of the invention provides a heat accumulator associated with the steam accumulator.
- the heat accumulator may comprise, for example, a latent heat storage medium whose physical state changes from solid to liquid in the region of the desired steam temperature. In this way, the temperature of the steam present in the steam accumulator can be maintained at the desired temperature even if only a little thermal energy can be taken from the exhaust gas or an excess of thermal energy
- a further development of the invention provides that at least one exhaust gas aftertreatment device is provided downstream and / or upstream of the steam generator.
- the exhaust aftertreatment device is for example a catalyst or a filter.
- FIG. 1 shows a schematic representation of a drive device in a first embodiment, wherein a steam cycle extends in regions together with an exhaust gas tract of an internal combustion engine and a heat exchanger is arranged downstream of an exhaust gas aftertreatment device,
- FIG. 2 shows the drive device known from FIG. 1, but with the heat exchanger arranged upstream of the exhaust gas aftertreatment device,
- FIG. 3 shows a second embodiment of the drive device, in which the steam cycle runs separately from the exhaust gas tract, ie the steam cycle is closed and separated from the exhaust gas tract
- FIG. 4 shows the drive device known from FIG. 3, wherein a fluid feed is provided in a steam accumulator,
- Figure 5a shows the steam accumulator in a first embodiment
- the charging device 3 has a turbine part 4, which has at least one drive turbine, and a compressor part 5, which are connected via a shaft 6 in operative connection.
- the charging device 3 is an exhaust gas turbocharger 7, the turbine part 4 is at least traversed by the exhaust gas of the internal combustion engine 2.
- the compressor part 5 serves, in particular from an environment of the drive device 1 originating to compress air and thus bring to a higher pressure. The compressed air is then supplied to the internal combustion engine 2.
- the resulting exhaust gases are combined from cylinders 8 of the internal combustion engine 2 by means of an exhaust manifold 9 and discharged in an exhaust gas duct 10.
- the exhaust manifold 9 is formed for example as a fan header. Adjoining this is an exhaust gas intake pipe 10 ', which is part of the exhaust gas guide pipe 10.
- the internal combustion engine 2 may also have a plurality of cylinder banks, in this case, both a plurality
- Exhaust manifold 9 and exhaust manifolds 10 'and exhaust guide tubes 10 is provided.
- the exhaust gas passes through the exhaust gas guide tube 10 at least into the turbine part 4 of the charging device 3. Downstream of the charging device 3 and the exhaust gas turbocharger 7, a first exhaust gas aftertreatment device 11 and a second exhaust gas aftertreatment device 12 are arranged in series.
- the second exhaust aftertreatment device 12 is an SCR catalytic converter.
- Exhaust-gas-carrying parts described so far, such as the exhaust gas guide pipe 10 form an exhaust tract 13, through which the exhaust gas is discharged from the internal combustion engine 2.
- the first exhaust aftertreatment device 1 1 consists, for example, in a diesel engine of an HC oxidation catalyst (DOC) and a diesel particulate filter (DPF), in a gasoline engine usually from a 3-way catalyst.
- the second exhaust gas treatment device 12 can, in a diesel engine of a reduction catalyst with upstream urea dosing device or injection proper (SCR), and wherein one, in particular with direct injection, stratified charge spark-ignition engine of a NO x - consist storage catalyst (NSC).
- SCR upstream urea dosing device or injection proper
- NSC stratified charge spark-ignition engine of a NO x - consist storage catalyst
- the second exhaust aftertreatment device 12 usually operates at lower temperatures than the first exhaust aftertreatment device 1 1 and is therefore arranged downstream of it.
- a steam cycle 14 is further shown.
- this steam is generated, which is also the exhaust gas turbocharger 7 can be fed.
- the exhaust gas tract 13 and the steam circuit 14 have a common region 15, through which the generated steam flows together with the exhaust gas.
- the steam cycle 14 initially has a fluid delivery device 16, for example a pump. This is connected via a fluid line 17 to a steam generator 18 and can supply this fluid.
- the steam generator 18 is provided for evaporation of the supplied fluid. Subsequent to the steam generator 18, the steam thus generated passes through a steam line 19 into a steam reservoir 20, in which the steam is stored.
- the steam accumulator 20 has a steam valve 21, by means of which steam can be released from the steam accumulator 20. In this way, the present in the steam accumulator 20 steam pressure can be regulated or limited.
- the steam accumulator 20 is connected to the exhaust gas turbocharger 7 via a first supply line 22 and a second supply line 23. Via the supply lines 22 and 23 so steam in the exhaust gas turbocharger 7 and its
- Turbine part 4 are introduced.
