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EP1899595B1 - Device for recycling and cooling exhaust gas for an internal combustion engine - Google Patents

Device for recycling and cooling exhaust gas for an internal combustion engine Download PDF

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Publication number
EP1899595B1
EP1899595B1 EP06762098.9A EP06762098A EP1899595B1 EP 1899595 B1 EP1899595 B1 EP 1899595B1 EP 06762098 A EP06762098 A EP 06762098A EP 1899595 B1 EP1899595 B1 EP 1899595B1
Authority
EP
European Patent Office
Prior art keywords
exhaust
exhaust gas
valve
cooling
gas
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP06762098.9A
Other languages
German (de)
French (fr)
Other versions
EP1899595A1 (en
Inventor
Jochen Eitel
Markus Flik
Peter Geskes
Thomas Heckenberger
Dieter Heinle
Jens Ruckwied
Andreas Thumm
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mahle Behr GmbH and Co KG
Original Assignee
Behr GmbH and Co KG
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Filing date
Publication date
Application filed by Behr GmbH and Co KG filed Critical Behr GmbH and Co KG
Publication of EP1899595A1 publication Critical patent/EP1899595A1/en
Application granted granted Critical
Publication of EP1899595B1 publication Critical patent/EP1899595B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/24—Layout, e.g. schematics with two or more coolers
    • 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
    • F02M26/04—EGR systems specially adapted for supercharged engines with a single turbocharger
    • F02M26/06—Low pressure loops, i.e. wherein recirculated exhaust gas is taken out from the exhaust downstream of the turbocharger turbine and reintroduced into the intake system upstream of the compressor
    • 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
    • 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
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/25—Layout, e.g. schematics with coolers having bypasses
    • 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
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/23—Layout, e.g. schematics
    • F02M26/28—Layout, e.g. schematics with liquid-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
    • F02B29/0406—Layout of the intake air cooling or coolant circuit
    • F02B29/0412—Multiple heat exchangers arranged in parallel or in series
    • 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
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/14—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the exhaust system
    • F02M26/15—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the exhaust system in relation to engine exhaust purifying apparatus
    • 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
    • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
    • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
    • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
    • F02M26/30—Connections of coolers to other devices, e.g. to valves, heaters, compressors or filters; Coolers characterised by their location on the engine

