EP3387245B1 - Regulating device for an internal combustion engine - Google Patents

Regulating device for an internal combustion engine Download PDF

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Publication number
EP3387245B1
EP3387245B1 EP16795065.8A EP16795065A EP3387245B1 EP 3387245 B1 EP3387245 B1 EP 3387245B1 EP 16795065 A EP16795065 A EP 16795065A EP 3387245 B1 EP3387245 B1 EP 3387245B1
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EP
European Patent Office
Prior art keywords
exhaust gas
internal combustion
combustion engine
gas recirculation
regulating device
Prior art date
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Application number
EP16795065.8A
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German (de)
French (fr)
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EP3387245A1 (en
Inventor
Dirk VIERKOTTEN
Maximilian Flender
Christian Vigild
Andreas Kuske
Franz Arnd Sommerhoff
Jörg Kemmerling
Helmut Kindl
Vanco Smiljanovski
Hanno Friederichs
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.)
Pierburg GmbH
Ford Werke GmbH
Original Assignee
Pierburg GmbH
Ford Werke GmbH
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Publication of EP3387245A1 publication Critical patent/EP3387245A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
    • F02D9/1005—Details of the flap
    • F02D9/101—Special flap shapes, ribs, bores or the like
    • F02D9/1015—Details of the edge of the flap, e.g. for lowering flow noise or improving flow sealing in closed flap position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/08—Throttle valves specially adapted therefor; Arrangements of such valves in conduits
    • F02D9/10—Throttle valves specially adapted therefor; Arrangements of such valves in conduits having pivotally-mounted flaps
    • F02D9/1005—Details of the flap
    • F02D9/101—Special flap shapes, ribs, bores or the like
    • 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
    • F02M26/17—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the intake system
    • F02M26/21—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories in relation to the intake system with EGR valves located at or near the connection to the intake system
    • 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
    • F02M26/50—Arrangements or methods for preventing or reducing deposits, corrosion or wear caused by impurities
    • 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
    • F02M26/52—Systems for actuating EGR valves
    • F02M26/64—Systems for actuating EGR valves the EGR valve being operated together with an intake air throttle
    • 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
    • F02M26/65—Constructional details of EGR valves
    • F02M26/70—Flap valves; Rotary valves; Sliding valves; Resilient valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D9/00—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits
    • F02D9/02—Controlling engines by throttling air or fuel-and-air induction conduits or exhaust conduits concerning induction conduits
    • F02D2009/0201—Arrangements; Control features; Details thereof
    • F02D2009/0276—Throttle and EGR-valve operated together