- the vapor can already be brought together with the exhaust gas upstream of the exhaust-gas turbocharger 7 or, as shown in FIG. 1, be combined with it in the exhaust-gas turbocharger 7.
- a cross-section adjustment element 24 for example an electrically adjustable throttle valve, is arranged.
- Amount of the introduced from the steam accumulator 20 in the exhaust gas turbocharger 7 Controlling and / or regulating steam. Because so-called saturated steam is present in the steam accumulator 20, the first supply line 22 can also be referred to as saturated steam line 25. In the second supply line 23 is first a superheater 26 and downstream of this also a Queritessverstellelement 27 is provided. Steam or saturated steam can be superheated by means of the superheater 26, so that superheater 26 is subsequently provided with superheated steam. By means of the Querterrorismsverstellelements 27, which is for example also an electrically adjustable throttle valve, the exhaust gas turbocharger 7 through a hot steam line 28 supplied amount of hot steam can be controlled or regulated regulating.
- the separator 29 the mixture of exhaust gas and steam, the steam or the fluid withdrawn and over a fluid line 30 of a Fluid inhabitsein- device 31, which has, for example, a filter supplied.
- the fluid cleaning device 31 the fluid is freed from impurities, for example dirt particles, which it has taken up from the exhaust gas.
- the fluid cleaning device 31 may, for example, also have a deacidification device.
- the fluid purified by means of the fluid cleaning device 31 is then fed back to the fluid delivery device 16. Alternatively, it may also enter a storage container (not shown) in which it is stored.
- the fluid can be supplied to the steam generator 18 again by means of the fluid delivery device 16.
- the steam generator 18 is operated to evaporate the fluid with thermal energy, which is taken from the exhaust gas of the internal combustion engine 2 by means of a heat exchanger 32.
- the heat exchanger 32 is provided in the exhaust gas tract or the exhaust gas guide tube 10.
- the superheater 26 is supplied with thermal energy by means of a high-temperature heat exchanger 33.
- the heat exchanger 32 is downstream of the exhaust aftertreatment devices 1 1 and 12, the high-temperature heat exchange 33 upstream (in each case based on the exhaust gas) of the exhaust gas turbocharger 7 is provided.
- a portion of the saturated steam is thus passed from the steam reservoir 20 in the superheater 26, which is supplied by the high-temperature heat exchanger 33 with thermal energy from the exhaust gas.
- the superheated steam thus generated reaches the exhaust-gas turbocharger 7 via the cross-section adjustment element 27. It is advantageous when the superheated steam flows in through a separate inlet opening into the turbine part 4.
- An advantageous embodiment of the turbine part 4 thus comprises a three-flow flow of a turbine wheel, not shown, which allows adapted to different pressures and / or temperatures of the exhaust gas or the saturated and / or superheated steam design of inlet nozzles. Such a multiple-flow admission of the turbine part 4 prevents a flow of the steam starting from the exhaust gas turbocharger 7 in the direction of the internal combustion engine 2.
- the distribution of the steam from the steam reservoir 20 to the hot steam line 28 or the saturated steam line 25 is adjusted continuously by means of the cross-section adjustment elements 24 and 27, which are present for example as throttle valves.
- the thermal energy extracted from the exhaust gas by means of the heat exchangers 32 and 33 can also be used for further purposes in addition to vaporization or overheating of the fluid.
- the energy can be delivered, for example, to an underbody air flow or via corresponding preheating devices to a passenger compartment to be heated up. It is also conceivable to provide the thermal energy to a cooling water or oil circuit of the internal combustion engine 2, so that they can be heated faster.
- the drive device 1 shown in FIG. 1, in which the heat exchanger 32 is arranged downstream of the exhaust gas aftertreatment devices 11 and 15, can usually be used when the internal combustion engine 2 is an Otto engine. For this it is necessary to maintain the temperature of the second exhaust gas aftertreatment device 12, which is for example the NO x storage catalytic converter, at a temperature greater than 300 ° C.
- FIG. 2 shows the exhaust gas aftertreatment device 1 known from FIG. 1 in an arrangement which can be used when the internal combustion engine 2 is a diesel engine.
- the heat exchanger 32 may be useful to arrange the heat exchanger 32 upstream of the second exhaust aftertreatment device 12 in order to provide the steam generator 18 with a sufficient amount of thermal energy.
- the SCR catalyst often provided as an exhaust aftertreatment device 12 is effective even at temperatures of about 170 ° C, and therefore can be easily disposed downstream of the heat exchanger 32.