Definitions

  • the invention relates to a device for returning and cooling exhaust gas of an internal combustion engine ( JP 11 200 955 ).
  • the exhaust gas recirculation (abbreviation: EGR), in particular the cooled exhaust gas recirculation is used in today's vehicles due to legal regulations, in order to reduce the particle and pollutant, in particular nitrogen oxide emissions.
  • EGR exhaust gas recirculation
  • the known EGR system has an exhaust gas turbocharger for a diesel engine and an EGR line with an EGR valve, which is arranged between the engine and the exhaust gas turbine.
  • the recirculated exhaust gas is preferably cooled in two stages, ie in two exhaust gas heat exchangers, which are each cooled by a separate coolant circuit and designed as a high-temperature and low-temperature exhaust gas cooler are.
  • the cooled, recirculated exhaust gas is combined with compressed and cooled charge air and fed to the intake manifold of the engine.
  • Exhaust heat exchangers in particular exhaust gas cooler are known in various embodiments:
  • the applicant has been known a welded construction for an exhaust gas heat exchanger, which consists of a bundle of exhaust pipes, which are surrounded on its outside by coolant, which is taken from the cooling circuit of the internal combustion engine.
  • Exhaust heat exchangers are often also equipped with a bypass duct for the exhaust gas, ie in the event that cooling of the exhaust gas or - for heating purposes - a heating of the coolant is not required or not advantageous.
  • a bypass duct for the exhaust gas, ie in the event that cooling of the exhaust gas or - for heating purposes - a heating of the coolant is not required or not advantageous.
  • the applicant and in the DE 102 03 003 A1 are such exhaust gas heat exchanger disclosed with an integrated bypass, wherein in an inlet diffuser or in the outlet region of the Abgas139übertragers a bypass valve, preferably in the form of a bypass valve is arranged, which acts as a switch for the exhaust gas flow and passes either through the bypassed by coolant tube bundle or through the bypass channel ,
  • the bypass duct for the exhaust gas heat exchanger can also be arranged separately, ie outside the heat exchanger.
  • the EGR valve is disposed in the return of the EGR passage, that is, downstream of the exhaust gas cooler in the exhaust gas flow direction.
  • a device for exhaust gas recirculation with a valve device in which a bypass channel is integrated with a bypass valve.
  • the exhaust gas heat exchanger has a bundle of U-shaped exhaust pipes, which are cooled by a liquid coolant.
  • the integration of a first and a second exhaust gas heat exchanger to a structural unit or a module is provided.
  • the two exhaust gas heat exchangers are preferably designed as high-temperature and low-temperature exhaust gas coolers, which are each cooled by a separate cooling circuit, by the coolant circuit of the internal combustion engine and by a low-temperature cooling circuit.
  • Both heat exchangers are mechanically or cohesively, ie connected by screwing, welding or soldering together to form a structural unit.
  • the advantage here is that such a module can be produced in a manufacturing process and mounted as a unit in the vehicle, which also eliminates the need to install intermediate cables. This reduces the costs.
  • a further advantage is a reduction of the installation space, since the components of the module are arranged compact and without intermediate lines.
  • the cooling of the exhaust gas is not limited to liquid cooling, air cooling or liquid and air cooling are also possible.
  • the two exhaust gas cooler on a bypass channel, which may be either integrated or arranged separately.
  • the bypass channel is assigned a bypass valve, which is arranged on the inlet or outlet side of the exhaust gas cooler.
  • the EGR valve is integrated into the module, wherein here also an arrangement on the exhaust gas inlet or exhaust gas outlet side is possible.
  • the EGR valve can either be designed as a pure shut-off valve or according to the invention as a flow control valve, as a three-way valve to regulate the recirculated mass flow.
  • the high-temperature radiator on an inlet diffuser in which a particulate filter and / or an oxidation catalyst is arranged, which is particularly advantageous for the exhaust gas purification of diesel engines and prevents soot in the exhaust pipes of the radiator.
  • the exhaust gas is cooled in the first or second radiator with air, wherein the respective other cooling stage is cooled with coolant.
  • Fig. 1a shows an exhaust gas recirculation (EGR) system for a supercharged, designed as a diesel engine internal combustion engine 1 of a motor vehicle, not shown.
  • the diesel engine 1 has an intake pipe 2 and an exhaust pipe 3, wherein in the exhaust pipe 3, an exhaust gas turbine 4 and in the intake 2 a driven by the exhaust turbine 4 compressor 5 (so-called exhaust gas turbocharger) are arranged.
  • a charge air cooler 6 is arranged, which, which is not shown, is cooled by a liquid coolant or by air.
  • a particulate filter and an oxidation catalyst represented by a rectangle 7, are arranged downstream of the exhaust gas turbine 4, a particulate filter and an oxidation catalyst, represented by a rectangle 7, are arranged.
  • the portion 3a of the exhaust pipe 3 located downstream of the exhaust gas turbine 4 and the portion 2a of the upstream pipe 2 located upstream of the compressor 5 are referred to as the low pressure side.
  • an exhaust gas recirculation line (EGR line) 8 and an exhaust gas cooler 9 are arranged, which is connectable via two nozzles 9a, 9b to a not shown coolant circuit of the engine 1.
  • the function of the illustrated EGR system is as follows: Fresh air is sucked in via the low-pressure section 2 a, brought from the compressor 5 to an elevated pressure, the boost pressure, fed to the charge air cooler 6 via the intake line 2, cooled there to increase the delivery rate and the engine 1 fed.
  • the exhaust gases leaving the engine drive the exhaust gas turbine 4, which in turn drives the compressor 5.
  • Behind the exhaust gas turbine 4, the diesel exhaust gases are cleaned by the particulate filter and the oxidation catalyst 7.
  • a partial flow is branched off via the EGR line 8, cooled in the exhaust gas cooler 9 and fed to the low-pressure section 2 a, where mixing of the recirculated exhaust gases with the intake fresh air takes place.
  • the performance or the Pressure difference at the compressor 5 is thus decisive for the exhaust gas recirculated via the exhaust gas cooler 9 (mass flow) and thus can be considerably increased, based on a known EGR system on the high pressure side, where only the pressure difference between the engine exhaust side and engine intake side is available for the flow ,
  • Fig. 1b shows an exhaust gas recirculation system (EGR system) as shown in Fig. 1a is described.
  • EGR system exhaust gas recirculation system
  • the tubing (4) is designed as a two-stage turbine system and the compressor (5) as a two-stage compression system with intermediate cooling.
  • the function of the illustrated EGR system is as follows: Fresh air is drawn in via the low-pressure section 2 a, brought from the first compressor stage 5 a to a higher pressure, the intermediate pressure and fed via an intermediate pressure section 2 b to an intermediate heat exchanger 25.
  • the intermediate heat exchanger the exhaust gas / air mixture is cooled to limit the temperature and then in a second compressor stage 5b increased to the intermediate pressure, the boost pressure, fed via the intake 2 to the intercooler 6, cooled there to increase the degree of delivery and the engine 1 supplied.
  • the exhaust gases leaving the engine drive a first exhaust gas turbine 4a, which in turn drives the second compressor stage 5b.
  • the expanded exhaust gas is fed to a second exhaust gas turbine 4b, which in turn drives the first compressor stage 5a.
  • the diesel exhaust gases are cleaned by the particulate filter and the oxidation catalyst 7.
  • a partial flow is branched off via the EGR line 8, cooled in the exhaust gas cooler 9 and fed to the low-pressure section 2 a, where mixing of the recirculated exhaust gases with the intake fresh air takes place.
  • Fig. 2a shows a further embodiment of the invention, ie an EGR system on the low pressure side of the engine 1 - for like parts, the same reference numerals as in Fig. 1a used.
  • the EGR system according to Fig. 2a corresponds on the high pressure side of the Fig. 1a ; on the low pressure side, ie between the line sections 2a, 3a is also a EGR line 8 is provided, which leads to a module 10, ie a constructed of different components assembly comprising primarily two exhaust side connected exhaust gas cooler 11, 12, the mechanical, ie, for example, by screwing or cohesively, ie by soldering or welding connected to each other.
  • the exhaust side upstream exhaust gas cooler 11 is formed as a high-temperature radiator and connected to the cooling circuit of the engine 1, not shown.
  • the exhaust side downstream cooler 12 is designed as a low-temperature cooler and connected to a low-temperature cooling circuit, not shown.
  • Upstream of the high-temperature cooler 11, a valve device 13 with a bypass flap 14 and a bypass line 15 bypassing the exhaust gas coolers 11, 12 is provided.
  • the latter can be integrated in the exhaust gas cooler 11, 12 or formed as a separate line.
  • the valve device 13 with bypass flap 14 can - contrary to the graphic representation - also downstream of the exhaust gas cooler 11, 12 may be arranged.
  • an EGR valve 16 designed as a shut-off valve is provided, which is likewise integrated into the module 10, ie connected to the remaining parts to form a structural unit.
  • a particulate filter and / or an oxidation catalytic converter 17, which is likewise structurally integrated, can be provided in an inlet diffuser, not shown, of the exhaust gas cooler 11, that is to say of the high-temperature radiator.
  • the module 10 is used in the assembly in the EGR line 8, the exhaust gas cooler 11, 12 are connected to the respective cooling circuits, and the valve device 13 and the control valve 16 are connected to control devices, not shown.
  • the attachment of the module 10 may take place at a suitable location in the motor vehicle.
  • the function of the illustrated EGR system is similar to Fig. 1a , initially with the difference that here is a two-stage cooling of the recirculated via the EGR line 8 exhaust stream. If no cooling is required or advantageous, both exhaust gas cooler 11, 12 by the bypass line 15 are bypassed.
  • the amount of the recirculated exhaust gas 8 is controlled by the shut-off valve 16, wherein in the simplest cases, a black-and-white control (open or close) is sufficient.
  • the particulate filter 17, which is provided in addition to the particulate filter 7 in the exhaust pipe 3a, prevents soot from accumulating in the exhaust pipes, not shown, of the two exhaust coolers 11, 12.
  • the exhaust gas cooler module 10 on the low pressure side (2a, 3a) is arranged, is also here an arbitrarily high pressure difference for the promotion of the exhaust gas flow to the compressor 5 is available, which is due to the large number of components in the EGR line 8 and high exhaust gas mass flows of advantage.
  • FIG. 2b shows a further embodiment of the invention, ie an EGR system on the low pressure side of the engine 1 - for like parts, the same reference numerals as in Fig. 1b and 2a used.
  • the tubing (4) is designed as a two-stage turbine system and the compressor (5) as a two-stage compression system with intermediate cooling, as in Fig. 1b is described.
  • FIG. 2c shows a further embodiment of the invention, ie an EGR system on the low pressure side of the engine 1 - for like parts, the same reference numerals as in Fig. 2a used.
  • Fig. 2a is formed as a shut-off valve EGR valve 16, which is also integrated into the module 10, that is connected to the other parts to form a unit, downstream of the exhaust gas cooler 11, 12 and the junction point of the bypass channel 15 is arranged.
  • Figure 2d shows a further embodiment of the invention, ie an EGR system on the low pressure side of the engine 1 - for like parts, the same reference numerals as in Fig. 2a and 2c used.
  • the tubing (4) is designed as a two-stage turbine system and the compressor (5) as a two-stage compression system with intermediate cooling; like this in Fig. 1b is described.
  • Fig. 3a shows a further embodiment of the invention for an EGR system on the low pressure side of the engine 1, again with like reference numerals be used for the same parts.
  • an exhaust gas recirculation guide 8 is arranged, which is largely integrated in a module 18.
  • the module 18, like the module 10 in FIG Fig. 2a also the exhaust gas cooler 11, 12, the valve device 13 with bypass valve 14 and bypass channel 15, and further includes the particulate filter and / or the oxidation catalyst 17.
  • Deviating from the embodiment according to Fig. 2 is a designed as a three-way valve flow control valve 19 (EGR valve), which is arranged at the branch point of the exhaust pipe 3a and EGR pipe 8.
  • EGR valve three-way valve flow control valve
  • the control valve 19 Through the control valve 19, the proportion of exhaust gas, which is taken from the total exhaust gas flow can be adjusted. As a result, a more accurate control of the recirculated exhaust gas mass flow is possible.
  • the functions of the module 18 are equal to the module 10 in FIG Fig. 2a ,
  • Fig. 3b shows a further embodiment of the invention for an EGR system on the low pressure side of the engine 1, again with the same reference numerals for the same parts as in Fig. 3a be used.
  • the tubing (4) is designed as a two-stage turbine system and the compressor (5) as a two-stage compression system with intermediate cooling, as in Fig. 1b is described.
  • Fig. 4a shows a further embodiment of the invention for an EGR system on the low pressure side of the engine 1, again using like reference numerals for the same.
  • the EGR valve 19, the valve device 13 and the bypass flap 14 are combined to form a structural unit, which form a multi-function valve 26.
  • Fig. 4b shows a further embodiment of the invention for an EGR system on the low pressure side of the engine 1, again using like reference numerals for the same.
  • tubing (4) is designed as a two-stage turbine system and the compressor (5) as a two-stage compression system with intermediate cooling, as in Fig. 1b is described.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust-Gas Circulating Devices (AREA)

Description

Die Erfindung betrifft eine Vorrichtung zur Rückführung und Kühlung von Abgas einer Brennkraftmaschine ( JP 11 200 955 ).The invention relates to a device for returning and cooling exhaust gas of an internal combustion engine ( JP 11 200 955 ).