Definitions

  • the invention relates to a control device for an internal combustion engine with an intake duct, an exhaust gas recirculation duct which opens into the intake duct, a housing in which the intake duct and the exhaust gas recirculation duct are formed, a shaft serving as an axis of rotation, on which a control body is eccentrically mounted, and the is arranged perpendicular to the central axes of the intake duct and the exhaust gas recirculation duct, a normal vector of a first surface of the control body pointing to the upstream side of the intake duct and in a second end position in a first end position in which the intake duct is at least throttled upstream of an opening of the exhaust gas recirculation duct and in which the exhaust gas recirculation channel is closed, a normal vector of a second surface of the control body faces the exhaust gas recirculation channel.
  • Such control devices are used in internal combustion engines to control the gas flow to be introduced into a cylinder of an internal combustion engine with regard to its composition of recirculated exhaust gas quantities or freshly drawn-in air quantities.
  • different mixing ratios must be set to achieve minimum exhaust gas values and maximum performance values.
  • Either two separate valves can be used for control, in which case total quantity control is also possible via the two valves, or these control valves contain two valve bodies which are actuated by a common actuating device, so that only the mixture is changed. This execution will used especially in supercharged engines where the total intake volume can be controlled via the performance of the compressor. In order to be able to make a corresponding control device even smaller, it is also known to use only one control body which interacts with both channels instead of two control bodies. In these designs, the exhaust gas recirculation duct usually opens into the air intake duct immediately downstream of the flap serving as a throttle valve.
  • the throttle valve is then closed to the same extent when the exhaust gas recirculation valve is opened, which in addition to increasing the free cross section of the exhaust gas recirculation duct also results in an increase in the pressure gradient in the exhaust gas recirculation duct, which increases the proportion of exhaust gas compared to the amount of air drawn in ,
  • Such an arrangement is for example in the DE 10 2012 101 851 B4 discloses, in which two flaps arranged in parallel are actuated via a common rotary shaft, so that with rotation of the two flaps the first flap moves away from the valve seat of the air intake duct, while the second flap moves away from the valve seat of the exhaust gas recirculation duct, which is arranged perpendicular to the valve seat of the air intake duct , approaches until the air intake duct is fully open and the exhaust gas recirculation duct is completely closed.
  • the valve seats are each designed as stops, against which the flaps rest circumferentially in their position closing the respective duct.
  • the rotating shaft is arranged on a housing wall between the mouth of the exhaust gas recirculation duct and the valve seat in the air intake duct, so that the flow is not influenced by the shaft.
  • a swirl generator is additionally arranged, by means of which a swirl is applied to the exhaust gas flow in order to improve mixing with the air flow.
  • a flap which is arranged in an intake duct and in the interior of which a duct is formed, through which exhaust gas flows, which is introduced into the air flow at the flap end opposite the shaft.
  • This arrangement ensures thorough mixing of the two gas flows, but both the manufacture of the flap is very complex and the connection of the exhaust gas recirculation channel to the flap interior is not possible without leakage. It is not possible to control the amount of exhaust gas returned with this flap.
  • Throttle valves are also known, but in which a throttle valve half is provided with wind deflectors to reduce noise emissions.
  • guide ribs are formed on the second surface, along which an exhaust gas stream flows into the intake duct when the exhaust gas recirculation channel opens, allows the recirculated exhaust gas stream to be directed into the intake duct.
  • condensation of the water in the exhaust gas can be avoided as well as a reduction in performance of the compressor due to poor flow against the impeller and resulting flow resistance due to turbulence.
  • a first valve seat is preferably formed in the intake duct, on which the control body rests with its first surface in its first end position. Such an axial support of the surface on the valve seat results in an almost leak-free closure of the intake duct.
  • a second valve seat is formed at the mouth of the exhaust gas recirculation duct, against which the second surface of the control body lies in its second end position with a region free of ribs.
  • the exhaust gas recirculation duct can also be sealed very well in spite of the guide ribs are closed by using an area for axially supporting the surface on the valve seat, on which no guide ribs are formed.
  • control body has an eccentrically fastened flap with the first and the second surface and a coupling member that extends from the second surface and on which a closing member is formed, which interacts with the second valve seat, wherein the guide ribs extend from the second surface up to the closing member.
  • the guide ribs advantageously extend parallel to one another along the second surface, as a result of which the exhaust gas flow is rectified, which leads to low pressure losses and enables the exhaust gas flow to be oriented in a targeted manner.
  • the guide ribs extend perpendicular to the axis of rotation of the control body.
  • the exhaust gas system is thus specifically introduced into the air flow with low pressure losses.
  • the mixed gas flow can thus be introduced in parallel and straight into a subsequent compressor inlet, which increases its efficiency.
  • the guide ribs can extend at a fixed angle to the axis of rotation of the control body.
  • an angle to the main flow direction of the air can be forced on the exhaust gas flow, as a result of which a spiral flow can be generated at the inlet of the compressor in order to improve performance.
  • the guide ribs inclined to one another in the direction of extension from the axis of rotation to the end remote from the axis of rotation.
  • a kind of fan is spanned by the ribs, the narrow end of which is formed on the side of the flap remote from the shaft.
  • the exhaust gas is bundled and can be introduced, for example, into areas away from the wall, as a result of which the condensation of water from the exhaust gas can be reduced in the case of cold pipe walls, thereby increasing the service life of the compressor.
  • the second surface is preferably curved.
  • Such a curvature also serves to direct the exhaust gas flow into a desired area. For example, with a convex configuration, there is an introduction into the air flow, with a concave configuration of the curvature, an introduction without great mixing with the air flow in the flow shadow of the flap.
  • the curvature is also used accordingly to direct the exhaust gas flow into the desired areas of the duct with the lowest possible pressure loss.
  • the guide ribs are preferably shaped in such a way that the exhaust gas flow can be introduced into a defined area of the intake duct. This may depend on the training and subsequent channel routing. Depending on the internal combustion engine, either thorough mixing, a stratified flow, straight or swirl flows may be desired. Depending on the required flow, a corresponding position of the guide ribs can be formed to improve the engine performance.
  • a plane spanned by the first valve seat to a plane spanned by the second valve seat Plane includes an angle of 70 ° to 80 °.
  • Such a smaller setting angle means that the air and exhaust gas flows are also changed over the entire setting range when the flap rotates. The slope of the control curve thus remains essentially unchanged in this setting range.
  • the first valve seat preferably has a smaller circumference than the section of the intake duct downstream of the first valve seat and the regulating body in its second end position closing the exhaust gas recirculation duct is immersed in a recess in the intake duct, which is arranged in the flow shadow of the upstream section of the intake duct.
  • a control device is thus created, with which both the air mass flow in the intake duct and the exhaust gas mass flow of the exhaust gas recirculation circuit can be regulated, the performance of a subsequent compressor for charging an internal combustion engine being optimized at the same time by improved flow guidance.
  • the flow guidance can be adapted by the guide ribs to the respective requirements of the internal combustion engine or to the existing inflow conditions of the compressor used. Preventing condensation of the water vapor conveyed with the exhaust gas prevents damage to the compressor and, in particular, to its fins.
  • the Figure 1 shows a perspective view of a control device according to the invention in a sectional view.
  • FIGS 2 a) to d schematically show possible arrangements of the guide ribs of a control device according to the invention.
  • the control device consists of a housing 10 which delimits an intake duct 12 and on which an opening 14 of an exhaust gas recirculation duct 16 is formed.
  • the intake duct 12 extends essentially in a straight direction to an axial inlet (not shown) of a compressor housing of a turbocharger, while the exhaust gas recirculation duct 16 opens into the intake duct 12 approximately perpendicularly to the latter.
  • the housing 10 consists of a first, essentially tubular suction housing 18, the downstream end of which is inclined and forms an angle ⁇ of approximately 80 ° to a central axis of the suction channel 12.
  • This suction housing 18 projects with this downstream end into a mixing housing 20, or is inserted into the mixing housing 20 until a flange 22 abuts, via which the suction housing 18 is fastened to the mixing housing 20 by means of screws 24.
  • the mouth 14 of the exhaust gas recirculation channel 16 projects laterally into an opening 26 of the mixing housing 20 and is designed as a separate housing part.
  • the mixing housing 20 forms an extension of the intake duct 12, which in turn subsequently opens into the axial inlet of the compressor housing.
  • a shaft 28 is rotatably mounted about an axis of rotation 30, which can be actuated via an actuator 32.
  • the axis of rotation 30 of this shaft 28 is arranged perpendicular to the central axes of the intake duct 12 and the exhaust gas recirculation duct 16 and is located between the mouth 14 of the exhaust gas recirculation duct 16 at the upstream end of the air flow Exhaust gas recirculation duct 16 and the axial end of the intake housing 18 on its side facing the exhaust gas recirculation duct 16.
  • the flow cross-section of the suction housing 18 is smaller than that of the mixing housing 20, the suction housing 18 being fastened to the mixing housing 20 in such a way that a recess 34 formed downstream of the mouth 14 of the exhaust gas recirculation channel 16 is arranged in the flow shadow of the air flow from the suction housing 18, in which the Shaft 28 penetrates the mixing housing 20.
  • a control body 36 is fastened, which consists of a flap 38 and a closing member 42 fastened to the first flap 38 via a coupling member 40.
  • the flap 38 extends from the shaft 28 into the interior of the mixing housing 20 and controls the flow cross-section of the intake duct 12.
  • the flap 38 cooperates with its first surface 44 with the axial end of the intake housing 18, which serves as the first valve seat 46, on which the flap 38, in the state closing the intake duct 12, rests with its first surface 44 in a first end position, so that in this state a normal vector of the first surface 44 faces the upstream side of the intake duct 12 or the intake housing 18.
  • a bore is formed in the flap 38, in which the coupling member 40 is fastened to the flap 38.
  • This coupling member 40 extends to the side opposite the suction housing 18 perpendicular to the flap 38 and penetrates with its opposite end the closing member 42, which in turn is attached to this end of the coupling member 40.
  • This fastening of the closing member 42 means that when the shaft 28 is rotated into a second end position, in which the closing member 42 rests on a second valve seat 48 formed at the end of the mouth 14 of the exhaust gas recirculation duct 16, the exhaust gas recirculation duct 16 closes.
  • a plurality of guide ribs 52 are formed on a second surface 50 opposite the first surface 44 of the flap 38 and extend from the second surface 50 to the closing member 42, so that these guide ribs 52 are arranged opposite to its mouth 14 when the exhaust gas recirculation channel 16 is closed, without extending into the mouth 14.
  • a normal vector of the second surface 50 points into the exhaust gas recirculation duct 16.
  • An exhaust gas stream is accordingly guided along these guide ribs 52 when the exhaust gas recirculation duct 16 is opened.
  • these guide ribs 52 run parallel to one another and perpendicular to the shaft 28. They are either integrally connected to the flap 38 or are produced in one piece with it.
  • the control body 36 consisting of the flap 38, the guide ribs 52, the closing member 42 and the coupling member 40 is now in the position shown in FIG Figure 1 position shown, the exhaust gas flow is introduced in the same direction as the air flow, so that a uniform, slow-moving mixing takes place without major turbulence and consequently with little pressure loss.
  • This low flow resistance means that a large amount of mixed gas can be supplied to the compressor via the compressor inlet, which increases the performance of the following internal combustion engine.
  • the Figure 2 c) shows a further possible formation of the guide ribs 52 on the surface 50.
  • the distance between these guide ribs 52 decreases with increasing distance from the shaft 28. This means that the guide ribs 52 have an inclination to one another.
  • the exhaust gas flow is bundled centrally accordingly. Any other bundling to another location of the intake duct 12 would also be conceivable with such a version, the central introduction of the exhaust gas stream having the advantage that the hot and water vapor-transporting exhaust gas stream is introduced into an area in which it is not directly related to the respective under certain circumstances, cold walls 56 of the intake duct 12 are routed. Accordingly, any condensation of the water that may occur is significantly reduced, which in turn prevents damage to the blades of the compressor.
  • the guide ribs 52 are again perpendicular to the axis of rotation 30, but they are located on a surface 58 which is concavely curved in cross section, which means that the exhaust gas flow is not conducted directly into the air flow, but instead a stratified flow occurs in the mixing housing 20 which can also prevent the exhaust gas stream from cooling too quickly by mixing it with a possibly cold air stream.
  • the control device described is thus suitable for the very exact metering of an exhaust gas mass flow into an air mass flow and for the exact control of the air mass flow with only one actuator, the flows being able to be directed almost arbitrarily by the use of guide ribs on the second surface of the flap in order to improve the performance of the Optimizing the internal combustion engine or the performance of a downstream compressor without having to use any further internals.
  • the exhaust gas flow can be rectified, bundled or subjected to a swirl by arranging the ribs accordingly. In addition, it can either be kept away from the air flow or be directed directly into it. In addition to degrees of mixing that can be influenced in this way flow resistance or condensation of the exhaust gas can be influenced.

Description

Die Erfindung betrifft eine Regelvorrichtung für eine Verbrennungskraftmaschine mit einem Ansaugkanal, einem Abgasrückführkanal, der in den Ansaugkanal mündet, einem Gehäuse, in dem der Ansaugkanal und der Abgasrückführkanal ausgebildet sind, einer als Drehachse dienenden Welle, auf der ein Regelkörper exzentrisch gelagert ist, und die senkrecht zu den Mittelachsen des Ansaugkanals und des Abgasrückführkanals angeordnet ist, wobei in einer ersten Endposition, in der der Ansaugkanal stromaufwärts einer Mündung des Abgasrückführkanals zumindest gedrosselt ist, ein Normalenvektor einer ersten Oberfläche des Regelkörpers zur stromaufwärtigen Seite des Ansaugkanals weist und in einer zweiten Endposition, in der der Abgasrückführkanal verschlossen ist, ein Normalenvektor einer zweiten Oberfläche des Regelkörpers zum Abgasrückführkanal weist.The invention relates to a control device for an internal combustion engine with an intake duct, an exhaust gas recirculation duct which opens into the intake duct, a housing in which the intake duct and the exhaust gas recirculation duct are formed, a shaft serving as an axis of rotation, on which a control body is eccentrically mounted, and the is arranged perpendicular to the central axes of the intake duct and the exhaust gas recirculation duct, a normal vector of a first surface of the control body pointing to the upstream side of the intake duct and in a second end position in a first end position in which the intake duct is at least throttled upstream of an opening of the exhaust gas recirculation duct and in which the exhaust gas recirculation channel is closed, a normal vector of a second surface of the control body faces the exhaust gas recirculation channel.

