Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B41/00—Engines characterised by special means for improving conversion of heat or pressure energy into mechanical power
  • F02B41/02—Engines with prolonged expansion
  • F02B41/10—Engines with prolonged expansion in exhaust turbines
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
  • F02B37/004—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust drives arranged in series
• • 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
  • F02B37/013—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in series
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
  • F02B37/04—Engines with exhaust drive and other drive of pumps, e.g. with exhaust-driven pump and mechanically-driven second pump
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
  • F02B37/12—Control of the pumps
  • F02B37/18—Control of the pumps by bypassing exhaust from the inlet to the outlet of turbine or to the atmosphere
• • 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
  • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
  • F02B29/04—Cooling of air intake supply
  • F02B29/0406—Layout of the intake air cooling or coolant circuit
  • F02B29/0425—Air cooled heat exchangers
• • 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
  • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
  • F02B29/04—Cooling of air intake supply
  • F02B29/045—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly
  • F02B29/0475—Constructional details of the heat exchangers, e.g. pipes, plates, ribs, insulation, materials, or manufacturing and assembly the intake air cooler being combined with another device, e.g. heater, valve, compressor, filter or EGR cooler, or being assembled on a special engine location
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
  • F02M26/02—EGR systems specially adapted for supercharged engines
  • F02M26/08—EGR systems specially adapted for supercharged engines for engines having two or more intake charge compressors or exhaust gas turbines, e.g. a turbocharger combined with an additional compressor
• • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
  • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
  • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
  • Y02T10/00—Road transport of goods or passengers
  • Y02T10/10—Internal combustion engine [ICE] based vehicles
  • Y02T10/12—Improving ICE efficiencies