Die Abgasrückführung (Abkürzung: AGR), insbesondere die gekühlte Abgasrückführung wird in heutigen Fahrzeugen aufgrund gesetzlicher Bestimmungen eingesetzt, um die Partikel- und Schadstoff-, insbesondere Stickoxidemissionen zu senken. Da die Anforderungen an die Abgasreinhaltung strenger werden, sind größere Abgasmassenströme erforderlich, die mit den bekannten AGR-Systemen nur bedingt zu beherrschen sind.The exhaust gas recirculation (abbreviation: EGR), in particular the cooled exhaust gas recirculation is used in today's vehicles due to legal regulations, in order to reduce the particle and pollutant, in particular nitrogen oxide emissions. As the requirements for exhaust gas purification become stricter, larger exhaust gas mass flows are required, which can only be controlled to a limited extent with the known EGR systems.

Bekannte AGR-Systeme sind auf der Hochdruckseite des Verbrennungsmotors angeordnet, wie in der US 6,244,256 B1 beschrieben. Das bekannte AGR-System weist einen Abgasturbolader für einen Dieselmotor und eine AGR-Leitung mit einem AGR-Ventil auf, welches zwischen Motor und Abgasturbine angeordnet ist. Das rückgeführte Abgas wird vorzugsweise in zwei Stufen, d. h. in zwei Abgaswärmeübertragem gekühlt, welche jeweils durch einen gesonderten Kühlmittelkreislauf gekühlt werden und als Hochtemperatur- und Niedertemperatur-Abgaskühler ausgebildet sind. Das gekühlte, rückgeführte Abgas wird mit verdichteter und gekühlter Ladeluft zusammengeführt und dem Ansaugtrakt des Motors zugeführt.Known EGR systems are arranged on the high pressure side of the internal combustion engine, as in the US 6,244,256 B1 described. The known EGR system has an exhaust gas turbocharger for a diesel engine and an EGR line with an EGR valve, which is arranged between the engine and the exhaust gas turbine. The recirculated exhaust gas is preferably cooled in two stages, ie in two exhaust gas heat exchangers, which are each cooled by a separate coolant circuit and designed as a high-temperature and low-temperature exhaust gas cooler are. The cooled, recirculated exhaust gas is combined with compressed and cooled charge air and fed to the intake manifold of the engine.

Abgaswärmeübertrager, insbesondere Abgaskühler sind in verschiedenen Ausführungsformen bekannt: Durch die DE 199 07 163 A1 der Anmelderin wurde eine Schweißkonstruktion für einen Abgaswärmeübertrager bekannt, welcher aus einem Bündel von Abgasrohren besteht, die auf ihrer Außenseite von Kühlmittel umströmt werden, welches dem Kühlkreislauf der Brennkraftmaschine entnommen wird.Exhaust heat exchangers, in particular exhaust gas cooler are known in various embodiments: By the DE 199 07 163 A1 The applicant has been known a welded construction for an exhaust gas heat exchanger, which consists of a bundle of exhaust pipes, which are surrounded on its outside by coolant, which is taken from the cooling circuit of the internal combustion engine.

Abgaswärmeübertrager sind vielfach auch mit einem Bypasskanal für das Abgas ausgestattet, d. h. für den Fall, dass eine Kühlung des Abgases oder - bei Heizzwecken - eine Erwärmung des Kühlmittels nicht erforderlich oder nicht vorteilhaft ist. In der DE 199 62 863 A1 der Anmelderin und in der DE 102 03 003 A1 sind derartige Abgaswärmeübertrager mit einem integrierten Bypass offenbart, wobei in einem Eintrittsdiffusor oder im Austrittsbereich des Abgaswärmeübertragers ein Bypassventil, vorzugsweise in Form einer Bypassklappe angeordnet ist, welche als Weiche für den Abgasstrom wirkt und diesen entweder durch das von Kühlmittel umspülte Rohrbündel oder durch den Bypasskanal leitet.Exhaust heat exchangers are often also equipped with a bypass duct for the exhaust gas, ie in the event that cooling of the exhaust gas or - for heating purposes - a heating of the coolant is not required or not advantageous. In the DE 199 62 863 A1 the applicant and in the DE 102 03 003 A1 are such exhaust gas heat exchanger disclosed with an integrated bypass, wherein in an inlet diffuser or in the outlet region of the Abgaswärmeübertragers a bypass valve, preferably in the form of a bypass valve is arranged, which acts as a switch for the exhaust gas flow and passes either through the bypassed by coolant tube bundle or through the bypass channel ,

Wie durch die EP 1 030 050 A1 bekannt, kann der Bypasskanal für den Abgaswärmeübertrager auch separat, d. h. außerhalb des Wärmeübertragers angeordnet sein. Bei diesem bekannten AGR-System ist das AGR-Ventil im Übrigen im Rücklauf der AGR-Leitung, d. h. in Abgasströmungsrichtung hinter dem Abgaskühler angeordnet.How through the EP 1 030 050 A1 As is known, the bypass duct for the exhaust gas heat exchanger can also be arranged separately, ie outside the heat exchanger. Incidentally, in this known EGR system, the EGR valve is disposed in the return of the EGR passage, that is, downstream of the exhaust gas cooler in the exhaust gas flow direction.

Durch die DE 198 41 927 A1 wurde eine Vorrichtung zur Abgasrückführung mit einer Ventileinrichtung bekannt, in welche ein Bypasskanal mit einer Bypassklappe integriert ist. Der Abgaswärmeübertrager weist ein Bündel von U-förmig geformten Abgasrohren auf, welche durch ein flüssiges Kühlmittel gekühlt werden.By the DE 198 41 927 A1 a device for exhaust gas recirculation with a valve device has been known, in which a bypass channel is integrated with a bypass valve. The exhaust gas heat exchanger has a bundle of U-shaped exhaust pipes, which are cooled by a liquid coolant.

Durch die DE 197 50 588 A1 wurde eine Vorrichtung zur Abgasrückführung bekannt, bei welcher ein Abgaswärmeübertrager mit einem Abgasrückführventil (AGR-Ventil) zu einer Baueinheit integriert ist. Damit lässt sich eine vereinfachte und damit verbilligte Herstellung durchführen, da auf einzelne Teile verzichtet werden kann.By the DE 197 50 588 A1 a device for exhaust gas recirculation has been known, in which an exhaust gas heat exchanger with an exhaust gas recirculation valve (EGR valve) is integrated into a structural unit. This makes it possible to carry out a simplified and therefore cheaper production, since it is possible to dispense with individual parts.

Nachteilig bei den bekannten AGR-Systemen ist, dass diese aus einer Vielzahl von Einzelteilen bestehen, die separat gefertigt und einzeln montiert werden, was die Kosten erhöht. Darüber hinaus ist bei den bekannten AGR-Systemen von Nachteil, dass größere Abgasmassenströme nicht rückgeführt werden können, da die Druckdifferenz - aufgrund der Anordnung des AGR-Systems auf der Hochdruckseite des Motors - zwischen Abgas- und Ansaugseite des Motors nicht ausreicht, um größere Massenströme zu fördern.A disadvantage of the known EGR systems that they consist of a variety of items that are manufactured separately and mounted individually, which increases the cost. Moreover, in the known EGR systems of disadvantage that larger exhaust gas mass flows can not be returned, since the pressure difference - due to the arrangement of the EGR system on the high pressure side of the engine - between the exhaust and suction of the engine is not sufficient to larger mass flows to promote.