Derartige Regelvorrichtungen werden in Verbrennungskraftmaschinen genutzt, um den in einen Zylinder eines Verbrennungsmotors einzuleitenden Gasstrom bezüglich seiner Zusammensetzung von zurückgeführten Abgasmengen oder frisch angesaugten Luftmengen zu steuern. Je nach Betriebszustand des Verbrennungsmotors sind zur Erreichung minimaler Abgaswerte und maximaler Leistungswerte unterschiedliche Mischungsverhältnisse einzustellen.Such control devices are used in internal combustion engines to control the gas flow to be introduced into a cylinder of an internal combustion engine with regard to its composition of recirculated exhaust gas quantities or freshly drawn-in air quantities. Depending on the operating state of the internal combustion engine, different mixing ratios must be set to achieve minimum exhaust gas values and maximum performance values.

Für eine Regelung können entweder zwei getrennte Ventile verwendet werden, wobei dann auch eine Gesamtmengenregelung über die beiden Ventile möglich ist oder diese Regelventile enthalten zwei Ventilkörper, die über eine gemeinsame Stellvorrichtung betätigt werden, so dass lediglich das Gemisch verändert wird. Diese Ausführung wird insbesondere bei aufgeladenen Motoren, bei denen die Gesamtansaugmenge über die Leistung des Verdichters gesteuert werden kann, genutzt. Um eine entsprechende Regelvorrichtung noch kleiner ausführen zu können, ist es auch bekannt, statt zweier Regelkörper lediglich einen Regelkörper zu verwenden, der mit beiden Kanälen zusammenwirkt. Bei diesen Ausführungen mündet der Abgasrückführkanal üblicherweise unmittelbar stromabwärts der als Drosselventil dienenden Klappe in den Luftansaugkanal. Bei gewünschter Erhöhung der Abgasrückführrate wird dann mit Öffnen des Abgasrückführventils in gleichem Maße die Drosselklappe geschlossen, was neben der Erhöhung des freien Querschnitts des Abgasrückführkanals auch eine Erhöhung des Druckgefälles im Abgasrückführkanal zur Folge hat, wodurch der Anteil des Abgases im Vergleich zur angesaugten Luftmenge erhöht wird.Either two separate valves can be used for control, in which case total quantity control is also possible via the two valves, or these control valves contain two valve bodies which are actuated by a common actuating device, so that only the mixture is changed. This execution will used especially in supercharged engines where the total intake volume can be controlled via the performance of the compressor. In order to be able to make a corresponding control device even smaller, it is also known to use only one control body which interacts with both channels instead of two control bodies. In these designs, the exhaust gas recirculation duct usually opens into the air intake duct immediately downstream of the flap serving as a throttle valve. If the increase in the exhaust gas recirculation rate is desired, the throttle valve is then closed to the same extent when the exhaust gas recirculation valve is opened, which in addition to increasing the free cross section of the exhaust gas recirculation duct also results in an increase in the pressure gradient in the exhaust gas recirculation duct, which increases the proportion of exhaust gas compared to the amount of air drawn in ,

Eine derartige Anordnung wird beispielsweise in der DE 10 2012 101 851 B4 offenbart, bei der zwei parallel angeordnete Klappen über eine gemeinsame Drehwelle betätigt werden, so dass mit Drehung der beiden Klappen sich die erste Klappe vom Ventilsitz des Luftansaugkanals entfernt, während sich die zweite Klappe dem Ventilsitz des Abgasrückführkanals, der senkrecht zum Ventilsitz des Luftansaugkanals angeordnet ist, nähert, bis der Luftansaugkanal vollständig geöffnet ist und der Abgasrückführkanal vollständig verschlossen ist. Sowohl für die den Abgasrückführkanal beherrschende zweite Klappe als auch für die den Luftansaugkanal beherrschende erste Klappe sind die Ventilsitze jeweils als Anschläge ausgebildet, gegen die die Klappen in ihrer den jeweiligen Kanal verschließenden Stellung umfänglich aufliegen. Die Drehwelle ist an einer Gehäusewand zwischen der Mündung des Abgasrückführkanals und dem Ventilsitz im Luftansaugkanal angeordnet, so dass die Strömung nicht durch die Welle beeinflusst wird. Im Bereich der Mündung des Abgasrückführkanals ist zusätzlich ein Drallerzeuger angeordnet, über den dem Abgasstrom zur Verbesserung der Durchmischung mit dem Luftstrom ein Drall aufgeprägt wird.Such an arrangement is for example in the DE 10 2012 101 851 B4 discloses, in which two flaps arranged in parallel are actuated via a common rotary shaft, so that with rotation of the two flaps the first flap moves away from the valve seat of the air intake duct, while the second flap moves away from the valve seat of the exhaust gas recirculation duct, which is arranged perpendicular to the valve seat of the air intake duct , approaches until the air intake duct is fully open and the exhaust gas recirculation duct is completely closed. Both for the second flap dominating the exhaust gas recirculation duct and for the first flap dominating the air intake duct, the valve seats are each designed as stops, against which the flaps rest circumferentially in their position closing the respective duct. The rotating shaft is arranged on a housing wall between the mouth of the exhaust gas recirculation duct and the valve seat in the air intake duct, so that the flow is not influenced by the shaft. In the area of the mouth of the exhaust gas recirculation duct, a swirl generator is additionally arranged, by means of which a swirl is applied to the exhaust gas flow in order to improve mixing with the air flow.

Eine ähnliche Anordnung ist auch aus der DE 10 2014 200 699 A1 bekannt.A similar arrangement is also from the DE 10 2014 200 699 A1 known.

Zusätzlich ist aus der US 2009/0283076 A1 eine Klappe bekannt, die in einem Ansaugkanal angeordnet ist und in deren Innern ein Kanal ausgebildet ist, der mit Abgas durchströmt wird, welches am zur Welle entgegengesetzten Klappenende in den Luftstrom eingeleitet wird. Durch diese Anordnung wird eine gute Durchmischung der beiden Gasströme erreicht, jedoch ist sowohl die Herstellung der Klappe sehr aufwendig als auch der Anschluss des Abgasrückführkanals zum Klappeninnern nicht leckagefrei möglich. Eine Regelung der zurückgeführten Abgasmenge ist mit dieser Klappe nicht möglich.In addition, from the US 2009/0283076 A1 a flap is known which is arranged in an intake duct and in the interior of which a duct is formed, through which exhaust gas flows, which is introduced into the air flow at the flap end opposite the shaft. This arrangement ensures thorough mixing of the two gas flows, but both the manufacture of the flap is very complex and the connection of the exhaust gas recirculation channel to the flap interior is not possible without leakage. It is not possible to control the amount of exhaust gas returned with this flap.

Auch ist aus der DE 10 2006 051 987 B4 eine zentrisch gelagerte Drosselklappe bekannt, auf deren Oberfläche mehrere senkrecht zur Klappenwelle verlaufende Rippen ausgebildet sind, die dazu dienen, den Gasstrom zu begradigen.Is also from the DE 10 2006 051 987 B4 a centrally mounted throttle valve is known, on the surface of which a plurality of ribs extending perpendicular to the valve shaft are formed, which serve to straighten the gas flow.

Aus der DE 102 40 762 A1 und der JP 2001-098959 A sind ebenfalls Drosselklappen bekannt, bei denen jedoch eine Drosselklappenhälfte mit Windleitblechen versehen ist, um die Geräuschemissionen zu senken.From the DE 102 40 762 A1 and the JP 2001-098959 A Throttle valves are also known, but in which a throttle valve half is provided with wind deflectors to reduce noise emissions.