- FIG. 3 shows a second embodiment of the drive device 1. This differs from the first embodiment as shown in FIG. 1 with regard to the design of the steam cycle 14 and the exhaust gas turbocharger 7.
- the turbine part 4 is first of all constructed in a multiple-flow manner (here: twin-flow). In this case, it has an exhaust gas flow 34 and two steam flows 35
- the exhaust gas flow 34 is connected to the exhaust gas guide tube 10 and is flowed through exclusively by exhaust gas.
- the steam fl ows 35 are only flowed through by steam, one of the steam fl ows 35 being able to be acted upon by the saturated steam line 25 and the other by the hot steam line 28.
- the floods 34 and 35 are therefore completely separated from each other in terms of flow.
- a turbine wheel is in each case provided, which is driven by the exhaust gas or the steam.
- the turbine wheels are connected to the compressor part 5 via a common shaft 6. The shaft 6 is thus driven by both the exhaust gas flow 34 and the steam flow 35.
- a condenser 36 Downstream of the steam flutes 35 of the exhaust gas turbocharger 7, a condenser 36 is provided, by means of which the steam flowing out of the steam flutes 35 is condensed, so that the fluid is present in the condenser 36 and can be discharged therefrom.
- the fluid is stored in a reservoir 37, from which it can be supplied by means of the fluid conveyor 16 to the steam generator 18. This is, as already described with reference to Figure 1, from the heat exchanger 32 - which is arranged in the exhaust tract 13 - supplied with thermal energy and serves to evaporate the fluid.
- the generated steam is supplied to the steam reservoir 20 via the steam line 19, from which it can be supplied to the exhaust gas turbocharger 7 via the supply lines 22 and 23 or the saturated steam line 25 and the superheated steam line 28.
- the outlet nozzles and turbine wheels of the steam flutes 35 are each optimized for the properties of the saturated steam or superheated steam.
- the inlet openings of the steam flutes 35 may be designed as Laval nozzles.
- a multi-flow, in particular double-flow, embodiment of the steam flutes 35 prevents dissipation by turbulent mixing of hot and saturated steam in the turbine inlet flow.
- the exhaust gas flow 34 and the steam flutes 35 are arranged in a common housing (not shown).
- a Laval turbine wheel can be used in the exhaust gas turbocharger 7.
- the heat exchanger 32 can also, as can be seen from FIG. 2, be arranged upstream of at least the second exhaust gas aftertreatment device 12. If the steam cycle 14, as here, separate from the exhaust tract 13, so runs in the steam cycle 14, a Clausius-Rankine steam process.
- the fluid is sprayed or atomized during introduction into the steam reservoir 20.
- the saturated steam contained in the steam accumulator 20 can be moistened, so that wet steam is present.
- This wet steam can flow directly into the exhaust gas turbocharger 7 from the steam reservoir 20 via the first supply line 22 or the saturated steam line 25.
- the wet steam is overheated in the exhaust gas turbocharger 7 and cools it down.
- the amount of heat absorbed by the wet steam essentially corresponds to the enthalpy of vaporization of the liquid phase contained, that is to say of the fluid introduced via the fresh fluid line 38 into the vapor reservoir 20.
- the fresh fluid line 38 and the cross-sectional Adjusting device 39 is provided in the drive device 1 according to Figures 1 and 2.
- the exhaust gas temperature can be lowered directly by the introduced fluid, so that the temperature load of the exhaust gas turbocharger 7 and the exhaust aftertreatment devices 1 1 and 12 is reduced.
- FIGS. 5a and 5b each show an embodiment of the vapor accumulator 20.
- the vapor accumulator 20 of FIG. 5a has a tubular design and is arranged together with the heat exchanger 32 and the steam generator 18 in the exhaust gas guide tube 10. This means that both steam reservoir 20 and heat exchanger 32 are flowed through by the exhaust gas. In this way, heat losses of the vapor accumulator 20 are reduced. Likewise, no additional external space in the area of a vehicle underbody is claimed.
- a heat accumulator 40 which in particular comprises a latent heat storage medium, may be provided in the vapor accumulator 20. The physical state of this latent heat storage medium changes in the range of the desired saturated steam temperature from solid to liquid. By means of the steam valve 21, saturated steam can be released from the steam accumulator 20 into the exhaust gas duct 10.
- FIG. 5b shows a further embodiment of the vapor accumulator 20.
- this vapor accumulator 20 surrounds the exhaust gas guide tube 10, preferably in a region close to the engine.