Es ist eine Aufgabe der vorliegenden Erfindung, eine Vorrichtung zur Abgasrückführung der eingangs genannten Art einfacher und kostengünstiger zu gestalten. Darüber hinaus ist es Aufgabe der Erfindung, eine Anordnung zur Abgasrückführung zu schaffen, welche die Rückführung und Kühlung größerer Abgasmassenströme ermöglicht.It is an object of the present invention to make a device for exhaust gas recirculation of the type mentioned easier and cheaper. In addition, it is an object of the invention to provide an arrangement for exhaust gas recirculation, which allows the return and cooling of larger exhaust gas mass flows.

Diese Aufgabe wird durch die Merkmale des Patentanspruches 1 gelöst. Erfindungsgemäß ist die Integration eines ersten und eines zweiten Abgaswärmeübertragers zu einer Baueinheit bzw. einem Modul vorgesehen. Vorzugsweise sind die beiden Abgaswärmeübertrager als Hochtemperatur- und Niedertemperatur-Abgaskühler ausgebildet, welche jeweils durch einen separaten Kühlkreis gekühlt werden, durch den Kühlmittelkreislauf der Brennkraftmaschine und durch einen Niedertemperaturkühlkreislauf. Beide Wärmeübertrager sind mechanisch oder stoffschlüssig, d. h. durch Verschraubung, Schweißen oder Löten miteinander zu einer Baueinheit verbunden. Vorteilhaft hierbei ist, dass ein solches Modul in einem Fertigungsprozess hergestellt und als Einheit im Fahrzeug montiert werden kann, wobei auch die Montage von Zwischenleitungen entfällt. Dies reduziert die Kosten. Vorteilhaft ist ferner eine Reduzierung des Bauraumes, da die Komponenten des Moduls kompakt und ohne Zwischenleitungen angeordnet sind. Die Kühlung des Abgases ist nicht auf eine Flüssigkeitskühlung beschränkt, eine Luftkühlung oder eine Flüssigkeits- und Luftkühlung sind ebenfalls möglich.This object is solved by the features of claim 1. According to the invention, the integration of a first and a second exhaust gas heat exchanger to a structural unit or a module is provided. The two exhaust gas heat exchangers are preferably designed as high-temperature and low-temperature exhaust gas coolers, which are each cooled by a separate cooling circuit, by the coolant circuit of the internal combustion engine and by a low-temperature cooling circuit. Both heat exchangers are mechanically or cohesively, ie connected by screwing, welding or soldering together to form a structural unit. The advantage here is that such a module can be produced in a manufacturing process and mounted as a unit in the vehicle, which also eliminates the need to install intermediate cables. This reduces the costs. A further advantage is a reduction of the installation space, since the components of the module are arranged compact and without intermediate lines. The cooling of the exhaust gas is not limited to liquid cooling, air cooling or liquid and air cooling are also possible.

Gemäß der Erfindung weisen die beiden Abgaskühler einen Bypasskanal auf, der entweder integriert oder separat angeordnet sein kann. Dem Bypasskanal ist ein Bypassventil zugeordnet, welches eintritts- oder austrittsseitig am Abgaskühler angeordnet ist. Auch diese Komponenten, Bypass und Bypassventil, sind somit Bestandteil des erfindungsgemäßen Moduls.According to the invention, the two exhaust gas cooler on a bypass channel, which may be either integrated or arranged separately. The bypass channel is assigned a bypass valve, which is arranged on the inlet or outlet side of the exhaust gas cooler. These components, bypass and bypass valve, are thus part of the module according to the invention.

Gemäß der Erfindung ist auch das AGR-Ventil in das Modul integriert, wobei auch hier eine Anordnung auf der Abgaseintritts- oder Abgasaustrittsseite möglich ist. Das AGR-Ventil kann entweder als reines Absperrventil oder ist erfindungsgemäß als Mengehregelventil, als Drei-Wege-Ventil ausgebildet, um den rückgeführten Massenstrom zu regeln.According to the invention, the EGR valve is integrated into the module, wherein here also an arrangement on the exhaust gas inlet or exhaust gas outlet side is possible. The EGR valve can either be designed as a pure shut-off valve or according to the invention as a flow control valve, as a three-way valve to regulate the recirculated mass flow.

In weiterer vorteilhafter Ausgestaltung der Erfindung weist der Hochtemperaturkühler einen Eintrittsdiffusor auf, in welchem ein Partikelfilter und/oder ein Oxidationskatalysator angeordnet ist, was insbesondere für die Abgasreinigung von Dieselmotoren von Vorteil ist und eine Rußablagerung in den Abgasrohren des Kühlers verhindert. Diese Komponenten werden also auch in das Modul integriert und bedürfen keiner zusätzlichen Montage.In a further advantageous embodiment of the invention, the high-temperature radiator on an inlet diffuser, in which a particulate filter and / or an oxidation catalyst is arranged, which is particularly advantageous for the exhaust gas purification of diesel engines and prevents soot in the exhaust pipes of the radiator. These components are also integrated into the module and require no additional assembly.

In einer weiteren vorteilhaften Ausgestaltung wird das Abgas im ersten oder zweiten Kühler mit Luft gekühlt, wobei die jeweils andere Kühlstufe mit Kühlmittel gekühlt wird.In a further advantageous embodiment, the exhaust gas is cooled in the first or second radiator with air, wherein the respective other cooling stage is cooled with coolant.

Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden im Folgenden näher beschreiben. Es zeigen

Fig. 1a
ein AGR-System mit Abgaskühler auf der Niederruckseite,
Fig. 1b
ein AGR-System mit Abgaskühler auf der Niederruckseite und einem zweistufigen Turbinen-/Verdichtersystem mit Zwischenkühlung,
Fig. 2a
ein AGR-System mit zweistufiger Abgaskühlung und Abgaskühlermodul auf der Niederdruckseite, wobei das AGR-Ventil auf der heißen Abgasseite, d.h. vor der zweistufigen Abgaskühlung angeordnet ist,
Fig. 2b
ein AGR-System mit zweistufiger Abgaskühlung und Abgaskühlermodul auf der Niederdruckseite, wobei das AGR-Ventil auf der heißen Abgasseite, d.h. vor der zweistufigen Abgaskühlung angeordnet ist und das Turbinen-/ Verdichtersystem zweistufig ist sowie über eine Zwischenkühlung verfügt,
Fig. 2c
ein AGR-System mit zweistufiger Abgaskühlung und Abgaskühlermodul auf der Niederdruckseite, wobei das AGR-Ventil auf der kalten Abgasseite, d.h. nach der zweistufigen Abgaskühlung angeordnet ist,
Fig. 2d
ein AGR-System mit zweistufiger Abgaskühlung und Abgaskühlermodul auf der Niederdruckseite, wobei das AGR-Ventil auf der kalten Abgasseite, d.h. nach der zweistufigen Abgaskühlung angeordnet ist und das Turbinen-/ Verdichtersystem zweistufig ist sowie über eine Zwischenkühlung verfügt,
Fig. 3a
ein AGR-System mit Abgaskühlermodul und integriertem AGR-Ventil sowie Partikelfilter und/oder Oxidationskatalysator,
Fig. 3b
ein AGR-System mit Abgaskühlermodul und integriertem AGR-Ventil sowie Partikelfilter und/oder Oxidationskatalysator sowie einem zweistufigen Turbinen-/ Verdichtersystem mit Zwischenkühlung,
Fig. 4a
ein AGR-System mit Abgaskühlermodul und integriertem AGR-Ventil, Bypass-Ventil sowie Partikelfilter und/oder Oxidationskatalysator, wobei das AGR-Ventil und das Bypass-Ventil in einem Multifunktionsventil zu einer Baueinheit zusammengefasst sind und
Fig. 4b
ein AGR-System mit Abgaskühlermodul und integriertem AGR-Ventil, Bypass-Ventil sowie Partikelfilter und/oder Oxidationskatalysator, wobei das AGR-Ventil und das Bypass-Ventil in einem Multifunktionsventil zu einer Baueinheit zusammengefasst sind sowie einem zweistufigen Turbinen-/ Verdichtersystem mit Zwischenkühlung.
Embodiments of the invention are illustrated in the drawings and will be described in more detail below. Show it
Fig. 1a
an EGR system with exhaust gas cooler on the low pressure side,
Fig. 1b
an EGR system with exhaust gas cooler on the low-pressure side and a two-stage turbine / compressor system with intermediate cooling,
Fig. 2a
an EGR system with two-stage exhaust gas cooling and exhaust gas cooler module on the low-pressure side, wherein the EGR valve is arranged on the hot exhaust gas side, ie before the two-stage exhaust gas cooling,
Fig. 2b
an EGR system with two-stage exhaust gas cooling and exhaust gas cooler module on the low-pressure side, wherein the EGR valve is arranged on the hot exhaust side, ie before the two-stage exhaust gas cooling and the turbine / compressor system is two-stage and has an intermediate cooling,
Fig. 2c
an EGR system with two-stage exhaust gas cooling and exhaust gas cooler module on the low-pressure side, wherein the EGR valve is arranged on the cold exhaust gas side, ie after the two-stage exhaust gas cooling,
Fig. 2d
an EGR system with two-stage exhaust gas cooling and exhaust gas cooler module on the low-pressure side, wherein the EGR valve is arranged on the cold exhaust side, ie after the two-stage exhaust gas cooling and the turbine / compressor system is two-stage and has an intermediate cooling,
Fig. 3a
an EGR system with exhaust gas cooler module and integrated EGR valve as well as particulate filter and / or oxidation catalytic converter,
Fig. 3b
an EGR system with exhaust gas cooler module and integrated EGR valve as well as particle filter and / or oxidation catalyst and a two-stage turbine / compressor system with intercooling,
Fig. 4a
an EGR system with exhaust gas cooler module and integrated EGR valve, bypass valve and particulate filter and / or oxidation catalyst, wherein the EGR valve and the bypass valve are combined in a multi-function valve to form a unit and
Fig. 4b
an EGR system with exhaust gas cooler module and integrated EGR valve, bypass valve and particulate filter and / or oxidation catalyst, wherein the EGR valve and the bypass valve are combined in a multi-function valve to form a unit and a two-stage turbine / compressor system with intercooling.