Durch diese bekannten Anordnungen wird zwar eine gute Regelung des Abgasrückführsystems bei Minimierung der Kosten und Bauteile erreicht, jedoch hat es sich gezeigt, dass insbesondere bei Niederdruckabgasrückführsystemen, durch bei der Mischung des Abgasstroms mit dem Luftstrom entstehende Turbulenzen, die Leistung des nachgeschalteten Verdichters des Turboladers oder eines elektrischen Verdichters negativ beeinflusst wird. Des Weiteren können Probleme aufgrund von Kondensation entstehen, falls der feuchte Abgasstrom direkt in den kalten Luftstrom oder gegen kalte Leitungswände geleitet wird. Diese im Gasstrom entstehenden Kondensate können ebenfalls Schäden am Verdichter verursachen.Although these known arrangements achieve good regulation of the exhaust gas recirculation system while minimizing costs and components, it has been shown that, in particular in the case of low-pressure exhaust gas recirculation systems, due to turbulence arising when the exhaust gas stream is mixed with the air stream, the performance of the downstream compressor of the turbocharger or of an electric compressor is negatively affected. Problems can also arise due to condensation if the moist exhaust gas flow is led directly into the cold air flow or against cold pipe walls. These condensates in the gas flow can also damage the compressor.

Es ist daher Aufgabe der Erfindung, eine Regelvorrichtung für eine Verbrennungskraftmaschine zu schaffen, mit der bei guter Regelbarkeit des Luftstroms und des Abgasstroms im Vergleich zu bekannten Ausführungen eine Leistungssteigerung eines nachgeschalteten Verdichters erreichbar ist und Schäden aufgrund von auftretender Kondensation zuverlässig vermieden werden kann.It is therefore an object of the invention to provide a control device for an internal combustion engine with which, with good controllability of the air flow and the exhaust gas flow in comparison to known designs, an increase in performance of a downstream compressor can be achieved and damage due to condensation occurring can be reliably avoided.

Diese Aufgabe wird durch eine Regelvorrichtung für eine Verbrennungskraftmaschine mit den Merkmalen des Hauptanspruchs gelöst.This object is achieved by a control device for an internal combustion engine with the features of the main claim.

Dadurch, dass auf der zweiten Oberfläche Leitrippen ausgebildet sind, entlang derer ein Abgasstrom beim Öffnen des Abgasrückführkanals in den Ansaugkanal strömt, kann der zurückgeführte Abgasstrom gerichtet in den Ansaugkanal geleitet werden. Je nach Ausführung und Anordnung der Leitrippen kann hierdurch sowohl eine Kondensation des Wassers im Abgas vermieden werden als auch eine Leistungsminderung des Verdichters durch eine schlechte Anströmung des Laufrades und entstehende Strömungswiderstände aufgrund auftretender Turbulenzen verhindert werden.The fact that guide ribs are formed on the second surface, along which an exhaust gas stream flows into the intake duct when the exhaust gas recirculation channel opens, allows the recirculated exhaust gas stream to be directed into the intake duct. Depending on the design and arrangement of the guide ribs, condensation of the water in the exhaust gas can be avoided as well as a reduction in performance of the compressor due to poor flow against the impeller and resulting flow resistance due to turbulence.

Vorzugsweise ist im Ansaugkanal ein erster Ventilsitz ausgebildet, an dem der Regelkörper mit seiner ersten Oberfläche in seiner ersten Endposition anliegt. Durch eine derartige axiale Auflage der Oberfläche auf dem Ventilsitz wird ein beinahe leckagefreier Verschluss des Ansaugkanals erreicht.A first valve seat is preferably formed in the intake duct, on which the control body rests with its first surface in its first end position. Such an axial support of the surface on the valve seat results in an almost leak-free closure of the intake duct.

Des Weiteren ist es vorteilhaft, wenn an der Mündung des Abgasrückführkanals ein zweiter Ventilsitz ausgebildet ist, gegen den die zweite Oberfläche des Regelkörpers in seiner zweiten Endposition mit einem leitrippefreien Bereich anliegt. So kann auch der Abgasrückführkanal trotz der Leitrippen sehr gut abgedichtet verschlossen werden, indem zur axialen Auflage der Oberfläche auf dem Ventilsitz ein Bereich genutzt wird, an dem keine Leitrippen ausgebildet sind.Furthermore, it is advantageous if a second valve seat is formed at the mouth of the exhaust gas recirculation duct, against which the second surface of the control body lies in its second end position with a region free of ribs. The exhaust gas recirculation duct can also be sealed very well in spite of the guide ribs are closed by using an area for axially supporting the surface on the valve seat, on which no guide ribs are formed.

In einer alternativen vorteilhaften Weiterbildung weist der Regelkörper eine exzentrisch auf der Welle befestigte Klappe mit der ersten und der zweiten Oberfläche und ein Koppelglied auf, dass sich von der zweiten Oberfläche aus erstreckt und an dem ein Schließglied ausgebildet ist, welches mit dem zweiten Ventilsitz zusammenwirkt, wobei sich die Leitrippen von der zweiten Oberfläche bis maximal zum Schließglied erstrecken.In an alternative advantageous development, the control body has an eccentrically fastened flap with the first and the second surface and a coupling member that extends from the second surface and on which a closing member is formed, which interacts with the second valve seat, wherein the guide ribs extend from the second surface up to the closing member.

Die Leitrippen erstrecken sich vorteilhafterweise parallel zueinander entlang der zweiten Oberfläche, wodurch ein Gleichrichten des Abgasstroms erfolgt, was zu geringen Druckverlusten führt und es ermöglicht, den Abgasstrom gezielt auszurichten.The guide ribs advantageously extend parallel to one another along the second surface, as a result of which the exhaust gas flow is rectified, which leads to low pressure losses and enables the exhaust gas flow to be oriented in a targeted manner.

In einer hierzu weiterführenden vorteilhaften Ausführungsform erstrecken sich die Leitrippen senkrecht zur Drehachse des Regelkörpers. Der Abgasstorm wird somit bei geringen Druckverlusten gezielt gerade in den Luftstrom eingeführt. Somit kann der Mischgasstrom parallel und gerade in einen nachfolgenden Verdichtereinlass eingeführt werden, wodurch dessen Wirkungsgrad erhöht wird.In a further advantageous embodiment, the guide ribs extend perpendicular to the axis of rotation of the control body. The exhaust gas system is thus specifically introduced into the air flow with low pressure losses. The mixed gas flow can thus be introduced in parallel and straight into a subsequent compressor inlet, which increases its efficiency.

Alternativ ist es möglich, dass sich die Leitrippen unter einem festen Winkel zur Drehachse des Regelkörpers angestellt erstrecken. Durch eine derartige Ausführung kann dem Abgasstrom ein Winkel zur Hauptströmungsrichtung der Luft aufgezwungen werden, wodurch eine spiralförmige Strömung zur Leistungsverbesserung am Eingang des Verdichters erzeugt werden kann.Alternatively, it is possible for the guide ribs to extend at a fixed angle to the axis of rotation of the control body. With such a design, an angle to the main flow direction of the air can be forced on the exhaust gas flow, as a result of which a spiral flow can be generated at the inlet of the compressor in order to improve performance.

Eine noch stärkere Spiralströmung bei verringertem Druckverlust wird erzielt, indem die Leitrippen mit wachsendem Abstand zur Drehachse eine wachsende Neigung zu einer Senkrechten auf die Drehachse aufweisen.An even stronger spiral flow with reduced pressure loss is achieved by the guide ribs with increasing distance from the axis of rotation have a growing inclination to a perpendicular to the axis of rotation.