Definitions

• the present invention relates to a drive train, in particular
• Motor vehicle drive train with a supercharged internal combustion engine and a turbocompound system, as for example for driving a
• truck or rail vehicle is used.
• the invention is also applicable to other powertrains, such as stationary drive trains, or other vehicles, such as passenger cars.
• a turbine is arranged in the ⁇ bgasstrom of the internal combustion engine, which is usually designed as a piston engine, such as diesel engine, and is offset by the exhaust gas flow in a rotational movement, which drives a compressor which supplied to the engine
• turbocharger Fresh air or a fresh air mixture compressed.
• the combination of turbine and compressor is referred to as a turbocharger, with the turbine and compressor typically being mounted on a common shaft, turbocharger shaft.
• the turbine as turbocharger turbine and the compressor as
• turbocompound system likewise comprises a turbine acted upon and driven by the exhaust gas, in the present case referred to as a useful turbine, which converts thermal energy and flow energy of the exhaust gas into mechanical energy or drive power.
• drive power is not supplied to a compressor, but the same drive train in which the internal combustion engine its drive power
• the exhaust gas turbine is thus at least indirectly in one
• European Patent EP 0 091 139 B2 describes the combination of a turbocharger and a turbo compound system. According to a first
• the turbine of the turbocharger is arranged in the exhaust stream parallel to the exhaust gas turbine. According to a second embodiment, the exhaust gas first flows through the turbine of the turbocharger and then the
• Exhaust gas turbine of the turbo compound system In a parallel circuit of the turbines, the turbine surface is divided, namely accounts for 70% of the area on the turbine of the turbocharger and 10% on the exhaust gas turbine. Accordingly, the exhaust gas turbine is a very small and fast-rotating turbine. In the case of series connection, the supercharger turbine is designed for a turbine cross section of 80%. In the downstream turbine, the residual gradient in
• the utility turbine is thus voluminous and expensive and is usually applied to smaller engines. It is advantageous that the transmission between the power turbine and the internal combustion engine compared to the high-speed parallel turbine can be made cheaper.
• the present invention has for its object to provide a drive train, which is improved in terms of the requirements mentioned. At the same time, the drive train should be as inexpensive to produce and work reliably.
• the object of the invention is achieved by a drive train with the
• the drive train according to the invention has a charged
• Internal combustion engine such as diesel engine or other piston engine
• the drive power is, for example, in stationary vehicles or in a vehicle to drive an aggregate, in particular one
• Working machine or a generator used, or in vehicles drive wheels are driven by means of the drive power of the internal combustion engine.
• the engine alone or in combination with other engines contributes to the traction of the vehicle.
• a turbocharger comprising a plurality of turbocharger turbines in the exhaust gas flow of the internal combustion engine and turbocharger compressors in a fresh air flow supplied to the internal combustion engine.
• turbocharger compressors in a fresh air flow supplied to the internal combustion engine.
• fresh air flow is both a pure fresh air flow to understand that after its compression by means of the turbocharger compressor fuel and in particular a certain proportion of exhaust gas is supplied, or a fresh air flow mixture, which already contains next to the fresh air other components, such as fuel and / or exhaust gas.
• turbocharger turbine and the turbocharger compressor each stage of the turbocharger are advantageous in a purely mechanical drive connection with each other and can be arranged, for example, rotatably on a common shaft or carried by this.
• the drive train according to the invention also has a turbocompound system, comprising an exhaust gas turbine, which in the exhaust gas flow of the internal combustion engine is arranged, for example, in the flow direction behind the first
• Turbocharger turbine of turbocharger The exhaust gas turbine is in one
• Under drive connection is doing both an immediate drive connection and an indirect drive connection, for example via an intermediate gear, for example
• Exhaust gas turbine are transmitted and which, if it is emptied, allows to interrupt the drive connection between the exhaust gas turbine and the output shaft of the internal combustion engine.
• the exhaust gas turbine of the turbocompound system is parallel to the second turbocharger turbine, that is to the low pressure turbine of the
• Turbocharger arranged in the exhaust stream of the internal combustion engine. This means that the exhaust gas stream of the internal combustion engine is subdivided into at least two partial exhaust gas streams, in particular by means of a controllable exhaust gas distributor, and in the first partial exhaust gas stream the exhaust gas turbine flows through the exhaust gas