Fig. 1a zeigt ein Abgasrückführsystem (AGR-System) für eine aufgeladene, als Dieselmotor ausgebildete Brennkraftmaschine 1 eines nicht dargestellten Kraftfahrzeuges. Der Dieselmotor 1 weist eine Ansaugleitung 2 und eine Abgasleitung 3 auf, wobei in der Abgasleitung 3 eine Abgasturbine 4 und in der Ansaugleitung 2 ein von der Abgasturbine 4 angetriebener Verdichter 5 (so genannter Abgasturbolader) angeordnet sind. Zwischen Verdichter 5 und dem nicht näher dargestellten Ansaugtrakt des Motors 1 ist ein Ladeluftkühler 6 angeordnet, welcher, was nicht dargestellt ist, durch ein flüssiges Kühlmittel oder durch Luft gekühlt wird. Stromabwärts von der Abgasturbine 4 sind ein Partikelfilter und ein Oxidationskatalysator, dargestellt durch ein Rechteck 7, angeordnet. Der stromabwärts der Abgasturbine 4 befindliche Bereich 3a der Abgasleitung 3 und der stromaufwärts vom Verdichter 5 befindliche Abschnitt 2a der Ansauleitung 2 werden als Niederdruckseite bezeichnet. Zwischen den Leitungsabschnitten 2a, 3a sind eine Abgasrückführleitung (AGR-Leitung) 8 sowie ein Abgaskühler 9 angeordnet, welcher über zwei Stutzen 9a, 9b an einen nicht dargestellten Kühlmittelkreislauf des Motors 1 anschließbar ist. Fig. 1a shows an exhaust gas recirculation (EGR) system for a supercharged, designed as a diesel engine internal combustion engine 1 of a motor vehicle, not shown. The diesel engine 1 has an intake pipe 2 and an exhaust pipe 3, wherein in the exhaust pipe 3, an exhaust gas turbine 4 and in the intake 2 a driven by the exhaust turbine 4 compressor 5 (so-called exhaust gas turbocharger) are arranged. Between the compressor 5 and the intake tract of the engine 1, not shown, a charge air cooler 6 is arranged, which, which is not shown, is cooled by a liquid coolant or by air. Downstream of the exhaust gas turbine 4, a particulate filter and an oxidation catalyst, represented by a rectangle 7, are arranged. The portion 3a of the exhaust pipe 3 located downstream of the exhaust gas turbine 4 and the portion 2a of the upstream pipe 2 located upstream of the compressor 5 are referred to as the low pressure side. Between the line sections 2a, 3a, an exhaust gas recirculation line (EGR line) 8 and an exhaust gas cooler 9 are arranged, which is connectable via two nozzles 9a, 9b to a not shown coolant circuit of the engine 1.

Die Funktion des dargestellten AGR-Systems ist folgende: Frischluft wird über den Niederdruckabschnitt 2a angesaugt, vom Verdichter 5 auf einen erhöhten Druck, den Ladedruck, gebracht, über die Ansaugleitung 2 dem Ladeluftkühler 6 zugeführt, dort zwecks Erhöhung des Liefergrades gekühlt und dem Motor 1 zugeführt. Die den Motor verlassenden Abgase treiben die Abgasturbine 4 an, die ihrerseits den Verdichter 5 antreibt. Hinter der Abgasturbine 4 werden die Dieselabgase durch den Partikelfilter und den Oxidationskatalysator 7 gereinigt. Bevor die Abgase ins Freie treten, wird ein Teilstrom über die AGR-Leitung 8 abgezweigt, im Abgaskühler 9 gekühlt und dem Niederdruckabschnitt 2a zugeführt, wo eine Vermischung der rückgeführten Abgase mit der angesaugten Frischluft erfolgt. Die Leistung bzw. die Druckdifferenz am Verdichter 5 ist somit maßgebend für die über den Abgaskühler 9 rückgeführte Abgasmenge (Massenstrom) und kann somit beträchtlich gesteigert werden, bezogen auf ein bekanntes AGR-System auf der Hochdruckseite, wo nur die Druckdifferenz zwischen Motorabgasseite und Motoransaugseite für den Förderstrom zur Verfügung steht.The function of the illustrated EGR system is as follows: Fresh air is sucked in via the low-pressure section 2 a, brought from the compressor 5 to an elevated pressure, the boost pressure, fed to the charge air cooler 6 via the intake line 2, cooled there to increase the delivery rate and the engine 1 fed. The exhaust gases leaving the engine drive the exhaust gas turbine 4, which in turn drives the compressor 5. Behind the exhaust gas turbine 4, the diesel exhaust gases are cleaned by the particulate filter and the oxidation catalyst 7. Before the exhaust gases enter the atmosphere, a partial flow is branched off via the EGR line 8, cooled in the exhaust gas cooler 9 and fed to the low-pressure section 2 a, where mixing of the recirculated exhaust gases with the intake fresh air takes place. The performance or the Pressure difference at the compressor 5 is thus decisive for the exhaust gas recirculated via the exhaust gas cooler 9 (mass flow) and thus can be considerably increased, based on a known EGR system on the high pressure side, where only the pressure difference between the engine exhaust side and engine intake side is available for the flow ,

Fig. 1b zeigt ein Abgasrückführsystem (AGR-System) wie es in Fig. 1a beschrieben ist. Im Unterschied zu Fig. 1a ist die Tubine (4) als zweistufiges Turbinensystem und der Verdichter (5) als zweistufiges Verdichtungssystem mit Zwischenkühlung ausgeführt. Fig. 1b shows an exhaust gas recirculation system (EGR system) as shown in Fig. 1a is described. In contrast to Fig. 1a the tubing (4) is designed as a two-stage turbine system and the compressor (5) as a two-stage compression system with intermediate cooling.