Alternativ ist es vorteilhaft, die Leitrippen in Erstreckungsrichtung von der Drehachse aus zum von der Drehachse entfernten Ende zueinander geneigt auszubilden. Dies bedeutet, dass durch die Rippen eine Art Fächer aufgespannt wird, dessen schmales Ende an der von der Welle entfernten Seite der Klappe ausgebildet ist. Auf diese Weise wird das Abgas gebündelt und kann gezielt beispielswiese in wandentfernte Bereiche eingeleitet werden, wodurch die auftretende Kondensation von Wasser aus dem Abgas bei kalten Rohrwänden verringert werden kann, wodurch die Lebensdauer des Verdichter erhöht wird.Alternatively, it is advantageous to design the guide ribs inclined to one another in the direction of extension from the axis of rotation to the end remote from the axis of rotation. This means that a kind of fan is spanned by the ribs, the narrow end of which is formed on the side of the flap remote from the shaft. In this way, the exhaust gas is bundled and can be introduced, for example, into areas away from the wall, as a result of which the condensation of water from the exhaust gas can be reduced in the case of cold pipe walls, thereby increasing the service life of the compressor.

Vorzugsweise ist die zweite Oberfläche gewölbt ausgebildet. Eine derartige Wölbung dient ebenfalls zur Leitung des Abgasstroms in einen gewünschten Bereich. So ergibt sich beispielswiese bei einer konvexen Ausbildung eine Einleitung in den Luftstrom, bei einer konkaven Ausbildung der Wölbung eine Einleitung ohne große Durchmischung mit dem Luftstrom in den Strömungsschatten der Klappe. Die Wölbung wird entsprechend ebenfalls genutzt, um den Abgasstrom bei möglichst geringem Druckverlust in gewünschte Bereiche des Kanals zu leiten.The second surface is preferably curved. Such a curvature also serves to direct the exhaust gas flow into a desired area. For example, with a convex configuration, there is an introduction into the air flow, with a concave configuration of the curvature, an introduction without great mixing with the air flow in the flow shadow of the flap. The curvature is also used accordingly to direct the exhaust gas flow into the desired areas of the duct with the lowest possible pressure loss.

Entsprechend sind die Leitrippen vorzugsweise derart ausgeformt, dass der Abgasstrom in einen definierten Bereich des Ansaugkanals einleitbar ist. Dies kann von der Ausbildung und folgenden Kanalführungen abhängig sein. Je nach Verbrennungsmotor kann entweder eine gute Durchmischung, eine Schichtenströmung, gerade oder Drallströmungen gewünscht sein. Je nach geforderter Strömung kann zur Verbesserung der Motorleistung eine entsprechende Stellung der Leitrippen ausgebildet werden.Accordingly, the guide ribs are preferably shaped in such a way that the exhaust gas flow can be introduced into a defined area of the intake duct. This may depend on the training and subsequent channel routing. Depending on the internal combustion engine, either thorough mixing, a stratified flow, straight or swirl flows may be desired. Depending on the required flow, a corresponding position of the guide ribs can be formed to improve the engine performance.

Zusätzlich ist es vorteilhaft, wenn eine durch den ersten Ventilsitz aufgespannte Ebene zu einer durch den zweiten Ventilsitz aufgespannte Ebene einen Winkel von 70° bis 80° einschließt. Ein derartiger kleinerer Stellwinkel führt dazu, dass über den gesamten Stellbereich der Luft- und der Abgasstrom bei Drehung der Klappe ebenfalls geändert werden. In diesem Stellbereich bleibt somit die Steigung der Regelkurve im Wesentlichen unverändert.In addition, it is advantageous if a plane spanned by the first valve seat to a plane spanned by the second valve seat Plane includes an angle of 70 ° to 80 °. Such a smaller setting angle means that the air and exhaust gas flows are also changed over the entire setting range when the flap rotates. The slope of the control curve thus remains essentially unchanged in this setting range.

Vorzugsweise weist der erste Ventilsitz einen geringeren Umfang auf als der zum ersten Ventilsitz stromabwärtige Abschnitt des Ansaugkanals und der Regelkörper in seiner den Abgasrückführkanal verschließenden zweiten Endposition in einer Ausnehmung im Ansaugkanal eintaucht, die im Strömungsschatten des stromaufwärtigen Abschnitts des Ansaugkanals angeordnet ist. Dies bedeutet, dass bei geöffnetem Ansaugkanal kein Strömungswiderstand durch die Klappe vorhanden ist, so dass der Verdichter mit einem größeren Luftstrom versorgt wird. Zusätzlich wird der Kanal durch die anliegende Klappe im Wesentlichen verlängert, so dass eine Wirbelbildung hinter dem Ventilsitz, die ebenfalls zu Strömungsverlusten führen würde, auch verhindert wird.The first valve seat preferably has a smaller circumference than the section of the intake duct downstream of the first valve seat and the regulating body in its second end position closing the exhaust gas recirculation duct is immersed in a recess in the intake duct, which is arranged in the flow shadow of the upstream section of the intake duct. This means that when the intake duct is open, there is no flow resistance through the flap, so that the compressor is supplied with a larger air flow. In addition, the channel is essentially lengthened by the flap, so that a vortex formation behind the valve seat, which would also lead to flow losses, is also prevented.

Es wird somit eine Regelvorrichtung geschaffen, mit der sowohl der Luftmassenstrom im Ansaugkanal als auch der Abgasmassenstrom des Abgasrückführkreises regelbar ist, wobei gleichzeitig die Leistung eines nachfolgenden Verdichters zur Aufladung eines Verbrennungsmotors durch verbesserte Strömungsführung optimiert wird. Die Strömungsführung kann durch die Leitrippen an die jeweiligen Erfordernisse des Verbrennungsmotors beziehungsweise an die vorhandenen geforderten Einströmbedingungen des verwendeten Verdichters angepasst werden. Durch das Verhindern einer Kondensation des mit dem Abgas geförderten Wasserdampfes werden Schäden am Verdichter und insbesondere an dessen Berippung verhindert.A control device is thus created, with which both the air mass flow in the intake duct and the exhaust gas mass flow of the exhaust gas recirculation circuit can be regulated, the performance of a subsequent compressor for charging an internal combustion engine being optimized at the same time by improved flow guidance. The flow guidance can be adapted by the guide ribs to the respective requirements of the internal combustion engine or to the existing inflow conditions of the compressor used. Preventing condensation of the water vapor conveyed with the exhaust gas prevents damage to the compressor and, in particular, to its fins.

Ein Ausführungsbeispiel einer erfindungsgemäßen Regelvorrichtung ist in den Figuren dargestellt und wird nachfolgend beschrieben.An embodiment of a control device according to the invention is shown in the figures and is described below.

Die Figur 1 zeigt eine perspektivische Ansicht einer erfindungsgemäßen Regelvorrichtung in geschnittener Darstellung.The Figure 1 shows a perspective view of a control device according to the invention in a sectional view.

Die Figuren 2 a) bis d) zeigen schematisch mögliche Anordnungen der Leitrippen einer erfindungsgemäßen Regelvorrichtung. Figures 2 a) to d ) schematically show possible arrangements of the guide ribs of a control device according to the invention.

Die erfindungsgemäße Regelvorrichtung besteht aus einem Gehäuse 10, welches einen Ansaugkanal 12 begrenzt und an dem eine Mündung 14 eines Abgasrückführkanals 16 ausgebildet ist. Der Ansaugkanal 12 verläuft im Wesentlichen in gerader Richtung zu einem nicht dargestellten axialen Einlass eines Verdichtergehäuses eines Turboladers, während der Abgasrückführkanal 16 etwa senkrecht zum Ansaugkanal 12 in diesen mündet.The control device according to the invention consists of a housing 10 which delimits an intake duct 12 and on which an opening 14 of an exhaust gas recirculation duct 16 is formed. The intake duct 12 extends essentially in a straight direction to an axial inlet (not shown) of a compressor housing of a turbocharger, while the exhaust gas recirculation duct 16 opens into the intake duct 12 approximately perpendicularly to the latter.

Das Gehäuse 10 besteht aus einem ersten im Wesentlichen rohrförmig ausgebildeten Ansauggehäuse 18, dessen stromabwärtiges Ende schräg ausgebildet ist und einen Winkel α von etwa 80° zu einer Mittelachse des Ansaugkanals 12 einschließt. Dieses Ansauggehäuse 18 ragt mit diesem stromabwärtigen Ende in ein Mischgehäuse 20, beziehungsweise wird in das Mischgehäuse 20 bis zur Anlage eines Flansches 22 eingeschoben, über den das Ansauggehäuse 18 mittels Schrauben 24 am Mischgehäuse 20 befestigt ist.The housing 10 consists of a first, essentially tubular suction housing 18, the downstream end of which is inclined and forms an angle α of approximately 80 ° to a central axis of the suction channel 12. This suction housing 18 projects with this downstream end into a mixing housing 20, or is inserted into the mixing housing 20 until a flange 22 abuts, via which the suction housing 18 is fastened to the mixing housing 20 by means of screws 24.