• the turbocharger turbine is arranged, and in the second partial exhaust stream, the turbocharger turbine is arranged through the exhaust gas.
• Under controllable exhaust gas flow distributor is any suitable device to understand, which can vary the allocation of the exhaust gas flow to the at least two partial exhaust gas streams selectively and selectively. So not only
• Applicable exhaust gas flow distributors which operate in a closed loop, but also controllable exhaust gas flow distributors, which are controlled in an open loop or with a simple control.
• a desired value for the proportion of the exhaust gas in the respective partial exhaust gas flow both a volume flow and a mass flow can be specified.
• Others too Specifications such as a valve position or an opening cross-section of the exhaust pipe are possible to the division of the
• Exhaust aftertreatment system in the flow direction of the exhaust gas downstream of the exhaust gas turbine and / or the parallel turbocharger turbine is the
• Exhaust gas flow manifold advantageously designed such that in addition to the first two exhaust gas streams with the exhaust gas turbine and turbocharger turbine, a third exhaust partial flow is provided parallel to the first two exhaust gas streams, by means of which exhaust gas can be passed both to the exhaust gas turbine and to the turbocharger turbine arranged parallel thereto. If, according to one embodiment, all or different partial exhaust gas streams in the flow direction behind the exhaust gas turbines - waste gas utilization turbine and turbocharger turbine (s) - are brought together again to form a common exhaust gas flow, then
• the turbocharger is designed in two stages and includes only the first turbocharger turbine and the second turbocharger turbine.
• the first turbocharger turbine drives a first turbocharger compressor in the fresh air flow
• the second turbocharger turbine drives a second turbocharger compressor in the fresh air flow.
• the two turbocharger turbines with their associated turbocharger compressors in a purely mechanical drive connection with each other and are particularly advantageous rotationally fixed driven or carried by a common shaft.
• the first turbocharger turbine is disposed in the exhaust stream upstream of the second turbocharger turbine.
• the first turbocharger compressor is in the fresh air flow downstream of the second Turbocharger compressor arranged.
• Turbocharger compressor as high pressure compressor and the second
• Turbocharger compressor as low-pressure compressor, as well as the first turbocharger turbine as a high-pressure turbine and the second turbocharger turbine as a low-pressure turbine.
• a third stage is further provided. Even more levels are possible.
• the exhaust gas turbine is in
• the distribution of the exhaust gas stream into at least two partial exhaust gas streams is advantageously carried out in
• the last turbocharger turbine is arranged parallel to the exhaust gas turbine in the exhaust gas flow, or at three or more stages is a predetermined plurality of in
• the exhaust gas recirculation can be a
• Exhaust gas recirculation line comprise downstream of the exhaust gas flow distributor, in particular in the flow direction in front of the exhaust gas turbine and the
• Parallel turbocharger turbine branches off the exhaust pipe.
• the diversion of an exhaust gas recirculation line may be provided upstream of the exhaust gas flow distributor, in particular in the flow direction of the exhaust gas upstream of a first turbocharger turbine.
• the mouth of one or a plurality of exhaust gas recirculation line (s) is advantageously according to the
• control device in particular electronic control device is provided which controlling and / or regulating on the
• Exhaust gas flow distributor accesses to the division of the exhaust gas flow to the various A. to vary partial gas flows.
• the division can, for example, in dependence on the speed of the output shaft of the internal combustion engine or a dependent therefrom speed, for example, a speed in a the
• a corresponding speed sensor may be provided, which detects this speed and is connected to the control device to the measurement result of
• control device may operate such that at least one of
• This control or regulation may be superimposed on a further control, which, if necessary, a relatively larger proportion of the exhaust gas stream passing two parallel exhaust gas turbines past into an exhaust aftertreatment system.
• This superimposed regulation or control can then take place, for example, independently of the detected or calculated rotational speeds or other relevant variables for distribution control.
• a bypass is connected in parallel with the at least one turbocharger turbine arranged upstream of the exhaust gas flow distributor in the exhaust gas flow in order to bypass exhaust gas at this turbocharger turbine and supply it to the exhaust gas distributor and / or at least one partial exhaust gas stream downstream of the exhaust gas distributor.
• Compressor stages or the individual turbocharger compressor to deal with a common or each with its own bypass.
• Figure 1 shows a first embodiment of an inventive
• Figure 2 shows a second embodiment of an inventive
• the internal combustion engine is designated by the reference numeral 1, the turbocharger by the reference numeral 2 and the turbocompound system by the reference numeral 3.