Die Funktion des dargestellten AGR-Systems ist folgende: Frischluft wird über den Niederdruckabschnitt 2a angesaugt, von der ersten Verdichterstufe 5a auf einen höheren Druck, den Zwischendruck gebracht und über einen Zwischendruckabschnitt 2b einem Zwischenwärmetauscher 25 zugeführt. In dem Zwischenwärmetauscher wird das Abgas-/Luftgemisch zur Temperaturbegrenzung gekühlt und anschließend in einer zweiten Verdichterstufe 5b auf einen gegenüber dem Zwischendruck erhöhten Druck, den Ladedruck, gebracht, über die Ansaugleitung 2 dem Ladeluftkühler 6 zugeführt, dort zwecks Erhöhung des Liefergrades gekühlt und dem Motor 1 zugeführt.The function of the illustrated EGR system is as follows: Fresh air is drawn in via the low-pressure section 2 a, brought from the first compressor stage 5 a to a higher pressure, the intermediate pressure and fed via an intermediate pressure section 2 b to an intermediate heat exchanger 25. In the intermediate heat exchanger, the exhaust gas / air mixture is cooled to limit the temperature and then in a second compressor stage 5b increased to the intermediate pressure, the boost pressure, fed via the intake 2 to the intercooler 6, cooled there to increase the degree of delivery and the engine 1 supplied.

Die den Motor verlassenden Abgase treiben eine erste Abgasturbinen 4a an, die ihrerseits die zweite Verdichterstufe 5b antreibt. Über eine Abgaszwischenleitung 3b wird das entspannte Abgas einer zweiten Abgasturbine 4b zugeführt, die ihrerseits die erste Verdichterstufe 5a antreibt. Hinter der Abgasturbine 4 werden die Dieselabgase durch den Partikelfilter und den Oxidationskatalysator 7 gereinigt. Bevor die Abgase ins Freie treten, wird ein Teilstrom über die AGR-Leitung 8 abgezweigt, im Abgaskühler 9 gekühlt und dem Niederdruckabschnitt 2a zugeführt, wo eine Vermischung der rückgeführten Abgase mit der angesaugten Frischluft erfolgt.The exhaust gases leaving the engine drive a first exhaust gas turbine 4a, which in turn drives the second compressor stage 5b. Via an exhaust gas intermediate line 3b, the expanded exhaust gas is fed to a second exhaust gas turbine 4b, which in turn drives the first compressor stage 5a. Behind the exhaust gas turbine 4, the diesel exhaust gases are cleaned by the particulate filter and the oxidation catalyst 7. Before the exhaust gases enter the atmosphere, a partial flow is branched off via the EGR line 8, cooled in the exhaust gas cooler 9 and fed to the low-pressure section 2 a, where mixing of the recirculated exhaust gases with the intake fresh air takes place.

Fig. 2a zeigt ein weiteres Ausführungsbeispiel der Erfindung, d. h. ein AGR-System auf der Niederdruckseite des Motors 1 - für gleiche Teile werden gleiche Bezugszahlen wie in Fig. 1a verwendet. Das AGR-System gemäß Fig. 2a entspricht auf der Hochdruckseite dem von Fig. 1a; auf der Niederdruckseite, d. h. zwischen den Leitungsabschnitten 2a, 3a ist ebenfalls eine AGR-Leitung 8 vorgesehen, welche zu einem Modul 10 führt, d. h. einer aus verschiedenen Komponenten aufgebauten Baueinheit, welche primär zwei abgasseitig hintereinander geschaltete Abgaskühler 11, 12 umfasst, die mechanisch, d. h. z. B. durch Verschraubung oder stoffschlüssig, d. h. durch Verlöten oder Verschweißen fest miteinander verbunden sind. Der abgasseitig stromaufwärts gelegene Abgaskühler 11 ist als Hochtemperaturkühler ausgebildet und an den nicht dargestellten Kühlkreislauf des Motors 1 angeschlossen. Der abgasseitig stromabwärts gelegene Kühler 12 ist als Niedertemperaturkühler ausgelegt und an einen nicht dargestellten Niedertemperaturkühlkreis angeschlossen. Stromaufwärts vom Hochtemperaturkühler 11 ist eine Ventileinrichtung 13 mit einer Bypassklappe 14 und einer die Abgaskühler 11, 12 umgehenden Bypassleitung 15 vorgesehen. Letztere kann in die Abgaskühler 11, 12 integriert oder als separate Leitung ausgebildet sein. Die Ventileinrichtung 13 mit Bypassklappe 14 kann - entgegen der zeichnerischen Darstellung - auch stromabwärts der Abgaskühler 11, 12 angeordnet sein. Vor der Ventileinrichtung 13, d. h. hier stromaufwärts gelegen, ist ein als Absperrventil ausgebildetes AGR-Ventil 16 vorgesehen, welches ebenfalls in das Modul 10 integriert, d. h. mit den übrigen Teilen zu einer Baueinheit verbunden ist. Schließlich kann in einem nicht dargestellten Eintrittsdiffusor des Abgaskühlers 11, also des Hochtemperaturkühters, ein Partikelfilter und/oder ein Oxidationskatalysator 17 vorgesehen werden, der ebenfalls baulich integriert wird. Somit sind die Komponenten 11, 12, 13, 14, 15, 16, 17 zu einem Modul 10 integriert, welches als eine Einheit herstellbar und lieferbar ist und somit auch als Einheit oder Baugruppe im Fahrzeug mit relativ wenigen Handgriffen montierbar ist. Das Modul 10 wird bei der Montage in die AGR-Leitung 8 eingesetzt, die Abgaskühler 11, 12 werden an die jeweiligen Kühlkreisläufe angeschlossen, und die Ventileinrichtung 13 sowie das Regelventil 16 werden mit nicht dargestellten Steuereinrichtungen verbunden. Die Befestigung des Moduls 10 kann an geeigneter Stelle im Kraftfahrzeug erfolgen. Fig. 2a shows a further embodiment of the invention, ie an EGR system on the low pressure side of the engine 1 - for like parts, the same reference numerals as in Fig. 1a used. The EGR system according to Fig. 2a corresponds on the high pressure side of the Fig. 1a ; on the low pressure side, ie between the line sections 2a, 3a is also a EGR line 8 is provided, which leads to a module 10, ie a constructed of different components assembly comprising primarily two exhaust side connected exhaust gas cooler 11, 12, the mechanical, ie, for example, by screwing or cohesively, ie by soldering or welding connected to each other. The exhaust side upstream exhaust gas cooler 11 is formed as a high-temperature radiator and connected to the cooling circuit of the engine 1, not shown. The exhaust side downstream cooler 12 is designed as a low-temperature cooler and connected to a low-temperature cooling circuit, not shown. Upstream of the high-temperature cooler 11, a valve device 13 with a bypass flap 14 and a bypass line 15 bypassing the exhaust gas coolers 11, 12 is provided. The latter can be integrated in the exhaust gas cooler 11, 12 or formed as a separate line. The valve device 13 with bypass flap 14 can - contrary to the graphic representation - also downstream of the exhaust gas cooler 11, 12 may be arranged. In front of the valve device 13, ie located upstream there, an EGR valve 16 designed as a shut-off valve is provided, which is likewise integrated into the module 10, ie connected to the remaining parts to form a structural unit. Finally, a particulate filter and / or an oxidation catalytic converter 17, which is likewise structurally integrated, can be provided in an inlet diffuser, not shown, of the exhaust gas cooler 11, that is to say of the high-temperature radiator. Thus, the components 11, 12, 13, 14, 15, 16, 17 are integrated into a module 10, which can be manufactured and delivered as a unit and thus can be mounted as a unit or assembly in the vehicle with relatively few handles. The module 10 is used in the assembly in the EGR line 8, the exhaust gas cooler 11, 12 are connected to the respective cooling circuits, and the valve device 13 and the control valve 16 are connected to control devices, not shown. The attachment of the module 10 may take place at a suitable location in the motor vehicle.