Die Mündung 14 des Abgasrückführkanals 16 ragt seitlich in eine Öffnung 26 des Mischgehäuses 20 und ist als separates Gehäuseteil ausgebildet. Das Mischgehäuse 20 bildet eine Verlängerung des Ansaugkanals 12, der wiederum im Folgenden in den axialen Einlass des Verdichtergehäuses mündet. Im Mischgehäuse 20 ist eine Welle 28 um eine Drehachse 30 drehbar gelagert, die über einen Aktor 32 betätigt werden kann. Die Drehachse 30 dieser Welle 28 ist senkrecht zu den Mittelachsen des Ansaugkanals 12 und des Abgasrückführkanals 16 angeordnet und befindet sich zwischen der Mündung 14 des Abgasrückführkanals 16 am bezüglich des Luftstroms stromaufwärtigen Ende des Abgasrückführkanals 16 und dem axialen Ende des Ansauggehäuses 18 an dessen zum Abgasrückführkanal 16 gewandten Seite. Der Durchströmungsquerschnitt des Ansauggehäuses 18 ist kleiner als der des Mischgehäuses 20, wobei das Ansauggehäuse 18 derart am Mischgehäuse 20 befestigt ist, dass eine stromabwärtig zur Mündung 14 des Abgasrückführkanals 16 ausgebildete Ausnehmung 34 im Strömungsschatten des Luftstroms aus dem Ansauggehäuse 18 angeordnet ist, in der die Welle 28 das Mischgehäuse 20 durchdringt.The mouth 14 of the exhaust gas recirculation channel 16 projects laterally into an opening 26 of the mixing housing 20 and is designed as a separate housing part. The mixing housing 20 forms an extension of the intake duct 12, which in turn subsequently opens into the axial inlet of the compressor housing. In the mixing housing 20, a shaft 28 is rotatably mounted about an axis of rotation 30, which can be actuated via an actuator 32. The axis of rotation 30 of this shaft 28 is arranged perpendicular to the central axes of the intake duct 12 and the exhaust gas recirculation duct 16 and is located between the mouth 14 of the exhaust gas recirculation duct 16 at the upstream end of the air flow Exhaust gas recirculation duct 16 and the axial end of the intake housing 18 on its side facing the exhaust gas recirculation duct 16. The flow cross-section of the suction housing 18 is smaller than that of the mixing housing 20, the suction housing 18 being fastened to the mixing housing 20 in such a way that a recess 34 formed downstream of the mouth 14 of the exhaust gas recirculation channel 16 is arranged in the flow shadow of the air flow from the suction housing 18, in which the Shaft 28 penetrates the mixing housing 20.

An dieser exzentrisch im Ansaugkanal 12 angeordneten Welle 28 ist ein Regelkörper 36 befestigt, der aus einer Klappe 38 sowie einem über ein Koppelglied 40 an der ersten Klappe 38 befestigten Schließglied 42 besteht. Die Klappe 38 erstreckt sich von der Welle 28 aus in das Innere des Mischgehäuses 20 und beherrscht den Durchströmungsquerschnitt des Ansaugkanals 12. Hierzu wirkt die Klappe 38 mit ihrer ersten Oberfläche 44 mit dem axialen Ende des Ansauggehäuses 18 zusammen, das als erster Ventilsitz 46 dient, auf dem die Klappe 38 im den Ansaugkanal 12 verschließenden Zustand mit ihrer ersten Oberfläche 44 in einer ersten Endposition anliegt, so dass in diesem Zustand ein Normalenvektor der ersten Oberfläche 44 zur stromaufwärtigen Seite des Ansaugkanals 12 beziehungsweise zum Ansauggehäuse 18 weist.On this shaft 28, which is arranged eccentrically in the intake duct 12, a control body 36 is fastened, which consists of a flap 38 and a closing member 42 fastened to the first flap 38 via a coupling member 40. The flap 38 extends from the shaft 28 into the interior of the mixing housing 20 and controls the flow cross-section of the intake duct 12. For this purpose, the flap 38 cooperates with its first surface 44 with the axial end of the intake housing 18, which serves as the first valve seat 46, on which the flap 38, in the state closing the intake duct 12, rests with its first surface 44 in a first end position, so that in this state a normal vector of the first surface 44 faces the upstream side of the intake duct 12 or the intake housing 18.

In der Klappe 38 ist eine Bohrung ausgebildet, in der das Koppelglied 40 an der Klappe 38 befestigt ist. Dieses Koppelglied 40 erstreckt sich zur zum Ansauggehäuse 18 gegenüberliegenden Seite senkrecht zur Klappe 38 und durchdringt mit seinem gegenüberliegenden Ende das Schließglied 42, welches wiederum an diesem Ende des Koppelgliedes 40 befestigt ist. Diese Befestigung des Schließgliedes 42 führt dazu, dass bei Drehung der Welle 28 in eine zweite Endposition, in der das Schließglied 42 auf einem am Ende der Mündung 14 des Abgasrückführkanals 16 ausgebildeten zweiten Ventilsitz 48 aufliegt, ein Verschluss des Abgasrückführkanals 16 erfolgt.A bore is formed in the flap 38, in which the coupling member 40 is fastened to the flap 38. This coupling member 40 extends to the side opposite the suction housing 18 perpendicular to the flap 38 and penetrates with its opposite end the closing member 42, which in turn is attached to this end of the coupling member 40. This fastening of the closing member 42 means that when the shaft 28 is rotated into a second end position, in which the closing member 42 rests on a second valve seat 48 formed at the end of the mouth 14 of the exhaust gas recirculation duct 16, the exhaust gas recirculation duct 16 closes.

Erfindungsgemäß sind auf einer zur ersten Oberfläche 44 der Klappe 38 gegenüberliegenden zweiten Oberfläche 50 mehrere Leitrippen 52 ausgebildet, welche sich von der zweiten Oberfläche 50 bis zum Schließglied 42 erstrecken, so dass diese Leitrippen 52 bei verschlossenem Abgasrückführkanal 16 gegenüberliegend zu seiner Mündung 14 angeordnet sind, ohne sich in die Mündung 14 zu erstrecken. In dieser zweiten Endposition weist ein Normalenvektor der zweiten Oberfläche 50 in den Abgasrückführkanal 16. Ein Abgasstrom wird entsprechend bei Öffnung des Abgasrückfürkanals 16 entlang dieser Leitrippen 52 geleitet.According to the invention, a plurality of guide ribs 52 are formed on a second surface 50 opposite the first surface 44 of the flap 38 and extend from the second surface 50 to the closing member 42, so that these guide ribs 52 are arranged opposite to its mouth 14 when the exhaust gas recirculation channel 16 is closed, without extending into the mouth 14. In this second end position, a normal vector of the second surface 50 points into the exhaust gas recirculation duct 16. An exhaust gas stream is accordingly guided along these guide ribs 52 when the exhaust gas recirculation duct 16 is opened.

Im ersten in der Figur 1 dargestellten Ausführungsbeispiel verlaufen diese Leitrippen 52 parallel zueinander und senkrecht zur Welle 28. Sie sind entweder stoffschlüssig mit der Klappe 38 verbunden oder einstückig mit dieser hergestellt. Befindet sich nun der aus der Klappe 38, den Leitrippen 52, dem Schließglied 42 und dem Koppelglied 40 bestehende Regelkörper 36 in der in der Figur 1 dargestellten Position, wird der Abgasstrom gleichgerichtet zum Luftstrom in diesen eingeführt, so dass eine gleichmäßige langsam verlaufende Durchmischung ohne größere Turbulenzen und daraus folgend unter geringem Druckverlust stattfindet. Dieser geringe Strömungswiderstand führt dazu, dass eine große Mischgasmenge dem Verdichter über den Verdichtereinlass zugeführt werden kann, wodurch die Leistung des folgenden Verbrennungsmotors gesteigert wird.In the first in the Figure 1 In the exemplary embodiment shown, these guide ribs 52 run parallel to one another and perpendicular to the shaft 28. They are either integrally connected to the flap 38 or are produced in one piece with it. The control body 36 consisting of the flap 38, the guide ribs 52, the closing member 42 and the coupling member 40 is now in the position shown in FIG Figure 1 position shown, the exhaust gas flow is introduced in the same direction as the air flow, so that a uniform, slow-moving mixing takes place without major turbulence and consequently with little pressure loss. This low flow resistance means that a large amount of mixed gas can be supplied to the compressor via the compressor inlet, which increases the performance of the following internal combustion engine.