- the steam accumulator 20 also comprises the exhaust manifold 9 at least in certain areas.
- the steam accumulator 20 in conjunction with the
- High-temperature heat exchanger 33 and the superheater 26 advantageously designed as a double-walled molded part with high heat storage capacity.
- the molded part can provide a mounting flange for the exhaust gas turbine and a tap for exhaust gas recirculation, in particular a high-pressure exhaust gas recirculation.
- the heat accumulator 40 (not shown) may be arranged.
- Such an embodiment of the vapor accumulator 20 leads to a substantial reduction of the unwanted heat radiation in an engine compartment of the internal combustion engine 2. It uses the high-temperature waste heat of the exhaust gas manifold 9 for overheating the saturated steam and for quickly bringing about the readiness for operation during warm-up of the internal combustion engine. 2.
- Control unit of the internal combustion engine 2 is built up in the steam accumulator 20 vapor pressure and vapor mass, as by the operation of the internal combustion engine 1 to an already sufficient exhaust gas temperature and waste heat quantity or thermal energy is available.
- a quick warm start of the internal combustion engine 2 can also be achieved in a "start-stop" operation by means of the described drive device 1.
- the steam accumulator 20 also maintains the pressure and temperature of the steam during prolonged operating pauses of the internal combustion engine 2, since the evaporation of the fluid and so that the supply of the steam accumulator 20 with steam operates continuously while the internal combustion engine 2 is running.This also applies if there is no steaming of the exhaust gas turbocharger 7.
- the admission of the exhaust gas turbocharger 7 is suppressed with steam, as well as during a warm-up phase of the precatalyst warm-running gasoline engines, since temporarily higher exhaust gas temperatures are desired in these phases of operation to the Reheat exhaust after treatment devices 1 1 and 12.
- the application of superheated steam to the exhaust gas turbocharger 7 would reduce the exhaust gas temperature too far. During these phases, therefore, the cross-section adjustment elements 24 and 27 are closed.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
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- General Engineering & Computer Science (AREA)
- Supercharger (AREA)
Abstract
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
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BR112012007994A BR112012007994A2 (pt) | 2009-10-06 | 2010-09-21 | conjunto de acionamento |
CN2010800448037A CN102656348A (zh) | 2009-10-06 | 2010-09-21 | 驱动装置 |
EP10760974A EP2486257A1 (de) | 2009-10-06 | 2010-09-21 | Antriebseinrichtung |
US13/499,865 US20120260654A1 (en) | 2009-10-06 | 2010-09-21 | Driving device |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102009045380.6 | 2009-10-06 | ||
DE102009045380A DE102009045380A1 (de) | 2009-10-06 | 2009-10-06 | Antriebseinrichtung |
Publications (1)
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WO2011042297A1 true WO2011042297A1 (de) | 2011-04-14 |
Family
ID=43414879
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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PCT/EP2010/063880 WO2011042297A1 (de) | 2009-10-06 | 2010-09-21 | Antriebseinrichtung |
Country Status (6)
Country | Link |
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US (1) | US20120260654A1 (de) |
EP (1) | EP2486257A1 (de) |
CN (1) | CN102656348A (de) |
BR (1) | BR112012007994A2 (de) |
DE (1) | DE102009045380A1 (de) |
WO (1) | WO2011042297A1 (de) |
Cited By (1)
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WO2012048959A1 (de) * | 2010-10-13 | 2012-04-19 | Robert Bosch Gmbh | Vorrichtung und verfahren zur abwärmenutzung einer brennkraftmaschine |
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JP5185910B2 (ja) * | 2009-10-16 | 2013-04-17 | 三菱重工業株式会社 | ミラーサイクルエンジン |