Die Funktion des dargestellten AGR-Systems ist ähnlich wie bei Fig. 1a, zunächst mit dem Unterschied, dass hier eine zweistufige Abkühlung des über die AGR-Leitung 8 rückgeführten Abgasstromes erfolgt. Sofern keine Abkühlung erforderlich oder vorteilhaft ist, können beide Abgaskühler 11, 12 durch die Bypassleitung 15 umgangen werden. Die Menge des rückgeführten Abgases 8 wird über das Absperrventil 16 geregelt, wobei in den einfachsten Fällen eine Schwarz-Weiß-Regelung (auf oder zu) ausreichend ist. Der Partikelfilter 17, der zusätzlich zu dem Partikelfilter 7 in der Abgasleitung 3a vorgesehen ist, verhindert eine Rußablagerung in den nicht dargestellten Abgasrohren der beiden Abgaskühler 11, 12. Da das Abgaskühlermodul 10 auf der Niederdruckseite (2a, 3a) angeordnet ist, steht auch hier eine beliebig hohe Druckdifferenz zur Förderung des Abgasstromes am Verdichter 5 zur Verfügung, was aufgrund der Vielzahl von Komponenten in der AGR-Leitung 8 und hohen Abgasmassenströmen von Vorteil ist.The function of the illustrated EGR system is similar to Fig. 1a , initially with the difference that here is a two-stage cooling of the recirculated via the EGR line 8 exhaust stream. If no cooling is required or advantageous, both exhaust gas cooler 11, 12 by the bypass line 15 are bypassed. The amount of the recirculated exhaust gas 8 is controlled by the shut-off valve 16, wherein in the simplest cases, a black-and-white control (open or close) is sufficient. The particulate filter 17, which is provided in addition to the particulate filter 7 in the exhaust pipe 3a, prevents soot from accumulating in the exhaust pipes, not shown, of the two exhaust coolers 11, 12. Since the exhaust gas cooler module 10 on the low pressure side (2a, 3a) is arranged, is also here an arbitrarily high pressure difference for the promotion of the exhaust gas flow to the compressor 5 is available, which is due to the large number of components in the EGR line 8 and high exhaust gas mass flows of advantage.

Fig.2b zeigt ein weiteres Ausführungsbeispiel der Erfindung, d. h. ein AGR-System auf der Niederdruckseite des Motors 1 - für gleiche Teile werden gleiche Bezugszahlen wie in Fig. 1b und 2a verwendet. Im Unterschied zu Fig. 2a ist die Tubine (4) als zweistufiges Turbinensystem und der Verdichter (5) als zweistufiges Verdichtungssystem mit Zwischenkühlung ausgeführt, wie dieses in Fig. 1b beschrieben ist. 2b shows a further embodiment of the invention, ie an EGR system on the low pressure side of the engine 1 - for like parts, the same reference numerals as in Fig. 1b and 2a used. In contrast to Fig. 2a the tubing (4) is designed as a two-stage turbine system and the compressor (5) as a two-stage compression system with intermediate cooling, as in Fig. 1b is described.

Fig.2c zeigt ein weiteres Ausführungsbeispiel der Erfindung, d. h. ein AGR-System auf der Niederdruckseite des Motors 1 - für gleiche Teile werden gleiche Bezugszahlen wie in Fig. 2a verwendet. Im Unterschied zu Fig. 2a ist das als Absperrventil ausgebildete AGR-Ventil 16, welches ebenfalls in das Modul 10 integriert ist, d. h. mit den übrigen Teilen zu einer Baueinheit verbunden ist, stromabwärts der Abgaskühler 11, 12 und der Einmündungsstelle des Bypasskanals 15 angeordnet. Figure 2c shows a further embodiment of the invention, ie an EGR system on the low pressure side of the engine 1 - for like parts, the same reference numerals as in Fig. 2a used. In contrast to Fig. 2a is formed as a shut-off valve EGR valve 16, which is also integrated into the module 10, that is connected to the other parts to form a unit, downstream of the exhaust gas cooler 11, 12 and the junction point of the bypass channel 15 is arranged.

Fig.2d zeigt ein weiteres Ausführungsbeispiel der Erfindung, d. h. ein AGR-System auf der Niederdruckseite des Motors 1 - für gleiche Teile werden gleiche Bezugszahlen wie in Fig. 2a und 2c verwendet. Im Unterschied zu Fig. 2c ist die Tubine (4) als zweistufiges Turbinensystem und der Verdichter (5) als zweistufiges Verdichtungssystem mit Zwischenkühlung ausgeführt; wie dieses in Fig. 1b beschrieben ist. Figure 2d shows a further embodiment of the invention, ie an EGR system on the low pressure side of the engine 1 - for like parts, the same reference numerals as in Fig. 2a and 2c used. In contrast to Fig. 2c the tubing (4) is designed as a two-stage turbine system and the compressor (5) as a two-stage compression system with intermediate cooling; like this in Fig. 1b is described.

Fig. 3a zeigt ein weiteres Ausführungsbeispiel der Erfindung für ein AGR-System auf der Niederdruckseite des Motors 1, wobei wiederum gleiche Bezugszahlen für gleiche Teile verwendet werden. Auf der Niederdruckseite, d. h. zwischen dem Ansaugleitungsabschnitt 2a und dem Abgasleitungsabschnitt 3a ist eine Abgasrückführleiturig 8 angeordnet, die weitestgehend in ein Modul 18 integriert ist. Das Modul 18 weist wie das Modul 10 in Fig. 2a ebenfalls die Abgaskühler 11, 12, die Ventileinrichtung 13 mit Bypassklappe 14 sowie Bypasskanal 15 auf, und enthält ferner das Partikelfilter und/oder den Oxidationskatalysator 17. Abweichend gegenüber dem Ausführungsbeispiel gemäß Fig. 2 ist ein als Drei-Wege-Ventil ausgebildetes Mengenregelventil 19 (AGR-Ventil), welches an der Abzweigungsstelle von Abgasleitung 3a und AGR-Leitung 8 angeordnet ist. Durch das Regelventil 19 kann der Anteil an Abgas, welcher dem Gesamtabgasstrom entnommen wird, eingestellt werden. Dadurch ist eine genauere Regelung des rückgeführten Abgasmassenstromes möglich. Im Übrigen sind die Funktionen des Moduls 18 gleich gegenüber dem Modul 10 in Fig. 2a. Fig. 3a shows a further embodiment of the invention for an EGR system on the low pressure side of the engine 1, again with like reference numerals be used for the same parts. On the low-pressure side, ie between the intake line section 2a and the exhaust pipe section 3a, an exhaust gas recirculation guide 8 is arranged, which is largely integrated in a module 18. The module 18, like the module 10 in FIG Fig. 2a also the exhaust gas cooler 11, 12, the valve device 13 with bypass valve 14 and bypass channel 15, and further includes the particulate filter and / or the oxidation catalyst 17. Deviating from the embodiment according to Fig. 2 is a designed as a three-way valve flow control valve 19 (EGR valve), which is arranged at the branch point of the exhaust pipe 3a and EGR pipe 8. Through the control valve 19, the proportion of exhaust gas, which is taken from the total exhaust gas flow can be adjusted. As a result, a more accurate control of the recirculated exhaust gas mass flow is possible. Incidentally, the functions of the module 18 are equal to the module 10 in FIG Fig. 2a ,