In diesem Zusammenhang sei darauf hingewiesen, dass es selbstverständlich auch möglich ist, auf das zusätzliche Koppelglied 40 und das zusätzliche Schließglied 42 zu verzichten und die zweite Oberfläche 50 der Klappe 38 direkt zum Verschließen des zweiten Ventilsitzes 48 zu nutzen. Bei einer derartigen Ausführung ist es lediglich notwendig, den auf dem zweiten Ventilsitz 48 aufliegenden Bereich nicht mit Leitrippen 52 auszuführen und die Leitrippen 52 so anzuordnen, dass die Drehbewegung der Welle 28 aus der den Abgasrückführkanal 16 verschließenden Endposition nicht durch ein Anschlagen der Leitrippen 52 an Kanalwänden 54 des Abgasrückführkanals 16 gestört wird.In this context, it should be pointed out that it is of course also possible to dispense with the additional coupling member 40 and the additional closing member 42 and to use the second surface 50 of the flap 38 directly to close the second valve seat 48. In such an embodiment, it is only necessary not to design the area resting on the second valve seat 48 with guide ribs 52 and to arrange the guide ribs 52 such that the rotary movement of the shaft 28 out of the exhaust gas recirculation channel 16 closing end position is not disturbed by striking the guide ribs 52 on the channel walls 54 of the exhaust gas recirculation channel 16.

In der Figur 2 sind verschiedene weitere vorteilhafte Ausbildungen dieser Leitrippen 52 dargestellt, deren Form und Anordnung je nach Ausführung und Größe des folgenden Verdichters und des Verbrennungsmotors sowie Einsatzbereichen unterschiedlich sein kann.In the Figure 2 Various further advantageous designs of these guide ribs 52 are shown, the shape and arrangement of which can vary depending on the design and size of the following compressor and the internal combustion engine, as well as areas of application.

So zeigt die Figur 2 a) Leitrippen 52 auf der zweiten Oberfläche 50 der Klappe 38, welche um einen Winkel von etwa 20° zu einer senkrechten auf die Drehachse der Welle 28 angestellt sind. Dies hat zur Folge, dass ein Abgasstrom durch diese Leitrippen 52 zur Seite abgelenkt wird und ein Drall im Mischgasstrom beim Eintritt des Abgasstroms in den Luftstrom erzeugt wird. Das führt zu einer schnelleren Durchmischung der beiden Gasströme und führt in der Regel zu einer Leistungssteigerung des Verdichters durch das drallförmige Einströmen.So it shows Figure 2a) Guide ribs 52 on the second surface 50 of the flap 38, which are set at an angle of approximately 20 ° to a perpendicular to the axis of rotation of the shaft 28. As a result, an exhaust gas flow is deflected to the side by these guide ribs 52 and a swirl is generated in the mixed gas flow when the exhaust gas flow enters the air flow. This leads to a faster mixing of the two gas flows and usually leads to an increase in performance of the compressor due to the swirling inflow.

Auch die in der Figur 2 b) dargestellte Version hat eine derartige Leistungssteigerung des folgenden Verdichters aufgrund eines aufgeprägten Dralls zur Folge, allerdings bei verringertem Strömungswiderstand und damit erhöhtem Gesamtmischgasstrom. In dieser Version sind die erneut parallel verlaufenden Leitrippen 52 bogenförmig ausgebildet, wobei die Neigung zur Senkrechten auf die Drehachse der Welle 28 mit wachsendem Abstand von der Welle 28 ebenfalls wächst. Durch diese allmähliche Ablenkung des Abgasstroms im Vergleich zur in Figur 2 a) dargestellten Version entstehen weniger Turbulenzen und daraus folgend verringert sich der Strömungswiderstand.Even those in the Figure 2 b) Version shown results in such an increase in performance of the following compressor due to an imposed swirl, but with reduced flow resistance and thus increased total mixed gas flow. In this version, the again parallel guiding ribs 52 are arcuate, the inclination to the perpendicular to the axis of rotation of the shaft 28 also increasing with increasing distance from the shaft 28. This gradual deflection of the exhaust gas flow compared to the in Figure 2a) Version shown less turbulence and consequently the flow resistance is reduced.

Die Figur 2 c) zeigt eine weitere mögliche Ausbildung der Leitrippen 52 auf der Oberfläche 50. Der Abstand dieser Leitrippen 52 zueinander sinkt mit wachsendem Abstand von der Welle 28, Dies bedeutet, dass die Leitrippen 52 eine Neigung zueinander aufweisen. Im dargestellten Ausführungsbeispiel wird der Abgasstrom entsprechend zentral gebündelt. Auch eine beliebige andere Bündelung an eine andere Stelle des Ansaugkanals 12 wäre mit einer solchen Version vorstellbar, wobei die zentrale Einleitung des Abgasstroms den Vorteil hat, dass der heiße und Wasserdampf transportierende Abgasstrom in einen Bereich eingeleitet wird, in dem er nicht direkt auf die je nach Umgebungsbedingungen unter Umständen kalten Wände 56 des Ansaugkanals 12 geleitet wird. Entsprechend wird eine gegebenenfalls auftretende Kondensation des Wassers deutlich verringert, wodurch wiederum Schäden an den Schaufeln des Verdichters vermieden werden.The Figure 2 c) shows a further possible formation of the guide ribs 52 on the surface 50. The distance between these guide ribs 52 decreases with increasing distance from the shaft 28. This means that the guide ribs 52 have an inclination to one another. In the illustrated Embodiment, the exhaust gas flow is bundled centrally accordingly. Any other bundling to another location of the intake duct 12 would also be conceivable with such a version, the central introduction of the exhaust gas stream having the advantage that the hot and water vapor-transporting exhaust gas stream is introduced into an area in which it is not directly related to the respective under certain circumstances, cold walls 56 of the intake duct 12 are routed. Accordingly, any condensation of the water that may occur is significantly reduced, which in turn prevents damage to the blades of the compressor.

Bei der in Figur 2 d) dargestellten Ausbildung sind die Leitrippen 52 wieder senkrecht zur Drehachse 30 ausgebildet, jedoch befinden sie sich auf einer im Querschnitt konkav gewölbten Oberfläche 58, was dazu führt, dass der Abgasstrom nicht direkt in den Luftstrom geleitet wird, sondern im Mischgehäuse 20 eine Schichtströmung entsteht, durch die ebenfalls ein zu schnelles Abkühlen des Abgasstroms durch ein Vermischen mit einem gegebenenfalls kalten Luftstrom verhindert werden kann.At the in Figure 2 d) In the illustrated embodiment, the guide ribs 52 are again perpendicular to the axis of rotation 30, but they are located on a surface 58 which is concavely curved in cross section, which means that the exhaust gas flow is not conducted directly into the air flow, but instead a stratified flow occurs in the mixing housing 20 which can also prevent the exhaust gas stream from cooling too quickly by mixing it with a possibly cold air stream.