• the internal combustion engine 1 has an output shaft 1.1, which in a drive connection with not shown drive wheels and / or by means of the internal combustion engine 1 to be driven unit and also in a drive connection with the exhaust gas turbine 3.1 of the turbocompound system 3 is.
• Output shaft 1.1 are various mechanical gear ratio stages and a hydrodynamic coupling, which is designed to be adjustable here, arranged.
• the control of the hydrodynamic coupling 10 can by
• the exhaust gas turbine 3.1 is in the exhaust stream 5 parallel to a second
• Turbocharger turbine 2.3 of the turbocharger 2 arranged.
• the second turbocharger turbine 2.3 drives a second turbocharger compressor 2.4.
• In the fresh air stream 4 downstream of the second turbocharger compressor 2.4 is a first
• Turbocharger compressor 2.2 arranged by means of a first turbocharger turbine 2.1 is driven.
• the first turbocharger turbine 2.1 is arranged in the exhaust gas flow 5 upstream of the second turbocharger turbine 2.3 and thus also downstream of the exhaust gas utilization turbine 3.1 of the turbocompound system 3.
• Exhaust gas stream 5 is divided downstream of the first turbocharger turbine 2.1 by means of an exhaust gas flow distributor 6 into three partial exhaust gas streams 5.1, 5.2 and 5.3.
• the exhaust gas turbine 3.1 is arranged, in the second partial exhaust stream 5.2, the second turbocharger turbine 2.3 is arranged, and the third partial exhaust stream 5.3 is free of any exhaust gas turbine.
• variable distribution of the exhaust stream 5 to the various partial exhaust streams 5.1, 5.2, 5.3 by means of the exhaust manifold 6 can be directed at high charge air demand, the exhaust stream 5 for the most part to the second turbocharger turbine 2.3, whereas, especially at higher engine speeds at which more exhaust energy is available ,
• the mass flow or volume flow of the exhaust gas is relatively stronger or completely directed to the exhaust gas turbine 3.1.
• Exhaust manifold 6 can be supplied.
• the compressed fresh air stream 4 is in this case passed through a charge air cooler 12 before it is supplied to the internal combustion engine 1.
• a charge air cooler 12 instead of the single intercooler 12 provided, it would also be possible to provide a plurality of charge air coolers, for example in individual or all recirculated exhaust gas partial streams.
• the intercooler 12 is part of a cooling system, in particular vehicle cooling system, comprising in addition to the
• Intercooler 12 a cooling water cooler 13, which together with the
• Charge air cooler 12 flows through or is flowed around by ambient air.
• Turbocharger compressor 2.2 and / or the second turbocharger compressor 2.4 can be bypassed partially or completely. Instead of the two bypasses 14, 15 provided separately, one by-pass per
• Turbocharger compressor could also be provided a common bypass.
• Fresh air stream 4 can be passed.
• a line 7.1 branches upstream of the
• Abgasstromverteilers 6 from the exhaust stream 5 from, in this case upstream of the first turbocharger turbine 2.1.
• the lines 7.2, 7.3 and 7.4 downstream of the exhaust gas flow distributor 6 open downstream of the second turbocharger compressor 2.4 and upstream of the first turbocharger compressor 2.2 in the fresh air flow 4.
• the first line 7.1 opens downstream of the turbocharger compressor 2.4, 2.2 in the fresh air flow. 4
• Control device 8 shown schematically, the division of the
• Exhaust stream 5 to the various partial exhaust streams 5.1, 5.2, 5.3 by means of Exhaust gas flow distributor 6 controls and / or regulates.
• the control device 8 is connected to a rotational speed sensor 9, which detects the rotational speed of the output shaft 1.1 of the internal combustion engine 1. The measurement result is used to determine which portion of the exhaust gas stream 5 is supplied to which partial exhaust gas stream 5.1, 5.2 and 5.3.
• a rotational speed sensor 9 which detects the rotational speed of the output shaft 1.1 of the internal combustion engine 1.
• the measurement result is used to determine which portion of the exhaust gas stream 5 is supplied to which partial exhaust gas stream 5.1, 5.2 and 5.3.
• Combustion engine can be optimally controlled. At the same time, adjustments can be made with regard to the exhaust gas temperature for exhaust gas aftertreatment.

Landscapes

• Engineering & Computer Science (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Supercharger (AREA)

Priority Applications (4)

Applications Claiming Priority (2)

Publications (1)

Family

ID=45974226

Family Applications (1)

Country Status (6)

Cited By (7)

Families Citing this family (10)

Citations (5)

Family Cites Families (2)

• 2011
  • 2011-02-17 DE DE102011011637A patent/DE102011011637A1/de not_active Withdrawn
• 2012
  • 2012-02-10 CN CN2012800043082A patent/CN103282620A/zh active Pending
  • 2012-02-10 BR BR112013018407A patent/BR112013018407A2/pt not_active Application Discontinuation
  • 2012-02-10 JP JP2013553832A patent/JP2014506651A/ja active Pending
  • 2012-02-10 EP EP12714555.5A patent/EP2676018A1/de not_active Withdrawn
  • 2012-02-10 WO PCT/EP2012/000602 patent/WO2012110217A1/de active Application Filing

Patent Citations (5)

Also Published As

Similar Documents

Legal Events