Die Darstellungen der Module 10, 18 und ihrer Komponenten sind schematischer Art, d. h. es sind viele konstruktive Varianten möglich. Dies gilt zunächst für die Abgaskühler 11, 12, welche als Rohrbündel Wärmeübertrager mit geraden oder U-förmig gebogenen Rohren mit kreisförmigen, rechteckförmigen oder sonstigen Querschnitten ausgebildet sein können. Ebenso sind für die Bypasseinrichtung verschiedene Varianten bezüglich des Ventilschließgliedes, des zugehörigen Stellantriebes und des Bypasskanals (integriert oder separat) möglich. Entscheidend ist, dass die genannten Komponenten weitestgehend zu einer transportfähigen vorgefertigten Baueinheit zusammengefasst sind, die am Fahrzeug mit geringem Montage- und Zeitaufwand in das gesamte AGR-System einsetzbar und anschließbar ist. Daraus ergibt sich schließlich auch ein entscheidender Bauraumvorteil, da die Komponenten eine kompakte Multifunktionseinheit bilden.The illustrations of the modules 10, 18 and their components are schematic in nature, d. H. There are many constructive variants possible. This applies initially to the exhaust gas cooler 11, 12, which may be formed as a tube bundle heat exchanger with straight or U-shaped tubes with circular, rectangular or other cross-sections. Likewise, different variants with respect to the valve closure member, the associated actuator and the bypass channel (integrated or separate) are possible for the bypass device. It is crucial that the components mentioned are largely combined to a transportable prefabricated unit that can be used and connected to the vehicle with little installation and time in the entire EGR system. This ultimately results in a decisive space advantage, since the components form a compact multifunction unit.

Fig. 3b zeigt ein weiteres Ausführungsbeispiel der Erfindung für ein AGR-System auf der Niederdruckseite des Motors 1, wobei wiederum gleiche Bezugszahlen für gleiche Teile wie in Fig. 3a verwendet werden. Im Unterschied zu Fig. 3a ist die Tubine (4) als zweistufiges Turbinensystem und der Verdichter (5) als zweistufiges Verdichtungssystem mit Zwischenkühlung ausgeführt, wie dieses in Fig. 1b beschrieben ist. Fig. 3b shows a further embodiment of the invention for an EGR system on the low pressure side of the engine 1, again with the same reference numerals for the same parts as in Fig. 3a be used. In contrast to Fig. 3a the tubing (4) is designed as a two-stage turbine system and the compressor (5) as a two-stage compression system with intermediate cooling, as in Fig. 1b is described.

Fig. 4a zeigt ein weiteres Ausführungsbeispiel der Erfindung für ein AGR-System auf der Niederdruckseite des Motors 1, wobei wiederum gleiche Bezugszahlen für gleiche verwendet werden. Fig. 4a shows a further embodiment of the invention for an EGR system on the low pressure side of the engine 1, again using like reference numerals for the same.

Im Unterschied zu den vorhergehenden Ausführungsformen sind das AGR-Ventil 19, die Ventileinrichtung 13 und die Bypassklappe14 zu einer Baueinheit zusammengefasst, die ein Multifunktionsventil 26 bilden.In contrast to the previous embodiments, the EGR valve 19, the valve device 13 and the bypass flap 14 are combined to form a structural unit, which form a multi-function valve 26.

Fig. 4b zeigt ein weiteres Ausführungsbeispiel der Erfindung für ein AGR-System auf der Niederdruckseite des Motors 1, wobei wiederum gleiche Bezugszahlen für gleiche verwendet werden. Fig. 4b shows a further embodiment of the invention for an EGR system on the low pressure side of the engine 1, again using like reference numerals for the same.

Im Unterschied zu Fig. 4a ist die Tubine (4) als zweistufiges Turbinensystem und der Verdichter (5) als zweistufiges Verdichtungssystem mit Zwischenkühlung ausgeführt, wie dieses in Fig. 1b beschrieben ist.In contrast to Fig. 4a the tubing (4) is designed as a two-stage turbine system and the compressor (5) as a two-stage compression system with intermediate cooling, as in Fig. 1b is described.

Claims (10)

  1. Device for recirculating and cooling exhaust gas of an internal combustion engine (1), especially of a diesel engine, in a motor vehicle with an exhaust-gas recirculation (AGR) line (8), at least one exhaust-gas heat exchanger (11), and an exhaust-gas recirculation (AGR) valve (19), wherein a first and a second exhaust-gas heat exchanger (11, 12) are combined into one structural unit and form one module (10, 18), wherein the first and second exhaust-gas heat exchangers are connected one behind the other on the exhaust-gas side and are designed as high-temperature coolers (11) and low-temperature coolers (12), and the high-temperature cooler (11) can be cooled by a first cooling circuit as the cooling circuit of the internal combustion engine (1), and the low-temperature cooler (12) can be cooled by a second cooling circuit, wherein the high-temperature and the low-temperature coolers (11, 12) are connected to each other mechanically or materially, wherein the high-temperature cooler (11) is made from a different material than the low-temperature cooler (12), and the high-temperature cooler (11) is made from a corrosion-resistant stainless steel, and the low-temperature cooler (12) is made from aluminum, which is protected from corrosion, wherein the two exhaust-gas heat exchangers are operated with reverse flow, wherein the high-temperature cooler and the low-temperature cooler (11, 12) have a bypass channel (15) for the exhaust gas, wherein a bypass valve (13, 14), through which the exhaust-gas flow can be guided either through the coolers (11, 12) or through the bypass channel (15), is assigned to the bypass channel (15), and the AGR valve (16, 19) is integrated into the module (10, 18), wherein the AGR valve (16, 19) is arranged in front of the coolers (11, 12), wherein the AGR valve is a volume-controlling valve, which controls the mass flow that is recirculated, and the AGR valve is constructed as a three-way valve.
  2. Device according to claim 1, characterized in that the cooling agent of the first cooling circuit differs from the cooling agent of the second cooling circuit.
  3. Device according to one of the preceding claims 1 or 2, characterized in that the cooling agent of the first cooling circuit is gaseous and the cooling agent of the second cooling circuit is liquid or vice versa.
  4. Device according to one of the preceding claims, characterized in that the cooling agent of the first cooling circuit is preferably air and the cooling agent of the second cooling circuit is preferably a coolant or vice versa.
  5. Device according to one of the preceding claims, characterized in that the particulate filter forms one structural unit with the AGR valve (16).
  6. Device according to one of the preceding claims, characterized in that the high-temperature cooler (11) has an inlet diffuser in which a particulate filter and/or an oxidation-type catalytic converter (17) are arranged.
  7. Device according to one of the preceding claims, characterized in that it includes a first compressor stage (5a) and at least one other compressor stage (5b).
  8. Device according to one of the preceding claims, characterized in that it includes a first exhaust-gas turbine (4a) and at least one second exhaust-gas turbine (4b).
  9. Device according to one of the preceding claims, characterized in that it includes at least one intermediate heat exchanger (25), which is arranged preferably on the downstream side of the first compressor stage (5a) and on the inflow side of the second compressor stage (5b).
  10. Device according to one of the preceding claims, characterized in that the first exhaust-gas turbine (4a) is coupled to the second compressor stage (5b) and the second exhaust-gas turbine (4b) is coupled to the first compressor stage (5b).
EP06762098.9A 2005-06-24 2006-06-20 Device for recycling and cooling exhaust gas for an internal combustion engine Not-in-force EP1899595B1 (en)

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DE102005029322A DE102005029322A1 (en) 2005-06-24 2005-06-24 Device for recycling and cooling exhaust gas for an internal combustion engine
PCT/EP2006/005908 WO2006136372A1 (en) 2005-06-24 2006-06-20 Device for recycling and cooling exhaust gas for an internal combustion engine

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US8061334B2 (en) 2011-11-22
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US20090044789A1 (en) 2009-02-19

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