Die beschriebene Regelvorrichtung eignet sich somit zur sehr exakten Dosierung eines Abgasmassenstroms in einen Luftmassenstrom und zur exakten Regelung des Luftmassenstroms mit nur einem Aktor, wobei die Strömungen durch die Verwendung von Leitrippen an der zweiten Oberfläche der Klappe beinahe beliebig gerichtet werden können, um die Performance der Verbrennungskraftmaschine beziehungsweise die Leistung eines nachgeschalteten Verdichters zu optimieren, ohne weitere Einbauten verwenden zu müssen. Der Abgasstrom kann hierzu durch entsprechende Anordnung der Rippen gleichgerichtet, gebündelt oder mit einem Drall beaufschlagt werden. Zusätzlich kann er entweder vom Luftstrom entfernt gehalten werden oder direkt in diesen hineingeleitet werden. Neben auf diese Weise beeinflussbaren Vermischungsgraden können Strömungswiderstände oder Kondensation des Abgases beeinflusst werden.The control device described is thus suitable for the very exact metering of an exhaust gas mass flow into an air mass flow and for the exact control of the air mass flow with only one actuator, the flows being able to be directed almost arbitrarily by the use of guide ribs on the second surface of the flap in order to improve the performance of the Optimizing the internal combustion engine or the performance of a downstream compressor without having to use any further internals. For this purpose, the exhaust gas flow can be rectified, bundled or subjected to a swirl by arranging the ribs accordingly. In addition, it can either be kept away from the air flow or be directed directly into it. In addition to degrees of mixing that can be influenced in this way flow resistance or condensation of the exhaust gas can be influenced.

Es sollte deutlich sein, dass der Schutzbereich der vorliegenden Anmeldung nicht auf das beschriebene Ausführungsbeispiel beschränkt ist. Es sind verschiedene Versionen der Stellung der Leitrippen ebenso denkbar, wie unterschiedliche Formen der Oberflächen der Klappe. Zusätzlich ist es, wie beschrieben möglich die Regelvorrichtung mit oder ohne zusätzliches Schließglied auszuführen.It should be clear that the scope of protection of the present application is not limited to the exemplary embodiment described. Different versions of the position of the guide ribs are conceivable, as are different shapes of the surfaces of the flap. In addition, as described, it is possible to design the control device with or without an additional closing element.

Claims (13)

  1. A regulating device for an internal combustion engines having
    an intake pipe (12),
    an exhaust gas recirculation pipe (16) that opens into said intake pipe (12),
    a housing (10) in which said intake pipe (12) and said exhaust gas recirculation pipe (16) are formed,
    a shaft (28) acting as an axis of rotation (30) on which a regulating element (36) is eccentrically mounted and which is arranged perpendicularly to the center lines of said intake pipe (12) and of said exhaust gas recirculation pipe (16),
    wherein in a first end position, in which said intake pipe (12) is at least throttled upstream of an opening of said exhaust gas recirculation pipe (16), a normal vector of a first surface (44) of said regulating element (36) points to the upstream side of said intake pipe (12), and in a second end position, in which said exhaust gas recirculation pipe (16) is closed, a normal vector of a second surface (50) of said regulating element (36) points to said exhaust gas recirculation pipe (16),
    characterized in that
    on said second surface (50) guide ribs (52) are formed along which an exhaust gas flow flows into said intake pipe (12) when said exhaust gas recirculation pipe (16) is opened.
  2. The regulating device for an internal combustion engine according to claim 1,
    characterized in that
    in the intake pipe (12) a first valve seat (46) is formed against which the first surface (44) of the regulating element (36) rests in its first end position.
  3. The regulating device for an internal combustion engine according to any one of claims 1 or 2,
    characterized in that
    at the opening (14) of the exhaust gas recirculation pipe (16) a second valve seat (48) is formed against which a guide-rib-free area of the second surface (50) of the regulating element (36) rests in its second end position.
  4. The regulating device for an internal combustion engine according to any one of claims 1 or 2,
    characterized in that
    the regulating element (36) comprises a damper (38) eccentrically fastened to the shaft (28) and having the first surface (44) and the second surface (50), and a coupling element (40) which extends from said second surface (50) and on which a closing member (42) is formed that cooperates with the second valve seat (48), wherein the guide ribs (52) extend from said second surface (50) maximally up to said closing member (42).
  5. The regulating device for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    the guide ribs (52) extend in parallel to each other along the second surface (50).
  6. The regulating device for an internal combustion engine according to claim 5,
    characterized in that
    the guide ribs (52) extend perpendicularly to the axis of rotation (30) of the regulating element (36).
  7. The regulating device for an internal combustion engine according to claim 5,
    characterized in that
    the guide ribs (52) extend such that they are positioned at a fixed angle to the axis of rotation (30) of the regulating element (36).
  8. The regulating device for an internal combustion engine according to claim 5,
    characterized in that
    the guide ribs (52), with an increasing distance to the axis of rotation (30), have an increasing inclination towards a normal to said axis of rotation (30).
  9. The regulating device for an internal combustion engine according to any one of claims 1 to 4,
    characterized in that
    the guide ribs (52) are formed such that they are inclined towards each other in the direction of extension from the axis of rotation (30) to the end distal to said axis of rotation (30).
  10. The regulating device for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    the second surface (50) is of a curved configuration.
  11. The regulating device for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    the guide ribs (52) are formed such that the exhaust gas flow is adapted to be introduced into a defined area of the intake pipe (12).
  12. The regulating device for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    a plane spanned by the first valve seat (46) includes an angle of 70° to 80° to a plane spanned by the second valve seat (48).
  13. The regulating device for an internal combustion engine according to any one of the preceding claims,
    characterized in that
    the first valve seat (46) has a smaller circumference than the section of the intake pipe (12) downstream of said first valve seat (46), and the regulating element (36) in its second end position, in which it closes the exhaust gas recirculation pipe (16), is inserted into a recess (34) in said intake pipe (12), which is arranged in the flow shadow of the upstream section of said intake pipe (12).
EP16795065.8A 2015-12-11 2016-11-14 Regulating device for an internal combustion engine Active EP3387245B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015121616.7A DE102015121616B4 (en) 2015-12-11 2015-12-11 Regulating device for an internal combustion engine
PCT/EP2016/077571 WO2017097540A1 (en) 2015-12-11 2016-11-14 Regulating device for an internal combustion engine

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EP3387245A1 EP3387245A1 (en) 2018-10-17
EP3387245B1 true EP3387245B1 (en) 2020-02-12

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US (1) US10767570B2 (en)
EP (1) EP3387245B1 (en)
CN (1) CN108431394B (en)
DE (1) DE102015121616B4 (en)
WO (1) WO2017097540A1 (en)

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Publication number Priority date Publication date Assignee Title
EP3669064B1 (en) * 2017-08-15 2021-04-21 Volvo Truck Corporation Vaned valve for exhaust gas recirculation line
DE102019115633A1 (en) * 2019-06-07 2020-12-10 Elringklinger Ag Valve device
DE102020112870B4 (en) * 2020-05-12 2022-03-24 Borgwarner Inc. Compressor device of a charging device for an internal combustion engine

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DE19649713A1 (en) 1996-11-30 1998-06-04 Daimler Benz Ag Intake for multi=cylinder combustion engine with exhaust gas re=circulation
JP2001098959A (en) * 1999-10-01 2001-04-10 Aisan Ind Co Ltd Throttle controller for internal combustion engine
US6824119B2 (en) * 2001-08-30 2004-11-30 Visteon Global Technologies, Inc. Throttle plate having reduced air rush noise and method
JP2004132236A (en) * 2002-10-09 2004-04-30 Aisan Ind Co Ltd Throttle control device
JP4592108B2 (en) 2008-05-14 2010-12-01 株式会社日本自動車部品総合研究所 Intake device for internal combustion engine
DE102012101851B4 (en) * 2012-03-06 2014-06-05 Pierburg Gmbh Abgaseinleitvorrichtung for an internal combustion engine
US9918496B2 (en) * 2013-07-24 2018-03-20 Altria Client Services Llc Electronic smoking article
DE102013223053A1 (en) * 2013-11-13 2015-05-28 Robert Bosch Gmbh Gas supply arrangement with controllable flow, in particular for supplying gas to an internal combustion engine in a motor vehicle
DE102014200698A1 (en) * 2014-01-16 2015-07-16 Ford Global Technologies, Llc Low-pressure EGR valve
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DE102006051987A1 (en) * 2005-11-04 2007-05-16 Aisan Ind Butterfly valve

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Publication number Publication date
US20190003401A1 (en) 2019-01-03
CN108431394B (en) 2020-11-24
DE102015121616A1 (en) 2017-06-14
CN108431394A (en) 2018-08-21
WO2017097540A1 (en) 2017-06-15
US10767570B2 (en) 2020-09-08
DE102015121616B4 (en) 2018-06-14
EP3387245A1 (en) 2018-10-17

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