DE102010042412A1 (de) * | 2010-10-13 | 2012-04-19 | Robert Bosch Gmbh | Dampfturbine |
JP5727900B2 (ja) * | 2011-09-02 | 2015-06-03 | ダイムラー・アクチェンゲゼルシャフトDaimler AG | 内燃機関の過給制御装置 |
DE102011121471A1 (de) | 2011-12-17 | 2013-06-20 | Volkswagen Aktiengesellschaft | Wärmespeicher zur Speicherung einer Abwärme für ein Fahrzeug sowie Verfahren und System zur Erzeugung mechanischer oder thermischer Energie aus einer Abwärme eines Fahrzeugs |
DE102012019967B4 (de) | 2012-10-08 | 2014-04-24 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Aufladeeinrichtung für Brennkraftmaschinen |
KR101449141B1 (ko) * | 2012-11-07 | 2014-10-08 | 현대자동차주식회사 | 차량의 폐열 회수 시스템을 이용한 터보장치 |
DE102012222035B4 (de) * | 2012-12-03 | 2019-10-31 | Robert Bosch Gmbh | Verfahren zum Betreiben eines Systems zur Energierückgewinnung aus einem Abwärmestrom einer Brennkraftmaschine |
EP2978943A1 (de) * | 2013-03-25 | 2016-02-03 | Dana Limited | Abfallwärmerückgewinnungssystem und verfahren zur steuerung der massedurchflussrate eines verdrängerexpanders in solch einem system |
EP2921688A1 (de) * | 2014-03-20 | 2015-09-23 | ABB Turbo Systems AG | Aufladesystem mit Abgas-Rezirkulation |
DE102014205878A1 (de) * | 2014-03-28 | 2015-10-01 | Mtu Friedrichshafen Gmbh | Brennkraftmaschine und Verfahren zum Betreiben einer Brennkraftmaschine |
US20160097305A1 (en) * | 2014-10-06 | 2016-04-07 | Cummins, Inc. | Oxidation catalyst for waste heat recovery performance improvement |
EP3051098B1 (de) | 2015-02-02 | 2018-04-11 | Volvo Car Corporation | Twin-scroll-turboladervorrichtung mit verbesserter turboreaktion |
DE102015208360A1 (de) * | 2015-05-06 | 2016-11-10 | Bayerische Motoren Werke Aktiengesellschaft | Kraftfahrzeug |
EP3095982B1 (de) | 2015-05-20 | 2018-12-05 | Volvo Car Corporation | Verbessertes turboladersystem |
AT517368B1 (de) * | 2015-06-24 | 2017-08-15 | Avl List Gmbh | Brennkraftmaschine mit einem abwärmerückgewinnungssystem |
WO2017023686A1 (en) * | 2015-08-05 | 2017-02-09 | Borgwarner Inc. | Turbocharger assist system using organic rankine cycle fluid energy |
US10132233B2 (en) * | 2015-10-29 | 2018-11-20 | Superturbo Technologies, Inc. | Compressor map based driven turbocharger control system |
GB2552482A (en) * | 2016-07-25 | 2018-01-31 | Jaguar Land Rover Ltd | Direct injection of gas into a turbine volute |
DE102016010642B4 (de) | 2016-09-02 | 2018-11-15 | Adolf Gudermann | Antriebsvorrichtung mit Verbrennungsmotor und Fahrzeug enthaltend die Antriebsvorrichtung |
CN106194402B (zh) * | 2016-09-19 | 2018-08-31 | 吉林大学 | 一种蓄热式复合涡轮增压装置 |
GB2561837A (en) * | 2017-04-24 | 2018-10-31 | Hieta Tech Limited | Turbine rotor, turbine, apparatus and method |
US11156152B2 (en) | 2018-02-27 | 2021-10-26 | Borgwarner Inc. | Waste heat recovery system with nozzle block including geometrically different nozzles and turbine expander for the same |
US10378408B1 (en) * | 2018-03-26 | 2019-08-13 | Caterpillar Inc. | Ammonia generation and storage systems and methods |
EP3546709A1 (de) * | 2018-03-29 | 2019-10-02 | Volvo Car Corporation | Fahrzeug mit system zur rückgewinnung von abwärme |
CN111120066A (zh) * | 2018-11-01 | 2020-05-08 | 上海汽车集团股份有限公司 | 车辆及其发动机冷却系统 |
UA141780U (uk) * | 2019-10-21 | 2020-04-27 | Іван Іванович Котурбач | Дизель-парова електростанція |
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2010
- 2010-09-21 CN CN2010800448037A patent/CN102656348A/zh active Pending
- 2010-09-21 WO PCT/EP2010/063880 patent/WO2011042297A1/de active Application Filing
- 2010-09-21 EP EP10760974A patent/EP2486257A1/de not_active Withdrawn
- 2010-09-21 US US13/499,865 patent/US20120260654A1/en not_active Abandoned
- 2010-09-21 BR BR112012007994A patent/BR112012007994A2/pt not_active IP Right Cessation
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Also Published As
Publication number | Publication date |
---|---|
EP2486257A1 (de) | 2012-08-15 |
BR112012007994A2 (pt) | 2017-07-25 |
US20120260654A1 (en) | 2012-10-18 |
DE102009045380A1 (de) | 2011-04-07 |
CN102656348A (zh) | 2012-09-05 |
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